Heat pump system

Abstract

A heat pump system comprises a heat pump circuit (10), a heating unit (30), a low-temperature-side heat transfer fluid circuit (40), and a control unit (70). The heat pump circuit includes a compressor (11), a condenser (12), a pressure reduction unit (14b), and an evaporator (16). The heating unit heats ventilation air to be blown into a room to be air-conditioned by using heat released by a high-pressure refrigerant in the condenser as a heat source. The low-temperature-side heat transfer fluid circuit is configured to circulate a low-temperature-side heat transfer fluid and cause the refrigerant in the evaporator to absorb heat from the low-temperature-side heat transfer fluid. It includes a heat source device (42, 45, 46) and a heat quantity adjustment unit (41, 44, 47).The control unit causes a heat transfer quantity in the heating unit to heat the ventilation air by adjusting the temperature of the low-temperature heat medium (Twl) to approach a predetermined setpoint by controlling the speed (Nc) of the compressor and the operation of at least one of the heat source device and the heat quantity adjustment unit.

Description

CROSS-REFERENCE TO RELATED APPLICATION

[0001] This application is based on Japanese Patent Application No. 2021-205661 filed on December 20, 2021, and is incorporated herein by reference. TECHNICAL FIELD

[0002] The present disclosure relates to a heat pump system having a low-temperature side heat medium circuit including a heat source device, and relates to a heat pump system that performs heating by using heat of a low-temperature side heat medium. STATE OF THE ART

[0003] Conventionally, a heat pump system has been a technology that uses a heat pump cycle including a chiller to pump up heat from a low-temperature side heat medium circulating in a low-temperature side heat medium circuit, and utilizes the pumped-up heat. For example, a technology described in Patent Literature 1 can be found as such a heat pump system.

[0004] The heat pump system in Patent Literature 1 has an auxiliary electric heater and a battery in a low-temperature side heat medium circuit, and pumps up heat generated by the auxiliary electric heater and the like in the heat pump circuit via a low-temperature side heat medium, thereby utilizing the heat to heat an interior of a vehicle cabin. PRIOR ART LITERATURE PATENT LITERATURE

[0005] Patent literature 1: WO 2013 / 013790 SUMMARY OF THE INVENTION

[0006] In a heat pump system as disclosed in Patent Literature 1, when heating the interior of the vehicle cabin using heat from the low-temperature side heat medium, a change in the situation surrounding a heating operation may affect the heating performance. For example, when a required capacity changes when heating the interior of the vehicle cabin (e.g., a change in a set temperature), a time period at which a required heating capacity is achieved may be delayed compared to a required time because the heating operation is performed via the low-temperature side heat medium.Even if an environment (a traveling speed of the vehicle or the like) is changed during the heating operation, a response to a change in the environment may be insufficient because the heating operation is carried out via the low-temperature side heat medium.

[0007] In view of the above points, an object of the present disclosure is to provide a heat pump system having a low-temperature side heat medium circuit including a heat source device, the heat pump system being capable of performing efficient heating while reducing fluctuation in heating capacity when heating is performed with heat of a low-temperature side heat medium.

[0008] A heat pump system according to one aspect of the present disclosure includes a heat pump cycle, a heating unit, a low-temperature side heat medium circuit, and a control unit. The heat pump cycle includes a compressor, a condenser, a pressure reduction unit, and an evaporator. The compressor is configured to compress and discharge a refrigerant. The condenser is configured to release heat from a high-pressure refrigerant compressed by the compressor and condense the high-pressure refrigerant. The pressure reduction unit is configured to reduce a pressure of the refrigerant discharged from the condenser. The evaporator is configured to cause the refrigerant, whose pressure is reduced by the pressure reduction unit, to absorb heat and evaporate.

[0009] The heating unit is configured to heat ventilation air blown into a space to be air-conditioned using a heat source, which is the heat released from the high-pressure refrigerant in the condenser. The low-temperature-side heat medium circuit is configured to circulate a low-temperature-side heat medium and cause the refrigerant in the evaporator to absorb heat from the low-temperature-side heat medium. The low-temperature-side heat medium circuit includes a heat source device and a heat quantity adjustment unit. The heat source device is configured to heat the low-temperature-side heat medium. The heat quantity adjustment unit is configured to adjust a heat quantity carried by the low-temperature-side heat medium. The control unit is configured to control an operation of the heat quantity adjustment unit.

[0010] The control unit is configured to cause a heat transfer amount in the heating unit for heating the ventilation air to approach a predetermined target value through adjustment at a temperature of the low-temperature side heat medium by controlling a rotation speed of the compressor and an operation of at least one of the heat source device and the heat amount adjustment unit.

[0011] According to the heat pump system, the heat of the low-temperature side heat medium circulating in the low-temperature side heat medium circuit can be pumped up through the heat pump circuit and used to heat the ventilation air in the heating unit. The heat pump system causes the heat transfer amount for heating the ventilation air in the heating unit to approach a predetermined setpoint via an adjustment at a temperature of the low-temperature side heat medium by controlling the rotational speed of the compressor and controlling an operation of at least one of the heat source device and the heat amount adjustment unit.That is, the heat pump system is capable of ensuring the ventilation air heating capacity required by the heating unit by adjusting the low-temperature side heat medium temperature by utilizing heat absorbed from the low-temperature side heat medium and heat released to the low-temperature side heat medium. According to the heat pump system, the heating capacity of the low-temperature side heat medium in the low-temperature side heat medium circuit can be effectively utilized, and thus, it is possible to appropriately cope with fluctuations in the heating capacity required by the heating unit. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] The above object and other objects, features and advantages of the present disclosure will become further apparent from the following detailed description with reference to the accompanying drawings. Fig. 1 is an overall configuration diagram of a heat pump system according to a first embodiment. Fig. 2 is a schematic configuration diagram of an indoor air conditioning unit according to the first embodiment. Fig. 3 is a block diagram showing a control system of the heat pump system according to the first embodiment. Fig. 4 is a diagram showing a functional configuration of a temperature adjustment control unit according to the first embodiment. Fig. 5 is a flowchart relating to a heat amount adjustment program during a heating operation according to the first embodiment. Fig. 6 is a graph showing a relationship between a traveling speed of a vehicle and an upper limit speed of a compressor. Fig. 7 is a characteristic diagram showing a relationship between a compressor rotation speed, a high-temperature side heat transfer amount, and a low-temperature side heat medium temperature. Fig. 8 is a characteristic diagram showing a relationship between a compressor rotation speed, a low-temperature side heat transfer amount, and a low-temperature side heat medium temperature. Fig. 9 is a diagram showing an example of an operating state when a heating request is changed. Fig. 10 is a diagram showing an example of a heating operation by the heat pump system according to the first embodiment. Fig. 11 is a flowchart relating to a heat amount adjustment program during a heating operation according to a second embodiment. Fig. 12 is a diagram showing an example of an operation state when a target value of the warm-up operation is changed according to a change in a running state of a vehicle. Fig. 13 is a diagram showing an example of an operation state when the target value of the warming operation is determined based on a stopped state of the vehicle. Fig. 14 is a diagram showing an example of a heating operation by a heat pump system according to a third embodiment. Fig. 15 is a diagram concerning a calculation of a lead preparation time in the third embodiment. Fig. 16 is a flowchart relating to a prediction function setting program in a fourth embodiment. Fig. 17 is a diagram showing an example of an operation state when a heating operation is started from a heating stop state. Fig. 18 is a diagram showing an example of a heating operation by a heat pump system according to the fourth embodiment. EMBODIMENTS FOR CARRYING OUT THE INVENTION

[0013] Hereinafter, several embodiments will be described with reference to the drawings. A part corresponding to an element described in a preceding embodiment is designated by the same reference numeral, and its description may be omitted. When only a part of a component is described in one embodiment, the other part of the component may be assumed to be the component of a preceding embodiment. In addition to the combination of components expressly described in each embodiment, it is also possible to combine components of different embodiments as long as the combination does not pose a problem even if it is not expressly described. (First embodiment)

[0014] A first embodiment in the present disclosure will be described with reference to Fig. 1 to 10. In the first embodiment, a heat pump system 1 according to the present disclosure is applied to a vehicle A. The vehicle A is a battery electric vehicle (BEV) equipped with a battery for running and running by electric power of the battery.

[0015] The heat pump system 1 of an electric vehicle performs air conditioning in a vehicle cabin, which is a space to be air-conditioned, and temperature adjustment of a battery and a heat generating device 46.

[0016] The heat pump system 1 is capable of switching between a cooling mode, a heating mode, and a dehumidification and heating mode as an air conditioning operation mode in which air conditioning is performed in the vehicle cabin. The cooling mode is an operation mode in which ventilation air blown into the vehicle cabin is cooled and blown into the vehicle cabin. The heating mode is an operation mode in which ventilation air is heated and blown into the vehicle cabin. The dehumidification and heating mode is an operation mode for performing dehumidification and heating in the vehicle cabin by reheating the cooled and dehumidified ventilation air and blowing the ventilation air into the vehicle cabin.

[0017] In a heat pump circuit 10 of the heat pump system 1, an HFO-based refrigerant (specifically, HFO1234yf) is used as a refrigerant, and a subcritical refrigeration circuit is configured in which a high-pressure side refrigerant pressure does not exceed a critical refrigerant pressure. The refrigerant contains refrigeration oil for lubricating a compressor 11. Polyalkylene glycol (PAG) oil, which is compatible with liquid-phase refrigerants, is used as the refrigeration oil. Some of the refrigeration oil circulates together with the refrigerant in a circuit.

[0018] Next, a specific configuration of the heat pump system 1 according to the first embodiment will be described with respect to Fig. 1 and Fig. 2. The heat pump system 1 according to the first embodiment includes a heat pump cycle 10, a heating unit 30, a low-temperature side heat medium cycle 40, an indoor air conditioning unit 60, and an energy manager 70.

[0019] First, the component devices that make up the heat pump cycle 10 in the heat pump system 1 will be described. The heat pump cycle 10 is a vapor-compression type refrigeration cycle. First, the compressor 11 draws in the refrigerant in the heat pump cycle 10, compresses it, and discharges it. The compressor 11 is arranged on an engine hood of a vehicle.

[0020] The compressor 11 is an electric compressor that rotates a fixed-capacity type compression mechanism with a fixed discharge capacity by an electric motor. The rotational speed (i.e., the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the power manager 70, which will be described later. In the compressor 11, an upper speed limit value Ncul is determined, and the upper speed limit value Ncul is determined to be higher as the traveling speed of the vehicle A increases. This point will be described later.

[0021] An inlet side of a refrigerant passage 12a in a heat medium / refrigerant heat exchanger 12 is connected to a discharge port of the compressor 11. The heat medium / refrigerant heat exchanger 12 is a heat exchanger that releases heat of a high-pressure refrigerant discharged from the compressor 11 to a high-temperature side heat medium circulating in a high-temperature side heat medium circuit 31 of the heating unit 30, and heats a high-temperature side heat medium.

[0022] The heat medium / refrigerant heat exchanger 12 includes the refrigerant passage 12a through which the refrigerant flows in the heat pump cycle 10, and a heat medium passage 12b through which the high-temperature-side heat medium flows in the high-temperature-side heat medium circuit 31. The heat medium / refrigerant heat exchanger 12 is formed of the same type of metal (an aluminum alloy in the first embodiment) that has excellent thermal conductivity, and components are integrated by brazing.

[0023] Accordingly, the high-pressure refrigerant flowing through the refrigerant passage 12a and the high-temperature side heat medium flowing through the heat medium passage 12b are able to exchange heat with each other. The heat medium / refrigerant heat exchanger 12 is an example of a condenser that releases heat from the high-pressure refrigerant and forms part of the heating unit 30, which will be described later.

[0024] A first connecting portion 13a, having a three-way junction structure, is connected to an outlet of the refrigerant passage 12a of the heat medium / refrigerant heat exchanger 12. In the first connecting portion 13a, one of the three inflow and outflow ports is a refrigerant inflow port, and the remaining two are refrigerant outflow ports. That is, the first connecting portion 13a is a branching portion that branches a flow of the liquid-phase refrigerant flowing out of the heat medium / refrigerant heat exchanger 12.

[0025] A refrigerant outlet port of the first connecting portion 13a is connected to a refrigerant inlet side of an air conditioning evaporator 15 via a first expansion valve 14a. The other refrigerant outlet port of the refrigerant branch portion is connected to a refrigerant inlet side of a chiller 16 via a second expansion valve 14b.

[0026] The first expansion valve 14a reduces the pressure of the refrigerant that has flowed out of one of the refrigerant outlet ports of the first connecting portion 13a, at least in an operating mode in which the ventilation air is cooled. The first expansion valve 14a is an electric variable throttle mechanism and includes a valve body and an electric actuator. The first expansion valve 14a includes a so-called electric expansion valve.

[0027] The valve body of the first expansion valve 14a is configured to change the passage opening degree (in other words, the throttle opening degree) of the refrigerant passage. The electric actuator includes a stepper motor that changes the throttle opening degree of the valve body. Operation of the first expansion valve 14a is controlled by a control signal output from the energy manager 70.

[0028] The first expansion valve 14a has a variable throttling mechanism that has a full opening function in which the refrigerant passage is fully opened when the throttle opening degree is fully open, and a full closing function in which the refrigerant passage is closed when the throttle opening degree is fully closed. That is, the first expansion valve 14a can be prevented from exerting a pressure-reducing action on the refrigerant by fully opening the refrigerant passage.

[0029] The first expansion valve 14a is capable of blocking the flow of refrigerant into the air conditioning evaporator 15 by closing the refrigerant passage. That is, the first expansion valve 14a functions both as a pressure reducing unit that reduces the pressure of the refrigerant and as a refrigerant circuit switching unit that switches a refrigerant circuit. The first expansion valve 14a is capable of adjusting the flow rate of the refrigerant flowing into the air conditioning evaporator 15 by adjusting the throttle opening degree with respect to the refrigerant passage.

[0030] An outlet of the first expansion valve 14a is connected to the refrigerant inlet side of the air conditioning evaporator 15. As shown in Fig. As shown in Figure 2, the air conditioning evaporator 15 is arranged in a housing 61 of the indoor air conditioning unit 60. At least in an operating mode in which the ventilation air is cooled, the air conditioning evaporator 15 exchanges heat between the low-pressure refrigerant, whose pressure is reduced by the first expansion valve 14a, and the ventilation air, evaporates the low-pressure refrigerant, and cools the ventilation air.

[0031] As in Fig. As shown in Figure 1, the second expansion valve 14b is connected to the other refrigerant outlet port of the first connecting portion 13a. The second expansion valve 14b reduces the pressure of the refrigerant that has flowed out from the other refrigerant outlet port of the first connecting portion 13a, at least in the heating mode.

[0032] Like the first expansion valve 14a, the second expansion valve 14b is an electric variable throttle mechanism and includes a valve body and an electric actuator. That is, the second expansion valve 14b is a so-called electric expansion valve and has a full opening and a full closing function.

[0033] That is, the second expansion valve 14b can be prevented from exerting a pressure-reducing effect on the refrigerant by fully opening the refrigerant passage. The second expansion valve 14b is capable of blocking the refrigerant from flowing into the chiller 16 by closing the refrigerant passage. That is, the second expansion valve 14b functions both as a pressure-reducing unit that reduces the pressure of the refrigerant and as a refrigerant circuit switching unit that switches a refrigerant circuit. The second expansion valve 14b is an example of the pressure-reducing unit.

[0034] An outlet of the second expansion valve 14b is connected to the refrigerant inlet side of the chiller 16. The chiller 16 is a heat exchanger that exchanges heat between the low-pressure refrigerant, whose pressure is reduced by the second expansion valve 14b, and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40.

[0035] The chiller 16 has a refrigerant passage 16a through which the low-pressure refrigerant flows, the pressure of which is reduced by the second expansion valve 14b, and a heat medium passage 16b through which the low-temperature-side heat medium circulating in the low-temperature-side heat medium circuit 40 flows. Accordingly, the chiller 16 is an evaporator that evaporates the low-pressure refrigerant and absorbs heat from the low-temperature-side heat medium through heat exchange between the low-pressure refrigerant flowing through the refrigerant passage 16a and the low-temperature-side heat medium flowing through the heat medium passage 16b. That is, the chiller 16 corresponds to an example of the evaporator.

[0036] As in Fig. As shown in FIG. 1, one refrigerant inlet side of a second connecting portion 13b is connected to a refrigerant outlet of the air conditioning evaporator 15. The other refrigerant inlet side of the second connecting portion 13b is connected to a refrigerant outlet side of the chiller 16. The second connecting portion 13b has a three-way junction structure similar to that of the first connecting portion 13a, and two of the three inflow and outflow ports are refrigerant inlets, and the remaining one is a refrigerant outlet.

[0037] Accordingly, the second connecting portion 13b is a merging portion that merges a flow of refrigerant discharged from the air conditioning evaporator 15 and a flow of refrigerant discharged from the chiller 16. A refrigerant outlet of the second connecting portion 13b is connected to a suction port side of the compressor 11.

[0038] Next, the heating unit 30 in the heat pump system 1 will be described. The heating unit 30 is configured to heat the ventilation air supplied to the space to be air-conditioned by using the high-pressure refrigerant in the heat pump cycle 10 as a heat source.

[0039] The heating unit 30 according to the first embodiment includes the high-temperature-side heat medium circuit 31. The high-temperature-side heat medium circuit 31 is a heat medium circuit that circulates the high-temperature-side heat medium, and a solution containing ethylene glycol, an antifreeze, or the like can be used as the high-temperature-side heat medium.

[0040] As in Fig. 1, in the high-temperature side heat medium circuit 31, the heat medium passage 12b of the heat medium / refrigerant heat exchanger 12, a high-temperature side pump 32, a heater core 33, a high-temperature side outside air heat exchanger 34, a high-temperature side flow rate adjusting valve 35, a high-temperature side heater 36, and the like are arranged.

[0041] As described above, in the heat medium passage 12b of the heat medium / refrigerant heat exchanger 12, the high-temperature side heat medium is heated by heat exchange with the high-pressure refrigerant flowing through the refrigerant passage 12a. That is, the high-temperature side heat medium is heated using heat pumped up by the heat pump cycle 10.

[0042] A discharge port of a high-temperature-side pump 32 is connected to an inlet side of the heat medium passage 12b of the heat medium-refrigerant heat exchanger 12. The high-temperature-side pump 32 is a heat medium pump that pumps the high-temperature-side heat medium to circulate the high-temperature-side heat medium in the high-temperature-side heat medium circuit 31. The high-temperature-side pump 32 is an electric pump whose rotation speed (i.e., a pumping capacity) is controlled by a control signal output from the energy manager 70.

[0043] The high-temperature-side heater 36 is connected to an outlet side of the heat medium passage 12b of the heat medium / refrigerant heat exchanger 12. The high-temperature-side heater 36 generates heat by being supplied with electric power and heats the high-temperature-side heat medium flowing through a heat medium passage of the high-temperature-side heater 36. For example, a PTC heater having a PTC element (i.e., a positive characteristic thermistor) can be used as the high-temperature-side heater 36. The high-temperature-side heater 36 is capable of freely adjusting a heat amount for heating the high-temperature-side heat medium according to a control voltage output from the power manager 70.

[0044] An inlet port of the high-temperature-side flow rate adjusting valve 35 is connected to an outlet side of the heat medium passage of the high-temperature-side heater 36. The high-temperature-side flow rate adjusting valve 35 comprises a three-way electric flow rate adjusting valve having three inlet and outlet ports.

[0045] An inlet port of the heater core 33 is connected to an outlet port of the high-temperature side flow rate adjustment valve 35. The heater core 33 is a heat exchanger that heats the ventilation air by exchanging heat between the high-temperature side heat medium heated by the heat medium / refrigerant heat exchanger 12 and the like and the ventilation air that has passed through the air conditioning evaporator 15. As shown in Fig. As shown in Figure 2, the heater core 33 is disposed in the housing 61 of the indoor air conditioning unit 60. Accordingly, the heater core 33 corresponds to an example of a heating heat exchanger.

[0046] One inlet port of the high-temperature-side outside air heat exchanger 34 is connected to the other outlet port of the high-temperature-side flow rate adjustment valve 35. The high-temperature-side outside air heat exchanger 34 exchanges heat between the high-temperature-side heat medium heated by the heat medium / refrigerant heat exchanger 12 and the like and outside air OA, and releases the heat of the high-temperature-side heat medium to the outside air OA.

[0047] The high-temperature-side outside air heat exchanger 34 is arranged on a front side near the engine hood of the vehicle. As the vehicle A travels, the outside air OA flows from a vehicle front to a vehicle rear and passes through a heat exchange unit of the high-temperature-side outside air heat exchanger 34. Accordingly, the high-temperature-side outside air heat exchanger 34 is capable of releasing heat to the outside air OA by utilizing the wind.

[0048] A high-temperature side merging portion of a three-way node structure is connected to an outflow port of the high-temperature side outside air heat exchanger 34 and an outflow port of the heater core 33. In the high-temperature side merging portion, one of the three inflow and outflow ports in the three-way node structure is an outflow port, and the remaining two are inflow ports. Accordingly, the high-temperature side merging portion is capable of merging a flow of the high-temperature side heat medium that has passed through the high-temperature side outside air heat exchanger 34 and a flow of the high-temperature side heat medium that has passed through the heater core 33. A suction port of the high-temperature side pump 32 is connected to the outflow port at the high-temperature side merging portion.

[0049] Thus, in the high-temperature-side heat medium circuit 31 in the first embodiment, the high-temperature-side outside air heat exchanger 34 and the heater core 33 are connected in parallel with respect to a flow of the high-temperature-side heat medium passing through the heat medium passage 12b of the heat medium / refrigerant heat exchanger 12. In the high-temperature-side heat medium circuit 31, the high-temperature-side flow rate adjustment valve 35 is capable of continuously adjusting a flow rate ratio of a flow rate of the high-temperature-side heat medium flowing into the heater core 33 to a flow rate of the high-temperature-side heat medium flowing into the high-temperature-side outside air heat exchanger 34.

[0050] That is, by controlling an operation of the high-temperature side flow rate adjustment valve 35, it is possible to adjust a heat amount of the high-temperature side heat medium released to the outside air OA through the high-temperature side outside air heat exchanger 34 and a heat amount of the high-temperature side heat medium released to the ventilation air through the heater core 33.

[0051] Next, the low-temperature side heat medium circuit 40 in the heat pump system 1 will be described. The low-temperature side heat medium circuit 40 is a heat medium circuit that circulates the low-temperature side heat medium. A fluid similar to the high-temperature side heat medium in the high-temperature side heat medium circuit 31 can be used as the low-temperature side heat medium.

[0052] The low-temperature side heat medium circuit 40 includes the heat medium passage 16b of the chiller 16, a low-temperature side pump 41, a battery heat exchange unit 42, a low-temperature side outdoor air heat exchanger 43, a low-temperature side flow rate adjusting valve 44, a low-temperature side heater 45, a heat generating device 46, a shutter device 47, and the like. A discharge port side of the low-temperature side pump 41 is connected to an inflow port of the heat medium passage 16b of the chiller 16.

[0053] The low-temperature-side pump 41 is a heat medium pump that pumps the low-temperature-side heat medium to the heat medium passage 16b of the chiller 16 in the low-temperature-side heat medium circuit 40. A basic configuration of the low-temperature-side pump 41 is similar to that of the high-temperature-side pump 32. Since a flow rate of the low-temperature-side heat medium passing through the chiller 16 and the like can be adjusted, the low-temperature-side pump 41 corresponds to an example of a heat quantity adjustment unit.

[0054] An inlet side of a heat medium passage in the heat generating device 46 is connected to an outlet port in the heat medium passage 16b of the chiller 16. The heat generating device 46 comprises a device that generates heat from in-vehicle devices mounted in the vehicle A in connection with operation for a purpose of driving or the like. The heat generating device 46 corresponds to an example of a heat source device.

[0055] The heat generating device 46 includes an inverter INV and a motor generator MG. The heat medium passage of the heat generating device 46 is provided so that component devices can be cooled by circulating a heat medium.

[0056] The inverter (INV) is a power conversion unit that converts direct current into alternating current. The motor generator (MG) supplies driving power for driving by supplying it with electric power and generates regenerative electric power during deceleration or similar situations.

[0057] A final drive device may be used as the heat generating device 46. The final drive device is a device in which a transmission, a final gear, and a differential gear are integrated.

[0058] An inlet side of a heat medium passage 42a of the battery heat exchange unit 42 is connected to an outlet side of the heat medium passage of the heat generation device 46. The battery heat exchange unit 42 is connected to the low-temperature side heat medium circuit 40 to be cooled by the low-temperature side heat medium and is configured to maintain a temperature of a battery within a predetermined temperature range. Specifically, the low-temperature side heat medium passes through the heat medium passage 42a of the battery heat exchange unit 42 to exchange heat, so that heat generated in the battery is absorbed by the low-temperature side heat medium, and the temperature of the battery is adjusted. The battery heat exchange unit 42 and the battery correspond to an example of the heat source device.

[0059] The battery supplies power to various electrical devices of the vehicle A, and, for example, a chargeable and dischargeable secondary battery (a lithium-ion battery in the present embodiment) is used. The battery generates heat during charging and discharging. The battery is a so-called assembled battery, which is provided by stacking multiple battery cells and electrically connecting the battery cells in series or parallel. In this type of battery, output tends to decrease at low temperatures, and deterioration tends to progress at high temperatures.

[0060] Therefore, it is necessary for the temperature of the battery to be maintained within a reasonable temperature range (for example, 10°C or more and 40°C or less) in which a charge and discharge capacity of the battery can be sufficiently utilized. Therefore, in the heat pump system 1, the temperature of the battery is appropriately adjusted by controlling a flow rate or the like of the low-temperature side heat medium flowing through the battery heat exchange unit 42.

[0061] The low-temperature side flow rate adjustment valve 44 is connected to the outlet side of the heat medium passage 42a of the battery heat exchange unit 42. The low-temperature side flow rate adjustment valve 44 comprises an electric three-way flow rate adjustment valve having three inflow and outflow ports. As shown in Fig. 1, an inflow port of the low-temperature side flow rate adjusting valve 44 is connected to the outlet side of the heat medium passage 42a of the battery heat exchange unit 42.

[0062] An inflow port side of the low-temperature-side outside air heat exchanger 43 is connected to an outflow port of the low-temperature-side flow rate adjustment valve 44. The low-temperature-side outside air heat exchanger 43 is a heat exchanger that exchanges heat between the low-temperature-side heat medium circulating in the low-temperature-side heat medium circuit 40 and the outside air OA blown by an outside air fan 43a. The low-temperature-side outside air heat exchanger 43 is arranged on a front side near a drive device chamber. Therefore, when the vehicle is traveling, a traveling wind can be applied to the low-temperature-side outside air heat exchanger 43.

[0063] The low-temperature-side heater 45 is connected to an outlet port of the low-temperature-side outside air heat exchanger 43. The low-temperature-side heater 45 generates heat by being supplied with electric power and heats the low-temperature-side heat medium flowing through the heat medium passage of the low-temperature-side heater 45. The low-temperature-side heater 45 corresponds to an example of the heat source device.

[0064] A PTC heater can be used as the low-temperature-side heater 45, similar to the high-temperature-side heater 36. The low-temperature-side heater 45 is capable of freely adjusting the amount of heat for heating the high-temperature-side heat medium according to a control voltage output from the power manager 70. A suction port side of the low-temperature-side pump 41 is connected to a discharge port of the heat medium passage of the low-temperature-side heater.

[0065] One end of a bypass flow path for circulating the low-temperature side heat medium to bypass the low-temperature side outside air heat exchanger 43 is connected to the other outlet port of the low-temperature side flow rate adjustment valve 44. A junction portion of a three-way node structure is connected to the other end of the bypass flow path. In the junction portion, two of the three inflow and outflow ports in the three-way node structure are inflow ports, and the remaining one is an outflow port.

[0066] The merging portion is arranged in a heat medium flow path connecting the outflow port of the low-temperature-side outside air heat exchanger 43 and an inflow port of the low-temperature-side heater 45. Accordingly, the merging portion merges a flow of the low-temperature-side heat medium that has flowed through the low-temperature-side outside air heat exchanger 43 and a flow of the low-temperature-side heat medium that has flowed through the bypass flow path, and causes the flow to flow to the suction port side of the low-temperature-side pump 41.

[0067] Therefore, the low-temperature-side flow rate adjustment valve 44 is capable of continuously adjusting a flow rate ratio between a flow rate of the low-temperature-side heat medium passing through the low-temperature-side outside air heat exchanger 43 and a flow rate of the low-temperature-side heat medium bypassing the low-temperature-side outside air heat exchanger 43 with respect to a flow of the low-temperature-side heat medium passing through the heat medium passage 16b of the chiller 16. That is, the low-temperature-side heat medium circuit 40 is capable of switching the flow of the low-temperature-side heat medium by controlling an operation of the low-temperature-side flow rate adjustment valve 44. The low-temperature-side flow rate adjustment valve 44 corresponds to an example of the heat quantity adjustment unit.

[0068] As in Fig. As shown in FIG. 1, in the low-temperature-side heat medium circuit 40, the outside air fan 43a and the shutter device 47 are arranged as devices for the low-temperature-side outside air heat exchanger 43. The outside air fan 43a blows the outside air OA to the low-temperature-side outside air heat exchanger 43. The outside air fan 43a is an electric blower whose rotation speed (i.e., an air blowing capacity) is controlled by a control voltage output from the power manager 70. That is, the outside air fan 43a is capable of adjusting a wind speed (an air volume) of outside air to the low-temperature-side outside air heat exchanger 43 and can be used to adjust a heat amount to the low-temperature-side heat medium. The outside air fan 43a corresponds to an example of the heat amount adjustment unit.

[0069] The shutter device 47 is arranged on a vehicle front side relative to the low-temperature side outside air heat exchanger 43. The shutter device 47 is configured to rotatably arrange a plurality of louvers in an opening portion of a frame-shaped frame. The plurality of louvers rotate together by operation of an electric actuator (not shown) to adjust an opening area in the opening portion of the frame.

[0070] Accordingly, the shutter device 47 is capable of adjusting a flow rate of the outside air OA passing through the low-temperature side outside air heat exchanger 43 and is capable of adjusting a heat exchange capacity of the low-temperature side outside air heat exchanger 43. Accordingly, the shutter device 47 corresponds to an example of the heat quantity adjustment unit.

[0071] Next, the indoor air conditioning unit 60 constituting the heat pump system 1 is described with respect to Fig. 2. In the heat pump system 1, the interior air conditioning unit 60 is a unit that blows ventilation air, whose temperature is adjusted by the heat pump circuit 10, to an appropriate location in the vehicle cabin. The interior air conditioning unit 60 is arranged within a dashboard (i.e., an instrument panel) at a frontmost portion in the vehicle cabin.

[0072] The interior air conditioning unit 60 is configured by accommodating a blower 62, the air conditioning evaporator 15, the heater core 33, and the like in an air passage provided within the casing 61 forming an outer shell thereof. The casing 61 forms an air passage for ventilation air to be blown into the vehicle cabin. The casing 61 is formed of a resin (specifically, polypropylene) that has a certain degree of elasticity and excellent strength.

[0073] As in Fig. As shown in Figure 2, an inside / outside air switching device 63 is arranged on the most upstream side of the casing 61 in a ventilation air flow. The inside / outside air switching device 63 switches and introduces inside air (air inside the vehicle cabin) and outside air (air outside the vehicle cabin) into the casing 61.

[0074] The indoor / outdoor air switching device 63 continuously adjusts the opening areas of an indoor air introduction port for introducing indoor air into the casing 61 and an outdoor air introduction port for introducing outdoor air through an indoor / outdoor air switching damper, and changes the introduction ratio of an intake air volume of indoor air and an intake air volume of outdoor air. The indoor / outdoor air switching damper is driven by an actuator for the indoor / outdoor air switching damper. Operation of the electric actuator is controlled by a control signal output from the power manager 70.

[0075] The blower 62 is arranged downstream of the inside / outside air switching device 63 in the ventilation airflow. The blower 62 comprises an electric blower that drives a multi-blade centrifugal fan by an electric motor. The blower 62 blows air drawn in by the inside / outside air switching device 63 toward an interior of the vehicle cabin. The rotational speed (i.e., the air blowing capacity) of the blower 62 is controlled by a control voltage output from the power manager 70.

[0076] Downstream of the fan 62 in the ventilation air flow, the air conditioning evaporator 15 and the heater core 33 are arranged in this order with respect to a ventilation air flow. That is, the air conditioning evaporator 15 is arranged upstream of the heater core 33 in the ventilation air flow. Accordingly, in the indoor air conditioning unit 60 of the heat pump system 1, at least a portion of the ventilation air that has passed through the air conditioning evaporator 15 can be heated by the heater core 33.

[0077] A cold air bypass passage 65 is provided in the housing 61. The cold air bypass passage 65 is an air passage through which the ventilation air that has passed through the air conditioning evaporator 15 bypasses the heater core 33 and flows downstream.

[0078] An air mix damper 64 is disposed downstream of the air conditioning evaporator 15 in the ventilation air flow and upstream of the heater core 33 in the ventilation air flow. The air mix damper 64 adjusts an air volume ratio between an air volume passing through the heater core 33 and an air volume passing through the cold air bypass passage 65 in the ventilation air after passing through the air conditioning evaporator 15.

[0079] The air mix damper 64 is driven by an electric actuator for driving the air mix damper. Operation of the electric actuator is controlled by a control signal output from the power manager 70.

[0080] A mixing chamber is provided downstream of the heater core 33 in the ventilation air flow. In the mixing chamber, ventilation air heated by the heater core 33 and ventilation air that has passed through the cold air bypass passage 65 and has not been heated by the heater core 33 are mixed.

[0081] Opening holes are arranged at the downstream portion of the casing 61 in the ventilation air flow for discharging the ventilation air (air conditioning air) mixed in the mixing chamber into the vehicle cabin. A face opening hole, a foot opening hole, and a defrost opening hole (all not shown) are provided as the opening holes.

[0082] The face vent is an opening for blowing air conditioning toward the upper body of an occupant in the vehicle cabin. The foot vent is an opening for blowing air conditioning toward the occupant's feet. The defrost vent is an opening for blowing air conditioning toward the inner surface of a window glass on a front surface of the vehicle.

[0083] The face opening hole, the foot opening hole, and the defrost opening hole are respectively connected to a face blowing port, a foot blowing port, and a defrosting blowing port (all not shown) provided in the vehicle cabin via ducts forming air passages.

[0084] Accordingly, the air mix damper 64 adjusts the air volume ratio between the air volume passing through the heater core 33 and the air volume passing through the cold air bypass passage 65, thereby adjusting the temperature of the air conditioning air mixed in the mixing chamber. Accordingly, the temperature of the ventilation air (air conditioning air) blown into the vehicle cabin from each blow port is also adjusted.

[0085] A face flap, a foot flap, and a defrost flap (all not shown) are arranged upstream of the face opening, the foot opening, and the defrost opening, respectively, in the ventilation airflow. The face flap adjusts an opening area of ​​the face opening. The foot flap adjusts an opening area of ​​the foot opening. The defrost flap adjusts an opening area of ​​the defrost opening.

[0086] The face flap, the foot flap, and the defrost flap constitute a blowing mode switching device that switches the blowing port from which the air conditioning air is blown. The face flap, the foot flap, and the defrost flap are coupled to a blowing port mode electric actuator via a linkage mechanism or the like and are rotated together. Operation of the electric actuator is controlled by a control signal output from the power manager 70.

[0087] Next, a control system of the heat pump system 1 according to the first embodiment will be described with reference to Fig. 3 and Fig. 4. The energy manager 70 controls an operation of each device constituting the vehicle A having the heat pump system 1. As shown in Fig. 3, the energy manager 70 includes a temperature adjustment control unit 71, a motion manager 80, an air conditioning manager 81, a high-temperature side manager 82, a circuit manager 83, a low-temperature side manager 84, and an information notification unit 85.

[0088] The power manager 70 is implemented by an in-vehicle computer including a processing unit, a RAM, a storage unit, an input and output interface, and a bus connecting these components. The processing unit is hardware for a calculation process combined with the RAM. The processing unit executes various operations for implementing functions of functional units described later by accessing the RAM. The storage unit includes a non-volatile storage medium. The storage unit stores various programs (such as a heat amount adjustment program) that are executed by the processing unit. A specific configuration and each functional unit of the power manager 70 will be described in detail later.

[0089] In addition to the energy manager 70, the vehicle A is equipped with a communication module 90, a navigation device 91, a user input unit 92, a plurality of consumption domains DEc and the like.

[0090] The communication module 90 is a communication module (data communication module) mounted in the vehicle A. The communication module 90 transmits and receives radio waves to and from a base station around the vehicle A through wireless communication according to a communication standard such as Long Term Evolution (LTE) and 5G. By mounting the communication module 90, the vehicle A becomes a connected vehicle that can be connected to a network NW.

[0091] The communication module 90 is capable of transmitting and receiving information to and from a cloud server 100 and the like via the network NW. The cloud server 100 is an information distribution server located in a cloud and distributes, for example, weather information and traffic information.

[0092] The navigation device 91 is an in-vehicle device that guides a travel path to a destination set by a user. The navigation device 91 performs guidance such as driving straight ahead, turning left or right, changing lanes, at an intersection, branching point, merging point, or the like through a screen display, sound playback, or the like. The navigation device 91 is capable of providing the power manager 70 with information such as a distance to a destination, a vehicle speed in each travel area, and an elevation difference as environmental information as navigation information.

[0093] The travel path may include areas with different speed ranges depending on the travel area, such as a general road or an expressway. Since the maximum speed on an expressway is higher than the maximum speed applicable to a general road, it is assumed that the battery output required for travel on the expressway is higher than that required for travel on the general road.

[0094] The travel path may include a travel area formed by a flat surface and a travel area formed by a mountainous surface. There is a case where the travel area for traveling in the mountainous area is formed by a travel area in which the vehicle climbs an incline of one or more degrees. It is assumed that the battery output required when traveling on an uphill section is greater than that when traveling on a flat surface.

[0095] The user input unit 92 is an operation device that receives an input operation from a user who is a passenger in the vehicle A. For example, a user operation of operating the navigation device 91, a user operation of switching between enabling and disabling a heating prediction, and a user operation of changing various setting values ​​related to the vehicle A are input to the user input unit 92. The user input unit 92 is capable of providing input information to the energy manager 70 based on a user operation.

[0096] For example, a steering switch provided on a spoke portion of a steering wheel, a switch and a select lever arranged on a center console or the like, and a voice input device for capturing a driver's utterance are mounted on the vehicle A as the user input unit 92. A touchscreen or the like of the navigation device 91 may function as the user input unit 92. Further, a user terminal such as a smartphone or a tablet terminal may function as the user input unit 92 by connecting it to the power manager 70 via a cable or wirelessly.

[0097] The consumption domain is an in-vehicle device group that implements various vehicle functions using electrical power from a battery or the like. A consumption domain has at least one domain manager and includes a set of in-vehicle device groups whose power consumption is managed by the domain manager. The multiple consumption domains include a travel control domain and a temperature adjustment control domain.

[0098] The travel control domain is a consumption domain for controlling a travel of the vehicle A. The travel control domain includes the motor generator MG, the inverter INV, a steering control system SCS, a braking control system BCS, and the motion manager 80.

[0099] The motor generator MG is a power source that generates driving force to cause vehicle A to travel. The inverter INV controls power flow and regeneration through the motor generator MG. The steering control system SCS controls steering of vehicle A. The braking control system BCS controls braking force generated in vehicle A.

[0100] During power flow through the motor generator MG, the inverter INV converts the direct current supplied from the battery into three-phase alternating current and supplies the three-phase alternating current to the motor generator MG. The inverter INV is capable of adjusting the frequency, current, and voltage of the alternating current and controls the driving force generated by the motor generator MG. On the other hand, during regeneration by the motor generator MG, the inverter INV converts the alternating current into direct current and supplies the direct current to the battery.

[0101] The motion manager 80 integrally controls the inverter INV, the steering control system SCS, and the brake control system BCS, and implements driving of the vehicle A according to a driver's drive operation. The motion manager 80 functions as a domain manager of the travel control domain and comprehensively manages power consumption by the motor generator MG, the inverter INV, the steering control system SCS, and the brake control system BCS.

[0102] The motion manager 80 includes a power transmission control unit 80a. The power transmission control unit 80a integrally controls the inverter INV, the steering control system SCS, and the brake control system BCS to execute control related to driving of the vehicle A.

[0103] The temperature adjustment control domain is a consumption domain that performs air conditioning of a living space of vehicle A and temperature adjustment of the battery. The temperature adjustment control domain includes a consumption domain related to the interior air conditioning unit 60, a consumption domain related to the high-temperature side heat medium circuit 31, a consumption domain related to the heat pump cycle 10, and a consumption domain related to the low-temperature side heat medium circuit 40.

[0104] The consumption domain related to the indoor air conditioning unit 60 includes component devices of the indoor air conditioning unit 60 and the air conditioning manager 81. Examples of the component devices of the indoor air conditioning unit 60 include the blower 62, the inside / outside air switching device 63, and the electric actuator of the air mix door 64. The air conditioning manager 81 is a domain manager related to the component devices of the indoor air conditioning unit 60 and comprehensively controls the component devices to achieve an air conditioning environment desired by the user. The air conditioning control unit 81a adjusts an air volume of air conditioning air and a ratio of inside air to outside air in the air conditioning air, and comprehensively manages power consumption of each component device in the indoor air conditioning unit 60.

[0105] The consumption domain related to the high-temperature side heat medium circuit 31 includes the high-temperature side pump 32, the high-temperature side flow rate adjustment valve 35, the high-temperature side heater 36, and the high-temperature side manager 82. The high-temperature side manager 82 is a domain manager related to a component device of the high-temperature side heat medium circuit 31 and controls a flow of the high-temperature side heat medium in the high-temperature side heat medium circuit 31 to be in a desired state.

[0106] The high-temperature-side manager 82 has a circuit control unit 82a, and controls, through the circuit control unit 82a, a pumping capacity of the high-temperature-side heat medium in the high-temperature-side pump 32, a flow rate balance in the high-temperature-side flow rate adjusting valve 35, and a heating amount of the high-temperature-side heat medium in the high-temperature-side heater 36.

[0107] A high-temperature-side heat medium temperature Twh, which is a temperature of the high-temperature-side heat medium circulating in the high-temperature-side heat medium circuit 31, is input to the high-temperature-side manager 82 through a plurality of temperature sensors arranged in the high-temperature-side heat medium circuit 31. Accordingly, the high-temperature-side manager 82 is capable of controlling a heat generation amount of the high-temperature-side heater 36 and the like by using the detected high-temperature-side heat medium temperature Twh.

[0108] The consumption domain related to the heat pump cycle 10 includes the compressor 11, the first expansion valve 14a, the second expansion valve 14b, and the circuit manager 83. The circuit manager 83 is a domain manager related to component devices of the heat pump cycle 10 and controls a state of the refrigerant circulating in the heat pump cycle 10 to a desired state.

[0109] The circuit manager 83 has a cycle control unit 83a and controls, through the cycle control unit 83a, the refrigerant discharge capacity (rotational speed) of the compressor 11, a pressure reduction amount of the first expansion valve 14a, and a pressure reduction amount of the second expansion valve 14b.

[0110] Detection results concerning a refrigerant temperature and a refrigerant pressure are input to the circuit manager 83 by a refrigerant temperature sensor and a refrigerant pressure sensor arranged in the heat pump cycle 10. Accordingly, the circuit manager 83 is able to adjust the rotational speed of the compressor 11, the throttle opening degree of the first expansion valve 14a, and the like by using detection values ​​of the refrigerant temperature and the refrigerant pressure.

[0111] The consumption domain related to the low-temperature side heat medium circuit 40 includes the low-temperature side pump 41, the low-temperature side flow rate adjustment valve 44, the low-temperature side heater 45, the shutter device 47, and the low-temperature side manager 84. The low-temperature side manager 84 is a domain manager related to component devices of the low-temperature side heat medium circuit 40 and controls a flow of the low-temperature side heat medium in the low-temperature side heat medium circuit 40 to be in a desired state.

[0112] The low-temperature-side manager 84 includes a circuit control unit 84a. The circuit control unit 84a controls a pumping capacity of the low-temperature-side heat medium in the low-temperature-side pump 41, a flow rate balance in the low-temperature-side flow rate adjustment valve 44, and the like. Furthermore, the circuit control unit 84a controls a heating amount of the low-temperature-side heat medium in the low-temperature-side heater 45 and an opening area in the shutter 47.

[0113] A low-temperature-side heat medium temperature Twl, which is a temperature of the low-temperature-side heat medium circulating in the low-temperature-side heat medium circuit 40, is input to the low-temperature-side manager 84 through a plurality of temperature sensors arranged in the low-temperature-side heat medium circuit 40. Accordingly, the low-temperature-side manager 84 is capable of controlling a heat generation amount of the low-temperature-side heater 45 and the like by using the detected low-temperature-side heat medium temperature Twl.

[0114] At least one of the temperature sensors that detect the low-temperature side heat medium temperature Twl is arranged on an inlet side of the heat medium passage 16b of the chiller 16 and detects the low-temperature side heat medium temperature Twl of the low-temperature side heat medium flowing into the chiller 16.

[0115] As in Fig. As shown in FIG. 3, the power manager 70 according to the first embodiment includes the temperature adjustment control unit 71, the motion manager 80, the air conditioning manager 81, the high-temperature side manager 82, the circuit manager 83, the low-temperature side manager 84, and the information notification unit 85. As described above, a battery manager, the motion manager 80, and a thermal manager are in-vehicle computers that control specific functions (for example, a driving function and a temperature adjustment function of the vehicle) and constitute a part of the power manager 70.

[0116] The temperature adjustment control unit 71 uses various types of information output from the battery manager, the motion manager 80, and the thermal manager to integrally manage electric power consumption by each consumption domain. The temperature adjustment control unit 71 includes an in-vehicle computer and forms part of the power manager 70. The temperature adjustment control unit 71 plays a major role in a control process in the power manager 70.

[0117] The information notification unit 85 is an in-vehicle computer that functions as a domain manager for notifying various information acquired from the cloud server 100 or the like, and constitutes a part of the power manager 70. A consumption domain for notifying the user of the vehicle A of information is connected to the information notification unit 85. For example, a display or speaker of the navigation device 91, a display unit arranged on the instrument panel (i.e., the instrument panel) at the frontmost portion of the vehicle cabin, and the like are connected to the information notification unit 85.

[0118] Accordingly, the information notification unit 85 is capable of displaying the information specified by the temperature adjustment control unit 71 on the display or the like of the navigation device 91. The information notification unit 85 is capable of outputting the information specified by the temperature adjustment control unit 71 from the speaker of the navigation device 91. The display, speaker, and the like of the navigation device 91 correspond to an example of an information transmission unit.

[0119] Power is supplied to the power manager 70, which is the in-vehicle computer, even when the vehicle A is in a non-driveable state (e.g., an ignition-off state). Therefore, the power manager 70 is capable of activating each functional unit and executing a predetermined operation if necessary to execute the control even during a non-use period.

[0120] As described above, in the heat pump system 1, a control sensor group is arranged to appropriately perform an air conditioning operation and a device temperature adjustment operation by the heat pump system 1. The control sensor group for controlling a control target device in the heat pump system 1 is connected to the energy manager 70. The control sensor group includes an indoor air temperature sensor, an outdoor air temperature sensor, a radiation sensor, a high pressure sensor, an evaporator temperature sensor, and a merging portion pressure sensor.

[0121] The inside air temperature sensor is an inside air temperature detection unit that detects a temperature inside the vehicle cabin (inside air temperature) Tr. The outside air temperature sensor is an outside air temperature detection unit that detects an outside air temperature of the vehicle cabin (outside air temperature) Tam. The radiation sensor is a radiation amount detection unit that detects a radiation amount As radiated into the vehicle cabin. The high-pressure sensor is a refrigerant pressure detection unit that detects a high-pressure refrigerant pressure Pd in ​​a refrigerant flow path extending from a discharge port side of the compressor 11 to an inlet side of the first expansion valve 14a or the second expansion valve 14b.

[0122] The evaporator temperature sensor is an evaporator temperature detection unit that detects a refrigerant evaporation temperature (evaporator temperature) Tefin in the air conditioning evaporator 15. The joining section pressure sensor is a refrigerant pressure detection unit that detects a refrigerant pressure in a second connecting section 13b of the heat pump cycle 10. A joining section pressure indicates a refrigerant pressure on a low-pressure side of the heat pump cycle 10.

[0123] The control sensor group further includes a battery temperature sensor, a ventilation air temperature sensor, and an intake air temperature sensor. The battery temperature sensor is a battery temperature detection unit that detects a battery temperature, which is a temperature of the battery. The battery temperature sensor includes multiple temperature detection units and detects temperatures at multiple locations on the battery. Therefore, the power manager 70 is also capable of detecting a temperature difference between parts of the battery. Furthermore, an average value of detection values ​​from the multiple temperature detection units is used as a battery temperature TBA.

[0124] The ventilation air temperature sensor is a ventilation air temperature detection unit that detects a temperature TAV of ventilation air blown into the vehicle cabin. The intake air temperature sensor is an intake air temperature detection unit that detects an intake air temperature, which is a temperature of ventilation air flowing into the air conditioning evaporator 15. The intake air temperature sensor is arranged within the housing 61 of the cabin air conditioning unit 60 and upstream of the air conditioning evaporator 15 in the ventilation air flow.

[0125] Furthermore, the control sensor group includes a plurality of heat medium temperature sensors for detecting a temperature of the heat medium in the high-temperature-side heat medium circuit 31 and the low-temperature-side heat medium circuit 40. The plurality of heat medium temperature sensors includes a first heat medium temperature sensor to a fifth heat medium temperature sensor. The first heat medium temperature sensor is arranged at an outlet portion of the heat medium passage of the high-temperature-side heater 36 and detects a temperature of the high-temperature-side heat medium flowing out of the high-temperature-side heater 36.

[0126] The second heat medium temperature sensor is arranged at an outlet portion of the high-temperature-side outside air heat exchanger 34 and detects a temperature of the high-temperature-side heat medium that has passed through the high-temperature-side outside air heat exchanger 34. The third heat medium temperature sensor is arranged at an inlet portion of the heater core 33 and detects a temperature of the high-temperature-side heat medium flowing into the heater core 33.

[0127] The fourth heat medium temperature sensor is arranged at an inlet portion of the heat medium passage 16b of the chiller 16 and detects a temperature of the low-temperature side heat medium flowing into the chiller 16. The fifth heat medium temperature sensor is arranged at an outlet portion of the low-temperature side outside air heat exchanger 43 and detects a temperature of the low-temperature side heat medium flowing out of the low-temperature side outside air heat exchanger 43.

[0128] In the temperature adjustment control unit 71 of the energy manager 70, a control unit that controls various control target devices connected as a consumption domain and a power supply domain is integrally configured. As shown in Fig. 4, in the temperature adjustment control unit 71, a configuration (hardware and software) that controls an operation of each control target device constitutes a control unit that controls an operation of each control target device.

[0129] For example, of the temperature detection control unit 71, a configuration that sets a required high-temperature side heat transfer amount Qh as a heat transfer amount from the refrigerant to the high-temperature side heat medium in the heat medium / refrigerant heat exchanger 12 by using a target blowing temperature TaO or the like when the vehicle cabin is heated constitutes a high-temperature side heat transfer amount setting unit 71a.

[0130] Of the temperature adjustment control unit 71, a configuration that sets a high-temperature side target heat medium temperature Twoh as a target value of the high-temperature side heat medium temperature Twh necessary to achieve the required high-temperature side heat transfer amount Qh when the vehicle cabin is heated constitutes a high-temperature side target heat medium temperature setting unit 71b.

[0131] Of the temperature adjustment control unit 71, a configuration that sets the upper speed limit Ncul of the compressor 11 according to the traveling speed of the vehicle A constitutes an upper speed limit setting unit 71c. The upper speed limit setting unit 71c sets an upper speed limit of the compressor 11 to be higher as the traveling speed of the vehicle A is higher.

[0132] Of the temperature adjustment control unit 71, a configuration that sets a low-temperature side target heat medium temperature Twol as a target value of the low-temperature side heat medium temperature Twl necessary to achieve a required heating capacity when heating the vehicle cabin constitutes a low-temperature side target heat medium temperature setting unit 71d. The low-temperature side target heat medium temperature setting unit 71d is set according to a relationship between the high-temperature side heat transfer amount Qh and the upper limit speed value Ncul of the compressor 11.

[0133] Of the temperature adjustment control unit 71, a configuration that estimates a future driving situation of the vehicle A in which the heat pump system 1 is mounted based on environmental information constitutes a driving situation estimation unit 71e. The future driving situation of the vehicle A indicates a future situation, such as a stop or a travel of the vehicle A, or a driving speed range when the vehicle A is traveling.

[0134] The environmental information includes information provided from the exterior of the vehicle A, and may include, for example, center information distributed from the cloud server 100 or the like. The environmental information includes weather information and road traffic information. The weather information includes information indicating an outside air temperature, a radiation amount, a radiant heat amount from a road surface, the presence or absence of rain or snow, and the like on a travel path set in the navigation device 91.

[0135] Furthermore, the environmental information of information affecting driving of vehicle A includes information generated within vehicle A. For example, information provided by the navigation device 91, the power supply domain, the consumption domain, and the like correspond to an example of the environmental information. The information provided by the navigation device 91 includes information such as the number of traffic lights (the number of times of stopping), a maximum speed, and a gradient of a road, in addition to a distance to the destination, the vehicle speed, and the elevation difference in each area.

[0136] Information provided by the user input unit 92 may be acquired as the environmental information. In this case, the information may be information input to the user input unit 92 by a user traveling in the vehicle A, or information input by a user outside the vehicle A to a user terminal acting as the user input unit 92. The information may be information input by the user in real time in response to a query from a system such as the power manager 70, or may be information indicating a setting value recorded by a user's past operation.A user input operation inputted using the user input unit 92 includes input operations of an automatic switch, an air conditioning switch, an air volume setting switch, a temperature setting switch, and the like.

[0137] The automatic switch is operated when automatic control of an air conditioning operation by the heat pump system 1 is set or canceled. The air conditioning switch is operated when the air conditioning evaporator 15 is requested to cool the ventilation air. The air conditioning switch is configured to switch whether to cool the ventilation air according to an input operation of the air conditioning switch. The air volume setting switch is operated when an air volume of the blower 62 is manually adjusted. The temperature setting switch is operated when a vehicle interior setting temperature Tset, which is a target temperature in the vehicle cabin, is set.

[0138] Of the environmental information, information provided by the consumption domain is capable of including status information indicating a state of each consumption domain. For example, the status information includes air conditioning information indicating a set temperature of an air conditioning system of the living space (hereinafter referred to as "air conditioning request information") and a current temperature, temperature information about a heat medium in a heat medium circuit, and information indicating a state (e.g., a current temperature) of the motor generator MG and the inverter INV.

[0139] The environmental information is not limited to information with a current actual measured value, but may include information with a future estimated value. In particular, a future usage plan for vehicle A can be set.

[0140] Of the temperature adjustment control unit 71, a configuration that predicts a possibility that heating is carried out in the vehicle cabin in the running vehicle A by using various kinds of information acquired as the environmental information constitutes a heating prediction unit 71f.

[0141] Next, an air conditioning operation of the heat pump system 1 in the first embodiment will be described. As described above, in the heat pump system 1 according to the first embodiment, an operation mode can be appropriately switched from various operation modes. The operation mode switching is performed by executing a control program stored in advance in the energy manager 70.

[0142] Specifically, in the control program, the target blowing temperature TaO of the ventilation air to be blown into the vehicle cabin is calculated based on a detection signal detected by an air conditioning control sensor group and an operation signal output from the user input unit 92.

[0143] In particular, the target blowing temperature TaO is calculated by the following formula F1. TaO=Kset×Tset−Kr×Tr−Kam×Tam−Ks×As+C Tset is the target temperature in the vehicle cabin set by the temperature setting switch (vehicle interior set temperature), Tr is the indoor air temperature detected by the indoor air temperature sensor, Tam is the outdoor air temperature detected by the outdoor air temperature sensor, and As is the radiation amount detected by the radiation sensor. Kset, Kr, Kam, and Ks are control gains, and C is a constant for correction.

[0144] In the control program, when the target blowing temperature TaO is lower than a predetermined reference cooling temperature α in a state where an air conditioning switch of the user input unit 92 is turned on, an air conditioning operation mode is switched to the cooling mode.

[0145] In the control program, when the target blowing temperature TaO is equal to or higher than the reference cooling temperature α in a state where the air conditioning switch of the user input unit 92 is turned on, the air conditioning operation mode is switched to the dehumidification and heating mode. When the target blowing temperature TaO is equal to or higher than the reference cooling temperature α in a state where the air conditioning switch is not turned on, the air conditioning operation mode is switched to the heating mode. (a) Cooling mode

[0146] The cooling mode is an operation mode in which the ventilation air is cooled by the air conditioning evaporator 15 using the heat pump cycle 10 and blown into the vehicle cabin. In the cooling mode, the circuit manager 83 of the energy manager 70 opens the first expansion valve 14a at a predetermined throttle opening degree and completely closes the second expansion valve 14b.

[0147] Accordingly, in the heat pump cycle 10 in the cooling mode, a circulation circuit of the refrigerant is configured to flow through the compressor 11, the heat medium / refrigerant heat exchanger 12, the first expansion valve 14a, the air conditioning evaporator 15, and the compressor 11 in this order.

[0148] In this circuit configuration, the energy manager 70 controls the operation of various control target devices connected to an output side to be in a mode suitable for the cooling mode, in accordance with the detection results of the control sensor group and the like. Specifically, the circuit manager 83 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening degree of the first expansion valve 14a, and the air conditioning manager 81 controls the air blowing capacity of the blower 62, an opening degree of the air mix door 64, and the like.

[0149] When the high-temperature side heat medium circuit 31 is in the cooling mode, the high-temperature side manager 82 controls the high-temperature side pump 32 and the high-temperature side flow rate adjustment valve 35 to be in a state suitable for the cooling mode. Accordingly, in the high-temperature side heat medium circuit 31, the high-temperature side heat medium circulates in this order through the high-temperature side pump, the heat medium / refrigerant heat exchanger 12, the high-temperature side heater 36, the high-temperature side flow rate adjustment valve 35, the high-temperature side outside air heat exchanger 34, and the high-temperature side pump 32.

[0150] In the low-temperature side heat medium circuit 40 in the cooling mode, since the low-pressure refrigerant does not flow into the chiller 16, the low-temperature side manager 84 may stop circulation of the low-temperature side heat medium in the low-temperature side heat medium circuit 40.

[0151] Accordingly, in the heat pump system 1, in the cooling mode, the ventilation air cooled by the air conditioning evaporator 15 is blown into the vehicle cabin, so that the vehicle cabin can be cooled. (b) Heating mode

[0152] The heating mode is an operation mode in which the heat pump cycle 10 is used to pump up heat of the low-temperature side heat medium, the heater core 33 heats the ventilation air, and the ventilation air is blown into the vehicle cabin. In the heating mode, the circuit manager 83 fully closes the first expansion valve 14a and opens the second expansion valve 14b at a predetermined throttle opening degree. Accordingly, in the heat pump cycle 10 in the heating mode, a refrigerant circulation circuit is configured in which the refrigerant circulates in order from the compressor 11, the heat medium / refrigerant heat exchanger 12, the second expansion valve 14b, the chiller 16, and the compressor 11.

[0153] In this circuit configuration, the energy manager 70 controls the operation of various control target devices connected to the discharge side to be in a mode suitable for the heating mode, in accordance with the detection results of the control sensor group and the like. Specifically, the circuit manager 83 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening degree of the second expansion valve 14b, and the air conditioning manager 81 controls the air blowing capacity of the blower 62, the opening degree of the air mix damper 64, and the like.

[0154] When the high-temperature side heat medium circuit 31 is in the heating mode, the high-temperature side manager 82 controls the high-temperature side pump 32, the high-temperature side flow rate adjustment valve 35, and the high-temperature side heater 36 to be in a state suitable for the heating mode. Accordingly, in the high-temperature side heat medium circuit 31, the high-temperature side heat medium circulates in this order in the high-temperature side pump 32, the heat medium / refrigerant heat exchanger 12, the high-temperature side flow rate adjustment valve 35, the high-temperature side heater 36, the heater core 33, and the high-temperature side pump 32.

[0155] At this time, the high-temperature-side manager 82 can cause a part of the high-temperature-side heat medium that has flowed from the high-temperature-side heater 36 into the high-temperature-side outside air heat exchanger 34 to flow out via the high-temperature-side outside air heat exchanger 34 to a suction port side of the high-temperature-side pump 32. Accordingly, since a part of the heat of the high-temperature-side heat medium is released to the outside air through the high-temperature-side outside air heat exchanger 34, a heating capacity of the heater core 33 can be adjusted to a desired state.

[0156] Regarding the low-temperature side heat medium circuit 40 in the heating mode, the low-temperature side manager 84 controls the low-temperature side pump 41, the outside air fan 43a, the low-temperature side flow rate adjustment valve 44, the heat generating device 46, and the shutter device 47 so that a circulation path of the low-temperature side heat medium is in a state suitable for the heating mode. Specifically, the low-temperature side manager 84 controls the pumping capacity of the low-temperature side pump 41, the air blowing capacity of the outside air fan 43a, the flow rate balance of the low-temperature side flow rate adjustment valve 44, a heat generation amount of the heat generating device 46, an opening degree of the shutter device 47, and the like.

[0157] Accordingly, in the low-temperature side heat medium circuit 40, the low-temperature side heat medium circulates in this order in the low-temperature side pump 41, the chiller 16, the heat generating device 46, the battery heat exchange unit 42, the low-temperature side flow rate adjusting valve 44, the low-temperature side outside air heat exchanger 43, the low-temperature side heater 45, and the low-temperature side pump 41.

[0158] According to this aspect, heat released from the battery and the heat generating device 46 can be stored in the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40 and can be used as a heat source for heating the vehicle cabin. The low-temperature side manager 84 is capable of adjusting the heat amount for heating the low-temperature side heat medium by the low-temperature side heater 45, and is capable of adjusting the heat amount to be exchanged between the low-temperature side heat medium and the outside air in the low-temperature side outside-air heat exchanger 43 by the outside air fan 43a and the shutter device 47. Accordingly, the heat amount of the low-temperature side heat medium can be adjusted to a desired state, and a heat source for heating can be ensured.

[0159] The heat pump system 1 in the heating mode is capable of performing a heating operation in which the heat of the low-temperature side heat medium in the low-temperature side heat medium circuit 40 in the heat pump cycle 10 is pumped up and used to heat the ventilation air via the high-temperature side heat medium circuit 31. (c) Dehumidification and heating mode

[0160] The dehumidification and heating mode is an operation mode in which the ventilation air cooled by the air conditioning evaporator 15 is heated by the heater core 33 using the heat pump cycle 10 and blown into the vehicle cabin. In the dehumidification and heating mode, the circuit manager 83 opens the first expansion valve 14a and the second expansion valve 14b at a predetermined throttle opening degree.

[0161] Accordingly, in the heat pump cycle 10 in the dehumidification and heating mode, the refrigerant circulates in this order in the compressor 11, the heat medium / refrigerant heat exchanger 12, the first expansion valve 14a, the air conditioning evaporator 15, and the compressor 11. At the same time, the refrigerant circulates in this order in the compressor 11, the heat medium / refrigerant heat exchanger 12, the second expansion valve 14b, the chiller 16, and the compressor 11. That is, in the heat pump cycle 10 in the dehumidification and heating mode, a refrigerant circulation circuit is configured in which the air conditioning evaporator 15 and the chiller 16 are connected in parallel with the flow of the refrigerant flowed out from the heat medium / refrigerant heat exchanger 12.

[0162] In this circuit configuration, the energy manager 70 controls the operation of various control target devices connected to the discharge side to be in a mode suitable for the dehumidification and heating mode, in accordance with detection results from the control sensor group and the like. Specifically, the circuit manager 83 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening degrees of the first expansion valve 14a and the second expansion valve 14b, and the air conditioning manager 81 controls the air blowing capacity of the blower 62, the opening degree of the air mix damper 64, and the like.

[0163] When the high-temperature side heat medium circuit 31 is in the dehumidification and heating mode, the high-temperature side manager 82 controls the high-temperature side pump 32, the high-temperature side flow rate adjustment valve 35, and the high-temperature side heater 36 to be in a state suitable for the dehumidification and heating mode. Accordingly, in the high-temperature side heat medium circuit 31, the high-temperature side heat medium circulates in this order in the high-temperature side pump 32, the heat medium / refrigerant heat exchanger 12, the high-temperature side flow rate adjustment valve 35, the high-temperature side heater 36, the heater core 33, and the high-temperature side pump 32.

[0164] For the low-temperature side heat medium circuit 40 in the dehumidification and heating mode, the low-temperature side manager 84 controls the low-temperature side pump 41, the outside air fan 43a, the low-temperature side flow rate adjustment valve 44, and the shutter 47 to be in a state suitable for the dehumidification and heating mode. Specifically, the low-temperature side manager 84 controls the pumping capacity of the low-temperature side pump 41, the air blowing capacity of the outside air fan 43a, the flow rate balance of the low-temperature side flow rate adjustment valve 44, the heat generation amount of the heat generation device 46, the opening degree of the shutter 47, and the like.

[0165] As a result, in the low-temperature side heat medium circuit 40, the low-temperature side heat medium circulates in this order in the low-temperature side pump 41, the chiller 16, the heat generating device 46, the battery heat exchange unit 42, the low-temperature side flow rate adjusting valve 44, the low-temperature side outside air heat exchanger 43, the low-temperature side heater 45, and the low-temperature side pump 41.

[0166] According to this aspect, heat released from the battery and the heat generating device 46 can be stored in the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40 and can be used as a heat source for heating the vehicle cabin. The low-temperature side manager 84 is capable of adjusting the heat amount for heating the low-temperature side heat medium by the low-temperature side heater 45, and is capable of adjusting the heat amount to be exchanged between the low-temperature side heat medium and the outside air in the low-temperature side outside-air heat exchanger 43 by the outside air fan 43a and the shutter device 47. Accordingly, the heat amount of the low-temperature side heat medium can be adjusted to a desired state, and a heat source for heating can be ensured.

[0167] The heat pump system 1 in the dehumidification and heating mode is capable of performing a dehumidification and heating operation in which the ventilation air dehumidified by the air conditioning evaporator 15 is heated by using the heat of the low-temperature side heat medium in the low-temperature side heat medium circuit 40.

[0168] Next, processing contents of the heat quantity adjustment program according to the first embodiment will be described with respect to Fig. 5 to 8. The heat amount adjustment program according to the first embodiment is executed to appropriately adjust various heat amounts used as a heat source for heating the vehicle cabin during the heating operation in the heat pump system 1.

[0169] As described above, the heat amount adjustment program according to the first embodiment is stored in the storage unit of the energy manager 70 and is read out and executed by the temperature adjustment control unit 71 which constitutes the processing unit.

[0170] As in Fig. 5, first, at step S1, the target blowing temperature TaO is set. The target blowing temperature TaO is a set value concerning a temperature of the ventilation air supplied to the vehicle cabin during heating, which is the space to be air-conditioned. As described above, the target blowing temperature TaO is calculated according to the vehicle interior set temperature Tset, the inside air temperature Tr, the outside air temperature Tam, the radiation amount As, and the like, and according to the formula F1.

[0171] At step S2, the high-temperature-side target heat medium temperature Twoh is set, which is a temperature of the high-temperature-side heat medium necessary to achieve the target blowing temperature TaO. The high-temperature-side target heat medium temperature Twoh is calculated using an intake air temperature related to the heater core 33, a blowing air volume supplied into the vehicle cabin, the target blowing temperature TaO, and the like. The intake air temperature related to the heater core 33 is calculated using an inside / outside air ratio in the inside / outside air switching device 63, the inside air temperature Tr, the outside air temperature Tam, and the like.

[0172] At step S3, the upper limit speed Ncul of the compressor 11 in the heat pump cycle 10 is determined according to the traveling speed of the vehicle A. The upper limit speed Ncul of the compressor 11 means an upper limit of the refrigerant discharge capacity of the compressor 11, and a speed Nc of the compressor 11 is controlled so as not to exceed the upper limit speed Ncul.

[0173] In the first embodiment, the upper speed limit value Ncul of the compressor 11 is determined according to a control map stored in the storage unit of the energy manager 70. As shown in Fig. 6, in the control map, the traveling speed of the vehicle A is linked to be proportional to the upper limit speed Ncul of the compressor 11, and it is determined that the higher the traveling speed of the vehicle A, the larger the upper limit speed Ncul of the compressor 11.

[0174] Accordingly, at step S3, the upper speed limit value Ncul of the compressor 11 in the heat pump cycle 10 is determined based on information about the traveling speed of the vehicle A obtained from the motion manager 80 and the control map shown in Fig. 6 is shown.

[0175] In the first embodiment, as shown in Fig. 6, the traveling speed of the vehicle A and the upper limit speed Ncul of the compressor 11 are determined to be in a proportional relationship, but the invention is not limited to this aspect. Various aspects can be employed as long as a relationship is such that the higher the traveling speed of the vehicle A, the larger the upper limit speed Ncul of the compressor 11. For example, two or more upper limit speeds Ncul may be linked according to the traveling speed range, such as the upper limit speed Ncul when the traveling speed of the vehicle A is low and the upper limit speed Ncul when the traveling speed of the vehicle A is high.

[0176] At step S4, the low-temperature-side target heat medium temperature Twol necessary to achieve the target blowing temperature TaO is set. As described above, in the heating operation of the heat pump system 1, the heat of the low-temperature-side heat medium is pumped up through the heat pump cycle 10 to the high-temperature-side heat medium circuit 31 and is used to heat the ventilation air in the heater core 33. Accordingly, the low-temperature-side target heat medium temperature Twol is set according to a target value of a heat amount usable as the heating heat source in the low-temperature-side heat medium circuit 40.

[0177] When the low-temperature side target heat medium temperature Twol is set, the high-temperature side heat transfer amount Qh is first calculated. The high-temperature side heat transfer amount Qh is a heat amount heat transferred from the high-pressure refrigerant to the high-temperature side heat medium in the heat medium / refrigerant heat exchanger 12, and means a heat amount necessary to reach the target blowing temperature TaO. The high-temperature side heat transfer amount Qh is calculated using, for example, the target blowing temperature TaO, the intake air temperature with respect to the heater core 33, and the blowing air volume supplied into the vehicle cabin, and is calculated by multiplying a temperature difference between the target blowing temperature TaO and the intake air temperature by the blowing air volume supplied into the vehicle cabin.

[0178] In the heat pump system 1, from the high-temperature side heat transfer amount Qh, the upper speed limit value Ncul of the compressor 11, the low-temperature side heat medium temperature Twl and the low-temperature side heat transfer amount Ql, relationships are recognized, which are shown in Fig. 7 and Fig. 8 are shown. In Fig. 7 and Fig. 8, five values ​​are determined as the upper limit speed Ncul of the compressor 11, and the values ​​are shown in the order of the smaller upper limit speed Ncul of Nca, Ncb, Ncc, Ncd, and Nce.

[0179] The high-temperature side heat transfer amount Qh corresponding to the predetermined target blowing temperature TaO is referred to as a high-temperature side heat transfer amount Qha, and the high-temperature side heat transfer amount Qh corresponding to a higher target blowing temperature TaO is referred to as a high-temperature side heat transfer amount Qhb. Fig. 7 and Fig. In Figure 8, Qla, Qlb, and Qlc are shown as the low-temperature side heat transfer amount Ql, and the low-temperature side heat transfer amount Qla corresponds to a low-temperature side heat medium temperature Twla. That is, the low-temperature side heat transfer amount Qla and the high-temperature side heat transfer amount Qha are related to each other via the low-temperature side heat medium temperature Twla. The low-temperature side heat transfer amount Qlc corresponds to a low-temperature side heat medium temperature Twlb. Accordingly, the low-temperature side heat transfer amount Qlc and the high-temperature side heat transfer amount Qhb are related to each other via the low-temperature side heat medium temperature Twlb.

[0180] As in Fig. 7 and Fig. As shown in Figure 8, in the heat pump system 1, the high-temperature-side heat transfer amount Qh, which is determined to achieve the target blowing temperature TaO, is linked to the low-temperature-side heat medium temperature Twl for each upper limit speed value Ncul of the compressor 11. A correspondence is made such that the larger the high-temperature-side heat transfer amount Qh, the higher the low-temperature-side heat medium temperature Twl.

[0181] In the heat pump system 1, the heat amount pumped up from the low-temperature side heat medium through the chiller 16 is used to heat the high-temperature side heat medium in the heat medium / refrigerant heat exchanger 12. Accordingly, the high-temperature side heat transfer amount Qh determined as described above corresponds to the low-temperature side heat transfer amount QI, which is a heat transfer amount from the low-temperature side heat medium to the low-pressure refrigerant in the chiller 16.

[0182] That is, the low-temperature side heat transfer amount QI determined to achieve the target blowing temperature TaO is also related to the low-temperature side heat medium temperature Twl for each upper speed limit Ncul of the compressor 11. Specifically, as the upper speed limit of the compressor 11 increases in the order of Nca, Ncb, Ncc, Ncd, and Nce, the low-temperature side heat medium temperature Twl decreases.

[0183] By using the relationships defined in Fig. 7 and Fig. 8, for example, consider a case where the high-temperature side heat transfer amount Qh required during the heating operation increases from Qha to Qhb. It is understood that in a state where the upper speed limit Ncul of the compressor 11 is Nce, a requirement for the high-temperature side heat transfer amount Qhb cannot be met unless the low-temperature side heat medium temperature Twl is increased from Twla to Twlb. Accordingly, in this case, Twlb is determined as the low-temperature side target heat medium temperature Twol.

[0184] Next, consider a case where the upper speed limit Ncul of the compressor 11 is limited from Nce to Ncd in a state where the high-temperature side heat transfer amount Qh required during the heating operation is Qha. In this case, it is understood that in a state where the upper speed limit Ncul of the compressor 11 is Ncd and the low-temperature side heat medium temperature is Twla, the required high-temperature side heat transfer amount Qha is insufficient.

[0185] From these relationships, which Fig. 7 and Fig. 8, it is understood that in order to achieve the required high-temperature side heat transfer amount Qha in a state where the upper limit speed Ncul of the compressor 11 is limited to Ncd, it is necessary to increase the low-temperature side heat medium temperature Twl from Twla to Twlc. That is, in this case, Twlc is determined as the low-temperature side target heat medium temperature Twol.

[0186] Accordingly, at step S4, the low-temperature side heat transfer amount QI and the low-temperature side target heat medium temperature Twol for achieving the set high-temperature side heat transfer amount Qh are determined under a condition that the refrigerant discharge capacity of the compressor 11 agrees with the upper speed limit value Ncul set at step S3. As understood from the relationships shown in Fig. 7 and Fig. 8, as the upper speed limit value Ncul of the compressor 11, the low-temperature side target heat medium temperature Twol for achieving the high-temperature side heat transfer amount Qh is individually linked to two or more values.

[0187] Proceeding to step S5, it is determined whether the current low-temperature side heat medium temperature Twl is equal to or lower than a predetermined reference value KTwl. The reference value KTwl represents an upper limit of the low-temperature side heat medium temperature Twl, which is determined by a relationship with the component devices of the low-temperature side heat medium circuit 40. Therefore, in step S5, it is determined whether the low-temperature side heat medium has an excess amount of heat with respect to the heating operation.

[0188] When the low-temperature-side heat medium temperature Twl is equal to or lower than the reference value KTwl, the process proceeds to step S6, and low-temperature-side heat storage control is executed. The low-temperature-side heat storage control controls operation of the component devices of the low-temperature-side heat medium circuit 40 to store waste heat of the heat generating device 46 and the like as much as possible in the low-temperature-side heat medium circulating in the low-temperature-side heat medium circuit 40. Specifically, waste heat generated by operation of the heat generating device 46, heat generated by input and output of the battery via the battery heat exchange unit 42, heat generated by the low-temperature-side heater 45, and the like are stored in the low-temperature-side heat medium.When the low-temperature side heat storage control ends, the process proceeds to step S8.

[0189] On the other hand, if the low-temperature side heat medium temperature Twl is higher than the reference value KTwl, the process proceeds to step S7, and a low-temperature side heat release control is executed. The low-temperature side heat release control controls the operation of the component devices of the low-temperature side heat medium circuit 40 to release excess heat of the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40 to the outside air OA.

[0190] Specifically, the low-temperature-side heat release control is implemented by controlling a heat exchange capacity between the low-temperature-side heat medium in the low-temperature-side outside air heat exchanger 43 and the outside air OA. For example, the heat exchange capacity between the low-temperature-side heat medium and the outside air can be adjusted by adjusting a flow rate of the low-temperature-side heat medium passing through the low-temperature-side outside air heat exchanger 43 by a pumping amount of the low-temperature-side heat medium by the low-temperature-side pump 41.The heat exchange capacity of the low-temperature-side outside air heat exchanger 43 can be adjusted by adjusting a flow rate balance of the low-temperature-side heat medium flowing into the low-temperature-side outside air heat exchanger 43 through the low-temperature-side flow rate adjustment valve 44. The heat exchange capacity can be adjusted by adjusting an opening area of ​​the shutter 47 and a blowing air volume of the outside air fan 43a, and by adjusting a flow rate of the outside air OA passing through the low-temperature-side outside air heat exchanger 43. When the low-temperature-side heat release control ends, the process proceeds to step S8.

[0191] In other words, the low-temperature-side heat storage control at step S6 can be referred to as a control for reducing the amount of heat released to the outside air OA with respect to heat from the low-temperature-side heat medium. Therefore, in the low-temperature-side heat storage control, the low-temperature-side pump 41, the low-temperature-side flow rate adjusting valve 44, the outside air fan 43a, and the shutter device 47 in the low-temperature-side heat medium circuit 40 are operated in a manner opposite to the low-temperature-side heat release control.

[0192] At step S8, it is determined whether the high-temperature side heat medium temperature Twh is equal to or lower than the high-temperature side target heat medium temperature Twh. That is, it is determined whether the heat of the high-temperature side heat medium is sufficient with respect to the heating operation targeting the target blowing temperature TaO.

[0193] When the high-temperature side heat medium temperature Twh is equal to or lower than the high-temperature side target heat medium temperature Twoh, speed control via the compressor 11 is executed because the heat of the high-temperature side heat medium is insufficient for the heating operation targeting the target blowing temperature TaO. In speed control via the compressor 11, the speed of the compressor 11 is controlled so that the high-temperature side heat medium temperature Twh of the high-temperature side heat medium flowing through the heat medium / refrigerant heat exchanger 12 approaches the high-temperature side target heat medium temperature Twoh determined based on the target blowing temperature TaO.

[0194] Accordingly, a heat absorption amount from the low-temperature side heat medium to the refrigerant in the chiller 16 and a heat release amount from the high-pressure refrigerant to the high-temperature side heat medium in the heat medium / refrigerant heat exchanger 12 are adjusted using the refrigerant discharge capacity of the compressor 11 as an index. The refrigerant discharge capacity of the compressor 11 is adjusted so that the high-temperature side heat medium temperature Twh approaches the target high-temperature side heat medium temperature Twoh. As a result, since the heat absorption amount from the low-temperature side heat medium in the chiller 16 is also adjusted, it can be said that the low-temperature side heat medium temperature Twl is adjusted.

[0195] According to the heat pump system 1, since the operation is performed under the conditions of the processes from step S5 to step S7, it is possible to reduce energy consumption related to the operation of the heat pump cycle 10. When the speed control over the compressor 11 ends, the process proceeds to step S11.

[0196] On the other hand, when the high-temperature side heat medium temperature Twh is higher than the high-temperature side target heat medium temperature Twoh, high-temperature side heat release control is executed at step S10 to release excess heat of the high-temperature side heat medium with respect to the heating operation targeting the target blowing temperature TaO. In the high-temperature side heat release control, an operation of component devices of the high-temperature side heat medium circuit 31 is controlled so that the high-temperature side heat medium temperature Twh approaches the high-temperature side target heat medium temperature Twoh.

[0197] Specifically, the high-temperature-side heat release control is implemented by controlling a heat exchange capacity between the high-temperature-side heat medium in the high-temperature-side outside air heat exchanger 34 and the outside air OA. The heat exchange capacity between the high-temperature-side heat medium and the outside air can be adjusted, for example, by adjusting a flow rate of the high-temperature-side heat medium passing through the high-temperature-side outside air heat exchanger 34 by a pumping amount of the high-temperature-side heat medium by the high-temperature-side pump 32. The heat exchange capacity of the high-temperature-side outside air heat exchanger 34 can be adjusted by adjusting a flow rate balance of the high-temperature-side heat medium flowing into the high-temperature-side outside air heat exchanger 34 by the high-temperature-side flow rate adjustment valve 35.When the high-temperature side heat release control ends, the process returns to step S1.

[0198] At step S11, in the speed control of the compressor 11, it is determined whether the speed Nc of the compressor 11 is the upper speed limit value Ncul set at step S3. That is, it is determined whether a maximum refrigerant discharge capacity of the compressor 11 is used in the speed control of the compressor 11. If the speed Nc of the compressor 11 is not the upper speed limit value Ncul, it is determined that there is a margin in the refrigerant discharge capacity due to the performance of the compressor 11, and the process returns to step S1.

[0199] On the other hand, when the rotational speed Nc of the compressor 11 is the upper limit speed value Ncul, heat amount adjustment control is executed in the low-temperature-side heat medium circuit 40 at step S12. When the process proceeds to step S12, the compressor 11 is operated at the upper limit speed value Ncul by using heat of the low-temperature-side heat medium at a current time as a heat source, and the low-temperature-side heat medium temperature Twl is lower than the low-temperature-side target heat medium temperature Twol.

[0200] Therefore, to ensure the heat quantity required to reach the target blowing temperature TaO, heat quantity adjustment control is executed, in which the component devices in the low-temperature side heat medium circuit 40 are operated to intentionally generate heat. Specifically, for example, the inverter INV and the like, which are the heat generation devices 46, are operated in an inefficient manner different from normal, thereby increasing the amount of heat generation from normal. Regarding the battery, input and output to and from the battery are performed inefficiently, thereby increasing the amount of heat generation in the battery and increasing heat of the low-temperature side heat medium via the battery heat exchange unit 42.By heating the low-temperature side heat medium with the low-temperature side heater 45, the temperature can be adjusted to the low-temperature side target heat medium temperature Two1. When the heat amount adjustment control ends, the process returns to step S1.

[0201] Thus, by executing the heat quantity adjustment control at step S12 on the low-temperature-side heat medium circuit 40, the low-temperature-side heat medium temperature Twl can be adjusted to the low-temperature-side target heat medium temperature Twol. The heat of the low-temperature-side heat medium is pumped up through the heat pump circuit 10 and used to heat the high-temperature-side heat medium. That is, the heat quantity adjustment control at step S12 adjusts the low-temperature-side heat medium temperature Twl so that the low-temperature-side heat medium temperature Twl approaches the high-temperature-side target heat medium temperature Twoh.

[0202] By executing the heat amount adjustment program, the heat pump system 1 is able to secure the heat amount on one side of the low-temperature side heat medium circuit 40 necessary for the heating operation aiming at the target blowing temperature TaO, and is able to utilize the heat on the side of the low-temperature side heat medium circuit 40 when the heating operation is performed.

[0203] Next, effects of the heat quantity adjustment program according to the first embodiment with respect to Fig. 9 and Fig. 10 described. Fig. 9 is a comparative example for clarifying the effect of the heat amount adjustment program, and shows an operation of the heat pump system 1 concerning the heating operation when heat amount adjustment is not performed in the low-temperature side heat medium circuit 40 or the like.

[0204] In the example shown in Fig. As shown in Figure 9, a basic configuration of the heat pump system 1 is similar to that of the above-described embodiment, and a control mode of each component device during the heating operation is different from that of the first embodiment. As a precondition for the heat pump cycle 10 in the heating operation shown in Fig. 9, assume that the high-temperature side heat transfer amount Qh necessary to reach the target blowing temperature TaO is Qha and the rotational speed of the compressor 11 is operated at the upper limit speed Ncul.

[0205] As a precondition of the low-temperature side heat medium circuit 40, it is assumed that waste heat from the heat generating device 46 and the like is sufficient, and part of the heat of the low-temperature side heat medium is released to the outside air via the low-temperature side outside air heat exchanger 43. It is assumed that the low-temperature side heat medium temperature Twl is adjusted to the low-temperature side heat medium temperature Twla corresponding to the high-temperature side heat transfer amount Qha by releasing heat to the outside air OA.

[0206] In a state according to this precondition, since the heat of the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40 is capable of securing a sufficient amount of heat with respect to a required value at the high-temperature side heat transfer amount Qha, the heating operation at this time can be implemented at the target blowing temperature TaO.

[0207] A case where the vehicle interior set temperature Tset is set higher from the warming operation in a state according to the precondition is considered. In Fig. 9 and Fig. 10 is a time when the vehicle interior setting temperature Tset is set to be higher than a setting temperature change time tc.

[0208] In Fig. 9, as indicated by an alternating long and short dashed line, when the vehicle interior set temperature Tset is set to be higher at the set temperature change time tc, the target blowing temperature TaO is changed to be higher, and accordingly, the high-temperature side heat transfer amount Qh increases from Qha to Qhb. On the other hand, since the actual high-temperature side heat transfer amount Qh remains at Qha at the set temperature change time tc, the actual high-temperature side heat transfer amount Qh remains in a state according to the precondition.

[0209] With the change from the high-temperature side heat transfer amount Qha to Qhb, the heat amount on the low-temperature side heat medium circuit 40 becomes insufficient. Therefore, the heat release amount to the outside air OA in the low-temperature side outside air heat exchanger 43 is reduced to increase the low-temperature side heat medium temperature Twl from Twla. At this time, in the heat pump circuit 10, the compressor 11 is operated at the upper speed limit Ncul as in a case of the precondition. As shown in Fig. 9, the low-temperature side heat medium temperature Twl gradually increases from a time when the heat release amount to the outside air OA is reduced, and reaches the low-temperature side heat medium temperature Twlb corresponding to the high-temperature side heat transfer amount Qhb after the setting change.

[0210] Thus, when an attempt is made to match a change in the high-temperature side heat transfer amount Qh required with the setting change by a change in a heat amount in the low-temperature side heat medium circuit 40 (i.e., the low-temperature side heat medium temperature Twl), a response delay of the low-temperature side heat medium temperature Twl occurs. Therefore, it is assumed that a desired heating capacity cannot be achieved from the setting temperature change time tc until the requirement for the high-temperature side heat transfer amount Qh after the change is met, and comfort in the vehicle cabin cannot be sufficiently improved.

[0211] Next, an operation of the heating operation when the heat amount adjustment program according to the first embodiment is applied will be described with reference to Fig. 10. In a case described in Fig. 10 is like a case shown in Fig. 9, assume that the high-temperature side heat transfer amount Qh is the high-temperature side heat transfer amount Qha before the set temperature change time tc and is changed to the high-temperature side heat transfer amount Qhb by changing the vehicle interior set temperature Tset to be higher at the set temperature change time tc.

[0212] As described in steps S5 and S6 of the heat amount adjustment program in the first embodiment, when the low-temperature side heat medium temperature Twl is equal to or lower than the reference value KTwl, the low-temperature side heat storage control is executed. Therefore, until the reference value KTwl is reached as an upper limit of the low-temperature side heat medium temperature Twl, waste heat from the heat generating device 46 and the battery is stored in the low-temperature side heat medium. That is, before the set temperature change time tc, the low-temperature side heat medium temperature Twl is maintained equal to or higher than the low-temperature side heat medium temperature Twla corresponding to the high-temperature side heat transfer amount Qha.

[0213] By keeping the low-temperature side heat medium temperature Twl high, it is possible to keep the rotational speed Nc of the compressor 11 low, and it is possible to keep the rotational speed Nc in a state where there is a margin with respect to the upper limit speed value Ncul.

[0214] According to the heat quantity adjustment program in the first embodiment, until the low-temperature side heat medium temperature Twl becomes equal to or lower than the reference value KTwl, waste heat of the heat generating device 46 or the like can be stored in the low-temperature side heat medium. Therefore, the heat pump system 1 is capable of creating a state in which there is a margin with respect to the upper speed limit value Ncul with respect to an operating state of the compressor 11.

[0215] Accordingly, even if the high-temperature side heat transfer amount Qh increases with a change in the vehicle interior set temperature Tset at the set temperature change time tc from Qha to Qhb, the high-temperature side heat transfer amount Qhb can be achieved by increasing the rotational speed Nc of the compressor 11. As a result, as shown in Fig. 10, the heat pump system 1 is capable of quickly changing the heating capacity in response to a change in the vehicle interior set temperature Tset.

[0216] As described above, the heat pump system 1 according to the first embodiment includes the heat pump cycle 10, the heating unit 30 including the high-temperature side heat medium circuit 31, the low-temperature side heat medium circuit 40, and the energy manager 70. The heat pump system 1 is capable of performing a heating operation in which the heat of the low-temperature side heat medium is pumped up through the heat pump cycle 10 and used to heat the ventilation air in the heating unit 30.

[0217] According to the heat pump system 1, the speed control via the compressor 11 at step S9, the low-temperature side heat storage control at step S6, and the heat amount adjustment control at step S12 are executed to approach the high-temperature side heat transfer amount Qh determined as a target value with respect to heating the ventilation air.

[0218] Accordingly, since a heat absorption amount from the low-temperature side heat medium, a heat amount related to the low-temperature side heat medium, and a heat release amount can be adjusted in response to a change in the high-temperature side heat transfer amount Qh or the like, a required heating capacity of the ventilation air can be secured at the heating unit 30 as the high-temperature side heat transfer amount Qh. According to the heat pump system 1, a heat capacity of the low-temperature side heat medium in the low-temperature side heat medium circuit 40 can be effectively utilized, and thus, it is possible to appropriately cope with a fluctuation in a heating capacity required at the heating unit 30.

[0219] At step S5, when the low-temperature side heat medium temperature Twl is equal to or lower than the reference value KTwl, the low-temperature side heat storage control (step S6) is executed, and when the low-temperature side heat medium temperature Twl is higher than the reference value KTwl, the low-temperature side heat release control (step S7) is executed.

[0220] Therefore, waste heat of the heat generating device 46 and the like can be stored in the low-temperature-side heat medium until the low-temperature-side heat medium temperature Twl reaches the reference value KTwl determined as the upper limit of the low-temperature-side heat medium temperature Twl. Accordingly, the heat pump system 1 is capable of realizing a state in which the amount of heat that can be used in the low-temperature-side heat medium circuit 40 is stored, so that when the heating capacity required for the heating operation is changed, it is possible to quickly respond by utilizing heat from the low-temperature-side heat medium circuit 40.

[0221] When the high-temperature-side heat medium temperature Twh is equal to or lower than the high-temperature-side target heat medium temperature Twoh at step S8, the speed control of the compressor 11 at step S9 and the heat amount adjustment control at step S12 are executed. At step S9 and step S12, the speed of the compressor 11 and the heat amount at the heat generating device 46, and the like, are adjusted so that the high-temperature-side heat medium temperature Twh approaches the high-temperature-side target heat medium temperature Twoh, and as a result, the low-temperature-side heat medium temperature Twl is adjusted.

[0222] As a result, according to the heat pump system 1, even in the heating unit 30 having the high-temperature side heat medium circuit 31, the heat stored in the low-temperature side heat medium circuit 40 can be effectively used, and it is possible to quickly and flexibly deal with a change in heating capacity or the like.

[0223] In the heat pump system 1, the high-temperature side heat transfer amount Qh is determined based on an air conditioning load at the time of heating indicated by the target blowing temperature TaO or the like, and the low-temperature side target heat medium temperature Twol, which is the target value of the low-temperature side heat medium temperature Twl, is determined to approximate the high-temperature side heat transfer amount Qh.

[0224] Accordingly, according to the heat pump system 1, relationships between the target blowing temperature TaO, the high-temperature side heat transfer amount Qh, and the low-temperature side target heat medium temperature Twol can be found, and a heat amount of the low-temperature side heat medium circuit 40 can be appropriately adjusted according to a required heating capacity.

[0225] As in Fig. As shown in Figure 1, a low-temperature-side outside air heat exchanger 43 is arranged in the low-temperature-side heat medium circuit 40. At the low-temperature-side outside air heat exchanger 43, heat of the low-temperature-side heat medium can be released to the outside air OA.

[0226] Therefore, in the heat pump system 1, in the low-temperature side heat release control at step S7, the heat of the low-temperature side heat medium can be released to the outside air OA via the low-temperature side outside air heat exchanger 43. Accordingly, the heat pump system 1 is able to appropriately manage the heat amount of the low-temperature side heat medium circuit 40 during the heating operation.

[0227] When the upper speed limit value Ncul of the compressor 11 is set at step S3, reference is made to the control map shown in Fig. 6. In the control map, it is determined that the higher the traveling speed of the vehicle A, the larger the upper limit speed Ncul of the compressor 11.

[0228] Therefore, by intervening on noise and vibration generated with running of the vehicle A, it is possible to reduce an influence of the noise and vibration due to an increase in the rotational speed of the compressor 11 and improve comfort in the vehicle cabin.

[0229] At step S4, when the low-temperature side target heat medium temperature Twol is set, the low-temperature side heat medium temperature Twl is determined to be a target value by applying the relationships shown in Fig. 7 and Fig. 8, the high-temperature side heat transfer amount Qh and the upper speed limit value Ncul of the compressor 11 are used. That is, each upper speed limit value Ncul of the compressor 11 refers to the low-temperature side heat medium temperature Twl, which is a target value for achieving the high-temperature side heat transfer amount Qh.

[0230] Therefore, when the upper limit speed Ncul of the compressor 11 changes due to a change in a driving situation of the vehicle A or the like, the heat pump system 1 is able to quickly respond to the change in the heating capacity and smoothly implement the heating operation by using the heat from the low-temperature side heat medium circuit 40.

[0231] According to the heat pump system 1 in the first embodiment, when the heat amount is insufficient by the heat stored in the low-temperature side heat medium circuit 40 in a normal state, and the refrigerant discharge capacity of the compressor 11 is used at a maximum limit, the heat amount adjustment control is executed at step S12. In the heat amount adjustment control, since inefficient operation of the heat generating device 46 and the like is performed compared with a normal state, it is considered that there is room for improvement in energy efficiency related to the heating operation.

[0232] In this respect, as in Fig. 5, before the heat quantity adjustment control, the low-temperature side heat storage control is executed at step S6 and the speed control via the compressor 11 is executed at step S9, and control with high energy efficiency is prioritized. Therefore, according to the heat pump system 1, it is possible to implement energy-efficient control with respect to the heating operation by utilizing the heat of the low-temperature side heat medium circuit 40. (Second embodiment)

[0233] Next, a second embodiment which is different from the above-described embodiment will be described with respect to Fig. 11. In the second embodiment, a usage mode of a high-temperature-side heater 36 arranged in a high-temperature-side heat medium circuit 31 differs from that of the above-described embodiment. Other basic configurations and the like are similar to those of the above-described embodiment and will therefore not be described again.

[0234] In the first embodiment described above, during the heating operation, the heating operation is performed by pumping up the heat amount of the low-temperature side heat medium circuit 40 in the heat pump cycle 10 without using the high-temperature side heater 36. As the heat source in the low-temperature side heat medium circuit 40, heat generated by input and output of the battery, heat generated by operation of the heat generating device 46, and heat generated by the low-temperature side heater 45 are used.

[0235] In this regard, in the second embodiment, in addition to the heating heat source used in the first embodiment, a heating operation is performed using heat from the high-temperature side heater 36. Processing contents of the heat amount adjustment program concerning the heating operation in this case will be described with reference to Fig. 11 described.

[0236] As in Fig. As shown in FIG. 11, first, in step S21, a target blowing temperature TaO is set. The target blowing temperature TaO is calculated in a similar manner to step S1 in the first embodiment according to an air conditioning load in a heating operation. In step S22, a high-temperature-side target heat medium temperature Twoh is set. The high-temperature-side target heat medium temperature Twoh is calculated by a similar method to step S2.

[0237] When proceeding to step S23, an upper speed limit value Ncul of a compressor 11 is set. Similar to the first embodiment, the upper speed limit value Ncul of the compressor 11 is set with respect to a traveling speed of a vehicle A and the control map shown in Fig. 6 is shown.

[0238] At step S24, a low-temperature side target heat medium temperature Twol is set. When the low-temperature side target heat medium temperature Twol is set, a high-temperature side heat transfer amount Qh is first calculated as in the first embodiment.

[0239] The high-temperature-side heat transfer amount Qh according to the second embodiment is calculated by considering a maximum heating capacity of the high-temperature-side heater 36, using, for example, a current high-temperature-side heat medium temperature Twh, an intake air temperature with respect to a heater core 33, a vehicle interior setting temperature Tset, a blown air volume supplied into a vehicle cabin, and the target blown temperature TaO. In other words, the high-temperature-side heat transfer amount Qh according to the second embodiment is obtained by subtracting the maximum heating capacity of the high-temperature-side heater 36 from a value corresponding to the high-temperature-side heat transfer amount Qh in the first embodiment.

[0240] The low-temperature side target heat medium temperature Twol is determined by referring to the high-temperature side heat transfer amount Qh according to the second embodiment obtained in this way, the upper limit speed value Ncul of the compressor 11, and relationship diagrams shown in Fig. 7 and Fig. 8. Accordingly, the low-temperature-side target heat medium temperature Twol according to the second embodiment is a target value of a low-temperature-side heat medium temperature Twl for achieving the high-temperature-side heat transfer amount Qh in a state where the compressor 11 is operated at the upper limit speed Ncul and the high-temperature-side heater 36 exhibits the maximum heating capability.

[0241] At step S25, it is determined whether the low-temperature side heat medium temperature Twl is equal to or lower than a reference value KTwl. If the low-temperature side heat medium temperature Twl is equal to or lower than the reference value KTwl, low-temperature side heat storage control is executed at step S26. If the low-temperature side heat medium temperature Twl is higher than the reference value KTwl, low-temperature side heat release control is executed at step S27. Since processing contents of steps S25 to S27 are similar to those of steps S5 to S7 in the first embodiment, a description thereof will not be repeated.

[0242] Proceeding to step S28, it is determined whether the high-temperature-side heat medium temperature Twh is equal to or lower than the high-temperature-side target heat medium temperature Twoh. If the high-temperature-side heat medium temperature Twh is equal to or lower than the high-temperature-side target heat medium temperature Twoh, speed control over the compressor 11 is executed at step S29. If the high-temperature-side heat medium temperature Twh is higher than the high-temperature-side target heat medium temperature Twoh, high-temperature-side heat release control is executed at step S30. Since processing contents of steps S28 to S30 are similar to those of steps S8 to S10 in the first embodiment, a description thereof will not be repeated.

[0243] At step S31, in the speed control of the compressor 11, it is determined whether a speed Nc of the compressor 11 is the upper speed limit value Ncul set at step S3. That is, at step S31, the same determination as at step S11 in the first embodiment is performed.

[0244] In the second embodiment, when the rotational speed Nc of the compressor 11 is the upper limit speed value Ncul, the processing proceeds to step S32, and output control via the high-temperature-side heater 36 is executed. In the output control via the high-temperature-side heater 36, a heat generation amount of the high-temperature-side heater 36 is controlled so that the high-temperature-side heat medium temperature Twh approaches the target high-temperature-side heat medium temperature Twoh. On the other hand, when the rotational speed Nc of the compressor 11 is not the upper limit speed value Ncul, the processing returns to step S21.

[0245] At step S33, heat quantity adjustment control is executed in a low-temperature side heat medium circuit 40. Since the processing contents of the heat quantity adjustment control at step S33 are similar to those at step S12 in the first embodiment, a description thereof will not be repeated. When the heat quantity adjustment control ends at step S33, the process returns to step S21.

[0246] According to a heat pump system 1 in the second embodiment, during a heating operation using heat of the low-temperature side heat medium circuit 40, waste heat in the low-temperature side heat medium circuit 40 and a refrigerant discharge capacity of the compressor 11 are used in this order with priority as a heating heat source.

[0247] In a state where the waste heat in the low-temperature side heat medium circuit 40 is largely utilized and the rotational speed Nc of the compressor 11 reaches the upper speed limit Ncul, a high-temperature side heat medium is heated for the first time by the high-temperature side heater 36. When a heating capacity of ventilation air is insufficient upon heating by the high-temperature side heater 36, heat amount adjustment control is executed in the low-temperature side heat medium circuit 40.

[0248] According to the heat pump system 1 in the second embodiment, by performing heating by the high-temperature side heater 36 at step S32 in preference to the heat amount adjustment control at step S34, it is possible to reduce a heat release loss due to piping or the like, and it is possible to efficiently achieve a desired heating capacity.

[0249] As described above, according to the heat pump system 1 in the second embodiment, even when the high-temperature side heater 36 is used as the heating heat source, it is possible, similar to the above-described embodiment, to obtain an operation and effect obtained from a configuration and operation common to the above-described embodiment.

[0250] As in Fig. As shown in FIG. 11, the output control via the high-temperature-side heater 36 is executed with a lower priority than the high-temperature-side heat storage control and the rotational speed control via the compressor 11, and with a higher priority than the heat amount adjustment control via the low-temperature-side heat medium circuit 40. Therefore, the heat pump system 1 is capable of utilizing heat generated at the high-temperature-side heater 36 for the heating capacity while reducing an influence of heat release loss due to piping or the like, and is capable of improving energy efficiency of a heating operation by utilizing the heat of the low-temperature-side heat medium circuit 40. (Third embodiment)

[0251] Next, a third embodiment which is different from the above-described embodiment will be described with respect to Fig. 12 to 15. The third embodiment differs from the above-described embodiment in that temperature control is performed via a low-temperature side heat medium circuit 40 according to a driving condition of a vehicle A. Other basic configurations and the like are similar to those of the above-described embodiment and will therefore not be described again. Therefore, processing contents of a heat quantity adjustment program are substantially the same as those of the above-described embodiment.

[0252] Next, effects of the heat quantity adjustment program in a heat pump system 1 according to the third embodiment will be described with respect to Fig. 12 to 15 described. Fig. 12 is a comparative example for clarifying the effect of the heat amount adjustment program, and shows an operation of the heat pump system 1 when a low-temperature side target heat medium temperature Twol is changed in a warming operation according to a running state (running, stopping) of the vehicle A.

[0253] In the example shown in Fig. 12, a basic configuration of the heat pump system 1 is similar to that of the above-described embodiment, a control mode of each component device during the heating operation is different from that of the above-described embodiment, and the low-temperature side target heat medium temperature Twol is changed according to the running state of the vehicle A.

[0254] In the example shown in Fig. As shown in Figure 12, assume that vehicle A travels on a general road, passes through a highway, and then travels again on a general road. At this time, when vehicle A travels, a predetermined low-temperature side heat medium temperature Twl is set as the low-temperature side target heat medium temperature Twol. On the other hand, when vehicle A is stopped, a higher low-temperature side heat medium temperature TwIc is set than the low-temperature side target heat medium temperature Twol.

[0255] As described above, an upper limit speed value Ncul of a compressor 11 is determined according to a traveling speed of the vehicle A. Therefore, when the vehicle A is in the traveling state, Nce is set, which is the highest upper limit speed value Ncul, and when the vehicle A is in a stopped state, Ncd is set, which is the low upper limit speed value Ncul.

[0256] Therefore, in the example shown in Fig. As shown in Fig. 12, when the vehicle A is changed from the running state to the stopped state, the upper limit speed Ncul of the compressor 11 is switched to Ncd. At this time, the high-temperature side heat transfer amount Qh required in the warm-up operation with respect to the vehicle A is Qha, and in order to achieve the high-temperature side heat transfer amount Qha in a state where the upper limit speed Ncul of the compressor 11 is Ncd, the low-temperature side target heat medium temperature Twol must be equal to Twlc.

[0257] If a higher low-temperature side target heat medium temperature Twol is not achieved under a condition that the upper limit speed Ncul of the compressor 11 is lower than that in the running state, the high-temperature side heat transfer amount Qh corresponding to the target blowing temperature TaO cannot be achieved.

[0258] Even when the vehicle A is in the stopped state, the low-temperature side target heat medium temperature Twl gradually increases by recovering waste heat from the heat generating device 46 and the like. However, since the vehicle is in the stopped state, the temperature gradually approaches the low-temperature side target heat medium temperature Twl. That is, in the example shown in Fig. As shown in Fig. 12, a heating capacity decreases at a time when the vehicle A is changed from the running state to the stopped state, and a time lag is required until the heating capacity in the stopped state is restored to the heating capacity that has been reached. During this time lag, since the heating capacity in a vehicle cabin does not meet a passenger's requirement, it is assumed that comfort in the vehicle cabin is deteriorated.

[0259] Next, another comparative example is presented to clarify the effect of the heat quantity adjustment program on Fig. 13. The comparative example shown in Fig. 13 shows an operation of the heat pump system 1 in which control is executed based on a state of the vehicle A in a stopped state during a warming operation, and the low-temperature side target heat medium temperature Twol corresponding to the stopped state is used as a reference.

[0260] In the example shown in Fig. As shown in FIG. 13, the operation of each component device of the heat pump system 1 is controlled using the stopped state of the vehicle A as a reference. Therefore, the upper limit speed Ncul of the compressor 11 is determined to be Ncd based on the stopped state, and the low-temperature side target heat medium temperature Twol is determined to be Twlc, which is determined assuming the stopped state. The high-temperature side heat transfer amount Qh is also determined based on a state where the vehicle A is stopped.

[0261] In this case, as in Fig. 13, regardless of whether the vehicle A is running on a general road or the vehicle A is running on an expressway, the heating operation is carried out assuming that the vehicle A is stopped by using the heat of the low-temperature side heat medium circuit 40.

[0262] When vehicle A travels on a general road or a highway, waste heat is generated by a battery or the heat generating device 46. However, when control is executed based on the stopped state, there is a possibility that heating is performed by a low-temperature side heater 45 to reach the low-temperature side target heat medium temperature Twol. That is, as shown in Fig. 13, when the control is executed based on the stopped state, there is a possibility that the low-temperature side heater 45 having a low priority is used, and it is assumed that energy efficiency with respect to the heating operation is reduced.

[0263] Next, effects of the heat quantity adjustment program in the heat pump system 1 according to the third embodiment will be described with respect to Fig. 14. In the third embodiment, in the same way as in the above-described embodiments, the target blowing temperature TaO is set, a high-temperature side target heat medium temperature Twoh is determined, the upper limit speed Ncul of the compressor 11 is determined, and the low-temperature side target heat medium temperature Twol is determined.

[0264] In the third embodiment, the target blowing temperature TaO, the high-temperature side target heat medium temperature Twoh, the upper limit speed Ncul of the compressor 11, and the low-temperature side target heat medium temperature Twol are determined not only with respect to a current state of the vehicle A but also with respect to a future situation of the vehicle A.

[0265] Specifically, the future situation of vehicle A is estimated as a driving state of vehicle A after a predetermined time by using information (e.g., weather information or road traffic information) obtained from a cloud server 100 via the communication module 90 or navigation information via a navigation device 91. When an operation plan, such as a driving or pausing time or a travel path to a destination, is defined in the navigation device 91, the future situation of vehicle A can be specified with reference to information about the operation plan.

[0266] In the third embodiment, the upper limit speed value Ncul of the compressor 11 is substantially different between a traveling speed range when the vehicle A is traveling on an expressway and a traveling speed range when the vehicle A is traveling or stopping on a general road. Specifically, in a traveling speed range when the vehicle A is traveling on the expressway, Nce is set as the upper limit speed value Ncul of the compressor 11. In the traveling speed range when the vehicle A is traveling or stopping on the general road, Ncd is set as the upper limit speed value Ncul of the compressor 11.

[0267] First, in the heat pump system 1, when the vehicle is stopped for a predetermined time on a road on which the vehicle is traveling on a general road, an operation of each component device is controlled so that the low-temperature side heat medium temperature Twl approaches the low-temperature side target heat medium temperature Twol determined to achieve the high-temperature side heat transfer amount Qh.

[0268] At this time, the upper speed limit value Ncul of the compressor 11 is set to Ncd and does not change even when the vehicle is stopped. The high-temperature side heat transfer amount Qh does not change between a case where the vehicle is traveling on the general road and a case where the vehicle is in a stopped state, and indicates the high-temperature side heat transfer amount Qha. Therefore, in the third embodiment, the target low-temperature side heat medium temperature Twol does not change from Twlc when the vehicle is traveling on a general road and when the vehicle is stopped. Therefore, according to the heat pump system 1 in the third embodiment, a response of the low-temperature side heat medium temperature Twl is not delayed in the stopped state, and a desired heating capacity can be ensured.

[0269] In the example shown in Fig. As shown in Fig. 14, by referring to the road traffic information, the navigation information, and the like, it is possible to specify a time in the future when the vehicle A enters an expressway from a general road and a time when the vehicle A exits an expressway and travels on a general road. In a case of traveling on a general road, it is assumed that traveling and stopping occur irregularly depending on a traffic environment or a traffic signal. On the other hand, when the vehicle A travels on an expressway, it is assumed that traveling is to continue for a period in which a traveling speed of the vehicle A is high.Since a traveling speed range of the vehicle A, a frequency of traveling and stopping, and the like affect the upper limit speed Ncul of the compressor 11 and an amount of waste heat in the low-temperature side heat medium circuit 40, it is desirable to appropriately use different settings in view of energy efficiency of a heating operation.

[0270] In the heat pump system 1 according to the third embodiment, an operation of each component device is controlled according to a future change in a driving environment of the vehicle A. Specifically, first, a time point at which the vehicle A enters an expressway from a general road in the future is specified with reference to the road traffic information and the like. When traveling on an expressway, it is estimated that the vehicle will continue to travel at a high speed for a certain period of time, so the upper limit speed value Ncul of the compressor 11, the low-temperature side target heat medium temperature Twol, and the like are changed in advance to a mode corresponding to traveling on an expressway. A time for advance preparation before a change in the driving environment or the like is referred to as an advance preparation time tap.

[0271] In the example shown in Fig. As shown in Figure 14, in the pre-preparation time tap, the upper limit speed value Ncul of the compressor 11 is gradually increased from Ncd to Nce. At the same time, the low-temperature side target heat medium temperature Twol is lowered from Twlc, which corresponds to the general road, to Twla. Accordingly, at a time when the vehicle A enters the expressway, the upper limit speed value Ncul of the compressor 11 and the low-temperature side heat medium temperature Twl are suitable for expressway travel, so that the energy efficiency in terms of warming operation can be improved when the vehicle travels on an expressway.

[0272] Vehicle A will exit the expressway in the future and travel on a general road. Since a travel speed range when traveling on a general road is lower than a travel speed range when traveling on an expressway, it is expected that the amount of heat that can be used as the heating heat source in the low-temperature side heat medium circuit 40 will be reduced. When traveling on a general road, unlike traveling on an expressway, traveling and stopping occur irregularly, which is considered to greatly affect the heating capacity.

[0273] Therefore, when the vehicle departs from the expressway onto a general road, the upper speed limit value Ncul of the compressor 11, the low-temperature side target heat medium temperature Twol, and the like are preliminarily changed to a mode corresponding to general road driving. In this case, during the pre-preparation time tap, the upper speed limit value Ncul of the compressor 11 is gradually decreased from Nce to Ncd. At the same time, the low-temperature side target heat medium temperature Twol is increased from Twla, corresponding to the expressway, to Twlc.

[0274] Accordingly, at a time when the vehicle departs from the expressway onto a general road, the upper speed limit value Ncul of the compressor 11 or the low-temperature side heat medium temperature Twl suitable for general road driving is reached. Accordingly, the heat pump system 1 is capable of ensuring the required heating capacity while improving energy efficiency with respect to heating operation during general road driving accompanied by irregular driving and stopping.

[0275] A method of specifying the pre-preparation time tap in the third embodiment will be described with reference to Fig. 15. First, as an example of calculating the advance preparation time tap, a case where the vehicle A is traveling on a general road at a present time and enters an expressway in the future, and a case where the vehicle A is traveling on an expressway at a present time and exits to a general road in the future will be described.

[0276] As in Fig. 15, the pre-preparation time tap is calculated by dividing a temperature difference between the low-temperature side heat medium temperature Twl before the pre-preparation time tap and the low-temperature side heat medium temperature after the pre-preparation time tap by a temperature change rate ΔT.

[0277] Accordingly, when entering the expressway in the future, the pre-preparation time tap is calculated by subtracting the low-temperature side heat medium temperature Twlc after the pre-preparation time tap from the low-temperature side heat medium temperature Twla before the pre-preparation time tap, and dividing the value by the temperature change rate ΔT. On the other hand, when exiting to a general road in the future, the pre-preparation time tap is calculated by subtracting the low-temperature side heat medium temperature Twla after the pre-preparation time tap from the low-temperature side heat medium temperature Twlc before the pre-preparation time tap, and dividing the value by the temperature change rate ΔT.

[0278] The temperature change rate ΔT is a change rate per unit time of the low-temperature side heat medium temperature Twl in the pre-preparation time tap. The temperature change rate ΔT is calculated by subtracting a low-temperature side heat transfer amount QI and a pipeline heat release amount Qp from a low-temperature side heating heat generation amount Qlht and dividing the value by a low-temperature side cycle heat capacity Cwl.

[0279] The low-temperature side heating heat generation amount Qlht means a heat generation amount of the low-temperature side heater 45 when a temperature of a low-temperature side heat medium is adjusted. When the low-temperature side heat medium temperature Twl is increased, the low-temperature side heating heat generation amount Qlht is determined by a maximum heat generation capacity of the low-temperature side heater 45. On the other hand, when the low-temperature side heat medium temperature Twl is decreased, the low-temperature side heating heat generation amount Qlht indicates 0. The low-temperature side heat transfer amount QI is an amount of heat transferred from the low-temperature side heat medium to a low-pressure refrigerant through the chiller 16 during the heating operation.The pipeline heat release amount Qp is a heat release amount from the low-temperature side heat medium in the pipeline of the low-temperature side heat medium circuit 40.

[0280] Thus, according to the heat pump system 1 in the third embodiment, it is possible to specify a time at which the driving environment changes, such as a time when entering an expressway or exiting to a general road, by using information acquired by the communication module 90 or the like.

[0281] As in Fig. As shown in FIG. 15, by specifying the advance preparation time tap, the heat pump system 1 is able to pre-adjust a heat amount on one side of the low-temperature side heat medium circuit 40 so that sufficient heating capacity can be demonstrated at a time when the driving environment changes. Accordingly, according to the heat pump system 1 in the third embodiment, it is possible to flexibly and appropriately implement the heating operation corresponding to a change in the driving environment, and it is possible to maintain a high level of comfort in the vehicle cabin.

[0282] As described above, according to the heat pump system 1 in the third embodiment, even when the heat amount of the low-temperature side heat medium circuit 40 is adjusted in consideration of a future change in the driving environment, it is possible to achieve, in a similar manner, an operation and an effect achieved by a configuration and an operation common to the above-described embodiment.

[0283] According to the heat pump system 1 in the third embodiment, it is possible to estimate a future driving situation of the vehicle A by using information obtained through the communication module 90 or the like, and adjust the amount of heat stored in the low-temperature side heat medium circuit 40 according to a change in the driving situation. Accordingly, as shown in Fig. 14, the heat pump system 1 is capable of adjusting a heating capacity according to a change in a future driving situation, and is capable of maintaining comfort in the vehicle cabin while reducing an influence of a change in the driving situation.

[0284] When the low-temperature side target heat medium temperature Twol is changed based on a change in a future driving situation, the advance preparation time tap is determined by using the temperature change rate ΔT of the low-temperature side heat medium calculated by using the low-temperature side heating heat generation amount Qlht and the low-temperature side heat medium temperature Twl at a current time. Accordingly, the heat pump system 1 is capable of generating a state adapted to an appropriate low-temperature side heat medium temperature Twl at a time when a future driving situation changes, is capable of reducing a change in heating capacity due to the change in the driving situation, and is capable of maintaining comfort in the vehicle cabin. (Fourth embodiment)

[0285] Next, a fourth embodiment which is different from the above-described embodiment will be described with respect to Fig. 16 to 18. The fourth embodiment differs from the above-described embodiment in adjusting a heat amount to a low-temperature side heat medium temperature Twl when there is a possibility that heating of a vehicle cabin is required. Other basic configurations and the like are similar to those of the above-described embodiment and will therefore not be described again.

[0286] A heat pump system 1 according to the fourth embodiment is provided with a heating prediction function for predicting whether there is a possibility that a heating operation will be requested by a user. In the fourth embodiment, a prediction function setting program is executed for executing a setting related to enabling and disabling a prediction function.

[0287] First, processing contents of the prediction function setting program related to Fig. 16. The prediction function setting program is stored in a storage unit of the energy manager 70 and is read out and executed by a temperature adjustment control unit 71, which forms a processing unit.

[0288] As in Fig. 16, first, at step S41, it is determined whether a heating request is enabled. The heating request indicates that a heating operation is requested in the vehicle cabin. At step S41, it is determined whether the heating request is enabled based on whether the user performs a heating request operation using a user input unit 92.

[0289] If the heating request is on, the heating operation is executed, and therefore, at step S42, the heating prediction function is set to ON, and then the heating operation is started. After the heating operation is started, the process returns to step S41. On the other hand, if the heating request is not on, the process proceeds to step S43.

[0290] At step S43, it is determined whether an outside air temperature Tam is equal to or lower than a predicted determination value KTam. The outside air temperature Tam is a temperature of the outside air of the vehicle cabin in vehicle A and is specified using a detection value of an outside air temperature sensor in a control sensor group. The predicted determination value KTam is a parameter indicating a situation in which a warming operation is likely to be performed, and the outside air temperature is used and may be set to a value such as, for example, 0 degrees.

[0291] When the outside air temperature Tam is higher than the predicted determination value KTam, it is assumed that the outside air temperature Tam is high, and a probability that a heating operation is requested is low, so the heating prediction function is turned off at step S44. On the other hand, when the outside air temperature Tam is equal to or lower than the predicted determination value KTam, it is assumed that an environment is one in which the outside air temperature Tam is low and a need for a heating operation is high, so the heating prediction function is turned on at step S45. After the heating prediction function is set at step S44 and step S45, the process returns to step S41.

[0292] Next, effects of the heat quantity adjustment program in the heat pump system 1 according to the fourth embodiment will be described with respect to Fig. 17 and Fig. 18 described. Fig. 17 is a comparative example for clarifying an effect of the heat amount adjustment program and shows an operation of the heat pump system 1 when a heating operation is executed in a situation where the heating prediction function is turned on.

[0293] In the example shown in Fig. As shown in Figure 17, a basic configuration of the heat pump system 1 is similar to that of the above-described embodiment, and assume that the vehicle A is running and the heating operation is in an operation stop state. From the operation stop state of the heat pump system 1, a heating request is made via the user input unit 92 at a heating request effective time td, and the heating operation is started.

[0294] In this case, since the heat pump system 1 is in the operation stop state, a rotation speed Nc of the compressor 11 is 0, and a high-temperature side heat transfer amount Qh is also 0. Since the vehicle A is in a running state, the low-temperature side heat medium temperature Twl indicates a temperature corresponding to waste heat due to waste heat from a heat generating device 46 and a battery. At this time, since it is not necessary to use heat of the low-temperature side heat medium as a heating heat source or the like, the heat is released to outside air OA in a low-temperature side outside-air heat exchanger 43. Therefore, a low-temperature side heat release amount indicates a value corresponding to waste heat of the battery or the like.

[0295] In this situation, when the heating operation is started based on the heating request made at the heating request effective time td, the upper speed limit value Ncul of the compressor 11 becomes effective with the start of the heating operation. Accordingly, as shown by an alternating long and short dashed line in Fig. 17, the high-temperature side heat transfer amount Qh is set to a high-temperature side heat transfer amount Qha determined based on a target blowing temperature TaO.

[0296] A low-temperature side target heat medium temperature Twol is set to a low-temperature side heat medium temperature Twla corresponding to the high-temperature side heat transfer amount Qha. In this case, it is necessary to raise the low-temperature side heat medium temperature Twl to Twla, which is the low-temperature side target heat medium temperature Twol, and in order to effectively utilize waste heat of the battery or the like, an operation of a component device (for example, a shutter device 47) is controlled so that the low-temperature side heat release amount becomes 0.

[0297] Based on the heating request at the heating request action time td, a set value of the high-temperature side heat transfer amount Qh is changed to the high-temperature side heat transfer amount Qha. However, the low-temperature side heat medium temperature Twl gradually increases toward Twla, which is the low-temperature side set heat medium temperature Twl. Therefore, an actual measured value of the high-temperature side heat transfer amount Qh gradually increases toward the high-temperature side heat transfer amount Qha as the low-temperature side heat medium temperature Twl increases.

[0298] Thus, when the heating operation is started from the operation stop state, if an attempt is made to correspond to a change in the required high-temperature side heat transfer amount Qh by a change in a heat amount in the low-temperature side heat medium circuit 40 (that is, the low-temperature side heat medium temperature Twl), a response delay of the low-temperature side heat medium temperature Twl occurs. Therefore, it is assumed that a desired heating capacity cannot be achieved from the heating request acting time td until a request for the high-temperature side heat transfer amount Qh after the change is satisfied, and comfort in the vehicle cabin cannot be sufficiently improved.

[0299] Next, an operation of a heating operation when the heat amount adjustment program is applied to the heat pump system 1 according to the fourth embodiment will be described with reference to Fig. 18. In a case described in Fig. 18, first assume that a heating prediction function is enabled by the prediction function setting program described above. That is, a starting point in Fig. 18 corresponds to a warming prediction effect time tp.

[0300] Also in the fourth embodiment, when the low-temperature side heat medium temperature Twl is equal to or lower than a reference value KTwl, low-temperature side heat storage control is executed. Therefore, until the reference value KTwl is reached as an upper limit of the low-temperature side heat medium temperature Twl, waste heat from the heat generating device 46 and the battery is stored in the low-temperature side heat medium. That is, even before the heating request action time td, it is possible to create a state showing the low-temperature side heat medium temperature Twl equal to or higher than the low-temperature side heat medium temperature Twla corresponding to the high-temperature side heat transfer amount Qha.

[0301] When the heating operation is started based on the heating request action time td in this state, as shown in Fig. 18, by immediately increasing the rotational speed Nc of the compressor 11, it is possible to pump up heat of the low-temperature side heat medium, which is sufficiently secured, and to achieve the high-temperature side heat transfer amount Qha that has satisfied the heating requirement. That is, as shown in Fig. 17, it is possible to prevent a response delay for the high-temperature side heat transfer amount Qh with respect to a change in a set value of the high-temperature side heat transfer amount Qh, and it is possible to quickly respond to a heating request.

[0302] According to the heat pump system 1 in the fourth embodiment, by adjusting the heat of the low-temperature side heat medium in advance when the heating prediction function is turned on, even when a heating operation is started from an operation stop state, a heating capacity in response to a heating request can be quickly ensured.

[0303] As described above, according to the heat pump system 1 in the fourth embodiment, even when the heat amount of the low-temperature side heat medium circuit 40 is adjusted in preparation for a future heating operation, it is possible to achieve, in a similar manner, an operation and an effect achieved by a configuration and an operation common to the above-described embodiment.

[0304] According to the heat pump system 1 in the fourth embodiment, when it is determined based on the outside air temperature Tam or the like that there is a higher probability that the heating request is made, it is possible to store heat in the low-temperature side heat medium circuit 40 through the low-temperature side heat storage control from a time point before the heating request is made. When the heating request is made, the heat pump system 1 is able to pump up heat stored on one side of the low-temperature side heat medium circuit 40 through speed control via the compressor 11, quickly achieving a desired heating capacity, and improving heating performance.

[0305] The present disclosure is not limited to the above-described embodiment, and various modifications may be made as follows without departing from the gist of the present disclosure.

[0306] In the heat pump system 1 according to the above-described embodiment, the high-temperature side heat medium circuit 31, which includes the heat medium / refrigerant heat exchanger 12 and the heater core 33, is employed as the heating unit 30, but the invention is not limited to this aspect. As long as the heat pump cycle 10 is capable of pumping up heat on the low-temperature side heat medium circuit 40 to heat the ventilation air, various modes can be employed as the heating unit 30. For example, an indoor condenser may be employed instead of the heat medium / refrigerant heat exchanger 12. In this case, the indoor condenser is arranged inside the casing 61 in a manner similar to the heater core 33 in the above-described embodiment, and heats the ventilation air using heat from the high-pressure refrigerant.

[0307] A configuration of the low-temperature side heat medium circuit according to the present disclosure is not limited to the aspect described in the above-described embodiment. Various modes can be employed as long as the low-temperature side heat medium circuit includes at least one component device corresponding to the heat source and at least one component device corresponding to the heat quantity adjustment unit.

[0308] In the embodiment described above, the heat generating device 46, the battery heat exchange unit 42 including the battery, and the low-temperature side heater 45 are mounted as the heat source, but any of the heat generating device 46, the battery heat exchange unit 42, and the low-temperature side heater 45 may be used. The heat source can have any configuration as long as the heat source is capable of applying heat to the low-temperature side heat medium. Other components may be used instead of the heat generating device 46.

[0309] In the above-described embodiment, the low-temperature side pump 41, the outside air fan 43a, the low-temperature side flow rate adjustment valve 44, and the shutter device 47 are provided as the heat amount adjustment unit to adjust the heat release amount in the low-temperature side outside air heat exchanger 43, but the invention is not limited to this aspect. Other component devices can be used as long as the heat amount of the low-temperature side heat medium can be adjusted.

[0310] The arrangement of the component devices in the low-temperature side heat medium circuit is not limited to the above-described embodiment. A connection mode of the heat medium piping to the component devices in the low-temperature side heat medium circuit is not limited to the mode described in the above-described embodiment. For example, in the above-described embodiment, the low-temperature side flow rate adjusting valve 44 branches into a flow on one side of the low-temperature side outside air heat exchanger 43 and a flow bypassing the low-temperature side outside air heat exchanger 43, but a configuration in which the flows are connected without branching may be employed.

[0311] In the high-temperature side heat medium circuit 31 in the above-described embodiment, the high-temperature side heater 36 is arranged as a component device, but the invention is not limited to this aspect. For example, when executing the heat quantity adjustment program according to the first embodiment, it is possible to employ a mode in which the high-temperature side heater 36 is excluded from the component device of the high-temperature side heat medium circuit 31.

[0312] The arrangement of the component devices in the high-temperature side heat medium circuit is not limited to the above-described embodiment. A connection mode of the heat medium piping to the component devices in the high-temperature side heat medium circuit is not limited to the mode described in the above-described embodiment. For example, in the above-described embodiment, the high-temperature side flow rate adjustment valve 35 branches into a flow on one side of the heater core 33 and a flow on one side of the high-temperature side outside air heat exchanger 34, but a configuration in which the flows are connected without branching may be employed.

[0313] While the present disclosure has been described with reference to embodiments thereof, it should be understood that the disclosure is not limited to the embodiments and configurations. Rather, the present disclosure is intended to cover various modifications and equivalent arrangements. Moreover, while the various elements are shown in various combinations and configurations, which are exemplary, other combinations and configurations including more, fewer, or only a single element are also within the spirit and scope of the present disclosure. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] JP 2021-205661

[0001] WO 2013 / 013790

[0005]

Claims

[1] Heat pump system, with: a heat pump circuit (10) which a compressor (11) configured to compress and discharge a refrigerant, a condenser (12) configured to release heat of a high-pressure refrigerant compressed by the compressor and to condense the high-pressure refrigerant, a pressure reducing unit (14b) configured to reduce a pressure of the refrigerant flowed out of the condenser, and an evaporator (16) configured to cause the refrigerant, the pressure of which is reduced by the pressure reducing unit, to absorb heat and evaporate; a heating unit (30) configured to heat ventilation air to be blown into a space to be air-conditioned by using a heat source which is the heat released from the high-pressure refrigerant in the condenser; a low-temperature-side heat medium circuit (40) configured to circulate a low-temperature-side heat medium and to cause the refrigerant in the evaporator to absorb heat of the low-temperature-side heat medium, wherein the low-temperature-side heat medium circuit a heat source device (42, 45, 46) configured to heat the low-temperature side heat medium, and a heat quantity adjustment unit (41, 44, 47) configured to adjust a heat quantity carried by the low-temperature side heat medium; and a control unit (70) configured to control an operation of the heat quantity adjustment unit, wherein the control unit is configured to cause a heat transfer amount in the heating unit for heating the ventilation air to approach a predetermined target value via an adjustment at a temperature (Twl) of the low-temperature side heat medium by controlling a rotational speed (Nc) of the compressor and an operation of at least one of the heat source device and the heat amount adjustment unit. [2] The heat pump system according to claim 1, wherein the control unit is configured to maintain the amount of heat carried by the low-temperature side heat medium at least until the temperature of the low-temperature side heat medium reaches a predetermined reference value (KTwl) when the ventilation air is heated by the heating unit. [3] Heat pump system according to claim 1 or 2, wherein the heating unit (30) comprises a high-temperature-side heat medium circuit (31) configured to circulate a high-temperature-side heat medium and to cause the high-pressure refrigerant in the condenser to release heat to the high-temperature-side heat medium, wherein the high-temperature-side heat medium circuit comprises a heating heat exchanger (33) configured to heat the ventilation air via heat exchange with the high-temperature-side heat medium, and the control unit is configured to cause a temperature of the high-temperature-side heat medium to approach a target high-temperature-side heat medium temperature (Twoh) through the adjustment in the temperature (Twl) of the low-temperature-side heat medium by controlling the rotational speed (Nc) of the compressor and the operation of at least one of the heat source device and the heat amount adjusting unit, wherein the target high-temperature-side heat medium temperature is determined based on a target value (Qh) of the heat transfer amount in the heating unit. [4] Heat pump system according to claim 3, wherein the control unit is configured, to determine the target value (Qh) of the amount of heat transfer according to a target blowing temperature (TaO) of the ventilation air to be blown into a vehicle cabin, and to determine a low-temperature-side target heat medium temperature (Twol), which is a target value of the temperature of the low-temperature-side heat medium at which the heat transfer amount in the heating unit approaches the target value of the amount of heat transfer. [5] Heat pump system according to one of claims 1 to 4, wherein the low-temperature-side heat medium circuit comprises a low-temperature-side outside air heat exchanger (43) configured to perform heat exchange between the low-temperature-side heat medium and outside air, and the control unit is configured to control an operation of the heat amount adjusting unit to adjust a heat release amount from the low-temperature side heat medium to the outside air. [6] Heat pump system according to one of claims 1 to 5, wherein the control unit is configured, to determine at least two or more upper limits of the compressor speed, to determine a low-temperature side target heat medium temperature (Twol) for each of the two or more upper speed limits of the compressor, wherein the low-temperature side target heat medium temperature is a target value of the temperature of the low-temperature side heat medium required for the heat transfer amount in the heating unit to reach the target value of the amount of heat transfer, and to cause the temperature of the low-temperature side heat medium (Twl) to approach the low-temperature side target heat medium temperature by controlling the operation of the heat quantity adjustment unit. [7] Heat pump system according to one of claims 1 to 6, wherein the heat pump system is mounted in a vehicle (A) and the control unit is configured to determine an upper speed limit (Ncul) of the compressor according to a traveling speed of the vehicle. [8] Heat pump system according to one of claims 1 to 7, wherein the heat pump system is mounted in a vehicle (A) and the control unit has a driving situation estimation unit (71e) configured to estimate a future driving situation of the vehicle, and the control unit is configured to change a low-temperature side target heat medium temperature (Twol), which is a target value of the temperature of the low-temperature side heat medium, based on the future driving situation of the vehicle estimated by the driving situation estimation unit. [9] The heat pump system according to claim 8, wherein the control unit is configured to determine a lead preparation time (tap) based on a temperature change rate (ΔT) of the low-temperature side heat medium and the temperature of the low-temperature side heat medium (Twl) at a current time before the low-temperature side target heat medium temperature (Twol) is changed based on the future driving situation of the vehicle estimated by the driving situation estimation unit, wherein the lead preparation time is a time at which the heat source is operated before a time of changing at the low-temperature side target heat medium temperature, the temperature change rate (ΔT) of the low-temperature side heat medium being calculated based on a maximum heat generation capacity of the heat source device.

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