JP2009127902A - Refrigeration equipment and compressor - Google Patents

Abstract

Even when an R32 refrigerant is used, the discharge gas temperature of the compressor can be lowered, and the heat resistance and wear resistance of the compressor can be ensured to improve the reliability and operating capacity. A refrigeration apparatus is provided.
An airtight container includes a compressor 1 having a discharge pressure atmosphere, an outdoor heat exchanger 3, a gas-liquid separator 5, a first expansion valve 7, and an indoor heat exchanger 9. A refrigeration system using R32 or a mixed refrigerant containing at least 60% by mass of R32 refrigerant, and a part of the refrigerant is injected into the compressor 1 from the gas-liquid separator outlet as flash gas, which is a gas-liquid two-phase saturated refrigerant. The injection circuit 40 is provided.
[Selection] Figure 1

Description

  The present invention relates to a refrigeration apparatus using R32 refrigerant and a compressor used in the refrigeration apparatus.

  Conventionally, there is a refrigeration apparatus having a refrigeration cycle in which a compressor, a condenser, an expansion valve, and an evaporator are sequentially connected by a refrigerant pipe. In this type of refrigeration apparatus, when R32 refrigerant is used as the refrigerant, the discharge gas temperature at the time of compression is higher by 10 to 20 ° C. due to its thermal properties than R22 refrigerant and R410A refrigerant. When the discharge gas temperature becomes high in this way, there is a problem that the temperature of the compressor rises during an overload operation such as during low outside air heating, and the heat resistance temperature of the motor insulating material is exceeded, leading to a decrease in reliability.

  Further, as a compressor for a refrigeration system, a hermetic compressor in which lubricating oil is sealed in a hermetic container is used. In this type of compressor, lubricating oil is applied to a sliding portion of a compression element inside the compressor. Driving while supplying. That is, the compression operation is performed while preventing wear by supplying lubricating oil to the sliding portion. However, as the discharge gas temperature increases, the internal temperature of the entire compressor also increases, so the temperature of the lubricating oil also increases. As a result, the viscosity of the lubricating oil decreases, resulting in poor lubrication and wear. There was a sexual problem. In addition, there is a problem that the driving ability is reduced.

  Therefore, in recent years, a refrigerant circuit including a compressor, a condenser, an expansion valve, and an evaporator, a supercooling heat exchanger disposed between the condenser and the expansion valve, and the refrigerant via the supercooling heat exchanger In a refrigeration system using R32 refrigerant, comprising: a bypass pipe that bypasses the gas side and the liquid side of the circuit; and a subcooling decompression means that is disposed upstream of the supercooling heat exchanger of the bypass pipe. When the discharge temperature of the compressor reaches a certain temperature or higher, the refrigerant at the outlet of the condenser is caused to flow to the evaporator outlet side through the bypass pipe by controlling the pressure reducing means for supercooling. There has been a method of reducing the discharge temperature of the compressor (see, for example, Patent Document 1).

JP 2001-227823 A

  However, in the technique of Patent Document 1, the liquid refrigerant that has been reduced in pressure after passing through the supercooling heat exchanger may be injected into the gas refrigerant on the evaporator outlet side as the liquid refrigerant. In this case, the liquid refrigerant is compressed as it is in the compressor, and there is a problem that an excessive load is applied to the compression element portion and reliability is lowered.

  The present invention has been made to solve the above-described problems. Even when an R32 refrigerant is used, the discharge gas temperature of the compressor can be lowered, and the heat resistance and wear resistance of the compressor can be reduced. It is an object of the present invention to provide a refrigeration apparatus that can be secured to improve reliability and operating capacity, and a compressor used in the refrigeration apparatus.

  The refrigeration apparatus according to the present invention includes a compressor having a discharge container with a discharge pressure atmosphere, a condenser, a gas-liquid separator, an expansion valve, and an evaporator, and at least 60 R32 or R32 refrigerant is used as a refrigerant. A refrigeration apparatus using a mixed refrigerant containing at least% mass, comprising an injection circuit for injecting a part of the refrigerant from the gas-liquid separator outlet into the compressor as flash gas that is a gas-liquid two-phase saturated refrigerant It is.

  According to the present invention, since the flash gas, which is a gas-liquid two-phase saturated refrigerant, is injected into the compressor, the internal temperature of the compressor can be reduced and the discharge temperature can be lowered. As a result, it is possible to improve the reliability of the compressor and the operating capacity as compared with the case where the injection injection is not performed.

  Hereinafter, the refrigeration apparatus of the present invention will be described with reference to the drawings.

Embodiment 1 FIG.
FIG. 1 is a diagram showing a schematic configuration of an air conditioner as a refrigeration apparatus according to Embodiment 1 of the present invention.
The air conditioner shown in FIG. 1 uses an R32 refrigerant (including a mixed refrigerant containing at least 60% by mass of R32 refrigerant) as a working refrigerant, and includes a hermetic rotary refrigerant compressor 1, a four-way valve 2, outdoor heat. The exchanger 3, the bridge circuit 4, the gas-liquid separator 5, the internal heat exchanger 6, the first expansion valve 7, the indoor heat exchanger 9, and the accumulator 10 are sequentially connected by a refrigerant pipe to constitute a refrigeration cycle. The hermetic rotary refrigerant compressor 1 is configured so that the inside of the hermetic container has a discharge pressure atmosphere, and has a high pressure. Further, a part of the refrigerant from the gas-liquid separator 5 to the internal heat exchanger 6 is bypassed to the hermetic rotary refrigerant compressor 1 via the second expansion valve 8 and the internal heat exchanger 6 as a throttle portion. An injection circuit 40 is provided. The bridge circuit 4 has four check valves 4a, 4b, 4c, and 4d, and has two input / output ports, one input port, and one output port.

  Further, inside the air conditioner, a discharge temperature sensor 11 for detecting the temperature on the discharge side of the hermetic rotary refrigerant compressor 1, a temperature sensor 12 for detecting the refrigerant temperature of the outdoor heat exchanger, and an indoor heat exchanger And a temperature sensor 13 for detecting the refrigerant temperature.

FIG. 2 is a block diagram showing an electrical configuration of the air conditioner of FIG. In FIG. 2, parts necessary for explaining the characteristic part of the present invention are shown, and illustrations other than the necessary parts are omitted.
The air conditioner includes a control unit 14 composed of a microcomputer. The control unit 14 includes a discharge temperature sensor 11, a temperature sensor 12, a temperature sensor 13, a first expansion valve 7, a second expansion valve 8, and The four-way valve 2 is electrically connected. The control unit 14 includes a CPU, a RAM that stores various data, and a ROM (none of which is shown) that stores a program and the like for performing operation control in each operation mode described below, and each temperature sensor. Based on the temperature information from 11 to 13, the first expansion valve 7, the second expansion valve 8 and the four-way valve 2 are appropriately controlled according to the program in the ROM, and various operation controls including a cooling operation and a heating operation described later are performed.

  The cooling operation and the heating operation in the air conditioner configured as described above will be sequentially described.

<Cooling operation>
When performing the cooling operation, the four-way valve 2 is switched to the switching position indicated by the solid line in FIG. When the hermetic rotary refrigerant compressor 1 is started, high-temperature and high-pressure refrigerant is discharged from the hermetic rotary refrigerant compressor 1, and the four-way valve 2, the outdoor heat exchanger 3, and the check valve 4a of the bridge circuit 4 are opened. It passes in order and flows into the gas-liquid separator 5, where it is separated into a gas phase and a liquid phase.

  During normal cooling operation, the liquid refrigerant separated by the gas-liquid separator 5 flows into the internal heat exchanger 6 as it is, and then is reduced from high pressure to low pressure by the first expansion valve 7. The air then passes through the check valve 4d of the bridge circuit 4 and exchanges heat with the indoor air in the indoor heat exchanger 9 to absorb the heat and perform a cooling action. Then, the refrigerant again passes through the four-way valve 2 and returns into the main body of the hermetic rotary refrigerant compressor 1 via the accumulator 10 of the hermetic rotary refrigerant compressor 1. This cycle is repeated to cool the room.

  Here, while the cooling operation is continued, when the discharge temperature of the hermetic rotary refrigerant compressor 1 becomes equal to or higher than a predetermined temperature set in advance, the control unit 14 opens the second expansion valve 8 and opens the gas-liquid A part of the refrigerant flowing out of the separator 5 is bypassed to the hermetic rotary refrigerant compressor 1 via the second expansion valve 8 and the internal heat exchanger 6. As a result, a part of the refrigerant exiting the gas-liquid separator 5 is reduced from high pressure to intermediate pressure by the second expansion valve 8, flows into the internal heat exchanger 6, and exchanges internal heat from the regular circulation channel. Heat is exchanged in the internal heat exchanger 6 with the high-pressure refrigerant flowing into the vessel 6. As a result, the intermediate pressure refrigerant flowing into the internal heat exchanger 6 is injected into the hermetic rotary refrigerant compressor 1 as flash gas in a gas-liquid two-phase saturated refrigerant state.

  In the hermetic rotary refrigerant compressor 1, refrigerant that normally circulates in the refrigeration cycle flows through the accumulator 10 and is compressed to high temperature and pressure in a compression chamber (see compression chamber 27 in FIG. 4 described later). However, a gas-liquid two-phase flash gas is further injected there. Thereby, compared with the case where flash gas is not drawn in, the discharge temperature of the sealed rotary refrigerant compressor 1 can be lowered. The discharge temperature can be controlled by adjusting the opening of the second expansion valve 8 and adjusting the amount of refrigerant bypassed from the gas-liquid separator 5 outlet.

  Here, the dryness (ratio of gas) of the flash gas injected into the sealed rotary refrigerant compressor 1 is preferably 0.2 to 0.8 for the following reason. That is, when the dryness is in the range of 0 to 0.2, the ratio of the liquid is excessive, so that liquid compression occurs in the hermetic rotary refrigerant compressor 1, and the same reliability degradation problem as in the prior art occurs. On the other hand, in the range of 0.8 to 1, since the latent heat of the flash gas becomes small, the discharge gas temperature cannot be lowered effectively. Therefore, it is preferable to set it as 0.2-0.8. The dryness is calculated by the control unit 14 based on the temperature information of the temperature sensor 12 that detects the temperature of the outdoor heat exchanger 3 that functions as a condenser, and the control unit 14 makes the calculated dryness fall within the above range. The opening degree of the second expansion valve 8 is adjusted. As a result, the discharge temperature can be lowered more effectively.

<Heating operation>
When the heating operation is performed, the four-way valve 2 is switched to the switching position indicated by the dotted line in FIG. When the hermetic rotary refrigerant compressor 1 is started, high-temperature and high-pressure refrigerant is discharged from the hermetic rotary refrigerant compressor 1 and flows into the indoor heat exchanger 9 through the four-way valve 2. Then, the indoor heat exchanger 9 exchanges heat with room air to dissipate heat and perform a heating operation. Then, the refrigerant sequentially passes through the check valve 4b of the bridge circuit 4 and flows into the gas-liquid separator 5, where the refrigerant is separated into a gas phase and a liquid phase.

  During normal heating operation, the liquid refrigerant separated by the gas-liquid separator 5 flows into the internal heat exchanger 6 as it is, and then is reduced from high pressure to low pressure by the first expansion valve 7. Then, after passing through the check valve 4c of the bridge circuit 4 and exchanging heat with outdoor air in the outdoor heat exchanger 3, it passes through the four-way valve 2 again and flows into the accumulator 10 of the hermetic rotary refrigerant compressor 1. .

  Here, when the discharge temperature of the hermetic rotary refrigerant compressor 1 becomes equal to or higher than a preset predetermined temperature while the heating operation is continued, the control unit 14 performs the second expansion similarly to the cooling operation. The valve 8 is opened, and a part of the refrigerant after the gas-liquid separator 5 outlet is bypassed to the hermetic rotary refrigerant compressor 1 via the second expansion valve 8 and the internal heat exchanger 6. As a result, a part of the refrigerant exiting the gas-liquid separator 5 is reduced from high pressure to intermediate pressure by the second expansion valve 8, flows into the internal heat exchanger 6, and exchanges internal heat from the regular circulation channel. Heat is exchanged in the internal heat exchanger 6 with the high-pressure refrigerant flowing into the vessel 6. As a result, the intermediate-pressure refrigerant flowing into the internal heat exchanger 6 becomes flash gas that is in a gas-liquid two-phase saturated refrigerant state, and is injected into the hermetic rotary refrigerant compressor 1. In the heating operation, as in the cooling operation, the flush gas injected into the hermetic rotary refrigerant compressor 1 preferably has a dryness of 0.2 to 0.8.

  In the hermetic rotary refrigerant compressor 1, a refrigerant that normally circulates in the refrigeration cycle flows in through an accumulator 10 and is compressed to a high temperature and a high pressure in a compression chamber. Flash gas will be injected. Thereby, compared with the case where flash gas is not drawn in, the discharge temperature of the sealed rotary refrigerant compressor 1 can be lowered. The discharge temperature can be controlled by adjusting the opening of the second expansion valve 8 and adjusting the amount of refrigerant bypassed from the gas-liquid separator 5 outlet.

FIG. 3 is a Mollier diagram in which the horizontal axis represents enthalpy h and the vertical axis represents pressure P in the air conditioner of FIG. FIG. 3 shows a Mollier diagram in a state where the discharge temperature of the hermetic rotary refrigerant compressor 1 is equal to or higher than a predetermined temperature and the second expansion valve 8 is opened.
The refrigerant in the state A on the inlet side of the hermetic rotary refrigerant compressor 1 is changed to the high pressure state B by the hermetic rotary refrigerant compressor 1 and then the pressure remains constant due to condensation in the outdoor heat exchanger 3. Entropy decreases. Then, after passing through the outdoor heat exchanger 3, the state E is entered before branching into the regular circulation circuit and the injection circuit 40. Then, the refrigerant passing through the regular circulation circuit flows into the internal heat exchanger 6 via the second expansion valve 8. Here, since a part of the medium in the state E flows into the internal heat exchanger 6 via the second expansion valve 8, the refrigerant that passes through the regular circulation circuit is passed through the second expansion valve 8. Due to the heat exchange with the intermediate pressure refrigerant, the enthalpy is in a lower state C. Then, after passing through the first expansion valve 7, the pressure decreases to state D while the enthalpy remains constant, and then the enthalpy increases while the pressure remains constant due to evaporation in the indoor heat exchanger 9. It becomes.

  On the other hand, a part of the medium in the state E passes through the second expansion valve 8, so that the pressure is reduced to the state F with the enthalpy being constant, and flows into the internal heat exchanger 6. Then, the internal heat exchanger 6 exchanges heat with the refrigerant that passes through the regular circulation circuit, and the enthalpy rises with the pressure kept constant, resulting in a state G. In this state G, that is, when the gas-liquid two-phase flash gas is caused to flow into the closed rotary refrigerant compressor 1, the state changes from the state A to the high pressure state B in the closed rotary refrigerant compressor 1. Then, the enthalpy of the refrigerant that has been in the state B1 is lowered, and the state B1 is changed to the state G. Then, at the outlet of the hermetic rotary refrigerant compressor 1, the state H is smaller than the state B. That is, the discharge temperature is lowered.

  Here, the effect of injecting the gas-liquid two-phase flash gas into the hermetic rotary refrigerant compressor 1 will be considered based on FIG. As shown in FIG. 3, the refrigerant in the state E enters the state C by exchanging heat with the intermediate-pressure refrigerant after passing through the second expansion valve 8 in the internal heat exchanger 6. The amount of change in enthalpy between state E and state C is an increase in driving ability.

  As described above, according to the first embodiment, since the flash gas, which is a gas-liquid two-phase saturated refrigerant, is injected into the hermetic rotary refrigerant compressor 1, the hermetic rotary refrigerant compressor 1 is injected. The internal temperature can be reduced, and the discharge temperature can be lowered. As a result, the driving ability can be improved as compared with the case where injection injection is not performed.

  In addition, since it is possible to prevent deterioration of the motor insulating material of the hermetic rotary refrigerant compressor 1 and to prevent a decrease in the viscosity of the lubricating oil accompanying an increase in internal temperature, the sliding portion ( It is possible to prevent wear of the sliding portion and the bearing portion in the compression chamber and improve the reliability.

  Further, since the refrigerant to be injected into the hermetic rotary refrigerant compressor 1 is a gas-liquid two-phase flash gas, liquid compression by injecting the liquid refrigerant into the hermetic rotary refrigerant compressor 1 as in the prior art. Can be avoided. As a result, the reliability of the hermetic rotary refrigerant compressor 1 can be improved, and thus the reliability of the refrigeration apparatus can be improved.

  Further, since the dryness of the flash gas is set to 0.2 to 0.8, the discharge temperature can be effectively lowered.

  Conventionally, there has been a closed type rotary refrigerant compressor having a liquid injection cycle. According to the first embodiment, liquid refrigerant having a dryness of 0 is directly injected into the compression chamber. Therefore, it is possible to solve the problem that the sliding portion (sliding portion and bearing portion in the compression chamber) is damaged by the excessive pressure generated by the liquid refrigerant compression.

Embodiment 2. FIG.
In the first embodiment, the timing for injecting the gas-liquid two-phase flash gas into the hermetic rotary refrigerant compressor 1 is not particularly described. However, in the second embodiment, the effective injection timing and the timing thereof are used. A specific hermetic rotary refrigerant compressor structure for injection will be described.

First, a specific structure of the hermetic rotary refrigerant compressor 1 will be described below.
4 and 5 are diagrams showing a cross-sectional structure of the hermetic rotary refrigerant compressor 1 of FIG. 1 of the first embodiment and a cross-sectional structure of the inside of the compression chamber.
The hermetic rotary refrigerant compressor 1 includes an electric element portion 21 including a stator 21a and a rotor 21b in a hermetic container 20, and a rotary shaft (crankshaft) 38 that is integrally mounted with the rotor 21b. A compression element portion 23 to be driven and a refrigerating machine oil (not shown) accommodated in the sealed container 20 are provided. The scroll compression element 23 includes a cylinder 24 having a cylindrical opening through which the crankshaft 38 passes, and an upper bearing 25 and a lower bearing 26 that close the opening of the cylinder 24 from above and below and support the crankshaft 38. ing. The space surrounded by the inner peripheral side wall of the opening of the cylinder 24, the upper bearing 25, and the lower bearing 26 constitutes a compression chamber 27 in which refrigerant is compressed.

  A crankpin 28 is formed eccentrically on the outer periphery of the crankshaft 38, and a roller 29 is fitted on the outer periphery of the crankpin 28. When the crankshaft 38 rotates, the roller 29 comes into contact with the inner peripheral surface of the compression chamber 27 and performs an eccentric rotational movement to perform a compression action. A vane 31 is inserted into the vane groove 30 in the cylinder 24 so as to freely enter and exit. The vane 31 comes into contact with the roller 29 while following the movement of the roller 29, and the compression chamber 27 has a high pressure space and a low pressure space. It is divided into and. In the example of FIG. 5, the chamber on the left side of the vane 31 of the compression chamber 27 is a high-pressure space, the chamber on the right side of the vane 31 is a suction space, and a suction port 33 is opened in the suction space.

  Further, a suction pipe 32 that connects the accumulator 10 and the compression chamber 27 is connected to the side surface of the hermetic rotary refrigerant compressor 1, and the suction of the compression chamber 27 from the suction port 33 through the suction pipe 32. A refrigerant is injected into the space. Further, an injection pipe 34 is connected to the side surface of the hermetic rotary refrigerant compressor 1, and flash gas, which is a gas-liquid two-phase saturated refrigerant, is compressed from the injection pipe 34 through the injection hole 35 into the compression chamber 27. It is designed to be injected inside. Further, a discharge pipe 36 for discharging the refrigerant to the outside of the hermetic rotary refrigerant compressor 1 is connected to the upper part of the hermetic rotary refrigerant compressor 1. The lower bearing 26 is covered with a discharge muffler 37.

6 (a), 6 (b), 6 (c), and 6 (d) show a compression chamber composed of a cylinder 24, a crankshaft 38, a roller 29, and a vane 31, and an injection hole 35. It is the detailed figure shown about the relationship of the arrangement | positioning position.
6 (a), FIG. 6 (b), FIG. 6 (c), and FIG. 6 (d) respectively show the cases where the rotation angle of the crankshaft 38 is 0 °, 150 °, 180 °, and 270 °, respectively. A cross-sectional view of the compression element portion 23 viewed from the bearing 26 side is shown.

  As shown in FIG. 6A, when the rotation angle of the crankshaft 38 is 0 °, low-pressure refrigerant exists in the compression chamber 27. Then, as the crankshaft 38 rotates and the rotation angle increases as shown in FIGS. 6B to 6D, the pressure of the refrigerant in the high-pressure space of the compression chamber 27 increases.

  Here, it is preferable that the gas-liquid two-phase flash gas is injected into the hermetic rotary refrigerant compressor 1 while the refrigerant pressure in the compression chamber reaches from the low pressure to the intermediate pressure (intermediate pressure stage). . This is because, for example, when the refrigerant pressure in the compression chamber is high, the internal temperature of the compression chamber, that is, the hermetic rotary type refrigerant compressor 1 is already high, and the high temperature cannot be prevented. . Therefore, it is preferable to inject before reaching the high temperature and high pressure state. It is also necessary to start the injection of the flash gas while the refrigerant pressure in the compression chamber is lower than the pressure of the flash gas. This is because if the refrigerant pressure in the compression chamber is higher than the flash gas pressure, the refrigerant in the compression chamber may flow backward toward the injection pipe 34 if an attempt is made to inject the flash gas.

  As a structure for injecting flash gas into the compression chamber at the timing as described above, in this embodiment, a straight line A connecting the crankshaft 38 and the vane 31 and a straight line B orthogonal to the straight line A (FIG. 6 ( a))), the third region in the rotation direction of the crankshaft 38 (the rotation angle of the crankshaft 38 when the position of the vane 31 is 0) The injection hole 35 is disposed at a position where the roller 29 is opened and closed. The injection hole 35 is disposed at a position not communicating with the ineffective volume space 27a (see FIG. 4) inside the roller 29, and the flash gas is surely injected into the compression chamber to effectively lower the discharge temperature. It is possible.

  By disposing at such a position, it is possible to inject flash gas when the refrigerant in the compression chamber is at a low pressure to an intermediate pressure. Explaining in the example of FIG. 6, the refrigerants in the compression chambers of FIGS. 6A to 6D are in a low pressure state, a medium pressure state, a high pressure state, and a high pressure state, respectively, and the state of FIG. Then, since the injection hole 35 is opened, flash gas is injected from the injection hole 35 into the compression chamber. Even in the state shown in FIG. 6B, since the gas is still partially opened, the injection of the flash gas is continued. 6C and 6D, the injection hole 35 is completely closed, and the flash gas is not injected into the compression chamber. Further, the flash gas is not injected into the compression chamber until the crankshaft 38 further rotates from the position shown in FIG. 6 (d) until the refrigerant is further increased in pressure and discharged from the compression chamber.

  As described above, according to the second embodiment, the same effects as those of the first embodiment can be obtained, and the gas-liquid two-phase flash gas can be used while the medium pressure in the compression chamber reaches from the low pressure to the intermediate pressure. Since the injection is performed, the temperature in the compression chamber can be lowered at an effective timing.

  As described above, the gas-liquid two-phase flash gas injection timing is preferably the timing described above, but is not necessarily limited to the timing and structure described above. For example, as an example of injecting at another timing, in the hermetic rotary refrigerant compressor 1, the flash gas may be injected into the inlet portion of the refrigerant from the accumulator 10. Also in this case, the temperature lowering effect in the compression chamber can be obtained.

  In each of the above-described embodiments, a sealed rotary refrigerant compressor having a single-stage sealed rotary refrigerant compression mechanism is mainly specified, but the same applies even if the flash gas is injected into a two-stage compressor. The effect is obtained.

  Moreover, in the said embodiment, although the case where the refrigeration apparatus was applied to the air conditioner was demonstrated to the example, it is applicable also to a refrigerator etc.

It is a figure which shows schematic structure of the freezing apparatus of Embodiment 1 of this invention. It is a block diagram which shows the electric constitution of the air conditioner of FIG. FIG. 3 is a Mollier diagram in a state where the discharge temperature of the hermetic rotary refrigerant compressor of FIG. 1 is equal to or higher than a predetermined temperature and the second expansion valve is opened. It is a figure which shows the cross-section of the sealed rotary refrigerant compressor of FIG. It is a figure which shows the cross-section of the compression chamber inside of the sealed rotation type refrigerant compressor of FIG. FIG. 2 is a detailed view showing the relationship between the arrangement positions of the compression chamber and the injection hole of the hermetic rotary refrigerant compressor of FIG. 1.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Sealing type rotary refrigerant compressor, 3 outdoor heat exchanger, 4 bridge circuit, 4a check valve, 4b check valve, 4c check valve, 4d check valve, 5 gas-liquid separator, 6 internal heat exchanger , 7 1st expansion valve, 8 2nd expansion valve, 9 indoor heat exchanger, 10 accumulator, 11 discharge temperature sensor, 12 temperature sensor, 13 temperature sensor, 14 control part, 20 airtight container, 21 electric element part, 21a fixed Child, 21b rotor, 23 compression element part, 24 cylinder, 25 upper bearing, 26 lower bearing, 27 compression chamber, 27a invalid volume space, 28 crankpin, 29 roller, 30 vane groove, 31 vane, 32 suction pipe, 33 suction port, 34 injection pipe, 35 injection hole, 36 discharge pipe, 37 discharge muffler, 38 crankshaft, 40 injection circuit.

Claims (5)

The airtight container has a compressor having a discharge pressure atmosphere, a condenser, a gas-liquid separator, an expansion valve, and an evaporator, and the refrigerant used is a refrigerant containing at least 60% by mass of R32 or R32 refrigerant. Refrigeration equipment
A refrigeration apparatus comprising an injection circuit that injects a part of the refrigerant from the gas-liquid separator outlet into the compressor as flash gas that is a gas-liquid two-phase saturated refrigerant. A compressor used in the refrigeration apparatus of claim 1,
The compressor includes an accumulator on a suction side of a compression element, and injects the flash gas into an inlet portion of the accumulator. A compressor used in the refrigeration apparatus of claim 1,
The compression element of the compressor includes a compression chamber, a vane inserted into a vane groove provided on a side wall of the compression chamber, a crankshaft, and a rotation of the crankshaft while abutting the vane. And a roller that compresses the refrigerant by eccentric rotation while contacting the inner peripheral surface of the compression chamber,
The compressor is characterized in that the position of the vane in the compression chamber is 0 °, and the flash gas is injected into a position between the rotation angle of the crankshaft of 180 ° to 270 ° in the compression chamber.   The liquid refrigerant is bypassed by the gas-liquid separator provided at the outlet of the condenser, the dryness of the flash gas is set to 0.2 to 0.8 through the throttle, and the flash gas is injected into the compressor. The refrigeration apparatus according to claim 1.   The refrigeration apparatus according to claim 4, wherein an internal heat exchanger is provided on an outlet side of the throttle portion.

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