JP2006248338A - Cold storage heat exchanger equipped with ejector, expansion valve, and air-conditioner for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the vehicle loading performance by integrally constituting required constituent parts. <P>SOLUTION: A coolant flow-in section 11b of this cold storage heat exchanger 11 is arranged on the top side in the vertical direction, and a coolant flow-out section 11c is arranged on the bottom side. At the same time, the coolant flow-out direction of this ejector 9 is arranged on the top side, and the suction section 9b is connected and integrated with the coolant flow-out section 11c. Thus, the gas coolant which is evaporated in an evaporator 8 at the time of a cold emitting mode turns into a condensed liquid by a cooled cold storage heat exchanger 11, and is collected in the lower section of the cold storage heat exchanger 11 by the gravity. Then, the ejector 9 efficiently sucks the condensed liquid coolant by connecting the coolant flow-out section 11c arranged at the lower section with the suction section 9b of the ejector 9 by a minimum distance, and the coolant can be circulated again to the evaporator 8. Also, a cold storage unit 15 can be constituted to be compact by making the ejector 9 and the cold storage heat exchanger 11 approximately in parallel, and arranging in the vertical direction, and thus, the vehicle loading performance can be improved. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a cold storage heat exchanger that provides a cooling action when a refrigerant compressor is stopped, and more specifically, to a cold storage heat exchanger that includes an ejector, an expansion valve that is suitable for use together with this, and these ejectors. The present invention relates to a vehicle air conditioner including a cold storage heat exchanger and an expansion valve.

  In recent years, vehicles (eco-run vehicles such as hybrid vehicles) that automatically stop the vehicle engine when stopping, such as waiting for traffic lights, have been put to practical use for the purpose of environmental protection and improved fuel efficiency of the vehicle engine. The number of vehicles that stop the engine tends to increase. By the way, in the vehicle air conditioner, since the refrigerant compressor of the refrigeration cycle is driven by the vehicle engine, the refrigerant compressor also stops every time the vehicle engine is stopped in the eco-run vehicle due to stopping at a signal or the like. However, since the temperature of the cooling refrigerant evaporator rises and the temperature of air blown into the passenger compartment rises, there arises a problem that the cooling feeling of the occupant deteriorates.

  Therefore, it is provided with cold storage means for storing cold during operation of the vehicle engine (refrigerant compressor), and when the vehicle engine (refrigerant compressor) stops and the cooling action of the refrigerant evaporator stops, the cold storage heat amount of the cold storage means is used. There is an increasing need for a regenerative vehicle air conditioner that can cool the air blown into the passenger compartment. As this type of regenerative type vehicle air conditioner, one described in Patent Document 1 is known.

In addition, the inventors of the present invention have problems with vehicle mountability in the cool storage type vehicle air conditioner configured as shown in Patent Document 1, and therefore, as means for improving the vehicle mountability, the cool storage heat exchanger, Patent Document 2 has applied for a method of configuring a liquid tank, an electric pump, and a check valve in the same tank. This is a cold storage operation, in which the cold storage agent filled in the cold storage heat exchanger is cooled with low-temperature refrigerant decompressed and expanded by an expansion valve to cool the cold storage, and when the vehicle engine (refrigerant compressor) stops, the electric pump is operated to perform cold storage heat exchange. The refrigerant cooled and liquefied by the cooler is supplied to the refrigerant evaporator and evaporated to cool down, thereby realizing air conditioning when the vehicle engine (refrigerant compressor) is stopped.
JP 2000-313226 A JP 2004-51077 A (US Pat. No. 6,701,731)

  Furthermore, the inventors of the present invention are disclosed in Japanese Patent Application No. 2005-4450 as a regenerative type vehicle air conditioner that can improve durability and reliability and reduce the manufacturing cost by simplifying the configuration. Has been filed. This uses an ejector as a liquid refrigerant circulation means (fluid pump means), accumulates cold heat in the cold storage heat exchanger during traveling, and mainly uses the pressure energy of the high-pressure refrigerant remaining in the refrigerant radiator when stopped. Is driven, and the refrigerant cooled by the cold storage heat exchanger is sent out to the cooling refrigerant evaporator, thereby realizing the vehicle interior cooling operation when the vehicle engine (refrigerant compressor) is stopped.

  However, the above-mentioned conventional technology has a merit that it can be cooled by the pressure energy of the high-pressure refrigerant and can improve the durability of the apparatus because there is no moving part, but in addition to the ejector, there is a check valve, a regenerative heat exchanger, and an ejector. Since a driving flow path for guiding the high-pressure refrigerant is required, there is a problem that if these are connected as they are, a large mounting space on the vehicle is required. The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to provide cold storage heat provided with an ejector that can integrate necessary constituent parts and improve vehicle mountability. It is providing a exchanger, an expansion valve, and a vehicle air conditioner.

In order to achieve the above object, the present invention employs technical means described in claims 1 to 7. That is, in the invention according to claim 1, a refrigerant compressor (1) for compressing the refrigerant,
A refrigerant radiator (6) for radiating high-pressure refrigerant discharged from the refrigerant compressor (1);
An expansion valve (7) for depressurizing the refrigerant that has passed through the refrigerant radiator (6);
A refrigerant evaporator (8) for evaporating the low-pressure refrigerant decompressed by the expansion valve (7) and cooling the air blown into the vehicle interior;
A regenerator heat exchanger (11) having a regenerator material (11a) provided on the upstream side of the refrigerant evaporator (8) and cooled by the low-pressure refrigerant when the refrigerant compressor (1) is operated;
A bypass path (12) having a check means (13) for bypassing the refrigerant from the suction side of the refrigerant compressor (1) to immediately after the expansion valve (7);
A drive flow path (14) branched from the high pressure side of the expansion valve (7);
The pressure energy of the high-pressure refrigerant flowing from the drive flow path (14) is converted to velocity energy, and the nozzle (9a) that decompresses and expands the refrigerant is connected to the low-pressure side by the high-speed refrigerant flow that is injected from the nozzle (9a). The refrigerant is sucked from the cold storage heat exchanger (11), and the sucked refrigerant and the refrigerant injected from the nozzle (9a) are mixed to convert the speed energy into pressure energy to increase the pressure of the refrigerant to evaporate the refrigerant. An ejector (9) having a boosting section (9c, 9d) for flowing into the vessel (8);
A bypass (17) for bypassing the ejector (9) to supply refrigerant from the cold storage heat exchanger (11) to the refrigerant evaporator (8) and having a check means (18);
In the cold storage heat exchanger (11) used for the vehicle air conditioner that drives the ejector (9) when the refrigerant compressor (1) stops,
While arrange | positioning the refrigerant | coolant inflow part (11b) of a cool storage heat exchanger (11) as the ceiling side of a top-and-bottom direction, and a refrigerant | coolant outflow part (11c) as a ground side,
The refrigerant outlet direction of the ejector (9) is the top side, and the suction part (9b) is connected to the refrigerant outlet part (11c) to be integrated.

Moreover, in invention of Claim 2, the refrigerant | coolant compressor (1) which compresses a refrigerant | coolant,
A refrigerant radiator (6) for radiating high-pressure refrigerant discharged from the refrigerant compressor (1);
An expansion valve (7) for depressurizing the refrigerant that has passed through the refrigerant radiator (6);
A refrigerant evaporator (8) for evaporating the low-pressure refrigerant decompressed by the expansion valve (7) and cooling the air blown into the vehicle interior;
A regenerator heat exchanger (11) having a regenerator material (11a) provided on the upstream side of the refrigerant evaporator (8) and cooled by the low-pressure refrigerant when the refrigerant compressor (1) is operated;
A bypass path (12) having a check means (13) for bypassing the refrigerant from the suction side of the refrigerant compressor (1) to immediately after the regenerative heat exchanger (11);
A drive flow path (14) branched from the high pressure side of the expansion valve (7);
The pressure energy of the high-pressure refrigerant flowing from the drive flow path (14) is converted into velocity energy, and the nozzle (9a) that decompresses and expands the refrigerant, and the high-speed refrigerant flow that is injected from the nozzle (9a) are connected to the low-pressure side. The refrigerant is sucked from the cold storage heat exchanger (11), and the sucked refrigerant and the refrigerant injected from the nozzle (9a) are mixed to convert the speed energy into pressure energy to increase the pressure of the refrigerant to evaporate the refrigerant. An ejector (9) having a boosting section (9c, 9d) for flowing into the vessel (8);
In parallel with the ejector (9), a refrigerant is supplied from the regenerator heat exchanger (11) to the refrigerant evaporator (8) and has a communication passage (17) having a check means (18).
In the cold storage heat exchanger (11) used for the vehicle air conditioner that drives the ejector (9) when the refrigerant compressor (1) stops,
While arrange | positioning the refrigerant | coolant inflow / outflow part (11b, 11c) of a cool storage heat exchanger (11) in the top-and-bottom side of a top-and-bottom direction,
The refrigerant outlet direction of the ejector (9) is the top side, and the suction part (9b) is connected to the ground side refrigerant inlet / outlet part (11c) to be integrated.

  Claim 1 and claim 2 are different from each other in the premise of the configuration of the refrigeration cycle. However, in any invention, the gas refrigerant evaporated in the refrigerant evaporator (8) in the cooling mode is cooled. It becomes condensate in the cold storage heat exchanger (11) and collects in the lower part of the cold storage heat exchanger (11) by gravity. By connecting the refrigerant outflow part (refrigerant inflow / outflow part) (11c) and the suction part (9b) of the ejector (9) at the shortest distance, the ejector (9) efficiently condenses the condensate refrigerant. The refrigerant can be sucked and circulated through the refrigerant evaporator (8) again.

  Moreover, the cool storage unit (15) as a cool storage heat exchanger provided with an ejector can be made small by arranging the ejector (9) and the cool storage heat exchanger (11) in the vertical direction so as to be substantially parallel. The vehicle mountability can be improved.

  Moreover, in invention of Claim 3, in the cool storage heat exchanger provided with the ejector in any one of Claim 1 or Claim 2, an expansion valve (7), a refrigerant evaporator (8), an ejector (9 ) And the regenerator heat exchanger (11) are integrally formed, and the check means (13, 18) are configured in the refrigerant flow path.

  According to the third aspect of the present invention, the above-described refrigerant flow paths between the respective devices are integrally configured, and the check means (13, 18) are integrally configured in the refrigerant flow paths. Thereby, it can comprise not only as a cool storage heat exchanger (11) provided with the ejector (9) but as a complete cool storage unit (15).

  And between the refrigerant evaporator (8) normally arrange | positioned in a vehicle interior, the refrigerant compressor (1) arrange | positioned in an engine room, and a refrigerant radiator (6), a cool storage unit (15) + expansion valve (7) can be put together in a layout that just inserts, so not only can the space on the vehicle be saved, but it is also very useful to add to the existing refrigeration cycle that is not equipped with a cold storage unit. Will be convenient.

  In the invention described in claim 2, the refrigerant flow direction in the regenerator heat exchanger (11) is reversed between the normal cooling / cold storage mode and the cool-down cooling mode. By doing in this way, the refrigerant | coolant piping part pressure-reduced with an expansion valve (7) can be connected with the suction part (9b) of an ejector (9), and the lower part of a cool storage heat exchanger (11), Claim 1 In the invention described in the above, an ascending refrigerant flow path disposed beside the ejector (9) is not required, and a refrigerant flow path having a check means (18) disposed on the side of the ejector (9). And the check means (18) can be moved upward. From these, in the invention described in claim 2, the ejector (9) disposed on the side of the regenerator heat exchanger (11) and the refrigerant flow path portion can be configured more compactly and simply, so that they can be integrated. Is suitable.

  Moreover, in invention of Claim 4, in the cool storage heat exchanger provided with the ejector in any one of Claim 1 or Claim 2, an expansion valve (7), a refrigerant evaporator (8), an ejector (9 ) And the regenerator heat exchanger (11) are integrated with each other, and the connecting portions (15a to 15c) with the expansion valve (7) are arranged on the lower side of the ejector (9). It is characterized by that.

  According to the fourth aspect of the present invention, since the drive inlet to the normal ejector (9) and the suction part (9b) are close to each other, the expansion valve (7) is close to the suction part (9b). That is, it becomes rational from the upper surface of space efficiency to arrange | position to the lower side of an ejector (9) and a cool storage heat exchanger (11). In addition, by arranging a plurality of connecting portions (15a to 15c) in a uniform manner, a structure in which the plurality of connecting portions (15a to 15c) can be connected at a time in combination with a box-type expansion valve (7) to be described later. Can do.

  Moreover, in invention of Claim 5, in the cool storage heat exchanger provided with the ejector in any one of Claim 1 or Claim 2, an expansion valve (7), a refrigerant evaporator (8), an ejector (9 ) And the regenerator heat exchanger (11) are integrated with each other, and the connection portions (15d, 15e) with the refrigerant evaporator (8) are arranged to be aligned with the side portions on the top side. It is characterized by that.

  According to the fifth aspect of the present invention, by arranging the connecting portions (15d, 15e) with the refrigerant evaporator (8) to be aligned, the plurality of connecting portions (15d, 15e) are combined with the block joint. The structure can be connected at a time.

  In the invention described in claim 6, the high-pressure refrigerant passage (74) inside the structure (B) is provided with a drive flow path (14) branched from a portion upstream of the valve means (73). The refrigerant outlet via the valve means (73), the refrigerant outlet of the driving flow path (14), and the low-pressure refrigerant passage (75) are provided on the same surface of the structure (B).

  According to the sixth aspect of the present invention, the high-pressure refrigerant can be guided to the drive inlet of the ejector (9) at the shortest distance, and the drive flow path (14) can be made extremely short. Moreover, the connection part corresponding to the connection part (15a-15c) with an ejector (9) and a cool storage heat exchanger (11) can be concentrated on the same surface of a structure (B), and a some connection part (15a To 15c) can be connected at a time.

  Moreover, in invention of Claim 7, the cool storage heat exchanger (15) provided with the ejector in any one of Claim 1 thru | or 5, and the expansion valve (7) in Claim 6 are made into a vehicle. It is characterized by the fact that it is used for an air conditioner for automobiles.

  According to the seventh aspect of the present invention, a small-sized regenerator in which the connection portions (15a to 15c) with the expansion valve (7) and the connection portions (15d, 15e) with the refrigerant evaporator (8) are combined. Since it is configured as a unit (15), it is between the refrigerant evaporator (8) normally disposed in the passenger compartment and the refrigerant compressor (1) and refrigerant radiator (6) disposed in the engine room. Thus, the layout can be summarized in such a manner that the cold storage unit (15) and the expansion valve (7) are simply sandwiched, so that the vehicle air conditioner can be mounted on the vehicle.

  Further, even in a vehicle air conditioner that is not currently equipped with a cold storage unit, a vehicle air conditioner capable of additionally mounting only the portion of the cold storage unit (15) + expansion valve (7) as an additional function is provided. it can. Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with the specific means described in the embodiments described later.

(First embodiment)
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. FIG. 1 is a schematic diagram showing an overall configuration of a vehicle air conditioner according to a first embodiment of the present invention. The vehicle air conditioner of the present embodiment is mounted on a vehicle such as a hybrid vehicle that automatically stops the vehicle engine when the vehicle stops, such as waiting for a signal.

  The refrigeration cycle of a vehicle air conditioner has a compressor 1 that constitutes a refrigerant compressor that sucks, compresses, and discharges refrigerant, and the compressor 1 is provided with an electromagnetic clutch 2 for power interruption. The compressor 1 is driven by the power of the vehicle engine 4 transmitted through the electromagnetic clutch 2 and the belt 3, and the energization of the electromagnetic clutch 2 is intermittently performed by an air conditioning control device 5 that constitutes a control means for air conditioning. The operation of the compressor 1 is intermittent.

  The high-temperature and high-pressure superheated vapor phase refrigerant discharged from the compressor 1 flows into a condenser (refrigerant condenser) 6 constituting a refrigerant radiator, and is cooled and condensed by exchanging heat with outside air blown from a cooling fan (not shown). The condenser 6 separates the condensing unit 6a, the gas / liquid of the refrigerant after passing through the condensing unit 6a, stores the liquid refrigerant and discharges the liquid refrigerant, and passes the liquid refrigerant from the liquid receiver 6b. This is a well-known unit integrally configured with the supercooling portion 6c to be cooled.

  The supercooled liquid refrigerant from the supercooling section 6c is decompressed to a low pressure by the expansion valve 7 constituting the decompression means, and enters a low pressure gas-liquid two-phase state. The expansion valve 7 is a temperature type expansion valve that adjusts the opening degree (refrigerant flow rate) of the valve means 73 so as to adjust the degree of refrigerant superheat at the outlet of the evaporator 8 constituting the refrigerant evaporator.

  In particular, in this example, the low pressure refrigerant passage 75 through which the outlet refrigerant of the evaporator 8 flows is configured in the box type valve block B, and the temperature sensing mechanism E of the outlet refrigerant of the evaporator 8 is integrated in the valve block B. A temperature type expansion valve 7 is used. A structural example of the expansion valve 7 will be described later.

  The evaporator 8 of the cooling heat exchanger evaporates the low-pressure refrigerant decompressed by the expansion valve 7 and cools the air blown into the vehicle interior. FIG. 2 is a schematic cross-sectional view showing a schematic configuration of the air conditioning indoor unit 20 in FIG. The indoor unit 20 is usually mounted inside the instrument panel at the front of the vehicle interior. The air conditioning case 21 of the indoor unit 20 constitutes a passage for air blown into the vehicle interior, and the evaporator 8 is installed in the air conditioning case 21.

  In the air conditioning case 21, a blower 22 is disposed on the upstream side of the evaporator 8, and the blower 22 is provided with a centrifugal multiblade fan (sirocco fan) 22a and a drive motor 22b. An inside / outside air switching box 23 is disposed on the suction side of the blower fan 22a, and outside air (inside the vehicle interior air) or inside air (inside the vehicle interior) is switched and introduced by an inside / outside air switching door 23a in the inside / outside air switching box 23.

  In the air conditioning case 21, an air mix door 24 is disposed on the downstream side of the evaporator 8, and on the downstream side of the air mix door 24, a hot water heater core that heats air using hot water (cooling water) of the vehicle engine 4 as a heat source. 25 is installed as a heat exchanger for heating. A bypass passage 26 that bypasses the hot water heater core 25 and flows air (cold air) is formed on the side (upper portion) of the hot water heater core 25.

  The air mix door 24 is a rotatable plate-like door, and adjusts the air volume ratio between the hot air passing through the hot water heater core 25 and the cold air passing through the bypass passage 26, and the air volume ratio of the cold / hot air. The temperature of the air blown into the passenger compartment is adjusted by adjusting. Therefore, the air mix door 24 forms a temperature adjusting means for the air blown into the passenger compartment, and the hot air from the hot water heater core 25 and the cold air from the bypass passage 26 are mixed in the air mixing unit 27, Air at the desired temperature can be created.

  Further, an air outlet mode switching unit is configured on the downstream side of the air mixing unit 27 in the air conditioning case 21. That is, a defroster opening 28 that blows air toward the inner surface of the vehicle windshield, a face opening 29 that blows air toward the upper body side of the passenger in the vehicle interior, and a foot opening 30 that blows air toward the feet of the passenger in the vehicle interior, It opens and closes by the blowing mode doors 31-33.

  The temperature sensor 34 of the evaporator 8 is disposed in a portion of the air conditioning case 21 immediately after the air blowing of the evaporator 8 and detects the evaporator blowing temperature Te. Here, the evaporator blowout temperature Te detected by the evaporator temperature sensor 34 is the same as in an ordinary air conditioner, and is used to control the on / off of the electromagnetic clutch 2 of the compressor 1 or the discharge capacity control when the compressor 1 is a variable displacement type. The cooling capacity of the evaporator 8 is adjusted by the clutch on / off control and the discharge capacity control to control the blowing temperature of the evaporator 8.

  As shown in FIG. 1, in addition to the temperature sensor 34, the air-conditioning control device 5 detects the inside air temperature Tr, the outside air temperature Tam, the solar radiation amount Ts, the hot water temperature Tw and the like for air conditioning control. Detection signals are input from the sensor group 35. In addition, an operation signal of an operation switch group of the air conditioning control panel 36 installed near the vehicle interior instrument panel is also input to the air conditioning control device 5. The air conditioning control panel 36 is provided with various operation switch groups (not shown) such as a temperature setting switch manually operated by a passenger, an air volume switching switch, a blowing mode switch, an inside / outside air switching switch, and an air conditioner switch for generating an on / off signal for the compressor 1. It has been.

  The air-conditioning control device 5 is connected to an engine control device 37, and a rotational speed signal, a vehicle speed signal, and the like of the vehicle engine 4 are input from the engine control device 37 to the air-conditioning control device 5. As is well known, the engine control device 37 comprehensively controls the fuel injection amount, ignition timing, etc. to the vehicle engine 4 based on signals from a sensor group 38 that detects the operating state of the vehicle engine 4 and the like. .

  Further, in the eco-run vehicle that is the object of the present embodiment, when the stop state is determined based on the rotational speed signal, the vehicle speed signal, the brake signal, etc. of the vehicle engine 4, the engine control device 37 The vehicle engine 4 is automatically stopped by stopping fuel injection or the like. Further, after the engine is stopped, when the vehicle shifts from the stop state to the start state by the driver's driving operation, the engine control device 37 determines the start state of the vehicle based on the accelerator signal or the like, and automatically activates the vehicle engine 4. To start.

  In addition, the air-conditioning control device 5 is in a state in which the cooling and cooling mode described later after the vehicle engine 4 is stopped for a long time, and the cooling by the stored heat amount of the cold storage heat exchanger 11 described later cannot be maintained. That is, when the evaporator blowout temperature Te rises to a predetermined target upper limit temperature, an engine restart request signal is output to the engine control device 37.

  The air-conditioning control device 5 and the engine control device 37 are configured by a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and peripheral circuits thereof. The air conditioning control device 5 and the engine control device 37 may be integrated as one control device. And in the vehicle air conditioner of this embodiment, the cool storage heat exchanger 11 which incorporates the cool storage material 11a cooled by the low pressure refrigerant at the time of operation of the compressor 1 is provided upstream of the evaporator 8.

  FIG. 3 is a cross-sectional view showing a specific configuration example of the cold storage heat exchanger 11 according to the embodiment of the present invention. The regenerator heat exchanger 11 in FIG. 3 is a regenerator capsule based on a heat exchanger configuration generally referred to as a shell and tube type, and refrigerant is placed on the top side in the top-down direction of the shell 11d that is a cylindrical tank member. It has a refrigerant inlet 11b that flows in, and a refrigerant outlet 11c from which the refrigerant flows out on the ground side in the vertical direction. In the embodiment of the present invention to be described later, the refrigerant inflow port 11b and the refrigerant outflow port 11c are configured on the side surface side.

  In addition, a tube (refrigerant tube) 11e that is fixed in the shell 11d and forms a refrigerant flow path, and a fin 11f that is thermally integrated with the tube 11e and forms an enlarged heat transfer surface of the tube 11e are provided. is doing. In the shell 11d, the upper end portion and the lower end portion of the cylindrical main body portion 11g are sealed by the upper lid portion 11h and the lower lid portion 11i, and the upper and lower portions thereof are further sealed by the refrigerant distribution side tank portion 11q and the refrigerant assembly side tank portion 11r. It is configured.

  In this example, the tube 11e is a circular tube, and the fin 11f is a plate fin having a circular flat plate shape. A burring hole 11j for inserting a tube is formed in the fin 11f. A large number of plate-like fins 11f are laminated at a predetermined fin pitch Pf, and the tubular tube 11e is expanded after inserting the tubular tube 11e into the harling hole 11j, thereby connecting the fin 11f and the tube 11e to the machine. At the same time, the fins 11f and the tubes 11e are thermally coupled together.

  Then, after fixing the fin 11f and the tube 11e, the tube 11e is placed vertically with respect to the shell 11d, and a combined body of a large number of fins 11f and the tube 11e is accommodated in the shell 11d, and The tube 11e is assembled so that the upper end portion and the lower end portion thereof protrude to the upper side of the upper lid portion 11h and the lower side of the lower lid portion 11i, respectively. In this assembling, the vicinity of the upper end portion and the lower end portion of the tube 11e are sealed and fixed to the upper lid portion 11h and the lower lid portion 11i by joining means such as brazing.

  The tube 11e and the fin 11f are formed of a metal having good thermal conductivity, for example, aluminum. Each part 11g, 11h, 11i, 11q, and 11r of the shell 11d is also formed of a metal such as aluminum. A cool storage material injection port 11k is provided in a part of the shell 11d forming the sealed case structure, for example, in the vicinity of the upper lid portion 11h, and the cool storage material 11a is injected into the shell 11d from the injection port 11k.

  Inside the shell 11d, the regenerator material 11a is filled in a gap between the flat fins 11f (a gap formed by the fin pitch Pf). After the injection of the cold storage material 11a is completed, the injection port 11k is sealed with a plug 11m. Here, since the cold storage material 11a is used for cold storage of a vehicle air conditioner, a material having a melting point of about 4 ° C. to 8 ° C. and having physical properties that do not cause overcooling is preferable. Specifically, paraffin (n-tetradecane) is suitable for satisfying such physical properties.

  By the way, since the paraffin used as the cold storage material 11a has a considerably lower thermal conductivity than that of a metal, it is desirable to increase the heat transfer area by thinning the paraffin layer in order to increase the cold storage capacity and the cooling capacity. . For this purpose, the regenerator heat exchanger 11 has a shell-and-tube type heat exchanger configuration, and the fine gaps between the fins 11f (the gaps formed by the fin pitch Pf) are filled with paraffin in a thin film shape.

  In addition, the cold storage material 11a undergoes a phase change with changes in the cold storage mode / cooling mode, and the density changes and the volume changes accordingly. Stress is generated in the flat fins 11f due to the volume change of the cold storage material 11a, which causes metal fatigue of the cold storage heat exchanger 11. Therefore, through holes 11n penetrating in a vertical direction through a large number of laminated plate-like fins 11f are provided in each fin 11f as shown in FIG.

  Thereby, even if the volume of the regenerator material 11a increases when the regenerator material 11a changes from the solid phase state to the liquid phase state in the cooling mode, the liquid regenerator material 11a between the fins passes through the through holes 11n. Smooth movement to the outside of the fin. FIG. 3 shows an example in which the through hole 11n is provided only at one central portion of the plate fin 11f having a circular flat plate shape. However, in actuality, the liquid phase regenerator material 11a is smoothly moved. Therefore, it is preferable to provide a plurality of through holes 11n at predetermined intervals.

  Further, a gap 11p for heat insulation having a predetermined interval B is provided between the inner peripheral surface of the cylindrical main body 11g of the shell 11d and the outer peripheral end of the flat fin 11f. This gap portion 11p is for ensuring the heat insulation effect of the cold storage heat of the cold storage material 11a even if the cold storage heat exchanger 11 is installed in a high temperature environment outside the vehicle compartment such as an engine room. As described above, a circular tube (round tube) is used as the tube 11e in this example, but a flat tube or a flat porous tube may be used as the tube 11e.

  Next, a configuration according to the present invention will be described. First, a bypass path 12 for bypassing the refrigerant from the suction side of the compressor 1 to immediately after the expansion valve 7 is provided in the cooling / cooling mode to be described later, and the bypass path 12 is expanded in the normal cooling / cold storage mode to be described later. A check valve 13 serving as a check means is provided so that the refrigerant decompressed by the valve 7 does not bypass to the suction side of the compressor 1.

  A drive flow path 14 branched from the high pressure side of the expansion valve 7 is provided. An ejector 9 is provided as a liquid refrigerant circulating means (fluid pump means) instead of the conventional electric pump. FIG. 4 is a sectional view showing an outline of the structure of the ejector 9 according to the embodiment of the present invention. The ejector 9 has a nozzle 9a that converts the pressure energy (pressure head) of the high-pressure refrigerant flowing from the drive flow path 14 into velocity energy (speed head) to decompress and expand the refrigerant.

  And the mixing part which mixes the suction part 9b which attracts | sucks a refrigerant | coolant from the cool storage heat exchanger 11 connected to the low voltage | pressure side with the high-speed refrigerant | coolant flow injected from the nozzle 9a, and the refrigerant | coolant injected from the nozzle 9a Part 9c and a diffuser 9d for increasing the pressure of the refrigerant by converting velocity energy into pressure energy.

  The refrigerant that has flowed out of the ejector 9 flows into the evaporator 8. Note that the refrigerant ejected from the ejector 9 is not necessarily boosted only by the diffuser 9d, and the mixing unit 9c also increases the refrigerant pressure when sucking the vapor-phase refrigerant evaporated on the low pressure side. The part 9c and the diffuser 9d are collectively referred to as a boosting part. In the example of FIG. 4, the cross-sectional area of the mixing unit 9c is constant up to the diffuser 9d, but the cross-sectional area of the mixing unit 9c may be tapered so as to increase toward the diffuser 9d.

  In the present embodiment, in the normal cooling / cold storage mode in which the ejector 9 is not used, the refrigerant path from the cold storage heat exchanger 11 to the evaporator 8 is supplied with the refrigerant path to the suction unit 9b and the refrigerant path from the diffuser 9d. A communication path 17 for communication is provided in parallel with the ejector 9. The communication passage 17 is provided with a check valve 18 that forms a check means so that the refrigerant pressurized by the diffuser 9d does not flow to the suction portion 9b through the communication passage 17 in the cooling / cooling mode using the ejector 9. .

  Next, the main structure of the present invention will be described. FIG. 6 is a schematic diagram of a refrigeration cycle in the first embodiment of the present invention, and FIG. 7 shows a structural outline of a cold storage unit (cold storage heat exchanger provided with an ejector) 15 in the first embodiment of the present invention. It is sectional drawing. The cold storage unit 15 of the present embodiment is configured integrally with a portion indicated by a one-dot chain line in the refrigeration cycle of FIG. First, the refrigerant inflow portion 11b of the regenerator heat exchanger 11 is arranged on the top side in the vertical direction, the refrigerant outflow portion 11c is on the ground side, the refrigerant outflow direction of the ejector 9 is on the top side, and the suction portion 9b is the refrigerant outflow portion. 11c is connected and integrated.

  And the refrigerant | coolant flow path which connects between the expansion valve 7, the evaporator 8, the ejector 9, and the cool storage heat exchanger 11 is comprised integrally. The check valves 13 and 18 are integrally formed in the refrigerant flow path. In addition, this cool storage unit 15 may be integrally processed by cutting from a block-shaped member, or may be assembled by brazing or welding the tubular members to each other.

  And as a connection part with the expansion valve 7, the high pressure refrigerant | coolant for ejector drive from the drive flow path 14 branched from the refrigerant | coolant inlet 15a into which the refrigerant decompressed with the expansion valve 7 flows in, and the high pressure side of the expansion valve 7 The refrigerant inlet 15b into which the refrigerant flows and the refrigerant outlet 15c after evaporation from which the refrigerant sucked into the compressor 1 evaporated by the evaporator 8 flows out are arranged on the lower side of the ejector 9.

  The expansion valve 7 connected to correspond to these connection portions 15a to 15c is provided by branching the drive flow path 14 from a portion upstream of the valve portion 73 in the high-pressure refrigerant passage 74 inside the structure B (see FIG. 6), a refrigerant outlet through the valve portion 73, a refrigerant outlet of the driving flow path 14, and a low-pressure refrigerant passage 75 are provided on the same surface of the structure B.

  FIG. 5 is a cross-sectional view showing a structural example of the expansion valve 7 according to the embodiment of the present invention. The expansion valve 7 of this structural example is of a so-called box type. The expansion valve 7 includes a valve block (structure according to the present invention) B, an element portion E, a heat transfer portion 71, a transmission rod 72, a ball valve (valve means according to the present invention) 73, and the like. The valve block B is made of, for example, aluminum and has a substantially rectangular parallelepiped shape, and includes a high-pressure refrigerant passage 74 and a low-pressure refrigerant passage 75.

  The high-pressure refrigerant passage 74 has an inflow port 74a connected to the outlet side of the condenser 6, normally an outflow port 74b connected to the inlet side of the evaporator 8, and a communication hole that connects the inflow port 74a side and the outflow port 74b side. 74c, and a conical sheet surface 74d is provided on the inlet side (inflow port 74a side) of the communication hole 74c. The low-pressure refrigerant passage 75 normally connects the inflow port 75a connected to the outlet side of the evaporator 8, the outflow port 75b connected to the suction side of the compressor 1, and the inflow port 75a and the outflow port 75b. A communication path 75 c communicating with 71 is also provided.

  The element portion E includes a diaphragm 76 made of a flexible thin metal plate, a receiving portion 77 for sandwiching the diaphragm 76, and a lid portion 78, and is screwed to the upper portion of the valve block B via a packing 79. Is done. The receiving portion 77 and the lid portion 78 are joined by, for example, TIG welding, and the diaphragm 76 and the lid portion 78 form a diaphragm chamber 80.

  The diaphragm chamber 80 is filled with the same kind of saturated gas as the refrigerant gas used in the refrigeration cycle. The lid portion 78 is provided with a hole for allowing saturated gas to enter the diaphragm chamber 80. After the saturated gas is introduced, the lid portion 78 is airtightly closed by a plug 81. In addition, each component (diaphragm 76, receiving portion 77, lid portion 78, and plug 81) constituting the element portion E is formed using the same metal material such as stainless steel, for example.

  The heat transfer part 71 is formed in a cylindrical shape using a metal material having high thermal conductivity such as aluminum or brass. The cylindrical upper surface is in close contact with the lower surface of the diaphragm 76 by receiving an urging force (described later) from below, and the temperature change of the refrigerant flowing in the low-pressure refrigerant passage 75 (the vapor-phase refrigerant evaporated by the evaporator 8) is detected by the diaphragm 76. The transmission rod 72 is in contact with the cylindrical lower surface, and the displacement of the diaphragm 76 is transmitted to the ball valve 73 in cooperation with the transmission rod 72.

  The transmission rod 72 is disposed below the heat transfer section 71 and is slidably held by the valve block B. The upper end abuts on the lower surface of the heat transfer section 71, penetrates the low-pressure refrigerant passage 75 (communication passage 75c) in the vertical direction, is inserted into the communication hole 74c of the high-pressure refrigerant passage 74, and the lower end is conical. It abuts against the upper surface of the ball valve 73 that presses against the seat surface 74d. Further, with respect to the transmission rod 72 that is slidably inserted in the vertical direction, a seal portion by an O-ring 82 is provided in the valve block B portion between the high-pressure refrigerant passage 74 and the low-pressure refrigerant passage 75. Yes.

  As shown in FIG. 5, the ball valve 73 is disposed on the inlet side of the communication hole 74c, is held between the transmission rod 72 and the valve receiving member 77, and is seated on the seat surface 74d so that the communication hole 74c is formed. The communication hole 74c can be opened by closing and releasing (lifting) from the seat surface 74d. The ball valve 73 is shown in FIG. 5 via a force that pushes the diaphragm 76 downward (pressure in the diaphragm chamber 80 -pressure of refrigerant vapor acting on the lower side of the diaphragm 76) and a valve receiving member 83. 5 is stationary at a position where the load of the spring 84 biased upward is balanced.

  The spring 84 is disposed between an adjusting screw 85 attached to the lower end of the valve block B and the valve receiving member 84, and the ball valve 73 is moved upward (in FIG. To the direction). The adjusting screw 85 adjusts the valve opening pressure of the ball valve 73 (the load of the spring 84 that urges the ball valve 73), and is screwed to the lower end of the valve block B via an O-ring 86.

  Next, the operation of the expansion valve 7 will be described. The flow rate of the refrigerant passing through the communication hole 74c is determined by the opening degree of the ball valve 73, that is, the position (lift amount) of the ball valve 73 with respect to the seat surface 74d. The ball valve 73 includes a pressure in a diaphragm chamber 80 that urges the diaphragm 76 downward in FIG. 4, a load of a spring 84 that urges the diaphragm 76 upward in FIG. 5, and a low pressure in the cycle (under the diaphragm 76 The refrigerant vapor pressure acting on the side) moves to a balanced position.

  Therefore, when the temperature in the passenger compartment rises from the state where the evaporation pressure is stable and the refrigerant rapidly evaporates in the evaporator 8, the temperature (superheat degree) of the refrigerant vapor at the outlet of the evaporator 8 increases. As a result, the temperature change of the refrigerant vapor flowing through the low-pressure refrigerant passage 75 is transmitted to the gas sealed in the diaphragm chamber 80 via the heat transfer section 71 and the diaphragm 76, and the diaphragm chamber 80 increases with the temperature rise of the gas. Pressure increases.

  As a result, the diaphragm 76 is pushed downward in FIG. 5, and the ball valve 73 moves downward in FIG. 5 through the heat transfer portion 71 and the transmission rod 72, thereby increasing the valve opening and supplying it to the evaporator 8. The refrigerant flow rate to be increased. On the other hand, when the temperature in the passenger compartment decreases and the degree of superheat at the outlet of the evaporator 8 decreases, the temperature change of the refrigerant vapor flowing through the low-pressure refrigerant passage 75 is transmitted to the gas in the diaphragm chamber 80, and as the temperature of the gas decreases. As a result, the pressure in the diaphragm chamber 80 decreases.

  As a result, the diaphragm 76 is pushed upward in FIG. 5 and the ball valve 73 moves upward in FIG. 5, thereby reducing the valve opening and reducing the flow rate of the refrigerant supplied to the evaporator 8. With the above operation, during normal cycle operation, the valve opening is adjusted so that the temperature (superheat degree) of the refrigerant vapor evaporated by the evaporator 8 becomes, for example, approximately 5 ° C., and the flow rate of refrigerant flowing through the communication hole 74c is controlled. is doing.

  The expansion valve 7 of the present embodiment is provided by branching the drive flow path 14 to the ejector 9 from a portion upstream of the ball valve 73 in the high-pressure refrigerant passage 74 of the expansion valve 7 of the above structural example. The downstream side of the ball valve 73 is connected to the refrigerant inlet 15a after depressurization of the regenerator unit 15, the downstream side of the driving flow path 14 is connected to the driving flow refrigerant inlet 15b, and the low pressure refrigerant passage 75 is connected to the refrigerant outlet 15c after evaporation. (See FIG. 7).

  Further, as a connection portion with the evaporator 8, a pre-evaporation refrigerant outlet 15 d from which the refrigerant to be supplied to the evaporator 8 flows out and a post-evaporation refrigerant inlet 15 e into which the refrigerant evaporated by the evaporator 8 flows are connected to the top of the cold storage unit 15. Aligned to the side part of the side.

  Next, the operation of the first embodiment in the above configuration will be described. 6 and 7 show how the refrigerant flows in the normal cooling / cold storage mode. In the normal cooling / cold storage mode, the refrigeration cycle is operated by driving the compressor 1 by the vehicle engine 4. The high-pressure gas-phase refrigerant discharged from the compressor 1 is cooled by the condenser 6 and becomes a supercooled liquid refrigerant and flows into the expansion valve 7.

  The high-pressure liquid refrigerant is branched inside the expansion valve 7, and one of the high-pressure liquid refrigerant is decompressed by the valve portion 73 to be in a low-temperature and low-pressure gas-liquid two-phase state and flows into the cold storage unit 15 from the refrigerant inlet 15 a after decompression. And first, it flows in into the cool storage heat exchanger 11 from the upper refrigerant | coolant inflow part 11b. At this time, the check valve 13 closes the flow path to the compressor 1 suction side because the pressure on the expansion valve 7 side is higher. And the refrigerant | coolant which flowed in in the cool storage heat exchanger 11 flows in many tubes 11e, flows downward while cool-storage in the cool storage material 11a, and flows out from the downward refrigerant | coolant outflow part 11c.

  The refrigerant that has passed through the cold storage heat exchanger 11 passes through the check valve 18 and flows out from the pre-evaporation refrigerant outlet 15d to the evaporator 8. Then, the evaporator 8 absorbs heat from the blown air in the air conditioning case 21 and evaporates to become a gas phase refrigerant, and flows into the cold storage unit 15 from the refrigerant inlet 15e after evaporation. Then, after evaporating, the refrigerant flows out from the refrigerant outlet 15c, passes through the low-pressure refrigerant passage 75 of the expansion valve 7, is sucked into the compressor 1, and is compressed again. The cool air absorbed by the evaporator 8 is blown out from the face opening 29 or the like into the vehicle interior to cool the vehicle interior.

  The high-pressure liquid refrigerant branched inside the other expansion valve 7 and flowing into the drive flow path 14 flows into the cold storage unit 15 from the drive flow refrigerant inlet 15b, and a part of the refrigerant that has passed through the cold storage heat exchanger 11 is removed. The refrigerant flows through the ejector 9 while being taken in from the suction portion 9b, merges with the refrigerant that has passed through the check valve 18 on the upstream side of the pre-evaporation refrigerant outlet 15d, and flows out to the evaporator 8.

  Although it is not necessary to drive the ejector 9 in the cold storage mode, the actual nozzle 9a is formed with a thin diameter of about 0.6 mm, and the refrigerant flow bypassed through the ejector 9 due to the large resistance at the ejector 9 is The effect on cooling is usually small enough to be acceptable.

  Next, a case where the vehicle engine 4 is automatically stopped when the vehicle stops, such as waiting for a signal, will be described. FIG. 8 shows how the refrigerant flows in the cooling cooling mode in the refrigeration cycle of FIG. 6, and FIG. 9 shows how the refrigerant flows in the cooling cooling mode in the cool storage unit 15 of FIG. Even when the vehicle is stopped, the compressor 1 of the refrigeration cycle is forcibly stopped along with the stop of the vehicle engine 4 even in the air conditioning operation state (operation state of the blower 22).

  The high-pressure refrigerant accumulated in the condenser 6 flows into the expansion valve 7 and is branched inside, and one of the refrigerant passes through the drive flow path 14 from the drive flow refrigerant inlet 15b to the high pressure inlet of the ejector 9 in the cold storage unit 15. Inflow. As a result, the ejector 9 converts the pressure energy of the high-pressure refrigerant into velocity energy by the nozzle 9a, decompresses and expands the refrigerant, and is connected to the suction portion 9b on the low-pressure side by the high-speed refrigerant flow injected from the nozzle 9a. The cooled refrigerant is sucked from the regenerator heat exchanger 11, and the sucked refrigerant and the refrigerant jetted from the nozzle 9a are mixed by the boosting units 9c and 9d, and the speed energy is converted into pressure energy to change the refrigerant energy. The pressure is increased and the refrigerant flows out from the pre-evaporation refrigerant outlet 15d to the evaporator 8.

  Due to the pressure increasing action of the ejector 9, the refrigerant pressure acts on the check valve 18 of the communication passage 17 in the reverse direction, and the check valve 18 is closed. Then, the evaporator 8 absorbs heat from the blown air in the air conditioning case 21 and evaporates to become a gas phase refrigerant, and flows into the cold storage unit 15 from the refrigerant inlet 15e after evaporation. The pressure of the refrigerant after evaporation acts on the check valve 13 of the bypass path 12 in the forward direction because the compressor 1 is stopped and is not sucked, and the check valve 13 is opened.

  Therefore, as indicated by an arrow in FIG. 9, the refrigerant that has passed through the check valve 13 flows into the regenerator heat exchanger 11 from the upper refrigerant inflow portion 11b, flows through the numerous tubes 11e, and stores the regenerator material 11a. The refrigerant flows downward while being cooled by the refrigerant and flows out from the lower refrigerant outlet 11c. Then, the refrigerant circulates in the refrigerant circulation circuit including the cold storage heat exchanger 11 → the ejector 9 → the evaporator 8 → the check valve 13 → the cold storage heat exchanger 11.

  Therefore, in the evaporator 8, the refrigerant cooled by the cold storage heat exchanger 11 absorbs heat from the air blown from the blower 22 and evaporates. Therefore, the cooling action of the evaporator 8 can be continued even after the compressor is stopped, and the cooling operation in the vehicle compartment is continued. it can. Since the temperature of the vapor-phase refrigerant evaporated by the evaporator 8 is higher than the freezing point of the regenerator material 11a of the regenerator heat exchanger 11, the regenerator material 11a absorbs the latent heat of fusion from the vapor-phase refrigerant and changes its phase (melt) from the solid phase to the liquid phase. )

  Thereby, a gaseous-phase refrigerant | coolant is cooled and condensed by the cool storage material 11a. And while the high pressure refrigerant | coolant in the capacitor | condenser 6 remains, the vehicle interior cooling action at the time of a stop (at the time of a compressor stop) can be continued. In addition, since the stop time by waiting for a signal is usually a short time of about 1 to 2 minutes, by using about 420 g of paraffin having a freezing point = 6 ° C. and a latent heat of solidification = 229 kJ / kg as the regenerator material 11a, It has been confirmed that the cabin cooling function can be continued while the vehicle is stopped for about 2 minutes.

  Next, features and effects of this embodiment will be described. First, the refrigerant inflow portion 11b of the regenerator heat exchanger 11 is arranged on the top side in the vertical direction, the refrigerant outflow portion 11c is on the ground side, the refrigerant outflow direction of the ejector 9 is on the top side, and the suction portion 9b is the refrigerant outflow portion. 11c is connected and integrated.

  According to this, the gas refrigerant evaporated by the evaporator 8 in the cooling mode is converted into a condensate in the cooled regenerator heat exchanger 11 and gathers in the lower part of the regenerator heat exchanger 11 by gravity. By connecting the refrigerant outflow part 11c arranged in the lower part and the suction part 9b of the ejector 9 at the shortest distance, the ejector 9 can efficiently suck the condensate refrigerant and circulate the refrigerant again in the evaporator 8. it can. Moreover, by arrange | positioning the ejector 9 and the cool storage heat exchanger 11 in the top-and-bottom direction as substantially parallel, the cool storage unit 15 can be comprised in a small size, and vehicle mounting property can be improved.

  Further, the refrigerant flow path connecting the expansion valve 7, the evaporator 8, the ejector 9, and the cold storage heat exchanger 11 is integrally formed, and check valves 13 and 18 are formed in the refrigerant flow path. According to this, the regenerator heat provided with the ejector 9 is formed by integrating the refrigerant flow paths between the devices as described above and integrating the check valves 13 and 18 in the refrigerant flow path. It can be configured not only as the exchanger 11 but also as a complete cold storage unit 15.

  And since it can be put together into a layout in which the cold storage unit 15 + the expansion valve 7 is sandwiched between the evaporator 8 and the compressor 1 and the condenser 6 which are normally arranged in the engine compartment, This not only saves space on the vehicle but also makes it very convenient to add additional functions to the existing refrigeration cycle that is not equipped with a cold storage unit.

  Further, the refrigerant flow path connecting the expansion valve 7, the evaporator 8, the ejector 9, and the cold storage heat exchanger 11 is integrally formed, and the connection portions 15 a to 15 c with the expansion valve 7 are aligned on the lower side of the ejector 9. Arranged. According to this, since the drive inlet to the normal ejector 9 and the suction portion 9b are close to each other, the expansion valve 7 is disposed at a position close to the suction portion 9b, that is, below the ejector 9 and the cold storage heat exchanger 11. It is reasonable from the top of space efficiency. Moreover, it can be set as the structure which can connect the some connection parts 15a-15c at once by combining with the box-type expansion valve 7 by arrange | positioning the some connection parts 15a-15c in alignment.

  In addition, the refrigerant flow path connecting the expansion valve 7, the evaporator 8, the ejector 9, and the regenerator heat exchanger 11 is integrally formed, and the connection portions 15d and 15e with the evaporator 8 are aligned on the side portion on the top side. Arranged. According to this, by arranging the connecting portions 15d and 15e to the evaporator 8 in a uniform arrangement, it is possible to make a structure that allows a plurality of connecting portions 15d and 15e to be connected at a time in combination with the block joint.

  Further, the driving flow path 14 is branched from the upstream portion of the valve portion 73 and the refrigerant outlet via the valve portion 73, the refrigerant outlet of the driving flow path 14, and the low-pressure refrigerant passage 75 are connected to the structure B. It is provided on the same surface.

  According to this, the high-pressure refrigerant can be guided to the drive inlet of the ejector 9 at the shortest distance, and the drive flow path 14 can be configured to be extremely short. Moreover, the structure which can concentrate and comprise the connection part corresponding to connection part 15a-15c with the ejector 9 and the cool storage heat exchanger 11 on the same surface of the structure B, and can connect several connection part 15a-15c at once. can do.

  Moreover, said cold storage unit 15 and the expansion valve 7 are used for the vehicle air conditioner. According to this, since it is comprised as the small-sized cool storage unit 15 which united the connection parts 15a-15c with the expansion valve 7, and the connection parts 15d * 15e with the evaporator 8, respectively, the evaporator arrange | positioned in a normal vehicle interior 8 and the compressor 1 and the condenser 6 arranged in the engine room can be combined into a layout in which the cold storage unit 15 and the expansion valve 7 are simply sandwiched, and the vehicle air conditioner having good vehicle mounting properties can be obtained. be able to.

  Further, even in a vehicle air conditioner that is not currently equipped with a cold storage unit, it is possible to provide a vehicle air conditioner in which only the cold storage unit 15 + expansion valve 7 portion can be additionally mounted as a function addition.

(Second Embodiment)
FIG. 10 is a schematic diagram of a refrigeration cycle in the second embodiment of the present invention, and FIG. 11 shows a schematic structure of a cold storage unit (cold storage heat exchanger provided with an ejector) 15 in the second embodiment of the present invention. It is sectional drawing. The difference from the first embodiment described above is that the bypass path 12 from the suction side of the compressor 1 is connected immediately after the regenerator heat exchanger 11, and the regenerator heat exchanger is used in the normal cooling / cold storage mode and the cool-down cooling mode. The refrigerant flow direction in 11 is reversed.

  The cold storage unit 15 of the present embodiment is configured integrally with a portion indicated by a one-dot chain line in the refrigeration cycle of FIG. First, the refrigerant inflow / outflow portions 11b and 11c of the cold storage heat exchanger are arranged on the top side and the ground side in the vertical direction, the refrigerant outflow direction of the ejector 9 is set to the top side, and the suction portion 9b is connected to the refrigerant outflow portion 11c. And united.

  And the refrigerant | coolant flow path which connects between the expansion valve 7, the evaporator 8, the ejector 9, and the cool storage heat exchanger 11 is comprised integrally. The check valves 13 and 18 are integrally formed in the refrigerant flow path. The cold storage unit 15 may also be a unit integrally processed by cutting from a block-shaped member, or may be an assembly of tubular members that are brazed or welded together.

  And as a connection part with the expansion valve 7, the high pressure refrigerant | coolant for ejector drive from the drive flow path 14 branched from the refrigerant | coolant inlet 15a into which the refrigerant decompressed with the expansion valve 7 flows in, and the high pressure side of the expansion valve 7 The refrigerant inlet 15b into which the refrigerant flows and the refrigerant outlet 15c after evaporation from which the refrigerant sucked into the compressor 1 after being evaporated by the evaporator 8 flows out are arranged on the lower side of the ejector 9.

  The expansion valve 7 connected to correspond to these connection portions 15a to 15c is provided by branching the drive flow path 14 from a portion upstream of the valve portion 73 in the high-pressure refrigerant passage 74 inside the structure B (see FIG. The refrigerant outlet via the valve part 73, the refrigerant outlet of the drive flow path 14, and the low-pressure refrigerant passage 75 are provided on the same surface of the structure B.

  The expansion valve 7 of this embodiment branches the drive flow path 14 from the site | part upstream from the valve part 73 in the high pressure refrigerant path 74 of the expansion valve 7 to the ejector 9 similarly to the above-mentioned 1st Embodiment. The downstream side of the valve unit 73 is connected to the refrigerant inlet 15a after decompression, the downstream side of the driving flow path 14 is connected to the driving flow refrigerant inlet 15b, and the low-pressure refrigerant passage 75 is connected to the refrigerant outlet 15c after evaporation. They are connected (see FIG. 11).

  Further, as a connection portion with the evaporator 8, a pre-evaporation refrigerant outlet 15d from which the refrigerant to be supplied to the evaporator 8 flows out and a post-evaporation refrigerant inlet 15e into which the refrigerant evaporated by the evaporator 8 flows are connected to the top of the regenerator unit 15. Aligned to the side part of the side.

  Next, the operation of the second embodiment in the above configuration will be described. 10 and 11 show how the refrigerant flows in the normal cooling / cold storage mode. In the normal cooling / cold storage mode, the refrigeration cycle is operated by driving the compressor 1 by the vehicle engine 4. The high-pressure gas-phase refrigerant discharged from the compressor 1 is cooled by the condenser 6 and becomes a supercooled liquid refrigerant and flows into the expansion valve 7.

  The high-pressure liquid refrigerant is branched inside the expansion valve 7, and one of the high-pressure liquid refrigerant is decompressed by the valve portion 73 to be in a low-temperature and low-pressure gas-liquid two-phase state and flows into the cold storage unit 15 from the refrigerant inlet 15 a after decompression. First, the refrigerant flows into the cold storage heat exchanger 11 from the lower refrigerant inflow / outflow portion 11c. And the refrigerant | coolant which flowed in in the cool storage heat exchanger 11 flows through many tubes 11e, flows upwards, cools in the cool storage material 11a, and flows out from the upper refrigerant | coolant inflow / outflow part 11b. At this time, the check valve 13 closes the flow path to the compressor 1 suction side because the pressure on the expansion valve 7 side is higher.

  The refrigerant that has passed through the cold storage heat exchanger 11 passes through the check valve 18 and flows out from the pre-evaporation refrigerant outlet 15d to the evaporator 8. Then, the evaporator 8 absorbs heat from the blown air in the air conditioning case 21 and evaporates to become a gas phase refrigerant, and flows into the cold storage unit 15 from the refrigerant inlet 15e after evaporation. Then, after evaporating, the refrigerant flows out from the refrigerant outlet 15c, passes through the low-pressure refrigerant passage 75 of the expansion valve 7, is sucked into the compressor 1, and is compressed again. The cool air absorbed by the evaporator 8 is blown out from the face opening 29 or the like into the vehicle interior to cool the vehicle interior.

  The high-pressure liquid refrigerant branched into the other expansion valve 7 and flowing into the drive flow path 14 flows into the cold storage unit 15 from the drive flow refrigerant inlet 15b, and a part of the refrigerant flowing into the cold storage heat exchanger 11 is removed. The refrigerant flows through the ejector 9 while being taken in from the suction portion 9b, merges with the refrigerant that has passed through the check valve 18 on the upstream side of the pre-evaporation refrigerant outlet 15d, and flows out to the evaporator 8.

  Although it is not necessary to drive the ejector 9 in the cold storage mode, the actual nozzle 9a is formed with a thin diameter of about 0.6 mm, and the refrigerant flow bypassed through the ejector 9 due to the large resistance at the ejector 9 is The effect on cooling is usually small enough to be acceptable.

  Next, a case where the vehicle engine 4 is automatically stopped when the vehicle stops, such as waiting for a signal, will be described. FIG. 12 shows how the refrigerant flows in the cooling cooling mode in the refrigeration cycle of FIG. 10, and FIG. 13 shows how the refrigerant flows in the cooling cooling mode in the cool storage unit 15 of FIG. Even when the vehicle is stopped, the compressor 1 of the refrigeration cycle is forcibly stopped along with the stop of the vehicle engine 4 even in the air conditioning operation state (operation state of the blower 22).

  The high-pressure refrigerant accumulated in the condenser 6 flows into the expansion valve 7 and is branched inside, and one of the refrigerant passes through the drive flow path 14 from the drive flow refrigerant inlet 15b to the high-pressure inlet side of the ejector 9 in the cold storage unit 15. Inflow. As a result, the ejector 9 converts the pressure energy of the high-pressure refrigerant into velocity energy by the nozzle 9a, decompresses and expands the refrigerant, and is connected to the suction portion 9b on the low-pressure side by the high-speed refrigerant flow injected from the nozzle 9a. The cooled refrigerant is sucked from the regenerator heat exchanger 11, and the sucked refrigerant and the refrigerant jetted from the nozzle 9a are mixed by the boosting units 9c and 9d, and the speed energy is converted into pressure energy to change the refrigerant energy. The pressure is increased and the refrigerant flows out from the pre-evaporation refrigerant outlet 15d to the evaporator 8.

  Due to the pressure increasing action of the ejector 9, the refrigerant pressure acts on the check valve 18 of the communication passage 17 in the reverse direction, and the check valve 18 is closed. The evaporator 8 absorbs heat from the blown air in the air conditioning case 21 and evaporates to become a gas phase refrigerant, and flows into the cold storage unit 15 from the refrigerant inlet 15e after evaporation. The pressure of the refrigerant after evaporation acts on the check valve 13 in the bypass path 12 in the forward direction because the compressor 1 is stopped and is not sucked, so that the check valve 13 is opened.

  Therefore, as indicated by an arrow in FIG. 13, the refrigerant that has passed through the check valve 13 flows into the regenerator heat exchanger 11 from the upper refrigerant inflow / outflow part 11 b, flows through the numerous tubes 11 e, and stores the regenerator material 11 a. The refrigerant flows downward while being cooled by the refrigerant, and flows out from the lower refrigerant inflow / outflow portion 11c. Then, the refrigerant circulates in the refrigerant circulation circuit including the cold storage heat exchanger 11 → the ejector 9 → the evaporator 8 → the check valve 13 → the cold storage heat exchanger 11.

  Therefore, in the evaporator 8, the refrigerant cooled by the cold storage heat exchanger 11 absorbs heat from the air blown from the blower 22 and evaporates. Therefore, the cooling action of the evaporator 8 can be continued even after the compressor is stopped, and the cooling operation in the vehicle compartment is continued. it can. Since the temperature of the vapor phase refrigerant evaporated by the evaporator 8 is higher than the freezing point of the regenerator material 11a of the regenerator heat exchanger 11, the regenerator material 11a absorbs the latent heat of fusion from the vapor refrigerant and changes its phase (melting) from the solid phase to the liquid phase. ) Thereby, a gaseous-phase refrigerant | coolant is cooled and condensed by the cool storage material 11a. And while the high pressure refrigerant | coolant in the capacitor | condenser 6 remains, the vehicle interior cooling action at the time of a stop (at the time of a compressor stop) can be continued.

  Next, features of the present embodiment will be described. Since the first embodiment and the second embodiment are partially different from each other in the refrigeration cycle, the same effects as those of the first embodiment can be obtained. In the second embodiment, the refrigerant flow direction in the cold storage heat exchanger 11 is reversed between the normal cooling / cold storage mode and the cool-down cooling mode.

  By doing in this way, the refrigerant | coolant piping part pressure-reduced with the expansion valve 7 can be connected with the suction part 9b of the ejector 9, and the lower part of the cool storage heat exchanger 11, and the ejector 9 is the structure shown in 1st Embodiment. As a result, the ascending refrigerant flow path disposed on the side of the ejector 9 becomes unnecessary, and the refrigerant flow path having the check valve 18 disposed on the side of the ejector 9 is also unnecessary, so that the check valve 18 moves upward. Can be made. From these things, in this 2nd Embodiment, since the ejector 9 arrange | positioned to the side of the cool storage heat exchanger 11 and a refrigerant | coolant flow path part can be comprised more compactly and simply, it is suitable for integration.

(Other embodiments)
In the first embodiment described above, the on-off valve 15 of the drive flow path 14 is omitted as compared with that shown in Japanese Patent Application No. 2005-4450. As described above, since the influence by bypassing the ejector 9 is small, an expensive on-off valve is omitted. However, in terms of operation, opening and closing the drive flow with the on / off valve can provide stable performance regardless of the ejector design. Therefore, an open / close valve is provided in the drive flow path 14 and is opened and closed by the air conditioning controller 5. The structure to control may be sufficient.

It is a mimetic diagram showing the whole vehicle air-conditioner composition in a 1st embodiment of the present invention. It is a cross-sectional schematic diagram which shows schematic structure of the air-conditioning indoor unit part 20 in FIG. It is sectional drawing which shows the specific structural example of the cool storage heat exchanger 11 which concerns on embodiment of this invention. It is sectional drawing which shows the structure outline | summary of the ejector 9 which concerns on embodiment of this invention. It is sectional drawing which shows the structural example of the expansion valve 7 which concerns on embodiment of this invention. It is a schematic diagram of the refrigerating cycle in 1st Embodiment of this invention, and shows how to flow the refrigerant | coolant at the time of normal cooling and a cool storage mode. It is sectional drawing which shows the structure outline | summary of the cool storage unit 15 in 1st Embodiment of this invention, and shows how to flow the refrigerant | coolant at the time of normal cooling and cold storage mode. FIG. 7 shows how the refrigerant flows in the cooling cooling mode in the refrigeration cycle of FIG. 6. In the cool storage unit 15 of FIG. 7, how the refrigerant flows in the cool-down cooling mode is shown. It is a schematic diagram of the refrigerating cycle in 2nd Embodiment of this invention, and shows how to flow the refrigerant | coolant at the time of normal cooling and cold storage mode. It is sectional drawing which shows the structure outline | summary of the cold storage unit 15 in 2nd Embodiment of this invention, and shows how to flow the refrigerant | coolant at the time of normal cooling and cold storage mode. FIG. 11 shows how the refrigerant flows in the cooling cooling mode in the refrigeration cycle of FIG. 10. In the cool storage unit 15 of FIG. 11, how the refrigerant flows in the cool-down cooling mode is shown.

Explanation of symbols

1 ... Compressor (refrigerant compressor)
4 ... Vehicle engine 6 ... Condenser (refrigerant radiator)
7 ... Expansion valve 8 ... Evaporator
DESCRIPTION OF SYMBOLS 9 ... Ejector 9a ... Nozzle 9b ... Suction part 9c * 9d ... Boosting part 11 ... Cold storage heat exchanger 11a ... Cold storage material 11b ... Refrigerant inflow part 11c ... Refrigerant outflow part, refrigerant outflow / inflow part 12 ... Bypass path 13 ... Check valve ( Non-return means)
14 ... Driving flow path 15 ... Cold storage unit (cool storage heat exchanger with ejector)
15a: Refrigerant inlet after decompression (connection portion with expansion valve)
15b ... Driving flow refrigerant inlet (connection portion with expansion valve)
15c ... Refrigerant outlet after evaporation (connection with expansion valve)
15d: Pre-evaporation refrigerant outlet (connection portion with refrigerant evaporator)
15e ... Post-evaporation refrigerant inlet (connecting part with refrigerant evaporator)
17 ... Communication passage 18 ... Check valve (check means)
73 ... Ball valve (valve means)
74 ... High-pressure refrigerant passage B ... Valve block (structure)

Claims (7)

A refrigerant compressor (1) for compressing the refrigerant;
A refrigerant radiator (6) for radiating high-pressure refrigerant discharged from the refrigerant compressor (1);
An expansion valve (7) for depressurizing the refrigerant that has passed through the refrigerant radiator (6);
A refrigerant evaporator (8) for evaporating the low-pressure refrigerant decompressed by the expansion valve (7) and cooling the air blown into the vehicle interior;
A cold storage heat exchanger (11) having a cold storage material (11a) that is provided upstream of the refrigerant evaporator (8) and is cooled by the low-pressure refrigerant when the refrigerant compressor (1) is in operation;
A bypass path (12) having a check means (13) for bypassing the refrigerant from the suction side of the refrigerant compressor (1) to immediately after the expansion valve (7);
A drive flow path (14) branched from the high pressure side of the expansion valve (7);
The pressure energy of the high-pressure refrigerant flowing from the drive flow path (14) is converted to velocity energy, and the nozzle (9a) that decompresses and expands the refrigerant, and the high-velocity refrigerant flow that is injected from the nozzle (9a) The refrigerant is sucked from the connected cold storage heat exchanger (11), and the sucked refrigerant and the refrigerant injected from the nozzle (9a) are mixed to convert velocity energy into pressure energy to increase the pressure of the refrigerant. An ejector (9) having a boosting section (9c, 9d) for flowing into the refrigerant evaporator (8).
A bypass (17) for bypassing the ejector (9) to supply refrigerant from the cold storage heat exchanger (11) to the refrigerant evaporator (8) and having a check means (18);
In the regenerative heat exchanger (11) used for the vehicle air conditioner that drives the ejector (9) when the refrigerant compressor (1) stops,
While arrange | positioning the refrigerant | coolant inflow part (11b) of the said cold storage heat exchanger (11) as the ceiling side of a top-and-bottom direction, and a refrigerant | coolant outflow part (11c) as a ground side,
A regenerative heat exchanger having an ejector characterized in that the refrigerant outflow direction of the ejector (9) is the top side, and the suction part (9b) is connected to the refrigerant outflow part (11c) to be integrated. A refrigerant compressor (1) for compressing the refrigerant;
A refrigerant radiator (6) for radiating high-pressure refrigerant discharged from the refrigerant compressor (1);
An expansion valve (7) for depressurizing the refrigerant that has passed through the refrigerant radiator (6);
A refrigerant evaporator (8) for evaporating the low-pressure refrigerant decompressed by the expansion valve (7) and cooling the air blown into the vehicle interior;
A cold storage heat exchanger (11) having a cold storage material (11a) that is provided upstream of the refrigerant evaporator (8) and is cooled by the low-pressure refrigerant when the refrigerant compressor (1) is in operation;
A bypass path (12) having a check means (13) for bypassing the refrigerant from the suction side of the refrigerant compressor (1) to immediately after the cold storage heat exchanger (11);
A drive flow path (14) branched from the high pressure side of the expansion valve (7);
The pressure energy of the high-pressure refrigerant flowing from the drive flow path (14) is converted to velocity energy, and the nozzle (9a) that decompresses and expands the refrigerant, and the high-velocity refrigerant flow that is injected from the nozzle (9a) The refrigerant is sucked from the connected cold storage heat exchanger (11), and the sucked refrigerant and the refrigerant injected from the nozzle (9a) are mixed to convert velocity energy into pressure energy to increase the pressure of the refrigerant. An ejector (9) having a boosting section (9c, 9d) for flowing into the refrigerant evaporator (8).
In parallel with the ejector (9), a refrigerant is supplied from the cold storage heat exchanger (11) to the refrigerant evaporator (8), and a communication passage (17) having a check means (18) is provided.
In the regenerative heat exchanger (11) used for the vehicle air conditioner that drives the ejector (9) when the refrigerant compressor (1) stops,
While arranging the refrigerant inflow / outflow portions (11b, 11c) of the cold storage heat exchanger (11) on the top side and the ground side in the top and bottom direction,
Cold storage with an ejector characterized in that the refrigerant outflow direction of the ejector (9) is the top side, and its suction part (9b) is connected to the ground side refrigerant outflow / inflow part (11c). Heat exchanger.   A refrigerant flow path connecting the expansion valve (7), the refrigerant evaporator (8), the ejector (9), and the cold storage heat exchanger (11) is integrally formed, and the refrigerant flow path is formed in the refrigerant flow path. The cold storage heat exchanger provided with the ejector according to claim 1 or 2, wherein the check means (13, 18) is configured.   A refrigerant flow path connecting the expansion valve (7), the refrigerant evaporator (8), the ejector (9), and the cold storage heat exchanger (11) is integrally formed, and the expansion valve (7). The regenerative heat exchanger provided with the ejector according to claim 1, wherein the connecting portion (15 a to 15 c) is aligned with the lower side of the ejector (9).   A refrigerant flow path connecting the expansion valve (7), the refrigerant evaporator (8), the ejector (9), and the cold storage heat exchanger (11) is integrally formed, and the refrigerant evaporator (8 The regenerator heat exchanger having the ejector according to claim 1, wherein connecting portions (15 d, 15 e) with the ejector according to claim 1 are arranged so as to be aligned with the side portions on the top side.   In the high-pressure refrigerant passage (74) inside the structure (B), a driving flow path (14) is branched from a portion upstream of the valve means (73), and the refrigerant passes through the valve means (73). An expansion valve characterized in that an outlet, a refrigerant outlet of the drive flow path (14), and a low-pressure refrigerant passage (75) are provided on the same surface of the structure (B).   A vehicle air conditioner using the cold storage heat exchanger (15) including the ejector according to any one of claims 1 to 5 and the expansion valve (7) according to claim 6.

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