WO2017183588A1 - Dispositif de climatisation de véhicule et véhicule doté de ce dernier - Google Patents

Dispositif de climatisation de véhicule et véhicule doté de ce dernier Download PDF

Info

Publication number
WO2017183588A1
WO2017183588A1 PCT/JP2017/015339 JP2017015339W WO2017183588A1 WO 2017183588 A1 WO2017183588 A1 WO 2017183588A1 JP 2017015339 W JP2017015339 W JP 2017015339W WO 2017183588 A1 WO2017183588 A1 WO 2017183588A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
refrigerant
heat
load
vehicle air
Prior art date
Application number
PCT/JP2017/015339
Other languages
English (en)
Japanese (ja)
Inventor
輝明 辻
光彦 赤星
林　直人
真 吉田
祐二 中西
佐藤　元春
Original Assignee
株式会社ヴァレオジャパン
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社ヴァレオジャパン filed Critical 株式会社ヴァレオジャパン
Publication of WO2017183588A1 publication Critical patent/WO2017183588A1/fr

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the coefficient of performance is known as an index indicating the capacity of the refrigeration cycle, and is calculated as a value obtained by dividing the cooling capacity in the evaporator by the power for driving the compressor.
  • the coefficient of performance can be increased by increasing the cooling capacity and reducing the power for driving the compressor.
  • the coefficient of performance can be improved by providing an internal heat exchanger in the refrigeration cycle.
  • the coefficient of performance decreases depending on the thermal load around the refrigeration cycle. And there is room for improvement.
  • the present disclosure relates to a vehicle air conditioner including an internal heat exchanger, and provides a vehicle air conditioner capable of maintaining a high coefficient of performance even when a thermal load fluctuates, and a vehicle capable of maintaining a high coefficient of performance. It aims at providing the vehicle provided with the air conditioner for vehicles.
  • the vehicle air conditioner according to the present invention includes a refrigerant circuit that circulates a refrigerant by connecting a compressor, a condenser, an expansion device, and an evaporator with piping, and a refrigerant that is led from the condenser to the expansion device flows.
  • a refrigeration cycle having an internal heat exchanger for exchanging heat of the refrigerant between the first heat exchange unit and a second heat exchange unit through which the refrigerant is introduced from the evaporator to the suction side of the compressor.
  • a heat load detection device that detects a heat load of the refrigeration cycle, and a heat exchange amount adjustment mechanism that suppresses the heat exchange in the internal heat exchanger when the heat load is higher than a predetermined heat load; It is characterized by providing.
  • the heat exchange amount adjusting mechanism includes: (1) a first bypass circuit that bypasses the first heat exchange unit and guides the refrigerant from the condenser to the expansion device; Or (2) an internal heat exchanger detour having either or both of a second detour that bypasses the second heat exchange section and guides the refrigerant from the evaporator to the suction side of the compressor And ratio adjusting means for changing the ratio of the refrigerant flowing through the refrigerant circuit and the internal heat exchanger bypass, and a ratio control device for controlling the ratio adjusting means, the ratio control device, When the heat load is higher than the predetermined heat load, it is preferable to increase the ratio of the refrigerant flowing in the internal heat exchanger detour.
  • the ratio of refrigerant flowing through the internal heat exchanger bypass is increased, that is, the ratio of refrigerant flowing through the internal heat exchanger is decreased, and the degree of superheat of refrigerant sucked by the compressor Can be prevented from becoming too large.
  • the internal heat exchanger includes a plurality of internal heat exchange units in which the first heat exchange unit and the second heat exchange unit form a pair, and the internal heat exchange unit The units are respectively connected in parallel to the refrigerant circuit, and the heat exchange adjustment mechanism includes a distribution degree adjusting means for changing a distribution degree of the refrigerant flowing to each of the internal heat exchange units, and the distribution degree adjustment.
  • a distribution degree control device for controlling the means, and the distribution degree control device controls the distribution degree of the refrigerant flowing to each of the internal heat exchange units when the heat load is higher than the predetermined heat load. It is preferable to bias it. When the heat load is high, the distribution degree of the refrigerant flowing through the internal heat exchange unit can be biased, and the superheat degree of the refrigerant sucked by the compressor can be prevented from becoming too large.
  • the heat exchange adjustment mechanism includes: (1) connecting the refrigerant circuit and the first heat exchange unit at a plurality of positions, with respect to the first heat exchange unit.
  • the connection pipe part having either one or both of the second connection pipe parts arranged in series and the first connection pipe part or the second connection pipe part
  • a heat exchange area adjusting means for changing an effective area for heat exchange among the first heat exchange section and the second heat exchange section, and an effective area control device for controlling the heat exchange area adjustment means.
  • the effective area control device has the heat load when the heat load is higher than the predetermined heat load. It is preferable to reduce the effective area for the heat exchange. When the heat load is high, the effective area for heat exchange in the internal heat exchanger can be reduced, and the superheat degree of the refrigerant sucked by the compressor can be prevented from becoming too large.
  • the thermal load detection device is an outside air temperature detection device that detects an outside air temperature of the vehicle.
  • the heat load can be detected more appropriately.
  • the thermal load detection device is preferably a refrigerant state detection device that detects a pressure and a temperature of the refrigerant between the evaporator and the second heat exchange unit. . Since the amount of heat exchange in the internal heat exchanger can be controlled so that the superheat degree of the refrigerant sucked into the compressor becomes constant, a high coefficient of performance can be obtained stably.
  • the heat exchange amount adjusting mechanism includes a form in which the degree of suppression of the heat exchange in the internal heat exchanger is increased continuously or stepwise as the heat load increases. To do.
  • the heat exchange amount adjusting mechanism suppresses the flow of the refrigerant in the second heat exchange unit.
  • the suction pressure by the compressor can be further reduced, and the power of the compressor can be further reduced.
  • the heat exchange amount adjusting mechanism suppresses the flow of the refrigerant in the first heat exchange unit.
  • An increase in the degree of superheat of the refrigerant flowing through the second heat exchange unit is suppressed, the suction pressure by the compressor can be reduced, and the power of the compressor can be further reduced.
  • a vehicle according to the present invention includes the vehicle air conditioner according to the present invention.
  • a vehicle air conditioner including an internal heat exchanger it is possible to provide a vehicle air conditioner capable of maintaining a high coefficient of performance even when a thermal load fluctuates, and to maintain a high coefficient of performance.
  • the vehicle provided with the vehicle air conditioner which can be provided can be provided.
  • FIG. 1 is a system diagram showing an example of a vehicle air conditioner according to the present embodiment.
  • the vehicle air conditioner according to the present embodiment includes a refrigerant circuit 9 that circulates refrigerant by connecting the compressor 2, the condenser 3, the expansion device 4, and the evaporator 5 through pipes 61 to 66, and the expansion device from the condenser 3.
  • the internal heat that exchanges heat between the first heat exchange unit 11 through which the refrigerant guided to 4 flows and the second heat exchange unit 12 through which the refrigerant guided from the evaporator 5 to the suction side of the compressor 2 flows.
  • the refrigeration cycle 1 having the exchanger 10, the thermal load detection device 40 for detecting the thermal load of the refrigeration cycle 1, and the heat exchange in the internal heat exchanger 10 when the thermal load is higher than a predetermined thermal load. And a heat exchange amount adjusting mechanism 50 to be suppressed.
  • the refrigerant circuit 9 is a closed circuit in which the compressor 2, the condenser 3, the expansion device 4, and the evaporator 5 are connected by pipes 61 to 66, and the refrigerant circulates therein.
  • the refrigerant is, for example, a fluorocarbon material such as R134a, HFO-1234yf, or carbon dioxide.
  • the refrigerant circuit 9 separates a gaseous refrigerant and a liquid refrigerant inside the condenser 3 or between the condenser 3 and the internal heat exchanger 10 when the refrigerant circulating inside is a fluorocarbon material.
  • a liquid tank (not shown) for storing a part of the refrigerant is provided.
  • the refrigerant circuit 9 includes an accumulator (not shown) that stores a part of the refrigerant between the evaporator 5 and the compressor 2 when the refrigerant circulating inside is carbon dioxide.
  • the compressor 2 receives a driving force from an engine (not shown) or a driving force of a motor (not shown) driven by electric power, compresses the refrigerant in a vaporized state at low temperature and low pressure, Use high-pressure vaporized refrigerant.
  • the compressor 2 is, for example, a fixed capacity type compressor or a variable capacity type compressor.
  • the condenser 3 is generally disposed in front of the radiator in the engine room at the front end (front) of the vehicle.
  • the condenser 3 is a heat exchanger, and is a vehicle in which high-temperature and high-pressure vaporized refrigerant discharged from the compressor 2 is provided on the front surface of a vehicle such as a front grill and is introduced from a grill opening (not shown). It is cooled by the outside air in front and made into a liquefied refrigerant at high temperature and pressure.
  • the outside air introduced from the grill opening is generated by either or both of running the vehicle and operating a cooling fan (not shown).
  • the expansion device 4 depressurizes and expands the refrigerant condensed in the condenser 3 to produce a low-temperature and low-pressure mist refrigerant (gas-liquid mixed refrigerant) and adjusts the flow rate of the refrigerant.
  • the expansion device 4 is, for example, a temperature-sensitive expansion valve or an electronically controlled expansion valve.
  • the evaporator 5 is a heat exchanger, vaporizes the refrigerant that has become a gas-liquid mixture in the expansion device 4, and cools and dehumidifies the blown air that passes through the evaporator 5 by the heat of evaporation at that time.
  • the internal heat exchanger 10 is disposed on the refrigerant circuit 9.
  • the internal heat exchanger 10 includes a first heat exchange unit 11 through which the refrigerant guided from the condenser 3 to the expansion device 4 flows, and a second heat exchange unit through which the refrigerant guided from the evaporator 5 to the suction side of the compressor 2 flows. 12, and performs heat exchange between a relatively high temperature refrigerant flowing through the first heat exchange unit 11 and a relatively low temperature refrigerant flowing through the second heat exchange unit 12.
  • the internal heat exchanger 10 is an internal heat exchanger having a laminated structure in which the first heat exchange units 11 and the second heat exchange units 12 are alternately arranged in parallel, or constitutes the second heat exchange unit 12.
  • An internal heat exchanger having a double-pipe structure in which an inner pipe constituting the first heat exchange unit 11 is arranged inside the outer pipe may be used.
  • the pipe 61 connects the outlet of the compressor 2 and the inlet of the condenser 3 directly or indirectly.
  • the pipe 62 connects the outlet of the condenser 3 and the inlet of the first heat exchange unit 11 directly or indirectly.
  • the pipe 63 connects the outlet of the first heat exchange unit 11 and the inlet of the expansion device 4 directly or indirectly.
  • the pipe 64 connects the outlet of the expansion device 4 and the inlet of the evaporator 5 directly or indirectly.
  • the pipe 65 connects the outlet of the evaporator 5 and the inlet of the second heat exchange unit 12 directly or indirectly.
  • the pipe 66 connects the outlet of the second heat exchange unit 12 and the inlet of the compressor 2 directly or indirectly.
  • the thermal load detection device 40 is an outside air temperature detection device that detects the outside air temperature of the vehicle.
  • the heat load can be detected more appropriately.
  • the outside temperature detection device is, for example, an outside temperature sensor.
  • the thermal load detection device 40 is preferably a refrigerant state detection device that detects the pressure and temperature of the refrigerant between the evaporator 5 and the second heat exchange unit 12. Since the degree of superheat of the refrigerant flowing out of the evaporator 5 can be detected and the heat load that the refrigeration cycle is receiving at the present time can be suitably detected, a high coefficient of performance can be obtained stably.
  • the refrigerant state detection device is a device having a pressure detection unit that detects the pressure of the refrigerant and a temperature detection unit that detects the temperature of the refrigerant.
  • the pressure detection unit is, for example, a pressure sensor
  • the temperature detection unit is, for example, a temperature sensor.
  • the refrigerant state detection device includes, for example, a refrigerant outlet pipe (not shown) of the evaporator 5 or a pipe 65 that directly or indirectly connects the outlet of the evaporator 5 and the inlet of the second heat exchange unit 12. It is attached so that the refrigerant flowing inside and the measurement point are in contact.
  • the pressure sensor is attached so that the refrigerant flowing through the refrigerant outlet pipe or pipe 65 of the evaporator 5 is in contact with the refrigerant
  • the temperature sensor is attached to the refrigerant outlet pipe of the evaporator 5.
  • the heat exchange amount adjusting mechanism 50 is a mechanism that changes the heat exchange amount in the internal heat exchanger 10 according to the heat load of the refrigeration cycle 1. When the heat load is higher than the predetermined heat load, the heat exchange amount adjusting mechanism 50 suppresses the flow of the refrigerant in one or both of the first heat exchange unit 11 and the second heat exchange unit 12. It is preferable.
  • the heat exchange amount adjusting mechanism 50 is preferably, for example, the heat exchange amount adjusting mechanism of the first to third examples shown in FIGS.
  • FIG. 2 is a view for explaining the heat exchange amount adjusting mechanism of the first example.
  • the heat exchange amount adjusting mechanism of the first example includes (1) a first detour 151A that bypasses the first heat exchange section 11 and guides the refrigerant from the condenser 3 to the expansion device 4, or (2) the second An internal heat exchanger detour 151 having one or both of a second detour 151B that bypasses the heat exchange section 12 and guides the refrigerant from the evaporator 5 to the suction side of the compressor 2, and a refrigerant circuit 9 and the ratio controller 152 (152A, 152B) for changing the ratio of the refrigerant flowing through the internal heat exchanger bypass circuit 151 (151A, 151B) and the ratio controller 153 for controlling the ratio adjuster 152 (152A, 152B).
  • the ratio control device 153 preferably increases the ratio of the refrigerant flowing through the internal heat exchanger detours 151 (151A, 151B) when the heat load is higher
  • the internal heat exchanger detour 151 has both a first detour 151A and a second detour 151B (shown in FIG. 2), a first detour 151A, and In addition, a configuration without the second detour 151B (not shown) or a configuration without the first detour 151A and having the second detour 151B (not shown) is included. Of these, at least the second bypass 151B is preferred. That is, it is preferable that the heat exchange amount adjustment mechanism suppress the flow of the refrigerant in the second heat exchange unit 12. As the flow rate of the refrigerant flowing through the second heat exchange unit 12 is smaller, the amount of increase in passage resistance at the second heat exchange unit 12 is suppressed. And the suction pressure by the compressor 2 can be made smaller, and the motive power of the compressor 2 can be reduced more.
  • the first detour 151 ⁇ / b> A has one end connected to the pipe 62 and the other end connected to the pipe 63.
  • the second detour 151B has one end connected to the pipe 65 and the other end connected to the pipe 66.
  • the ratio adjusting means 152 is, for example, a three-way valve (shown in FIG. 2).
  • the ratio adjusting means 152 (152A, 152B) is a three-way valve
  • the three-way valve is connected to the connection point between the pipe 62 and the first detour 151A and / or the connection point between the pipe 65 and the second detour 151B.
  • the ratio adjusting means 152 (152A, 152B) is preferably an electromagnetic valve or a temperature sensitive valve, and more preferably a temperature sensitive valve.
  • the ratio adjusting unit 152A changes the ratio of the refrigerant flowing through the first heat exchange unit 11 and the first detour 151A.
  • the ratio adjusting means 152B changes the ratio of the refrigerant flowing through the second heat exchanging unit 12 and the second detour 151B.
  • the ratio control device 153 is a microcomputer including a CPU, a ROM, a RAM, and the like, for example.
  • the ratio control device 153 is preferably mounted on an air conditioning control unit (not shown) or mounted on an engine control unit.
  • Control by the ratio control device 153 will be described by taking as an example a case where the internal heat exchanger bypass route does not have the first bypass route 151A and has the second bypass route 151B.
  • the ratio control device 153 receives heat load information from the heat load detection device 40, and compares the heat load with a predetermined heat load (step 11).
  • the ratio control device 153 controls the ratio adjusting unit 152B to increase the ratio of the refrigerant flowing through the second bypass circuit 151B (step). 12). In step 12, the ratio control device 153 increases the ratio of the refrigerant flowing through the second detour 151B as the heat load increases. Further, depending on the value of the heat load, the refrigerant may not be allowed to flow through the second detour 151 ⁇ / b> B and the refrigerant may not be allowed to flow through the second heat exchange unit 12.
  • step 12 when the heat load is high, the ratio of the refrigerant flowing through the second heat exchange unit 12 is reduced, so that heat exchange in the internal heat exchanger 10 is suppressed. As a result, it is possible to prevent the degree of superheat of the refrigerant sucked by the compressor 2 from becoming too large.
  • the ratio control device 153 controls the ratio adjusting unit 152B to reduce the ratio of the refrigerant flowing through the second bypass route 151B. (Step 13).
  • step 13 it is preferable that the refrigerant flow through the second heat exchanging unit 12 and the refrigerant does not flow through the second bypass 151B.
  • the ratio of the refrigerant flowing through the second heat exchange unit 12 is increased, and the wetness of the refrigerant sucked by the compressor 2 can be lowered. For this reason, it is possible to reduce the proportion of liquid refrigerant mixed in the refrigerant sucked by the compressor 2 and to suppress an increase in power for driving the compressor 2.
  • FIG. 3 is a diagram for explaining the heat exchange amount adjusting mechanism of the second example.
  • the internal heat exchanger 10 includes an internal heat exchange unit in which the first heat exchange units 11a, 11b, and 11c and the second heat exchange units 12a, 12b, and 12c form a pair.
  • the internal heat exchange units 10A, 10B, 10C are respectively connected in parallel to the refrigerant circuit 9, and the heat exchange adjustment mechanism of the second example is the internal heat exchange unit 10A, A distribution degree adjusting means 252 (252A, 252B, 252C) for changing the distribution degree of the refrigerant flowing to each of 10B and 10C, a distribution degree control device 253 for controlling the distribution degree adjusting means 252 (252A, 252B, 252C), and The distribution degree control device 253 biases the distribution degree of the refrigerant flowing to each of the internal heat exchange units 10A, 10B, and 10C when the heat load is higher than the predetermined heat load. Door is preferable.
  • the internal heat exchange unit 10A includes a first heat exchange unit 11a and a second heat exchange unit 12a, and heat exchange of refrigerant between the first heat exchange unit 11a and the second heat exchange unit 12a. Is an internal heat exchanger.
  • the internal heat exchange unit 10B has a first heat exchange part 11b and a second heat exchange part 12b, and heat exchange of the refrigerant between the first heat exchange part 11b and the second heat exchange part 12b.
  • the internal heat exchange unit 10C includes a first heat exchange unit 11c and a second heat exchange unit 12c, and heat exchange of the refrigerant between the first heat exchange unit 11c and the second heat exchange unit 12c. Is an internal heat exchanger.
  • the internal heat exchange units 10A, 10B, 10C are connected in parallel to the refrigerant circuit 9.
  • the pipe 62 is branched into three and connected to the inlets of the first heat exchange parts 11a, 11b, and 11c
  • the pipe 63 is branched into three and the first heat exchange parts 11a, 11b and 11c are connected to the outlets.
  • the refrigerant flowing out of the condenser 3 is divided into a plurality of first heat exchange units 11a, 11b, and 11c and merged downstream of the first heat exchange units 11a, 11b, and 11c, so that the expansion device 4 Can lead to.
  • the pipe 65 is branched into three and connected to the inlets of the second heat exchange units 12a, 12b, and 12c, and the pipe 66 is branched into three and each of the first heat exchange units 12a, 12b, and 12c. Connected to the exit.
  • the refrigerant flowing out of the evaporator 5 is divided into a plurality of second heat exchange units 12a, 12b, and 12c, merged downstream of the second heat exchange units 12a, 12b, and 12c, and sent to the compressor 2. Can lead.
  • the number of the internal heat exchange units 10A, 10B, and 10C may be two or more, and the present invention is not limited to the number of internal heat exchange units.
  • FIG. 3 shows an example in which the number of internal heat exchange units 10A, 10B, and 10C is three as an example.
  • the distribution degree adjusting means 252 is a valve that opens and closes the circulation of the refrigerant that is heat-exchanged by the internal heat exchange units 10A, 10B, 10C, and is, for example, a stop valve.
  • the distribution degree adjusting unit 252 is provided in the second heat exchange units 12a, 12b, and 12c. It may be provided in the heat exchange units 11a, 11b, 11c, or may be provided in both the first heat exchange units 11a, 11b, 11c and the second heat exchange units 12a, 12b, 12c.
  • the heat exchange amount adjustment mechanism suppress the flow of the refrigerant in the first heat exchange unit 11.
  • the bias of the refrigerant flowing through the first heat exchange units 11a, 11b, and 11c increases, the increase in the degree of superheat of the refrigerant flowing through the second heat exchange unit 12 is suppressed.
  • the suction pressure by the compressor 2 can be made smaller, and the motive power of the compressor 2 can be reduced more.
  • the distribution degree control device 253 is a microcomputer including a CPU, a ROM, a RAM, and the like, for example.
  • the distribution degree control device 253 is preferably mounted on an air conditioning control unit (not shown) or mounted on an engine control unit.
  • the heat exchange adjustment mechanism of the second example is not paired with the first heat exchange unit, and the internal heat exchanger bypass pipe 67 through which the refrigerant guided from the evaporator 5 to the suction side of the compressor 2 flows, or the first 2 and / or an internal heat exchanger bypass pipe (not shown) through which the refrigerant guided from the condenser 3 to the expansion device 4 flows without being paired with the heat exchanger 2 and the internal heat exchanger bypass pipe It is preferable to further include a distribution degree adjusting means 252D for changing the flow rate of the refrigerant flowing to 67.
  • the control by the distribution degree control device 253 will be described by taking as an example a case where the distribution degree adjusting means 252 opens and closes the circulation of the refrigerant in the second heat exchange unit 12.
  • the distribution degree control device 253 receives heat load information from the heat load detection device 40, and compares the heat load with a predetermined heat load (step 21).
  • the distribution degree control device 253 controls the distribution degree adjusting means 252 (252A, 252B, 252C, 252D), and the internal heat exchange unit 10A. , 10B, and 10C, the distribution ratio of the refrigerant flowing to each of them is biased (step 22).
  • the distribution degree adjusting means 252A and 252B are opened, and the distribution degree adjusting means 252C and 252D are closed.
  • the internal heat exchange units 10A and 10B exchange heat of the refrigerant, but the internal heat exchange unit 10C does not exchange heat of the refrigerant.
  • the amount of heat exchange in the internal heat exchanger 10 is suppressed to about 2/3 as compared with the case where heat exchange is performed in all the internal heat exchange units 10A, 10B, and 10C. Further, when the distribution degree adjusting means 252A is opened and the distribution degree adjusting means 252B, 252C, 252D is closed, the heat exchange amount in the internal heat exchanger 10 is increased in heat in all the internal heat exchange units 10A, 10B, 10C. Compared to the case where the exchange is performed, it is suppressed to about 1/3.
  • the distribution degree control device 253 increases the number of distribution degree adjustment means 252A, 252B, and 252C to be closed in steps of one, two, and so on as the heat load increases. Also, the distribution degree adjusting means 252A, 252B, 252C are closed, the distribution degree adjusting means 252D is opened, and the internal heat exchanger 10 (internal heat exchange units 10A, 10B, 10C) compresses the refrigerant without performing heat exchange. You may flow to the machine 2.
  • step 22 when the heat load is high, heat exchange in the internal heat exchanger 10 is suppressed, and the degree of superheat of the refrigerant sucked by the compressor can be prevented from becoming too large.
  • the distribution degree control device 253 controls the distribution degree adjusting means 252 (252A, 252B, 252C, 252D) to control the internal heat exchange unit 10A. , 10B, and 10C are made uniform in the distribution degree of the refrigerant (step 23). That is, the distribution degree adjusting means 252A, 252B, and 253C are opened, and the distribution degree adjusting means 252D is closed. By step 23, the wetness of the refrigerant sucked by the compressor 2 can be lowered.
  • the distribution degree adjusting means 252 (252A, 252B, 252C, 252D) opens and closes the circulation of the refrigerant in the second heat exchange unit 12 has been described.
  • the distribution degree adjustment unit 252 ( 252A, 252B, 252C, 252D) performs the same control as in the case where the refrigerant flow in the second heat exchange unit 12 is opened and closed, thereby providing the same operational effects.
  • FIG. 4 is a view for explaining the heat exchange amount adjusting mechanism of the third example.
  • the heat exchange adjustment mechanism of the third example connects the refrigerant circuit 9 and the second heat exchange unit 12 at a plurality of positions, and the connection units T1, T2, and T3 are serially connected to the second heat exchange unit 12.
  • the connection pipe part 351 (351A, 351B, 351C) disposed in the pipe and the connection pipe part 351 (351A, 351B, 351C) are heat that changes the effective area for heat exchange in the second heat exchange part 12.
  • connection piping part 351 (351A, 351B, 351C) is connected to the plurality of connection parts S1, S2, S3 provided along the refrigerant flow direction of the pipe 65 and the refrigerant flow direction of the second heat exchange part 12. It is piping which connects the some connection part T1, T2, T3 provided along each.
  • One connection portion T1 among the connection portions T1, T2, and T3 provided in the second heat exchange portion 12 is on the upstream side in the refrigerant flow direction of the second heat exchange portion 12 (in this example, on the evaporator 5 side). ) Is preferably provided at the end.
  • the other connecting portions T2 and T3 are located in the middle of the second heat exchanging portion 12, for example, downstream of the connecting portion T1 (in this example, the compressor 2 side) and upstream of the downstream end. Provided.
  • the distances between the adjacent connecting portions T1, T2, T3 may be equal as shown in FIG. 4 or may be unequal.
  • the connection piping part 351 includes, for example, an upstream connection piping part 351A connected to an upstream end of the second heat exchange part 12 and a midstream connection piping part 351B connected in the middle of the second heat exchange part 12. And a downstream connection piping part 351C connected to the downstream side of the second connection piping part 351B.
  • the plurality of connection pipe portions 351A, 351B, 351C preferably do not cross each other, and more preferably are arranged in parallel to each other.
  • the heat exchange area adjusting means 352 is a valve that opens and closes the flow of the refrigerant in the connection pipe portion 351 (351A, 351B, 351C), and is, for example, a stop valve.
  • the effective area control device 353 is, for example, a microcomputer including a CPU, a ROM, a RAM, and the like.
  • the effective area control device 353 is preferably mounted on an air conditioning control unit (not shown) or mounted on an engine control unit.
  • the heat exchange adjustment mechanism of the third example is not connected to the second heat exchange unit, and the internal heat exchanger bypass pipe 68 through which the refrigerant guided from the evaporator 5 to the suction side of the compressor 2 flows, and the internal heat It is preferable to further include a heat exchange area adjusting unit 352D that changes the flow rate of the refrigerant flowing to the exchanger bypass pipe 68.
  • the internal heat exchanger 10 is an internal heat exchanger having a double tube structure.
  • the heat exchange adjustment mechanism of the third example connects the refrigerant circuit 9 and the second heat exchange unit 12 at a plurality of positions, and the connection units T1, T2, T3 with respect to the second heat exchange unit 12.
  • a connection pipe part hereinafter, also referred to as a second connection pipe part
  • the heat exchange adjustment mechanism of the third example connects the refrigerant circuit 9 and the first heat exchange unit 11 at a plurality of positions, and the connection unit is arranged in series with the first heat exchange unit 11. You may have 1 connection piping part (not shown).
  • the heat exchange adjustment mechanism does not have the first connection pipe part, but has the second connection pipe part 351 (shown in FIG. 4), the first connection pipe part, The form (not shown) which does not have the 2 connection piping part 351, or the form (not shown) which has both the 1st connection piping part and the 2nd connection piping part 351 is included.
  • it is preferable that it is a form which has the 2nd connection piping part 351 at least. That is, it is preferable that the heat exchange amount adjustment mechanism suppress the flow of the refrigerant in the second heat exchange unit 12. As the flow rate of the refrigerant flowing through the second heat exchange unit 12 is smaller, the amount of increase in passage resistance at the second heat exchange unit 12 is suppressed. And the suction pressure by the compressor 2 can be made smaller, and the motive power of the compressor 2 can be reduced more.
  • the control by the effective area control device 353 will be described by taking as an example the case of having the second connection pipe portion 351.
  • the effective area control device 353 receives heat load information from the heat load detection device 40, and compares the heat load with a predetermined heat load (step 31).
  • the effective area control device 353 controls the heat exchange area adjusting means 352 to reduce the effective area for heat exchange (step 32). ).
  • the heat exchange area adjustment means 352A of the upstream connection piping section 351A and the heat exchange area adjustment means 352C of the downstream connection piping section 351C are closed, and the heat exchange area adjustment means 352B of the midstream connection piping section 351B is opened. If it does so, the refrigerant
  • the effective area for heat exchange is a region downstream from the connection portion T3 of the second heat exchange section 12. Reduced to Thus, the effective area where heat exchange is performed can be changed by selecting the connection piping parts 351A, 351B, and 351C through which the refrigerant flows. The amount of heat exchange in the internal heat exchanger 10 can be suppressed as compared with the case where heat exchange is performed in the entire region of the internal heat exchanger 10.
  • the effective area control device 353 preferably reduces the effective area where heat exchange is performed as the heat load increases. For example, as the heat load increases, the effective area control device 353 shifts the heat exchange area adjustment means 352 to be opened from the upstream side to the downstream side like 352A, 352B, and 352C. Further, the heat exchange area adjusting means 352A, 352B, 352C may be closed and the heat exchange area adjusting means 352D may be opened, and the internal heat exchanger 10 may flow the refrigerant to the compressor 2 without performing heat exchange.
  • the effective area for heat exchange is reduced, and the superheat degree of the refrigerant sucked by the compressor 2 can be prevented from becoming too large.
  • the effective area control device 353 controls the heat exchange area adjusting means 352 to increase the effective area for heat exchange (step 33). ).
  • the heat exchange area adjustment means 352A of the upstream connection pipe section 351A is opened, and the heat exchange area adjustment means 352B and 352C of the midstream connection pipe section 351B and the downstream connection pipe section 351C are closed. If it does so, the refrigerant
  • connection part T1 connection part of the 2nd heat exchange part 12
  • FIG. 5 is a diagram showing the relationship between the degree of suppression of heat exchange and COP, (a) is a graph showing the relationship between thermal load and COP, and (b) shows the degree of inhibition of thermal load and heat exchange. It is a graph to show.
  • the horizontal axis indicates the heat load
  • the heat load increases as the distance from the vertical axis (the right side) increases
  • the vertical axis indicates the degree of suppression of heat exchange in the internal heat exchanger. The further away from the axis (upper side), the greater the degree of suppression.
  • a suppression degree of 0% means a state in which the internal heat exchanger 10 exhibits its inherent heat exchange capability.
  • a suppression degree of 100% means that the internal heat exchanger 10 does not perform any heat exchange.
  • Line 800 includes an internal heat exchanger and the degree of heat exchange suppression in a vehicle air conditioner (hereinafter referred to as a conventional vehicle air conditioner) that does not suppress heat exchange in the internal heat exchanger, line 900.
  • a conventional vehicle air conditioner a vehicle air conditioner
  • line 900 line 900.
  • , 901, 902 indicate the degree of suppression of heat exchange in the vehicle air conditioner according to this embodiment.
  • the horizontal axis is coaxial with the horizontal axis in FIG. 5B
  • the vertical axis indicates COP
  • the COP increases as the distance from the horizontal axis increases.
  • a line 80 indicates a COP when the line 800 is controlled
  • a line 90 indicates a COP when the lines 900, 901 and 902 are controlled.
  • the effect of the vehicle air conditioner which concerns on this embodiment is demonstrated.
  • heat exchange in the internal heat exchanger 10 is not suppressed as indicated by a line 800 in FIG. 5B, and therefore the degree of superheat of the refrigerant sucked into the compressor 2 as the heat load increases. Tends to grow.
  • the rate at which COP decreases as the thermal load increases.
  • the heat exchange amount adjusting mechanism of the first to third examples has a heat load as indicated by lines 900, 901, and 902 in FIG. when higher than a predetermined heat load h 0, suppresses heat exchange in the internal heat exchanger 10.
  • the rate at which the COP decreases even when the heat load increases becomes smaller than that of the conventional vehicle air conditioner (line 80).
  • the maximum value of the coefficient of performance is larger than that of the conventional vehicle air conditioner and is obtained on the higher heat load side than the conventional vehicle air conditioner.
  • both the conventional vehicle air conditioner and the vehicle air conditioner according to the present embodiment perform heat exchange with the internal heat exchanger, so that the compressor The wetness of the refrigerant to be sucked can be lowered.
  • the COP can be improved compared to the case where the vehicle air conditioner does not have an internal heat exchanger.
  • the vehicle air conditioner according to the present embodiment prevents an increase in the degree of superheat of the refrigerant sucked by the compressor when the heat load is high, and sucks the compressor when the heat load is low. The wetness of the refrigerant can be lowered, and a high coefficient of performance of the refrigeration cycle can be obtained stably.
  • the heat exchange amount adjusting mechanisms of the first to third examples control the degree of suppression of the heat exchange in the internal heat exchanger continuously or stepwise as the heat load increases. Includes a raised form.
  • the form in which the degree of suppression is continuously increased is, for example, a form in which the degree of suppression is increased to a straight line that rises to the right as shown by a line 900 in FIG. It is a form.
  • the ratio of the refrigerant flowing in the internal heat exchanger bypass circuit 151 (151A, 151B) is continuously changed in the heat exchange amount adjusting mechanism of the first example shown in FIG. It is a way to increase.
  • the form in which the degree of suppression is increased stepwise is, for example, a form in which the degree of suppression is increased in a stepped manner that rises to the right as shown by a line 902 in FIG.
  • FIG. 5 shows an example in which the height is increased to three stages as an example, the present invention is not limited to the number of stages.
  • a control method for increasing the degree of suppression stepwise is, for example, in the heat exchange amount adjusting mechanism of the first example shown in FIG. 2 in which the ratio of the refrigerant flowing in the internal heat exchanger detour 151 (151A, 151B) is stepwise.
  • the form of increasing the degree of suppression may be a combination of continuous and stepwise.
  • a control method for increasing the degree of suppression by a combination of continuous and stepwise is, for example, the refrigerant flowing in the internal heat exchanger bypass circuit 151 (151A, 151B) in the heat exchange amount adjusting mechanism of the first example shown in FIG. This is a method in which the ratio is increased continuously or stepwise.
  • the vehicle according to the present embodiment includes the vehicle air conditioner according to the present embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

Le problème selon la présente invention concerne un dispositif de climatisation de véhicule doté d'un échangeur de chaleur interne, l'invention visant à proposer un dispositif de climatisation de véhicule capable de maintenir un coefficient de performance élevé même en cas de fluctuations de la charge thermique, et concerne également un véhicule équipé du dispositif de climatisation de véhicule capable de maintenir un coefficient de performance élevé. La solution selon l'invention porte sur un dispositif de climatisation de véhicule comprenant : un cycle de réfrigération (1) qui comprend un circuit de réfrigérant (9) qui est configuré par un compresseur (2), un condenseur (3), un dispositif d'expansion (4) et un évaporateur (5) raccordés par des tuyaux (61 à 66) et faisant circuler un réfrigérant à travers ce dernier, et un échangeur de chaleur interne (10) qui réalise un échange de chaleur de réfrigérant entre un premier échangeur de chaleur (11) à travers lequel circule le réfrigérant devant être guidé vers le dispositif d'expansion (4) à partir du condenseur (3) et un second échangeur de chaleur (12) à travers lequel circule le réfrigérant devant être guidé vers le côté d'aspiration du compresseur (2) à partir de l'évaporateur (5) ; un dispositif de détection de charge thermique (40) qui détecte une charge thermique dans le cycle de réfrigération (1) ; et un mécanisme de réglage de quantité d'échange de chaleur (50) qui supprime l'échange de chaleur dans l'échangeur de chaleur interne (10) lorsque la charge thermique est supérieure à une charge thermique prédéterminée.
PCT/JP2017/015339 2016-04-19 2017-04-14 Dispositif de climatisation de véhicule et véhicule doté de ce dernier WO2017183588A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-083312 2016-04-19
JP2016083312A JP2017193212A (ja) 2016-04-19 2016-04-19 車両用空調装置及びそれを備える車両

Publications (1)

Publication Number Publication Date
WO2017183588A1 true WO2017183588A1 (fr) 2017-10-26

Family

ID=60115993

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/015339 WO2017183588A1 (fr) 2016-04-19 2017-04-14 Dispositif de climatisation de véhicule et véhicule doté de ce dernier

Country Status (2)

Country Link
JP (1) JP2017193212A (fr)
WO (1) WO2017183588A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3711984A4 (fr) * 2018-09-25 2021-12-29 Hangzhou Sanhua Research Institute Co., Ltd. Système de climatisation et procédé de commande associé

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7479115B2 (ja) * 2017-11-24 2024-05-08 富士電機株式会社 冷却装置
WO2019223612A1 (fr) 2018-05-23 2019-11-28 三花控股集团有限公司 Système de gestion thermique
JP2020019439A (ja) * 2018-08-02 2020-02-06 マレリ株式会社 車両用の空調装置
WO2024079852A1 (fr) * 2022-10-13 2024-04-18 三菱電機株式会社 Dispositif à cycle frigorifique

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11193967A (ja) * 1997-12-26 1999-07-21 Zexel:Kk 冷凍サイクル
JP2001001754A (ja) * 1999-06-24 2001-01-09 Japan Climate Systems Corp 車両用空調装置
JP2003214713A (ja) * 2002-01-23 2003-07-30 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2008008523A (ja) * 2006-06-28 2008-01-17 Hitachi Appliances Inc 冷凍サイクル及び温水器
JP2010526985A (ja) * 2007-05-14 2010-08-05 キャリア コーポレイション フラッシュタンクエコノマイザを備えた冷媒蒸気圧縮システム
WO2013080244A1 (fr) * 2011-11-29 2013-06-06 三菱電機株式会社 Dispositif de réfrigération/climatisation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11193967A (ja) * 1997-12-26 1999-07-21 Zexel:Kk 冷凍サイクル
JP2001001754A (ja) * 1999-06-24 2001-01-09 Japan Climate Systems Corp 車両用空調装置
JP2003214713A (ja) * 2002-01-23 2003-07-30 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2008008523A (ja) * 2006-06-28 2008-01-17 Hitachi Appliances Inc 冷凍サイクル及び温水器
JP2010526985A (ja) * 2007-05-14 2010-08-05 キャリア コーポレイション フラッシュタンクエコノマイザを備えた冷媒蒸気圧縮システム
WO2013080244A1 (fr) * 2011-11-29 2013-06-06 三菱電機株式会社 Dispositif de réfrigération/climatisation

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3711984A4 (fr) * 2018-09-25 2021-12-29 Hangzhou Sanhua Research Institute Co., Ltd. Système de climatisation et procédé de commande associé
US11828507B2 (en) 2018-09-25 2023-11-28 Hangzhou Sanhua Research Institute Co., Ltd. Air conditioning system and control method therefor

Also Published As

Publication number Publication date
JP2017193212A (ja) 2017-10-26

Similar Documents

Publication Publication Date Title
WO2017183588A1 (fr) Dispositif de climatisation de véhicule et véhicule doté de ce dernier
US9352634B2 (en) Air conditioner for a vehicle using a composite heat exchanger
JP6201434B2 (ja) 冷凍サイクル装置
JP5983335B2 (ja) 熱交換器
US20130213083A1 (en) Refrigeration cycle apparatus and refrigerant circulating method
US20080041079A1 (en) Refrigerant cycle device with ejector
US20130284415A1 (en) Refrigerant radiator
CN102933924A (zh) 热泵循环
WO2012077275A1 (fr) Climatiseur
WO2018110185A1 (fr) Système de circuit de fluide frigorigène et procédé de commande d'un tel système
JP2012153356A (ja) 冷媒放熱器
CN106796061A (zh) 二级升压式制冷循环装置
CN109642755A (zh) 制冷循环装置
JP2017121818A (ja) 冷却装置の制御装置
JP2017015299A (ja) 冷却装置
WO2017086343A1 (fr) Cycle de réfrigération pour dispositif de climatisation de véhicule, et véhicule équipé de celui-ci
JP4715797B2 (ja) エジェクタ式冷凍サイクル
JP5510374B2 (ja) 熱交換システム
JP2017137012A (ja) 車両用空調装置、それを備える車両及び車両用空調装置の制御方法
JP2017137011A (ja) 車両用空調装置、それを備える車両及び車両用グリル装置の制御方法
JP5556697B2 (ja) 冷媒放熱器
JP2015116934A (ja) ヒートポンプサイクル装置。
JP6891711B2 (ja) 複合型熱交換器
JP4835296B2 (ja) エジェクタ式冷凍サイクル
JP6714864B2 (ja) 冷凍サイクル装置

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17785926

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 17785926

Country of ref document: EP

Kind code of ref document: A1