JP5050890B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to a vehicle air conditioner that performs air conditioning when a compressor is stopped due to a stop of a vehicle engine by a refrigeration cycle including a cold storage heat exchanger.

  BACKGROUND ART Conventionally, an apparatus described in Patent Document 1 is known as a vehicle air conditioner that performs air conditioning when a compressor is stopped by a refrigeration cycle including a cold storage heat exchanger. In this vehicle air conditioner, as shown in FIG. 1 of Patent Document 1, a regenerative heat exchanger in the refrigeration cycle is connected in series to the evaporator between the evaporator and the compressor.

  During the cold storage operation, the low temperature refrigerant decompressed and expanded by the expansion valve cools the heat storage material of the cold storage heat exchanger to store cold (stores low-temperature heat), and cools when the engine and compressor are stopped (cold storage). When the heat is released), the refrigerant evaporated in the evaporator is condensed in the regenerative heat exchanger so that the evaporation pressure is kept low and the cooling capacity of the evaporator is maintained.

In addition, the conventional cold storage heat exchanger has a configuration in which a passage through which a refrigerant that is a working medium of the refrigeration cycle passes and a heat storage material are disposed adjacent to each other, and enables heat exchange between the two and the refrigerant and air It is a heat exchanger that enables both heat exchange with air and heat exchange between air and the heat storage material. For example, one having a configuration described in Patent Documents 2, 3, and 4 is known.
Japanese Patent Laid-Open No. 2007-1485 (see FIG. 1) JP 2000-205777 A JP 2002-337537 A JP 2004-184071 A

  However, it is assumed that the vehicle air conditioner described in Patent Document 1 is applied to a so-called idle stop vehicle, and an evaporator and a cold storage heat exchanger are connected in series. The refrigerant pressure becomes equal to the suction pressure of the compressor. And since the refrigerant | coolant pressure of a low voltage | pressure side circuit cannot be made below into a predetermined pressure from a viewpoint of frost prevention, a cold storage amount will be restrict | limited and the improvement of further fuel consumption will become difficult.

  Accordingly, the present invention has been made in view of the above-described problems, and an object thereof is to provide a vehicle air conditioner that can further improve the travel fuel consumption.

In order to achieve the above object, the following technical means are adopted. The invention according to claim 1 relating to the vehicle air conditioner is a compressor (2) for sucking and discharging refrigerant, a condenser (3) for cooling the discharged refrigerant, and cooling by the condenser (3). A decompressor (5) for decompressing the decompressed refrigerant, and an evaporator (6) for evaporating the decompressed refrigerant to cool the air sent to the passenger compartment, in order to form a first ring A vapor compression refrigeration cycle (1) having a flow path (13) is provided.

  The vapor compression refrigeration cycle (1) branches from the first flow path (13) on the upstream side of the refrigerant flow with respect to the decompressor (5) between the decompressor (5) and the condenser (3), and is compressed. It has a second flow path (14) that merges with the first flow path (13) on the suction side of the machine (2). In the second channel (14), a cold storage heat exchanger (9) having a heat storage material (9a) is provided in parallel with the evaporator (6).

The cold storage heat exchanger (9) is cooled by the refrigerant when the compressor (2) is operated, and is cooled by exchanging heat between the heat storage material (9a) and the surrounding air, and around the heat storage material (9a). The air is characterized by flowing toward the condenser (3) after exchanging heat with the heat storage material (9a).

According to the present invention, since the pressure and temperature of the refrigerant flowing through the cold storage heat exchanger can be controlled independently of the refrigerant evaporation pressure in the evaporator, the cold storage is performed even when the output of the compressor is reduced. The amount can be secured to prevent a decrease in refrigeration capacity. Thereby, the vehicle air conditioner excellent in both the air conditioning capability and the COP (coefficient of performance) of the refrigeration cycle can be obtained, and the running fuel consumption can be improved. By cooling the condenser by sending air cooled by heat exchange with the heat storage material to the condenser, the refrigerant pressure on the high-pressure side of the refrigeration cycle decreases, reducing the work of the compressor and saving power Can be planned. Moreover, the thermal energy stored in the cold storage heat exchanger (thermal energy of low-temperature heat (also expressed as cold heat in the present application)) can be transmitted to the refrigeration cycle through the air and utilized.

According to a second aspect of the present invention , the regenerative heat exchanger (9) is provided adjacent to the condenser on the upstream side of the condenser in the flow direction of the air exchanged heat with the refrigerant in the condenser (3). It is characterized by being . According to this invention, the thermal energy stored in the cold storage heat exchanger (thermal energy of low-temperature heat) is supplied to the condenser via air to be transmitted to the refrigeration cycle, thereby improving the COP of the refrigeration cycle. it can. Moreover, it is easy to increase the volume of the heat exchange part of the cold storage heat exchanger, and the travel fuel consumption can be further improved by expanding the cold storage heat capacity.

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

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. In the case where only a part of the configuration is described in each embodiment, the other parts of the configuration are the same as those described previously. In addition to the combination of parts specifically described in each embodiment, the embodiments may be partially combined as long as the combination is not particularly troublesome.

(First embodiment)
The vehicle air conditioner according to the first embodiment, which is an embodiment of the present invention, automatically activates the vehicle engine even when the air conditioner is in an ON state, for example, when a predetermined condition for the vehicle to stop due to waiting for a signal or the like is reached. It is used for a vehicle that reduces the amount of exhaust gas when the vehicle is stopped by stopping and setting an idling stop state. This vehicle air conditioner includes a regenerative heat exchanger disposed in parallel with the evaporator in order to ensure cooling capacity when the engine is stopped and to reduce the air conditioning load. And this regenerative heat exchanger is used to actively store regenerative energy during vehicle deceleration (stores low-temperature heat (also expressed as cold heat in this application)), and stops the compressor in inefficient operating areas. Alternatively, the air-conditioning operation is performed by reducing the operation load, and the traveling fuel consumption is improved.

  Hereinafter, the present embodiment will be described with reference to FIGS. FIG. 1 is a schematic diagram illustrating a refrigerant flow in a cold storage mode in a vapor compression refrigeration cycle 1 according to the vehicle air conditioner of the present embodiment. The vapor compression refrigeration cycle 1 includes a compressor 2 that sucks and discharges refrigerant, a condenser 3 that cools the refrigerant discharged from the compressor 2, and an expansion valve 5 that decompresses the refrigerant cooled by the condenser 3. And the evaporator 6 that evaporates the refrigerant decompressed by the expansion valve 5 and cools the air that is blown into the passenger compartment. It has. In the first flow path 13, a liquid receiving tank 4 is further provided between the condenser 3 and the expansion valve 5.

  The vapor compression refrigeration cycle 1 includes a second flow path 14 in addition to the first flow path 13. The second flow path 14 includes an expansion valve 8 and a regenerative heat exchanger by a pipe branched from the first flow path 13 at a pipe portion 11 upstream of the expansion valve 5 between the expansion valve 5 and the condenser 3. 9 are connected in order, and then connected to the first flow path 13 at the piping portion 12 on the suction side of the compressor 2 to be merged.

  The compressor 2 is a fluid machine that sucks and discharges the refrigerant in the vapor compression refrigeration cycle 1 by a compression mechanism. The compressor 2 is driven by the engine via an electromagnetic clutch. The electromagnetic clutch is ON / OFF controlled based on, for example, an ON / OFF signal output from a control device (not shown), and the operation of the compressor 2 is controlled. When the compressor 2 is composed of a variable capacity compressor, the refrigerating capacity can be controlled by changing the discharge capacity continuously or stepwise by the capacity control valve. The compressor 2 may be driven by an electric motor. This is because when the vehicle air conditioner of the present embodiment is used in a hybrid vehicle or an electric vehicle, it can be driven by an electric motor using a large amount of power supplied from the hybrid vehicle or the electric vehicle.

  The gas refrigerant compressed to high temperature and high pressure by the compressor 2 flows into the condenser 3. The condenser 3 is a heat exchanger that cools the refrigerant compressed to a high temperature and a high pressure by the compressor 2 to condense and liquefy it. The cooling air is blown to the condenser 3 by the traveling wind of the vehicle and an electric fan (not shown), so that the gas refrigerant in the condenser 3 is cooled and condensed. The liquid-receiving tank 4 is a receiver that separates the refrigerant condensed in the condenser 3 into a gas-phase refrigerant and a liquid-phase refrigerant and flows out the liquid-phase refrigerant.

  The expansion valve 5 is a decompressor that can decompress and expand the refrigerant that has flowed out of the liquid receiving tank 4 to a predetermined pressure, and is a temperature type expansion valve that includes a valve part and a temperature sensing part that detects the outlet temperature of the evaporator 6. is there. The degree of superheat of the refrigerant at the outlet of the evaporator 6 is controlled to a predetermined value by controlling the opening degree of the valve unit according to the temperature of the refrigerant detected by the temperature sensing unit. A pipe provided with the expansion valve 5 is provided with a bleed port 10 of a thin pipe that is always open, separately from the valve portion. Further, an expansion valve 5 with a bleed port may be used.

  The evaporator 6 cools the air in the passenger compartment by the latent heat of vaporization of the refrigerant, and is provided in an air conditioning case (not shown) arranged on the back side of an air conditioner operation panel (not shown). And in an air-conditioning case, the air taken in from the vehicle interior or the exterior of the vehicle interior is blown toward the evaporator 6 by a blower (not shown), so that the air cooled by the evaporator 6 is sent out into the vehicle interior. A flow path resistance portion 7 is provided in the first flow path 13 between the evaporator 6 and the suction side of the compressor 2. The flow path resistance unit 7 is a throttle mechanism that controls the refrigerant that has flowed out of the evaporator 6 to a predetermined pressure.

  A post-evaporator sensor (not shown) for detecting the temperature of the cooling air blown by the blower is provided on the downstream side of the evaporator 6. The temperature information detected by the post-evaporator sensor is transmitted to an air conditioner control device (not shown) and used for adjusting the cooling capacity of the evaporator 6. Further, the post-evaporator sensor has a function of preventing frost formation. When the cooling capacity wins the cooling load, the refrigerant evaporation pressure decreases, the surface temperature of the evaporator 6 becomes 0 ° C. or less, the freezing of condensed water progresses, and the flow of the passing air is prevented, and the evaporation pressure further decreases. Air will stop flowing. In order to prevent such a state, the function which controls the cooling capacity of a refrigerating cycle and prevents frost formation is required. In order to know the temperature of the evaporator 6, a fin temperature sensor that directly detects the fin temperature of the evaporator 6 may be used instead of the post-evaporator sensor.

  Further, in the air conditioning case, an air mix door (not shown) is disposed on the downstream side of the evaporator 6, and a heater core (not shown) is used on the downstream side of the air mix door to heat the air using engine hot water as a heat source. ) Is arranged. The air mix door has a function of adjusting the temperature of the air blown into the passenger compartment, and adjusts the ratio between the warm air from the heater core and the air flowing directly from the evaporator 6.

  The expansion valve 8 provided in the second flow path 14 is a decompressor similar to the expansion valve 5 described above. The cold storage heat exchanger 9 is provided in parallel to the evaporator 6. The cold storage heat exchanger 9 has a configuration capable of exchanging heat between a refrigerant (for example, HFC134a) that is a working medium of the refrigeration cycle, air, and a heat storage material (for example, paraffin, ice). The heat storage material can store heat (cold heat, warm heat) and the like carried by the refrigerant. In the cold storage (stores cold energy in the heat storage material) mode, the refrigerant having a temperature lower than the melting point of the heat storage material is circulated through the cold storage heat exchanger 9 to solidify the heat storage material and store the solidified latent heat. In the cooling mode (releasing the stored heat) mode, air having a temperature higher than the melting point of the heat storage material is circulated, so that the heat storage material is heated and melted by receiving the latent heat of fusion.

  For example, it has the structure which arrange | positions the thermal storage material cell 9a with which the thermal storage material is filled, and the channel | path through which a refrigerant | coolant adjoins, and enables heat exchange between both. Furthermore, it has the structure arrange | positioned adjacent to the channel | path through which the thermal storage material cell 9a and air pass, and heat exchange is enabled between both. As a specific configuration of such a heat exchanger, various configurations can be adopted including the configuration described in the above-mentioned column of the prior art. For example, a fin-and-tube type heat exchanger forms a portion that encloses a heat storage material in a double-structure tube and a flow path that allows refrigerant to pass through, and further promotes heat exchange between the inside of the tube and the surrounding air. For this purpose, the fins are alternately laminated with the tubes.

  The air conditioner control device has a built-in microcomputer (not shown) in which a control program related to air conditioning control, an arithmetic expression, and the like are stored, and detects a signal output by operation of the air conditioner operation panel, the temperature of the inside air or the outside air Based on signals output from sensor groups such as an air detection sensor, solar radiation sensor, post-evaporator sensor, engine water temperature sensor, and signals transmitted from an engine control device (not shown) The air switch door, air mix door, electromagnetic clutch, blower, compressor 2 and the like are controlled.

  The engine control device controls the engine on the basis of a group of sensors that detect the operation state of the engine such as a rotation speed signal, a vehicle speed signal, and a brake signal, and transmits the operation state of the engine to the air conditioner control device. When the engine control device detects a stop state based on an engine speed signal, a vehicle speed signal, a brake signal, or the like, the engine control device shuts off the power to the ignition device, stops fuel injection, or the like, and automatically stops the engine. Then, after the engine is stopped, when the vehicle is shifted to a state where the vehicle is started by a driver's driving operation, the engine control device recognizes the start state based on an accelerator signal and the like, and starts the engine. Further, the engine control device and the air conditioner control device may be integrated as a single control device.

  Next, the operation of the vapor compression refrigeration cycle 1 in the above configuration will be described. The operation of the vapor compression refrigeration cycle 1 includes a cold storage mode, a cooling mode in which the compressor 2 is operating, and a cooling mode in which the compressor 2 is stopped.

  When the compressor 2 is driven by the engine when the vehicle is running and the vapor compression refrigeration cycle 1 is activated, the cold storage mode is started thereafter. As shown in FIG. 1, the refrigerant discharged by the compressor 2 is condensed by the condenser 3 and separated into gas and liquid by the liquid receiving tank 4. A part of the refrigerant flowing out of the liquid receiving tank 4 is decompressed and expanded by the expansion valve 5 and then evaporated by absorbing heat from the surrounding air by the evaporator 6 to cool the surrounding air. The refrigerant evaporated in the evaporator 6 is decompressed by the flow path resistance unit 7 and then merged with the refrigerant that has flowed through the second flow path 14 (to be described later) in the piping portion 12 (merging portion) on the suction side of the compressor 2. Then, it is sucked into the compressor 2.

  On the other hand, the remaining portion of the refrigerant that has flowed out of the liquid receiving tank 4 is branched at the piping portion 11 (branch portion) upstream of the expansion valve 5 between the expansion valve 5 and the condenser 3, and the second flow path 14. The refrigerant is decompressed and expanded by the expansion valve 8 and flows into the refrigerant passage of the cold storage heat exchanger 9. In the cold storage heat exchanger 9, when the refrigerant evaporates, the heat storage material in the heat storage material cell 9a is cooled from the heated state, and low-temperature heat is stored in the heat storage material. Until this cool storage is completed, the air passing from the front of the cool storage heat exchanger 9 toward the rear (air sent to the front surface of the condenser 3) is not cooled, so the high pressure side flowing in the condenser 3 is not cooled. The refrigerant is not cooled. The refrigerant that has flowed out of the cold storage heat exchanger 9 merges with the refrigerant that has flowed through the first flow path 13 in the piping portion 12 on the suction side of the compressor 2 and is sucked into the compressor 2. When the cold storage to the heat storage material is completed, the heat transfer between the refrigerant and the heat storage material in the cold storage heat exchanger 9 is stopped.

  Next, the cooling mode will be described with reference to FIGS. FIG. 2 is a schematic diagram showing the refrigerant flow in the cooling mode when the compressor 2 is operating. FIG. 3 is a schematic diagram showing the refrigerant flow in the cooling mode when the compressor 2 is stopped.

  As shown in FIG. 2, when the cold storage mode is completed, the cold storage heat exchanger 9 cools the air sent to the front surface of the condenser 3 by the pressure reduction by the expansion valve 8 and the heat storage material cooled in the cold storage mode. Then, the cold energy (heat energy of low temperature heat) stored in the heat storage material is released (cooled). As a result, the refrigerant flowing through the condenser 3 is further cooled than the outside air temperature, so that the refrigerant pressure is lowered, the compression ratio of the compressor 2 is lowered, and the COP (coefficient of performance) of the refrigeration cycle is improved.

  On the other hand, when the vehicle stops and, for example, a predetermined condition for idling stop is satisfied, the engine control device stops the engine and the compressor 2 also stops. Since the driving of the refrigeration cycle is stopped during the cooling mode when the compressor 2 is stopped, the blower for blowing air to the condenser 3 is stopped and forced as shown in FIG. No blast is made. At this time, in the refrigeration cycle, the refrigerant flows from the high pressure side condenser 3 and the liquid receiving tank 4 toward the low pressure side evaporator 6 due to the residual pressure. Then, the refrigerant that has flowed out of the evaporator 6 passes through the piping portion 12 on the suction side of the compressor 2, flows into the second flow path 14, and flows into the cold storage heat exchanger 9.

  In this case, the cooling capacity of the evaporator 6 is not affected even if the refrigerant flows into the regenerator heat exchanger 9 and is cooled by cooling the air on the front side of the condenser 3. However, since the heat storage material of the heat storage material cell 9a holds cold heat (thermal energy of low temperature heat), the gas refrigerant evaporated in the evaporator 6 flows into the cold storage heat exchanger 9, and is cooled and condensed inside. As a result, the refrigerant pressure on the low pressure side of the cycle (evaporator 6, piping on the suction side of the compressor 2, cold storage heat exchanger 9) is kept low while the amount of heat stored in the heat storage material remains.

  Further, in this cooling mode, the expansion valve 5 is closed, but the liquid refrigerant can flow into the evaporator 6 through the bleed port 10 while the residual pressure remains in the high pressure side condenser 3 or the like. The maintenance of the cooling capacity by the evaporator 6 can be helped. Further, according to this cooling mode, even when the compressor 2 is stopped, it is possible to supply cooling to the passengers in the passenger compartment, so as not to cause discomfort. Further, in the cooling mode, when the vehicle shifts to the running state, the engine control device starts the engine, and when the compressor 2 is also operated, the cooling storage mode is shifted to.

  The effect of the vehicle air conditioner according to this embodiment will be described below. According to the above configuration, for example, the cold storage mode with the movement of the cold, the cooling mode for operating the compressor 2, and the cooling mode for stopping the compressor 2 are repeated so that the engine stop and operation by the idling stop function are linked. The operation performed can be carried out. As a result, regenerative energy at the time of vehicle deceleration is actively used for driving the compressor 2 to perform cold storage, and in an inefficient operating range, the compressor is stopped or the operating load is reduced to perform air conditioning operation. , Improve driving fuel economy. Moreover, since the pressure of the refrigerant | coolant which distribute | circulates the cool storage heat exchanger 9 can be controlled independently of the evaporation pressure of the refrigerant | coolant in the evaporator 6, even if the output of the compressor 2 reduces, a cold storage amount is ensured. A refrigeration cycle that suppresses a decrease in refrigeration capacity can be provided.

  In addition, by allowing the compressor 2 to cool, the degree of freedom in controlling the refrigeration cycle operation can be expanded, and the cold storage operation and the cool operation can be applied according to various traveling conditions of the vehicle. The refrigeration cycle can be easily operated in a region where the fuel efficiency of the engine is high, and the driving fuel efficiency can be improved. In addition, even when the compressor 2 is in operation, a refrigeration cycle having a function of assisting the power of the compressor 2 can be provided by performing the cooling mode using the stored heat amount of the cold storage heat exchanger 9. An improvement in the COP of the refrigeration cycle is obtained.

  In addition, since the air around the heat storage material exchanges heat with the heat storage material and then flows toward the condenser 3, the condenser 3 is cooled by the low-temperature cold stored in the heat storage material, Since the refrigerant pressure on the high pressure side of the cycle is reduced, the compression ratio of the compressor 2 is reduced, and a power-saving refrigeration cycle can be realized.

  Further, the cold storage heat exchanger 9 is provided upstream of the condenser 3 of the air passing through the condenser 3 (in front of the vehicle) and adjacent to the condenser 3, so that the cold storage heat exchanger 9 Since it is easy to increase the volume of the heat exchange portion, it is possible to increase the cold storage heat capacity and increase the cooling time, and to further improve the driving fuel consumption.

( First reference form)
The vapor compression refrigeration cycle 20 relating to the vehicle air conditioner of the first reference embodiment will be described with reference to FIG. In this preferred embodiment, configurations different from the first embodiment, only describes operation and effects, others are the same as the first embodiment. FIG. 4 is a schematic diagram showing the refrigerant flow in the cooling mode when the compressor 2 is operating in the vapor compression refrigeration cycle 20.

  As shown in FIG. 4, the vapor compression refrigeration cycle 20 includes a compressor 2, a condenser 3, a liquid receiving tank 4, an expansion valve 5, an evaporator 6, and a flow path resistance portion 7 that are sequentially connected in an annular manner by piping. In addition to the configured first flow path 21 (main circuit), a second flow path 22 is provided. The second flow path 22 is connected to the expansion valve 8 by a pipe branched from the first flow path 21 at a piping portion 23 upstream of the expansion valve 5 between the expansion valve 5 and the liquid receiving tank 4. It connects to the 1st flow path 21 in the piping part 24 by the side of the suction of the compressor 2, and it is comprised after connecting the apparatus 9 in order. The cold storage heat exchanger 9 is connected to the evaporator 6 by a pipe so as to be in parallel, and is provided adjacent to the evaporator 6 in front of the evaporator 6.

  Next, the operation of the vapor compression refrigeration cycle 20 in the above configuration will be described. In the operation of the vapor compression refrigeration cycle 20, as in the vapor compression refrigeration cycle 1 of the first embodiment, the cold storage mode, the cooling mode in which the compressor 2 is operating, and the compressor 2 are stopped. There is a cooling mode, which is.

  Hereinafter, the cooling mode in which the compressor 2 is operating will be described with reference to FIG. At the stage when the cold storage mode is completed, the cold storage heat exchanger 9 cools the indoor air sent to the evaporator 6 by the pressure reduction by the expansion valve 8 and the heat storage material cooled in the cold storage mode, and stores the low temperature heat in the heat storage material. The heat energy is released (cooled). Thereby, the low-temperature heat stored in the cold storage heat exchanger 9 is supplied to the evaporator 6 through the indoor air, so that it can be transmitted to the refrigeration cycle for effective use.

Effects of air conditioning system according to this reference embodiment described below. In this preferred embodiment, after the air around the heat storage material has been heat-exchanged heat storage material, and is configured to flow toward the evaporator 6. According to this, heat exchange between the air before being cooled by the evaporator 6 and the heat storage material increases the temperature difference between the air and the heat storage material, so that the cooling capacity can be increased, and the refrigeration cycle. COP can be improved.

( Second reference form)
The vapor compression refrigeration cycle 30 relating to the vehicle air conditioner of the second reference embodiment will be described with reference to FIG. In this preferred embodiment, configurations different from the first embodiment, only describes operation and effects, others are the same as the first embodiment. FIG. 5 is a schematic diagram showing the refrigerant flow in the cooling mode in the vapor compression refrigeration cycle 30.

  As shown in FIG. 5, the vapor compression refrigeration cycle 30 includes a compressor 2, a condenser 3, a liquid receiving tank 4, an expansion valve 5, an evaporator 6, and a flow path resistance unit 7 that are sequentially connected in an annular manner by piping. In addition to the configured first flow path 31 (main circuit), a second flow path 32 is provided. The second flow path 32 is connected to the expansion valve 8 by a pipe branched from the first flow path 31 at a piping portion 33 upstream of the expansion valve 5 between the expansion valve 5 and the liquid receiving tank 4. It connects to the 1st flow path 31 in the piping site | part 34 of the suction side of the compressor 2, and it is comprised after connecting the apparatus 9 in order. The cold storage heat exchanger 9 is connected to the evaporator 6 by a pipe so as to be in parallel, and is provided in front of the evaporator 6 (on the windward side) and adjacent to the evaporator 6.

  Next, the operation of the vapor compression refrigeration cycle 30 in the above configuration will be described. The operation of the vapor compression refrigeration cycle 30 includes, as in the vapor compression refrigeration cycle 1 of the first embodiment, a cold storage mode, a cooling mode in which the compressor 2 is operating, and the compressor 2 is stopped. There is a cooling mode, which is.

Hereinafter, the cooling mode in which the compressor 2 is operating will be described with reference to FIG. At the stage where the cold storage mode is completed, the cold storage heat exchanger 9 further converts the indoor air cooled to some extent by heat exchange in the evaporator 6 to the heat storage material by the decompression by the expansion valve 8 and the heat storage material cooled in the cold storage mode. It cools and cools with the thermal energy of the stored low-temperature heat. Although the cooling at this time has a lower cooling capacity than the cooling described in the first embodiment, the heating of the heat storage material is kept low because the heating by the cooling immediately before that is suppressed. is there.

Effects of air conditioning system according to this reference embodiment described below. In this preferred embodiment, the cold storage heat exchanger 9 is provided on the downstream side of the evaporator 6 in the flow direction of air with the refrigerant heat exchanger inside the evaporator 6. According to this, first, the air cooled by the evaporator 6 exchanges heat with the heat storage material thereafter, so that heating of the heat storage material during cooling is suppressed and temperature rise of the heat storage material can be suppressed. Therefore, the ability to cool the heat storage material can be easily increased, and the cold storage time can be shortened.

( Third reference form)
A vapor compression refrigeration cycle 40 relating to a vehicle air conditioner according to a third embodiment will be described with reference to FIG. Vapor compression refrigeration cycle 40 of this preferred embodiment has a configuration of performing via the refrigerant of the refrigeration cycle without the intervention of the air as the transfer medium for cooling the storage heat quantity of the heat storage material. Further, in this preferred embodiment, configurations different from the first embodiment, only describes operation and effects, others are the same as the first embodiment. FIG. 6 is a schematic diagram showing a refrigerant flow in the cooling mode in the vapor compression refrigeration cycle 40.
Described below for the effect of the vehicle air conditioner according to the reference present reference embodiment. Vapor compression refrigeration cycle 40 of this preferred embodiment includes a second flow path 46, the cold storage heat exchanger 41 connected by piping in parallel with the evaporator 6, the bypass passage 47, cold storage heat by the bypass passage 47 A flow path resistance unit 7 connected in parallel to the exchanger 41, and further closed by a first on-off valve 42 that is closed during cold storage, and a first on-off valve 42 and a third on-off valve that are closed at the time of cooling. 44 as an opening / closing means. The cold storage heat exchanger 41 is cooled by the refrigerant when the compressor 2 is operated, and is cooled by heat exchange between the refrigerant evaporated in the evaporator 6 and the heat storage material by opening and closing of the opening / closing means.

  As shown in FIG. 6, the vapor compression refrigeration cycle 40 branches from the first flow path 45 at a piping portion (branch portion) upstream of the expansion valve 5 between the expansion valve 5 and the condenser 3. The second flow path 46 connected by piping so as to merge with the first flow path 45 at the piping portion 49 (merging portion) on the suction side of the compressor 2 is provided. Further, the vapor compression refrigeration cycle 40 is in parallel with the evaporator 6 in the second flow path 46 and the flow path resistance portion 7 provided on the downstream side of the evaporator 6 between the evaporator 6 and the compressor 2. And a cold storage heat exchanger 41 provided so as to become. Further, the vapor compression refrigeration cycle 40 is located between the evaporator 6 and the flow path resistance unit 7 and downstream of the evaporator 6 and more than the cold storage heat exchanger 41 of the second flow path 46. A bypass flow path 47 that connects the upstream piping section, and opening / closing means that switches the refrigerant flow between the inlet and outlet of the cold storage heat exchanger 41 and the first flow path 45 are provided. By connecting the first flow path 45 and the second flow path 46 by the bypass flow path 47, the cold storage heat exchanger 41 is in parallel with the flow path resistance unit 7.

  The opening / closing means includes a first opening / closing valve 42, a second opening / closing valve 43, and a third opening / closing valve 44, which are electromagnetic valves, respectively, and the inlet and outlet of the cold storage heat exchanger 41 and the first flow path. 45 is used to switch the circulation of the refrigerant. The first on-off valve 42 is provided on the upstream side of the second flow path 46 and on the downstream side of the expansion valve 8 with respect to the cold storage heat exchanger 41, and the refrigerant flowing out of the condenser 3 is in the second flow path. 46 is a valve that controls whether or not it can flow into 46. The second on-off valve 43 is a valve that is provided in the bypass flow path 47 and controls whether or not the refrigerant that has flowed out of the evaporator 6 can flow into the cold storage heat exchanger 41 of the second flow path 46. is there. The third on-off valve 44 is a valve that is provided on the downstream side of the cold storage heat exchanger 41 and controls whether or not the refrigerant in the cold storage heat exchanger 41 can be sucked into the compressor 2.

  Next, regarding the operation of the vapor compression refrigeration cycle 40 in the above configuration, a cold storage mode, a cooling mode in which the compressor 2 is operating, and a cooling mode in which the compressor 2 is stopped will be described. In FIG. 6, an alternate long and short dash line indicates the refrigerant flow in the cold storage mode, and a solid arrow indicates the refrigerant flow in the cooling mode.

  When the compressor 2 is driven by the engine when the vehicle is running and the vapor compression refrigeration cycle 40 is activated, the cold storage mode is started after an initial state (a state where the refrigerant flows only through the first flow path 45). In the cold storage mode, the first on-off valve 42 and the third on-off valve 44 are controlled to be opened, the second on-off valve 43 is controlled to be closed, and the refrigerant flow in the cycle forms two paths. To do. One is a path that flows in the order of the compressor 2, the condenser 3, the expansion valve 5, the evaporator 6, the flow path resistance unit 7, and the compressor 2, and the other is the compressor 2, the condenser 3, and the expansion valve 8. The first on-off valve 42, the regenerator heat exchanger 41, the third on-off valve 44, and the compressor 2 flow in this order. The refrigerant discharged from the compressor 2 is condensed and liquefied by the condenser 3. A part of the refrigerant flowing out of the condenser 3 is decompressed and expanded by the expansion valve 5 and then evaporated by absorbing heat from the surrounding air by the evaporator 6 to cool the surrounding air. The refrigerant evaporated in the evaporator 6 is depressurized by the flow path resistance unit 7 and then merged with the refrigerant that has flowed through the second flow path 46 in the piping portion 49 (merging portion) on the suction side of the compressor 2. It is sucked into the compressor 2.

  On the other hand, the remaining part of the refrigerant that has flowed out of the condenser 3 branches off at a piping portion (branch portion) upstream of the expansion valve 5 between the expansion valve 5 and the condenser 3 and flows into the second flow path 46. Then, after being decompressed and expanded by the expansion valve 8 and passing through the first on-off valve 42, the refrigerant flows into the refrigerant passage of the cold storage heat exchanger 41. In the cold storage heat exchanger 41, when the refrigerant evaporates, the heat storage material in the heat storage material cell 41a is cooled from the heated state, and low-temperature heat energy is stored in the heat storage material. The refrigerant that has flowed out of the cold storage heat exchanger 41 passes through the third on-off valve 44, joins the refrigerant that has flowed through the first flow path 45 in the piping portion 49 on the suction side of the compressor 2, and then enters the compressor 2. Inhaled. When the cold storage to the heat storage material is completed, the heat transfer between the refrigerant and the heat storage material in the cold storage heat exchanger 41 is stopped.

  Next, the cooling mode will be described. The cooling mode is a mode in which the stored heat amount of the heat storage material is allowed to cool through the refrigerant of the refrigeration cycle. When the cold storage mode is completed, the first on-off valve 42 and the third on-off valve 44 are controlled to be in a closed state, and when the second on-off valve 43 is controlled to be in an open state, the cooling mode is started. At this time, the refrigerant flow in the refrigeration cycle is divided from the path through the first flow path 45 and the pipe section 48 of the first flow path 45 downstream of the evaporator 6, and flows through the bypass flow path 47. Through the regenerator heat exchanger 41 (see the solid arrow line in FIG. 6). In the cooling mode, the flow rate of the refrigerant flowing into the regenerator heat exchanger 41 through the bypass channel 47 is a pressure difference between the two determined by the temperature of the regenerator material in the regenerator cell 41a and the outlet temperature of the evaporator 6. It becomes proportional. The refrigerant flow rate flowing into the cold storage heat exchanger 41 corresponds to a decrease in the refrigerant pressure on the high pressure side (refrigerant pressure in the condenser 3) with respect to the initial state. On the other hand, the pressure of the high-pressure side refrigerant decreases, and the COP of the refrigeration cycle is improved.

  On the other hand, when the vehicle stops and, for example, a predetermined condition for idling stop is satisfied, the engine control device stops the engine and the compressor 2 also stops. In such a cooling mode when the compressor 2 is stopped, the first on-off valve 42 and the third on-off valve 44 are controlled to be closed, and the second on-off valve 43 is controlled to be opened. At this time, in the refrigeration cycle, the refrigerant flows from the condenser 3 on the high pressure side toward the evaporator 6 on the low pressure side due to the residual pressure. The refrigerant that has flowed out of the evaporator 6 is diverted from the bypass flow path 47 and flows into the second flow path 46 and flows into the cold storage heat exchanger 41. Further, according to this cooling mode, even when the compressor 2 is stopped, it is possible to supply cooling to the passengers in the passenger compartment, so as not to cause discomfort. Further, in the cooling mode, when the vehicle shifts to the running state, the engine control device starts the engine, and when the compressor 2 is also operated, the cooling storage mode is shifted to.

Effects of air conditioning system according to this reference embodiment described below. Vapor compression refrigeration cycle 40 of this preferred embodiment includes a second flow path 46, the cold storage heat exchanger 41 connected by piping in parallel with the evaporator 6, the bypass passage 47, cold storage heat by the bypass passage 47 A flow path resistance unit 7 connected in parallel to the exchanger 41, and further closed by a first on-off valve 42 that is closed during cold storage, and a first on-off valve 42 and a third on-off valve that are closed at the time of cooling. 44 as an opening / closing means. The cold storage heat exchanger 41 is cooled by the refrigerant when the compressor 2 is operated, and is cooled by heat exchange between the refrigerant evaporated in the evaporator 6 and the heat storage material by opening and closing of the opening / closing means.

Thus, as with the other forms state of the vehicle air conditioner, the output of the compressor 2 can be prevented from reduction in refrigerating capacity to ensure the cold storage amount even when the reduction. Moreover, since it is the structure of the refrigerating cycle which can each arrange | position the condenser 3, the evaporator 6, and the cool storage heat exchanger 41 grade | etc., The freedom degree of the position which can mount the cool storage heat exchanger 41 in a vehicle becomes high. Moreover, since it is comprised so that the function of each heat exchangers, such as the evaporator 6, the condenser 3, and the cool storage heat exchanger 41, can be exhibited independently, the structure of each heat exchanger can be simplified.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

In the above form state, it was used expansion valve as a pressure reducing unit of the vapor compression refrigeration cycle apparatus 1,20,30,40, may alternatively be used ejector. The ejector has a nozzle part that decompresses and expands the high-pressure side refrigerant, and a pressure raising part that increases the pressure of the refrigerant by mixing the refrigerant injected from the nozzle part and the gas-phase refrigerant sucked from the evaporator 6. Thus, the power of the compressor 2 can be reduced.

In the third embodiment, a check valve (refrigerant is supplied from the regenerator heat exchanger 41 to the compressor) connected to the second flow path 46 of the vapor compression refrigeration cycle 40 in parallel with the third on-off valve 44. 2 may be provided to prevent flow to the suction port side.

It is the schematic diagram which showed the refrigerant | coolant flow at the time of the cool storage mode in the refrigerating cycle which concerns on the vehicle air conditioner of 1st Embodiment. It is the schematic diagram which showed the refrigerant | coolant flow at the time of the natural cooling mode in case the compressor is operate | moving in the refrigerating cycle of 1st Embodiment. It is the schematic diagram which showed the refrigerant | coolant flow at the time of the natural cooling mode when the compressor stopped in the refrigerating cycle of 1st Embodiment. It is the schematic diagram which showed the refrigerant | coolant flow at the time of the cooling mode in the refrigerating cycle which concerns on the vehicle air conditioner of a 1st reference form. It is the schematic diagram which showed the refrigerant | coolant flow at the time of the cooling mode in the refrigerating cycle which concerns on the vehicle air conditioner of a 2nd reference form. It is the schematic diagram which showed the refrigerant | coolant flow at the time of the cool storage mode in the refrigerating cycle which concerns on the vehicle air conditioner of a 3rd reference form, and the cool-down mode.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,40 ... Vapor compression refrigeration cycle 2 ... Compressor 3 ... Condenser 5 ... Expansion valve (decompressor)
6 ... Evaporator 9, 41 ... Cold storage heat exchanger 9a, 41a ... Thermal storage material cell (thermal storage material)
DESCRIPTION OF SYMBOLS 13, 45 ... 1st flow path 14, 46 ... 2nd flow path 42 ... 1st on-off valve (opening-closing means)
43 ... Second on-off valve (open / close means)
44. Third on-off valve (open / close means)
47. Bypass channel

Claims (2)

A compressor (2) for sucking and discharging the refrigerant, a condenser (3) for cooling the discharged refrigerant, and a decompressor (5) for depressurizing the refrigerant cooled by the condenser (3); A vapor compression refrigeration cycle having a first flow path (13) configured by sequentially connecting an evaporator (6) that evaporates the decompressed refrigerant and cools air that is blown into the passenger compartment in an annular manner. A vehicle air conditioner comprising (1),
The vapor compression refrigeration cycle (1) branches from the first flow path (13) upstream of the decompressor (5) between the decompressor (5) and the condenser (3). A second flow path (14) that merges with the first flow path (13) on the suction side of the compressor (2),
The second flow path (14) has a heat storage material (9a), and is provided with a cold storage heat exchanger (9) connected in parallel with the evaporator (6),
The cold storage heat exchanger (9) is cooled by the refrigerant when the compressor (2) is operated, and is cooled by heat exchange between the heat storage material (9a) and the surrounding air ,
The air conditioner for vehicles , wherein the air around the heat storage material (9a) flows toward the condenser (3) after exchanging heat with the heat storage material (9a) . The cold storage heat exchanger (9) is provided adjacent to the condenser on the upstream side of the condenser in the flow direction of the air exchanged with the refrigerant in the condenser (3). The vehicle air conditioner according to claim 1 , wherein

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