JP4508006B2 - Refrigeration cycle equipment for vehicles - Google Patents

Description

  The present invention relates to a vehicle refrigeration cycle apparatus suitable for use in a vehicle in which a vehicle engine is stopped according to a traveling condition, such as an idle stop vehicle.

  As a conventional automobile air conditioner, for example, one disclosed in Patent Document 1 is known. That is, this automobile air conditioner is mounted on a vehicle in which the engine is stopped when the vehicle is stopped, such as an idle stop vehicle. In the refrigeration cycle, the first evaporation that cools the conditioned air is provided. In addition to the vessel, a second evaporator to which a cold storage material is added is provided. Both evaporators are arranged in an air guide housing (air conditioning case) so that conditioned air can selectively flow through individual evaporators or both evaporators.

During engine operation, the conditioned air is cooled by the first evaporator, and the heat storage material added by the refrigerant flowing through the second evaporator is frozen. Further, when the engine is stopped by the idle stop function and the compressor in the refrigeration cycle is also stopped, the conditioned air flows through the second evaporator side and is cooled by the cold heat of the regenerator material. When the maximum refrigeration output is required (during pull-down operation), the conditioned air is cooled by both evaporators.
JP 2002-274165 A

  However, in the air conditioner, it is necessary to dispose two evaporators in the air guide housing, so that the indoor unit naturally becomes large. In recent vehicles, downsizing of the indoor unit is strongly demanded in order to give priority to the occupant's living space. In order to maintain the physique of the conventional indoor unit, each evaporator must be downsized. In this case, the basic cooling performance must be sacrificed.

  In view of the above problems, an object of the present invention is to provide a refrigeration cycle apparatus for a vehicle that allows a refrigeration function to be continued even when the compressor is stopped without adding an evaporator for an indoor unit.

  In order to achieve the above object, the present invention employs the following technical means.

In the first aspect of the present invention, the compressor (110), the condenser (120), the decompressor (140), and the evaporator (150) are sequentially connected in an annular shape, and the evaporator (150) is connected to the indoor unit (150A). It is disposed inside, and is compressed and discharged from the compressor (110) by the evaporator (150), and flows through the indoor unit (150A) to the refrigerant that has passed through the condenser (120) and the decompressor (140). In a vehicle refrigeration cycle apparatus that cools air-conditioned air by absorbing heat from the air-conditioned air,
A cold storage heat exchanger (160) is provided that has a cold storage material therein, stores the cold storage material in advance using a refrigerant, and cools the refrigerant from the cold storage material stored when the compressor (110) is stopped. ,
The cold storage heat exchanger (160) is disposed outside the indoor unit (150A) and between the evaporator (150) and the compressor (110) ,
Furthermore, the cold storage heat exchanger (160) is disposed in the tank (170),
In the tank (170), a small space communicating with the inflow side of the cold storage heat exchanger (160) is formed above the cold storage heat exchanger (160), and below the cold storage heat exchanger (160). , A large space is formed that communicates with the outflow side of the cold storage heat exchanger (160) and stores the refrigerant that is condensed when the cold storage material cools,
The outflow side of the evaporator (150) communicates with a small space in the tank (170),
The open end (172b) is located on the lower end side of the large space, passes through the regenerator heat exchanger (160), leads to the upper outside of the tank (170), and is connected to the suction side of the compressor (110). An outflow pipe (172) is provided,
The outflow pipe (172) is provided with an opening (172a) communicating with a small space .

  As a result, when the refrigerant circulates through the devices (120, 140, 150) by the operation of the compressor (110), the refrigerant absorbs heat in the evaporator (150), whereby the conditioned air is cooled and the evaporator The cold storage material of the cold storage heat exchanger (160) is stored cold by the low-temperature refrigerant flowing out from (150).

  When the compressor (110) is stopped, the refrigerant absorbed and evaporated by the evaporator (150) is condensed and liquefied by cooling from the cold storage material of the cold storage heat exchanger (160). Since the volume is reduced and the pressure on the evaporator (150) side is maintained at a low pressure, the residual pressure between the condenser (120) and the evaporator (150) is maintained while the cold storage heat of the cold storage material is maintained. The refrigerant can continuously flow into the evaporator (150), and cooling of the conditioned air by the evaporator (150) can be continued.

  Therefore, the vehicle refrigeration cycle apparatus (100) that allows the refrigeration function to be continued even when the compressor (110) is stopped without adding the evaporator (150) in the indoor unit (150A) as in the prior art. It can be.

Further, the cold storage heat exchanger (160) is arranged in the tank (170), and communicates with the outflow side of the cold storage heat exchanger (160) in the tank (170), so as to store the cold storage material. Since a large space is formed so as to store the refrigerant condensed when it cools, the refrigerant condensed by the cold storage material will not stagnate in the cold storage heat exchanger (160). Heat exchange between the cold storage material and the refrigerant in the exchanger (160) can be performed efficiently.

The regenerator heat exchanger (160) is arranged in the tank (170), and the regenerator heat exchanger (160) is disposed below the regenerator heat exchanger (160) in the tank (170). Since a large space is formed in communication with the outflow side of (160) to store the refrigerant that is condensed when the cool storage material cools, the coolant condensed by the cool storage material is separated by gravity by the tank (170 The refrigerant can be efficiently stored in the tank (170).

In addition, since the outflow pipe (172) is provided with an opening (172a) communicating with the small space , the compressor (110) is in the air in the tank (170) when the compressor (110) is restarted. Since the phase refrigerant is sucked, problems due to liquid compression can be avoided.

In addition, the open end (172b) is located at the lower end side of the large space, passes through the cold storage heat exchanger (160), leads to the upper outside of the tank (170), and enters the suction side of the compressor (110). Since the outlet pipe (172) to be connected is provided, the compressor (110) can suck a part of the liquid-phase refrigerant, so that it is usually supplemented with lubricating oil mixed in the liquid-phase refrigerant. The durability of the compressor (110) can be maintained and improved.

Moreover, since the cool storage heat exchanger (160) is arrange | positioned in the tank (170) and is integrally formed, it can be set as the compact vehicle refrigeration cycle apparatus (100).

In invention of Claim 2 , in invention of Claim 1 , it is between the refrigerant | coolant between a tank (170) and a compressor (110), and between a condenser (120) and a pressure reduction device (140). An internal heat exchanger (180) for exchanging heat with the refrigerant is provided.

Thereby, since the internal heat exchanger (180) can give the degree of superheat to the refrigerant (low-pressure side refrigerant) between the cold storage heat exchanger (160) and the compressor (110), the evaporator (150) The refrigerant flowing out from the refrigerant does not need to have a degree of heating, and does not lower the refrigerant pressure in the evaporator (150), that is, without reducing the efficiency (COP) of the refrigerator as the refrigeration cycle apparatus (100). Refrigerant temperature flowing into the heat exchanger (160) is lowered, and reliable cold storage for the cold storage material is possible.
  Moreover, the high-pressure side refrigerant flowing out of the condenser (120) is supercooled by the internal heat exchanger (180), and can be supplied to the evaporator (150) side by increasing the amount of liquid phase refrigerant. In the evaporator (150), the refrigerant flow resistance decreases as the amount of the liquid-phase refrigerant increases, and the cooling capacity of the conditioned air is improved. Furthermore, since the superheat degree can be set small in the evaporator (150), the refrigerant temperature can be lowered, the temperature difference with the conditioned air can be expanded, and the cooling performance of the conditioned air can be improved. And since the low-pressure side refrigerant | coolant which flows out out of a cool storage heat exchanger (160) is overheated by the internal heat exchanger (180) and becomes a gaseous-phase refrigerant | coolant reliably, the liquid compression with respect to a compressor (110) can be prevented.

The invention according to claim 3 is characterized in that the internal heat exchanger (180) has a double tube structure.

  Accordingly, the internal heat exchanger (180) can be easily installed by arranging either one inside the other using the high-pressure side pipe through which the high-pressure side refrigerant flows and the low-pressure side pipe through which the low-pressure side refrigerant flows. Can be formed.

According to a fourth aspect of the present invention, in the second to third aspects of the present invention, the throttle opening degree of the decompressor (140) is adjusted according to the temperature of the refrigerant flowing out of the evaporator (150). This temperature expansion valve (140) is characterized in that the refrigerant superheat degree based on the refrigerant temperature is set to be smaller than a predetermined value.

  Thereby, the temperature rise of the refrigerant | coolant discharged without suppressing the refrigerant | coolant pressure by the side of an evaporator (150) can be suppressed, and cold storage to a cool storage material can be performed, without worsening freezer efficiency (COP). .

The invention described in claim 5 is characterized in that the predetermined value is zero.

  Thereby, since the temperature of the refrigerant flowing out from the evaporator (150) can be further lowered, it is possible to easily store the cold in the cold storage material and to improve the cooling performance to the conditioned air in the evaporator (150). Can be made.

The invention according to claim 6 is characterized in that the temperature sensing part (142) for detecting the refrigerant temperature is provided between the evaporator (150) and the cold storage heat exchanger (160).

  Thereby, by setting the inlet side and the outlet side of the refrigerant in the evaporator (150) to the same side surface, the temperature sensing part (142) can be easily integrated with the temperature type expansion valve (140).

In the invention of claim 7 , in the invention of claims 2 to 3 , the decompressor (140) has its throttle opening adjusted in accordance with the temperature of the refrigerant flowing out of the evaporator (150). The temperature type expansion valve (140) is a temperature type expansion valve (140) that changes the state of the refrigerant based on the refrigerant temperature, and the refrigerant sucked into the compressor (110) by the heating by the internal heat exchanger (180). It is characterized by a gas-liquid two-phase state that is surely a gas-phase refrigerant.

Thereby, since the temperature of the refrigerant | coolant in an evaporator (150) can be reduced similarly to the invention of the said 4th and 5th , without making a refrigerator efficiency (COP) worse, it is to a cool storage material. Cold storage is possible. Moreover, the cooling performance to the conditioned air in the evaporator (150) can be improved.

The invention according to an eighth aspect is characterized in that in the invention according to the fourth to seventh aspects, a fixed restricting portion (191) interposed in parallel with the temperature type expansion valve (140) is provided.

  Thereby, even if the throttle opening degree of the temperature type expansion valve (140) is adjusted to be small according to the refrigerant temperature when the compressor (110) is stopped, the refrigerant from the condenser (120) is passed through the fixed throttle part (191). Since it can be made to flow in an evaporator (150), the refrigerating capacity at the time of a compressor (110) stop can be ensured.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description mentioned later.

(First embodiment)
In the first embodiment, the engine is stopped when the refrigeration cycle apparatus for vehicles (hereinafter referred to as the refrigeration cycle apparatus) 100 according to the present invention shifts from a traveling state to an idling stop state such as waiting for a signal. The present invention is applied to a so-called idle stop vehicle, and the basic configuration thereof will be described below with reference to FIGS. 1 is a schematic view showing the overall configuration of the refrigeration cycle apparatus 100, FIG. 2 is a perspective view showing a cold storage heat exchanger 160, and FIG. 3 is a cross-sectional view showing the cold storage heat exchanger 160 and the cold storage tank 170.

  The refrigeration cycle apparatus 100 moves the heat on the low temperature side to the high temperature side and uses the heat and heat for air conditioning. As shown in FIG. 1, a normal compressor 110, a condenser 120, a liquid receiving tank 130, A cool storage heat exchanger 160 and a cool storage tank 170 are added to a cycle in which the temperature type expansion valve 140 and the evaporator 150 are sequentially connected in an annular shape.

  The compressor 110 is a fluid machine that is operated using a vehicle engine (not shown) as a drive source, and compresses and discharges the refrigerant in the refrigeration cycle apparatus 100 to high temperature and high pressure. The condenser 120 is a heat exchanger that is provided on the refrigerant discharge side of the compressor 110 and cools the refrigerant compressed to high temperature and high pressure to be condensed and liquefied. The liquid receiving tank 130 is a receiver that separates the refrigerant condensed in the condenser 120 into a gas phase refrigerant and a liquid phase refrigerant and causes the liquid phase refrigerant to flow out.

  A temperature-type expansion valve (corresponding to the pressure reducer in the present invention, hereinafter referred to as an expansion valve) 140 is a unit that decompresses and expands the liquid phase refrigerant separated in the liquid receiving tank 130 in an enthalpy manner. 150 has a temperature sensing portion 142 provided on the refrigerant outflow side (between the evaporator 150 and the cold storage heat exchanger 170). In the expansion valve 140, the throttle opening degree of the valve unit 141 is controlled according to the refrigerant temperature detected by the temperature sensing unit 142, and the degree of superheat of the refrigerant flowing out of the evaporator 150 is set to a predetermined value (for example, 5 to 10 ° C.). ) And so on.

  The evaporator 150 is a heat exchanger that exerts an endothermic effect by evaporating the refrigerant decompressed by the expansion valve 140. The evaporator 150 is disposed in the air conditioning case 151 and supplied to the air conditioning case 151. Is cooled (heat absorption from conditioned air). In addition, in the air-conditioning case 151, there are provided a blower for air-conditioning air blowing, a heat exchanger for heating air-conditioning air, an air mix door mechanism for adjusting the mixing ratio of cooling air and heating air, etc. The indoor unit 150A is formed, and the indoor unit 150A is disposed in an instrument panel in the vehicle interior.

  A regenerator heat exchanger 160 is disposed between the evaporator 150 and the compressor 110 (so as to be in series with the evaporator 150). The cold storage heat exchanger 160 is a heat exchanger that exchanges heat between the refrigerant flowing out of the evaporator 150 and the cold storage material provided therein.

  Specifically, the regenerator heat exchanger 160 is a shell and tube type heat exchanger, and as shown in FIG. 2, a plurality of refrigerant tubes 161 are arranged in the stacking direction of a plurality of stacked circular plate fins 162. The refrigerant tube 161 and the plate fin 162 are thermally joined to each other and disposed in the casing (shell) 163. Note that both longitudinal ends of each refrigerant tube 161 are opened to the outside of the casing 163. Furthermore, the regenerator material is enclosed in the casing 163 from the regenerator material enclosure 164 (the regenerator material enclosure 164 is sealed after the regenerator material is encapsulated), and the regenerator material is placed on the surfaces of the refrigerant tubes 161 and the plate fins 162. I try to make contact. The cold storage material can be paraffin, ice, or the like.

  Further, between the cold storage heat exchanger 160 and the compressor 110, a cold storage tank for storing refrigerant that is condensed and liquefied when the cold storage material is allowed to cool in the cold storage heat exchanger 160 (corresponding to the tank in the present invention). ) 170 is provided. Here, the cold storage tank 170 is disposed below the cold storage heat exchanger 160, and in addition, the cold storage heat exchanger 160 and the cold storage tank 170 are integrally formed.

  That is, as shown in FIG. 3, the cold storage tank 170 is a cylindrical tank whose axis is directed to the top and bottom, both ends are closed, and the lower side is constricted. The regenerator heat exchanger 160 is disposed such that the longitudinal direction of the tube 161 is the top-and-bottom direction. In the cold storage tank 170, a small space is formed on the upper side of the cold storage heat exchanger 160, and a large space is formed on the lower side. The upper end portion of the refrigerant tube 161 of the cold storage heat exchanger 160 communicates with the small space, and the refrigerant tube The lower end portion of 161 communicates with the large space. As will be described later, the large space serves as a tank storage section for storing a refrigerant that is condensed and liquefied when the cold storage material is allowed to cool in the cold storage heat exchanger 160.

  Then, an inflow pipe 171 connected from the outflow side of the evaporator 150 and communicated with the small space of the cold storage tank 170, and an open end portion (corresponding to the liquid phase refrigerant inflow portion in the present invention) 172b at the lower end side of the large space. Is provided, and an outflow pipe 172 that passes through the cold storage heat exchanger 160 and is connected to the suction side of the compressor 110 through the upper outside of the cold storage tank 170 is provided. An opening 172a communicating with the small space is provided at a portion corresponding to the small space of the outflow pipe 172. The opening end portion 172b of the outflow pipe 172 is formed to be thin, and the opening area thereof is smaller than the opening area of the opening 172a.

  The cold storage heat exchanger 160 and the cold storage tank 170 integrally formed as described above are disposed in the vehicle engine room. If there is an allowable mounting space in the vehicle interior, the cool storage heat exchanger 160 and the cold storage tank 170 are disposed in the vehicle interior. It is preferable.

  Next, the operation of the refrigeration cycle apparatus 100 based on the above configuration and the function and effect thereof will be described.

1. Cold storage mode When the vehicle travels, the compressor 110 is driven by the engine, and the refrigeration cycle apparatus 100 operates. The refrigerant compressed and discharged by the compressor 110 is condensed into a condensate by the condenser 120, depressurized by the expansion valve 140 through the liquid receiving tank 130, absorbs heat from the conditioned air and evaporates by the evaporator 150, and cools the conditioned air. (Cool).

  And the refrigerant | coolant which flows out from the evaporator 150 flows through the refrigerant | coolant tube 161 of the cool storage heat exchanger 160 through the inflow pipe 171, and cools a cool storage material (a cool storage material is stored cold by the heat absorption from a refrigerant | coolant). Refrigerant absorbed by the evaporator 150 and the cold storage heat exchanger 160 respectively becomes superheated gas refrigerant, reaches the large space of the cold storage tank 170 from the refrigerant tube 161, and is sucked from the opening 172a or the opening end 172b of the outflow pipe 172. To return to the compressor 110. In the refrigeration cycle apparatus 100, in addition to the vehicle interior heat load, the cooling heat load of the cold storage material becomes a total cooling load, and when the cold storage to the cold storage material is completed, the refrigerant and the cold storage material in the cold storage heat exchanger 160 are completed. The heat transfer between is stopped.

2. Cooling mode When the vehicle stops and the engine is stopped, the compressor 110 is also stopped. At this time, in the refrigeration cycle apparatus 100, from the condenser 120 and the liquid receiving tank 130 on the high pressure side to the evaporator 150, the cold storage heat exchanger 160 and the cold storage tank 170 on the low pressure side, the residual pressure passes through the expansion valve 140. The refrigerant flows in.

  The refrigerant flowing into the evaporator 150 cools the conditioned air by heat exchange with the conditioned air and becomes superheated gas refrigerant, but flows into the cold storage heat exchanger 160 from the inlet pipe 171 and is cooled by the cold storage heat of the cold storage material. The liquid is condensed and liquefied, and is stored as liquid refrigerant in a large space below the cold storage tank 170 by gravity.

  That is, the superheated gas refrigerant from the evaporator 150 is condensed in the cold storage heat exchanger 160 to reduce the volume and maintain the pressure at a low pressure, so that the cold storage heat of the cold storage material is retained even when the compressor 110 is stopped. During this time, due to the residual pressure between the condenser 120 and the evaporator 150, the refrigerant can continuously flow into the evaporator 150, and the cooling of the conditioned air by the evaporator 150 can be continued.

  Therefore, the refrigeration cycle apparatus 100 for a vehicle that allows the refrigeration function to be continued even when the compressor 110 is stopped can be provided without adding the evaporator 150 in the indoor unit 150A as in the prior art.

  Further, since the cold storage tank 170 is provided below the cold storage heat exchanger 160, the liquid refrigerant condensed by the cold storage material flows down into the cold storage tank 170 due to gravity and stagnates in the cold storage heat exchanger 160. Thus, heat exchange between the cold storage material and the refrigerant in the cold storage heat exchanger 160 can be performed efficiently. That is, since the condensed liquid refrigerant does not remain as a thick film on the inner wall surface of the refrigerant tube 161 of the cold storage heat exchanger 160, a sufficient heat transfer surface with the cold storage material is ensured and efficient heat exchange is possible. It is a translation.

  Moreover, since the cold storage heat exchanger 160 and the cold storage tank 170 are integrally formed, the compact refrigeration cycle apparatus 100 can be obtained.

  In the cooling mode, when the vehicle shifts to the running state, the engine is started and the compressor 110 is also operated. The compressor 110 mainly sucks superheated gas refrigerant from the opening 172a having a large opening area in the outflow pipe 172, and can operate the refrigeration cycle apparatus 100 while avoiding problems due to liquid compression. .

  Here, since the open end 172b of the outflow pipe 172 opens to the lower side of the large space of the cold storage tank 170, the compressor 110 simultaneously sucks a part of the liquid refrigerant stored therein. . Normally, in the refrigeration cycle apparatus 100, the lubricating oil is mixed in the liquid refrigerant, and the lubricating oil is replenished to the compressor 110 together with the liquid refrigerant, so that the durability of the compressor 110 can be maintained and improved. .

  Further, since the temperature sensing part 142 of the expansion valve 140 is provided between the evaporator 150 and the cold storage heat exchanger 160, the refrigerant inlet side and outlet side in the evaporator 150 are set to the same side surface. Thus, the temperature sensing part 142 can be easily integrated with the temperature type expansion valve 140.

  Note that the condenser 120 may be integrally configured as a modulator tank in the condenser 120 in a system (so-called subcool condenser) that cools to a refrigerant supercooling region. The liquid tank 130 may be omitted.

  Further, in the system of the present embodiment, there is a characteristic that the longer the cooling time can be secured as the amount of the high-pressure side refrigerant is larger, so when the compressor 110 stoppable time should be maintained longer than a predetermined time, as necessary The liquid receiving tank 130 may be added, or the capacity of the liquid receiving tank 130 or the high-pressure pipe diameter may be increased.

(Second Embodiment)
A second embodiment of the present invention is shown in FIG. 2nd Embodiment adds the internal heat exchanger 180 to the refrigerating-cycle apparatus 100 with respect to the said 1st Embodiment.

  The internal heat exchanger 180 includes a high-pressure side refrigerant between the condenser 120 and the expansion valve 140 (specifically, between the liquid receiving tank 130 and the expansion valve 140), and between the cold storage tank 170 and the compressor 110. Heat exchange with the low-pressure side refrigerant. The internal heat exchanger 180 is formed, for example, by disposing a low-pressure side pipe through which the low-pressure side refrigerant flows in a predetermined region (predetermined length) of the high-pressure side pipe through which the high-pressure side refrigerant flows. That is, the high-pressure side refrigerant flows between the high-pressure side pipe and the low-pressure side pipe, and exchanges heat with the low-pressure side refrigerant flowing in the low-pressure side pipe. The high-pressure side refrigerant is supercooled by the low-pressure side refrigerant, and the low-pressure side refrigerant is superheated by the high-pressure side refrigerant.

  In addition, since the refrigerant before flowing into the compressor 110 is overheated by the internal heat exchanger 180 as described above, the refrigerant flowing out of the evaporator 150 is not given as much superheat as possible ( To reduce the degree of superheat). Specifically, the expansion valve 140 is set so that the degree of superheat is 0 to 3 ° C. (corresponding to a value smaller than a predetermined value in the present invention) (the throttle opening degree is greater than the refrigerant temperature in the temperature sensing unit 142). Etc.) to make it larger.

  In the second embodiment configured as described above, the cold storage heat exchanger 160 and the cold storage tank 170 perform the cold storage mode and the cooling mode similar to those of the first embodiment, and the refrigeration function when the compressor 110 is stopped. Can be continued.

  Further, since the superheat degree can be given to the low-pressure side refrigerant by the internal heat exchanger 180, the refrigerant flowing out of the evaporator 150 is prevented from having the superheat degree by setting the expansion valve 140. Without reducing the refrigerant pressure in the cooler 150, that is, without lowering the refrigerator efficiency (COP) as the refrigeration cycle apparatus 100, the temperature of the refrigerant flowing into the cold storage heat exchanger 160 is lowered, and the cold storage material can be reliably Cold storage is possible.

  Further, by adding the internal heat exchanger 180, the degree of supercooling of the refrigerant flowing from the condenser 120 to the evaporator 150 can be increased, and the amount of liquid-phase refrigerant flowing out of the condenser 120 is increased to increase the evaporator. Since it can supply to the 150 side, in the evaporator 150, the refrigerant | coolant circulation resistance reduces with the increase in the amount of liquid phase refrigerant | coolants, and can improve the cooling performance of conditioned air. Furthermore, since the degree of superheat in the evaporator 150 can be set small, the refrigerant temperature can be lowered, the temperature difference with the conditioned air can be expanded, and the cooling performance of the conditioned air can be improved. And since the refrigerant | coolant which flows out out of the cool storage tank 170 is overheated by the internal heat exchanger 180 and becomes a gaseous-phase refrigerant | coolant reliably, the liquid compression with respect to the compressor 110 can be prevented.

  In the above description, the superheat degree in the evaporator 150 is set to 0 to 3 ° C., for example. However, if the internal heat exchanger 180 can obtain a predetermined superheat degree (a gas phase refrigerant), May not have the degree of superheat completely, that is, the degree of superheat may be 0 ° C. or lower so that the refrigerant is in a gas-liquid two-phase state.

(Third embodiment)
A third embodiment of the present invention is shown in FIG. In the third embodiment, a fixed throttle portion 191 arranged in parallel with the expansion valve 140 is provided with respect to the second embodiment.

  Specifically, a bypass passage 190 that bypasses the valve portion 141 of the expansion valve 140 is provided, and a fixed throttle portion 191 that is fixed at a predetermined opening degree is provided in the bypass passage 190.

  In the cold storage mode (when the compressor 110 is in operation), the expansion valve 140 opens the valve unit 141 to a predetermined opening according to the refrigerant temperature (refrigerant superheat degree) of the temperature sensing unit 142, but in the cooling mode. Then, the low pressure side pressure increases due to the stop of the compressor 110, and the temperature sensing part 142 is cooled, so that the valve part 141 may be gradually closed.

  As described above, the cooling capacity in the cooling mode is limited by the opening degree of the expansion valve 140 at this time. However, in the third embodiment, the fixed throttle portion 191 is provided. Regardless of the throttle opening of the expansion valve 140 that can be varied, the refrigerant that flows out of the compressor 120 can flow into the evaporator 150 through the fixed throttle 191, so that the cooling capacity when the compressor 110 is stopped is ensured. be able to.

(Other embodiments)
Although the cold storage heat exchanger 160 in each said embodiment demonstrated as a shell and tube type thing, as shown in Fig.6 (a)-FIG.6 (c), not only this but the cold storage which enclosed the cold storage material Capsule 165 (rod-shaped capsule 165a, spherical capsule 165b, bowl-shaped capsule 165c, etc.) is filled in a predetermined casing (not shown), and the refrigerant flows through the gap between cool storage capsule 165 and cool storage capsule 165. Also good.

  Further, the internal heat exchanger 180 is not limited to a double pipe structure, and two parallel flow paths are provided inside, the high pressure side refrigerant flows in one flow path, and the low pressure flows in the other flow path. The side fluid may flow, and heat may be exchanged between the two.

It is a mimetic diagram showing the whole refrigeration cycle device composition in a 1st embodiment. It is a perspective view which shows a cool storage heat exchanger. It is sectional drawing which shows a cool storage heat exchanger and a cool storage tank. It is a schematic diagram which shows the whole structure of the refrigerating-cycle apparatus in 2nd Embodiment. It is a schematic diagram which shows the whole structure of the refrigeration cycle apparatus in 3rd Embodiment. It is a perspective view which shows the cool storage heat exchanger (cold storage capsule) in other embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 Refrigeration cycle apparatus for vehicles 110 Compressor 120 Condenser 140 Temperature type expansion valve (decompressor)
142 Temperature Sensing Unit 150 Evaporator 150A Indoor Unit 160 Cold Storage Heat Exchanger 170 Cold Storage Tank (Tank)
172 Outflow pipe (piping)
172b Open end (liquid refrigerant inflow portion)
180 Internal heat exchanger 191 Fixed throttle

Claims (8)

The compressor (110), the condenser (120), the decompressor (140), and the evaporator (150) are sequentially connected in an annular shape, and the evaporator (150) is disposed in the indoor unit (150A).
From the conditioned air flowing through the indoor unit (150A) to the refrigerant compressed and discharged from the compressor (110) through the condenser (120) and the decompressor (140) by the evaporator (150). In the vehicle refrigeration cycle apparatus that cools the conditioned air by absorbing heat,
A regenerative heat exchanger that has a regenerator material therein, stores the regenerator material in advance with the refrigerant, and cools the refrigerant from the regenerator material stored when the compressor (110) is stopped ( 160), and
The cold storage heat exchanger (160) is disposed outside the indoor unit (150A) and between the evaporator (150) and the compressor (110) ,
Furthermore, the cold storage heat exchanger (160) is disposed in the tank (170),
In the tank (170), a small space communicating with the inflow side of the cold storage heat exchanger (160) is formed above the cold storage heat exchanger (160), and the cold storage heat exchanger (160) On the lower side, a large space is formed which communicates with the outflow side of the cold storage heat exchanger (160) and stores the refrigerant condensed when the cold storage material cools down,
The outflow side of the evaporator (150) communicates with the small space in the tank (170),
An open end (172b) is positioned on the lower end side of the large space, passes through the cold storage heat exchanger (160), and leads to the upper outside of the tank (170) to suck the compressor (110). An outflow pipe (172) connected to the side is provided,
The refrigeration cycle device for vehicles, wherein the outflow pipe (172) is provided with an opening (172a) communicating with the small space . A refrigerant between the tank (170) and the compressor (110);
The vehicle refrigeration according to claim 1 , further comprising an internal heat exchanger (180) for exchanging heat with the refrigerant between the condenser (120) and the decompressor (140). Cycle equipment. The vehicular refrigeration cycle apparatus according to claim 2 , wherein the internal heat exchanger (180) has a double pipe structure. The pressure reducer (140) is a temperature type expansion valve (140) whose throttle opening is adjusted according to the temperature of the refrigerant flowing out of the evaporator (150),
The refrigeration cycle device for vehicles according to claim 2 or 3 , wherein the temperature type expansion valve (140) is set so that a degree of refrigerant superheating based on the refrigerant temperature is smaller than a predetermined value. . The vehicular refrigeration cycle apparatus according to claim 4 , wherein the predetermined value is zero. Temperature sensing unit for detecting the refrigerant temperature (142), according to claim 4 or claim 5, characterized in that provided between the evaporator (150) and the cold storage heat exchanger (160) Refrigeration cycle equipment for vehicles. The pressure reducer (140) is a temperature type expansion valve (140) whose throttle opening is adjusted according to the temperature of the refrigerant flowing out of the evaporator (150),
The temperature type expansion valve (140) has a refrigerant state based on the refrigerant temperature, and the degree that the refrigerant sucked into the compressor (110) by the heating by the internal heat exchanger (180) reliably becomes a gas phase refrigerant. The vehicle refrigeration cycle apparatus according to claim 2 or 3 , wherein the gas-liquid two-phase state is set. The vehicular refrigeration cycle apparatus according to any one of claims 4 to 7 , further comprising a fixed throttle portion (191) interposed in parallel with the temperature type expansion valve (140).

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