Heat Pump System

Abstract

This heat pump system includes a heat pump cycle (10), a heating unit (30), a low-temperature-side heat medium circuit (40), and a control unit (70). The heat pump cycle has a compressor (11), a condenser (12), a decompression unit (14b), and an evaporator (16). The heating unit heats blown air blown into a space to be air-conditioned, by using, as a heat source, heat of a high-pressure refrigerant dissipated at the condenser. The low-temperature-side heat medium circuit is configured to circulate a low-temperature-side heat medium, the heat of which is absorbed by a refrigerant at the evaporator, and has heat source devices (42, 45, 46), and heat amount adjustment units (41, 44, 47). The control unit adjust a temperature (Tw1) of the low-temperature-side heat medium by controlling the rotation speed (Nc) of the compressor, and the operation of at least one among the heat sources and the heat amount adjustment units such that a heat transfer amount for heating the blown air at the heating unit approaches a predetermined target value.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2021-205661 filed on December 20, 2021, the contents of which are 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 to a heat pump system that performs heating by utilizing heat contained in the low-temperature side heat medium. [Background technology]

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

[0004] The heat pump system in Patent Document 1 has an electric auxiliary heater and a battery in the low-temperature heat medium circuit, and the heat generated by the electric auxiliary heater etc. is pumped up in the heat pump cycle via the low-temperature heat medium and used to heat the vehicle cabin. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] International Publication No. 2013 / 013790 Summary of the Invention

[0006] In a heat pump system such as that described in Patent Document 1, when the heat of the low-temperature heat medium is used to heat the vehicle interior, it is expected that the heating performance will be affected if the circumstances surrounding the heating operation change. For example, when the capacity required for heating the vehicle interior is changed (such as a change in the set temperature), the timing at which the requested heating capacity is realized may be delayed from the requested time because the low-temperature heat medium is used. In addition, when the environment during heating operation (such as the vehicle's running speed) changes, it is expected that the response to the change in the environment may be lacking because the low-temperature heat medium is used.

[0007] In view of the above, the present disclosure relates to a heat pump system having a low-temperature side heat medium circuit including a heat source device, and aims to provide a heat pump system capable of efficient heating while suppressing fluctuations in heating capacity when performing heating using the heat of the low-temperature side heat medium.

[0008] A heat pump system according to an aspect of the present disclosure includes a heat pump cycle, a heating unit, a low-temperature 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 compresses and discharges a refrigerant. The condenser condenses the high-pressure refrigerant compressed by the compressor by dissipating heat. The pressure reduction unit reduces the pressure of the refrigerant flowing out from the condenser. The evaporator evaporates the refrigerant reduced in pressure by the pressure reduction unit by absorbing heat.

[0009] The heating unit heats the air to be blown into the space to be air-conditioned, using heat contained in the high-pressure refrigerant dissipated in the condenser as a heat source. The low-temperature side heat medium circuit is configured to circulate the low-temperature side heat medium whose heat is absorbed by the refrigerant in the evaporator, and has a heat source device and a heat quantity adjustment unit. The heat source device heats the low-temperature side heat medium. The heat quantity adjustment unit adjusts the amount of heat contained in the low-temperature side heat medium. The control unit controls the operation of the heat quantity adjustment unit.

[0010] The control unit then controls the compressor rotation speed and the operation of at least one of the heat source and the heat quantity adjustment unit to adjust the temperature of the low-temperature side heat medium so that the amount of heat transfer for heating the blown air in the heating unit approaches a predetermined target value.

[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 in a heat pump cycle and used to heat the air to be blown in the heating section. The heat pump system controls the rotation speed of the compressor and the operation of at least one of the heat source device and the heat amount adjustment section to adjust the temperature of the low-temperature side heat medium so that the amount of heat transfer for heating the air to be blown in the heating section approaches a predetermined target value. That is, the heat pump system can ensure the heating capacity of the air to be blown required in the heating section by adjusting the low-temperature side heat medium temperature using the amount of heat absorbed from the low-temperature side heat medium and the amount of heat acting on the low-temperature side heat medium. And, according to the heat pump system, the heat capacity of the low-temperature side heat medium in the low-temperature side heat medium circuit can be effectively utilized, so that it is possible to appropriately respond to fluctuations in the heating capacity required in the heating section. [Brief description of the drawings]

[0012] The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings. [Figure 1] 1 is an overall configuration diagram of a heat pump system according to a first embodiment. [Diagram 2] FIG. 1 is a schematic configuration diagram of an indoor air conditioning unit according to a first embodiment. [Diagram 3] FIG. 2 is a block diagram showing a control system of the heat pump system according to the first embodiment. [Figure 4] FIG. 2 is an explanatory diagram showing the functional configuration of a temperature adjustment control unit according to the first embodiment. [Diagram 5] 4 is a flowchart relating to a heat amount adjustment program during heating operation according to the first embodiment. [Figure 6] FIG. 4 is an explanatory diagram showing the relationship between the traveling speed of a vehicle and an upper limit value of the rotation speed of a compressor. [Figure 7] FIG. 4 is a characteristic diagram showing the relationship between the rotation speed of the compressor, the amount of heat transfer on the high-temperature side, and the temperature of the low-temperature side heat medium. [Figure 8]FIG. 4 is a characteristic diagram showing the relationship between the rotation speed of the compressor, the low-temperature side heat transfer amount, and the low-temperature side heat medium temperature. [Figure 9] FIG. 11 is an explanatory diagram showing an example of an operating state when a heating request changes. [Figure 10] FIG. 2 is an explanatory diagram showing an example of a heating operation by the heat pump system according to the first embodiment. [Figure 11] 10 is a flowchart relating to a heat amount adjustment program during heating operation according to a second embodiment. [Figure 12] 10 is an explanatory diagram showing an example of an operating state when a target value of a heating operation is changed in response to a change in a running state of a vehicle. FIG. [Figure 13] FIG. 11 is an explanatory diagram showing an example of an operating state when a target value of the heating operation is determined based on a vehicle stopped state. [Figure 14] FIG. 11 is an explanatory diagram showing an example of a heating operation by a heat pump system according to a third embodiment. [Figure 15] FIG. 13 is an explanatory diagram regarding calculation of an advance preparation period in the third embodiment. [Figure 16] 13 is a flowchart relating to a prediction function setting program in the fourth embodiment. [Figure 17] FIG. 11 is an explanatory diagram showing an example of an operating state when a heating operation is started from a heating stopped state. [Figure 18] FIG. 13 is an explanatory diagram showing an example of a heating operation by a heat pump system according to a fourth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0013] Hereinafter, a number of embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, the same reference numerals may be used to designate parts corresponding to matters described in the preceding embodiment, and duplicated descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other embodiments described previously may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically indicated as being possible in each embodiment, it is also possible to partially combine embodiments even if not indicated, as long as there is no particular problem with the combination.

[0014] (First embodiment) A first embodiment of the present disclosure will be described with reference to Fig. 1 to Fig. 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 BEV (Battery Electric Vehicle) equipped with a battery for driving and driven by the power of the battery.

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

[0016] The heat pump system 1 can switch between a cooling mode, a heating mode, and a dehumidifying and heating mode as air conditioning operation modes for air conditioning the vehicle cabin. The cooling mode is an operation mode in which the blown air to be blown into the vehicle cabin is cooled and blown into the vehicle cabin. The heating mode is an operation mode in which the blown air is heated and blown into the vehicle cabin. The dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blown air is reheated and blown into the vehicle cabin, thereby dehumidifying and heating the vehicle cabin.

[0017] The heat pump cycle 10 of the heat pump system 1 employs an HFO refrigerant (specifically, HFO1234yf) as the refrigerant, forming a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. Refrigerant oil is mixed into the refrigerant to lubricate the compressor 11. As the refrigerant oil, PAG oil (polyalkylene glycol oil) that is compatible with liquid phase refrigerant is employed. A portion of the refrigerant oil circulates through the cycle together with the refrigerant.

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

[0019] First, the components of 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 device. First, the compressor 11 draws in, compresses, and discharges a refrigerant in the heat pump cycle 10. The compressor 11 is disposed inside the vehicle hood.

[0020] The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-capacity compression mechanism with a fixed discharge capacity. The compressor 11 has its rotation speed (i.e., refrigerant discharge capacity) controlled by a control signal output from an energy manager 70, which will be described later. The compressor 11 has a rotation speed upper limit Ncul, which is determined so that the higher the traveling speed of the vehicle A, the higher the rotation speed upper limit Ncul. This will be described later.

[0021] The discharge port of the compressor 11 is connected to an inlet side of a refrigerant passage 12a in the heat medium refrigerant heat exchanger 12. The heat medium refrigerant heat exchanger 12 is a heat exchanger that dissipates heat contained in the 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 section 30, and heats the high-temperature side heat medium.

[0022] The heat medium refrigerant heat exchanger 12 has a refrigerant passage 12a through which the refrigerant of the heat pump cycle 10 flows, and a heat medium passage 12b through which the high-temperature side heat medium of the high-temperature side heat medium circuit 31 flows. The heat medium refrigerant heat exchanger 12 is formed of the same kind of metal (aluminum alloy in the first embodiment) having excellent thermal conductivity, and each component member is integrated by brazing.

[0023] As a result, the high-pressure refrigerant flowing through the refrigerant passage 12a and the high-temperature side heat medium flowing through the heat medium passage 12b can exchange heat with each other. The heat medium-refrigerant heat exchanger 12 is an example of a condenser that dissipates heat contained in the high-pressure refrigerant, and constitutes a part of the heating unit 30 described later.

[0024] A first connection part 13a having a three-way joint structure is connected to the outlet of the refrigerant passage 12a of the heat medium refrigerant heat exchanger 12. In the first connection part 13a, one of three inlet / outlets is a refrigerant inlet, and the remaining two are refrigerant outlets. In other words, the first connection part 13a is a branch part that branches the flow of the liquid-phase refrigerant flowing out from the heat medium refrigerant heat exchanger 12.

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

[0026] The first expansion valve 14a reduces the pressure of the refrigerant flowing out from one refrigerant outlet of the first connection part 13a at least during an operation mode in which the blown 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 is a so-called electric expansion valve.

[0027] The valve element of the first expansion valve 14a is configured to be able to change the passage opening (in other words, the throttle opening) of the refrigerant passage. The electric actuator has a stepping motor that changes the throttle opening of the valve element. The 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 is configured as a variable throttle mechanism having a full opening function that fully opens the refrigerant passage when the throttle opening is fully opened, and a full closing function that closes the refrigerant passage when the throttle opening is fully closed. In other words, the first expansion valve 14a can prevent the refrigerant from decompressing by fully opening the refrigerant passage.

[0029] The first expansion valve 14a can block the inflow of refrigerant to the air-conditioning evaporator 15 by closing the refrigerant passage. That is, the first expansion valve 14a has both a function as a decompression unit that decompresses the refrigerant and a function as a refrigerant circuit switching unit that switches the refrigerant circuit. The first expansion valve 14a can also adjust the flow rate of refrigerant flowing into the air-conditioning evaporator 15 by adjusting the throttle opening of the refrigerant passage.

[0030] The outlet of the first expansion valve 14a is connected to the refrigerant inlet side of the air conditioning evaporator 15. As shown in Fig. 2, the air conditioning evaporator 15 is disposed inside a casing 61 of an indoor air conditioning unit 60. At least during an operation mode in which the blown air is cooled, the air conditioning evaporator 15 exchanges heat between the low-pressure refrigerant decompressed by the first expansion valve 14a and the blown air to evaporate the low-pressure refrigerant and cool the blown air.

[0031] 1, the second expansion valve 14b is connected to the other refrigerant outlet of the first connection part 13a. The second expansion valve 14b reduces the pressure of the refrigerant flowing out from the other refrigerant outlet of the first connection part 13a at least in the heating mode.

[0032] The second expansion valve 14b is an electric variable throttle mechanism, similar to the first expansion valve 14a, 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-open function and a full-close function.

[0033] That is, the second expansion valve 14b can prevent the refrigerant from being depressurized by fully opening the refrigerant passage. Also, the second expansion valve 14b can block the inflow of refrigerant to the chiller 16 by closing the refrigerant passage. That is, the second expansion valve 14b has both a function as a depressurizing unit that depressurizes the refrigerant and a function as a refrigerant circuit switching unit that switches the refrigerant circuit. The second expansion valve 14b is an example of a depressurizing unit.

[0034] The 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 decompressed 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 decompressed by the second expansion valve 14b flows, 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. Therefore, the chiller 16 is an evaporator that evaporates the low-pressure refrigerant and absorbs heat from the low-temperature side heat medium by heat exchange between the low-pressure refrigerant flowing in the refrigerant passage 16a and the low-temperature side heat medium flowing in the heat medium passage 16b. In other words, the chiller 16 corresponds to an example of an evaporator.

[0036] 1, one refrigerant inlet side of the second connection part 13b is connected to the refrigerant outlet of the air conditioning evaporator 15. The other refrigerant inlet side of the second connection part 13b is connected to the refrigerant outlet side of the chiller 16. Here, the second connection part 13b has a three-way joint structure similar to the first connection part 13a, and two of the three inlet and outlets are refrigerant inlets and the remaining one is a refrigerant outlet.

[0037] Therefore, the second connection part 13b is a junction part where the flow of the refrigerant flowing out from the air conditioning evaporator 15 and the flow of the refrigerant flowing out from the chiller 16 are joined together. The suction port side of the compressor 11 is connected to the refrigerant outlet of the second connection part 13b.

[0038] Next, a description will be given of the heating unit 30 in the heat pump system 1. The heating unit 30 is configured to use the high-pressure refrigerant in the heat pump cycle 10 as a heat source to heat the blown air supplied to the space to be air-conditioned.

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

[0040] As shown in FIG. 1, the high-temperature side heat medium circuit 31 includes a 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 control valve 35, a high-temperature side heater 36, etc.

[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 by using the heat pumped by the heat pump cycle 10.

[0042] A discharge port of a high-temperature side pump 32 is connected to the 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 it in the high-temperature side heat medium circuit 31. The high-temperature side pump 32 is an electric pump whose rotation speed (i.e., pumping capacity) is controlled by a control voltage output from an energy manager 70.

[0043] A high-temperature side heater 36 is connected to the outlet side of the heat medium passage 12b of the heat medium refrigerant heat exchanger 12. The high-temperature side heater 36 generates heat when power is supplied, and heats the high-temperature side heat medium flowing through the heat medium passage of the high-temperature side heater 36. For example, a PTC heater having a PTC element (i.e., a positive temperature coefficient thermistor) can be used as the high-temperature side heater 36. The high-temperature side heater 36 can arbitrarily adjust the amount of heat for heating the high-temperature side heat medium by a control voltage output from the energy manager 70.

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

[0045] An inlet of the heater core 33 is connected to one outlet of the high-temperature side flow rate adjustment valve 35. The heater core 33 is a heat exchanger that exchanges heat between the high-temperature side heat medium heated in the heat medium refrigerant heat exchanger 12 or the like and the blown air that has passed through the air-conditioning evaporator 15, thereby heating the blown air. As shown in Fig. 2, the heater core 33 is disposed in a casing 61 of the indoor air-conditioning unit 60. Therefore, the heater core 33 corresponds to an example of a heating heat exchanger.

[0046] The other outlet of the high-temperature side flow rate adjustment valve 35 is connected to an inlet of a high-temperature side outside air heat exchanger 34. The high-temperature side outside air heat exchanger 34 exchanges heat between the high-temperature side heat medium heated in the heat medium-refrigerant heat exchanger 12 or the like and the outside air OA, and dissipates heat contained in the high-temperature side heat medium to the outside air OA.

[0047] The high-temperature side outside air heat exchanger 34 is disposed at the front side inside the vehicle bonnet. As the vehicle A travels, the outside air OA flows from the front side of the vehicle to the rear and passes through the heat exchange section of the high-temperature side outside air heat exchanger 34. Therefore, the high-temperature side outside air heat exchanger 34 can dissipate heat to the outside air OA by utilizing the traveling wind.

[0048] A high-temperature side junction of a three-way joint structure is connected to the outlet of the high-temperature side outdoor air heat exchanger 34 and the outlet of the heater core 33. The high-temperature side junction uses one of the three inlet / outlet ports of the three-way joint structure as an outlet and the remaining two as inlets. Therefore, the high-temperature side junction can merge the flow of the high-temperature side heat medium that has passed through the high-temperature side outdoor air heat exchanger 34 and the flow of the high-temperature side heat medium that has passed through the heater core 33. The suction port of the high-temperature side pump 32 is connected to the outlet of the high-temperature side junction.

[0049] As described above, in the high-temperature side heat medium circuit 31 of the first embodiment, the high-temperature side outside air heat exchanger 34 and the heater core 33 are connected in parallel with respect to the flow of the high-temperature side heat medium passing through the heat medium passage 12b of the heat medium refrigerant heat exchanger 12. The high-temperature side flow rate control valve 35 can continuously adjust the flow rate ratio between the flow rate of the high-temperature side heat medium flowing into the heater core 33 side and the flow rate of the high-temperature side heat medium flowing into the high-temperature side outside air heat exchanger 34 in the high-temperature side heat medium circuit 31.

[0050] In other words, by controlling the operation of the high-temperature side flow control valve 35, the amount of heat of the high-temperature side heat medium radiated to the outside air OA in the high-temperature side outdoor air heat exchanger 34 and the amount of heat of the high-temperature side heat medium radiated to the blown air in the heater core 33 can be adjusted.

[0051] Next, a description will be given of the low-temperature side heat medium circuit 40 in the heat pump system 1. The low-temperature side heat medium circuit 40 is a heat medium circuit that circulates a low-temperature side heat medium. As 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.

[0052] The low-temperature side heat medium circuit 40 includes a heat medium passage 16b of the chiller 16, a low-temperature side pump 41, a battery heat exchanger 42, a low-temperature side outside air heat exchanger 43, a low-temperature side flow rate control valve 44, a low-temperature side heater 45, a heat generating device 46, a shutter device 47, etc. The discharge port side of the low-temperature side pump 41 is connected to the inlet of the heat medium passage 16b in the chiller 16.

[0053] The low-temperature side pump 41 is a heat medium pump that pressure-feeds 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. The basic configuration of the low-temperature side pump 41 is similar to that of the high-temperature side pump 32. Since the 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 the heat medium passage of a heat generating device 46 is connected to an outlet of the heat medium passage 16b of the chiller 16. The heat generating device 46 is composed of devices that generate heat incidentally in association with operation for the purpose of traveling, etc., among the in-vehicle devices mounted on the vehicle A. The heat generating device 46 corresponds to an example of a heat source device.

[0055] The heat generating devices 46 include an inverter INV and a motor generator MG. The heat medium passages of the heat generating devices 46 are formed so that each of the components can be cooled by circulating a heat medium therethrough.

[0056] The inverter INV is a power conversion unit that converts DC current into AC current. The motor generator MG is supplied with power to output driving force for running, and also generates regenerative power during deceleration, etc.

[0057] It is also possible to adopt a transaxle device as the heat-generating device 46. The transaxle device is a device that integrates a transmission with a final gear and a differential gear (diff gear).

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

[0059] Here, the battery supplies power to various electrical devices of vehicle A, and may be, for example, a chargeable and dischargeable secondary battery (in this embodiment, a lithium ion battery). The battery generates heat when charging and discharging. The battery is a so-called assembled battery formed by stacking multiple battery cells and electrically connecting these battery cells in series or parallel. This type of battery is prone to a decrease in output at low temperatures and to degradation at high temperatures.

[0060] For this reason, the temperature of the battery needs to be maintained within an appropriate temperature range (for example, 10° C. or higher and 40° C. or lower) that allows the battery's charge / discharge capacity to be fully utilized. For this reason, in the heat pump system 1, the flow rate of the low-temperature side heat medium flowing through the battery heat exchanger 42 is controlled to appropriately adjust the battery temperature.

[0061] The outlet side of the heat medium passage 42a of the battery heat exchanger 42 is connected to a low-temperature side flow rate adjustment valve 44. The low-temperature side flow rate adjustment valve 44 is an electric three-way flow rate adjustment valve having three inlet and outlet ports. As shown in FIG. 1, the outlet side of the heat medium passage 42a of the battery heat exchanger 42 is connected to the inlet port of the low-temperature side flow rate adjustment valve 44.

[0062] One of the outlets of the low-temperature side flow rate adjustment valve 44 is connected to the inlet side of the low-temperature side outside air heat exchanger 43. The low-temperature side outside air heat exchanger 43 is a heat exchanger that exchanges heat between the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40 and the outside air OA blown by the outside air fan 43a. The low-temperature side outside air heat exchanger 43 is disposed on the front side of the drive unit compartment. Therefore, when the vehicle is traveling, the traveling wind can be applied to the low-temperature side outside air heat exchanger 43.

[0063] A low-temperature side heater 45 is connected to the outlet of the low-temperature side outdoor air heat exchanger 43. The low-temperature side heater 45 generates heat when power is supplied to it, 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 a 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 can arbitrarily adjust the amount of heat for heating the high-temperature side heat medium by a control voltage output from the energy manager 70. The suction port side of the low-temperature side pump 41 is connected to the outlet of the heat medium passage in the low-temperature side heater.

[0065] Here, one end of a bypass flow passage, which circulates the low-temperature side heat medium so as to bypass the low-temperature side outdoor air heat exchanger 43, is connected to the other outlet of the low-temperature side flow control valve 44. A junction part of a three-way joint structure is connected to the other end of the bypass flow passage. The junction part uses two of the three inlet / outlet ports of the three-way joint structure as inlet ports and the remaining one as an outlet port.

[0066] The junction is disposed in the heat medium flow path that connects the outlet of the low-temperature side outdoor air heat exchanger 43 and the inlet of the low-temperature side heater 45. Therefore, the junction merges the flow of the low-temperature side heat medium that has flowed through the low-temperature side outdoor air heat exchanger 43 with the flow of the low-temperature side heat medium that has flowed through the bypass flow path, and causes the merged flow to flow out to the inlet side of the low-temperature side pump 41.

[0067] For this reason, the low-temperature side flow rate adjustment valve 44 can continuously adjust the flow rate ratio between the flow rate of the low-temperature side heat medium passing through the low-temperature side outdoor air heat exchanger 43 and the flow rate of the low-temperature side heat medium bypassing the low-temperature side outdoor air heat exchanger 43, with regard to the flow of the low-temperature side heat medium that has passed through the heat medium passage 16b of the chiller 16. That is, the low-temperature side heat medium circuit 40 can switch the flow of the low-temperature side heat medium by controlling the 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 a heat quantity adjustment section.

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

[0069] A shutter device 47 is disposed on the vehicle front side of the low-temperature side outdoor air heat exchanger 43. The shutter device 47 is configured by rotatably disposing multiple blades at an opening of a frame. The multiple blades rotate in conjunction with each other by the operation of an electric actuator (not shown) to adjust the opening area of ​​the frame opening.

[0070] Thereby, the shutter device 47 can adjust the flow rate of the outside air OA passing through the low-temperature side outside air heat exchanger 43, and can adjust the heat exchange capacity in the low-temperature side outside air heat exchanger 43. Therefore, the shutter device 47 corresponds to an example of a heat quantity adjustment unit.

[0071] Next, the indoor air conditioning unit 60 constituting the heat pump system 1 will be described with reference to Fig. 2. The indoor air conditioning unit 60 is a unit for blowing out the blown air, the temperature of which has been adjusted by the heat pump cycle 10, to an appropriate location in the vehicle cabin in the heat pump system 1. The indoor air conditioning unit 60 is disposed inside the instrument panel (i.e., the instrument panel) at the frontmost part of the vehicle cabin.

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

[0073] 2, an inside / outside air switching device 63 is disposed on the most upstream side of the blown air flow of the casing 61. The inside / outside air switching device 63 switches between introducing inside air (air inside the vehicle cabin) and outside air (air outside the vehicle cabin) into the casing 61.

[0074] The inside / outside air switching device 63 continuously adjusts the opening area of ​​the inside air inlet for introducing inside air into the casing 61 and the outside air inlet for introducing outside air into the casing 61 using an inside / outside air switching door to change the ratio of the amount of inside air introduced to the amount of outside air introduced. The inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door. The operation of this electric actuator is controlled by a control signal output from the energy manager 70.

[0075] A blower 62 is disposed downstream of the inside / outside air switching device 63 in the flow of blown air. The blower 62 is configured by an electric blower that drives a centrifugal multi-blade fan by an electric motor. The blower 62 blows the air drawn in through the inside / outside air switching device 63 toward the vehicle interior. The rotation speed (i.e., blowing capacity) of the blower 62 is controlled by a control voltage output from the energy manager 70.

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

[0077] Further, a cold air bypass passage 65 is formed inside the casing 61. The cold air bypass passage 65 is an air passage that causes the blown air that has passed through the air-conditioning evaporator 15 to bypass the heater core 33 and flow downstream.

[0078] An air mix door 64 is disposed downstream of the airflow of the air conditioning evaporator 15 and upstream of the airflow of the heater core 33. The air mix door 64 adjusts the ratio of the amount of air passing through the heater core 33 and the amount of air passing through the cold air bypass passage 65, among the air passing through the air conditioning evaporator 15.

[0079] The air mix door 64 is driven by an electric actuator for driving the air mix door. The operation of this electric actuator is controlled by a control signal output from the energy manager 70.

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

[0081] Furthermore, openings for blowing out the blown air (conditioned air) mixed in the mixing space into the vehicle cabin are arranged at the most downstream portion of the blown air flow of the casing 61. As these openings, a face opening, a foot opening, and a defroster opening (none of which are shown) are provided.

[0082] The face opening is an opening for blowing conditioned air toward the upper body of the occupant in the vehicle cabin, the foot opening is an opening for blowing conditioned air toward the feet of the occupant, and the defroster opening is an opening for blowing conditioned air toward the inside surface of the window glass at the front of the vehicle.

[0083] These face opening holes, foot opening holes, and defroster opening holes are each connected to a face air outlet, a foot air outlet, and a defroster air outlet (none of which are shown) provided in the vehicle cabin via ducts that form air passages.

[0084] Therefore, the temperature of the conditioned air mixed in the mixing space is adjusted by the air mix door 64 adjusting the ratio of the air volume passing through the heater core 33 and the air volume passing through the cold air bypass passage 65. This also adjusts the temperature of the blown air (conditioned air) blown into the vehicle compartment from each air outlet.

[0085] A face door, a foot door, and a defroster door (none of which are shown) are disposed upstream of the face opening hole, the foot opening hole, and the defroster opening hole in the flow of blown air, respectively. The face door adjusts the opening area of ​​the face opening hole. The foot door adjusts the opening area of ​​the foot opening hole. The defroster door adjusts the opening area of ​​the defroster opening hole.

[0086] The face door, foot door, and defroster door constitute a blowing mode switching device that switches the blowing outlet from which the conditioned air is blown out. The face door, foot door, and defroster door are connected to an electric actuator for driving the blowing outlet mode door via a link mechanism or the like, and are rotated in conjunction with each other. The operation of this electric actuator is controlled by a control signal output from the energy manager 70.

[0087] Next, the 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 the operation of each device constituting the vehicle A including the heat pump system 1. As shown in Fig. 3, the energy manager 70 has a temperature adjustment control unit 71, a motion manager 80, an air conditioning manager 81, a high-temperature side manager 82, a cycle manager 83, a low-temperature side manager 84, and an information notification unit 85.

[0088] Here, the energy manager 70 is realized by an on-board computer including a processing unit, RAM, a storage unit, an input / output interface, and a bus connecting these. The processing unit is hardware for arithmetic processing coupled with the RAM. The processing unit accesses the RAM to execute various processes for implementing the functions of each functional unit described below. The storage unit includes a non-volatile storage medium. The storage unit stores various programs (such as a heat adjustment program) executed by the processing unit. The specific configuration of the energy manager 70 and each functional unit will be described in detail later.

[0089] Vehicle A is equipped with an energy manager 70, 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 data communication module mounted on the vehicle A. The communication module 90 transmits and receives radio waves to and from base stations around the vehicle A by wireless communication based on communication standards such as LTE (Long Term Evolution) and 5G. By mounting the communication module 90, the vehicle A becomes a connected car that can be connected to a network NW.

[0091] The communication module 90 can transmit and receive information to and from a cloud server 100 and the like via the network NW. The cloud server 100 is an information distribution server installed on a cloud, and distributes, for example, weather information, road traffic information, and the like.

[0092] The navigation device 91 is an in-vehicle device that provides guidance on a driving route to a destination set by a user. The navigation device 91 provides guidance, such as going straight, turning right or left, and changing lanes at intersections, branching points, and merging points, by displaying on a screen and playing audio, etc. The navigation device 91 can provide information, such as the distance to the destination, the vehicle speed in each driving section, and elevation difference, as navigation information, and information, such as environmental information, to the energy manager 70.

[0093] In addition, the driving route may include sections where the speed range differs depending on the driving section, such as general roads and expressways. Since the legal speed limit on expressways is higher than the legal speed limit on general roads, it is expected that the battery output required for driving on expressways will be higher than when driving on general roads.

[0094] A driving route may include a driving section made up of flat areas and a driving section made up of mountain areas. The driving section in the mountain area may be made up of a driving section that climbs a slope with a certain gradient or more, and it is expected that the battery output required when driving on this uphill section will be greater than when driving on flat areas.

[0095] The user input unit 92 is an operation device that accepts input operations by a user who is an occupant of the vehicle A. To the user input unit 92, for example, a user operation for operating the navigation device 91, a user operation for switching between enabled and disabled heating prediction, a user operation for changing various setting values ​​related to the vehicle A, etc. are input. The user input unit 92 can provide the energy manager 70 with input information based on the user operations.

[0096] For example, a steering switch provided on the spokes of the steering wheel, a switch and a dial installed on a center console or the like, a voice input device that detects the driver's speech, and the like are mounted on the vehicle A as the user input unit 92. Also, a touch panel or the like of the navigation device 91 may function as the user input unit 92. Furthermore, a user terminal such as a smartphone or a tablet terminal may function as the user input unit 92 by being connected to the energy manager 70 by wire or wirelessly.

[0097] A consumption domain is a group of in-vehicle devices that realize various vehicle functions by using power from a battery, etc. One consumption domain includes at least one domain manager and is composed of a group of in-vehicle devices whose power consumption is managed by the domain manager. The multiple consumption domains include a driving control domain and a temperature control domain.

[0098] The driving control domain is a consumption domain that controls the driving of the vehicle A. The driving control domain includes the motor generator MG, the inverter INV, the steering control system SCS, the brake control system BCS, and the motion manager 80.

[0099] The motor generator MG is a drive source that generates a drive force for running the vehicle A. The inverter INV controls the power generation and regeneration by the motor generator MG. The steering control system SCS controls the steering of the vehicle A. The brake control system BCS controls the braking force generated in the vehicle A.

[0100] During power running by the motor generator MG, the inverter INV converts DC power supplied from the battery into three-phase AC power and supplies it to the motor generator MG. The inverter INV can adjust the frequency, current, and voltage of the AC power 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 AC power into DC power and supplies it to the battery.

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

[0102] The motion manager 80 also has a power transmission control unit 80a. The power transmission control unit 80a comprehensively controls the inverter INV, the steering control system SCS, and the brake control system BCS, and performs control related to the running of the vehicle A.

[0103] The temperature adjustment control domain is a consumption domain that performs air conditioning of the passenger space of the 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 the components of the indoor air conditioning unit 60 and an air conditioning manager 81. The components 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 components of the indoor air conditioning unit 60, and comprehensively controls each component to realize the air conditioning environment desired by the user. The air conditioning control unit 81a adjusts the volume of the air conditioning air and the ratio of inside and outside air in the air conditioning air, and comprehensively manages the power consumption of each component in the indoor air conditioning unit 60.

[0105] The consumption domain for the high-temperature side heat medium circuit 31 includes the high-temperature side pump 32, the high-temperature side flow control 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 for the components of the high-temperature side heat medium circuit 31, and controls the 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, which controls the pumping capacity of the high-temperature side heat medium in the high-temperature side pump 32, the flow balance in the high-temperature side flow control valve 35, and the amount of heat of the high-temperature side heat medium in the high-temperature side heater 36.

[0107] Furthermore, a high-temperature side manager 82 receives a high-temperature side heat medium temperature Twh, which is the temperature of the high-temperature side heat medium circulating through the high-temperature side heat medium circuit 31, from a plurality of temperature sensors arranged in the high-temperature side heat medium circuit 31. Therefore, the high-temperature side manager 82 can control the amount of heat generated by the high-temperature side heater 36, etc., using the detected high-temperature side heat medium temperature Twh.

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

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

[0110] Furthermore, detection results relating to the refrigerant temperature and refrigerant pressure are input to the cycle manager 83 by a refrigerant temperature sensor and a refrigerant pressure sensor arranged in the heat pump cycle 10. Therefore, the cycle manager 83 can adjust the rotation speed of the compressor 11, the throttle opening of the first expansion valve 14a, etc., using the detected refrigerant temperature and refrigerant pressure values.

[0111] The consumption domain for the low-temperature side heat medium circuit 40 includes the low-temperature side pump 41, the low-temperature side flow control 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 for the components of the low-temperature side heat medium circuit 40, and controls the 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 has a circuit control unit 84a, which controls the pumping capacity of the low-temperature side heat medium in the low-temperature side pump 41 and the flow rate balance in the low-temperature side flow rate adjustment valve 44. Furthermore, the circuit control unit 84a controls the amount of heat applied to the low-temperature side heat medium in the low-temperature side heater 45 and the opening area of ​​the shutter device 47.

[0113] Furthermore, a low-temperature side manager 84 receives a low-temperature side heat medium temperature Twl, which is the temperature of the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40, from a plurality of temperature sensors arranged in the low-temperature side heat medium circuit 40. Therefore, the low-temperature side manager 84 can control the amount of heat generated by the low-temperature side heater 45, etc., using the detected low-temperature side heat medium temperature Twl.

[0114] At least one of the temperature sensors for detecting the low-temperature side heat medium temperature Twl is disposed on the 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] 3, the energy manager 70 according to the first embodiment has a temperature adjustment control unit 71, an motion manager 80, an air conditioning manager 81, a high temperature side manager 82, a cycle manager 83, a low temperature side manager 84, and an information notification unit 85. As described above, the battery manager, the motion manager 80, and the heat manager are in-vehicle computers that each handle control related to a specific function (for example, the vehicle's driving function or temperature adjustment function), and constitute part of the energy manager 70.

[0116] The temperature control unit 71 uses various information output from the battery manager, the motion manager 80, and the heat manager to comprehensively manage the power consumption by each consumption domain. The temperature control unit 71 is configured by an on-board computer and configures a part of the energy manager 70. The temperature control unit 71 plays a major role in the control processing in the energy manager 70.

[0117] The information notification unit 85 is an in-vehicle computer that functions as a domain manager for notifying various pieces of information acquired from the cloud server 100, etc., and constitutes a part of the energy manager 70. A consumption domain for notifying information to the user of the vehicle A is connected to the information notification unit 85. For example, a display and speaker of the navigation device 91, a display unit arranged on the instrument panel at the front end of the vehicle interior, etc. are connected to the information notification unit 85.

[0118] Therefore, the information notification unit 85 can display the information specified by the temperature adjustment control unit 71 on a display or the like of the navigation device 91. Furthermore, the information notification unit 85 can output the information specified by the temperature adjustment control unit 71 as audio from the speaker of the navigation device 91. The display, speaker, etc. of the navigation device 91 correspond to an example of an information transmission unit.

[0119] The power supply to the energy manager 70, which is an on-board computer, continues even when the vehicle A is not capable of running (for example, the ignition is off). Therefore, even during the unused period, the energy manager 70 can start up each functional unit and execute a predetermined process if control execution is required.

[0120] As described above, the heat pump system 1 is provided with a group of control sensors to appropriately perform air conditioning operations and equipment temperature adjustment operations by the heat pump system 1. The energy manager 70 is connected to the group of control sensors for controlling the controlled equipment in the heat pump system 1. The group of control sensors includes an inside air temperature sensor, an outside air temperature sensor, a solar radiation sensor, a high pressure sensor, an evaporator temperature sensor, and a junction pressure sensor.

[0121] The inside air temperature sensor is an inside air temperature detection unit that detects the temperature inside the vehicle cabin (inside air temperature) Tr. The outside air temperature sensor is an outside air temperature detection unit that detects the temperature outside the vehicle cabin (outside air temperature) Tam. The solar radiation sensor is an solar radiation amount detection unit that detects the amount of solar radiation As irradiated into the vehicle cabin. The high pressure sensor is a refrigerant pressure detection unit that detects the high-pressure refrigerant pressure Pd in ​​the refrigerant flow path from the discharge port side of the compressor 11 to the 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 the refrigerant evaporation temperature (evaporator temperature) Tefin in the air conditioning evaporator 15. The junction pressure sensor is a refrigerant pressure detection unit that detects the refrigerant pressure in the second connection part 13b of the heat pump cycle 10. The junction pressure indicates the refrigerant pressure on the low pressure side of the heat pump cycle 10.

[0123] Furthermore, the control sensor group includes a battery temperature sensor, a blowing air temperature sensor, and an intake air temperature sensor. The battery temperature sensor is a battery temperature detection unit that detects the battery temperature, which is the temperature of the battery. The battery temperature sensor has multiple temperature detection units and detects the temperatures of multiple points on the battery. Therefore, the energy manager 70 can also detect the temperature difference between each part of the battery. Furthermore, the average value of the detection values ​​of the multiple temperature detection units is used as the battery temperature TBA.

[0124] The blown air temperature sensor is a blown air temperature detection unit that detects the blown air temperature TAV blown into the vehicle cabin. The intake air temperature sensor is an intake air temperature detection unit that detects the intake air temperature, which is the temperature of the blown air flowing into the air conditioning evaporator 15. The intake air temperature sensor is disposed inside the casing 61 of the interior air conditioning unit 60, upstream of the blown air flow with respect to the air conditioning evaporator 15.

[0125] Furthermore, the control sensor group includes a plurality of heat medium temperature sensors for detecting the 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 include a first heat medium temperature sensor to a fifth heat medium temperature sensor. The first heat medium temperature sensor is disposed at the outlet portion of the heat medium passage of the high-temperature side heater 36, and detects the temperature of the high-temperature side heat medium flowing out from the high-temperature side heater 36.

[0126] The second heat medium temperature sensor is disposed at the outlet of the high-temperature side outdoor air heat exchanger 34, and detects the temperature of the high-temperature side heat medium that has passed through the high-temperature side outdoor air heat exchanger 34. The third heat medium temperature sensor is disposed at the inlet of the heater core 33, and detects the temperature of the high-temperature side heat medium that flows into the heater core 33.

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

[0128] Here, 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, the configuration (hardware and software) that controls the operation of each control target device configures a control unit that controls the operation of each control target device.

[0129] For example, among the temperature adjustment control unit 71, a configuration for setting a high-temperature side heat transfer amount Qh required as the amount of heat transfer from the refrigerant to the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12 using a target blowing temperature TaO, etc., when heating the vehicle cabin constitutes a high-temperature side heat transfer amount setting unit 71a.

[0130] Furthermore, in the temperature adjustment control unit 71, a configuration for setting a target high-temperature side heat medium temperature Twoh as a target value of the high-temperature side heat medium temperature Twh required to realize the required high-temperature side heat transfer amount Qh when heating the vehicle interior constitutes a target high-temperature side heat medium temperature setting unit 71b.

[0131] In the temperature adjustment control unit 71, a component that sets the upper limit value Ncul of the rotation speed of the compressor 11 in accordance with the traveling speed of the vehicle A constitutes an upper limit value setting unit 71c of the rotation speed. The higher the traveling speed of the vehicle A, the higher the upper limit value of the rotation speed of the compressor 11 is set by the upper limit value setting unit 71c.

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

[0133] Among the temperature adjustment control unit 71, a configuration for estimating the future driving conditions of the vehicle A equipped with the heat pump system 1 based on the environmental information constitutes a driving condition estimation unit 71e. The future driving conditions of the vehicle A indicate the future conditions of the vehicle A, such as whether the vehicle A will be stopped or running, and the driving speed range when the vehicle A is running.

[0134] The environmental information includes information provided from outside the vehicle A, such as center information distributed from the cloud server 100. The environmental information also includes meteorological information and road traffic information. The meteorological information includes information indicating the outside temperature, the amount of solar radiation, the amount of radiant heat from the road surface, and the presence or absence of rainfall or snowfall on the travel route set in the navigation device 91.

[0135] Furthermore, the environmental information includes information that affects the traveling of the vehicle A and is generated within the vehicle A. For example, information provided by the navigation device 91, the power supply domain, the power consumption domain, etc. corresponds to an example of the environmental information. The information provided by the navigation device 91 includes, in addition to the distance to the destination, the vehicle speed and the elevation difference in each section, information such as the number of traffic lights (number of stops), the legal speed limit, the slope of the road, etc.

[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 in the vehicle A, or information input to a user terminal functioning as the user input unit 92 by a user outside the vehicle A. Furthermore, the information may be information input in real time by the user in response to an inquiry from the system side, such as the energy manager 70, or information indicating setting values ​​recorded by the user's past operations. The input operations of the user input using the user input unit 92 include input operations of an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, etc.

[0137] The auto switch is operated to set or cancel automatic control of the air conditioning operation by the heat pump system 1. The air conditioner switch is operated to request cooling of the blown air by the air conditioning evaporator 15. The air conditioner switch is configured to switch between cooling and not cooling the blown air by inputting an input. The air volume setting switch is operated to manually set the air volume of the blower 62. And the temperature setting switch is operated to set the vehicle interior set temperature Tset, which is the target temperature inside the vehicle interior.

[0138] Among the environmental information, the information provided by the consumption domain can be status information indicating the state of each consumption domain. For example, the status information includes air conditioning information indicating the set temperature of the air conditioning in the living space (hereinafter, "air conditioning request information") and the current temperature, temperature information of the heat medium in the heat medium circuit, and information indicating the state (e.g., current temperature, etc.) of the motor generator MG and the inverter INV, etc.

[0139] The environmental information is not limited to information including current measured values, but may include information including future estimated values. Specifically, a future usage schedule can be set for vehicle A.

[0140] Furthermore, in the temperature adjustment control section 71, a configuration for predicting the possibility of heating the interior of the vehicle A while it is moving, using various information acquired as environmental information, constitutes a heating prediction section 71f.

[0141] Next, the 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 in the first embodiment, the operation mode can be appropriately switched from a plurality of operation modes. The switching of these operation modes is performed by executing a control program stored in advance in the energy manager 70.

[0142] More specifically, the control program calculates a target blowing temperature TaO of the air to be blown into the vehicle cabin based on detection signals detected by a group of sensors for air conditioning control and an operation signal output from a user input unit 92.

[0143] Specifically, the target blown air temperature TaO is calculated by the following formula F1. TaO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F1) In addition, Tset is the target temperature in the vehicle cabin set by the temperature setting switch (vehicle cabin set temperature), Tr is the inside air temperature detected by the inside air temperature sensor, Tam is the outside air temperature detected by the outside air temperature sensor, and As is the amount of solar radiation detected by the solar radiation sensor. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

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

[0145] In addition, the control program switches the air conditioning operation mode to the dehumidifying and heating mode when the air conditioner switch of the user input unit 92 is turned on and the target blowing temperature TaO is equal to or higher than the cooling reference temperature α. Furthermore, when the air conditioner switch is not turned on and the target blowing temperature TaO is equal to or higher than the cooling reference temperature α, the control program switches the air conditioning operation mode to the heating mode.

[0146] (a) Cooling mode The cooling mode is an operation mode in which the heat pump cycle 10 is used to cool the blown air by the air conditioning evaporator 15 and blow the air into the vehicle cabin. In the cooling mode, the cycle manager 83 of the energy manager 70 opens the first expansion valve 14a to a predetermined throttle opening and fully closes the second expansion valve 14b.

[0147] Therefore, in the heat pump cycle 10 in the cooling mode, a refrigerant circulation circuit is formed in which the refrigerant flows 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 cycle configuration, the energy manager 70 controls the operation of various controlled devices connected to the output side in a manner suitable for the cooling mode according to the detection results of the control sensors, etc. Specifically, the cycle manager 83 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening of the first expansion valve 14a, and the air conditioning manager 81 controls the blowing capacity of the blower 62, the opening of the air mix door 64, etc.

[0149] In the high-temperature side heat medium circuit 31 in the cooling mode, the high-temperature side manager 82 controls the high-temperature side pump 32 and the high-temperature side flow rate control valve 35 to be in a state suitable for the cooling mode. As a result, in the high-temperature side heat medium circuit 31, the high-temperature side heat medium flows and circulates in the following order: high-temperature side pump 32, heat medium-refrigerant heat exchanger 12, high-temperature side heater 36, high-temperature side flow rate control valve 35, high-temperature side outside air heat exchanger 34, and high-temperature side pump 32.

[0150] In addition, in the low-temperature side heat medium circuit 40 in the cooling mode, since no low-pressure refrigerant flows into the chiller 16, the low-temperature side manager 84 can also stop the circulation of the low-temperature side heat medium in the low-temperature side heat medium circuit 40.

[0151] Therefore, 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 compartment, thereby cooling the vehicle compartment.

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

[0153] In this cycle configuration, the energy manager 70 controls the operation of various controlled devices connected to the output side in a manner suitable for the heating mode according to the detection results of the control sensors, etc. Specifically, the cycle manager 83 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening of the second expansion valve 14b, and the air conditioning manager 81 controls the blowing capacity of the blower 62, the opening of the air mix door 64, etc.

[0154] For the high-temperature side heat medium circuit 31 in the heating mode, the high-temperature side manager 82 controls the high-temperature side pump 32, the high-temperature side flow rate control valve 35, and the high-temperature side heater 36 to be in a state suitable for the heating mode. As a result, in the high-temperature side heat medium circuit 31, the high-temperature side heat medium flows and circulates in the following order: high-temperature side pump 32, heat medium-refrigerant heat exchanger 12, high-temperature side flow rate control valve 35, high-temperature side heater 36, heater core 33, and high-temperature side pump 32.

[0155] At this time, the high-temperature side manager 82 may cause a portion 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 to the suction port side of the high-temperature side pump 32 via the high-temperature side outside-air heat exchanger 34. This causes a portion of the heat possessed by the high-temperature side heat medium to be dissipated to the outside air in the high-temperature side outside-air heat exchanger 34, making it possible to adjust the heating capacity of the heater core 33 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 control valve 44, the heat generating device 46, and the shutter device 47 so that the 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 blowing capacity of the outside air fan 43a, the flow rate balance in the low-temperature side flow rate control valve 44, the heat generation amount of the heat generating device 46, the opening degree of the shutter device 47, etc.

[0157] As a result, in the low-temperature side heat medium circuit 40, the low-temperature side heat medium circulates in the following order: low-temperature side pump 41, chiller 16, heat-generating device 46, battery heat exchange section 42, low-temperature side flow control valve 44, low-temperature side outdoor air heat exchanger 43, low-temperature side heater 45, and low-temperature side pump 41.

[0158] According to this embodiment, exhaust heat from the battery and heat generating device 46 can be stored in the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40, and can be used as a heat source for heating the vehicle interior. In addition, the low-temperature side manager 84 can adjust the amount of heat used to heat the low-temperature side heat medium by the low-temperature side heater 45, and can adjust the amount of heat exchanged between the low-temperature side heat medium and the outside air by the low-temperature side outside air heat exchanger 43 by the outside air fan 43a and the shutter device 47. This makes it possible to adjust the amount of heat possessed by the low-temperature side heat medium to a desired state, and ensure a heat source for heating.

[0159] In the heating mode, the heat pump system 1 can perform heating operation by pumping up the heat contained in the low-temperature side heat medium in the low-temperature side heat medium circuit 40 in the heat pump cycle 10 and using it to heat the blown air via the high-temperature side heat medium circuit 31.

[0160] (c) Dehumidification heating mode The dehumidifying and heating mode is an operation mode in which the blown air cooled by the air conditioning evaporator 15 is heated by the heater core 33 and blown into the vehicle cabin using the heat pump cycle 10. In the dehumidifying and heating mode, the cycle manager 83 opens the first expansion valve 14a and the second expansion valve 14b to predetermined throttle openings.

[0161] Therefore, in the heat pump cycle 10 in the dehumidifying and heating mode, the refrigerant circulates in the order of 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 the order of 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 dehumidifying and heating mode, a refrigerant circulation circuit is formed in which the air conditioning evaporator 15 and the chiller 16 are connected in parallel with respect to the flow of the refrigerant flowing out of the heat medium refrigerant heat exchanger 12.

[0162] In this cycle configuration, the energy manager 70 controls the operation of various controlled devices connected to the output side in a manner suitable for the dehumidifying and heating mode according to the detection results of the control sensors, etc. Specifically, the cycle manager 83 controls the refrigerant discharge capacity of the compressor 11 and the throttle openings of the first expansion valve 14a and the second expansion valve 14b, and the air conditioning manager 81 controls the blowing capacity of the blower 62, the opening of the air mix door 64, etc.

[0163] For the high-temperature side heat medium circuit 31 in the dehumidifying and heating mode, the high-temperature side manager 82 controls the high-temperature side pump 32, the high-temperature side flow rate control valve 35, and the high-temperature side heater 36 to be in a state suitable for the dehumidifying and heating mode. As a result, in the high-temperature side heat medium circuit 31, the high-temperature side heat medium flows and circulates in the following order: high-temperature side pump 32, heat medium-refrigerant heat exchanger 12, high-temperature side flow rate control valve 35, high-temperature side heater 36, heater core 33, and high-temperature side pump 32.

[0164] Furthermore, with regard to the low-temperature side heat medium circuit 40 in the dehumidifying 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 control valve 44, and the shutter device 47 to achieve a state suitable for the dehumidifying heating mode. Specifically, the low-temperature side manager 84 controls the pumping capacity of the low-temperature side pump 41, the blowing capacity of the outside air fan 43a, the flow rate balance in the low-temperature side flow rate control valve 44, the heat generation amount of the heat-generating device 46, the opening degree of the shutter device 47, etc.

[0165] As a result, in the low-temperature side heat medium circuit 40, the low-temperature side heat medium circulates in the following order: low-temperature side pump 41, chiller 16, heat generating device 46, battery heat exchanger 42, low-temperature side flow rate control valve 44, low-temperature side outside air heat exchanger 43, low-temperature side heater 45, and low-temperature side pump 41. According to this embodiment, exhaust heat from the battery and heat generating device 46 can be stored in the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40, and can be used as a heat source for heating the vehicle interior. In addition, the low-temperature side manager 84 can adjust the amount of heat used to heat the low-temperature side heat medium by the low-temperature side heater 45, and can adjust the amount of heat exchanged between the low-temperature side heat medium and the outside air by the low-temperature side outside air heat exchanger 43 by the outside air fan 43a and the shutter device 47. This makes it possible to adjust the amount of heat possessed by the low-temperature side heat medium to a desired state, and ensure a heat source for heating.

[0166] The heat pump system 1 in the dehumidifying heating mode can perform a dehumidifying heating operation in which the blown air dehumidified by the air conditioning evaporator 15 is heated by utilizing the heat of the low-temperature side heat medium in the low-temperature side heat medium circuit 40.

[0167] Next, the processing contents of the heat amount adjustment program according to the first embodiment will be described with reference to Fig. 5 to Fig. 8. The heat amount adjustment program according to the first embodiment is executed to appropriately adjust various heat amounts used as heat sources for heating the vehicle interior during heating operation in the heat pump system 1.

[0168] 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 and executed by the temperature adjustment control unit 71 that constitutes the processing unit.

[0169] As shown in Fig. 5, first, in step S1, a target blowing temperature TaO is set. The target blowing temperature TaO is a target value related to the temperature of the blown air supplied to the vehicle interior, which is the space to be air-conditioned, during heating. As described above, the target blowing temperature TaO is calculated according to the vehicle interior set temperature Tset, the interior air temperature Tr, the exterior air temperature Tam, the amount of solar radiation As, and the formula F1.

[0170] In step S2, a target high-temperature side heat medium temperature Twoh is set, which is the temperature of the high-temperature side heat medium required to achieve the target blown temperature TaO. The target high-temperature side heat medium temperature Twoh is calculated using the intake air temperature for the heater core 33, the amount of air supplied into the vehicle cabin, the target blown temperature TaO, etc. The intake air temperature for the heater core 33 is calculated using the inside / outside air ratio in the inside / outside air switching device 63, the inside air temperature Tr, the outside air temperature Tam, etc.

[0171] In step S3, a rotation speed upper limit value Ncul of the compressor 11 in the heat pump cycle 10 is determined according to the traveling speed of the vehicle A. The rotation speed upper limit value Ncul of the compressor 11 means an upper limit value of the refrigerant discharge capacity of the compressor 11, and the rotation speed Nc of the compressor 11 is controlled so as not to exceed the rotation speed upper limit value Ncul.

[0172] In the first embodiment, the upper limit value Ncul of the rotation speed of the compressor 11 is determined according to a control table stored in a storage unit of the energy manager 70. As shown in Fig. 6, in the control table, the travel speed of the vehicle A is correlated to the upper limit value Ncul of the rotation speed of the compressor 11 so as to be proportional to the travel speed of the vehicle A, and the upper limit value Ncul of the rotation speed of the compressor 11 is determined to be higher as the travel speed of the vehicle A is higher.

[0173] Therefore, in step S3, the upper limit value Ncul of the rotation speed of the compressor 11 in the heat pump cycle 10 is determined based on the information on the traveling speed of the vehicle A acquired from the motion manager 80 and the control table shown in FIG.

[0174] In the first embodiment, as shown in Fig. 6, the travel speed of the vehicle A and the upper limit value Ncul of the rotation speed of the compressor 11 are set to have a proportional relationship, but the present invention is not limited to this. Various aspects can be adopted as long as the relationship is such that the higher the travel speed of the vehicle A, the higher the upper limit value Ncul of the rotation speed of the compressor 11. For example, a configuration may be adopted in which two or more upper limit values ​​Ncul of the rotation speed are associated with each other depending on the travel speed range, such as an upper limit value Ncul of the rotation speed when the travel speed of the vehicle A is low and an upper limit value Ncul of the rotation speed when the travel speed of the vehicle A is high.

[0175] In step S4, a target low-temperature side heat medium temperature Twol required to realize the target blowing temperature TaO is set. As described above, in the heating operation of the heat pump system 1, the heat pump cycle 10 pumps the heat of the low-temperature side heat medium to the high-temperature side heat medium circuit 31 side and uses it to heat the blown air in the heater core 33. Therefore, a target low-temperature side heat medium temperature Twol corresponding to a target value of the amount of heat available as a heating heat source in the low-temperature side heat medium circuit 40 is set.

[0176] When setting the target low-temperature side heat medium temperature Twol, first, the high-temperature side heat transfer amount Qh is calculated. The high-temperature side heat transfer amount Qh is the amount of heat transferred from the high-pressure refrigerant to the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12, and means the amount of heat required to achieve the target blowing temperature TaO. The high-temperature side heat transfer amount Qh is calculated, for example, using the target blowing temperature TaO, the intake air temperature for the heater core 33, and the amount of air supplied to the vehicle cabin, and is calculated by multiplying the temperature difference between the target blowing temperature TaO and the intake air temperature by the amount of air supplied to the vehicle cabin.

[0177] Here, in the heat pump system 1, the relationships shown in Figures 7 and 8 are recognized among the high-temperature side heat transfer amount Qh, the upper limit value Ncul of the rotation speed of the compressor 11, the low-temperature side heat medium temperature Twl, and the low-temperature side heat transfer amount Ql. Note that in Figures 7 and 8, five values ​​are set as the upper limit value Ncul of the rotation speed of the compressor 11, and the values ​​shown in order from the smallest upper limit value Ncul of the rotation speed are Nca, Ncb, Ncc, Ncd, and Nce.

[0178] The high-temperature side heat transfer amount Qh corresponding to a predetermined target blowing temperature TaO is called the high-temperature side heat transfer amount Qha, and the high-temperature side heat transfer amount Qh corresponding to an even higher target blowing temperature TaO is called the high-temperature side heat transfer amount Qhb. Also, in Fig. 7 and Fig. 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 the 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 associated via the low-temperature side heat medium temperature Twla. Also, the low-temperature side heat transfer amount Qlc corresponds to the low-temperature side heat medium temperature Twlb. Therefore, the low-temperature side heat transfer amount Qlc and the high-temperature side heat transfer amount Qhb are associated via the low-temperature side heat medium temperature Twlb.

[0179] 7 and 8, in the heat pump system 1, the high-temperature side heat transfer amount Qh determined to realize the target blowing temperature TaO is associated with the low-temperature side heat medium temperature Twl for each upper limit value Ncul of the rotation speed of the compressor 11. The high-temperature side heat transfer amount Qh is associated with a higher low-temperature side heat medium temperature Twl.

[0180] In the heat pump system 1, the heat pumped from the low-temperature side heat medium in the chiller 16 is used to heat the high-temperature side heat medium in the heat medium-refrigerant heat exchanger 12. Therefore, the high-temperature side heat transfer amount Qh determined as above corresponds to the low-temperature side heat transfer amount Ql, which is the amount of heat transferred from the low-temperature side heat medium to the low-pressure refrigerant in the chiller 16.

[0181] That is, the low-temperature side heat transfer amount Ql determined to realize the target blow-out temperature TaO is also associated with the low-temperature side heat medium temperature Twl for each upper limit value Ncul of the rotation speed of the compressor 11. Specifically, the lower the upper limit value Nca, Ncb, Ncc, Ncd, and Nce of the rotation speed of the compressor 11, the lower the low-temperature side heat medium temperature Twl becomes.

[0182] Using the relationships shown in Figures 7 and 8, consider the case where the high-temperature side heat transfer amount Qh required during heating operation increases from Qha to Qhb. When the upper limit value Ncul of the rotation speed of the compressor 11 is Nce, it is clear that the required high-temperature side heat transfer amount Qhb cannot be realized unless the low-temperature side heat medium temperature Twl is increased from Twla to Twlb. Therefore, Twlb is set as the target low-temperature side heat medium temperature Twol in this case.

[0183] Next, consider the case where the rotation speed upper limit Ncul of the compressor 11 is limited from Nce to Ncd when the high-temperature side heat transfer amount Qh required during heating operation is Qha. In this case, it can be seen that when the rotation speed upper limit Ncul of the compressor 11 is Ncd and the low-temperature side heat medium temperature is Twla, a shortage occurs with respect to the required high-temperature side heat transfer amount Qha.

[0184] 7 and 8, it can be seen that in order to realize the required high-temperature side heat transfer amount Qha when the upper limit value Ncul of the rotation speed of the compressor 11 is limited to Ncd, the low-temperature side heat medium temperature Twl needs to be increased from Twla to Twlc. In other words, Twlc is determined as the target low-temperature side heat medium temperature Twol in this case.

[0185] Therefore, in step S4, under the condition that the refrigerant discharge capacity of the compressor 11 complies with the upper limit value Ncul of the rotation speed set in step S3, the low-temperature side heat transfer amount Ql and the target low-temperature side heat medium temperature Twol are determined to realize the set high-temperature side heat transfer amount Qh. As can be seen from the relationships shown in Figures 7 and 8, the target low-temperature side heat medium temperature Twol to achieve the high-temperature side heat transfer amount Qh is individually associated with each of two or more values ​​of the upper limit value Ncul of the rotation speed of the compressor 11.

[0186] When the process proceeds 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 means an upper limit value of the low-temperature side heat medium temperature Twl that is determined in relation to the components of the low-temperature side heat medium circuit 40. Therefore, in step S5, it is determined whether the low-temperature side heat medium has a surplus heat quantity in relation to the heating operation.

[0187] If the low-temperature side heat medium temperature Twl is equal to or lower than the reference value KTwl, the process proceeds to step S6, where low-temperature side heat storage control is executed. The low-temperature side heat storage control controls the operation of the components of the low-temperature side heat medium circuit 40 so as to store as much waste heat as possible from the heat generating devices 46 and the like in the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40. Specifically, the low-temperature side heat medium stores waste heat associated with the operation of the heat generating devices 46, heat generated associated with input and output of the battery via the battery heat exchanger 42, heat generated by the low-temperature side heater 45, etc. When the low-temperature side heat storage control is terminated, the process proceeds to step S8.

[0188] 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 low-temperature side heat dissipation control is executed. The low-temperature side heat dissipation control controls the operation of the components of the low-temperature side heat medium circuit 40 so that the excess heat of the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40 is dissipated to the outside air OA.

[0189] Specifically, the low-temperature side heat dissipation control is realized by controlling the heat exchange capacity between the low-temperature side heat medium and the outside air OA in the low-temperature side outside air heat exchanger 43. The heat exchange capacity between the low-temperature side heat medium and the outside air may be adjusted by, for example, adjusting the flow rate of the low-temperature side heat medium passing through the low-temperature side outside air heat exchanger 43 by the pumping amount of the low-temperature side heat medium by the low-temperature side pump 41. Also, the heat exchange capacity in the low-temperature side outside air heat exchanger 43 may be adjusted by adjusting the flow rate balance of the low-temperature side heat medium flowing into the low-temperature side outside air heat exchanger 43 by the low-temperature side flow rate adjustment valve 44. Furthermore, the heat exchange capacity may be adjusted by adjusting the opening area of ​​the shutter device 47 or the blowing amount of the outside air fan 43a to adjust the flow rate of the outside air OA passing through the low-temperature side outside air heat exchanger 43. When the low-temperature side heat dissipation control is ended, the process proceeds to step S8.

[0190] In addition, the low-temperature side heat accumulation control in step S6 can be said to be a control for suppressing the amount of heat released from the low-temperature side heat medium to the outside air OA. Therefore, in the low-temperature side heat accumulation control, the low-temperature side pump 41, the low-temperature side flow rate adjustment valve 44, the outside air fan 43a, and the shutter device 47 in the low-temperature side heat medium circuit 40 operate in the opposite manner to the low-temperature side heat release control.

[0191] In step S8, it is determined whether the high-temperature side heat medium temperature Twh is equal to or lower than the target high-temperature side heat medium temperature Twoh. That is, it is determined whether the heat of the high-temperature side heat medium is sufficient for the heating operation aimed at the target blowing temperature TaO.

[0192] When the high-temperature side heat medium temperature Twh is equal to or lower than the target high-temperature side heat medium temperature Twoh, the heat possessed by the high-temperature side heat medium is insufficient for heating operation aimed at the target blowing temperature TaO, and therefore the rotation speed of the compressor 11 is controlled. In this control of the rotation speed of the compressor 11, the rotation speed of the compressor 11 is controlled so that the high-temperature side heat medium temperature Twh of the high-temperature side heat medium circulating through the heat medium refrigerant heat exchanger 12 approaches the target high-temperature side heat medium temperature Twoh determined based on the target blowing temperature TaO.

[0193] As a result, the amount of heat absorbed from the low-temperature side heat medium to the refrigerant in the chiller 16 and the amount of heat released 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, the amount of heat absorbed from the low-temperature side heat medium in the chiller 16 is also adjusted, so it can be said that the low-temperature side heat medium temperature Twl is adjusted.

[0194] And, according to the heat pump system 1, since it operates on the premise of the processes of steps S5 to S7, it is possible to reduce the energy consumption related to the operation of the heat pump cycle 10. When the control of the rotation speed of the compressor 11 is ended, the process proceeds to step S11.

[0195] On the other hand, when the high-temperature side heat medium temperature Twh is higher than the target high-temperature side heat medium temperature Twoh, in step S10, high-temperature side heat dissipation control is performed to dissipate excess heat held by the high-temperature side heat medium during heating operation aimed at the target blowing temperature TaO. In the high-temperature side heat dissipation control, the operation of the components of the high-temperature side heat medium circuit 31 is controlled so that the high-temperature side heat medium temperature Twh approaches the target high-temperature side heat medium temperature Twoh.

[0196] Specifically, high-temperature side heat dissipation control is realized by controlling the heat exchange capacity between the high-temperature side heat medium and the outside air OA in the high-temperature side outside air heat exchanger 34. The heat exchange capacity between the high-temperature side heat medium and the outside air may be adjusted, for example, by adjusting the flow rate of the high-temperature side heat medium passing through the high-temperature side outside air heat exchanger 34 by the amount of high-temperature side heat medium pumped by the high-temperature side pump 32 to adjust the heat exchange capacity. Alternatively, the heat exchange capacity in the high-temperature side outside air heat exchanger 34 may be adjusted by adjusting the flow rate balance of the high-temperature side heat medium flowing into the high-temperature side outside air heat exchanger 34 using the high-temperature side flow rate adjustment valve 35. When the high-temperature side heat dissipation control is completed, the process returns to step S1.

[0197] In step S11, in the control of the rotation speed of the compressor 11, it is determined whether the rotation speed Nc of the compressor 11 is equal to the upper limit value Ncul of the rotation speed set in step S3. That is, in the control of the rotation speed of the compressor 11, it is determined whether the maximum refrigerant discharge capacity of the compressor 11 is being utilized. If the rotation speed Nc of the compressor 11 is not equal to the upper limit value Ncul of the rotation speed, it is determined that the performance of the compressor 11 has a margin in the refrigerant discharge capacity, and the process returns to step S1.

[0198] On the other hand, when the rotation speed Nc of the compressor 11 is equal to the rotation speed upper limit value Ncul, in step S12, heat quantity adjustment control is performed in the low-temperature side heat medium circuit 40. When proceeding to step S12, the low-temperature side heat medium temperature Twl is lower than the target low-temperature side heat medium temperature Twol in a state where the compressor 11 is operated up to the rotation speed upper limit value Ncul by utilizing the heat of the low-temperature side heat medium at the current time as a heat source.

[0199] Therefore, in order to secure the amount of heat required to realize the target blowing temperature TaO, heat amount adjustment control is executed for the components in the low-temperature side heat medium circuit 40, which intentionally operates the components to generate heat. Specifically, for example, the inverter INV, which is the heat generating device 46, is operated in an inefficient manner different from normal to increase the amount of heat generated. Also, for the battery, the input and output to and from the battery are inefficiently performed to increase the amount of heat generated in the battery, and the heat of the low-temperature side heat medium is increased via the battery heat exchanger 42. Then, the low-temperature side heat medium may be heated by the low-temperature side heater 45 to adjust the temperature to the target low-temperature side heat medium temperature Twol. When the heat amount adjustment control is finished, the process returns to step S1.

[0200] In this way, in step S12, by performing heat quantity adjustment control on the low-temperature side heat medium circuit 40, the low-temperature side heat medium temperature Twl can be adjusted to the target low-temperature side heat medium temperature Twol. Since the heat of the low-temperature side heat medium is pumped up by the heat pump cycle 10 and used to heat the high-temperature side heat medium, the heat quantity adjustment control in step S12 can be said to adjust the low-temperature side heat medium temperature Twl so as to approach the target high-temperature side heat medium temperature Twoh.

[0201] Furthermore, by executing the heat quantity adjustment program, the heat pump system 1 can ensure the amount of heat on the low-temperature side heat medium circuit 40 side required for heating operation aimed at the target blowing temperature TaO, and can utilize the heat on the low-temperature side heat medium circuit 40 side when performing heating operation.

[0202] Next, the effect of the heat quantity adjustment program according to the first embodiment will be described with reference to Fig. 9 and Fig. 10. Fig. 9 is a comparative example for clarifying the effect of the heat quantity adjustment program, and shows the operation of the heat pump system 1 in heating operation when no heat quantity adjustment is performed in the low-temperature side heat medium circuit 40, etc.

[0203] In the example shown in Fig. 9, the basic configuration of the heat pump system 1 is the same as that of the above-mentioned embodiment, but the control manner of each component device during heating operation differs from that of the first embodiment. As a precondition for the heat pump cycle 10 side during heating operation in Fig. 9, the high temperature side heat transfer amount Qh required to realize the target blowing temperature TaO is Qha, and the rotation speed of the compressor 11 is operated at the rotation speed upper limit value Ncul.

[0204] As a prerequisite for the low-temperature side heat medium circuit 40, it is assumed that there is sufficient waste heat from the heat-generating devices 46, etc., and that a portion of the heat contained in the low-temperature side heat medium is dissipated to the outside air via the low-temperature side outdoor 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 dissipating heat to the outdoor air OA.

[0205] Under these preconditions, the heat of the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 40 is sufficient to meet the required value for the high-temperature side heat transfer amount Qha, so that heating operation can be achieved at the target blowing temperature TaO at this time point.

[0206] Consider the case where the vehicle interior temperature setting Tset is set higher from the heating operation under these prerequisites. In Figures 9 and 10, the time when the vehicle interior temperature setting Tset is set higher is shown as the set temperature change time tc.

[0207] 9, when the vehicle interior set temperature Tset is set higher at the set temperature change time tc, the target outlet temperature TaO is changed higher, and the high-temperature side heat transfer amount Qh increases from Qha to Qhb. On the other hand, the actual high-temperature side heat transfer amount Qh remains at Qha because it is in accordance with the preconditions at the set temperature change time tc.

[0208] As the heat transfer rate on the low-temperature side heat medium circuit 40 side becomes insufficient due to the change from Qha to Qhb, the heat transfer rate to the outside air OA in the low-temperature side outside air heat exchanger 43 is reduced to raise the low-temperature side heat medium temperature Twl from Twla. At this time, the heat pump cycle 10 side operates the compressor 11 at the upper limit of the rotation speed Ncul, as in the case of the precondition. As shown in Fig. 9, the low-temperature side heat medium temperature Twl gradually rises from the point when the heat transfer rate 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 rate Qhb after the setting change.

[0209] In this way, if an attempt is made to respond to a change in the high-temperature side heat transfer amount Qh required due to a setting change by changing the heat amount in the low-temperature side heat medium circuit 40 (i.e., the low-temperature side heat medium temperature Twl), a response delay in the low-temperature side heat medium temperature Twl occurs. For this reason, it is possible that the desired heating capacity cannot be achieved from the time tc when the set temperature is changed until the requirement for the changed high-temperature side heat transfer amount Qh is met, and the comfort in the vehicle cabin cannot be sufficiently increased.

[0210] Next, the 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 the case shown in Fig. 10, before the set temperature change timing tc, the high temperature side heat transfer amount is Qha as in the case shown in Fig. 9, and by increasing the interior set temperature Tset at the set temperature change timing tc, the high temperature side heat transfer amount is changed to Qhb.

[0211] Here, as explained in steps S5 and S6 of the heat quantity 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, the waste heat of the heat generating device 46 and the battery is stored in the low-temperature side heat medium until the low-temperature side heat medium temperature Twl reaches the reference value KTwl as the upper limit value of the low-temperature side heat medium temperature Twl. In other words, even before the set temperature change timing tc, the low-temperature side heat medium temperature Twl is maintained at or higher than the low-temperature side heat medium temperature Twla corresponding to the high-temperature side heat transfer amount Qha.

[0212] Furthermore, by keeping the low-temperature-side heat medium temperature Twl high, the rotation speed Nc of the compressor 11 can be kept low, and can be kept in a state with some margin with respect to the rotation speed upper limit value Ncul.

[0213] According to the heat quantity adjustment program in the first embodiment, waste heat from the heat generating devices 46 and the like can be stored in the low-temperature side heat medium until the temperature falls below the reference value KTwl. This allows the heat pump system 1 to create a state in which the operating state of the compressor 11 has some margin with respect to the upper limit value Ncul of the rotation speed.

[0214] As a result, even if the high-temperature side heat transfer amount Qh rises from Qha to Qhb in accordance with a change in the vehicle interior set temperature Tset at the set temperature change timing tc, the high-temperature side heat transfer amount Qhb can be realized by increasing the rotation speed Nc of the compressor 11. As a result, the heat pump system 1 can quickly change the heating capacity in response to a change in the vehicle interior set temperature Tset, as shown in FIG.

[0215] As described above, the heat pump system 1 according to the first embodiment has the heat pump cycle 10, the heating section 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 can perform a heating operation in which heat contained in the low-temperature side heat medium is pumped up by the heat pump cycle 10 and used to heat the blown air in the heating section 30.

[0216] According to the heat pump system 1, the rotation speed control of the compressor 11 in step S9, the low-temperature side heat storage control in step S6, and the heat quantity adjustment control in step S12 are executed so as to approach the high-temperature side heat transfer amount Qh, which is set as a target value for heating the blown air.

[0217] This makes it possible to adjust the amount of heat absorbed from the low-temperature side heat medium, the amount of heat generated for the low-temperature side heat medium, and the amount of heat released in response to changes in the high-temperature side heat transfer amount Qh, thereby ensuring the heating capacity of the blown air required as the high-temperature side heat transfer amount Qh in the heating unit 30. Furthermore, according to the heat pump system 1, the heat capacity of the low-temperature side heat medium in the low-temperature side heat medium circuit 40 can be effectively utilized, making it possible to appropriately respond to fluctuations in the heating capacity required by the heating unit 30.

[0218] Also, in step S5, 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 (step S6) is executed, and if the low-temperature side heat medium temperature Twl is higher than the reference value KTwl, low-temperature side heat dissipation control (step S7) is executed.

[0219] Therefore, waste heat from the heat generating devices 46 and the like can be stored in the low-temperature side heat medium until the low-temperature side heat medium temperature Twl reaches a reference value KTwl defined as an upper limit value of the low-temperature side heat medium temperature Twl. As a result, the heat pump system 1 can store a usable amount of heat in the low-temperature side heat medium circuit 40, and therefore can quickly respond by using the heat in the low-temperature side heat medium circuit 40 when the heating capacity required for heating operation is changed.

[0220] Then, in step S8, if the high-temperature side heat medium temperature Twh is equal to or lower than the target high-temperature side heat medium temperature Twoh, the rotation speed of the compressor 11 is controlled in step S9, and the amount of heat is adjusted in step S12. In steps S9 and S12, the rotation speed of the compressor 11 and the amount of heat in the heat generating device 46 and the like are adjusted so that the high-temperature side heat medium temperature Twh approaches the target high-temperature side heat medium temperature Twoh, and as a result, the low-temperature side heat medium temperature Twl is adjusted.

[0221] As a result, according to the heat pump system 1, even if the heating section 30 is configured with the high-temperature side heat medium circuit 31, the heat stored in the low-temperature side heat medium circuit 40 can be effectively utilized, and the system can quickly and flexibly respond to changes in heating capacity, etc.

[0222] In the heat pump system 1, the high-temperature side heat transfer amount Qh is determined based on the air conditioning load during heating, which is indicated by the target blowing temperature TaO, etc., and the target low-temperature side heat medium temperature Twol, which is the target value of the low-temperature side heat medium temperature Twl, is determined so as to approach the high-temperature side heat transfer amount Qh.

[0223] As a result, according to the heat pump system 1, it is possible to find the relationship between the target blowing temperature TaO, the high-temperature side heat transfer amount Qh, and the target low-temperature side heat medium temperature Twol, and therefore it is possible to appropriately adjust the heat quantity of the low-temperature side heat medium circuit 40 according to the required heating capacity.

[0224] 1, a low-temperature side outside air heat exchanger 43 is disposed in the low-temperature side heat medium circuit 40. In the low-temperature side outside air heat exchanger 43, heat contained in the low-temperature side heat medium can be dissipated to the outside air OA.

[0225] Therefore, in the heat pump system 1, in the low-temperature side heat dissipation control in step S7, the heat of the low-temperature side heat medium can be dissipated to the outside air OA via the low-temperature side outside air heat exchanger 43. This allows the heat pump system 1 to appropriately manage the amount of heat in the low-temperature side heat medium circuit 40 during heating operation.

[0226] Then, in step S3, when setting the upper limit value Ncul of the rotation speed of the compressor 11, the control table shown in FIG. 6 is referenced. The control table stipulates that the higher the traveling speed of the vehicle A, the higher the upper limit value Ncul of the rotation speed of the compressor 11.

[0227] Therefore, by incorporating the noise and vibrations that occur as the vehicle A moves, the effects of the noise and vibrations that occur as the rotation speed of the compressor 11 increases can be suppressed, thereby improving comfort in the vehicle cabin.

[0228] Furthermore, in step S4, when setting the target low-temperature side heat medium temperature Twol, the target low-temperature side heat medium temperature Twl is determined using the relationships shown in Figures 7 and 8, the high-temperature side heat transfer amount Qh, and the upper limit value Ncul of the rotation speed of the compressor 11. That is, the low-temperature side heat medium temperature Twl, which is the target value for achieving the high-temperature side heat transfer amount Qh, is associated with each upper limit value Ncul of the rotation speed of the compressor 11.

[0229] Therefore, even if the upper limit value Ncul of the rotation speed of the compressor 11 changes due to a change in the driving conditions of the vehicle A, the heat pump system 1 can quickly respond to the change in the heating capacity and smoothly realize heating operation using the heat of the low-temperature side heat medium circuit 40.

[0230] Furthermore, according to the heat pump system 1 according to the first embodiment, when the amount of heat stored in the low-temperature side heat medium circuit 40 in a normal state is insufficient and the refrigerant discharge capacity of the compressor 11 is being utilized to the maximum, the heat amount adjustment control is executed in step S12. Since the heat amount adjustment control operates the heat generating equipment 46 etc. less efficiently than in the normal state, it is believed that there is room for improvement in the energy efficiency of the heating operation.

[0231] 5, the low-temperature side heat storage control in step S6 and the rotation speed control of the compressor 11 in step S9 are executed prior to the heat amount adjustment control, and energy-efficient control is prioritized. Therefore, according to the heat pump system 1, it is possible to realize control that takes energy efficiency into consideration for the heating operation that utilizes the heat of the low-temperature side heat medium circuit 40.

[0232] Second embodiment Next, a second embodiment different from the above-described embodiment will be described with reference to Fig. 11. In the second embodiment, the usage of the high-temperature side heater 36 arranged in the high-temperature side heat medium circuit 31 is different from that of the above-described embodiment. Other basic configurations are the same as those of the above-described embodiment, so repeated description will be omitted.

[0233] In the first embodiment described above, the heating operation is performed by pumping the heat in the low-temperature side heat medium circuit 40 by the heat pump cycle 10, without using the high-temperature side heater 36. As heat sources in the low-temperature side heat medium circuit 40, heat generated by input and output of the battery, heat associated with the operation of the heat generating device 46, and heat generated by the low-temperature side heater 45 are used.

[0234] 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. The processing contents of the heat amount adjustment program related to the heating operation in this case will be described with reference to FIG.

[0235] As shown in Fig. 11, first, in step S21, a target blowing temperature TaO is set. The target blowing temperature TaO is calculated in the same manner as in step S1 of the first embodiment according to the air conditioning load in the heating operation. In step S22, a target high-temperature side heat medium temperature Twoh is set. The target high-temperature side heat medium temperature Twoh is calculated in the same manner as in step S2.

[0236] Then, when the process proceeds to step S23, the upper limit value Ncul of the rotation speed of the compressor 11 is set. As in the first embodiment, the upper limit value Ncul of the rotation speed of the compressor 11 is set by referring to the traveling speed of the vehicle A and the control table shown in FIG.

[0237] In step S24, the target low-temperature side heat medium temperature Twol is set. When setting the target low-temperature side heat medium temperature Twol, first, the high-temperature side heat transfer amount Qh is calculated, as in the first embodiment.

[0238] Here, the high-temperature side heat transfer amount Qh according to the second embodiment is calculated using, for example, the current high-temperature side heat medium temperature Twh, the intake air temperature for the heater core 33, the vehicle interior temperature setting Tset, the amount of air supplied into the vehicle interior, the target outlet temperature TaO, etc., taking into consideration the maximum heating capacity of the high-temperature side heater 36. In other words, the high-temperature side heat transfer amount Qh according to the second embodiment is found by subtracting the maximum heating capacity of the high-temperature side heater 36 from a value equivalent to the high-temperature side heat transfer amount Qh in the first embodiment.

[0239] The target low-temperature side heat medium temperature Twol is determined by referring to the high-temperature side heat transfer amount Qh according to the second embodiment thus obtained, the upper limit value Ncul of the rotation speed of the compressor 11, and the relationship diagrams shown in Figures 7 and 8. Therefore, the target low-temperature side heat medium temperature Twol according to the second embodiment is a target value of the low-temperature side heat medium temperature Twl for achieving the high-temperature side heat transfer amount Qh when the compressor 11 operates in a state where the upper limit value Ncul of the rotation speed is reached and the high-temperature side heater 36 is exerting its maximum heating capacity.

[0240] In step S25, it is determined whether the low-temperature side heat medium temperature Twl is equal to or lower than the 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 in 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 in step S27. The process contents of steps S25 to S27 are the same as steps S5 to S7 in the first embodiment, so repeated explanation will be omitted.

[0241] When the process proceeds to step S28, it is determined whether the high-temperature side heat medium temperature Twh is equal to or lower than the target high-temperature side heat medium temperature Twoh. If the high-temperature side heat medium temperature Twh is equal to or lower than the target high-temperature side heat medium temperature Twoh, the rotation speed control of the compressor 11 is executed in step S29. If the high-temperature side heat medium temperature Twh is higher than the target high-temperature side heat medium temperature Twoh, the high-temperature side heat dissipation control is executed in step S30. The process contents of steps S28 to S30 are the same as steps S8 to S10 in the first embodiment, so a repeated description will be omitted.

[0242] In step S31, it is determined whether or not the rotation speed Nc of the compressor 11 is equal to the upper limit value Ncul of the rotation speed set in step S3 by controlling the rotation speed of the compressor 11. That is, in step S31, the same determination as in step S11 in the first embodiment is performed.

[0243] In the second embodiment, when the rotation speed Nc of the compressor 11 is equal to the rotation speed upper limit value Ncul, the process proceeds to step S32, and output control of the high-temperature side heater 36 is executed. In the output control of the high-temperature side heater 36, the 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 rotation speed Nc of the compressor 11 is not equal to the rotation speed upper limit value Ncul, the process returns to step S21.

[0244] In step S33, heat quantity adjustment control is executed in the low-temperature side heat medium circuit 40. The process content of the heat quantity adjustment control in step S33 is similar to that in step S12 in the first embodiment, and therefore will not be described again. When the heat quantity adjustment control in step S33 ends, the process returns to step S21.

[0245] According to the heat pump system 1 of the second embodiment, during heating operation using heat from the low-temperature side heat medium circuit 40, the heating heat source is preferentially used in the following order: waste heat in the low-temperature side heat medium circuit 40, and the refrigerant discharge capacity of the compressor 11.

[0246] Then, when the utilization of waste heat in the low-temperature side heat medium circuit 40 is at a maximum and the rotation speed Nc of the compressor 11 reaches the upper rotation speed limit value Ncul, the high-temperature side heat medium is heated by the high-temperature side heater 36 for the first time. When the heating capacity of the high-temperature side heater 36 is insufficient for the heating of the blown air, the heat quantity adjustment control in the low-temperature side heat medium circuit 40 is performed.

[0247] According to the heat pump system 1 of the second embodiment, by performing heating by the high-temperature side heater 36 in step S32 in preference to the heat quantity adjustment control in step S34, it is possible to suppress heat radiation loss due to piping, etc., and to efficiently achieve the desired heating capacity.

[0248] As described above, according to the heat pump system 1 of the second embodiment, even when the high-temperature side heater 36 is used as a heating heat source, the effects achieved from the configuration and operation common to the above-mentioned embodiments can be obtained in the same manner as in the above-mentioned embodiments.

[0249] 11, the output control of the high-temperature side heater 36 is executed with a lower priority than the low-temperature side heat storage control and the rotation speed control of the compressor 11, and with a higher priority than the heat quantity adjustment control of the low-temperature side heat medium circuit 40. Therefore, the heat pump system 1 can utilize the heat generated by the high-temperature side heater 36 for heating capacity while suppressing the influence of heat radiation loss due to piping, etc., and can improve the energy efficiency of the heating operation using the heat of the low-temperature side heat medium circuit 40.

[0250] Third embodiment Next, a third embodiment different from the above-described embodiment will be described with reference to Figs. 12 to 15. The third embodiment differs from the above-described embodiment in that the temperature of the low-temperature side heat medium circuit 40 is controlled in accordance with the running state of the vehicle A. Other basic configurations are the same as those of the above-described embodiment, and therefore will not be described again. Therefore, the processing contents of the heat quantity adjustment program are also basically the same as those of the above-described embodiment.

[0251] Next, the effect of the heat quantity adjustment program in the heat pump system 1 according to the third embodiment will be described with reference to Fig. 12 to Fig. 15. Fig. 12 is one of comparative examples for clarifying the effect of the heat quantity adjustment program, and shows the operation of the heat pump system 1 when the target low temperature side heat medium temperature Twol is changed in accordance with the running state (running, stopped) of the vehicle A during heating operation.

[0252] In the example shown in FIG. 12, the basic configuration of the heat pump system 1 is similar to that of the above-described embodiment, but the control manner of each component device during heating operation differs from that of the above-described embodiment, and the target low-temperature side heat medium temperature Twol is changed depending on the running state of vehicle A.

[0253] In the example shown in Fig. 12, vehicle A travels on a general road, then passes an expressway, and travels on the general road again. At this time, when vehicle A is traveling, a predetermined low-temperature side heat medium temperature Twl is set as the target low-temperature side heat medium temperature Twol. On the other hand, when vehicle A is stopped, a higher low-temperature side heat medium temperature Twlc is set as the target low-temperature side heat medium temperature Twol.

[0254] As described above, the upper limit value Ncul of the rotation speed of the compressor 11 is determined according to the traveling speed of the vehicle A. For this reason, when the vehicle A is traveling, the highest upper limit value Ncul, Nce, is set, and when the vehicle A is stopped, the lower upper limit value Ncul, Ncd, is set.

[0255] 12, when vehicle A changes from a traveling state to a stopped state, the upper limit Ncul of the rotation speed of the compressor 11 is switched to Ncd. At this time, the high-temperature side heat transfer amount Qh required for the heating operation of vehicle A is Qha, and in order to realize the high-temperature side heat transfer amount Qha when the upper limit Ncul of the rotation speed of the compressor 11 is Ncd, the target low-temperature side heat medium temperature Twol needs to be Twlc.

[0256] Unless a higher target low-temperature side heat medium temperature Twol is realized under conditions where the upper limit value Ncul of the rotation speed of the compressor 11 is lower than that in the running state, the high-temperature side heat transfer amount Qh corresponding to the target blown-out temperature TaO cannot be realized.

[0257] Even when vehicle A is stopped, the low-temperature side heat medium temperature Twl gradually rises by recovering waste heat from the heat generating device 46, etc., but since the vehicle is stopped, it slowly approaches the target low-temperature side heat medium temperature Twol. That is, in the example shown in Fig. 12, the heating capacity decreases when vehicle A changes from a traveling state to a stopped state, and a time lag is required for the heating capacity to be restored to the realized heating capacity in the stopped state. During this time lag, the heating capacity in the vehicle cabin does not satisfy the needs of the occupants, and it is expected that the comfort in the vehicle cabin will be impaired.

[0258] Next, another comparative example for clarifying the effect of the heat quantity adjustment program will be described with reference to Fig. 13. The comparative example shown in Fig. 13 shows the operation of the heat pump system 1 in which control is performed based on the state of vehicle A being stopped during heating operation and based on the target low-temperature side heat medium temperature Twol corresponding to the stopped state.

[0259] 13, the operation of each component of the heat pump system 1 is controlled so that the stopped state of the vehicle A is used as a reference. For this reason, the upper limit value Ncul of the rotation speed of the compressor 11 is set to Ncd based on the stopped state, and the target low-temperature side heat medium temperature Twol is set to Twlc that is set on the premise of the stopped state. In addition, the high-temperature side heat transfer amount Qh is also set on the basis of the state in which the vehicle A is stopped.

[0260] In this case, as shown in FIG. 13, regardless of whether vehicle A is traveling on a general road or on a highway, heating operation is performed using heat from the low-temperature side heat medium circuit 40, assuming that vehicle A is stopped.

[0261] When vehicle A is traveling on an ordinary road or an expressway, waste heat is generated by the battery and heat-generating equipment 46, but if control is performed based on the stopped state, heating may be performed by the low-temperature side heater 45 in order to achieve the target low-temperature side heat medium temperature Twol. In other words, as shown in Fig. 13, if control is performed based on the stopped state, the low-temperature side heater 45, which has a low priority, may be used, and it is expected that the energy efficiency of the heating operation will decrease.

[0262] Next, the effect of the heat quantity adjustment program in the heat pump system 1 according to the third embodiment will be described with reference to Fig. 14. In the third embodiment, similarly to the above-described embodiments, the target blowing temperature TaO is set, the target high-temperature side heat medium temperature Twoh is determined, the upper limit value Ncul of the rotation speed of the compressor 11 is determined, and the target low-temperature side heat medium temperature Twol is determined.

[0263] In the third embodiment, when determining the target blowing temperature TaO, the target high-temperature side heat medium temperature Twoh, the upper limit value Ncul of the rotation speed of the compressor 11, and the target low-temperature side heat medium temperature Twol, they are determined taking into consideration not only the current state of the vehicle A but also the future state of the vehicle A.

[0264] Specifically, the future status of vehicle A is estimated as the driving state of vehicle A after a predetermined time using information (e.g., weather information and road traffic information) acquired from the cloud server 100 via the communication module 90 and navigation information from the navigation device 91. If an operation plan including driving and rest periods and a driving route to a destination is determined in the navigation device 91, the future status of vehicle A may be identified by referring to the information in the operation plan.

[0265] Furthermore, in the third embodiment, the upper limit value Ncul of the rotation speed of the compressor 11 is basically different between a traveling speed range in which the vehicle A is traveling on an expressway and a traveling speed range in which the vehicle A is traveling on an ordinary road or is stopped. Specifically, in the traveling speed range in which the vehicle A is traveling on an expressway, Nce is set as the upper limit value Ncul of the rotation speed of the compressor 11. Furthermore, in the traveling speed range in which the vehicle A is traveling on an ordinary road or is stopped, Ncd is set as the upper limit value Ncul of the rotation speed of the compressor 11.

[0266] First, when the vehicle is stopped for a specified period of time while traveling on a public road, the operation of each component device in the heat pump system 1 is controlled so that the low-temperature side heat medium temperature Twl approaches the target low-temperature side heat medium temperature Twol, which is set to realize the high-temperature side heat transfer amount Qh.

[0267] At this time, the upper limit value Ncul of the rotation speed of the compressor 11 is set to Ncd and does not change even when the vehicle is stopped. In addition, the high-temperature side heat transfer amount Qh does not change whether the vehicle is traveling on a general road or is stopped, and indicates the high-temperature side heat transfer amount Qha. For this reason, in the third embodiment, the target low-temperature side heat medium temperature Twol does not change from Twlc whether the vehicle is traveling on a general road or is stopped. Therefore, according to the heat pump system 1 of the third embodiment, there is no delay in the response of the low-temperature side heat medium temperature Twl when the vehicle is stopped, and the desired heating capacity can be ensured.

[0268] In the example shown in FIG. 14, by referring to road traffic information, navigation information, and the like, it is possible to identify the timing when vehicle A will enter an expressway from a general road in the future, or the timing when vehicle A will exit the expressway and travel on a general road. When traveling on a general road, it is assumed that vehicle A will travel and stop irregularly depending on the traffic environment and traffic lights. On the other hand, when traveling on an expressway, it is assumed that vehicle A will continue to travel at a high speed for a certain period of time. The travel speed range of vehicle A and the frequency of travel and stops affect the upper limit value Ncul of the rotation speed of the compressor 11 and the amount of waste heat in the low-temperature side heat medium circuit 40, so it is desirable to use appropriate settings in consideration of the energy efficiency of the heating operation.

[0269] In the heat pump system 1 according to the third embodiment, the operation of each component device is controlled according to future changes in the driving environment of the vehicle A. To explain in detail, first, the timing when the vehicle A will enter the expressway from a general road in the future is identified by referring to road traffic information, etc. When driving on the expressway, it is estimated that high-speed driving will continue for a certain period of time, so the upper limit value Ncul of the rotation speed of the compressor 11 and the target low-temperature side heat medium temperature Twol, etc. are changed in advance to modes corresponding to driving on the expressway. The time for advance preparation in advance of changes in the driving environment, etc. is called advance preparation time tap.

[0270] In the example shown in Fig. 14, at the advance preparation time tap, the rotation speed upper limit value Ncul of the compressor 11 is gradually increased from Ncd to Nce. At the same time, the target low-temperature side heat medium temperature Twol is decreased from Twlc corresponding to a general road to Twla. As a result, when the vehicle A enters the expressway, the rotation speed upper limit value Ncul of the compressor 11 and the low-temperature side heat medium temperature Twl are suitable for driving on the expressway, so that it is possible to improve the energy efficiency of the heating operation when driving on the expressway.

[0271] In the future, the vehicle A will leave the expressway and travel on general roads. The speed range when traveling on general roads is lower than the speed range when traveling on expressways, so it is expected that the amount of heat available as a heating heat source in the low-temperature side heat medium circuit 40 will be reduced. In addition, when traveling on general roads, unlike when traveling on expressways, driving and stopping occur irregularly, which is thought to have a significant impact on the heating capacity.

[0272] For this reason, even when exiting an expressway onto a general road, the upper limit Ncul of the rotation speed of the compressor 11 and the target low-temperature side heat medium temperature Twol are changed in advance to modes corresponding to driving on general roads. In this case, at the advance preparation time tap, the upper limit Ncul of the rotation speed of the compressor 11 is gradually lowered from Nce to Ncd. At the same time, the target low-temperature side heat medium temperature Twol is raised from Twla corresponding to the expressway to Twlc.

[0273] As a result, when the vehicle A exits the expressway onto a general road, the upper limit value Ncul of the rotation speed of the compressor 11 and the low-temperature side heat medium temperature Twl are suitable for driving on general roads. As a result, the heat pump system 1 can improve the energy efficiency of the heating operation when driving on a general road with irregular driving and stopping, while at the same time ensuring the required heating capacity.

[0274] Here, a method for specifying the advance preparation time tap in the third embodiment will be described with reference to Fig. 15. First, as calculation examples of the advance preparation time tap, a case where vehicle A is currently traveling on an ordinary road and will enter an expressway in the future, and a case where vehicle A is currently traveling on an expressway and will exit onto an ordinary road in the future will be described.

[0275] As shown in FIG. 15, the advance preparation time tap is calculated by dividing the temperature difference between the low-temperature side heat medium temperature Twl before the advance preparation time tap and the low-temperature side heat medium temperature after the advance preparation time tap by the temperature change rate ΔT.

[0276] Therefore, when entering an expressway in the future, the temperature change rate is calculated by subtracting the low-temperature side heat medium temperature Twlc after the advance preparation time tap from the low-temperature side heat medium temperature Twla before the advance preparation time tap and dividing the result by the temperature change rate ΔT. On the other hand, when exiting onto an ordinary road in the future, the temperature change rate is calculated by subtracting the low-temperature side heat medium temperature Twla after the advance preparation time tap from the low-temperature side heat medium temperature Twlc before the advance preparation time tap and dividing the result by the temperature change rate ΔT.

[0277] Here, the temperature change rate ΔT is the rate of change per unit time of the low-temperature side heat medium temperature Twl at the advance preparation time tap. The temperature change rate ΔT is calculated by subtracting the low-temperature side heat transfer amount Ql and the piping heat dissipation amount Qp from the low-temperature side heater heat generation amount Qlht, and dividing the result by the low-temperature side circuit heat capacity Cwl.

[0278] The low-temperature side heater heat generation amount Qlht refers to the heat generation amount of the low-temperature side heater 45 when adjusting the temperature of the low-temperature side heat medium. When the low-temperature side heat medium temperature Twl is increased, the low-temperature side heater heat generation amount Qlht is set to the 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 heater heat generation amount Qlht indicates 0. The low-temperature side heat transfer amount Ql is the amount of heat transferred from the low-temperature side heat medium to the low-pressure refrigerant in the chiller 16 during heating operation. The piping heat dissipation amount Qp is the amount of heat dissipated from the low-temperature side heat medium in the piping of the low-temperature side heat medium circuit 40.

[0279] In this way, according to the heat pump system 1 of the third embodiment, it is possible to use information acquired by the communication module 90, etc., to identify times when the driving environment will change, such as when to enter a highway or when to exit onto a general road.

[0280] 15, by identifying the advance preparation time tap, the heat pump system 1 can adjust the amount of heat on the low-temperature side heat medium circuit 40 side so that sufficient heating capacity can be exerted when the driving environment changes. As a result, the heat pump system 1 according to the third embodiment can realize a heating operation that flexibly and appropriately responds to changes in the driving environment, and can maintain a high level of comfort in the vehicle cabin.

[0281] As described above, according to the heat pump system 1 of the third embodiment, even when the heat quantity of the low-temperature side heat medium circuit 40 is adjusted in consideration of future changes in the driving environment, it is possible to obtain the same advantageous effects achieved by the configuration and operation common to the above-mentioned embodiments.

[0282] According to the heat pump system 1 of the third embodiment, the future driving conditions of the vehicle A can be estimated using information acquired by the communication module 90, etc., and the amount of heat in the low-temperature side heat medium circuit 40 can be adjusted according to changes in the driving conditions. As a result, the heat pump system 1 can adjust the heating capacity according to future changes in the driving conditions as shown in Fig. 14, and can maintain comfort in the vehicle cabin by suppressing the effects of changes in the driving conditions.

[0283] Furthermore, when changing the target low-temperature side heat medium temperature Twol based on future changes in driving conditions, the advance preparation time tap is determined using the temperature change rate ΔT of the low-temperature side heat medium calculated using the low-temperature side heater heat generation amount Qlht and the current low-temperature side heat medium temperature Twl. This allows the heat pump system 1 to create a state in which the low-temperature side heat medium temperature Twl is adjusted appropriately at the timing when future driving conditions change, suppressing changes in heating capacity due to changes in driving conditions and maintaining comfort in the vehicle cabin.

[0284] (Fourth embodiment) Next, a fourth embodiment different from the above-mentioned embodiment will be described with reference to Fig. 16 to Fig. 18. The fourth embodiment differs from the above-mentioned embodiment in the heat amount adjustment on the low-temperature side heat medium temperature Twl side when there is a possibility that heating of the vehicle interior is required. Other basic configurations are the same as those of the above-mentioned embodiment, so repeated description will be omitted.

[0285] The heat pump system 1 according to the fourth embodiment is provided with a heating prediction function for predicting whether or not there is a possibility that a user will request a heating operation. In the fourth embodiment, a prediction function setting program is executed for setting whether this prediction function is enabled or disabled.

[0286] First, the process contents of the prediction function setting program will be described with reference to Fig. 16. The prediction function setting program is stored in the storage unit of the energy manager 70, and is read and executed by the temperature adjustment control unit 71 constituting the processing unit.

[0287] As shown in Fig. 16, first, in step S41, it is determined whether or not a heating request is ON. The heating request indicates a request for heating the vehicle interior. In step S41, it is determined whether or not the heating request is ON based on whether or not a heating request operation has been performed by the user using the user input unit 92.

[0288] If the heating request is ON, the heating operation is to be performed, so in step S42, the heating prediction function is set ON and 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.

[0289] In step S43, it is determined whether the outside air temperature Tam is equal to or lower than a predicted judgment value KTam. The outside air temperature Tam is the temperature of the air outside the passenger compartment of the vehicle A, and is determined using the detection value of an outside air temperature sensor included in the control sensor group. The predicted judgment value KTam uses the outside air temperature as a parameter indicating a situation in which the heating operation is likely to be performed, and can be set to a value such as 0 degrees.

[0290] If the outside air temperature Tam is higher than the prediction judgment value KTam, the outside air temperature Tam is high and it is considered that the possibility that heating operation will be required is low, so the heating prediction function is set to OFF in step S44. On the other hand, if the outside air temperature Tam is equal to or lower than the prediction judgment value KTam, it is considered that the outside air temperature Tam is low and the environment is highly necessary for heating operation, so the heating prediction function is set to ON in step S45. After the heating prediction function is set in steps S44 and S45, the process returns to step S41.

[0291] Next, the effect of the heat quantity adjustment program in the heat pump system 1 according to the fourth embodiment will be described with reference to Fig. 17 and Fig. 18. Fig. 17 is a comparative example for clarifying the effect of the heat quantity adjustment program, and shows the operation of the heat pump system 1 when a heating operation is performed with the heating prediction function turned on.

[0292] 17, the basic configuration of the heat pump system 1 is the same as that of the above-described embodiment, and it is assumed that the vehicle A is running and the heating operation is stopped. Then, when the heat pump system 1 is in the stopped state, a heating request is made via the user input unit 92 at the heating request effective time td, and the heating operation is started.

[0293] In this case, since the heat pump system 1 is not operating, the rotation speed Nc of the compressor 11 is 0, and the high-temperature side heat transfer amount Qh is also 0. Furthermore, since the vehicle A is traveling, the low-temperature side heat medium temperature Twl indicates a temperature corresponding to the waste heat due to the waste heat from the heat generating device 46 and the battery. At this time, since the heat contained in the low-temperature side heat medium does not need to be used as a heating heat source, etc., it is dissipated to the outside air OA in the low-temperature side outdoor air heat exchanger 43. Therefore, the low-temperature side heat dissipation amount indicates a value corresponding to the waste heat from the battery, etc.

[0294] In this situation, when the heating operation is started based on the heating request made at the heating request effective time td, the upper limit value Ncul of the rotation speed of the compressor 11 becomes effective with the start of the heating operation. As a result, as shown by the dashed line in Fig. 17, the high-temperature side heat transfer amount Qh is set to the high-temperature side heat transfer amount Qha determined based on the target blowing temperature TaO.

[0295] The target low-temperature side heat medium temperature Twol is set to the 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 target low-temperature side heat medium temperature Twol, and the operation of the components (e.g., shutter device 47) is controlled so that the low-temperature side heat dissipation amount becomes zero in order to effectively utilize the waste heat of the battery, etc.

[0296] Based on the heating request during the heating request effective period td, the target value of the high-temperature side heat transfer amount Qh is changed to the high-temperature side heat transfer amount Qha, but the low-temperature side heat medium temperature Twl gradually rises toward the target low-temperature side heat medium temperature Twol, Twla. Therefore, the actual value of the high-temperature side heat transfer amount Qh gradually rises toward the high-temperature side heat transfer amount Qha as the low-temperature side heat medium temperature Twl rises.

[0297] In this way, when the heating operation is started from the operation stop state, if an attempt is made to respond to a change in the required high-temperature side heat transfer amount Qh by changing the heat amount in the low-temperature side heat medium circuit 40 (i.e., the low-temperature side heat medium temperature Twl), a response delay in the low-temperature side heat medium temperature Twl occurs. For this reason, it is assumed that the desired heating capacity cannot be realized from the heating request effective time td until the request for the changed high-temperature side heat transfer amount Qh is satisfied, and the comfort in the vehicle cabin cannot be sufficiently increased.

[0298] Next, the operation of the heating operation in the heat pump system 1 according to the fourth embodiment when the heat quantity adjustment program is applied will be described with reference to Fig. 18. In the case shown in Fig. 18, it is assumed that the heating prediction function is set to ON by the prediction function setting program described above. That is, the initial stage in Fig. 18 corresponds to the heating prediction effective period tp.

[0299] In the fourth 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, waste heat from the heat generating device 46 and the battery is stored in the low-temperature side heat medium until the low-temperature side heat medium temperature Twl reaches the reference value KTwl as the upper limit of the low-temperature side heat medium temperature Twl. In other words, even before the heating request effective time td, it is possible to create a state in which the low-temperature side heat medium temperature Twl is equal to or higher than the low-temperature side heat medium temperature Twla corresponding to the high-temperature side heat transfer amount Qha.

[0300] In this state, when heating operation based on the heating request effective time td is started, the rotation speed Nc of the compressor 11 is instantly increased to pump up the heat of the low-temperature side heat medium, which is sufficiently secured, and the high-temperature side heat transfer amount Qha that meets the heating request can be realized, as shown in Fig. 18. In other words, as shown in Fig. 17, the response delay of the high-temperature side heat transfer amount Qh to a change in the target value of the high-temperature side heat transfer amount Qh can be suppressed, and the heating request can be quickly met.

[0301] According to the heat pump system 1 of the fourth embodiment, when the heating prediction function is on, the heat of the low-temperature side heat medium is adjusted in advance, so that heating capacity can be quickly secured even when heating operation is started from a stopped state in response to a heating request.

[0302] As described above, according to the heat pump system 1 of the fourth embodiment, even when the heat quantity of the low-temperature side heat medium circuit 40 is adjusted in preparation for future heating operation, it is possible to obtain the same advantageous effects achieved by the configuration and operation common to the above-mentioned embodiments.

[0303] According to the heat pump system 1 of the fourth embodiment, when it is determined that there is a high possibility that a heating request will be made based on the outside air temperature Tam or the like, it is possible to store heat in the low-temperature side heat medium circuit 40 from the point in time before the heating request is made by the low-temperature side heat storage control. Then, when a heating request is made, the heat pump system 1 pumps up the stored heat on the low-temperature side heat medium circuit 40 side by controlling the rotation speed of the compressor 11, thereby quickly achieving the desired heating capacity and improving the warm-up performance.

[0304] The present disclosure is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit and scope of the present disclosure.

[0305] In the heat pump system 1 according to the embodiment described above, the high-temperature side heat medium circuit 31 having the heat medium refrigerant heat exchanger 12 and the heater core 33 is used as the heating unit 30, but the present invention is not limited to this configuration. As long as the heat pump cycle 10 is capable of pumping up heat from the low-temperature side heat medium circuit 40 and heating the blown air, various configurations can be used as the heating unit 30. For example, an indoor condenser may be used as an alternative configuration to the heat medium refrigerant heat exchanger 12. In this case, the indoor condenser is disposed inside the casing 61, similar to the heater core 33 in the embodiment described above, and heats the blown air with the heat of the high-pressure refrigerant.

[0306] The configuration of the low-temperature side heat medium circuit according to the present disclosure is not limited to the aspects described in the above-mentioned embodiment, and various aspects can be adopted as long as the low-temperature side heat medium circuit has at least one component device corresponding to a heat source and at least one component device corresponding to a heat amount adjustment unit.

[0307] In the above-described embodiment, the heat source is provided with the heat generating device 46, the battery heat exchanger 42 including the battery, and the low-temperature side heater 45, but any one of these may be used. In addition, the heat source may be configured to add heat to the low-temperature side heat medium, and the heat generating device 46 and the like may be replaced by other components.

[0308] In the above embodiment, the heat quantity adjustment unit includes the low-temperature side pump 41, the outdoor air fan 43a, the low-temperature side flow rate adjustment valve 44, and the shutter device 47 as a configuration for adjusting the amount of heat released in the low-temperature side outdoor air heat exchanger 43, but is not limited to this. Other components can be used as long as they are capable of adjusting the amount of heat contained in the low-temperature side heat medium.

[0309] The arrangement of the components in the low-temperature side heat medium circuit is not limited to the above-described embodiment. Furthermore, the connection of the heat medium piping to the components in the low-temperature side heat medium circuit is not limited to the above-described embodiment. For example, in the above-described embodiment, the low-temperature side flow rate control valve 44 is configured to branch into a flow on the low-temperature side outdoor air heat exchanger 43 side and a flow that bypasses the low-temperature side outdoor air heat exchanger 43, but a configuration in which the flow is connected without branching can be adopted.

[0310] In the above-described embodiment, the high-temperature side heater 36 is disposed as a component of the high-temperature side heat medium circuit 31, but the present invention is not limited to this. For example, when executing the heat quantity adjustment program according to the first embodiment, it is possible to adopt an embodiment in which the high-temperature side heater 36 is excluded from the components of the high-temperature side heat medium circuit 31.

[0311] Furthermore, the arrangement of each component in the high-temperature side heat medium circuit is not limited to the embodiment described above. The manner in which the heat medium piping is connected to each component in the high-temperature side heat medium circuit is also not limited to the manner described in the embodiment described above. For example, in the embodiment described above, the high-temperature side flow rate control valve 35 is configured to branch into the flow on the heater core 33 side and the flow on the high-temperature side outside air heat exchanger 34 side. However, a configuration in which the flow is connected without branching may be used. It can be adopted.

[0312] Although the present disclosure has been described based on the embodiment, it is understood that the present disclosure is not limited to the embodiment or structure. The present disclosure also includes various modifications and modifications within the equivalent range. In addition, various combinations and forms, and other combinations and forms including only one element, more than one element, or less than one element, are also within the scope and concept of the present disclosure.

Claims

1. a heat pump cycle (10) including a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that condenses the high-pressure refrigerant compressed by the compressor by dissipating heat, a pressure reduction section (14b) that reduces the pressure of the refrigerant flowing out from the condenser, and an evaporator (16) that evaporates the refrigerant reduced in pressure by the pressure reduction section by absorbing heat; a heating unit (30) that heats the air to be blown into the space to be air-conditioned by using heat from the high-pressure refrigerant radiated in the condenser as a heat source; a low-temperature side heat medium circuit (40) configured to circulate a low-temperature side heat medium whose heat is absorbed by the refrigerant in the evaporator, the low-temperature side heat medium circuit having a heat source device (42, 45, 46) that heats the low-temperature side heat medium and a heat quantity adjustment unit (41, 44, 47) that adjusts the amount of heat possessed by the low-temperature side heat medium; A control unit (70) that controls the operation of the heat amount adjustment unit, The control unit controls the rotation speed (Nc) of the compressor and the operation of at least one of the heat source device and the heat quantity adjustment unit so that the amount of heat transfer for heating the blown air in the heating unit approaches a predetermined target value, thereby adjusting the temperature (Twl) of the low-temperature side heat medium.

2. The heat pump system according to claim 1, wherein the control unit performs control so as to at least maintain the heat of the low-temperature side heat medium until the temperature of the low-temperature side heat medium reaches a predetermined reference value (KTwl) when the blown air is heated by the heating unit.

3. the heating section (30) is configured to circulate a high-temperature side heat medium through which heat of the high-pressure refrigerant is dissipated in the condenser, and is configured by a high-temperature side heat medium circuit (31) having a heating heat exchanger (33) that heats the blown air by heat exchange with the high-temperature side heat medium, 3. The heat pump system according to claim 1, wherein the control unit adjusts the temperature (Twl) of the low-temperature side heat medium by controlling the rotation speed (Nc) of the compressor and the operation of at least one of the heat source device and the heat quantity adjustment unit so that the temperature of the high-temperature side heat medium approaches a target high-temperature side heat medium temperature (Twoh) determined based on the target value (Qh) of the heat transfer amount.

4. the control unit determines a target value of the heat transfer amount (Qh) in accordance with a target blowing temperature (TaO) determined for the blown air to be blown into the vehicle cabin; The heat pump system according to claim 3 , wherein a target low-temperature side heat medium temperature (Twol) which is a target value for a temperature of the low-temperature side heat medium is determined so that the amount of heat transfer in the heating section approaches a target value of the amount of heat transfer.

5. The low-temperature side heat medium circuit has a low-temperature side outside air heat exchanger (43) that exchanges heat between the low-temperature side heat medium and outside air, The heat pump system according to claim 1 , wherein the control unit adjusts an amount of heat released from the low-temperature side heat medium to outside air by controlling an operation of the heat amount adjustment unit.

6. At least two upper limit values ​​are defined for the rotation speed of the compressor, a target low-temperature side heat medium temperature (Twol) is set for each of the two or more upper rotation speed values ​​of the compressors, the target value being a temperature of the low-temperature side heat medium required for the amount of heat transfer in the heating unit to achieve the target value of the amount of heat transfer, The heat pump system according to claim 1 , wherein the control unit controls the operation of the heat quantity adjustment unit so that a temperature (Twl) of the low-temperature side heat medium approaches the target low-temperature side heat medium temperature.

7. The heat pump system is mounted on a vehicle (A), The heat pump system according to claim 1 , wherein the control unit determines an upper limit value (Ncul) of a rotation speed of the compressor in accordance with a traveling speed of the vehicle.

8. The heat pump system is mounted on a vehicle (A), The heat pump system of claim 1, wherein the control unit has a driving condition estimation unit (71e) that estimates future driving conditions of the vehicle, and changes a target low-temperature side heat medium temperature (Twol), which is a target value for the temperature of the low-temperature side heat medium, based on the future driving conditions of the vehicle estimated by the driving condition estimation unit.

9. When changing the target low-temperature side heat medium temperature (Twol) based on the future traveling condition of the vehicle estimated by the traveling condition estimation unit, The heat pump system of claim 8, wherein a pre-preparation timing (tap) for operating the heat source prior to the timing of changing the target low-temperature side heat medium temperature is determined using a temperature change rate (ΔT) of the low-temperature side heat medium based on the maximum heat generation capacity of the heat source device and a current temperature (Twl) of the low-temperature side heat medium.

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