KR100611273B1 - Composite power supply heat pump type airconditioner - Google Patents

Abstract

An object of the present invention is to reduce the running cost by miniaturizing an electric motor in a heat pump type air conditioner using an internal combustion engine and an electric motor as power sources.

In the combined power source heat pump type air conditioner, which is driven by the internal combustion engine 19, at least a part of the compressors used in a high demand load range is a variable displacement compressor 11A1, 11B1, 12A1, 12B1, and a control device. When the required load shifts from a high range to a low range, first, the internal combustion engine driving the compressor is operated at a low torque and high torque state which is energy efficient, and at the same time, the pushing down volume of the compressor driven by the internal combustion engine is reduced. In response to the change in the demand load, the power source of the compressor is switched from the internal combustion engine to the electric motor 13 when the demand load decreases within a range in which the demand load is low.

Compressors, variable displacement compressors, electric motors, internal combustion engines, control units

Description

Combined power source heat pump type air conditioning unit {COMPOSITE POWER SUPPLY HEAT PUMP TYPE AIRCONDITIONER}

BRIEF DESCRIPTION OF THE DRAWINGS Explanatory drawing which shows the whole structure of 1st Embodiment of the combined power source heat pump type air conditioning apparatus by this invention.

Fig. 2 is a diagram showing a compressor of the first embodiment and a drive unit thereof;

3 is an explanatory diagram of the operation of the first embodiment;

4 is an explanatory diagram showing an overall configuration of a second embodiment of the combined power source heat pump type air conditioner according to the present invention;

Fig. 5 shows a compressor of the second embodiment and a drive unit thereof;

6 is an explanatory diagram of the operation of the second embodiment;

Fig. 7 is an explanatory diagram showing the whole configuration of the third embodiment of the combined power source heat pump type air conditioner according to the present invention.

Fig. 8 shows a compressor of the third embodiment and a drive unit thereof;

9 is an explanatory diagram of the operation of the third embodiment;

10 is an explanatory diagram showing an overall configuration of a fourth embodiment of the combined power source heat pump type air conditioner according to the present invention;

Fig. 11 is a diagram showing a compressor of the fourth embodiment and a drive unit thereof;

12 is an explanatory diagram of the operation of the fourth embodiment;

Fig. 13 is a view corresponding to Fig. 2 showing an example of a combined power source heat pump type air conditioner according to the prior art.

14 is an explanatory diagram corresponding to FIG. 3 of the prior art shown in FIG.

Fig. 15 is an explanatory diagram showing an overall configuration of a fifth embodiment of the combined power source heat pump type air conditioner according to the present invention.

FIG. 16 is an explanatory diagram showing a control system of the embodiment shown in FIG. 15; FIG.

FIG. 17 is a diagram showing characteristics of an engine load with respect to the air conditioning load and the power generation load in the embodiment shown in FIG. 15; FIG.

FIG. 18 is a diagram showing characteristics of a running cost merit with respect to an air conditioning load of the combined power source heat pump type air conditioning apparatus shown in FIG. 15; FIG.

<Explanation of symbols for the main parts of the drawings>

11A1, 11B1, 11B2, 12A1, 12B1, 12B2: Compressor

11A1, 11B1, 12A1, 12B1: Variable Capacity Compressor

13: electric motor

13A: Variable Speed Motor (Inverter Motor)

13B: Constant speed motor (constant speed motor)

19: internal combustion engine (gas engine)

21, 119a: Indoor heat exchanger

25, 117a: outdoor heat exchanger

30: refrigerant circulation path

40: control unit

11: internal combustion engine (gas engine)

112: compressor

112d: clutch

113: power generation motor

115: refrigerant circulation path

120: commercial power

123: internal power line (internal AC power line)

124: control unit

A: predetermined load

[Document 1] Japanese Unexamined Patent Publication No. 2000-111198

[Document 2] Japanese Unexamined Patent Publication No. 2002-221371

The present invention relates to a combined power source heat pump type air conditioning (air conditioning) device in which a refrigerant is compressed by a compressor driven by an internal combustion engine and an electric motor.

In a heat pump type air conditioner, a compressor used to compress a refrigerant is usually driven by an internal combustion engine (gas engine) to reduce the running cost, and usually a predetermined rotational speed at which a stable output can be obtained. A fixed displacement compressor is driven by an internal combustion engine operating within the range. In the internal combustion engine, since the turndown ratio, which is the ratio between the maximum rotational speed and the minimum rotational speed at which a stable output can be obtained, is about 2 to 3, in this type of internal combustion engine drive compressor, the amount of refrigerant supplied is also limited to a certain range. On the other hand, in the air conditioner, it is necessary to continuously control the amount of refrigerant supplied from the outdoor unit to the indoor unit according to the load of the indoor unit, so that the excess refrigerant discharged from the compressor when the indoor unit load is low is passed through the control valve. Bypass control is performed to return to the suction side of the pump to reduce the supply amount of the coolant. However, in this method, the power consumed by the compressor has nothing to do with the bypass amount of the refrigerant, so there is a problem that the energy efficiency decreases when the load of the indoor unit decreases and the bypass amount increases.

As a technique for solving such a problem, there is a technique disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 2000-111198) and Patent Document 2 (Japanese Patent Laid-Open No. 2002-221371). In the technique of Patent Document 1, as shown in Fig. 13, the fixed displacement type compressor 1, which has a constant pushing volume, is selectively driven by the gas engine 2 via the clutch 2a, and is an inverter which is a variable speed electric motor. It is to drive selectively by the motor (3). In this technique, as shown in Fig. 14, in the range where the demand for the compressor is high, the fixed displacement compressor 1 is driven via the clutch 2a by the gas engine 2 operating at a predetermined rotation speed range. At the same time, by varying the rotation speed of the gas engine 2, the load variation of the range (50 to 100% in the illustrated example) is covered, while the drive load is driven by the inverter motor 3 while the required load is low. By varying the rotational speed, the variation of the load in the range (0 to 50% in the illustrated example) is covered.

In addition, in the technique of Patent Document 2, in an air conditioner using an electric motor (inverter motor) and a compressor driven by a prime mover other than the electric motor, heat storage means is provided in a line communicating the compressor with the indoor unit and the outdoor unit, and the air conditioning load is provided. When the temperature is low, the heat or cold heat is accumulated by the heat storage means by the excess refrigerant discharged from the compressor, and the accumulated heat or cold heat is extracted and used when the air conditioning load is large.

[Patent Document 1]

Japanese Patent Laid-Open No. 2000-111198

[Patent Document 2]

Japanese Patent Laid-Open No. 2002-221371

In the above-described technique of Patent Document 1, the compressor is driven by the gas engine in a range where the demand for high energy efficiency of operation by the gas engine is high, and the range where the demand load for lowering the energy efficiency of operation by the gas engine is low In this case, since the compressor is driven by an inverter motor which does not lower the energy efficiency even when the rotational speed is lowered, the overall energy efficiency can be improved. However, since the turndown ratio of the gas engine is usually about 2 to 3, the range of low demand loads that need to be covered by the inverter motor is considerably widened. Therefore, it is necessary to make the inverter motor to be large. As a result, the equipment cost increases, and the electric power has a higher energy cost than the gas, and thus there is a problem that the running cost increases even if the energy efficiency is improved.

In addition, in the above-described technique of Patent Document 2, heat storage means such as a heat storage tank is required, so that its installation cost increases, and an installation space is required, and the heat storage efficiency of the heat storage tank itself (including heat radiation during heat storage). In addition, there is also a problem such as energy loss due to heat loss during heat exchange. Moreover, in this technique, since night operation becomes a thermal storage operation mode, there also exists a restriction that air-conditioning operation cannot be performed continuously for 24 hours. Moreover, for the same reason as in the case of patent document 1, there also exists a problem which requires a large inverter motor. The present invention aims to solve each of these problems.

For this reason, the combined power source heat pump type air conditioner according to the invention of claim 1 includes a compressor for supplying a compressed refrigerant to a refrigerant circulation path provided with an indoor heat exchanger and an outside air heat exchanger, and operates within a predetermined rotation speed range. An internal combustion engine for selectively driving the engine, an electric motor for selectively driving the compressor, and an internal combustion engine for driving the compressor by the internal combustion engine in a range where the required load on the compressor is high and at the same time in a range where the demand load is low. A combined power source heat pump type air conditioning system comprising a control device for controlling an engine and an electric motor, wherein at least a part of a compressor used in a high load range is pushed into a variable displacement compressor capable of varying a wetting volume. The control unit can be used for variable capacity compression By changing the rotational speed of the internal combustion engine with the push-up volume of the machine at or near the maximum value, the internal combustion engine driving the compressor is first energy-efficient when the required load is changed from a high range to a low range. By operating at a good low rotational speed and high torque state and changing the pushing-down volume of the compressor driven by the internal combustion engine, it is possible to cope with fluctuations in the demand load, and the compressor in the case where the demand load is lowered within a low range. It is characterized by controlling to switch the power source from the internal combustion engine to the electric motor.

As shown in claim 2, in the combined power source heat pump type air conditioner according to claim 1, the compressor preferably comprises one variable displacement compressor selectively driven by an internal combustion engine and an electric motor.

As shown in claim 3, in the combined power source heat pump type air conditioner according to claim 1, the compressor comprises a first variable displacement compressor selectively driven by an internal combustion engine and an electric motor, and a first selectively driven by an internal combustion engine. It consists of two variable displacement compressors, and the control device connects and drives a 2nd variable displacement compressor to the said internal combustion engine in the range with high demand load, and if it moves to the low range from the high load demand range, a 2nd variable capacity compressor will start first. The internal combustion engine driving the type compressor is operated at an energy efficient low rotational speed and high torque state while changing the pushing-down volume of the second variable displacement compressor to cope with a change in the demand load, and the demand load range is low. If the demand load is lowered in the engine, the second variable displacement compressor is Deionized by preferably controlled to drive by connecting a first variable displacement compressor at the same time to stop the drive to the internal combustion engine or electric motor.

As shown in claim 4, in the combined power source heat pump type air conditioner according to claim 1, the compressor is a variable displacement compressor selectively driven by an internal combustion engine and an electric motor, and a fixed displacement type selectively driven by an internal combustion engine. The compressor consists of a compressor, and the control unit is connected to an internal combustion engine to drive both a variable displacement compressor and a fixed displacement compressor in a range where the demand load is high. And the internal combustion engine driving the fixed-capacity compressor to operate at an energy-efficient low-speed high-torque state while varying the push-down volume of the variable-capacity compressor to cope with the required load fluctuations, and the range of the low demanded load. If the demand load falls within the It is preferable to control the variable displacement compressor to be connected to the internal combustion engine or the electric motor to drive the motor while the drive is stopped from the engine.

As shown in claim 5, it is preferable that the electric motor of the combined power source heat pump type air conditioner of Claims 2-4 is a variable speed electric motor.

As shown in claim 6, the variable displacement compressor of the combined power source heat pump type air conditioner according to claims 2 to 4 is assumed to have a minimum push-down volume of substantially zero, and the electric motor is preferably a constant speed electric motor.

As shown in claim 7, in the combined power source heat pump type air conditioner according to claim 1, the electric motor is a variable speed electric motor, and the compressor is a fixed displacement compressor selectively driven by an internal combustion engine and a variable speed electric motor, and an internal combustion engine. And a variable displacement compressor that is selectively driven by the controller, and the control device drives both the fixed displacement compressor and the variable displacement compressor by connecting to the internal combustion engine in a range where the demand load is high, and a low range in a range where the demand load is high. First, the internal combustion engine driving the fixed displacement compressor and the variable displacement compressor is operated at low rotational speed and high torque, which is energy efficient, and at the same time changing the pushing volume of the variable displacement compressor to change the required load. Corresponding to the required load within a range of low demand load If the decrease is a fixed displacement compressor is preferably controlled to change the volume of the push jeothim to exit from the internal combustion engine and driving the variable capacity compressor by a variable speed motor for driving at the same time by the internal combustion engine.

As shown in claim 8, the combined power source heat pump type air conditioning apparatus according to claim 7 uses a variable displacement compressor having a minimum push-down volume of substantially zero instead of a fixed displacement compressor, and uses a constant speed motor instead of a variable speed motor. It is desirable to.

In order to solve the said subject, the combined power source heat pump type air conditioning apparatus which concerns on invention of Claim 9 is comprised as follows.

A compressor for supplying compressed refrigerant to a refrigerant circulation path having an indoor heat exchanger and an outdoor heat exchanger, an internal combustion engine that selectively drives the compressor by operating within a predetermined rotation speed range, and an electric motor for selectively driving the compressor. And a control device for controlling the internal combustion engine and the electric motor to drive the compressor by the internal combustion engine in a range where the demand load for the compressor is high, and to drive the compressor by the electric motor in a range where the demand load is low. A combined power source heat pump type air conditioner, comprising: an internal power supply line fed by a commercial power source and supplied to a heat pump type air conditioner, wherein the electric motor is a power generation motor having the function of a generator. In the load range where the air-conditioning load is greater than or equal to the predetermined load, By operating the engine, the clutch and the clutch are coupled to drive the compressor and the generator motor, and the compression and power generation simultaneous operation of power generation by the generator motor and feeding the heat pump type air conditioner itself is performed, and the air load range is less than the predetermined load. Control to control the operation of the internal combustion engine, the compressor, the clutch and the electric motor so as to disengage the clutch and to stop the internal combustion engine to feed the power generator motor from the internal power line to perform the electric operation driving the compressor. A combined power source heat pump type air conditioning apparatus comprising a device.

As shown in claim 10, in the combined power source heat pump type air conditioner according to claim 9, the control device has a running cost merit that is an air conditioning output per unit energy cost when the compressor and the power generator motor are driven by the internal combustion engine. In the air-conditioning load range which becomes larger than the running cost merit in the case of driving the said compressor by the said electric motor, the said air conditioning load range which carries out the said compression and power generation simultaneous operation, and the running cost merit in the latter case is larger than the running cost merit in the former case In the present invention, it is preferable to control the operation of the internal combustion engine, the compressor, the clutch, and the electric motor to perform the electric operation.

As shown in claim 11, in the combined power source heat pump type air conditioner according to claim 9 or 10, the power generator motor has a power generation capacity larger than the maximum value of the power supply capacity required by the heat pump type air conditioner, The control apparatus is configured to supply at least a portion of electric power supplied from the power generator motor to the internal power line via the internal power line to the commercial power supply side while the power generator is driven by the internal combustion engine. It is desirable to control the operation of the compressor, the clutch and the generator motor.

As shown in claim 12, in the combined power source heat pump type air conditioner according to any one of claims 9 to 11, it is preferable that the compressor has a variable pushing volume.

As shown in claim 13, in the combined power source heat pump type air conditioner according to any one of claims 9 to 12, the power generator motor is preferably built in the compressor.

As shown in claim 14, in the combined power source heat pump type air conditioner according to any one of claims 9 to 13, it is preferable to include switching means for switching the compression and power generation simultaneous operation and the electric operation.

As shown in claim 15, in the combined power source heat pump type air conditioner according to any one of claims 9 to 14, power generation by the power generating motor is the heat pump type air conditioner as an uninterruptible power supply at the time of power failure. It is preferable to feed on.

1 to 3, a description will be given of a first embodiment of a combined power source heat pump type air conditioner according to the present invention. As shown in Fig. 1, the combined power source heat pump type air conditioner of the first embodiment includes one outdoor unit 10 and a plurality of indoor units 20 which are installed in each chamber and can be individually operated and stopped. And a control device 40 for controlling the operation of the outdoor unit 10.

The outdoor unit 10 of the first embodiment includes one variable displacement compressor 11A1 that can be pushed within a predetermined range in accordance with a command from the outside to change the flip volume, and a discharge port of the compressor 11A1. An external air heat exchanger 25 and a four-way valve (switching valve) 14 provided in the refrigerant circulation path 30 connected to the 11a and the suction port 11b, and each of the refrigerant circulation paths 30 extending to each room. A plurality of indoor units 20 are provided in parallel at the distal ends of the pipelines 30b and 30c. The compressor 11A1 is connected to the inverter motor (variable speed motor) 13A integrally installed in the casing as shown in Fig. 2, and is operated within a predetermined rotation speed range and connected via the V belt and the clutch 19a. It is selectively driven by the water-cooled gas engine (internal combustion engine) 19. The four-way valve 14 switches the supply order of the refrigerant from the discharge port 11a of the compressor 11A1 to the external air heat exchanger 25 and the indoor heat exchanger 21 to switch heating and cooling. .

An oil separator 15 is provided in the middle of the pipeline 30a of the refrigerant circulation path 30 connecting the discharge port 11a of the compressor 11A1 to the inlet port of the four-way valve 14, and the bottom of the oil separator 15 is provided. The part communicates with the suction port 11b of the compressor 11A1 via the filter drier 32 and the capillary tube 31 to remove the foreign matter and water from the separated oil and return it to the compressor 11A1. The accumulator 16 and the double tube heat exchanger 33 are provided in the conduit 30d of the refrigerant circulation path 30 which connects the suction port 11b of the compressor 11A1 to the outlet port of the four-way valve 14. The remaining two switching ports of the four-way valve 14 are connected to each indoor unit 201 via the conduits 30b and 30c of the refrigerant circulation path 30, and the outside air heat exchanger 25 is in the middle of the one conduit 30b. It is installed. The external air heat exchanger 25 of this embodiment is two connected in parallel with each other, and is equipped with the fan 25a, respectively. The double tube heat exchanger 33 performs heat exchange between the cooling water of the gas engine 19 and the refrigerant.

The compressor 11A1 of the present embodiment is a scroll compressor comprising a fixed scroll and an orbiting scroll having an involute curve scroll wrap, which is formed between both scrolls and communicates with a compression chamber whose volume gradually decreases with operation. Passport 11c is provided. In the present embodiment, the bypass port 11c communicates with the accumulator 16 via a conduit 30e provided with a reducer valve (electromagnetic expansion valve) 17. The reducer valve 17 is controlled in a number of stages by the control device 40. By controlling the opening degree, the push-down volume of the compressor 11A1 is between 100% and 50%, which is the maximum value. Is changed to correspond to a change in the required load on the compressor 11A1. The control of the required load by the reduction of the push-down volume using such a reduce valve 17 has a slight decrease in energy efficiency compared with the bypass control according to the prior art described above.

The plurality of indoor units 20 arranged in each room are installed in parallel to the front ends of the conduits 30b and 30c of the refrigerant circulation path 30, respectively, and the indoor heat exchanger 21 and the outside air of the indoor heat exchanger 21 are respectively. It consists of the electromagnetic expansion valve 22 provided in series at the heat exchanger 25 side, and the capillary 23 and the check valve 24 connected in series with this electromagnetic expansion valve 22 in parallel. Each indoor heat exchanger 21 is provided with a sirocco fan 21a.

Next, the outline | summary of the general operation | movement of the combined power source heat pump type air conditioning apparatus of this 1st Embodiment is demonstrated. First, the operation during cooling operation will be described. When the compressor 11A1 is rotationally driven by the gas engine 19 (or by the inverter motor 13A) via the clutch 19a, the high temperature and high pressure gas phase refrigerant compressed by the compressor 11A1 is indicated by a broken arrow. As shown, it enters the outside air heat exchanger 25 from the four-way valve 14 through the pipeline 30b, and is cooled and liquefied by the outside air supplied from the fan 25a. The liquefied high-pressure refrigerant passes through the electromagnetic expansion valve (22) from the conduit (30b), depressurizes, enters the indoor heat exchanger (21), vaporizes, and deprives the latent heat of vaporization from the indoor heat exchanger (21). Cool). The air fed into the room from the sirocco fan 21a is cooled when passing through the room heat exchanger 21, whereby the room is cooled. The vaporized refrigerant enters the accumulator 16 through the conduit 30d provided with the four-way valve 14 and the double tube heat exchanger 33 from the conduit 30c, and gaseous liquid is separated from the accumulator 16 so that the compressor 11A1. ), And then compressed again to repeat the cooling cycle described above to cool the room.

In the heating operation, the high temperature and high pressure gaseous refrigerant compressed by the compressor 11A1 enters the indoor heat exchanger 21 from the four-way valve 14 through the pipeline 30c as indicated by the solid arrows. The air fed into the room from the sirocco fan 21a is heated by the high temperature and high pressure gaseous refrigerant when passing through the indoor heat exchanger 21, whereby the room is heated, and the gaseous refrigerant is cooled and liquefied. The liquefied high pressure refrigerant passes through the electromagnetic expansion valve 22 and is decompressed to enter the outside air heat exchanger 25 from the conduit 30b, and vaporize the latent heat of vaporization from the outside air supplied from the fan 25a. The capillary tube 23 and the check valve 24 provided in parallel with the electromagnetic expansion valve 22 reduce the degree of expansion by the electromagnetic expansion valve 22 in the case of heating than in the case of cooling. The vaporized refrigerant enters the accumulator 16 through the conduit 30d provided with the four-way valve 14 and the double tube heat exchanger 33 from the conduit 30b, and gaseous liquid is separated from the accumulator 16 so that the compressor 11A1. ), And then compressed again to heat the room by repeating the above heating cycle.

During the cooling and heating, the control device 40 that controls the operation of the combined power source heat pump type air conditioner measures the amount of circulation of the refrigerant required by each indoor unit 20, and the set temperature of each indoor unit 20, each room. The outdoor unit 10 calculates the integrated value as the required circulation amount of the refrigerant and calculates the accumulated value according to the capacity of the heat exchanger 21, the intake temperature, the heating and cooling temperatures, and the like, and the required load on the compressor 11A1 matches the required circulation amount. To control. In other words, the controller 40 calculates the required value by changing the rotational speed of the gas engine 19 with the pushed-up volume of the variable displacement compressor 11A1 as the maximum value in the range where the calculated refrigerant has a large integrated value, and thus the required load is high. Correspond to load fluctuations. When the required load shifts from a high range to a low range, the control device 40 first causes the gas engine 19 driving the compressor 11A1 to operate at a low rotational speed high torque state at a constant rotational speed with good energy efficiency. At the same time, by changing the pushing-down volume of the compressor 11A1 driven thereby, it corresponds to the change in the required load. When the demand load is lowered within the range where the demand load is low and the change in the pushing capacity of the variable displacement compressor 11A1 becomes unable to cope with the change in the demand load, the control device 40 determines that the compressor 11A1 The gas engine 19, the clutch 19a, the variable displacement compressor 11A1, the reducer valve 17, and the like, are switched from the gas engine 19 to the inverter motor 13A to correspond to the required load variations. To control its operation.

Next, the operation of the combined power source heat pump type air conditioner of the first embodiment will be described in detail with reference to FIG. In the first embodiment, the gas engine 19 is operated in the range of 1200 to 2400 r / min, and the minimum pushing up volume of the variable displacement compressor 11A1 is 50% of the maximum pushing up volume. The required load for the compressor 11A1 of the outdoor unit 10 is the air conditioning capacity required for each indoor unit 20, that is, the refrigerant of the above-described refrigerant, as indicated by the solid line in the line showing the air conditioning capability in FIG. It increases in proportion to the required circulation amount of the refrigerant which is an integrated value of the circulation amount. In addition, the value of the air-conditioning capacity is represented by making 100% the value when the push-down volume of the variable displacement compressor 11A1 is the maximum and it drives at 2400 r / min.

The range of 0 to 25% in which the required load on the compressor 11A1 is the maximum is in the range where the required load is low, and the required load is lowered, thus operating the gas engine 19 operating at a low rotational speed and high torque as described above. The change in the pushing-down volume of the variable displacement compressor 11A1 driven by Y) is in a state in which it is impossible to cope with the change in the required load. In this range, the control device 40 releases the clutch 19a and stops the gas engine 19 to drive the compressor 11A1 by the inverter motor 13A. In this range, the pushing-down volume of the compressor 11A1 is fixed at the maximum value, and the rotational speed of the inverter motor 13A is controlled to increase gradually from zero with the increase of the required load, and the amount of refrigerant discharged from the compressor 11A1 is It increases linearly from 0 to 25% as the demand load increases.

Next, in the range of 25 to 50% of the maximum required load, the required load is not lower but the required load is not lowered, and the gas engine 19 operating at a low rotational speed and high torque as described above. It is a state which respond | corresponds to the fluctuation of a request | requirement load by the change of the pushing-down volume of the variable displacement compressor 11A1 driven by. In this range, the control device 40 stops the operation of the inverter motor 13A, operates the gas engine 19 to engage the clutch 19a to drive the compressor 11A1 by the gas engine 19. , The throttle opening of the gas engine 19 is controlled so that the rotational speed is a constant value of the energy-efficient low rotational speed of 1200 r / min. In addition, the control device 40 controls the opening degree of the reducer valve 17 from fully open to fully closed, thereby controlling the pushing-down volume of the compressor 11A1 from 50% at the position where the required load is 25%, Gradually increase to 100% at the required load of 50%. As a result, in this range, the amount of refrigerant discharged by the compressor 11A1 increases linearly from 25% to 50% in accordance with the increase in the required load.

In addition, the range in which the required circulation amount is 50 to 100% is within a range in which the required load is high and the change in the rotational speed of the gas engine 19 is made to correspond to the change in the required load by maximizing the pushing-down volume of the compressor 11A1. . In this range, the control device 40 continuously stops the operation of the inverter motor 13A to drive the compressor 11A1 by the gas engine 19, and the compressor in the state in which the reduce valve 17 is completely closed. By maintaining the pushing down volume of 11A1 at 100%, the throttle opening degree of the gas engine 19 is controlled so that the rotational speed increases from 1200 r / min to 2400 r / min. As a result, in this range, the amount of refrigerant discharged from the compressor 11A1 increases linearly from 50% to 100% in accordance with the increase in the required load.

As described above, according to the combined power source heat pump type air conditioning apparatus of the first embodiment, the compressor 11A1 in a wide range (refer to the range of the gray hair arrow E in the lower part of FIG. 3) in which the required load is a maximum of 25 to 100%. Can be driven by the gas engine 19, and the range in which the compressor 11A1 is driven by the inverter motor 13A (see the range of the gray hair arrow M in the lower part of FIG. 3) is 0 to 25%. Since the inverter motor can be reduced from the prior art shown in Fig. 13, the inverter motor 13A is sufficient to be small. This reduces the installation cost and increases the use range of the fuel gas for the internal combustion engine, which has a lower energy cost than the electric power, so that the running cost of the combined power source heat pump type air conditioner can be reduced.

In addition, in the above-described first embodiment, the range in which the compressor 11A1 can be driven by the gas engine 19 is in the range of 25 to 100% where the required load is the maximum, but the minimum push of the variable displacement compressor 11A1 is achieved. If the flip volume is pushed up to 50% or less of the flip volume, this range can be expanded to the smaller side. For example, if this minimum pushing down volume is 30% of the maximum pushing down volume, the range of the required load when the compressor 11A1 is driven by the gas engine 19 as indicated by the broken arrow following the gray hair arrow E is shown. Can be expanded to 15%. Assuming that the same compressor 11A1 is used continuously, the compressor 11A1 can be driven by either the gas engine 19 or the inverter motor 13A in the range where the required load is 15 to 25%. Therefore, a larger cost merit can be selected from both of them. Alternatively, the compressor 11A1 can be downsized by the range in which the required load is widened.

In the above-described first embodiment, the compressor 11A1 is a scroll compressor, and the bypass port 11c communicates with the suction port 11b side by the pipeline 30e provided with the reducer valve 17. The reducer 17 is controlled by the control device 40 to change the pushing down volume of the compressor 11A1, and a simple scroll compressor is used as the compressor. The manufacturing cost can be reduced. However, the present invention is not limited thereto, and a vane pump having a variable pushing amount by changing the eccentricity of the cam ring for the rotor or a reciprocating piston compressor having a variable pushing amount by changing the piston stroke can be used. There is also. According to the latter, it is possible to reduce the cylinder contents at the time of the most compression so that the minimum pushing down volume is substantially zero. When the minimum pushing down volume is substantially zero as the compressor 11A1, the present invention may be implemented by using the constant speed motor 13B instead of the inverter motor 13A which is a variable speed motor. In this case, the change of the required load when the compressor 11A1 is driven by the constant speed motor 13B may be performed by changing the pushing down volume of the compressor 11A1.

In addition, in the first embodiment described above, the single compressor 11A1 is driven by the gas engine 19 and the inverter motor 13A (or the constant speed motor 13B). Thus, the most simplified combined power source heat pump type air conditioning is provided. Get the device.

Next, the second embodiment of the combined power source heat pump type air conditioner according to the present invention will be described with reference to FIGS. The second embodiment differs only in the structure in which the compressor of the outdoor unit 10 is composed of two variable displacement compressors 11A1 and 12A1 and the related structure thereof, within the same predetermined rotational speed range as in the first embodiment. It has a gas engine 19 which is operated. The two variable displacement compressors 11A1 and 12A1 of the second embodiment are both scroll compressors having bypass ports 11c and 12c similar to those of the first embodiment, and as shown in FIG. The variable displacement compressor 11A1 is selectively driven by the gas engine 19 connected via the clutch 19a and the inverter motor 13A integrally installed in the casing, in the same manner as in the first embodiment. The two variable displacement compressor 12A1 is selectively driven by the gas engine 19 connected via the clutch 19b. The bypass ports 11c and 12c of the first and second compressors 11A1 and 12A1 communicate with the accumulator 16 via the conduits 30e1 and 30e2 provided with reduce valves 17a and 17b, respectively. have. The opening degree of each reducer valve 17a and 17b is respectively controlled by the control apparatus 40, so that each pushing-down volume of each compressor 11 and 12 is 100%-50% of the maximum independent of each other, It changes between and respond | corresponds to the change of the request load to the compressors 11A1 and 12A1. Since the structure of this 2nd Embodiment is the same as that of 1st Embodiment except the above-mentioned difference, the detailed description hereafter is abbreviate | omitted.

Next, the operation of the combined power source heat pump type air conditioner of the second embodiment will be described in detail with reference to FIG. The gas engine 19 is operated in the range of 1200 to 2400 r / min, similar to the first embodiment, such that the minimum pushing down volumes of the first and second variable displacement compressors 11A1 and 12A1 are equal to the maximum pushing down volume. 50%. The required load is the same as in the first embodiment.

In the range of 0 to 25% of the required load in a state in which the demand load is in a low range and the demand load is in a low range, the control device 40 detaches both the clutches 19a and 19b and at the same time the gas engine 19 The first compressor 11A1 is driven by the inverter motor 13A. In this range, the pushing-down volume of the first compressor 11A1 is fixed at the maximum value, and the rotational speed of the inverter motor 13A is controlled to increase gradually from zero with the increase of the required load, and the first compressor 11A1 is discharged. The amount of refrigerant to be increased linearly from 0 to 25% as the required load increases.

Next, in the range of 25 to 50% of the required load in a state where the demand load is in the low range but the demand load is not lowered, the control device 40 stops the operation of the inverter motor 13A, and the gas By operating the engine 19 to engage only the clutch 19b to drive the second compressor 12A1 by the gas engine 19, the throttle opening of the gas engine 19 is controlled so that the rotational speed is energy efficient. Control to achieve a good low rotational speed of 1200 r / min. In addition, the control device 40 controls the opening degree of the reducer valve 17b from fully open to fully closed, thereby controlling the pushing-down volume of the second compressor 12A1 at 50% at the position where the required load is 25%. From 100% at the position where the required load is 50%. As a result, in this range, the amount of the refrigerant discharged by the second compressor 12A1 increases linearly from 25% to 50% in accordance with the increase in the required load.

Moreover, in the range of 50 to 100% of the required circulation amount in the range with a high demand load, the control apparatus 40 continues to drive only the 2nd compressor 12A1 by the gas engine 19, and will operate the reduce valve 17b. The push-down volume of the second compressor 12A1 is maintained at 100% in the state of full closure, thereby controlling the throttle opening of the gas engine 19 so that its rotational speed increases from 1200 r / min to 2400 r / min. To control. As a result, in this range, the amount of the refrigerant discharged by the second compressor 12A1 increases linearly from 50% to 100% according to the increase in the required load.

As described above, according to the combined power source heat pump type air conditioner of the second embodiment, as in the case of the first embodiment, the range M for driving the first compressor 11A1 by the inverter motor 13A (Fig. 6) can be reduced to a range of 0 to 25%, whereby the inverter motor 13A is sufficient to be small, thereby reducing the equipment cost, and also the use range of the fuel gas for the internal combustion engine, which is low in energy cost compared to electric power. Because of the increase, the running cost of the combined power source heat pump type air conditioner can be reduced.

Also in the second embodiment, when the minimum pushing down volume of the second variable displacement compressor 12A1 is 50% or less of the maximum pushing down volume, the change range of the required load when driven by the gas engine 19 is set. Since it can expand to 25% or less which is the maximum value, and the range L (refer FIG. 6) extended here, since the 1st compressor 11A1 can be driven by either the gas engine 19 and the inverter motor 13A, Of these, you can choose the one with the higher cost merit. In addition, when the minimum pushing down volume is substantially 0 as the first compressor 11A1, the present invention may be implemented by using a constant speed motor instead of the inverter motor 13A which is a variable speed motor.

In the second embodiment described above, in the range where the required load is 25 to 100%, only the second compressor 12A1 is described as being driven by the gas engine 19, but the two clutches 19a and 19b are coupled to each other. It is also possible to drive both compressors 11A1 and 12A1 simultaneously. By doing so, since the maximum capacity of each compressor 11A1 and 12A1 when the maximum air-conditioning capacity is the same is half, a combined power source heat pump type air conditioner can be miniaturized.

Next, the third embodiment of the combined power source heat pump type air conditioner according to the present invention will be described with reference to FIGS. In the third embodiment, as shown in Fig. 8, one of the two compressors of the outdoor unit 10 operates with the inverter motor 13A provided integrally to the casing within a predetermined rotational speed range, and V is used. A variable displacement compressor (11B1) selectively driven by a water-cooled gas engine (19) connected via a belt and a clutch (19a), and the other, selectively by the gas engine (19) via a clutch (19b). It is set as the fixed displacement compressor 12B2 to be driven. The compressor 11B1 is an inclined plate type axial piston compressor whose variable pushing angle is changed by changing the piston stroke with a variable inclination angle, for example, and the minimum pushing amount is substantially zero. The maximum capacity of the variable displacement compressor 11B1 and the capacity of the fixed displacement compressor 12B2 are half of the maximum capacity of the variable displacement compressor 11A1 of the first embodiment. Since other configurations are the same as those in the second embodiment, detailed description thereof will be omitted.

Next, operation | movement of the combined power source heat pump type air conditioning apparatus of this 3rd Embodiment is demonstrated concretely by FIG. The gas engine 19 is operated in the range of 1200 to 2400 r / min as in the first embodiment. The required load is the same as in the first embodiment.

In the range of 0 to 12.5% of the required load in a state where the demand load is in a low range and the demand load is in a low range, the control device 40 detaches both clutches 19a and 19b and at the same time the gas engine 19 The compressor 11B1 is driven by the inverter motor 13A. In this range, the pushing-down volume of the compressor 11B1 is fixed at the maximum value, and the rotational speed of the inverter motor 13A is controlled to increase gradually from zero with the increase of the required load, and the amount of refrigerant discharged from the compressor 11B1 is It increases linearly from 0 to 12.5% as the demand load increases.

Next, in the range of 12.5 to 25% of the required load in the state where the demand load is in the low range but the demand load is not lowered, the control device 40 stops the operation of the inverter motor 13A, and the gas The engine 19 is operated to engage only the clutch 19a to drive only the compressor 11B1 by the gas engine 19, and the throttle opening of the gas engine 19 is controlled so that the rotational speed thereof is low in energy efficiency. The rotation speed is controlled to be a constant value of 1200 r / min. In addition, by controlling the inclination angle of the inclined plate of the compressor 11B1, the control device 40 gradually increases the pushing down volume from 50% at the position where the demand load is 12.5% to 100% at the position where the demand load is 25%. Increase As a result, in this range, the amount of refrigerant discharged from the compressor 11B1 increases from 12.5% to 25% according to the increase in the required load.

Similarly, in the range of 25 to 50% of the required load in the state where the demand load is in the low range but the demand load is not lowered, the control device 40 engages the clutch 19a and the clutch 19b. The gas engine 19 drives both the compressor 11B1 and the compressor 12B2 to control the throttle opening of the gas engine 19 so that the rotational speed continues to be energy-efficient low rotational speed 1200 r / Control to be a constant value of minutes. In addition, by controlling the inclination angle of the inclined plate of the compressor 11B1, the control device 40 gradually increases the pushing volume from 0% at the position where the demand load is 25% to 100% at the position where the demand load is 50%. Increase As a result, in this range, the amount of refrigerant discharged from the compressors 11B1 and 12B2 increases from 25% to 50% in accordance with the increase in the required load.

In addition, in the range where the required circulation amount in the range where the required load is high is 50 to 100%, the control device 40 continuously drives both the compressor 11B1 and the compressor 12B2 by the gas engine 19, and the compressor ( By maintaining the pushing down volume of 11B1) at 100%, the throttle opening of the gas engine 19 is controlled so that the rotational speed increases from 1200 r / min to 2400 r / min. As a result, in this range, the amount of refrigerant discharged by the compressors 11B1 and 12B2 increases from 50% to 100% in accordance with the increase in the required load.

As described above, according to the combined power source heat pump type air conditioner of the third embodiment, the range in which the compressor 11B1 is driven by the inverter motor 13A can be reduced to the range of 0 to 12.5%. Since the inverter 13A can be made smaller than the above-described embodiments, the facility cost is further reduced, and the use range of the fuel gas for the internal combustion engine, which is lower in energy cost than the electric power, is further increased. The running cost of an air conditioning apparatus can be reduced.

In the above description, the drive by the inverter motor 13A to the compressor 11B1 and the drive by the gas engine 19 have been described as switching at a position where the required load is 12.5%, but the variable displacement compressor 11B1 is described. Since the minimum pushing down volume of is substantially zero, the drive of the compressor 11B1 by the gas engine 19 can be expanded below 12.5%, and the drive of the compressor 11b1 by the inverter motor 13A In the range where the capacity of the inverter motor 13A has a margin, it can be expanded upwards from 12.5%. Therefore, if the switching position of the inverter motor 13A and the gas engine 19 is selected suitably based on the fuel consumption of the gas engine 19, or the energy costs of fuel gas and electric power, running cost can be minimized. .

In the third embodiment, the constant speed motor 13B may be used instead of the inverter motor 13A, and the change of the required load when the compressor 11B1 is driven by the constant speed motor 13B is changed to the compressor 11B1. It is good to respond by changing the pushing volume of push.

10 to 12, a description will be given of a fourth embodiment of the combined power source heat pump type air conditioner according to the present invention. Although the fourth embodiment is similar to the third embodiment, as shown in Fig. 11, the compressor selectively driven by the gas engine 19 and the inverter motor 13A is referred to as a fixed displacement compressor 11B2. The compressor selectively driven by the gas engine 19 is a variable displacement compressor 12B1. The capacity of the fixed displacement compressor 11b2 and the maximum capacity of the variable displacement compressor 12B1 are half of the maximum capacity of the variable displacement compressor 11A1 of the first embodiment, and the minimum pushing-down volume of the compressor 12B1. Is 50%. The rest of the configuration is the same as in the second embodiment, and thus the detailed description thereof will be omitted.

Next, the operation of the combined power source heat pump type air conditioner of the fourth embodiment will be specifically described with reference to FIG. The gas engine 19 is operated in the range of 1200 to 2400 r / min as in the first embodiment. The required load is the same as in the case of the first embodiment.

In the range of 0 to 12.5% of the required load in a state where the demand load is in a low range and the demand load is in a low range, the control device 40 detaches both clutches 19a and 19b and at the same time the gas engine 19 The compressor 11B2 is driven by the inverter motor 13A. In this range, the rotational speed of the inverter motor 13A is controlled to increase gradually from zero as the demand load increases, and the amount of refrigerant discharged by the fixed capacity compressor 11B2 is from 0 to 12.5% according to the increase in the demand load. Increase linearly.

Similarly, in the range of 12.5 to 25% of the required load in a state in which the demand load is in a low range and the demand load is in a lower range, the control device 40 operates the gas engine 19 to engage only the clutch 19b. Only the compressor 12B1 is driven by the gas engine 19, and the throttle opening degree of the gas engine 19 is controlled so that the rotation speed becomes a constant value of the energy-efficient low rotation speed 1200 r / min. . In this range, the pushing-down volume of the compressor 12B1 is fixed at 50%, and the rotational speed of the inverter motor 13A is controlled to gradually increase from zero again as the demand load increases, thereby driving the compressor 11B2. As a result, the amount of refrigerant discharged from the compressors 11B2 and 12B1 increases linearly from 12.5% to 25% in accordance with the increase in the required load.

Similarly, in the range of 25 to 37.5% of the required load in a state in which the demand load is in a low range and the demand load is in a low state, which is the maximum value, the control device 40 continues by the gas engine 19 to the compressor 12B1. Only the drive is performed and the throttle opening of the gas engine 19 is controlled so that the rotational speed becomes a constant value of the energy-efficient low rotational speed 1200 r / min. In this range, the pushing-down volume of the compressor 12B1 is fixed at 100%, and the rotational speed of the inverter motor 13A is controlled to gradually increase from zero again as the demand load increases, thereby driving the compressor 11B2. As a result, in this range, the amount of refrigerant discharged from the compressors 11b2 and 12B1 increases linearly from 25% to 37.5% in accordance with the increase in the required load.

Next, in the range of 37.5 to 50% of the required load in the state where the demand load is in the low range but the demand load is not lowered, the control device 40 stops the operation of the inverter motor 13A, and then The gas engine 19 is operated to couple the clutch 19a to the clutch 19b to drive the compressor 12B1 and the compressor 11B2 by the gas engine 19, and to open the throttle opening of the gas engine 19. It controls so that the rotation speed may become a constant value of the energy-efficient low rotation speed 1200 r / min. In addition, the compressor 12B1 sequentially increases from 50% at the position where the demand load is 37.5% to 100% at the position where the demand load is 50%. As a result, in this range, the amount of refrigerant discharged from the compressors 11B2 and 12B1 increases linearly from 37.5% to 50% in accordance with the increase in the required load.

In addition, in the range where the required circulation amount is within a range of 50 to 100% in a high load range, the control device 40 continues to drive the compressor 11B2 and the compressor 12B1 by the gas engine 19 to control the compressor 12B1. By maintaining the pushing down volume at 100% and controlling the throttle opening of the gas engine 19, the rotational speed is controlled to increase from 1200 r / min to 2400 r / min. As a result, in this range, the amount of refrigerant discharged from the compressor 11B2 and the compressor 12B1 increases from 50% to 100% in accordance with the increase in the required load.

According to the combined power source heat pump type air conditioner of the fourth embodiment, the compressor 11B1 is driven by the inverter motor 13A in three ranges of 0 to 12.5%, 12.5 to 25%, and 25 to 37.5%. The range of discharge amount in each range is 0-12.5% in all. Therefore, since the inverter motor 13A only needs to drive the compressor 11B1 in the range of 0 to 12.5%, the inverter motor 13A is small as in the case of the third embodiment and can reduce the equipment cost and the running cost. have. In the fourth embodiment, in the range of 12.5 to 37.5% (indicated by L in FIG. 12), the gas engine 19 and the inverter motor 13A are used together to supply the refrigerant. Also in this fourth embodiment, when the minimum pushing down volume of the compressor 12B1 is 0, the constant speed motor 13B can be used instead of the inverter motor 13A. In that case, the compressor ( The change of the required load when driving 11B1 may be performed by changing the pushing down volume of the compressor 11B1.

In the second to fourth embodiments described above, the capacities of the two compressors (the maximum capacity in the case of the variable displacement compressor and the capacity of the fixed displacement compressor) are the same, but the present invention is not limited thereto. It is also applicable when the capacity of the two compressors is not the same. Moreover, this invention can also be implemented using three or more compressors.

15 to 18, a combined power source heat pump type air conditioner according to a fifth embodiment of the present invention will be described. As shown in Fig. 15, the combined power source heat pump type air conditioner according to the fifth embodiment includes a control unit 1124 for controlling the operation of the outdoor unit 110, the indoor unit 119, and the outdoor unit 110. It is a main configuration.

The outdoor unit 110 includes a compressor 112 capable of being pushed within a predetermined range to change the flip volume, and a water-cooled gas engine (internal combustion engine) that drives the compressor 112 via a clutch 112d with a rotational speed varying. 111, the refrigerant circulation path 115 connected to the discharge port 112a and the suction port 112b of the compressor 112, the four-way valve 16 and the outside air heat exchanger 17a). The coolant circulation path 115 is divided into two conduits 115a and 115b, which are provided on the compressor 112 side by the four-way valve 16, and three conduits 115c to 115e, and has a fan 17b. The exchanger 17a is provided between the conduit 115c and the conduit 115d. The indoor heat exchanger 119a of the indoor unit 119 having the sirocco fan 119c is installed between the conduit 15d and the conduit 115e, and an expansion valve is provided between the outdoor air exchanger 17a and the indoor heat exchanger 119a. 119b is provided, and a capillary tube and a check valve are provided in series with this expansion valve 119b in parallel. The four-way valve 16 switches the supply order of the refrigerant from the compressor 112 to the outdoor heat exchanger 17a and the indoor heat exchanger 119a, thereby switching heating and cooling. In the present embodiment, only one set of indoor units 119 is shown, but in general, a plurality of indoor units 119 which are provided in each chamber and which can be individually operated and stopped are connected to the pipe line 115c in parallel with each other. The outdoor unit 110 is normally one set.

The compressor 112 is a scroll compressor comprising a fixed scroll having an involute curve scroll wrap and a rotating scroll, and the fixed scroll is formed between the two scrolls, and is formed in a compression chamber in which the volume gradually decreases as the swing scroll rotates. The bypass port 112c which communicates is provided, and this bypass port 112c communicates with the suction port 112b via the reduce valve (electromagnetic expansion valve) 114. The reducer valve 114 is controlled in a number of stages by the control device 1124. By controlling the opening degree, the push-down volume of the compressor 112 is, for example, 50% from the maximum value. A change is made between% to correspond to a change in the required load on the compressor 112. The compressor 112 is provided with a power generation motor 113 having both functions of a generator and an electric motor. The power generation motor 113 of this embodiment is built in the compressor 112, and both the casing and the rotating shaft are integrally formed with each other. A clutch 112d is attached to one end of the rotary shaft of the compressor 112, and a power transmission belt 111b is provided on the outer periphery of the output pulley 11a and the clutch 112d attached to one end of the output shaft of the gas engine 111. Is wound and the clutch 112d is coupled, the compressor 112 and the power generating motor 113 are driven by the gas engine 111 via the output pulley 11a, the power transmission belt 111b and the clutch 112d. The compressor 112 is driven by the electric motor 113 in a state where it is driven and the clutch 112d is separated.

In the internal AC power line (internal power line) 123 of the combined power source heat pump type air conditioner, the system cooperation protection device 121 and the inverter 122 such as to prevent the generation load from affecting the power supply side. The electric power is supplied by the three-phase commercial power supply 120 via the via. A power generation motor 113 is connected to the internal AC power line 123 via a power conversion converter 125, and a fan 117b and an indoor unit 119 of the outdoor unit 110 via motor drivers 126 and 127. The sirocco fan 119c of () is connected, and the control apparatus (not shown) of the combined power source heat pump type air conditioner which contains the control apparatus 1124 is connected. Moreover, the stator 11c of the gas engine 111 is connected to the inverter 122 via the converter 128, and the direct current of DC 112V is supplied.

As shown in Figs. 15 and 16, the control device 124 operates the reducer valve 114 and the operation of the compressor 112 via the gas engine 111 based on the air conditioning load, the generation load, and the operating conditions. By controlling the operation of the power generation motor 113 through the power conversion converter 125, the flow rate of the refrigerant supplied from the compressor 112 to the refrigerant circulation path 115 and the amount of power generated by the power generation motor 113 In addition, the operation of the fan 117b and the sirocco fan 119c is controlled accordingly. The air conditioning load is a required circulation amount of the refrigerant calculated according to the set temperature of the indoor unit 119, the capacity and suction temperature of the indoor heat exchanger 119a, the heating and cooling temperatures, and the like. The cumulative value of the required circulation amount of the refrigerant at 119. The power generation load includes the fan 117b of the outdoor unit 110, the sirocco fan 119c of the indoor unit 119, the outdoor unit 110 and the indoor unit 119 including the control device 124, which are calculated according to the operating state at that time. ) Is the amount of power required by the control device. The operating conditions are conditions for protecting the apparatus such as the temperature, the pressure, the rotational speed, and the like of each part of the apparatus maintained within a predetermined limit.

The thermal efficiency of a gas engine has a high torque dependency, and the higher the torque, the higher the thermal efficiency. Therefore, in the gas engine driven heat pump type air conditioner, a control method of keeping the engine rotational speed low to maintain energy as high as possible and improve the energy efficiency is suitable. In the combined power source heat pump type air conditioner of the above-described embodiment, only the unit 112 is driven by the gas engine 111, and the unit energy cost per unit energy cost when the power generation by the power generation motor 113 is not performed. The characteristic of the running cost merit which is an air conditioning output becomes as shown by the characteristic a of FIG. 18 which becomes high in the range with high air conditioning load, and falls in the range with low air conditioning load.

However, when the generator motor 113 installed in the compressor 112 described above is also driven by the gas engine 111 and used as a power source for the heat pump type air conditioner, the gas engine is driven only by driving the generator motor 113. Since the driving torque of the 111 increases, the thermal efficiency is improved, the fuel economy is improved, and the power consumption of the external power is also reduced because the power generator motor 113 is used as a power source of the heat pump type air conditioner, thereby reducing the running cost. As shown in Fig. 18, the merit characteristic is a characteristic d which is generally improved by the value B corresponding to the torque rise required for driving the power generation motor 113.

As described above, the compressor 112 and the generator motor 113 are driven by the gas engine 111, the generator motor 113 is generated, and the power is supplied to the heat pump type air conditioner itself via the internal AC power line 123. And the power generation simultaneous operation, the control device 1124 first operates the stator 111c with the throttle opening degree of the gas engine 111 as a predetermined value to start the gas engine 111, and output pulley 111a. ), The compressor 112 and the power generating motor 113 are driven through the power transmission belt 111b and the clutch 112d. In addition, the control device 1124 controls the rotational speed of the compressor 112 by controlling the operation of the gas engine 111 based on the air conditioning load, and simultaneously pushes the compressor 112 by the reducer valve 114. The tilting volume is controlled to control the flow rate of the coolant supplied from the compressor 112 to the coolant circulation path 115 to be a value corresponding to the air conditioning load. In addition, the control device 124 controls the power conversion converter 25 on the basis of the generation load, so that the AC power output from the generation motor 113 is supplied to the fan 17b of the outdoor unit 110 and the indoor unit 119. The amount of power to be converted into the type of power required by the control device of the combined power source heat pump type air conditioner including the sirocco fan 119c and the control unit 1124 and supplied to the internal AC power line 23 is combined power source heat pump. The air conditioner controls the value according to the amount of power required. Thus, the unit energy cost in the case of using the gas engine 111 as a drive source is the cost of fuel gas per unit energy. Therefore, the characteristic a and the characteristic d change with the charge of the fuel gas at that time.

On the other hand, in the combined power source heat pump type air conditioner of the above-described embodiment, in the case of the electric drive that feeds the power generator motor 113 from the internal AC power line 123 and drives the compressor 112, the running cost merit The characteristic becomes as shown by the characteristic b of FIG. 18 which becomes high in the range with low air conditioning load, and falls in the range with high air conditioning load. In this case, the control device 1124 operates the power conversion converter 25 as an inverter, controls the rotational speed of the compressor 112 by the power generation motor 113 based on the air conditioning load, and at the same time reduces the valve. By 114, the pushing down volume of the compressor 112 is controlled, and the flow rate of the refrigerant supplied from the compressor 112 to the refrigerant circulation path 115 is controlled to be a value corresponding to the air conditioning load. Thus, the unit energy cost at the time of using the power generation motor 113 as a drive source is the power cost of the commercial power supply 20 per unit energy. Therefore, the characteristic b changes with the electric power charge at that time.

In this embodiment, the control apparatus 124 is the characteristic d of FIG. 18 which is a running cost merit which is the air-conditioning output per unit energy cost in the case of compression and power generation simultaneous operation, and the characteristic of FIG. 18 which is a running cost merit in the case of electric drive. By comparing b, in the range where the former characteristic d is larger than the latter characteristic b (the load range in which the air-conditioning load becomes more than the predetermined load A in FIG. 18), the gas engine 111 is operated to engage the clutch 112d. The compressor 112 and the generator motor 113 are driven, and the generator motor 113 is used as a power source for the heat pump type air conditioner, and the latter characteristic b is larger than the former characteristic d (air-conditioning in Fig. 18). In the load range in which the load is less than the predetermined load A), the gas engine 111 and the compressor (to drive the compressor 112 by the electric motor 113 while leaving the clutch 112d and stopping the gas engine 111). 112), clutter Teeth 112d and the operation of the electric motor 113 are controlled.

As described above, since the characteristic d and the characteristic b respectively change according to the fuel gas and the electric power charge at that time, the predetermined load A changes the fuel gas and electric power charge whenever the combined power source heat pump type air conditioner is installed. Each time, the calculation is made in advance so that the total amount of the gas fee due to the use of the gas engine 111 and the electric fee due to the use of the power generating motor 113 is minimized. Let's switch. This switching means is a switching switch installed in the control base or remote control of the combined power source heat pump type air conditioning apparatus, and the control device 1124 uses the predetermined load A and the air conditioning load at this time as the control base or remote control. Displayed on the display unit, the user may operate the changeover switch on the basis of the displayed predetermined load A and the air conditioning load at that time to switch compression and power generation simultaneous operation and electric operation. Alternatively, the switching means may compare the predetermined load A with the air conditioning load at that time, and automatically switch between the compression and power generation simultaneous operation and the electric operation.

According to the combined power source heat pump type air conditioning apparatus of this embodiment, as shown by characteristic e of FIG. 4, in the load range where the air conditioning load becomes a predetermined load A or more, high running equal to the characteristic d in the case of simultaneous compression and power generation operation A cost merit can be obtained and a high running cost merit similar to the characteristic b in the case of electric drive can be obtained in the load range which becomes less than predetermined load A. FIG. Thereby, in the combined power source heat pump type air conditioning apparatus of this embodiment, compared with the conventional technique which drives the compressor 112 by the gas engine 111, the running cost merit in the load range below the predetermined load A which is partial load is attained. In addition, since the running cost merit in the load range more than the predetermined load A which is the high load range including the rated load time is also improved, the running cost merit in the long term can be improved.

Even when the compressor 112 is driven by either the gas engine 111 or the power generating motor 113, in the case of the cooling operation, the four-way valve 116 is in a state shown by the solid line in FIG. 15, and the compressor ( The high temperature and high pressure gaseous refrigerant compressed by 112 enters the outside heat exchanger 117a from the pipe line 115c through the four-way valve 116 from the pipe line 115a and is cooled by the outside air fed from the fan 117b. And liquefy. The liquefied high-pressure refrigerant passes through the expansion valve 119b from the conduit 115d, is decompressed, enters the indoor heat exchanger 119a, and is vaporized. The vaporized heat is taken out of the indoor heat exchanger 119a. Cool. The air fed into the room from the sirocco fan 119c is cooled when passing through the room heat exchanger 119a, whereby the room is cooled. The vaporized refrigerant is sucked into the compressor 112 through the four-way valve 116 and the conduit 115b from the conduit 115e, and is again compressed to cool the room by repeating the above-described cooling cycle.

In the case of heating operation, the four-way valve 116 is in a state shown by a dotted line in FIG. 15, and the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 112 is indoors from the four-way valve 116 via the conduit 115e. Enter heat exchanger 119a. The air fed into the room from the sirocco fan 119c is heated by the high temperature and high pressure gaseous refrigerant when passing through the indoor heat exchanger 119a, whereby the room is heated while the gaseous refrigerant is cooled and liquefied. The liquefied high pressure refrigerant passes through the expansion valve 119b, is decompressed, enters the outside air heat exchanger 117a from the conduit 115d, and vaporizes the heat of vaporization from the outside air supplied from the fan 117b. The vaporized refrigerant is sucked into the compressor 112 through the four-way valve 116 and the conduit 115b from the conduit 115c, and is again compressed to heat the room by repeating the above-described heating cycle.

The compressor 112 and the power generator motor 113 are driven by the internal combustion engine 111, and the air conditioner load is supplied by supplying the refrigerant from the compressor 112 to the refrigerant circulation path 115, but the electric power is supplied from the power generator motor 113. When the power generation load is not added without taking out, the engine load increases proportionally with respect to the air conditioning load as shown by the characteristic g of FIG. In the present embodiment, the engine load limit is 130%, which is the rated value of the air conditioning load. Therefore, the combined power source heat pump type air conditioner can withstand overload in the short term to 130%. Moreover, as mentioned above, in the range which becomes less than predetermined load A among these air conditioning loads, the combined power source heat pump type air conditioning apparatus is driven by the generator electric motor 113. As shown in FIG.

Therefore, in the present embodiment, in the above-described case, it is possible to generate power by the power generating motor 113 and take out electric power. In that case, as shown in Fig. 17, the engine load is the maximum power generation described below. In the case of the load C, it is possible to increase the characteristic h1 which is higher than the characteristic g by the value D of the engine load and the characteristic h2 which is 130% higher than the rated load, and the power generation motor 113 has the characteristic load and the characteristic g. As long as it is within the range surrounded by h1 and the characteristic h2, it is possible to generate electricity as indicated by the characteristic i. In the present embodiment, the maximum power generation capacity of the power generation motor 113 is larger than the power generation load required by the combined power source heat pump type air conditioner. As described above, the control device 1124 uses the internal AC power line 123. The amount of power supplied to the combined power source heat pump type air conditioner is controlled so as to be a value corresponding to the amount of power required at that time. However, the control device 1124 operates the electric motor 113 at the maximum power generation at all times, and power exceeding the electric power required by the combined power source heat pump type air conditioner is transferred from the internal AC power line 123 to the inverter 122. And the commercial power supply 120 side via the system cooperative protection device 121. In this way, since the torque of the gas engine 111 always increases and fuel economy improves, the running cost merit of the combined power source heat pump type air conditioner can be further improved. In any case, the electric power required by the heat pump type air conditioner is supplied by the power generation motor 113 and does not require electric power from the outside. Therefore, even when a sudden power failure occurs during operation of the air conditioner, air conditioning is performed without any problem. You can continue driving.

The combined power source heat pump type air conditioner of the present embodiment can also be used as a power supply device at the time of power failure, and the maximum power generation load at that time is a value C determined by the maximum power generation capacity of the power generation motor 113. The characteristic f shown in FIG. 17 is a characteristic of the engine load with respect to the power generation load in the case where the discharge port 112a and the suction port 112b of the compressor 112 are shorted and the air conditioning load is zero. The power generation load is the value C, and the engine load at that time is the value D. In this case, the control device 1124 first starts the gas engine 111 to drive the power generation motor 113, and then controls the power conversion converter 25 to control the AC power output from the power generation motor 113. And converts the same number of cycles and voltage as the commercial power supply 120 into the internal AC power supply line 123, and supplies the same to the commercial power supply 20 through the inverter 22 and the grid cooperation protection device 121. Supply. In this way, when a sudden power failure occurs during operation of the air conditioner, the power generating motor 113 can be generated and used as a power supply device during power failure, thereby increasing the usefulness of the combined power source heat pump type air conditioner.

In the above-described embodiment, the running cost merit in the case of compression and power generation simultaneous operation is compared with the running cost merit in the case of electric driving, and the gas engine 111 is in a range where the former running cost merit is larger than the latter running cost merit. To drive the compressor 112 by engaging the clutch 112d, and to drive the generator motor 113 and to generate power by the generator motor 113 to be used as a power source for a heat pump type air conditioner. When the latter running cost merit is larger than the former running cost merit, the gas engine 111 is released from the clutch 112d and the gas engine 111 is stopped to drive the compressor 112 by the electric motor 113. , The operation of the compressor 112, the clutch 112d and the power generator motor 113 are controlled. Since the compression and power generation simultaneous operation and the electric drive are switched at the predetermined load A in which the merit of the running cost merit of the drive and the driving cost in the case of the electric drive is replaced, the range excellent in the running cost merit is selected, and the maximum of the running cost merit is selected. The effect can be obtained.

In addition, in the above-described embodiment, the predetermined load A, which is a switching point for switching between simultaneous compression and power generation operation and electric operation, is calculated in advance every time the fuel gas and electric power charge is changed, and based on this, compression and power generation simultaneous operation and electric operation are Since the range is always excellent in the running cost merit, the maximum effect on the running cost merit can be reliably obtained.

In addition, the predetermined load may be carried out at a fixed value determined for each model based on the average value of the fluctuations in the fuel gas and the electricity charges that are normally expected, and in doing so, the long-term running cost merit of the combined power source heat pump type air conditioning system is achieved. In addition, it is possible to simplify the control of switching between compression and power generation simultaneous operation and electric operation.

In the above-described embodiment, the compressor 112 is a scroll compressor, and the bypass port 112c communicates with the suction port 112b via the reducer valve 114, and is controlled by the control device 124. The deuce valve 114 is controlled to change the pushing down volume of the compressor 112. Since the simple scroll compressor is used as the compressor 112, the manufacturing cost of the combined power source heat pump type air conditioner can be reduced. . However, the present invention is not limited to this, and a vane pump having a variable pushing amount by changing the eccentricity of the cam ring for the rotor or a reciprocating piston compressor having a variable pushing amount by changing the piston stroke can be used. have. In addition, in the above-described embodiment, the scroll compressor 112 used has been described with respect to an example in which the change range of the push-down volume is 50 to 100%. However, the present invention is not limited thereto, and the push-up volume may vary depending on the specification. You may use a thing with a change range of push-down volume, such as 30 to 100% of a change range.

In addition, in the above-described embodiment, the power generator motor 113 is incorporated in the compressor 112. In this case, the structure of the combined power source heat pump type air conditioner is simplified, so that the manufacturing cost can be reduced.

According to the combined power source heat pump type air conditioner according to the invention of claim 1, at least a part of a compressor used in a high demand load range is pushed into a variable displacement compressor capable of changing the volume of displacement. In the high range, the push-down volume of the variable displacement compressor is set at or near the maximum value to change the rotational speed of the internal combustion engine to cope with the change in the demand load, and when the demand load shifts from the high range to the low range, the compressor is first driven. The internal combustion engine is operated at an energy efficient low rotational speed and high torque state, while changing the pushing volume of the compressor driven by the internal combustion engine to cope with the change in the demand load, and the demand load within a low load range. Is lowered, the power source of the compressor is transferred to the internal combustion engine. And the compressor is driven by an internal combustion engine operating at an energy efficient low rotational speed and high torque until the required load is lowered even within the required load range. In this case, the motor is driven by the electric motor after the required load falls within the range. As a result, the electric motor for driving the compressor only needs to cover the range in which the demand load is lowered even in the range where the demand load is low, so that the motor is small. Therefore, it is possible to reduce the equipment cost and increase the use range of the fuel for the internal combustion engine, which is lower in energy cost than the electric power, and thus reduce the running cost of the combined power source heat pump type air conditioner.

According to the combined power source heat pump type air conditioner of claim 2, the most simplified one of the combined power source heat pump type air conditioner according to the present invention can be obtained.

The combined power source heat pump type air conditioner of claim 3 is the combined power source heat pump type air conditioner according to claim 1, wherein the compressor comprises a first variable displacement compressor selectively driven by an internal combustion engine and an electric motor, and an internal combustion engine. And a second variable displacement compressor, which is selectively driven, wherein the control device connects and drives the second variable displacement compressor to the internal combustion engine when the demand load is high, and shifts from a high demand load to a low range. Firstly, the internal combustion engine driving the second variable displacement compressor is operated at low rotational speed and high torque with high energy efficiency and at the same time changing the push-down volume of the second variable displacement compressor to cope with the required load fluctuation. If the demand load is lowered within a range where the demand load is low, According to the combined power source heat pump type air conditioner of claim 3, wherein the variable displacement compressor is removed from the internal combustion engine to stop the drive, and the first variable displacement compressor is controlled to be connected to the internal combustion engine or the motor to drive the compressor. Is a first variable displacement compressor selectively driven by an internal combustion engine and an electric motor when the required load falls within that range even in a low range, and a second variable displacement compressor driven by an internal combustion engine in other cases. Since the range of the required load driven by the internal combustion engine and the range of the required load driven by the electric motor can be arbitrarily selected according to the energy cost of the electric power and the fuel for the internal combustion engine, the running cost can be reduced. . In addition, by selecting the capacity of the first and second variable displacement compressors, the range of the required load driven by the internal combustion engine and the range of the required load driven by the electric motor can be changed to expand the range of the above-described selection.

The combined power source heat pump type air conditioner of claim 4 is the combined power source heat pump type air conditioner according to claim 1, wherein the compressor is selectively provided by an internal combustion engine and a variable displacement compressor selectively driven by an internal combustion engine and an electric motor. It is composed of a fixed displacement compressor that is driven, and the control device drives both a variable displacement compressor and a fixed displacement compressor by connecting to an internal combustion engine in a range where the demand load is high. First of all, the internal combustion engine driving the variable displacement compressor and the fixed displacement compressor is operated at low torque and high torque with high energy efficiency, and at the same time, the change in the push-down volume of the variable displacement compressor is used to cope with the required load fluctuation. When the demand load falls within the range where the demand load is low Since the fixed displacement compressor was removed from the internal combustion engine to stop the drive, and the variable displacement compressor was controlled to be connected to the internal combustion engine or an electric motor to drive the variable displacement compressor. Is driven by the internal combustion engine, so the maximum of the air-conditioning capacity can be obtained when the sum of the pushing-down volumes of both compressors is the maximum and the rotational speed of the internal-combustion engine is the maximum, and each compressor contributes to the maximum of this air-conditioning capacity.

In the combined power source heat pump type air conditioner of claim 5, in the combined power source heat pump type air conditioner of claim 2 to 4, since the electric motor is a variable speed electric motor, the push-down volume of the variable displacement compressor driven by the variable speed electric motor is Regardless of the minimum value, the minimum discharge amount of the variable displacement compressor can be zero. As a result, the selection range of the required load of the compressor driven by the internal combustion engine and the required load of the compressor driven by the electric motor is expanded, so that an optimum operating state can be easily obtained.

The combined power source heat pump type air conditioner of claim 6 is the combined power source heat pump type air conditioner of claims 2 to 4, wherein the variable displacement compressor is assumed to have a minimum push-down volume of substantially zero, and the electric motor is a constant speed motor. Therefore, in the combined power source heat pump type air conditioner, as in the invention of claim 5, the minimum discharge amount of the compressor can be zero, thereby expanding the selection range of the required load of each compressor driven by the internal combustion engine and the electric motor. This makes it easier to obtain an optimal operating state.

The combined power source heat pump type air conditioner of claim 7 is the combined power source heat pump type air conditioner according to claim 1, wherein the electric motor is a variable speed electric motor, and the compressor is a fixed displacement compressor selectively driven by an internal combustion engine and a variable speed electric motor. And a variable displacement compressor selectively driven by the internal combustion engine, and the control device drives both the fixed displacement compressor and the variable displacement compressor by connecting to the internal combustion engine and drives the required load in a high load range. The transition from the high range to the low range involves first operating the internal combustion engines driving the fixed capacity compressors and the variable capacity compressors at low torque and high torque, which are energy efficient and at the same time varying the push-down volume of the variable capacity compressors. Corresponds to fluctuations in the demand load, and the demand load is in a low range In the case where the demand load is lowered, the fixed displacement compressor is driven away from the internal combustion engine and driven by a variable speed motor, and the variable displacement compressor is driven by the internal combustion engine and controlled to change the pushing volume. As in the case of the present invention, since both the fixed displacement compressor and the variable displacement compressor are driven by the internal combustion engine in the range where the demand load is high, the maximum air-conditioning capacity is the maximum sum of the pushed-down volumes of both compressors and the internal combustion engine. It can be obtained when the rotational speed of the engine is maximum, and each compressor contributes to the maximum of this air conditioning capacity.

The combined power source heat pump type air conditioning apparatus of claim 8, in the combined power source heat pump type air conditioning apparatus according to claim 7, uses a variable displacement compressor having a minimum push-down volume of substantially zero in place of the fixed displacement compressor. Since the constant speed electric motor was used instead of the electric motor, the minimum discharge amount of the compressor can be set to 0 as in the invention of claim 6, thereby expanding the selection range of the required load of each compressor driven by the internal combustion engine and the electric motor and It becomes easy to get the operating state.

The combined power source heat pump type air conditioner of claim 9 is provided with an internal power supply line fed by a commercial power source and fed to a heat pump type air conditioner, and a power generation motor installed in a compressor having both functions of a generator and an electric motor. In the load range where the load is greater than or equal to the predetermined load, the internal combustion engine is operated to couple the clutch to drive the compressor and the generator motor, and the compressor and the generator are driven at the same time to perform compression and power generation at the same time. As a result, the drive torque of the internal combustion engine increases only by driving the power generation motor, so that the fuel economy of the internal combustion engine is improved by the increase, and the amount of the external power source used is also reduced, thereby increasing the running cost merit. In addition, in the load range where the air conditioning load is less than the predetermined load, the running cost merit is increased by disengaging the clutch and stopping the internal combustion engine to feed electric power from the internal power supply line to the electric motor to drive the compressor. As described above, according to the present invention, in the load range in which the air conditioning load for which the running cost merit is lowered is lower than the predetermined load, the electric operation for driving the compressor by the electric motor instead of the internal combustion engine is performed. By increasing the running cost merit by performing, while the load range in which the air conditioning load in which the running cost merit increases becomes more than a predetermined load, the running cost merit is further increased by performing compression and power generation simultaneous operation by the internal combustion engine to drive the electric power generator. In addition, the running cost merit of the combined power source heat pump type air conditioner in the long term can be improved.

The combined power source heat pump type air conditioner of claim 10 is the combined power source heat pump type air conditioner of claim 9, wherein the control device is an air conditioning output per unit energy cost when driving the compressor and the power generating motor by an internal combustion engine. In the air-conditioning load range where the cost merit becomes larger than the running cost merit when the compressor is driven by the generator motor, the air-conditioning load range becomes larger than the running cost merit when the latter is the compression cost and power generation simultaneous operation, and the running cost merit in the latter case is the former. Since the operation of the internal combustion engine, the compressor, the clutch, and the power generating motor are controlled to perform the electric drive, the position at which the superiority of the running cost merit of the compression and power generation operation and the running cost merit of the electric drive is replaced. In the compression and generation simultaneous operation and ex Since the driving is switched and the range which always has the superior running cost merit can be selected, the maximum effect on the running cost merit can be reliably obtained.

The combined power source heat pump type air conditioner of claim 11 is the combined power source heat pump type air conditioner of claim 9 to 10, wherein the power generator motor has a power generation capacity that is greater than the maximum power supply capacity required by the heat pump type air conditioner. In the state where the control device is driven by the internal combustion engine to generate power, the internal combustion engine, the compressor, the clutch and the power generation are configured to supply at least a part of the electric power supplied from the power generator motor to the internal power line to the commercial power supply via the internal power line. Since the operation of the electric motor is controlled, the combined power source heat pump type air conditioner can be used as a power supply device in case of power failure, and the usefulness of the combined power source heat pump type air conditioner can be improved. In addition, even when the heat pump type air conditioner is driven by a gas engine, by supplying a part of electric power generated by the power generating motor to the commercial power supply side, the running cost merit of the combined power source heat pump type air conditioner can be further increased.

In the combined power source heat pump type air conditioner of claim 12, in the combined power source heat pump type air conditioner of claims 9 to 11, since the push-down volume of the compressor is variable, adjustment of the rotational speed of the compressor and adjustment of the push-down volume are made. Since the discharge amount of the refrigerant from the compressor can be adjusted by both of them, the adjustment range of the output range of the combined power source heat pump type air conditioner can be expanded.

The combined power source heat pump type air conditioner of claim 13 is the combined power source heat pump type air conditioner of claim 9 to 12, in which the power generator motor is built into the compressor, the structure of the combined power source heat pump type air conditioner is simplified, The manufacturing cost can be reduced.

The combined power source heat pump type air conditioner of claim 14, in the combined power source heat pump type air conditioner of claims 9 to 13, is provided with switching means for switching compression and power generation simultaneous operation and electric drive. Therefore, it becomes possible to switch the operation, and it is possible to realize the operation that brings the maximum cost merit to the individual user. The present invention is particularly effective when gas rates or electricity rates differ depending on the region.

The combined power source heat pump type air conditioner of claim 15 is the combined power source heat pump type air conditioner of claims 9 to 14, wherein power generation by a power generating motor is supplied to a heat pump type air conditioner as an uninterruptible power source at the time of power failure. Therefore, when a sudden power failure occurs during the operation of the air conditioner, the power generation motor can be generated and the combined power source heat pump type air conditioner can be continuously operated, thereby increasing the usability.

Claims (15)

A compressor for supplying the compressed refrigerant to a refrigerant circulation path provided with an indoor heat exchanger and an outdoor heat exchanger, an internal combustion engine that selectively drives the compressor by operating within a predetermined rotation speed range, and an electric motor that selectively drives the compressor. And a control device for controlling the internal combustion engine and the electric motor to drive the compressor by the internal combustion engine in a range where the demand load for the compressor is high, and to drive the compressor by the electric motor in a range where the demand load is low. A combined power source heat pump type air conditioner, comprising: a variable displacement compressor capable of pushing down at least a portion of the compressor used in a high range of the demanded load so as to change a wetting volume, and the control device is the required load. In the high range, the variable capacitance pressure By changing the rotational speed of the internal combustion engine with the push-up volume of the machine at or near the maximum value, it responds to the change in the demand load, and when the demand load shifts from a high range to a low range, first, the internal combustion driving the compressor is performed. The engine is operated at an energy-efficient low rotational speed and high torque while simultaneously changing the pushing-down volume of the compressor driven by the internal combustion engine to cope with a change in the demand load, and the demand load within a range where the demand load is low. And the power source of the compressor is controlled to switch from the internal combustion engine to the electric motor when the temperature is lowered. 2. The combined power source heat pump type air conditioning apparatus according to claim 1, wherein the compressor comprises one variable displacement compressor selectively driven by the internal combustion engine and an electric motor. The control apparatus of claim 1, wherein the compressor comprises a first variable displacement compressor selectively driven by the internal combustion engine and an electric motor, and a second variable displacement compressor selectively driven by the internal combustion engine. The second variable displacement compressor is driven by connecting the second variable displacement compressor to the internal combustion engine in a range where the demand load is high, and first driving the second variable displacement compressor when the demand load is shifted from a high range to a low range. The internal combustion engine is operated at an energy efficient low rotational speed high torque state and at the same time changing the push-down volume of the second variable displacement compressor to cope with a change in the demand load, and the demand load within a range where the demand load is low. Lowers the second variable displacement compressor from the internal combustion engine. Stopping the same at the same time the composite power source heat pump type air conditioner, characterized in that for controlling to drive to connect the said first variable displacement compressor to the internal combustion engine or electric motor. The compressor of claim 1, wherein the compressor comprises a variable displacement compressor selectively driven by the internal combustion engine and an electric motor, and a fixed displacement compressor selectively driven by the internal combustion engine, and the control device includes the required load. In the high range, both the variable displacement compressor and the fixed displacement compressor are connected to the internal combustion engine and driven, and when the required load is shifted from the high range to the low range, the variable displacement compressor and the fixed displacement compressor are first operated. The internal combustion engine being operated is operated at a low torque high torque state with high energy efficiency and at the same time changing the pushing-down volume of the variable displacement compressor to cope with a change in demand load, and the demand load is within a low range. When the demand load is lowered, the fixed displacement compressor A drive system for a combined power source heat pump type air conditioning apparatus, characterized in that the drive of the variable displacement compressor is connected to the internal combustion engine or the electric motor and driven to be stopped by driving away from the internal combustion engine. The combined power source heat pump type air conditioner according to any one of claims 2 to 4, wherein the electric motor is a variable speed electric motor. The combined power source heat pump type air conditioner according to any one of claims 2 to 4, wherein the variable displacement compressor has a minimum pushing down volume of substantially zero, and the electric motor is a constant speed electric motor. . The compressor of claim 1, wherein the electric motor is a variable speed electric motor, and the compressor comprises a fixed displacement compressor selectively driven by the internal combustion engine and the variable speed electric motor, and a variable displacement compressor selectively driven by the internal combustion engine. The control device connects both the fixed displacement compressor and the variable displacement compressor to the internal combustion engine in a range where the demand load is high, and when the transition from the high load to a low range occurs, the fixed device is first fixed. The internal combustion engine driving the capacitive compressor and the variable capacitive compressor is operated at an energy efficient low rotational speed high torque state and at the same time changing the push-down volume of the variable capacitive compressor to cope with fluctuation of the required load, The demand load is low within the range where the demand load is low. And the fixed displacement compressor is driven away from the internal combustion engine and driven by the variable speed motor, and the variable displacement compressor is driven by the internal combustion engine and controlled to change the pushing down volume. Power source heat pump type air conditioning unit. 8. The combined power source heat pump type air conditioning apparatus according to claim 7, wherein a variable displacement compressor having a minimum push-down volume of substantially zero is used instead of the fixed displacement compressor, and a constant speed motor is used instead of the variable speed motor. . A compressor for supplying the compressed refrigerant to a refrigerant circulation path provided with an indoor heat exchanger and an outdoor heat exchanger, an internal combustion engine that selectively drives the compressor by operating within a predetermined rotation speed range, and an electric motor that selectively drives the compressor. And a control device for controlling the internal combustion engine and the electric motor to drive the compressor by the internal combustion engine when the demand load for the compressor is high and to drive the compressor by the electric motor when the demand load is low. A combined power source heat pump type air conditioner, comprising: an internal power supply line fed by a commercial power source and supplied to a heat pump type air conditioner, wherein the electric motor is a power generating motor having a function of a generator, and an air conditioning load In the load range of more than a predetermined load The compressor and the clutch are coupled to drive the compressor and the generator motor, and the compressor and the generator motor are driven to perform compression and power generation at the same time by powering the heat pump type air conditioner itself. A control device for controlling the operation of the internal combustion engine, the compressor, the clutch, and the power generator motor to disengage the clutch and to stop the internal combustion engine to feed the power generator motor from the internal power line to perform the electric drive to drive the compressor; Combined power source heat pump type air conditioning apparatus comprising a. 10. The running cost according to claim 9, wherein the control device is a running cost merit that is an air conditioning output per unit energy cost when the compressor and the power generator motor are driven by the internal combustion engine. The internal combustion engine, the compressor, and the clutch are configured to perform the compression and power generation simultaneous operation in the air conditioning load range larger than the merit, and to perform the electric drive in the air conditioning load range larger than the running cost merit in the latter case. And a combined power source heat pump type air conditioner for controlling the operation of the electric motor. 11. The power generator of claim 9 or 10, wherein the power generator motor has a power generation capacity that is larger than a maximum value of the power supply capacity required by the heat pump type air conditioner, and the control device drives the power generator motor by the internal combustion engine. Operating the internal combustion engine, the compressor, the clutch and the power generator motor to supply at least a portion of the electric power supplied from the power generator motor to the internal power supply line to the commercial power supply side via the internal power supply line. Combined power source heat pump type air conditioner. The combined power source heat pump type air conditioning apparatus according to claim 9 or 10, wherein the compressor has a variable pushing volume. The combined power source heat pump type air conditioner according to claim 9 or 10, wherein the power generator motor is built in the compressor. The combined power source heat pump type air conditioner according to claim 9 or 10, further comprising switching means for switching the compression and power generation simultaneous operation and the electric operation. The combined power source heat pump type air conditioner according to claim 9 or 10, wherein power generation by the power generating motor is supplied to the heat pump type air conditioner as an uninterruptible power supply at the time of power failure.

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