Vehicle air conditioning system

Abstract

A vehicle air conditioning system (1) is provided with: a plurality of air conditioners (10) provided corresponding to each of a plurality of air conditioning areas; and a chiller (30) that cools a target device (BT) mounted on a vehicle. Each of the plurality of air conditioners includes a refrigeration cycle of a vapor compression type, and cools air blown out to the plurality of air conditioning areas by heat absorption due to evaporation of refrigerant. The chiller includes a cooling circuit (31) in which a heat medium that exchanges heat with the target device flows, and cools the heat medium using heat absorption in at least some of the plurality of air conditioners, thereby adjusting the temperature of the target device. Among the plurality of air conditioners, an air conditioner that air conditions a door side area is a door side air conditioner (10), and an air conditioner that air conditions a panel side area is a panel side air conditioner (20). At this time, the amount of heat absorption from the heat medium when the device temperature of the target device is adjusted by the plurality of air conditioners respectively performing cooling of the room and the target device is smaller for the panel side air conditioner than for the door side air conditioner.

Description

[0001] The present invention is based on Japanese Patent Application No. 2020-102380 filed on June 12, 2020, the contents of which are incorporated herein by reference. Technical Field

[0002] The present invention relates to a vehicle air conditioning system for conditioning the interior of a vehicle. Background Art

[0003] Conventionally, there is known an air conditioning system that uses the heat absorption effect of a refrigeration cycle included in an air conditioner to perform air conditioning in a vehicle interior and temperature control of a battery (see, for example, Patent Document 1).

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Application Laid-Open No. 2015-186989

[0007] The present inventors have studied a vehicle air conditioning system that cools vehicle-mounted equipment using an air conditioner, in which a room is divided into a plurality of air conditioning zones and air conditioning is performed in the plurality of air conditioning zones using a plurality of air conditioners provided for each of the plurality of air conditioning zones.

[0008] However, when cooling onboard equipment using multiple air conditioners, the heat absorbed by the onboard equipment limits the amount of heat absorbed from the room by the multiple air conditioners, making it impossible to ensure indoor comfort as desired. For example, air-conditioned areas farther from the vehicle's doors are less easily ventilated and more humid than areas near the vehicle's doors. Therefore, if the amount of heat absorbed from the room by the multiple air conditioners is limited due to cooling of the onboard equipment, the humidity in the air-conditioned areas farther from the vehicle's doors will be higher, reducing indoor comfort. These findings were discovered by the inventors after careful research. Summary of the Invention

[0009] An object of the present invention is to ensure comfort in an air-conditioned area away from a vehicle door even when cooling a target device in a vehicle air-conditioning system including a plurality of air conditioners for performing indoor air conditioning.

[0010] According to one aspect of the present invention,

[0011] Vehicle air conditioning system, comprising:

[0012] a plurality of air conditioners provided corresponding to each of the plurality of air conditioning areas; and

[0013] a cooling machine for cooling a target device mounted on a vehicle,

[0014] Each of the plurality of air conditioners includes a refrigeration cycle of a vapor compression type, and cools air blown out to the plurality of air conditioning zones by heat absorption due to evaporation of a refrigerant,

[0015] The cooling machine includes a cooling circuit in which a heat medium flows to exchange heat with the target device, and cools the heat medium using heat absorption in at least some of the plurality of air conditioners, thereby adjusting the temperature of the target device,

[0016] In the plurality of air conditioners, when an air conditioner that air conditions a door side zone separated from the outside by a door of the vehicle is a door side air conditioner, and an air conditioner that air conditions a panel side zone separated from the outside by a side panel member of the vehicle is a panel side air conditioner, the amount of heat absorption from the heat medium when the target device is temperature controlled by the plurality of air conditioners respectively cooling the indoor and temperature controlling the target device is smaller in the panel side air conditioner than in the door side air conditioner.

[0017] Accordingly, in the panel side air conditioner, since the amount of heat absorption from the heat medium is suppressed, the amount of heat absorption from air blown out to the panel side zone is large, and a dehumidification effect based on air cooling is easily obtained. Therefore, even when the target device is cooled, comfort in an air conditioning zone far from the door of the vehicle can be ensured.

[0018] Here, the side panel member is a panel member that constitutes a side surface of the vehicle. Further, according to the vehicle, an emergency exit for passengers to escape from the vehicle in an emergency and an opening and closing member that opens and closes the emergency exit are provided. The opening and closing member of the emergency exit constitutes a side surface of the vehicle in a state where the emergency exit is closed in an emergency. Therefore, in the present application, the emergency exit and the opening and closing member are a part of the side panel member. That is, the side panel member of the vehicle in which the emergency exit and the opening and closing member are provided includes the emergency exit and the opening and closing member.

[0019] In addition, the bracketed reference symbols attached to each structural element and the like indicate an example of a correspondence relationship with a specific structural element and the like described in the embodiments described below. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 is a schematic view of a bus vehicle to which the air conditioning system of the first embodiment is applied.

[0021] Figure 2 is an explanatory view for explaining the bus vehicle to which the air conditioning system of the first embodiment is applied.

[0022] Figure 3 is a schematic configuration view of the air conditioning system of the first embodiment.

[0023] Figure 4These are explanatory diagrams for explaining the differences between the door-side air conditioner and the panel-side air conditioner of the air conditioning system according to the first embodiment.

[0024] Figure 5 It is an explanatory diagram for explaining a first modified example of a bus vehicle to which the air conditioning system according to the first embodiment is applied.

[0025] Figure 6 This is a schematic diagram for explaining a second modified example of a bus vehicle to which the air conditioning system according to the first embodiment is applied.

[0026] Figure 7 This is an explanatory diagram for explaining a bus vehicle to which the air conditioning system according to the second embodiment is applied.

[0027] Figure 8 It is an explanatory diagram for explaining a first modified example of a bus vehicle to which the air conditioning system according to the second embodiment is applied.

[0028] Figure 9 It is an explanatory diagram for explaining a second modified example of a bus vehicle to which the air conditioning system according to the second embodiment is applied.

[0029] Figure 10 It is an explanatory diagram for explaining a third modified example of a bus vehicle to which the air conditioning system according to the second embodiment is applied.

[0030] Figure 11 This is an explanatory diagram for explaining a bus vehicle to which the air conditioning system according to the third embodiment is applied.

[0031] Figure 12 It is an explanatory diagram for explaining a first modified example of a bus vehicle to which the air conditioning system according to the third embodiment is applied.

[0032] Figure 13 It is an explanatory diagram for explaining a second modified example of a bus vehicle to which the air conditioning system according to the third embodiment is applied.

[0033] Figure 14 It is an explanatory diagram for explaining a third modified example of a bus vehicle to which the air conditioning system according to the third embodiment is applied.

[0034] Figure 15 It is a schematic configuration diagram of an air-conditioning system according to a fourth embodiment.

[0035] Figure 16 This is a flowchart showing the flow of processing executed when the control device of the air-conditioning system according to the fourth embodiment starts temperature adjustment of the device.

[0036] Figure 17 This is a flowchart showing the flow of processing executed when the control device of the air-conditioning system according to the fourth embodiment stops temperature control of the device.

[0037] Figure 18 are different explanatory diagrams for explaining the door-side air conditioning machine and the panel-side air conditioning machine of the air conditioning system of the fourth embodiment.

[0038] Figure 19 is an explanatory diagram for explaining a first modification example of the bus vehicle to which the air conditioning system of the fourth embodiment is applied.

[0039] Figure 20 is an explanatory diagram for explaining a second modification example of the bus vehicle to which the air conditioning system of the fourth embodiment is applied.

[0040] Figure 21 is an explanatory diagram for explaining a third modification example of the bus vehicle to which the air conditioning system of the fourth embodiment is applied.

[0041] Figure 22 is a schematic configuration diagram of the air conditioning system of the fifth embodiment.

[0042] Figure 23 are different explanatory diagrams for explaining the first cooling pipe and the second cooling pipe of the air conditioning system of the fifth embodiment.

[0043] Figure 24 represents a first modification example of the air conditioning system of the fifth embodiment, and represents a schematic view of a portion of the first cooling pipe that can be used in the cooling circuit.

[0044] Figure 25 represents a first modification example of the air conditioning system of the fifth embodiment, and represents a schematic view of a portion of the second cooling pipe that can be used in the cooling circuit.

[0045] Figure 26 represents a first modification example of the air conditioning system of the fifth embodiment, and is an explanatory diagram for explaining the first cooling pipe and the second cooling pipe.

[0046] Figure 27 represents a second modification example of the air conditioning system of the fifth embodiment, and represents a schematic view of a portion of the first cooling pipe that can be used in the cooling circuit portion.

[0047] Figure 28 represents a second modification example of the air conditioning system of the fifth embodiment, and represents a schematic view of a portion of the second cooling pipe that can be used in the cooling circuit portion.

[0048] Figure 29 represents a third modification example of the air conditioning system of the fifth embodiment, and represents a schematic view of a portion of the cooling pipe that can be used in the cooling circuit.

[0049] Figure 30 represents a third modification example of the air conditioning system of the fifth embodiment, and is an explanatory diagram for explaining the first cooling pipe and the second cooling pipe.

[0050] Figure 31 It is a schematic diagram of a bus vehicle to which the air conditioning system according to the sixth embodiment is applied.

[0051] Figure 32 It is a schematic configuration diagram of an air-conditioning system according to a sixth embodiment.

[0052] Figure 33 This is a flowchart showing the flow of processing executed when the control device of the air-conditioning system according to the seventh embodiment starts temperature adjustment of the device.

[0053] Figure 34 This is a flowchart showing the flow of processing executed when the control device of the air-conditioning system according to the seventh embodiment stops temperature regulation of the device.

[0054] Figure 35 It is a schematic configuration diagram showing a portion of a door-side air conditioner according to an eighth embodiment.

[0055] Figure 36 It is a schematic configuration diagram showing a portion of a panel-side air conditioner according to an eighth embodiment.

[0056] Figure 37 It is an explanatory diagram for explaining the pressure loss of the door side air conditioner and the panel side air conditioner according to the eighth embodiment.

[0057] Figure 38 It is an explanatory diagram for explaining a modified example of the eighth embodiment. DETAILED DESCRIPTION

[0058] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. Furthermore, in the following embodiments, portions identical or equivalent to those described in the preceding embodiments are denoted by the same reference numerals, and their descriptions may be omitted. Furthermore, when only a portion of a component is described in an embodiment, the components described in the preceding embodiments may apply to the remaining components. In the following embodiments, in particular, as long as no hindrance is created in the combination, even without specific indication, portions of the embodiments may be combined with one another.

[0059] (First embodiment)

[0060] Reference Figures 1 to 4 This embodiment will be described. In this embodiment, an example in which the vehicle air conditioning system of the present invention is applied to an air conditioning system 1 of a bus V will be described. Figure 1 、 Figure 2The arrows shown in FIG. 1 and FIG. 2 are for indicating the vertical direction DR1 of the bus vehicle V, the arrows indicating the front and rear directions DR2 of the bus vehicle V, and the arrows indicating the left and right directions DR3 of the bus vehicle V.

[0061] like Figure 1 and Figure 2 As shown, in a bus vehicle V, boarding and alighting ports E1 and E2 are provided at two locations, one in the front portion and the other in the center, on the side surface on the left side in the width direction DR3. Doors D1 and D2 are provided at each of the boarding and alighting ports E1 and E2. These doors D1 and D2 are doors that passengers open and close when boarding or alighting. Doors D1 and D2 are folding-door doors. Alternatively, doors D1 and D2 may be swing-door doors, sliding-door doors, or the like.

[0062] The bus V has no access doors on the right side of the width direction DR3. Instead, the entire right side of the width direction DR3 is covered by a side panel SP. The side panel SP forms the side of the bus V. This allows the bus V to be accessed from the left side of the width direction DR3. Furthermore, in the present invention, windows, emergency exit doors, and other components provided on the side of the bus V constitute part of the side panel SP.

[0063] The bus vehicle V is configured as an electric vehicle that travels using electric energy as a driving source. The bus vehicle V is equipped with a traveling motor MG and a battery BT that stores electric power supplied to the traveling motor MG.

[0064] The battery BT is composed of a series connection body in which a plurality of chargeable and dischargeable battery cells are electrically connected in series. Alternatively, the battery BT may be configured by connecting some of the plurality of battery cells in parallel.

[0065] The battery BT is connected to a power converter (not shown) and a traction motor MG. The power converter converts DC current supplied from the battery BT into AC current, and supplies the AC current to various electrical loads such as the traction motor MG.

[0066] The battery BT is arranged on the roof of the bus vehicle V. Specifically, the battery BT is installed on the roof panel RP of the bus vehicle V. By arranging the battery BT on the roof, the floor level of the bus vehicle V can be reduced, making it easier for passengers to get on and off.

[0067] The battery BT is a heat-generating device installed in a bus V. While the bus V is in motion, the battery BT generates heat, for example when supplying power, and this can lead to excessively high temperatures. Furthermore, even when the battery BT is parked in the summer, it can reach excessive temperatures. Excessively high battery BT temperatures accelerate cell degradation, significantly reducing battery life. Therefore, the battery BT temperature must be controlled to prevent it from reaching excessive temperatures.

[0068] In addition, the bus vehicle V can adjust the temperature of the battery BT by using the equipment for indoor air conditioning. In other words, the air conditioning system 1 of the bus vehicle V is not only configured to perform indoor air conditioning, but also to adjust the temperature of the battery BT with the battery BT as the target equipment.

[0069] like Figure 2 As shown, in a bus V, multiple air-conditioned zones Z are set up inside the bus V. Specifically, two air-conditioned zones Z are set up inside the bus V: a door-side zone Zd on the left side of the interior and a panel-side zone Zp on the right side of the interior. The door-side zone Zd is an air-conditioned zone Z inside the bus V that is separated from the outside by doors D1 and D2. The panel-side zone Zp is an air-conditioned zone Z inside the bus V that is separated from the outside by side panels SP.

[0070] The air conditioning system 1 is provided with a plurality of air conditioners 10 and 20 corresponding to each of the plurality of air conditioning zones Z. That is, the air conditioning system 1 is provided with a door-side air conditioner 10 corresponding to the door-side zone Zd and a panel-side air conditioner 20 corresponding to the panel-side zone Zp. Figure 3 As shown, each of the door-side air conditioner 10 and the panel-side air conditioner 20 includes a vapor compression refrigeration cycle RC1 or RC2.

[0071] The door-side air conditioner 10 includes a first compressor 11, a first radiator 12, a first indoor expansion valve 13, a first indoor evaporator 14, a first equipment expansion valve 15, a first equipment evaporator 16, a first indoor on-off valve 17, and a first equipment on-off valve 18. The panel-side air conditioner 20 includes a second compressor 21, a second radiator 22, a second indoor expansion valve 23, and a second indoor evaporator 24.

[0072] The first compressor 11 and the second compressor 21 compress and discharge refrigerant. The first compressor 11 and the second compressor 21 are electric compressors whose compression mechanisms are driven by electric motors. The refrigerant discharge capacity of the first compressor 11 and the second compressor 21 is controlled based on control signals from the control device 100, described later.

[0073] The first and second heat radiators 12 and 22 are devices that radiate refrigerant discharged from the first and second compressors 11 and 21 to the outside. The first and second heat radiators 12 and 22 have a condensing portion 121, 221, a receiver portion 122, 222, and a subcooling portion 123, 223, so that refrigerant on the outlet side becomes a subcooled state having a subcooling degree. The condensing portion 121, 221 is a heat exchanger that condenses refrigerant while radiating the refrigerant to the outside. The receiver portion 122, 222 is a gas-liquid separator that separates refrigerant after the condensing portion 121, 221, while storing refrigerant remaining in the cycle. The subcooling portion 123, 223 is a heat exchanger that cools liquid refrigerant stored in the receiver portion 122, 222 by radiating the refrigerant to the outside.

[0074] The first and second indoor expansion valves 13 and 23 are pressure reducing portions that reduce the pressure of refrigerant passing through the first and second heat radiators 12 and 22 to a desired pressure to expand the refrigerant. The first and second indoor expansion valves 13 and 23 are constituted by temperature type expansion valves that adjust the degree of throttling so that the degree of superheat of the refrigerant outlet side of the first and second indoor evaporators 14 and 24 becomes a predetermined value. Further, the first and second indoor expansion valves 13 and 23 are not limited to mechanical expansion valves, and can be constituted by electric expansion valves.

[0075] The first and second indoor evaporators 14 and 24 are heat exchangers that evaporate refrigerant reduced in pressure by the first and second indoor expansion valves 13 and 23. The first and second indoor fans 141 and 241 are provided in the first and second indoor evaporators 14 and 24. The first and second indoor fans 141 and 241 are constituted by electric fans that rotate impellers by electric motors.

[0076] The first indoor fan 141 is a supply fan that blows air to the door side region Zd. The first indoor evaporator 14 evaporates refrigerant reduced in pressure by the first indoor expansion valve 13 by exchanging heat with air blown from the first indoor fan 141. That is, the first indoor evaporator 14 absorbs heat from air before being blown to the door side region Zd to evaporate the refrigerant. Thus, air cooled and dehumidified in the first indoor evaporator 14 is blown toward the door side region Zd.

[0077] The second indoor fan 241 is a supply fan that blows air to the board side area Zp. The second indoor evaporator 24 causes the refrigerant that is decompressed at the second indoor expansion valve 23 to exchange heat with the air blown from the second indoor fan 241 to evaporate the refrigerant. That is, the second indoor evaporator 24 absorbs heat from the air before the air is blown to the board side area Zp to evaporate the refrigerant. Thus, the air that is cooled and dehumidified at the second indoor evaporator 24 is blown toward the board side area Zp.

[0078] Here, the door side air conditioner 10 is provided with a first equipment expansion valve 15 and a first equipment evaporator 16. The first equipment expansion valve 15 and the first equipment evaporator 16 are provided in parallel with the first indoor expansion valve 13 and the first indoor evaporator 14 with respect to the refrigerant flow.

[0079] The first equipment expansion valve 15 is a decompression portion that decompresses the refrigerant after the first radiator 12 to a desired pressure to expand the refrigerant. The first equipment expansion valve 15 is provided in a refrigerant pipe branched from a refrigerant pipe connecting the first radiator 12 and the first indoor expansion valve 13. The first equipment expansion valve 15 is provided in parallel with the first indoor expansion valve 13 with respect to the refrigerant flow. The first equipment expansion valve 15 is constituted by a temperature type expansion valve that adjusts the opening degree in such a manner that the degree of superheat of the refrigerant outlet side of the first equipment evaporator 16 becomes a predetermined value. Further, the first equipment expansion valve 15 is not limited to a mechanical type expansion valve, but can be constituted by an electric type expansion valve.

[0080] The first equipment evaporator 16 is a cooler that evaporates the refrigerant that is decompressed at the first equipment expansion valve 15. The first equipment evaporator 16 has a refrigerant flow path 161 in which the refrigerant that is decompressed at the first equipment expansion valve 15 flows, and a heat medium flow path 162 in which a heat medium that circulates in a cooling circuit 31 described later flows.

[0081] The first equipment evaporator 16 causes the refrigerant flowing in the refrigerant flow path 161 to exchange heat with the heat medium flow path 162 to evaporate the refrigerant. The heat medium flowing in the heat medium flow path 162 is cooled by absorbing heat from the refrigerant flowing in the refrigerant flow path 161.

[0082] Although not shown, an evaporating pressure adjusting valve that adjusts the pressure in one of the first indoor evaporator 14 and the first equipment evaporator 16 to a desired pressure is provided at the refrigerant outlet side of the evaporator. Thus, the pressures of the refrigerants of the first indoor evaporator 14 and the first equipment evaporator 16 can be adjusted in accordance with the respective heat loads.

[0083] The door-side air conditioner 10 is provided with a first indoor-side on-off valve 17 and a first equipment-side on-off valve 18. The first indoor-side on-off valve 17 and the first equipment-side on-off valve 18 function as flow path switching valves that switch the flow path of the refrigerant after passing through the first radiator 12. The first indoor-side on-off valve 17 and the first equipment-side on-off valve 18 are solenoid valves and are controlled by a control signal from a control device 100, described later.

[0084] The first indoor on-off valve 17 is provided in the refrigerant piping that guides the refrigerant, after passing through the first radiator 12, to the first indoor expansion valve 13. The first indoor on-off valve 17 is a switching unit that switches between allowing the refrigerant to flow to the first indoor evaporator 14 and blocking the flow of the refrigerant to the first indoor evaporator 14.

[0085] First equipment-side on-off valve 18 is provided in the refrigerant piping that guides the refrigerant, after passing through first radiator 12, to first equipment-use expansion valve 15. First equipment-side on-off valve 18 is a door-side switching unit that switches between a first allowing state, which allows the refrigerant to flow to first equipment-use evaporator 16, and a first blocking state, which blocks the refrigerant from flowing to first equipment-use evaporator 16.

[0086] On the other hand, the panel-side air conditioner 20 only includes the second indoor evaporator 24, which absorbs heat from the air blown into the room, and does not include a heat absorber that absorbs heat from the heat medium. In other words, the panel-side air conditioner 20 does not include a structure equivalent to the first equipment expansion valve 15 and the first equipment evaporator 16.

[0087] The air conditioning system 1 is equipped with a cooling unit 30 including the aforementioned cooling circuit 31. The cooling unit 30 cools the battery BT as the target device. The cooling unit 30 utilizes the heat absorption effect of some of the air conditioners 10 and 20 to cool the heat medium, thereby regulating the temperature of the battery BT. For example, an antifreeze solution containing ethylene glycol can be used as the heat medium.

[0088] The cooling device 30 includes a cooling circuit 31 for circulating a heat medium. The cooling circuit 31 includes a circulation pump 32, a heat medium flow path 162 of the first equipment evaporator 16, a three-way valve 33, a battery cooling unit 34, and a radiator 35.

[0089] The circulation pump 32 is an electric pump that pumps the heat medium to the heat medium flow path 162 of the first equipment evaporator 16. The pumping capacity of the circulation pump 32 is controlled by a control signal from a control device 100 described later.

[0090] The outlet side of the heat medium flow path 162 of the first equipment evaporator 16 is connected to the inlet of a three-way valve 33. The three-way valve 33 has one inlet and two outlets, that is, it is an electrically operated three-way flow control valve that can selectively open and close the two outlets. The three-way valve 33 is controlled by a control signal from the control device 100, described later.

[0091] One outlet side of the three-way valve 33 is connected to the inlet of the battery cooling unit 34. The battery cooling unit 34 has a plurality of heat exchange flow paths arranged in contact with the plurality of battery cells constituting the battery BT, and cools the battery BT by exchanging heat between the heat medium flowing through the heat exchange flow paths and the battery cells.

[0092] Such a battery cooling unit 34 can be realized by disposing heat exchange channels between adjacent battery cells. Alternatively, the battery cooling unit 34 can be formed integrally with the battery BT by providing heat exchange channels in a case that houses the battery cells.

[0093] The other outlet side of the three-way valve 33 is connected to the inlet of the radiator 35. The radiator 35 is a heat exchanger that exchanges heat between the heat medium that has passed through the first equipment evaporator 16 and the outside air to dissipate heat.

[0094] The battery cooler 34 and the radiator 35 are connected to the suction port of the circulation pump 32 via a confluence provided at the outlet side of the battery cooler 34 and the radiator 35. The battery cooler 34 and the radiator 35 are connected in parallel with the heat medium flow.

[0095] Next, we will describe the control device 100, which serves as the electronic control unit of the air conditioning system 1. The control device 100 is composed of a processor, a computer with memory, and its peripheral circuits. The control device 100 performs various calculations and processes according to programs stored in the memory, controlling the devices connected to its output. The memory of the control device 100 is composed of a non-transitory tangible storage medium.

[0096] The output side of the control device 100 is connected to the first compressor 11, the first indoor fan 141, the first indoor on-off valve 17, the first equipment-side on-off valve 18, the second compressor 21, the second indoor fan 241, the circulation pump 32, and the three-way valve 33. In this embodiment, the software and hardware for controlling the door-side air conditioner 10 and the panel-side air conditioner 20 in the control device 100 constitute the air conditioning control unit 100a.

[0097] A sensor group 101 for air conditioning control and battery temperature control is connected to the control device 100 on its input side. This sensor group 101 includes an interior temperature sensor, an exterior temperature sensor, a sunlight sensor, a PT sensor for detecting the pressure and temperature at the refrigerant outlet of each evaporator 14, 16, and 24, and a battery temperature sensor for detecting the temperature of the battery BT. Detection signals from the sensor group 101 are input to the control device 100. This allows the air conditioning system 1 to adjust the temperature of the air supplied to the room and the temperature of the battery BT, among other parameters, based on the physical quantities detected by the sensor group 101.

[0098] An operation panel 102, which can be used for various input operations, is connected to the input side of the control device 100. The operation panel 102 is located near the instrument panel and has various operation switches. Operation signals from the various operation switches provided on the operation panel 102 are input to the control device 100.

[0099] The various operating switches on the operation panel 102 include an automatic switch, an operating mode switch, an air volume setting switch, a temperature setting switch, and a blow mode switch. The air conditioning system 1 receives input from the operation panel 102 and switches the operating mode of the air conditioning system 1 as appropriate. Specifically, the control device 100 controls the first indoor-side on-off valve 17 and the first equipment-side on-off valve 18 to change the refrigerant flow pattern of the door-side air conditioner 10, thereby switching the operating mode of the air conditioning system 1.

[0100] The following describes the operation of the air conditioning system 1. The air conditioning system 1 is configured to perform both indoor cooling and device temperature control as operating modes. Indoor cooling is an operating mode in which the door-side air conditioner 10 and the panel-side air conditioner 20 cool the room. Device temperature control is an operating mode in which the door-side air conditioner 10 and the panel-side air conditioner 20 cool the room and control the temperature of the battery BT, respectively. The following describes the operation of the air conditioning system 1 in both indoor cooling and device temperature control modes.

[0101] <Indoor cooling>

[0102] Indoor cooling is an operation mode in which air cooled to a desired temperature by the first and second indoor evaporators 14 and 24 is blown into the interior of the bus vehicle V. Indoor cooling is performed by the air conditioning system 1 when the operation mode is set to cooling mode by the operation mode changeover switch, for example.

[0103] The control device 100 uses detection signals from the sensor group 101 and operation signals from the operation panel 102 to appropriately determine the operating states of various devices during indoor cooling. For example, the control device 100 controls the on-off valves 17 and 18 to open the first indoor-side on-off valve 17 and close the first device-side on-off valve 18. The control device 100 uses detection signals from the sensor group 101 and operation signals from the operation panel 102 to appropriately determine control signals for other devices, such as the compressors 11 and 21 and the indoor fans 141 and 241.

[0104] When the door-side air conditioner 10 is cooling the room, the high-pressure refrigerant discharged from the first compressor 11 flows into the condenser 121 of the first radiator 12, releasing heat. After passing through the condenser 121, the refrigerant flows into the liquid receiving section 122, where it undergoes gas-liquid separation. Furthermore, the liquid refrigerant separated in the liquid receiving section 122 flows into the subcooling section 123, releasing heat.

[0105] The refrigerant flowing out of the subcooling unit 123 flows into the first indoor expansion valve 13, where it is decompressed to the desired pressure. Furthermore, during indoor cooling, the first equipment-side on-off valve 18 is closed, so the refrigerant does not flow into the first equipment expansion valve 15, and the entire amount of the refrigerant is decompressed in the first indoor expansion valve 13.

[0106] The refrigerant, after being decompressed by the first indoor expansion valve 13, flows into the first indoor evaporator 14. The refrigerant flowing into the first indoor evaporator 14 absorbs heat from the air supplied by the first indoor fan 141 and evaporates. In other words, the refrigerant flowing into the first indoor evaporator 14 absorbs heat from the air before being blown out to the door-side area Zd and evaporates. As a result, the air cooled to the desired temperature by the first indoor evaporator 14 is blown out from the door-side area Zd.

[0107] The refrigerant having passed through the first indoor evaporator 14 is sucked into the first compressor 11. The refrigerant sucked into the first compressor 11 is compressed again in the first compressor 11 to become a high-pressure refrigerant.

[0108] On the other hand, in the panel-side air conditioner 20, similar to the door-side air conditioner 10, the high-pressure refrigerant discharged from the second compressor 21 flows into the condenser section 221 of the second radiator 22, releasing heat. The refrigerant after passing through the condenser section 221 flows into the liquid receiving section 222, where it is separated into gas and liquid. Furthermore, the liquid refrigerant separated in the liquid receiving section 222 flows into the subcooling section 223, releasing heat.

[0109] The refrigerant flowing out of the subcooling unit 223 flows into the second indoor expansion valve 23 and is decompressed to a desired pressure in the second indoor expansion valve 23. The refrigerant decompressed in the second indoor expansion valve 23 flows into the second indoor evaporator 24.

[0110] The refrigerant flowing into the second indoor evaporator 24 absorbs heat from the air supplied by the second indoor fan 241 and evaporates. Specifically, the refrigerant flowing into the second indoor evaporator 24 absorbs heat from the air before being blown out to the plate-side area Zp and evaporates. As a result, the air cooled to a desired temperature by the second indoor evaporator 24 is blown out from the plate-side area Zp.

[0111] The refrigerant having passed through the second indoor evaporator 24 is sucked into the second compressor 21. The refrigerant sucked into the second compressor 21 is compressed again in the second compressor 21 to become a high-pressure refrigerant.

[0112] As described above, when cooling the room, the air cooled by the first indoor evaporator 14 is blown out to the door side area Zd, while the air cooled by the second indoor evaporator 24 is blown out to the panel side area Zp, thereby achieving indoor cooling.

[0113] <Equipment Temperature Control>

[0114] Equipment temperature control is an operating mode in which air cooled to a desired temperature by the first and second indoor evaporators 14, 24 is blown into the interior of the bus vehicle V while utilizing the refrigerant's latent heat of evaporation to adjust the temperature of the battery BT, the target equipment. Equipment temperature control is executed by the air conditioning system 1 when the temperature of the battery BT exceeds the upper limit of the appropriate temperature, for example, when the automatic switch is turned on. The conditions for executing equipment temperature control may also differ from those described above.

[0115] The control device 100 uses detection signals from the sensor group 101 and operation signals from the operation panel 102 to appropriately determine the operating states of various devices during device temperature control. For example, the control device 100 controls the on-off valves 17 and 18 to open the first indoor-side on-off valve 17 and the first device-side on-off valve 18. The control device 100 controls the three-way valve 33 so that the entire amount of heat medium passing through the heat medium flow path 162 of the first device evaporator 16 flows to the battery cooling unit 34. The control device 100 uses detection signals from the sensor group 101 and operation signals from the operation panel 102 to appropriately determine control signals for other devices, such as the compressors 11 and 21, the indoor fans 141 and 241, and the circulation pump 32.

[0116] During equipment cooling, in the door-side air conditioner 10, the high-pressure refrigerant discharged from the first compressor 11 flows into the first radiator 12 to dissipate heat, similar to the indoor cooling operation. The refrigerant flowing out of the radiator 12 flows into the first indoor expansion valve 13 and the first equipment expansion valve 15.

[0117] The refrigerant flowing into the first indoor expansion valve 13 is decompressed to a desired pressure by the first indoor expansion valve 13 and then flows into the first indoor evaporator 14. The refrigerant flowing into the first indoor evaporator 14 absorbs heat from the air supplied by the first indoor fan 141 and evaporates. As a result, the air cooled to a desired temperature by the first indoor evaporator 14 is blown out into the door-side area Zd.

[0118] The refrigerant having passed through the first indoor evaporator 14 is sucked into the first compressor 11. The refrigerant sucked into the first compressor 11 is compressed again in the first compressor 11 to become a high-pressure refrigerant.

[0119] The refrigerant flowing into the first equipment expansion valve 15 is decompressed to a desired pressure by the first equipment expansion valve 15 and then flows into the first equipment evaporator 16. The refrigerant flowing into the first equipment evaporator 16 absorbs heat from the heat medium flowing through the cooling circuit 31 and evaporates. As a result, the heat medium flowing through the cooling circuit 31 is cooled as it passes through the heat medium flow path 162 of the first equipment evaporator 16.

[0120] The refrigerant having passed through the first indoor evaporator 14 and the refrigerant having passed through the first equipment evaporator 16 are sucked into the first compressor 11. The refrigerant sucked into the first compressor 11 is compressed again in the first compressor 11 to become a high-pressure refrigerant.

[0121] Here, the heat medium cooled in the first device evaporator 16 flows to the battery cooling unit 34, where it absorbs heat from the battery BT. This cools the battery BT. Specifically, during device temperature control, the battery BT is cooled by the heat absorbed by the evaporation of the refrigerant in the first device evaporator 16.

[0122] Meanwhile, in the panel-side air conditioner 20, similar to when cooling the room, the high-pressure refrigerant discharged from the second compressor 21 flows into the second radiator 22 to release heat. The refrigerant flowing out of the second radiator 22 flows into the second indoor expansion valve 23, where it is decompressed to the desired pressure. The refrigerant decompressed in the second indoor expansion valve 23 flows into the second indoor evaporator 24.

[0123] The refrigerant flowing into the second indoor evaporator 24 absorbs heat from the air supplied by the second indoor fan 241 and evaporates. Specifically, the refrigerant flowing into the second indoor evaporator 24 absorbs heat from the air before being blown out to the plate-side area Zp and evaporates. As a result, the air cooled to a desired temperature by the second indoor evaporator 24 is blown out from the plate-side area Zp.

[0124] The refrigerant having passed through the second indoor evaporator 24 is sucked into the second compressor 21. The refrigerant sucked into the second compressor 21 is compressed again in the second compressor 21 to become a high-pressure refrigerant.

[0125] As described above, during equipment temperature control, the air cooled by the indoor evaporators 14 and 24 is blown out to the zones Zd and Zp, while the heat medium cooled by the first equipment evaporator 16 is supplied to the battery cooling unit 34, thereby achieving indoor cooling and cooling of the battery BT.

[0126] The air conditioning system 1 described above is configured to divide the interior of a bus vehicle V into multiple air-conditioning zones Z. Multiple air conditioners 10 and 20 are provided for each of the multiple air-conditioning zones Z to provide air conditioning in the multiple air-conditioning zones Z. Specifically, the bus vehicle V is provided with one or more doors D on one side in the width direction DR3 and side panels SP on the other side in the width direction. A door-side zone Zd is defined on one side in the width direction DR3, and a panel-side zone Zp is defined on the other side in the width direction DR3. This ensures that conditioned air tailored to each air-conditioning zone Z is provided, ensuring indoor comfort.

[0127] Here, in the air-conditioned area Z, the panel-side area Zp away from the doors D1 and D2 of the bus vehicle V is difficult to ventilate and has a high humidity compared to the door-side area Zd near the doors D1 and D2 of the bus vehicle V.

[0128] Taking this into consideration, in the air conditioning system 1 of this embodiment, the door side air conditioner 10 includes the first equipment evaporator 16, and the panel side air conditioner 20 does not include a heat absorber that absorbs heat from the heat medium. Figure 4 As shown, the amount of heat absorbed from the heat medium during device temperature control is smaller in the panel-side air conditioner 20 than in the door-side air conditioner 10 .

[0129] Since the panel-side air conditioner 20 does not absorb heat from the heat medium during temperature control, the amount of heat absorbed by the air blown into the panel-side area Zp is increased, facilitating a dehumidification effect through air cooling. In other words, the panel-side air conditioner 20 can concentrate the heat absorption effect of the refrigeration cycle RC2 on the air blown into the panel-side area Zp. Therefore, even when cooling the battery BT, comfort can be maintained in the panel-side area Zp, which is away from the doors D1 and D2 of the bus vehicle V. In other words, the air conditioning system 1 can ensure comfort in air-conditioned areas that cannot be ventilated by opening and closing the entry and exit doors E1 and E2.

[0130] (Modification of the first embodiment)

[0131] In the first embodiment, the bus vehicle V is shown as having the boarding and alighting ports E1 and E2 and the doors D1 and D2 provided at two locations, the front portion and the center portion, on the left side surface in the width direction DR3. However, the bus vehicle V is not limited thereto.

[0132] The bus vehicle V may be provided with a door on one side of the width direction DR3, and a side panel SP may be provided on the other side. Figure 5 As shown, a boarding / entry port E1 and a door D1 may be provided at a location in the front portion of the side surface on the left side in the width direction DR3. In this case, a door-side area Zd is defined at the front of the interior, and a panel-side area Zp is defined at the rear of the interior. The door-side air conditioner 10 provides air conditioning in the door-side area Zd, while the panel-side air conditioner 20 provides air conditioning in the panel-side area Zp. This provides the same effects as the first embodiment. Furthermore, the bus vehicle V may also be provided with one or more doors on the side surface on the right side in the width direction DR3, for example.

[0133] For example, the bus vehicle V may be provided with one or more doors on one of the front or rear sides of the side surfaces in the width direction DR3, and a side panel SP may be provided on the other side. Figure 6 As shown, the bus V may be provided with boarding and exiting ports E1 and E2 and doors D1 and D2 at two locations in the front portion of the side surfaces on both sides in the width direction DR3. In this case, a door-side area Zd is defined at the front of the interior and a panel-side area Zp is defined at the rear of the interior. The door-side air conditioner 10 simultaneously air-conditions the door-side area Zd and the panel-side air conditioner 20 simultaneously air-conditions the panel-side area Zp, achieving the same effects as the first embodiment. For example, the bus V may also be provided with doors at the rear of the interior on both sides of the side surfaces in the width direction DR3.

[0134] (Second embodiment)

[0135] Next, refer to Figure 7 The second embodiment will be described. In this embodiment, the differences from the first embodiment will be mainly described.

[0136] In this embodiment, an example in which the air conditioning system 1 is applied to a bus vehicle V having air conditioning zones Z set at four locations, front, back, left, and right, will be described. Figure 7 As shown, in a bus vehicle V, boarding and exiting ports E1 and E2 and doors D1 and D2 are provided at two locations, one in the front portion and the other in the center portion, on the side surface on the left side in the width direction DR3. Four air-conditioned zones Z are defined in the bus vehicle V: a first door-side zone Zd1 on the left side of the interior, a second door-side zone Zd2 on the rear side, and a first panel-side zone Zp1 on the right side of the interior, and a second panel-side zone Zp2 on the rear side.

[0137] In the air conditioning system 1, a first door-side air conditioner 10A, a second door-side air conditioner 10B, a first panel-side air conditioner 20A, and a second panel-side air conditioner 20B are provided for each of the four air-conditioned zones Z. Each of the door-side air conditioners 10A and 10B has the same configuration as the door-side air conditioner 10 described in the first embodiment. Furthermore, each of the panel-side air conditioners 20A and 20B has the same configuration as the panel-side air conditioner 20 described in the first embodiment.

[0138] The other structures are the same as those of the first embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the first embodiment, as in the first embodiment.

[0139] Since the air conditioning system 1 of this embodiment has air conditioning zones Z set at four locations in the front, back, left, and right of the room, it can provide air conditioning air suitable for each space in the front, back, left, and right of the room, thereby fully ensuring indoor comfort.

[0140] (Modification of the Second Embodiment)

[0141] In the second embodiment, the bus V is exemplified as having boarding and alighting ports E1 and E2 and doors D1 and D2 provided at two locations, the front portion and the center portion, on the left side surface in the width direction DR3. However, the bus V is not limited to this.

[0142] For example, the bus vehicle V may be provided with one or more doors on one of the front or rear sides of the side surfaces in the width direction DR3, and a side panel SP may be provided on the other side. Figure 8 As shown, a bus V may be provided with boarding and exiting ports E1 and E2 and doors D1 and D2 at two locations in the front portion of the side surfaces on both sides in the width direction DR3. In this case, a first door-side zone Zd1 and a second door-side zone Zd2 are provided at the front of the interior, and door-side air conditioners 10A and 10B are used to air condition these zones, respectively, providing conditioned air suitable for the front portion of the interior, similarly to the second embodiment. Furthermore, a first panel-side zone Zp1 and a second panel-side zone Zp2 are provided at the rear portion of the interior, and panel-side air conditioners 20A and 20B are used to air condition these zones, respectively, providing conditioned air suitable for the rear portion of the interior, similarly to the second embodiment. Furthermore, the bus V may also be provided with one or more doors in the rear portion of the side surfaces on both sides in the width direction DR3.

[0143] For example, the bus vehicle V may be provided with a door on one side surface in the width direction DR3 and a side panel SP may be provided on the other side surface.

[0144] Specifically, if Figure 9As shown, a bus V may be provided with a boarding / entry port E1 and a door D1 at a location in the front portion of the left side of the vehicle in the width direction DR3. In this case, a door-side zone Zd is defined at the front left side of the room, and the door-side air conditioner 10 is used to air condition the door-side zone Zd, providing conditioned air suitable for the space in the front left side of the room. Furthermore, a first panel-side zone Zp1 is defined at the front left side of the room, and a second panel-side zone Zp2 and a third panel-side zone Zp3 are defined at the rear of the room. The panel-side air conditioners 20A, 20B, and 20C then air condition the panel-side zones Zp1, Zp2, and Zp3, respectively, providing conditioned air suitable for each location in the room.

[0145] Moreover, the bus V is Figure 10 As shown, a boarding and alighting port E1 and a door D1 may be provided at a location in the rear portion of the side surface on the left side in the width direction DR3. In this case, a door-side area Zd is set at the rear of the left side of the room, and the door-side air conditioner 10 is used to perform air conditioning on the door-side area Zd, thereby providing air-conditioned wind suitable for the space at the rear of the left side of the room. In addition, a first panel-side area Zp1 and a second panel-side area Zp2 are set at the front of the room, and a third panel-side area Zp3 is set at the rear of the right side of the room. Then, each panel-side air conditioner 20A, 20B, 20C is used to perform air conditioning on each panel-side area Zp1, Zp2, and Zp3, thereby providing air-conditioned wind suitable for various places in the room. In addition, the bus vehicle V may also be provided with one or more doors on the side surface on the right side in the width direction DR3, for example.

[0146] (Third embodiment)

[0147] Next, refer to Figure 11 In this embodiment, the differences from the second embodiment will be mainly described.

[0148] In this embodiment, an example in which the air conditioning system 1 is applied to a bus vehicle V in which air conditioning zones Z are set at three locations on both sides of the interior in the width direction DR3 will be described. Figure 11 As shown, the bus V has boarding and alighting ports E1, E2, and E3 and doors D1, D2, and D3 at three locations: the front, center, and rear of the side surface on the left side of the bus V in the width direction DR3. Three air-conditioned zones Z are defined on the left side of the interior of the bus V: a first door-side area Zd1 located in the front, a second door-side area Zd2 located in the rear, and a third door-side area Zd3 located in the center. Furthermore, three air-conditioned zones Z are defined on the right side of the interior: a first panel-side area Zp1 located in the front, a second panel-side area Zp2 located in the rear, and a third panel-side area Zp3 located in the center.

[0149] In the air conditioning system 1, a first door-side air conditioner 10A, a second door-side air conditioner 10B, a third door-side air conditioner 10C, a first panel-side air conditioner 20A, a second panel-side air conditioner 20B, and a third panel-side air conditioner 20C are provided for each of the six air-conditioning zones Z. Each of the door-side air conditioners 10A, 10B, and 10C has the same configuration as the door-side air conditioner 10 described in the first embodiment. Furthermore, each of the panel-side air conditioners 20A, 20B, and 20C has the same configuration as the panel-side air conditioner 20 described in the first embodiment.

[0150] The other structures are the same as those of the second embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the first and second embodiments, as in the first and second embodiments.

[0151] Since the air conditioning system 1 of this embodiment is provided with three air conditioning areas Z on both sides of the indoor width direction DR3, it can provide air conditioning wind suitable for the front, back, left, right and center spaces of the room, thereby fully ensuring indoor comfort.

[0152] (Modification of the Third Embodiment)

[0153] In the third embodiment, as for the bus vehicle V, although it is shown that the boarding and alighting ports E1, E2, E3 and doors D1, D2, D3 are provided at three locations, namely the front part, the center part and the rear part, on the side surface on the left side in the width direction DR3, the bus vehicle V is not limited to this.

[0154] For example, a bus V Figure 12 As shown, doors D1 and D2 may be provided at the front and rear of the left side surface in the width direction DR3, and side panels SP may be provided at the center of the left side surface and the right side surface. In this case, a first door-side zone Zd1 is defined at the front of the left side of the room, and a second door-side zone Zd2 is defined at the rear. Door-side air conditioners 10A and 10B air condition these door-side zones Zd1 and Zd2, providing conditioned air suitable for the front and rear of the left side of the room. Furthermore, a first panel-side zone Zp1 is defined at the center of the left side of the room, a second panel-side zone Zp2 is defined at the front of the right side of the room, a third panel-side zone Zp3 is defined at the rear, and a fourth panel-side zone Zp4 is defined at the center. Panel-side air conditioners 20A, 20B, 20C, and 20D air condition these panel-side zones Zp1, Zp2, Zp3, and Zp4, providing conditioned air suitable for the center of the left side of the room and the right side of the room. In addition, the bus vehicle V may be provided with one or more doors on the side surface on the right side in the width direction DR3, for example.

[0155] Moreover, a bus vehicle V is as follows Figure 13As shown, in the side surface of the left side of the width direction DR3, doors Dl, D2 are provided in the front and central portions, and side plates SP are provided in the rear portion of the left side and the right side. At this time, a first door side region Zd1 is set in the front of the left side in the room, and a second door side region Zd2 is set in the central portion. The air in each door side region Zd1, Zd2 is adjusted by the door side air conditioning machines 10A, 10B, and air conditioning air suitable for the front of the left side in the room and the central portion can be provided. Further, a first panel side region Zpl is set in the rear of the left side in the room. A second panel side region Zp2 is set in the front of the right side in the room, a third panel side region Zp3 is set in the rear of the right side, and a fourth panel side region Zp4 is set in the central portion. The air in each panel side region Zpl, Zp2, Zp3, Zp4 is adjusted by the panel side air conditioning machines 20A, 20B, 20C, 20D, and air conditioning air suitable for the central portion of the left side in the room and the right side in the room can be provided. Further, the bus vehicle V can be provided with one or more doors on the right side of the width direction DR3, for example.

[0156] Further, the bus vehicle V can be provided with one or more doors on the right side of the width direction DR3, for example. Figure 14 As shown, in the side surface of the left side of the width direction DR3, doors Dl, D2 are provided in the front and central portions, and side plates SP are provided in the rear portion of the left side and the right side. At this time, a first door side region Zd1 is set in the front of the left side in the room, and a second door side region Zd2 is set in the central portion. The air in each door side region Zd1, Zd2 is adjusted by the door side air conditioning machines 10A, 10B, and air conditioning air suitable for the front of the left side in the room and the central portion can be provided. Further, a first panel side region Zpl is set in the rear of the left side in the room. A second panel side region Zp2 is set in the front of the right side in the room, a third panel side region Zp3 is set in the rear of the right side, and a fourth panel side region Zp4 is set in the central portion. The air in each panel side region Zpl, Zp2, Zp3, Zp4 is adjusted by the panel side air conditioning machines 20A, 20B, 20C, 20D, and air conditioning air suitable for the central portion of the left side in the room and the right side in the room can be provided. Further, the bus vehicle V can be provided with one or more doors on the right side of the width direction DR3, for example.

[0157] (Fourth Embodiment)

[0158] Next, the fourth embodiment will be described with reference to Figures 15 to 17 The fourth embodiment will be described. In the present embodiment, the main description will be given for the different parts from the first embodiment.

[0159] The air conditioning system 1 of the present embodiment is provided with a heat absorber that absorbs heat from the heat medium in the door side air conditioning machine 10X and the panel side air conditioning machine 20X. The door side air conditioning machine 10X of the present embodiment is configured in the same manner as the one described in the first embodiment, and thus the description of the door side air conditioning machine 10X will be omitted.

[0160] As shown in FIG. 6, the bus vehicle V is provided with a door Dl on the left side of the width direction DR3, and a door D2 on the right side of the width direction DR3. Further, the bus vehicle V is provided with a side plate SP on the left side of the width direction DR3, and a side plate SP on the right side of the width direction DR3. Figure 15As shown, the panel-side air conditioner 20X of this embodiment is provided with a second equipment expansion valve 25 and a second equipment evaporator 26. The second equipment expansion valve 25 and the second equipment evaporator 26 are provided in parallel with the second indoor expansion valve 23 and the second indoor evaporator 24 with respect to the refrigerant flow.

[0161] The second equipment expansion valve 25 is a decompression unit that reduces the refrigerant pressure after passing through the second radiator 22 to a desired pressure, thereby causing it to expand. The second equipment expansion valve 25 is located in a refrigerant pipe that branches off from the refrigerant pipe connecting the second radiator 22 and the second indoor expansion valve 23. The second equipment expansion valve 25 is arranged in parallel with the second indoor expansion valve 23 relative to the refrigerant flow. The second equipment expansion valve 25 is a temperature-type expansion valve that adjusts the throttling opening so that the superheat on the refrigerant outlet side of the second equipment evaporator 26 reaches a predetermined value. Furthermore, the second equipment expansion valve 25 is not limited to a mechanical expansion valve and may also be an electric expansion valve.

[0162] The second equipment evaporator 26 is a cooler that evaporates the refrigerant whose pressure has been reduced by the second equipment expansion valve 25. The second equipment evaporator 26 includes a refrigerant flow path 261 through which the refrigerant whose pressure has been reduced by the second equipment expansion valve 25 flows, and a heat medium flow path 262 through which the heat medium circulates in the cooling circuit 31, described later, flows.

[0163] The second equipment evaporator 26 evaporates the refrigerant by exchanging heat between the refrigerant flowing in the refrigerant flow path 261 and the heat medium flow path 262. The heat medium flowing in the heat medium flow path 262 absorbs heat from the refrigerant flowing in the refrigerant flow path 261 and is cooled.

[0164] Although not shown, an evaporation pressure regulating valve is provided on the refrigerant outlet side of one of the second indoor evaporator 24 and the second equipment evaporator 26 to adjust the pressure in the evaporator to a desired pressure. This allows the refrigerant pressures in the second indoor evaporator 24 and the second equipment evaporator 26 to be adjusted according to their respective heat loads.

[0165] The panel-side air conditioner 20 is provided with a second indoor-side on-off valve 27 and a second equipment-side on-off valve 28. The second indoor-side on-off valve 27 and the second equipment-side on-off valve 28 function as flow path switching valves that switch the flow path of the refrigerant after passing through the second radiator 22. The second indoor-side on-off valve 27 and the second equipment-side on-off valve 28 are solenoid valves and are controlled by a control signal from the control device 100, which will be described later.

[0166] The second indoor on-off valve 27 is provided in the refrigerant piping that guides the refrigerant, after passing through the second radiator 22, to the second indoor expansion valve 23. The second indoor on-off valve 27 is a switching unit that switches between a state in which the refrigerant is allowed to flow to the second indoor evaporator 24 and a state in which the refrigerant is blocked from flowing to the second indoor evaporator 24.

[0167] The second equipment-side on-off valve 28 is provided in the refrigerant piping that guides the refrigerant passing through the second radiator 22 to the second equipment expansion valve 25. The second equipment-side on-off valve 28 is a door-side switching unit that switches between a second allowing state, which allows the refrigerant to flow to the second equipment evaporator 26, and a second blocking state, which blocks the refrigerant from flowing to the second equipment evaporator 26.

[0168] Cooling circuit 31A of chiller 30 is equipped with a circulation pump 32, heat medium flow path 162 for first equipment evaporator 16, heat medium flow path 262 for second equipment evaporator 26, a three-way valve 33, a battery cooler 34, and a radiator 35. In cooling circuit 31A, downstream of circulation pump 32, first equipment evaporator 16 and second equipment evaporator 26 are connected in series with respect to the heat medium flow.

[0169] Specifically, the second equipment evaporator 26 is located downstream of the heat medium flow of the first equipment evaporator 16 in the cooling circuit 31A, allowing the heat medium that has passed through the first equipment evaporator 16 to flow in. That is, the heat medium inlet side of the second equipment evaporator 26 is connected to the outlet side of the first equipment evaporator 16.

[0170] In the air-conditioning system 1 constructed in this way, the control device 100 controls the indoor side opening and closing valves 17, 27 and the equipment side opening and closing valves 18, 28 to change the flow mode of the refrigerant of the door side air conditioner 10X and the panel side air conditioner 20X, thereby switching the operation mode of the air-conditioning system 1.

[0171] The control device 100 of this embodiment controls the opening and closing valves 17, 18, 27, and 28 during indoor cooling so that the first indoor side opening and closing valve 17 and the second indoor side opening and closing valve 27 are opened and the first equipment side opening and closing valve 18 and the second equipment side opening and closing valve 28 are closed.

[0172] Furthermore, when adjusting the temperature of the equipment, the control device 100 controls the opening and closing valves 17, 18, 27, and 28 so that the first indoor side opening and closing valve 17, the second indoor side opening and closing valve 27, the first equipment side opening and closing valve 18, and the second equipment side opening and closing valve 28 are respectively opened.

[0173] The control device 100 executes, for example, at the start of the device temperature control Figure 16 This process is part of the startup process that is executed when the device is temperature-controlled. Figure 16The control program shown is executed periodically or irregularly by control device 100 .

[0174] like Figure 16 As shown, in step S100, the control device 100 reads various signals input from the sensor group 101, the operation panel 102, and the like. Next, in step S110, the control device 100 determines whether the temperature of the battery BT exceeds a predetermined high-temperature threshold THth. The high-temperature threshold THth is set to a desired temperature at which cooling of the battery BT is to begin. For example, the high-temperature threshold THth is set at the upper limit of the appropriate temperature of the battery BT. The determination process in step S110 may also be different from that described above.

[0175] When the temperature of the battery BT is higher than the high temperature threshold value THth, the control device 100 switches the first and second equipment-side on-off valves 18 and 28 to open states at substantially the same timing in step S120 .

[0176] The control device 100 exits this process after controlling the device-side on-off valves 18 and 28. If the temperature of the battery BT becomes lower than the high-temperature threshold value THth in step S110, the control device 100 skips step S120 and exits this process.

[0177] Furthermore, the control device 100 executes, for example, when the temperature control of the device is stopped. Figure 17 This process is part of the stop process that is executed when the device is temperature-controlled. Figure 17 The control program shown is executed periodically or irregularly by the control device 100 .

[0178] like Figure 17 As shown, in step S200, the control device 100 reads various signals input from the sensor group 101, the operation panel 102, and the like. Next, in step S210, the control device 100 determines whether the temperature of the battery BT is lower than a predetermined low-temperature threshold TLth. The low-temperature threshold TLth is set to a desired temperature at which cooling of the battery BT is stopped. For example, the low-temperature threshold TLth is set at the lower limit of the appropriate temperature of the battery BT. The determination process in step S210 may also be different from that described above.

[0179] When the temperature of the battery BT is lower than the low temperature threshold TLth, the control device 100 controls the facility valves 18 and 28 in step S220 to close the first facility valve 18 and the second facility valve 28 at substantially the same timing.

[0180] The control device 100 exits this process after controlling the equipment-side on-off valves 18 and 28. If the temperature of the battery BT is equal to or higher than the low-temperature threshold TLth in step S210, the control device 100 skips step S220 and exits this process.

[0181] By executing the above-described process, in the panel-side air conditioner 20X, during the equipment temperature adjustment, the refrigerant flowing out of the second radiator 22 flows into the second indoor expansion valve 23 and the second equipment expansion valve 25 .

[0182] The refrigerant flowing into the second indoor expansion valve 23 is decompressed to a desired pressure in the second indoor expansion valve 23 and then flows into the first indoor evaporator 14. The refrigerant flowing into the second indoor evaporator 24 absorbs heat from the air supplied by the second indoor fan 241 and evaporates. As a result, the air cooled to a desired temperature by the second indoor evaporator 24 is blown out into the plate side area Zp.

[0183] Meanwhile, the refrigerant flowing into the second equipment expansion valve 25 is decompressed to a desired pressure by the second equipment expansion valve 25 and then flows into the second equipment evaporator 26. The refrigerant flowing into the second equipment evaporator 26 absorbs heat from the heat medium flowing through the cooling circuit 31A and evaporates. As a result, the heat medium flowing through the cooling circuit 31A is cooled as it passes through the heat medium flow path 262 of the second equipment evaporator 26.

[0184] The refrigerant having passed through the second indoor evaporator 24 and the refrigerant having passed through the second equipment evaporator 26 are sucked into the second compressor 21. The refrigerant sucked into the second compressor 21 is compressed again in the second compressor 21 to become a high-pressure refrigerant.

[0185] Here, the heat medium cooled by the second device evaporator 26 flows to the battery cooling unit 34, where it absorbs heat from the battery BT. This cools the battery BT. In other words, during device temperature control, the battery BT is cooled by absorbing heat not only from the first device evaporator 16 but also from the second device evaporator 26.

[0186] As described above, during equipment temperature control, the air cooled by the indoor evaporators 14 and 24 is blown out to the zones Zd and Zp, while the heat medium cooled by the equipment evaporators 16 and 26 is supplied to the battery cooling unit 34 to cool the room and the battery BT.

[0187] The other structures are the same as those of the first embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the first embodiment, as in the first embodiment.

[0188] In the air conditioning system 1 of this embodiment, the first and second equipment evaporators 16 and 26 are arranged in series with respect to the heat medium flow in the cooling circuit 31A. This allows the heat medium cooled in each of the equipment evaporators 16 and 26 to be supplied to the battery cooling unit 34, thereby enabling sufficient cooling of the battery BT.

[0189] In particular, the second equipment evaporator 26 is positioned in the cooling circuit 31 downstream of the heat medium flow of the first equipment evaporator 16, allowing the heat medium to flow in after passing through the first equipment evaporator 16. Consequently, the heat medium flowing into the second equipment evaporator 26 is lower in temperature than that flowing into the first equipment evaporator 16. Consequently, the temperature difference between the heat medium before and after the evaporator is smaller than that in the first equipment evaporator 16. Consequently, the amount of heat absorbed from the heat medium during equipment temperature control is smaller in the second equipment evaporator 26 than in the first equipment evaporator 16.

[0190] Therefore, the panel side air conditioner 20X is as follows Figure 18 As shown, during temperature control, since the amount of heat absorbed by the heat medium is smaller than that of the door-side air conditioner 10X, the amount of heat absorbed by the air blown into the panel-side area Zp is greater, facilitating the dehumidification effect achieved through air cooling. Therefore, even when cooling the battery BT, comfort can be maintained in the panel-side area Zp, which is away from the doors D1 and D2 of the bus vehicle V. In other words, the air conditioning system 1 can ensure comfort in air-conditioned areas that cannot be ventilated by opening and closing the entry and exit doors E1 and E2.

[0191] (Modification of the Fourth Embodiment)

[0192] In the fourth embodiment, although the bus vehicle V to which the air conditioning system 1 is applied is not particularly described, the bus vehicle V may be, for example, Figure 19 As shown in FIG, it can also be constructed in the same manner as the first embodiment. Figure 20 The structure shown is the same as the second embodiment, and can also be as shown in FIG. Figure 21 The bus vehicle V may be configured similarly to the modified example of the first embodiment, the modified example of the second embodiment, or the modified example of the third embodiment. This also applies to the subsequent embodiments.

[0193] (Fifth embodiment)

[0194] Next, refer to Figure 22 、 Figure 23 In this embodiment, the differences from the fourth embodiment will be mainly described.

[0195] like Figure 22 As shown, in the cooling circuit 31B of the chiller 30 , downstream of the circulation pump 32 , the first device evaporator 16 and the second device evaporator 26 are connected in parallel with respect to the heat medium flow.

[0196] Cooling circuit 31B includes a first cooling pipe 311 that directs heat medium toward first equipment evaporator 16, and a second cooling pipe 312 that directs heat medium toward second equipment evaporator 26. Cooling circuit 31B branches into first cooling pipe 311 and second cooling pipe 312 downstream of circulation pump 32. The branched first cooling pipe 311 and second cooling pipe 312 merge immediately before three-way valve 33.

[0197] Specifically, the first cooling pipe 311 and the second cooling pipe 312 are connected to a branch portion 313 provided upstream of the heat medium flow of the first and second equipment evaporators 16 and 26 . The branch portion 313 is provided downstream of the circulation pump 32 .

[0198] Furthermore, the first cooling pipe 311 and the second cooling pipe 312 are connected to a merging portion 314 provided downstream of the heat medium flows of the first and second equipment evaporators 16 and 26 . The merging portion 314 is provided upstream of the three-way valve 33 .

[0199] Compared to the first cooling pipe 311, the second cooling pipe 312 is configured to experience greater pressure loss during heat medium flow. Specifically, a resistor 315 is provided to obstruct the flow of heat medium, resulting in greater pressure loss in the second cooling pipe 312 compared to the first cooling pipe 311. The resistor 315 can be formed, for example, from an orifice or a capillary tube. The resistor 315 is positioned downstream of the second equipment evaporator 26 in the second cooling pipe 312. Alternatively, the resistor 315 can be positioned upstream of the second equipment evaporator 26 in the second cooling pipe 312, or integrated with the second equipment evaporator 26.

[0200] The other structures are the same as those of the fourth embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the fourth embodiment, as in the fourth embodiment.

[0201] In the air conditioning system 1 of this embodiment, the first and second equipment evaporators 16 and 26 are arranged in parallel with respect to the heat medium flow in the cooling circuit 31B. This allows the heat medium cooled in the equipment evaporators 16 and 26 to be supplied to the battery cooling unit 34, thereby enabling sufficient cooling of the battery BT.

[0202] In particular, the second cooling pipe 312 is different from the first cooling pipe 311 and is provided with a resistor 315. Figure 23As shown, the pressure loss is larger than that of the first cooling pipe 311 .

[0203] The second cooling pipe 312 configured in this manner has a smaller flow rate of the heat medium than the first cooling pipe 311. As a result, the second equipment evaporator 26 absorbs less heat from the heat medium than the first equipment evaporator 16.

[0204] Therefore, during temperature control, the panel-side air conditioner 20X absorbs less heat from the heat medium, resulting in a greater amount of heat absorbed by the air blown into the panel-side area Zp, facilitating a dehumidification effect through air cooling. Consequently, even when cooling the battery BT, comfort can be maintained in the panel-side area Zp, which is away from the doors D1 and D2 of the bus vehicle V. In other words, the air conditioning system 1 ensures comfort in air-conditioned areas that cannot be ventilated by opening and closing the entry and exit doors E1 and E2.

[0205] (Modification of the Fifth Embodiment)

[0206] In the fifth embodiment, the resistor 315 is added to the second cooling pipe 312 to increase the pressure loss of the second cooling pipe 312 . However, this structure may be achieved by other means.

[0207] For example, Figure 24 and Figure 25 As shown, the bending angle θ2 of the bent portion 312a of the second cooling pipe 312 can be set larger than the bending angle θ1 of the bent portion 311a of the first cooling pipe 311, and the above-mentioned structure can also be achieved. Figure 26 As shown, the sum of the bending angles θ2 of the second cooling pipes 312 is set to be larger than the sum of the bending angles θ1 of the first cooling pipes 311 , thereby achieving a structure that increases the pressure loss of the second cooling pipes 312 .

[0208] Again, for example Figure 27 and Figure 28 As shown, the above-mentioned structure can also be achieved by setting the curvature radius R2 of the arc-shaped curved portion 312b in the second cooling pipe 312 to be smaller than the curvature radius R1 of the arc-shaped curved portion 311b in the first cooling pipe 311.

[0209] Furthermore, for example Figure 29 and Figure 30 As shown, the above-mentioned structure may be realized by setting the effective length L / D represented by the ratio of the tube length to the tube inner diameter to be a structure in which the second cooling tube 312 is larger than the first cooling tube 311.

[0210] (Sixth embodiment)

[0211] Next, refer to Figure 31、 Figure 32 The sixth embodiment will be described. In this embodiment, the differences from the fourth embodiment will be mainly described.

[0212] like Figure 31 As shown, the bus vehicle V has batteries BT installed in the roof and chassis. That is, the batteries BT include a first battery pack BP1 installed in the roof of the bus vehicle V and a second battery pack BP2 installed in the chassis of the bus vehicle V.

[0213] The first battery pack BP1 and the second battery pack BP2 are series-connected bodies in which the battery cells are electrically connected in series. Alternatively, the first battery pack BP1 and the second battery pack BP2 may be formed by connecting some of the battery cells in parallel.

[0214] The battery BT has a smaller number of battery cells in the second battery pack BP2 than in the first battery pack BP1. That is, in the bus vehicle V, the number of battery cells in the chassis is smaller than in the roof. The greater number of battery cells in the first battery pack BP1 compared to the second battery pack BP2 results in a greater heat capacity. In this embodiment, the first battery pack BP1 constitutes a roof-side device located on the vehicle's roof, while the second battery pack BP2 constitutes a chassis-side device located on the vehicle's chassis.

[0215] like Figure 32 As shown, the cooling circuit 31C of the cooling machine 30 includes a first circuit portion 31CA and a second circuit portion 31CB that are independent of each other. That is, the first circuit portion 31CA and the second circuit portion 31CB are configured as independent circuits.

[0216] The first circuit section 31CA is a circuit for the flow of heat medium that exchanges heat with the first battery pack BP1, which is located in the ceiling. The first circuit section 31CA includes a heat medium flow path 162 for the first equipment evaporator 16. In other words, the first equipment evaporator 16 is located in the first circuit section 31CA, allowing the heat medium flowing through the first circuit section 31CA. Specifically, the first circuit section 31CA includes a first circulation pump 32A, a heat medium flow path 162 for the first equipment evaporator 16, a first three-way valve 33A, a first battery cooling unit 34A, and a first radiator 35A. Like the first battery pack BP1, the first circuit section 31CA is located in the ceiling.

[0217] The second circuit section 31CB is a circuit for the flow of heat medium that exchanges heat with the second battery pack BP2, which is located in the floor. The second circuit section 31CB includes the heat medium flow path 262 for the second equipment evaporator 26. In other words, the second equipment evaporator 26 is located in the second circuit section 31CB, allowing the heat medium flowing through the second circuit section 31CB. Specifically, the second circuit section 31CB includes a second circulation pump 32B, the heat medium flow path 262 for the second equipment evaporator 26, a second three-way valve 33B, a second battery cooler 34B, and a second radiator 35B. In the second circuit section 31CB, the second battery cooler 34B is located in the floor, similar to the second battery pack BP2, while the remaining components are located in the ceiling. Therefore, the length from the heat medium flow path 262 for the second equipment evaporator 26 to the second battery cooler 34B is greater than the length from the first equipment evaporator 16 to the first battery cooler 34A.

[0218] Here, the first circulation pump 32A and the second circulation pump 32B are configured similarly to the circulation pump 32 described in the first embodiment. The first three-way valve 33A and the second three-way valve 33B are configured similarly to the three-way valve 33 described in the first embodiment. The first battery cooler 34A and the second battery cooler 34B are configured similarly to the battery cooler 34 described in the first embodiment. The first radiator 35A and the second radiator 35B are configured similarly to the radiator 35 described in the first embodiment.

[0219] The other structures are the same as those of the fourth embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the fourth embodiment, as in the fourth embodiment.

[0220] The cooling circuit 31C of this embodiment has a first circuit section 31CA and a second circuit section 31CB that are independent of each other. The first device evaporator 16 is arranged in the first circuit section 31CA, allowing the heat medium flowing in the first circuit section 31CA to pass through. Furthermore, the second device evaporator 26 is arranged in the second circuit section 31CB, allowing the heat medium flowing in the second circuit section 31CB to pass through. In this way, the cooling circuit 31C only needs to be configured so that the heat absorption of the first device evaporator 16 and the heat absorption of the second device evaporator 26 can be adjusted independently. The heat medium cooled in each device evaporator 16, 26 can fully cool the battery BT.

[0221] In particular, the cooling circuit 31C has a circuit structure in which the heat medium for exchanging heat with the first battery pack BP1 arranged in the ceiling portion flows through the first circuit portion 31CA, and the heat medium for exchanging heat with the second battery pack BP2 arranged in the floor portion flows through the second circuit portion 31CB.

[0222] In the bus vehicle V, the first battery group BP1 disposed in the ceiling portion is likely to be higher in temperature than the second battery group BP2 disposed in the floor portion due to the influence of sunlight, natural convection, and the like. In other words, the second battery group BP2 is less likely to be higher in temperature than the first battery group BP1 due to the influence of sunlight, natural convection, and the like.

[0223] Therefore, if the heat medium that exchanges heat with the first battery group BP1 flows in the first circuit portion 31CA and the heat medium that exchanges heat with the second battery group BP2 flows in the second circuit portion 31CB, the heat medium that is lower in temperature than the heat medium that flows into the first device evaporator 16 flows into the second device evaporator 26. Thus, the temperature difference of the heat medium before and after the second device evaporator 26 is smaller than that of the first device evaporator 16. Also, because the length from the second device evaporator 26 to the second battery cooling portion 34B is greater than the length from the first device evaporator 16 to the first battery cooling portion 34A, the flow rate of the heat medium of the second device evaporator 26 is likely to be reduced compared to the first device evaporator 16. Therefore, the heat absorption amount from the heat medium at the time of device temperature adjustment is likely to be smaller for the panel side air conditioner 20X than for the door side air conditioner 10X.

[0224] Also, the first battery group BP1 is greater in heat capacity than the second battery group BP2 because of the greater number of battery cells. Accordingly, the temperature of the second battery group BP2 is likely to decrease compared to the first battery group BP1, so that, at the time of device cooling, the heat medium that is lower in temperature than the heat medium that flows into the second device evaporator 26 is likely to flow into the first device evaporator 16. Thus, the temperature difference of the heat medium before and after the second device evaporator 26 is smaller than that of the first device evaporator 16. Therefore, the heat absorption amount from the heat medium at the time of device temperature adjustment is sufficiently small for the second device evaporator 26 than for the first device evaporator 16.

[0225] Further, the cooling circuit 31C is configured such that the number of battery cells that exchange heat with the heat medium is smaller in the second circuit portion 31CB than in the first circuit portion 31CA. Accordingly, the number of battery cells that become a cooling target is small in the second circuit portion 31CB, and the heat medium is likely to be lower in temperature compared to the first circuit portion 31CA. Therefore, at the time of device cooling, the heat medium that is lower in temperature than the heat medium that flows into the first device evaporator 16 is likely to flow into the second device evaporator 26. Thus, the temperature difference of the heat medium before and after the second device evaporator 26 is smaller than that of the first device evaporator 16. Therefore, the heat absorption amount from the heat medium at the time of device temperature adjustment is sufficiently small for the second device evaporator 26 than for the first device evaporator 16.

[0226] Therefore, during temperature control, the panel-side air conditioner 20X absorbs less heat from the heat medium, resulting in a greater amount of heat absorbed by the air blown into the panel-side area Zp, facilitating a dehumidification effect through air cooling. Consequently, even when cooling the battery BT, comfort can be maintained in the panel-side area Zp, which is located away from the doors D1 and D2 of the bus vehicle V. Specifically, the air conditioning system 1 ensures comfort in air-conditioned areas that cannot be ventilated by opening and closing the entry and exit doors E1 and E2.

[0227] (Modification of the Sixth Embodiment)

[0228] As long as the amount of heat absorbed from the heat medium during device temperature control is smaller in the second device evaporator 26 than in the first device evaporator 16, the air conditioning system 1 may have a configuration different from that of the sixth embodiment. For example, the first battery pack BP1 and the second battery pack BP2 may be arranged in the same position. Furthermore, the first battery pack BP1 and the second battery pack BP2 may be composed of the same number of battery cells.

[0229] (Seventh embodiment)

[0230] Next, refer to Figure 33 、 Figure 34 This embodiment will mainly describe the differences from the fourth embodiment.

[0231] The air conditioning system 1 of this embodiment controls the refrigerant flow rate in each device evaporator 16 , 26 by the control device 100 so that the amount of heat absorbed from the heat medium during device temperature control is smaller in the second device evaporator 26 than in the first device evaporator 16 .

[0232] When adjusting the temperature of the equipment, the control device 100 controls the equipment-side on-off valves 18 and 28 so that the time the second equipment-side on-off valve 28 remains open is shorter than the time the first equipment-side on-off valve 18 remains open. The time the second equipment-side on-off valve 28 remains open is the time it takes to enter the second permissible state, allowing the refrigerant to flow toward the second equipment evaporator 26. Furthermore, the time the first equipment-side on-off valve 18 remains open is the time it takes to enter the first permissible state, allowing the refrigerant to flow toward the first equipment evaporator 16.

[0233] The control device 100 executes, for example, at the start of the device temperature control Figure 33 This process is part of the start process executed when the device is temperature-controlled, and corresponds to the process described in the fourth embodiment. Figure 16 In addition, Figure 33 The control program shown is executed periodically or irregularly by control device 100 .

[0234] like Figure 33 As shown, in step S300, the control device 100 reads various signals input from the sensor group 101, the operation panel 102, and the like. Next, in step S310, the control device 100 determines whether the temperature of the battery BT exceeds a first high-temperature threshold value THth1. The first high-temperature threshold value THth1 is set to a desired temperature at which cooling of the battery BT is to be initiated. For example, the first high-temperature threshold value THth1 is set to a temperature slightly lower than the upper limit of the appropriate temperature of the battery BT.

[0235] When the temperature of the battery BT exceeds the first high-temperature threshold value THth1, the control device 100 switches the first equipment-side on-off valve 18 to the open state in step S320. That is, the control device 100 controls the first equipment-side on-off valve 18 to switch it from the first blocking state to the first enabling state.

[0236] Next, the control device 100 determines whether a first set time has elapsed since the first equipment-side on-off valve 18 was switched to the first permission state. Specifically, in step S330, the control device 100 determines whether the temperature of the battery BT is greater than a second high-temperature threshold value THth2. The second high-temperature threshold value THth2 is set to a temperature greater than the first high-temperature threshold value THth1. For example, the second high-temperature threshold value THth2 is set at the upper limit of the appropriate temperature of the battery BT.

[0237] When the temperature of the battery BT exceeds the second high-temperature threshold value THth2, the control device 100 switches the second equipment-side on-off valve 28 to the open state in step S340. That is, the control device 100 controls the second equipment-side on-off valve 28 to switch it from the second blocked state to the second permitted state.

[0238] The control device 100 exits this process after controlling the device-side on-off valves 18 and 28. If the temperature of the battery BT becomes lower than the first high-temperature threshold THth1 in step S310, the control device 100 skips steps S320 to S340 and exits this process.

[0239] Furthermore, the control device 100 executes, for example, when the temperature control of the device is stopped. Figure 34 This process is part of the stop process executed when the device is temperature-controlled, and corresponds to the process described in the fourth embodiment. Figure 17 In addition, Figure 34 The control program shown is executed periodically or irregularly by the control device 100 .

[0240] like Figure 34As shown, in step S400, the control device 100 reads various signals input from the sensor group 101, the operation panel 102, and the like. Next, in step S410, the control device 100 determines whether the temperature of the battery BT is lower than a first low-temperature threshold value TLth1. The first low-temperature threshold value TLth1 is set to a desired temperature at which cooling of the battery BT is stopped. For example, the first low-temperature threshold value TLth1 is set to a temperature slightly higher than the lower limit of the appropriate temperature of the battery BT.

[0241] When the temperature of the battery BT is lower than the first low-temperature threshold TLth by 1 hour, the control device 100 switches the second equipment-side on-off valve 28 to the closed state in step S420. That is, the control device 100 controls the second equipment-side on-off valve 28 to switch it from the second permitted state to the second blocked state.

[0242] Next, the control device 100 determines whether a second set time has elapsed since the second equipment-side on-off valve 28 was switched to the second blocked state. Specifically, in step S430, the control device 100 determines whether the temperature of the battery BT is lower than a second low-temperature threshold TLth2. The second low-temperature threshold TLth2 is set to a temperature lower than the first low-temperature threshold TLth1. For example, the second low-temperature threshold TLth2 is set at the lower limit of the appropriate temperature of the battery BT.

[0243] When the temperature of the battery BT is lower than the second low-temperature threshold TLth by 2 hours, the control device 100 switches the first facility-side on-off valve 18 to a closed state in step S440. In other words, the control device 100 controls the first facility-side on-off valve 18 to switch it from the first enabling state to the first blocking state.

[0244] The control device 100 exits this process after controlling the equipment-side on-off valves 18 and 28. If the temperature of the battery BT exceeds the first low-temperature threshold TLth1 in step S410, the control device 100 skips steps S420 to S440 and exits this process.

[0245] Due to the execution of the above-described process, during the device temperature adjustment, the flow rate of the refrigerant passing through the second device evaporator 26 becomes smaller than the flow rate of the refrigerant passing through the first device evaporator 16. In other words, during the device temperature adjustment, the flow rate of the refrigerant passing through the second indoor evaporator 24 becomes larger than the flow rate of the refrigerant passing through the first indoor evaporator 14.

[0246] The other structures are the same as those of the fourth embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the fourth embodiment, as in the fourth embodiment.

[0247] During equipment temperature control, the control device 100 of this embodiment controls each of the equipment-side on-off valves 18 and 28 so that the time during which the second equipment-side on-off valve 28 remains in the first permissible state is shorter than the time during which the first equipment-side on-off valve 18 remains in the first permissible state. Consequently, the refrigerant flow rate during equipment temperature control is smaller in the second equipment evaporator 26 than in the first equipment evaporator 16. Therefore, the amount of heat absorbed from the heat medium during equipment temperature control can be reduced in the second equipment evaporator 26 compared to the first equipment evaporator 16.

[0248] Therefore, during temperature control, the panel-side air conditioner 20X absorbs less heat from the heat medium, resulting in a greater amount of heat absorbed by the air blown into the panel-side area Zp, facilitating a dehumidification effect through air cooling. Consequently, even when cooling the battery BT, comfort can be maintained in the panel-side area Zp, which is located away from the doors D1 and D2 of the bus vehicle V. Specifically, the air conditioning system 1 ensures comfort in air-conditioned areas that cannot be ventilated by opening and closing the entry and exit doors E1 and E2.

[0249] (Modification of Seventh Embodiment)

[0250] While the seventh embodiment illustrates a control process that staggers the timing of the operation of each device-side on-off valve 18, 28 at the start and stop of device temperature control to reduce the refrigerant flow rate through the second device evaporator 26 during device temperature control, this control process is not limited to this. The control process executed by the controller 100 may also be another process as long as it reduces the refrigerant flow rate through the second device evaporator 26 during device temperature control. For example, the control process executed by the controller 100 may stagger the timing of the operation of each device-side on-off valve 18, 28 at the start and stop of device temperature control to reduce the refrigerant flow rate through the second device evaporator 26 during device temperature control.

[0251] Furthermore, the control process executed by the control device 100 shown in the seventh embodiment is not limited to the fourth embodiment, and can also be applied to the air conditioning system 1 shown in the fifth and sixth embodiments.

[0252] (Eighth Embodiment)

[0253] Next, refer to Figures 35 to 37 In this embodiment, the differences from the fourth embodiment will be mainly described.

[0254] The air conditioning system 1 of the present embodiment has a structure in which the pressure losses when the refrigeration cycle RC1 of the door side air conditioner 10X and the refrigeration cycle RC1 of the panel side air conditioner 20 form refrigerant flows are different.

[0255] Door side air conditioner 10X Figure 35 As shown, the configuration is similar to that of the first embodiment. In this embodiment, the point where the refrigerant after passing through the first indoor evaporator 14 and the refrigerant after passing through the first equipment evaporator 16 merge is referred to as the first confluence MP1. Furthermore, in this embodiment, the pressure loss from the inlet side of the first indoor evaporator 14 to the first confluence MP1 is referred to as ΔPD1, and the pressure loss from the inlet side of the first equipment evaporator 16 to the first confluence MP1 is referred to as ΔPD2.

[0256] On the other hand, the panel side air conditioner 20X is as follows Figure 36 As shown, a pressure loss body 29 that obstructs the flow of refrigerant is provided on the outlet side of the second equipment evaporator 26. The pressure loss body 29 is composed of, for example, an orifice. Alternatively, the pressure loss body 29 may be provided on the evaporation pressure regulating valve.

[0257] In this embodiment, the point where the refrigerant after passing through the second indoor evaporator 24 and the refrigerant after passing through the second equipment evaporator 26 merge is referred to as the second merging point MP2. Furthermore, in this embodiment, the pressure loss from the inlet side of the second indoor evaporator 24 to the second merging point MP2 is referred to as ΔPP1, and the pressure loss from the inlet side of the second equipment evaporator 26 to the second merging point MP2 is referred to as ΔPP2.

[0258] In the panel side air conditioner 20X, a pressure loss body 29 that obstructs the refrigerant flow is provided on the outlet side of the second equipment evaporator 26, thereby increasing the pressure loss ΔPP2 from the inlet side of the second equipment evaporator 26 to the second confluence point MP2. Figure 37 As shown, the second pressure loss ratio ΔPP, which is the ratio of the pressure loss ΔPP2 to the pressure loss ΔPP1, is greater than the first pressure loss ratio ΔPD, which is the ratio of the pressure loss ΔPD2 to the pressure loss ΔPD1.

[0259] The other structures are the same as those of the fourth embodiment. The air conditioning system 1 of this embodiment can obtain the effects achieved by the structures common to or equivalent to those of the fourth embodiment, as in the fourth embodiment.

[0260] In particular, in this embodiment, the second pressure loss ratio ΔPP is greater than the first pressure loss ratio ΔPD. Consequently, during temperature control, refrigerant is less likely to flow into the second equipment evaporator 26 and more likely to flow into the second indoor evaporator 24. Consequently, by adjusting the pressure loss in the refrigeration cycle of each air conditioner 10X or 20X, a configuration can be easily achieved in which the amount of heat absorbed from the heat medium during temperature control is smaller in the second equipment evaporator 26 than in the first equipment evaporator 16.

[0261] (Modification of the Eighth Embodiment)

[0262] While the eighth embodiment illustrates a structure in which the pressure loss ΔPP2 is increased by adding a pressure drop element 29 to the outlet of the second evaporator 26, this structure can also be achieved by other means. For example, the aforementioned structure can be achieved by setting the bend angle of the refrigerant piping on the outlet side of the second evaporator 26 larger than the bend angle of the refrigerant piping on the outlet side of the first evaporator 16. Furthermore, the aforementioned structure can be achieved by setting the radius of curvature of the bend in the refrigerant piping on the outlet side of the second evaporator 26 smaller than the radius of curvature of the arc-shaped bend in the refrigerant piping on the outlet side of the first evaporator 16. Furthermore, the aforementioned structure can be achieved by setting the effective length L / D of the refrigerant piping on the outlet side of the second evaporator 26 larger than the effective length L / D of the refrigerant piping on the outlet side of the first evaporator 16.

[0263] Here, if Figure 38 As shown, a configuration in which the amount of heat absorbed from the heat medium during device temperature control by the second device evaporator 26 is smaller than that by the first device evaporator 16 can be achieved by reducing the evaporation performance of the second device evaporator 26 compared to the first device evaporator 16. This configuration can be achieved by increasing the size of the second device evaporator 26 compared to the first device evaporator 16 or by reducing the fin pitch of the inner fins.

[0264] Furthermore, the configuration shown in the eighth embodiment is not limited to the fourth embodiment, and can also be applied to the air conditioning system 1 shown in the fifth and sixth embodiments.

[0265] (Other Embodiments)

[0266] Although representative embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications are possible, for example, as described below.

[0267] In the above-described embodiment, the first heat sink 12 and the second heat sink 22 include the liquid receiving portion 122 , 222 and the supercooling portion 123 , 223 . However, the present invention is not limited thereto and the liquid receiving portion 122 , 222 and the supercooling portion 123 , 223 may not be included.

[0268] In the door-side air conditioner 10 of the above embodiment, the first indoor evaporator 14 and the first equipment evaporator 16 are connected in parallel with respect to the refrigerant flow. However, this is not limiting. For example, the first indoor evaporator 14 and the first equipment evaporator 16 may be connected in series with respect to the refrigerant flow. Furthermore, the first indoor on-off valve 17 provided in the door-side air conditioner 10 is not essential.

[0269] In the panel-side air conditioner 20X of the above-described embodiment, the second indoor evaporator 24 and the second equipment evaporator 26 are connected in parallel with respect to the refrigerant flow. However, this is not limiting. For example, the second indoor evaporator 24 and the second equipment evaporator 26 may be connected in series with respect to the refrigerant flow. Furthermore, the second indoor on-off valve 27 provided in the panel-side air conditioner 20X is not essential.

[0270] While the above embodiment illustrates cooling the battery BT as the target device, this is not limiting. The air conditioning system 1 can also cool an onboard device such as the battery BT. In this case, the onboard device is not limited to self-heating devices. It also includes devices that are heated by external heat.

[0271] In the above embodiment, room cooling and equipment temperature control are exemplified as the operation modes of the air conditioning system 1 , but the operation modes are not limited thereto and may include, for example, a room heating mode and a battery BT temperature control mode.

[0272] In the above embodiments, a vehicle having two, four, or six air-conditioning zones Z set indoors is exemplified. However, the vehicle air-conditioning system of the present invention is applicable to a vehicle having a plurality of air-conditioning zones Z set other than the above numbers.

[0273] In the above-mentioned embodiment, the bus vehicle V is exemplified as an electric vehicle, but the bus vehicle V may be configured as a hybrid vehicle.

[0274] While the above-described embodiment describes the vehicle air conditioning system of the present invention as being applicable to a bus V, the vehicle air conditioning system of the present invention is not applicable to buses V and is applicable to any vehicle having doors offset to the front, back, left, or right. Furthermore, the "doors" described in the above-described embodiment are not limited to passenger entry and exit doors but also include doors primarily used for loading and unloading cargo, such as rear doors.

[0275] In the above-described embodiment, it is needless to say that the elements constituting the embodiment are not necessarily essential, except when it is particularly necessary to specify them or when it is considered that they must be clarified in principle.

[0276] In the above-mentioned embodiments, the numerical values ​​such as the number, value, amount, and range of the components of the embodiments are not limited to specific quantities except when specifically required or when it is necessary to clarify in principle.

[0277] In the above-mentioned embodiments, when the shapes, positional relationships, etc. of the components are mentioned, they are not limited by the shapes, positional relationships, etc. unless otherwise specified or in principle limited by specific shapes, positional relationships.

[0278] The control unit and its method described in the present invention can be realized by a dedicated computer provided by a programmed processor and memory to execute one or more functions embodied by a computer program. Alternatively, the control unit and its method described in the present invention can be realized by a dedicated computer provided by a processor composed of one or more dedicated hardware logic circuits. The control unit and its method described in the present invention can also be realized by a combination of a programmed processor and memory and a processor composed of one or more hardware logic circuits to constitute one or more dedicated computers to execute one or more functions. In addition, the computer program can also be stored in a non-transitory tangible storage medium readable by a computer as an instruction executed by a computer.

[0279] (Summarize)

[0280] According to a first aspect of some or all of the above-described embodiments, a vehicle air conditioning system includes: a plurality of air conditioners provided for each of a plurality of air conditioning zones; and a cooling device configured to cool target equipment mounted on the vehicle. The plurality of air conditioners include door-side air conditioners and panel-side air conditioners, and the panel-side air conditioners are configured such that the amount of heat absorbed from the heat medium during equipment temperature control is smaller in the panel-side air conditioners than in the door-side air conditioners.

[0281] According to a second aspect, the door-side air conditioner includes a first indoor evaporator and a device evaporator. The first indoor evaporator absorbs heat from air before being blown out to the door-side area to evaporate the refrigerant. The device evaporator is arranged in parallel with the first indoor evaporator with respect to the refrigerant flow and absorbs heat from a heat medium to evaporate the refrigerant. The panel-side air conditioner includes a second indoor evaporator that absorbs heat from air before being blown out to the panel-side area to evaporate the refrigerant, and does not include a heat absorber that absorbs heat from the heat medium.

[0282] Unlike door-side air conditioners, the panel-side air conditioner does not absorb heat from the heat medium. Therefore, the heat absorption effect of the refrigeration cycle is concentrated on the air blown into the panel-side area. Therefore, sufficient comfort is ensured in the air-conditioned area away from the vehicle door.

[0283] According to a third aspect, the door-side air conditioner includes a first indoor evaporator and a first equipment evaporator. The first indoor evaporator absorbs heat from air before it is blown out to the door-side area to evaporate the refrigerant. The first equipment evaporator is arranged in parallel with the first indoor evaporator with respect to the refrigerant flow and absorbs heat from the heat medium to evaporate the refrigerant. The panel-side air conditioner includes a second indoor evaporator and a second equipment evaporator. The second indoor evaporator absorbs heat from air before it is blown out to the panel-side area to evaporate the refrigerant. The second equipment evaporator is arranged in parallel with the second indoor evaporator with respect to the refrigerant flow and absorbs heat from the heat medium to evaporate the refrigerant. Furthermore, the amount of heat absorbed from the heat medium during equipment temperature control is smaller for the second equipment evaporator than for the first equipment evaporator.

[0284] As a result, the panel-side air conditioner absorbs less heat from the heat medium than the door-side air conditioner, allowing the refrigeration cycle's heat absorption to be concentrated on the air blown toward the panel-side area. This ensures sufficient comfort in the air-conditioned area away from the vehicle door.

[0285] According to a fourth aspect, the first and second evaporators are arranged in series with respect to the heat medium flow in the cooling circuit. The second evaporator is arranged in the cooling circuit downstream of the heat medium flow of the first evaporator so that the heat medium flows in after passing through the first evaporator.

[0286] Since the second evaporator receives a lower-temperature heat medium than the heat medium flowing into the first evaporator, the temperature difference between the heat medium before and after the evaporator is smaller than that of the first evaporator. Therefore, by arranging the second evaporator downstream of the heat medium flow of the first evaporator, it is possible to easily achieve a configuration in which the amount of heat absorbed from the heat medium during temperature control is smaller in the second evaporator than in the first evaporator.

[0287] According to a fifth aspect, the first and second evaporators are arranged in parallel with respect to the heat medium flow in a cooling circuit. The cooling circuit includes a first cooling pipe, the first cooling pipe directing the heat medium toward the first evaporator, and a second cooling pipe directing the heat medium toward the second evaporator. One end of each of the first and second cooling pipes is connected to a branching portion located upstream of the heat medium flow between the first and second evaporators, and the other end is connected to a converging portion located downstream of the heat medium flow between the first and second evaporators. The second cooling pipe is configured to produce a greater pressure loss during heat medium flow than the first cooling pipe.

[0288] The second cooling pipe configured in this manner has a lower heat medium flow rate than the first cooling pipe. Consequently, the second equipment evaporator absorbs less heat from the heat medium than the first equipment evaporator. Therefore, by adjusting the pressure loss in the second cooling pipe, it is possible to easily achieve a configuration in which the first equipment evaporator absorbs less heat from the heat medium than the second equipment evaporator during equipment temperature control.

[0289] Here, the second cooling pipe may have a larger bending angle at its curved portion than the first cooling pipe. The second cooling pipe may have a smaller radius of curvature at its arc-shaped curved portion than the first cooling pipe. The second cooling pipe may have a larger effective length (the ratio of the pipe length to the pipe inner diameter) than the first cooling pipe. A resistor that obstructs the flow of the heat medium may also be provided, thereby increasing the pressure loss in the second cooling pipe compared to the first cooling pipe.

[0290] According to a sixth aspect, the cooling circuit includes a first circuit portion and a second circuit portion that are independent of each other. The first device evaporator is disposed in the first circuit portion so as to allow the heat medium flowing in the first circuit portion to pass through. The second device evaporator is disposed in the second circuit portion so as to allow the heat medium flowing in the second circuit portion to pass through.

[0291] In this manner, in the cooling circuit, the amount of heat absorbed from the heat medium in the first device evaporator and the amount of heat absorbed from the heat medium in the second device evaporator can be adjusted independently.

[0292] According to a seventh aspect, the target device includes a ceiling-side device disposed on a vehicle ceiling and a chassis-side device disposed on a vehicle chassis. A first circuit portion allows heat medium to flow through the ceiling-side device for heat exchange. A second circuit portion allows heat medium to flow through the chassis-side device for heat exchange.

[0293] In a vehicle, the temperature of the equipment on the ceiling side is more likely to rise than that of the equipment on the chassis side due to the influence of sunlight, natural convection, etc. In other words, the temperature of the equipment on the chassis side is less likely to rise than that of the equipment on the ceiling side due to the influence of sunlight, natural convection, etc. Therefore, by configuring the cooling circuit so that the heat medium for heat exchange with the equipment on the ceiling flows to the first circuit portion of the cooling circuit, and the heat medium for heat exchange with the equipment on the chassis side flows to the second circuit portion, the heat medium flowing into the evaporator for the second equipment will be lower than the heat medium flowing into the evaporator for the first equipment. As a result, the temperature difference between the heat medium before and after the evaporator for the second equipment becomes smaller than that of the evaporator for the first equipment. Therefore, a structure can be achieved in which the amount of heat absorbed from the heat medium during equipment temperature control is smaller in the evaporator for the second equipment than in the evaporator for the first equipment.

[0294] According to the eighth aspect, the ceiling-side equipment has a greater heat capacity than the chassis-side equipment. Consequently, since the chassis-side equipment cools more easily than the ceiling-side equipment, during equipment cooling, heat medium at a lower temperature than the heat medium flowing into the first equipment evaporator is more likely to flow into the second equipment evaporator. Consequently, the temperature difference between the heat medium before and after the second equipment evaporator is smaller than that of the first equipment evaporator. Consequently, a configuration can be achieved in which the amount of heat absorbed by the heat medium during equipment temperature control is smaller in the second equipment evaporator than in the first equipment evaporator.

[0295] According to the ninth aspect, the target device is composed of a plurality of devices, and the cooling circuit is configured so that the number of devices exchanging heat with the heat medium in the second circuit portion is reduced compared to the first circuit portion.

[0296] With this arrangement, since the number of devices to be cooled in the second circuit is small, the heat medium is more likely to reach a lower temperature than in the first circuit. Therefore, when cooling devices, heat medium, which is lower than the heat medium flowing into the first evaporator, is more likely to flow into the second evaporator. This reduces the temperature difference between the heat medium before and after the second evaporator compared to the first evaporator. Consequently, the amount of heat absorbed from the heat medium during device temperature control can be reduced in the second evaporator compared to the first evaporator.

[0297] According to a tenth aspect, a vehicle air conditioning system includes an air conditioning control unit that controls a door-side air conditioner and a panel-side air conditioner. The door-side air conditioner includes a door-side switching unit that switches between a first permission state that allows the refrigerant to flow toward a first device evaporator and a first blocking state that blocks the refrigerant from flowing toward the first device evaporator. The panel-side air conditioner includes a panel-side switching unit that switches between a second permission state that allows the refrigerant to flow toward a second device evaporator and a second blocking state that blocks the refrigerant from flowing toward the second device evaporator. When the device is temperature-controlled, the air conditioning control unit controls the door-side switching unit and the panel-side switching unit so that the time spent in the second permission state is shorter than the time spent in the first permission state.

[0298] Therefore, since the refrigerant flow rate in the second evaporator during device temperature control is smaller than that in the first evaporator, the amount of heat absorbed from the heat medium during device temperature control can be reduced in size in the second evaporator compared to the first evaporator.

[0299] According to the eleventh viewpoint, when starting the temperature adjustment of the equipment, the air conditioning control unit controls the door side switching unit and the panel side switching unit so that after a predetermined time has passed since switching from the first blocking state to the first allowing state, it switches from the second blocking state to the second allowing state.

[0300] Thus, by changing the control method of the door-side switching unit and the panel-side switching unit when starting the device temperature control, a structure can be easily achieved in which the heat absorption amount from the heat medium during the device temperature control is smaller in the second device evaporator than in the first device evaporator.

[0301] According to the twelfth viewpoint, when the temperature adjustment of the equipment is stopped, the air conditioning control unit controls the door side switching unit and the panel side switching unit so that after a predetermined time has passed since the second permission state is switched to the second blocking state, the first permission state is switched to the first blocking state.

[0302] According to this, by changing the control method of the door-side switching unit and the panel-side switching unit when stopping the device temperature control, it is possible to simply realize a structure in which the heat absorption amount from the heat medium during the device temperature control is smaller in the second device evaporator than in the first device evaporator.

[0303] According to the thirteenth aspect, the second pressure loss ratio becomes larger than the first pressure loss ratio. Here, the first pressure loss ratio is the ratio of the pressure loss from the refrigerant inlet side of the first device evaporator to the first confluence to the pressure loss from the refrigerant inlet side of the first indoor evaporator to the first confluence. The first confluence is the confluence where the refrigerant passing through the first indoor evaporator and the refrigerant passing through the first device evaporator are merged. In addition, the second pressure loss is the ratio of the pressure loss from the refrigerant inlet side of the second device evaporator to the second confluence to the pressure loss from the refrigerant inlet side of the second indoor evaporator to the second confluence. The second confluence is the confluence where the refrigerant passing through the second indoor evaporator and the refrigerant passing through the second device evaporator are merged.

[0304] As a result, during temperature control, refrigerant is less likely to flow to the second evaporator and more likely to flow to the second indoor evaporator. This allows for adjustments to the pressure loss in the refrigeration cycle of each air conditioner, making it possible to easily achieve a configuration in which the amount of heat absorbed from the heat medium during temperature control is smaller in the second evaporator than in the first evaporator.

[0305] According to the fourteenth aspect, the target device is a heat-generating device mounted on the vehicle. This allows the heat-generating device to be cooled while ensuring comfort in the air-conditioned area away from the vehicle door.

[0306] According to a fifteenth aspect, the door is a passenger door that opens and closes the vehicle entrance when passengers get on and off the vehicle. The vehicle air conditioning system of the present invention can ensure comfort in an air-conditioned area that cannot be ventilated by opening and closing the vehicle entrance.

[0307] Here, the vehicle is provided with one or more doors on one side of the vehicle in the left-right direction, and a side panel is provided on the other side of the left-right direction. One side of the left-right direction in the room becomes the door side area, and the other side of the left-right direction in the room becomes the panel side area.

[0308] Alternatively, the vehicle may have one or more doors on the front side of one of the left and right sides of the vehicle, and may have side panels on each of the rear side of one of the left and right sides and the other side of the left and right sides. In this case, it is desirable that the front side of one of the left and right sides within the interior of the vehicle serve as the door side region, and the rear side of one of the left and right sides within the interior of the vehicle and the other side of the left and right sides serve as the panel side regions.

[0309] Alternatively, the vehicle may have one or more doors on the rear side of one of the left and right sides of the vehicle, and may have side panels on each of the front side of one of the left and right sides and the other side of the left and right sides. In this case, it is desirable that the rear side of one of the left and right sides within the interior of the vehicle serve as the door side region, and the front side and the other side of one of the left and right sides within the interior of the vehicle serve as the panel side regions.

[0310] In addition, the vehicle is provided with one or more doors on the front side and side panels on the rear side of the vehicle in the left and right directions. The front side in the room becomes the door side area, and the rear side in the room becomes the panel side area.

[0311] In addition, the vehicle is provided with one or more doors on the rear side and side panels on the front side of the vehicle in the left and right directions, and the rear side in the room becomes the door side area and the front side in the room becomes the panel side area.

Claims

1. A vehicle air conditioning system for performing air conditioning on a plurality of air-conditioning zones set in a vehicle interior, characterized in that: have: a plurality of air conditioners provided corresponding to each of the plurality of air conditioning areas; and a cooling machine for cooling a target device mounted on the vehicle, Each of the plurality of air conditioners includes a vapor compression refrigeration cycle and cools the air blown to the plurality of air-conditioning areas by absorbing heat due to evaporation of a refrigerant. The cooling machine includes a cooling circuit for a heat medium to flow through for heat exchange with the target device, and utilizes the heat absorption effect of at least some of the plurality of air conditioners to cool the heat medium, thereby adjusting the temperature of the target device. When, among the plurality of air conditioners, the air conditioner that performs air conditioning on the door side area separated from the outside by the door of the vehicle is referred to as the door side air conditioner, and the air conditioner that performs air conditioning on the panel side area separated from the outside by the side panel of the vehicle is referred to as the panel side air conditioner, the amount of heat absorbed from the heat medium when the indoor cooling and the temperature control of the target device are respectively performed by the plurality of air conditioners is smaller than that of the door side air conditioner. The door-side air conditioner includes a first indoor evaporator and a first equipment evaporator. The first indoor evaporator absorbs heat from air before being blown to the door-side area to evaporate refrigerant. The first equipment evaporator is arranged in parallel with the first indoor evaporator with respect to the refrigerant flow and absorbs heat from a heat medium to evaporate the refrigerant. The panel-side air conditioner includes a second indoor evaporator and a second equipment evaporator. The second indoor evaporator absorbs heat from air before being blown out to the panel-side area to evaporate the refrigerant. The second equipment evaporator is arranged in parallel with the second indoor evaporator with respect to the refrigerant flow and absorbs heat from the heat medium to evaporate the refrigerant. The amount of heat absorbed from the heat medium during the temperature adjustment of the device is smaller than that of the first device evaporator. The first device evaporator and the second device evaporator are arranged in series with respect to the heat medium flow in the cooling circuit. The second equipment evaporator is arranged in the cooling circuit on the downstream side of the heat medium flow of the first equipment evaporator so as to allow the heat medium that has passed through the first equipment evaporator to flow therein.

2. A vehicle air conditioning system for performing air conditioning on a plurality of air-conditioning zones set in a vehicle interior, characterized in that: have: a plurality of air conditioners provided corresponding to each of the plurality of air conditioning areas; and a cooling machine for cooling a target device mounted on the vehicle, Each of the plurality of air conditioners includes a vapor compression refrigeration cycle and cools the air blown to the plurality of air-conditioning areas by absorbing heat due to evaporation of a refrigerant. The cooling machine includes a cooling circuit for a heat medium to flow through for heat exchange with the target device, and utilizes the heat absorption effect of at least some of the plurality of air conditioners to cool the heat medium, thereby adjusting the temperature of the target device. When, among the plurality of air conditioners, the air conditioner that performs air conditioning on the door side area separated from the outside by the door of the vehicle is referred to as the door side air conditioner, and the air conditioner that performs air conditioning on the panel side area separated from the outside by the side panel of the vehicle is referred to as the panel side air conditioner, the amount of heat absorbed from the heat medium when the indoor cooling and the temperature control of the target device are respectively performed by the plurality of air conditioners is smaller than that of the door side air conditioner. The door-side air conditioner includes a first indoor evaporator and a first equipment evaporator. The first indoor evaporator absorbs heat from air before being blown to the door-side area to evaporate refrigerant. The first equipment evaporator is arranged in parallel with the first indoor evaporator with respect to the refrigerant flow and absorbs heat from a heat medium to evaporate the refrigerant. The panel-side air conditioner includes a second indoor evaporator and a second equipment evaporator. The second indoor evaporator absorbs heat from air before being blown out to the panel-side area to evaporate the refrigerant. The second equipment evaporator is arranged in parallel with the second indoor evaporator with respect to the refrigerant flow and absorbs heat from the heat medium to evaporate the refrigerant. The amount of heat absorbed from the heat medium during the temperature adjustment of the device is smaller than that of the first device evaporator. The first device evaporator and the second device evaporator are arranged in parallel with respect to the heat medium flow in the cooling circuit. The cooling circuit includes a first cooling pipe and a second cooling pipe. The first cooling pipe allows the heat medium to flow toward the first device evaporator, and the second cooling pipe allows the heat medium to flow toward the second device evaporator. One end of the first cooling pipe and the second cooling pipe is connected to a branch portion provided on the upstream side of the heat medium flow of the first equipment evaporator and the second equipment evaporator, and the other end is connected to a confluence portion provided on the downstream side of the heat medium flow of the first equipment evaporator and the second equipment evaporator. The second cooling pipe is configured to have a larger pressure loss when the heat medium flows than the first cooling pipe.

3. A vehicle air conditioning system for performing air conditioning on a plurality of air-conditioning zones set in a vehicle interior, characterized in that: have: a plurality of air conditioners provided corresponding to each of the plurality of air conditioning areas; and a cooling machine for cooling a target device mounted on the vehicle, Each of the plurality of air conditioners includes a vapor compression refrigeration cycle and cools the air blown to the plurality of air-conditioning areas by absorbing heat due to evaporation of a refrigerant. The cooling machine includes a cooling circuit for a heat medium to flow through for heat exchange with the target device, and utilizes the heat absorption effect of at least some of the plurality of air conditioners to cool the heat medium, thereby adjusting the temperature of the target device. When, among the plurality of air conditioners, the air conditioner that performs air conditioning on the door side area separated from the outside by the door of the vehicle is referred to as the door side air conditioner, and the air conditioner that performs air conditioning on the panel side area separated from the outside by the side panel of the vehicle is referred to as the panel side air conditioner, the amount of heat absorbed from the heat medium when the indoor cooling and the temperature control of the target device are respectively performed by the plurality of air conditioners is smaller than that of the door side air conditioner. The door-side air conditioner includes a first indoor evaporator and a first equipment evaporator. The first indoor evaporator absorbs heat from air before being blown to the door-side area to evaporate refrigerant. The first equipment evaporator is arranged in parallel with the first indoor evaporator with respect to the refrigerant flow and absorbs heat from a heat medium to evaporate the refrigerant. The panel-side air conditioner includes a second indoor evaporator and a second equipment evaporator. The second indoor evaporator absorbs heat from air before being blown out to the panel-side area to evaporate the refrigerant. The second equipment evaporator is arranged in parallel with the second indoor evaporator with respect to the refrigerant flow and absorbs heat from the heat medium to evaporate the refrigerant. The amount of heat absorbed from the heat medium during the temperature adjustment of the device is smaller than that of the first device evaporator. The vehicle air conditioning system further includes an air conditioning control unit that controls the door-side air conditioner and the panel-side air conditioner. The door-side air conditioner includes a door-side switching unit that switches between a first allowing state that allows the refrigerant to flow toward the first device evaporator and a first blocking state that blocks the refrigerant from flowing toward the first device evaporator. The panel-side air conditioner includes a panel-side switching unit configured to switch between a second allowing state for allowing the refrigerant to flow toward the second device evaporator and a second blocking state for blocking the refrigerant from flowing toward the second device evaporator. During temperature control of the device, the air conditioning control unit controls the door-side switching unit and the panel-side switching unit so that a time period in which the second permission state is maintained is shorter than a time period in which the first permission state is maintained.

4. The vehicle air conditioning system according to claim 3, wherein: When the device starts to adjust the temperature, the air conditioning control unit controls the door side switching unit and the panel side switching unit so that after a predetermined time has passed since the device switches from the first blocking state to the first allowing state, the device switches from the second blocking state to the second allowing state.

5. The vehicle air conditioning system according to claim 3, wherein: When the temperature adjustment of the device is stopped, the air conditioning control unit controls the door side switching unit and the panel side switching unit so that they switch from the first permission state to the first blocking state after a predetermined time has passed since the second permission state is switched to the second blocking state.

6. A vehicle air conditioning system for performing air conditioning on a plurality of air-conditioning zones set in a vehicle interior, characterized in that: have: a plurality of air conditioners provided corresponding to each of the plurality of air conditioning areas; and a cooling machine for cooling a target device mounted on the vehicle, Each of the plurality of air conditioners includes a vapor compression refrigeration cycle and cools the air blown to the plurality of air-conditioning areas by absorbing heat due to evaporation of a refrigerant. The cooling machine includes a cooling circuit for a heat medium to flow through for heat exchange with the target device, and utilizes the heat absorption effect of at least some of the plurality of air conditioners to cool the heat medium, thereby adjusting the temperature of the target device. When, among the plurality of air conditioners, the air conditioner that performs air conditioning on the door side area separated from the outside by the door of the vehicle is referred to as the door side air conditioner, and the air conditioner that performs air conditioning on the panel side area separated from the outside by the side panel of the vehicle is referred to as the panel side air conditioner, the amount of heat absorbed from the heat medium when the indoor cooling and the temperature control of the target device are respectively performed by the plurality of air conditioners is smaller than that of the door side air conditioner. The door-side air conditioner includes a first indoor evaporator and a first equipment evaporator. The first indoor evaporator absorbs heat from air before being blown to the door-side area to evaporate refrigerant. The first equipment evaporator is arranged in parallel with the first indoor evaporator with respect to the refrigerant flow and absorbs heat from a heat medium to evaporate the refrigerant. The panel-side air conditioner includes a second indoor evaporator and a second equipment evaporator. The second indoor evaporator absorbs heat from air before being blown out to the panel-side area to evaporate the refrigerant. The second equipment evaporator is arranged in parallel with the second indoor evaporator with respect to the refrigerant flow and absorbs heat from the heat medium to evaporate the refrigerant. The amount of heat absorbed from the heat medium during the temperature adjustment of the device is smaller than that of the first device evaporator. When the confluence point where the refrigerant passing through the first indoor evaporator and the refrigerant passing through the first equipment evaporator are joined is referred to as the first confluence point, and the confluence point where the refrigerant passing through the second indoor evaporator and the refrigerant passing through the second equipment evaporator are joined is referred to as the second confluence point, The second pressure loss ratio is greater than the first pressure loss ratio. The second pressure loss ratio is the ratio of the pressure loss from the refrigerant inlet side of the evaporator for the second device to the second confluence relative to the pressure loss from the refrigerant inlet side of the second indoor evaporator to the second confluence. The first pressure loss ratio is the ratio of the pressure loss from the refrigerant inlet side of the evaporator for the first device to the first confluence relative to the pressure loss from the refrigerant inlet side of the first indoor evaporator to the first confluence.

7. The vehicle air conditioning system according to any one of claims 1 to 6, characterized in that: The target device is a heat-generating device mounted on the vehicle.

8. The vehicle air conditioning system according to any one of claims 1 to 6, characterized in that: The door is an entry and exit door that opens and closes an entry and exit opening when passengers of the vehicle get on and off.

9. The vehicle air conditioning system according to any one of claims 3 to 6, characterized in that: The cooling circuit has a first circuit portion and a second circuit portion that are independent of each other. The first device evaporator is arranged in the first circuit portion so as to allow the heat medium flowing in the first circuit portion to pass through. The second equipment evaporator is arranged in the second circuit portion so as to allow the heat medium flowing in the second circuit portion to pass therethrough.

10. The vehicle air conditioning system according to claim 9, wherein: The target devices include a roof-side device arranged in a roof portion of the vehicle and a chassis-side device arranged in a chassis portion of the vehicle. The first circuit portion is used to allow the heat medium to flow for heat exchange with the ceiling side equipment. The second circuit portion allows a heat medium to flow for exchanging heat with the chassis-side equipment.

11. The vehicle air conditioning system according to claim 10, wherein: The ceiling-side equipment has a larger heat capacity than the chassis-side equipment.

12. The vehicle air conditioning system according to claim 9, wherein: The target device is composed of multiple devices. The cooling circuit is configured such that the number of devices that perform heat exchange with the heat medium in the second circuit portion is reduced compared to the first circuit portion.

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