JP2014043815A - Heat storage device and vehicle heat control system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a downsized heat storage device and a vehicle heat control system having a simplified component circuit.SOLUTION: A heat storage device 5 includes: a casing 7 which forms a first fluid passage 19 and a second fluid passage 20 therein, the casing 7 where inflow/outflow ports 9, 10, 11 used for flowing a fluid in or out or flowing the fluid in and out are formed therein; a division structure 17 which is provided in the casing 7 and forms a passage of the fluid; and heat storage means 12 which is provided in the first fluid passage 19, the heat storage means 12 which absorbs heat from the fluid flowed in from the inflow/outflow ports 9, 10, 11 and radiates heat to the fluid.

Description

  The present invention relates to a heat storage device and a vehicle heat management system for accumulating heat of a fluid and discharging the accumulated heat to the fluid.

  Conventionally, as a vehicle heat storage device that keeps engine cooling water stored warm, for example, as described in Patent Document 1, it has a double tank structure including a metal inner tank and an outer tank, and a gap between both tanks. There is known a heat insulation tank whose part is vacuum insulated.

  This heat retention tank takes in the engine coolant that has become hot during vehicle travel, and stores the engine coolant while keeping the vehicle warm. Then, the engine cooling water stored and stored in the tank at the next engine start is sent to the engine and the heater core for heating the vehicle interior, and used for promoting early warm-up of the engine and early heating.

Japanese Patent No. 4061728

  However, in the conventional vehicle heat storage device, a space for providing a heat retaining tank is required, or the weight of the entire system increases due to the weight of the heat retaining tank itself. In addition, a three-way valve for switching between a passage communicating with the heat retaining tank and a bypass passage bypassing the heat retaining tank is necessary, and there is a problem that the circuit becomes complicated.

  In view of the above problems, an object of the present invention is to provide a thermal management system for a vehicle in which a heat storage device and a constituent circuit that are smaller than conventional ones are simplified.

  The invention relating to the heat storage device of the present application includes the fluid passages (19, 20) therein and at least two inflow / outflow ports (9, 10, 11) through which the fluid flows in or out or both inflow and outflow. A casing (7) that is formed, and a partition structure (17) that is provided inside the casing (7) and changes a fluid flow path. 9, 10 and 11) are provided with heat storage means (12a and 12b) for transferring heat to and from the fluid flowing in, and the partition structure (17) is provided with the heat storage means (12a and 12b) as an inflow / outflow port. Changing the flow path of the fluid so that the case where heat is transferred to the fluid flowing in from (9, 10, 11) and the case where heat is not transferred to the fluid can be performed. It is characterized by.

  According to such a configuration, the partition structure for changing the flow path of the fluid and the heat storage means for transferring heat between the fluid flowing in from the inlet / outlet port are provided in the casing. Therefore, by changing the flow path of the fluid flowing in from the inflow / outflow port by the partition structure, the case where the heat storage means stores heat from the fluid, the case where heat is radiated to the fluid, and the case where neither heat storage nor heat dissipation is performed are realized. Can do. In the present invention, the heat accumulated in the heat storage device or the heat released from the heat storage device is a term that means a heat higher than the temperature outside the vehicle, a cold heat lower than the temperature outside the vehicle, or both.

  That is, conventionally, a three-way valve that controls the amount of fluid flowing into the heat retaining tank is provided outside the heat retaining tank, but in the present invention, a partition structure that changes the flow path and a heat storage means are provided inside the casing. Yes. Therefore, the heat storage device can be miniaturized by the amount that the three-way valve is not necessary. Moreover, since the said three-way valve becomes unnecessary, the thermal management system for vehicles which has a circuit simplified more than before can be provided.

  Furthermore, the partition structure (17) is a movable structure.

  According to such a configuration, the case where the heat storage means is used and the case where it is not used can be switched without providing an on-off valve outside the casing. Therefore, the circuit configuration can be further simplified.

  Note that the reference numerals in parentheses described in the claims and the above-described means are examples of a correspondence relationship with the specific means described in the embodiments described later as one aspect, and are technical terms of the present invention. It does not limit the range.

It is a mimetic diagram of the thermal management system for vehicles concerning a 1st embodiment. It is sectional drawing of the thermal storage apparatus which concerns on 1st Embodiment. It is a perspective view which shows the external appearance of the heat storage apparatus which concerns on 1st Embodiment. It is a perspective view which shows the external appearance of the valve body of the rotary valve | bulb of 1st Embodiment. It is a mimetic diagram of the 1st mode of the thermal management system for vehicles concerning a 1st embodiment. It is a schematic diagram of the 2nd mode of the thermal management system for vehicles which concerns on 1st Embodiment. It is a schematic diagram of the 3rd mode of the thermal management system for vehicles which concerns on 1st Embodiment. It is a schematic diagram of the 4th mode of the thermal management system for vehicles which concerns on 1st Embodiment. It is a mimetic diagram of the 5th mode of the thermal management system for vehicles concerning a 1st embodiment. It is a schematic diagram of the thermal management system for vehicles which concerns on 2nd Embodiment. It is sectional drawing of the thermal storage apparatus which concerns on 3rd Embodiment. (a) is sectional drawing which shows the state before supercooling cancellation | release of the heat storage apparatus which concerns on 4th Embodiment, (b) is a cross section which shows the state where the supercooling state of the heat storage apparatus which concerns on 4th Embodiment was cancelled | released FIG. It is sectional drawing of the thermal storage apparatus which concerns on 5th Embodiment. It is sectional drawing of the thermal storage apparatus which concerns on 6th Embodiment. It is a schematic diagram of the 1st mode of the thermal management system for vehicles concerning 6th Embodiment. It is a schematic diagram of the 2nd mode of the thermal management system for vehicles which concerns on 6th Embodiment. It is a schematic diagram of the 3rd mode of the thermal management system for vehicles concerning 6th Embodiment. It is a schematic diagram of the 4th mode of the thermal management system for vehicles concerning 6th Embodiment.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS. In this embodiment, the vehicle thermal management system 1 is applied to a vehicle that obtains driving force for traveling from an engine 2 (internal combustion engine).

  As shown in FIG. 1, the vehicle thermal management system 1 includes an engine 2, a radiator 3, a heater core 4, a heat storage device 5, and pumps 6a and 6b. The pumps 6a and 6b circulate engine cooling water.

  As shown in FIG. 1, the engine 2 is connected to a radiator 3 via a cooling water passage 2a. The radiator 3 is connected to the heater core 4 through the cooling water passage 2b. The heater core 4 is connected to the heat storage device 5 through the cooling water passage 2f. The heat storage device 5 is connected to the engine 2 via the cooling water passage 2e. The cooling water passage 2b is connected to branch passages 2c and 2d. The branch passage 2c is connected to the engine 2 and the branch passage 2d is connected to the heat storage device 5. In the cooling water passage 2b, the branch passage 2d is connected between the branch passage 2c and the branch point 2g of the cooling water passage 2b and the heater core 4.

  Moreover, the pump 6a is provided in the branch passage 2c, and it flows cooling water in the direction which flows into the engine 2 by driving. The pump 6b is provided in the cooling water passage 2b between the branching point 2g and the branching point 2h of the cooling water passage 2b and the branching passage 2d, and is driven to drive the cooling water from the branching point 2g to the branching point 2h. Shed.

  The radiator 3 is a heat dissipation heat exchanger that radiates heat of the cooling water to the outside air by exchanging heat between the cooling water and the outside air. The heater core 4 is a heat exchanger for heating that uses the heat of the cooling water to heat the air for heating blown into the vehicle interior. The pumps 6a and 6b are pumps for sucking and discharging cooling water, and are driven by an electric motor.

  The heat storage device 5 accumulates or discharges the heat of the cooling water, and changes the flow path of the cooling water on the fluid circuit 100. As shown in FIG. 2, the heat storage device 5 includes casings 7, 7 a, a valve body 8 of a rotary valve, a first pipe 9, a second pipe 10, a third pipe 11, and a heat storage means 12 a that constitute an inflow / outflow port. 12b. Further, as shown in FIG. 3, the heat storage device 5 has a drive means 13 for driving the valve body 8 of the rotary valve.

  Inside the casing 7, an internal casing 7a that forms a double structure with the casing 7 is provided, and a gap 7b is provided between the casing 7 and the internal casing 7a. The gap 7b is evacuated to provide vacuum insulation. With such a structure, the heat stored in the heat storage means 12a and 12b can be effectively prevented from escaping to the outside of the casing 7.

  In the casing 7, pipe openings 9a, 10a, 11a for connecting the pipes 9, 10, 11 are formed. The casings 7, 7 a are each formed with a rotation shaft opening (not shown) so that a rotation shaft 18 described later can penetrate from the inside of the casing 7 a to the outside of the casing 7. The casing 7, 7a is made of a synthetic resin material such as nylon, PPA, or PPS. Note that metal (aluminum, SUS material) is used when pressure resistance is required.

  In FIG. 2, the 2nd piping 10 and the 3rd piping 11 are mutually arrange | positioned on the straight line. The first pipe 9 protrudes in a direction perpendicular to the straight line. The first piping 9 is connected to the cooling water passage 2e, the second piping 10 is connected to the cooling water passage 2f, and the third piping 11 is connected to the branch passage 2d.

  The valve body 8 of the rotary valve of the present embodiment is provided inside the casing 7a, and rotates to provide a flow path through which the first pipe 9, the second pipe 10, and the third pipe 11 are selectively communicated. This is a rotary three-way valve to be formed. As shown in FIG. 4, the valve body 8 of the rotary valve includes an upper side wall 14 and a lower side wall 15 facing each other, a peripheral wall 16 formed therebetween so as to support the side walls 14 and 15, and a partition structure. 17. In this embodiment, the partition structure 17 is a partition plate for forming a flow path.

  A rotary shaft 18 extending in a direction connecting the opposing side walls 14 and 15 is coupled to the upper side wall 14, and by rotating the rotary shaft 18, the rotary shaft 18 and the valve body 8 of the rotary valve are connected to each other. Rotate together.

  As shown in FIG. 4, the peripheral wall 16 extends perpendicularly from the upper side wall 14, and has a straight line connecting the center point of the upper side wall 14 and the center point of the lower side wall 15 as the central axis, and is substantially the same as the upper side wall 14. An arcuate flat portion curved with a diameter is formed. An opening 16b is formed in the valve body 8 of the rotary valve by side walls 14 and 15 and a peripheral wall 16, and the opening 16b is further divided into two small openings 16c and 16d by a partition structure 17. The small opening 16d has such a size that both the first pipe 9 and the second pipe 10 can be opened simultaneously when the valve body 8 of the rotary valve stops at the position shown in FIG. The small opening 16c is approximately the same size as the pipes 9, 10, and 11. Further, the peripheral wall 16 has a size that allows all the pipes 9, 10, and 11 to be closed simultaneously when the valve body 8 of the rotary valve stops at the position shown in FIG.

  As shown in FIGS. 2 and 4, the partition structure 17 has one end 17 a extending to the outer periphery of the side walls 14, 15 and the other end 17 b extending to the front of the outer periphery of the side walls 14, 15. As described above, the one end 17a divides the opening 16b into two small openings 16c and 16d.

  Further, by rotating the valve body 8 of the rotary valve, it is possible to switch the cooling water flowing into the casing 7a to selectively flow into either a first fluid passage 19 or a second fluid passage 20 described later. .

  The material of the side walls 14 and 15 and the peripheral wall 16 is a resin material or the like having a heat insulating property that prevents heat from passing outside. Therefore, it is possible to prevent the heat stored in the heat storage means 12a and 12b from escaping to the outside of the valve body 8 of the rotary valve.

  The heat storage means 12a, 12b accumulates the heat of the cooling water flowing in from the inflow / outflow ports 9, 10, 11 or releases the accumulated heat to the cooling water. The heat storage means 12a and 12b are formed by incorporating paraffin inside an aluminum case. As shown in FIG. 2, the heat storage means 12 a is formed in an arcuate plane that is approximately the same size as the peripheral wall 16, and is attached to the inner peripheral surface of the peripheral wall 16. The heat storage means 12 b is provided on a surface of the partition structure 17 that faces the inner peripheral surface of the peripheral wall 16, and has a shape that swells in the direction of the inner peripheral surface of the peripheral wall 16. The height of the heat storage means 12b (the length in the direction perpendicular to the paper surface in FIG. 2) is substantially the same as that of the partition structure 17. With such a configuration, the first fluid passage 19 is formed by the casing 7 a, the valve body 8 of the rotary valve, and the heat storage means 12.

  As shown in FIG. 2, since the heat storage means 12b has a shape that swells along the inner periphery of the peripheral wall 16, the first fluid passage 19 has a curved shape along the heat storage means 12a. The small openings 16c and 16d form either an inlet or an outlet of the first fluid passage 19, respectively. With such a structure, the distance of the first fluid passage 19 can be longer than that of the second fluid passage 20. Therefore, the contact time between the heat storage means 12a, 12b and the cooling water can be lengthened, and the heat storage time and the time during which heat is released from the heat storage means 12a, 12b to the cooling water can be ensured long.

  When the valve body 8 of the rotary valve stops at the position shown in FIG. 2, the first pipe 9, the second fluid passage 20 and the second pipe 10 communicate with each other, and when the valve body 8 stops at the position shown in FIG. When the first pipe 9, the first fluid passage 19 and the second pipe 10 communicate with each other and stop at the position shown in FIG. 7, all the pipes 9, 10, 11 are closed simultaneously, and the position shown in FIG. When the operation is stopped, the first pipe 9, the first fluid passage 19, and the third pipe 11 are communicated. As described above, the valve body 8 of the rotary valve has a cooling water flow path so that the cooling water flowing into the casing 7 a selectively flows into one of the first fluid passage 19 and the second fluid passage 20. Can be switched.

  As shown in FIG. 2, a seal member 16a is provided in the inner casing 7a, the pipes 9, 10, 11 and the connection portions. With such a structure, it is possible to prevent the cooling water flowing into the casing 7a from flowing out from the closed pipe to the circuit 100 through a gap formed between the casing 7a and the valve 8 of the rotary valve. Can do. The material of the seal member 16a is preferably a rubber material that is durable to ethylene glycol, a rust inhibitor, a performance improver, and the like blended in the cooling water. Therefore, generally, EPDM and fluororubber are used. Further, in order to prevent the cooling water existing inside the casing 7a from leaking to the outside of the casing 7a through the rotating shaft opening, the rotating shaft opening is provided with a cylindrical seal by an O-ring.

  The drive means 13 shown in FIG. 3 drives the valve body 8 of the rotary valve by a predetermined rotation angle by transmitting the power of the drive source to the rotation shaft 18 and controlling the angle of the rotation shaft 18. Is repeated to stop. The drive means 13 includes a drive motor (not shown) and a power transmission member such as a gear that transmits the rotational power of the drive motor to the valve body 8 of the rotary valve.

  The engine 2 is provided with three cooling water openings (not shown), one connected to the cooling water passage 2a, the other connected to the branch passage 2c, and the other one. Is connected to the cooling water passage 2e.

  With the above configuration, cooling water can be flowed as follows. By driving the pump 6a, the cooling water flowing out from the engine 2 can flow into the engine 2 through the cooling water passage 2a, the radiator 3, the cooling water passage 2b, and the branch passage 2c (broken arrows in FIG. 5).

  The pump 6a is driven, the pump 6b is stopped, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. 5, so that the cooling water flowing out from the engine 2 flows into the cooling water passage 2e, the first pipe 9, It flows into the engine 2 through the first fluid passage 19, the second pipe 10, the cooling water passage 2f, the heater core 4, the cooling water passage 2b, and the branch passage 2c (solid arrow in FIG. 5).

  The pump 6a is driven, the pump 6b is stopped, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. 6, so that the cooling water flowing out from the engine 2 flows into the cooling water passage 2e, the first pipe 9, The second fluid passage 20, the second pipe 10, the cooling water passage 2 f, the heater core 4, the cooling water passage 2 b and the branch passage 2 c can be introduced into the engine 2 (solid arrow in FIG. 6).

  The pump 6a is stopped, the pump 6b is driven, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. 8, so that the cooling water flowing out from the engine 2 flows into the branch passage 2c, the cooling water passage 2b, the branch passage. 2d, the third pipe 11, the first fluid passage 19, the first pipe 9, and the cooling water passage 2e can be introduced into the engine 2 (solid arrow in FIG. 8).

  The pump 6a is stopped, the pump 6b is driven, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. 9, so that the cooling water flowing out from the engine 2 flows into the branch passage 2c, the cooling water passage 2b, and the heater core 4 The cooling water passage 2f, the second piping 10, the first fluid passage 19, the first piping 9, and the cooling water passage 2e can be flowed into the engine 2 (solid arrow in FIG. 9).

  Next, the outline of the operation of the present embodiment in the above configuration will be described. The vehicle thermal management system 1 is switched between the first mode to the fifth mode described below according to the situation by control signals from various sensors (not shown).

  The first mode is a heat storage mode in which the heat of the cooling water is stored in the heat storage means 5. In the first mode, the pump 6a is driven, the pump 6b is stopped, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. Thereby, the cooling water flows as shown by the broken line arrows and the solid line arrows in FIG. The cooling water radiates heat to the heat storage means 12a and 12b when passing through the first fluid passage 19, and is stored in the heat storage means 12a and 12b.

  The second mode is a heat storage unnecessary mode in the case where the accumulation of warm heat from the cooling water to the heat storage device 5 is completed in a state where the engine 2 is driven. In the second mode, the first pump 6a is driven, the second pump 6b is stopped, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. Thereby, the cooling water flows as shown by the broken line arrows and the solid line arrows in FIG. Therefore, the cooling water does not pass through the first fluid passage 19.

  The third mode is an engine stop mode in which the engine 2 is stopped. In the third mode, the pump 6a and the pump 6b are stopped, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. Thereby, each piping 9,10,11 is closed, and the flow of the fluid which flows through each piping 9,10,11 is interrupted | blocked. Therefore, it is possible to prevent the heat from escaping from the heat storage device 5 through the pipes 9, 10, 11 and flow to the circuit 100, and to keep the heat warm.

  In the fourth mode, the temperature stored in the heat storage means 5 is used to warm up the engine 2 before driving the engine 2, or the engine water temperature is increased immediately after the engine 2 is started. This is an engine pre-warm-up mode in which the temperature is equal to or lower than a temperature sufficient to warm up the engine 2. In this mode, for example, in a hybrid vehicle or a plug-in hybrid vehicle that can be charged from a commercial power supply to a traveling battery, the engine 2 is used and only the motor travels. 2 By estimating the time when the operation is required, the engine 2 is warmed up before the engine 2 is started. In the fourth mode, the pump 6a is stopped, the pump 6b is driven, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. Thereby, the cooling water flows as shown by the solid line arrow in FIG. The cooling water absorbs heat from the heat storage means 12 a and 12 b when passing through the first fluid passage 19. Thereafter, the cooling water flows into the engine 2. Therefore, the engine 2 can be pre-warmed using the heat of the heat storage device 5.

  The fifth mode is a vehicle having an idling stop mode in which the engine 2 automatically pauses when the vehicle is temporarily stopped due to a signal or the like while the vehicle is running, and warms up the room in the idling stop state. This mode is used when necessary. In the fifth mode, the pump 6a is stopped, the pump 6b is driven, and the valve body 8 of the rotary valve is stopped at the position shown in FIG. As a result, the cooling water flows as shown by the solid line arrows in FIG. When the cooling water passes through the first fluid passage 19, it absorbs the heat from the heat storage means 12a, 12b. Thereafter, the cooling water flows into the heater core 4 through the engine 2. Therefore, heating by the heater core 4 can be continuously performed by using the heat of the heat storage device 5 and allowing the heat to be continuously dissipated to the cooling water by the large heat capacity of the engine 2.

  After the fifth mode is canceled, when the temperature of the cooling water flowing into the heater core 4 is lower than a predetermined temperature (for example, 60 ° C.), the fifth mode is postponed. Alternatively, the pump 6a is driven to stop the pump 6b, the valve body 8 of the rotary valve is stopped at the position shown in FIG. 5, and the cooling water is allowed to flow as shown by the solid line arrow in FIG. An effect can be obtained. In this case, the cooling water that has flowed out of the heater core 4 flows into the cooling water passage 2 b, the branch passage 2 c, and the engine 2. Thereafter, the cooling water flowing out of the engine 2 flows into the first fluid passage 19 through the first pipe 9, absorbs heat from the heat storage means 12 a and 12 b, and then flows into the heater core 4 through the second pipe 10.

  As described above, the heat storage means 12a, 12b stores heat from the cooling water and dissipates heat to the cooling water by changing the flow path of the cooling water flowing in from the inflow / outflow ports 9, 10, 11 by the partition structure 17. And the case where neither heat storage nor heat dissipation is performed can be realized. That is, in this embodiment, the heat storage device 5 can be reduced in size by the amount that the three-way valve that changes the flow path of the cooling water is not necessary. Moreover, since the said three-way valve becomes unnecessary, the thermal management system 1 for vehicles which has the circuit 100 simplified rather than before can be provided.

(Second Embodiment)
In the first embodiment, the vehicle thermal management system 1 is configured to be applied to a vehicle that obtains driving force for traveling from the engine 2 (internal combustion engine). In the second embodiment, the vehicle thermal management system 1 is based on the water-cooled battery 26. It is applied to a vehicle that obtains driving force for traveling. The vehicle thermal management system 1 according to the first embodiment is composed of the engine 2, the radiator 3, the heater core 4, the heat storage device 5, and the pumps 6a and 6b, but the vehicle thermal management system according to the second embodiment. As shown in FIG. 10, 1A includes a first fluid circulation circuit 110 having a heater core 4, a radiator 3, a first fluid circulation pump 6c and a water-cooled condenser 21, a chiller 22, a cooler core 23, and a second fluid circulation pump 6d. And a cooling circuit 130 having a compressor 24, a water-cooled condenser 21, an expansion valve 25, and a chiller 22.

  Further, as shown in FIG. 10, the cooling water circulating through at least one of the first fluid circulation circuit 110 and the second fluid circulation circuit 120 is circulated on the downstream side of the heat storage device 5 and the temperature is adjusted. A water-cooled water-cooled battery 26 which is a regulating device is provided.

  The water-cooled condenser 21 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 24 and the heat medium (in this embodiment, cooling water flowing through the first fluid circulation circuit 110) to cool the refrigerant and heat the heat medium. It is a heat source that In the present embodiment, since chlorofluorocarbon (R134a) is used as the refrigerant, the enthalpy is lowered by cooling and condensing the refrigerant in the water-cooled condenser 21.

  The chiller 22 heats the refrigerant by exchanging heat between the low-temperature and low-pressure refrigerant discharged from the expansion valve 25 and the heat medium (in this embodiment, cooling water flowing through the second fluid circulation circuit 120), and cools the heat medium. It is a cold heat source. The cooler core 23 is a cooling heat exchanger that cools the blown air by exchanging heat between the cooling water and the blown air. The compressor 24 sucks and compresses the refrigerant. In this embodiment, the compressor 24 operates by obtaining power from driving means (not shown) via power transmission means. The expansion valve 25 is a decompression unit that decompresses the high-pressure refrigerant that has flowed out of the water-cooled condenser 21.

  The water-cooled battery 26 includes a fluid inflow port 26a through which cooling water on the circuit flows into the water-cooled battery 26, and a fluid outflow port 26b through which cooling water within the water-cooled battery 26 flows out onto the circuit. ,have. The water-cooled battery 26 is desirably maintained in a predetermined temperature range (about 10 ° C. to 40 ° C.) from the viewpoint of extending the life. The fluid inflow port 26a and the heat storage device 5 are connected via a cooling water passage 2i. The cooling water passage 2i is provided with cooling water temperature detecting means, for example, a thermistor 27 for detecting the temperature of the cooling water. Yes. The fluid outflow port 26b is connected to the first fluid circulation circuit 110 and the second fluid circulation circuit 120 through a valve device (not shown). The valve device controls the communication state between the fluid outflow port 26b and the first fluid circulation circuit 110 and the second fluid circulation circuit 120.

  As shown in FIG. 10, the heat storage device 5 includes a second pipe 10 that is a first inflow port, a third pipe 11 that is a second inflow port, and a first pipe 9 that is an outflow port. The second pipe 10 is provided in the first fluid circulation circuit 110 between the water-cooled condenser 21 and the heater core 4 at a portion where high-temperature cooling water heated by the water-cooled condenser 21 can flow. In the second fluid circulation circuit 120, the third pipe 11 is connected between the chiller 22 and the cooler core 23 and to a portion into which the low-temperature cooling water cooled by the chiller 22 can flow. The first pipe 9 is connected to the water-cooled battery 26 through the cooling water passage 2i.

  When the temperature detected by the cooling water temperature detecting means 27 is lower than a predetermined value lower than 25 ° C., the valve body 8 of the rotary valve has the second pipe 10, the first fluid passage 19, and the first pipe. 9 is stopped at a position where it communicates with the position 9 (position shown in FIG. 10). Stop at a communicating position (not shown). Further, when the cooling water does not flow on the circuits 110 and 120, the valve body 8 of the rotary valve stops at a position (not shown) where all the pipes 9, 10 and 11 are closed simultaneously.

  Here, a value obtained by adding or subtracting a predetermined value with respect to 25 ° C. is used as a criterion. If set at 25 ° C., the operation is frequently repeated when the water temperature is about 25 ° C. (hunting) This is because there is a possibility that hunting can be prevented by providing a width of a predetermined value.

  In the cooling circuit 130, the refrigerant flows as shown by the broken line in FIG. The refrigerant flowing into the compressor 24 is compressed by the compressor 24 and becomes a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant flows into the water-cooled condenser 21, where heat is released into the cooling water flowing through the first fluid circulation circuit 110 and liquefied. The liquid refrigerant is subjected to a throttling action by the expansion valve 25 to be depressurized to be in a low temperature and low pressure state, and then flows into the chiller 22. The refrigerant takes heat from the cooling water flowing through the second fluid circulation circuit 120 by the chiller 22 and vaporizes, and then flows into the compressor 24.

  In the first fluid circulation circuit 110, the cooling water flows as shown by the solid line in FIG. Cooling water flowing out from the water-cooled battery 26 flows into the water-cooled condenser 21 via the radiator 3. In addition, when heating is performed by flowing warm water through the heater core 4, if heat is released to the outside air by the radiator 3, energy loss occurs, so the cooling water passes through the bypass cooling water passage 2j. Thus, the three-way valve 28 is switched. Thereafter, the cooling water is heated by exchanging heat with the high-temperature and high-pressure refrigerant in the water-cooled condenser 21. Then, when a part of the heated cooling water flows into the heater core 4 and the aforementioned predetermined temperature condition (less than a predetermined value lower than 25 ° C.) is satisfied, the remaining cooling water is supplied to the second pipe 10. Into the heat storage device 5. After passing through the first fluid passage 19, the cooling water flows out from the first pipe 9 and flows into the water-cooled battery 26.

  In the second fluid circulation circuit 120, the cooling water flows as shown by a one-dot chain line in FIG. The cooling water flowing out of the water-cooled battery 26 is cooled by exchanging heat with the low-temperature and low-pressure refrigerant in the chiller 22. Then, when a part of the cooled cooling water flows into the cooler core 23 and the aforementioned predetermined temperature condition (above a value obtained by adding a predetermined value over 25 ° C.) is satisfied, the remaining cooling water is supplied to the third pipe. 11 flows into the heat storage device 5. After passing through the first fluid passage 19, the cooling water flows out from the first pipe 9 and flows into the water-cooled battery 26.

  Next, the outline of the operation of the present embodiment in the above configuration will be described. When the water-cooled battery 26 is driven, cooling water flows through the first fluid circulation circuit 110 and the second fluid circulation circuit 120, and refrigerant flows through the cooling circuit 130. When the temperature detected by the thermistor 27 is less than a predetermined value lower than 25 ° C., the cooling water flows from the third pipe 11 into the first fluid passage 19 and releases the heat to the heat storage means 12a and 12b. In addition, cold heat is absorbed from the heat storage means 12a, 12b. Thereafter, the cooling water flows out from the first pipe 9 and flows into the water-cooled battery 26.

  When the temperature detected by the cooling water temperature detection means 27 is not less than a predetermined value in addition to 25 ° C., the cooling water flows into the first fluid passage 19 from the second pipe 10 and enters the heat storage means 12a and 12b. Cold heat is released and heat is absorbed from the heat storage means 12a and 12b. Thereafter, the cooling water flows out from the first pipe 9 and flows into the water-cooled battery 26.

  By repeating these operations, cooling water in the vicinity of the median value (25 ° C.) of the predetermined temperature can be stably flowed to the water-cooled battery 26, and the life of the water-cooled battery 26 can be extended. Further, when there is no heat storage means 12a, 12b, there is a problem that frequent operation of the switching means 8 is necessary to aim at the median value of the predetermined temperature, and the operating life of the switching means 8 is shortened. By providing 12a and 12b, the water temperature slowly changes in a range close to the median value of the predetermined temperature, so that frequent operation of the switching means 8 becomes unnecessary.

  In addition, when the water-cooled battery 26 is not generating heat, for example, when the above-mentioned predetermined temperature condition is not applied, it is not necessary to flow cooling water through the circuits 110 and 120. It is closed by the valve body 8 of the type valve, and heat is kept inside the heat storage device 5. The retained heat can be used when the water-cooled battery 26 is driven next time.

(Third embodiment)
In the first embodiment, the switching means is the valve body 8 of the rotary valve provided inside the casings 7 and 7a. However, in the third embodiment, as shown in FIG. Thus, the pipes 9, 10 and 11 are provided with on-off valves 9b, 10b and 11b which are switching means, respectively. In addition, the on-off valves 9b, 10b, and 11b shown in FIG. 11 show a state in which the pipes 9, 10, and 11 are closed, respectively.

  A cylindrical heat storage means 12 c is provided at the center of the casing 7. In addition, fixed partition plates 29a and 29b that are longer in the vertical direction (in the direction perpendicular to the paper surface in FIG. 11) than the heat storage means 12c are provided inside the casing 7. As shown in FIG. 11, the fixed partition plate 29 a has a size facing the first pipe 9 and the third pipe 11, and when the cooling water flowing in from the first pipe 9 flows out from the third pipe 11, It is provided so that water does not contact the heat storage means 12c. A second fluid passage 20a is formed by the fixed partition plate 29a and the inner casing 7a. As shown in FIG. 11, the fixed partition plate 29 b is provided in the vicinity of the first pipe 9 on a passage communicating the first pipe 9 and the second pipe 10 formed inside the inner casing 7 a. . With such a configuration, the first fluid passage 19 a is formed on the passage communicating the third pipe 11 and the second pipe 10.

  As described above, by changing the flow path of the cooling water flowing from the inflow port by the fixed partition plates 29a and 29b, the heat storage means 12c stores heat from the cooling water, dissipates heat to the cooling water, and stores heat and releases heat. The case where neither is performed can be realized.

  That is, the heat storage device 5B can be reduced in size by the amount that eliminates the need for the three-way valve that changes the flow path of the coolant. Moreover, since the said three-way valve becomes unnecessary, the thermal management system 1B for vehicles which has a circuit simplified more than before can be provided.

  Further, the on-off valve 9b is closed, the on-off valve 10b and the on-off valve 11b are opened, or the on-off valve 9b and the on-off valve 10b are opened and the on-off valve 11b is closed, so that the cooling water flowing into the heat storage device 5B is the first. The fluid can pass through the fluid passage 19a and flow out of the heat storage device 5B. Therefore, heat can be stored in the heat storage means 12c from the cooling water, or the accumulated heat can be released to the cooling water. Further, by opening the on-off valve 9b and the on-off valve 11b and closing the on-off valve 10b, the cooling water flowing into the heat storage device 5B can pass through the second fluid passage 20a and flow out of the heat storage device 5B. it can. Therefore, it is possible to prevent the heat storage means 12c from performing either heat storage or heat dissipation. Thus, the internal structure of the heat storage device 5B can be simplified by providing the on-off valves 9b, 10b, and 11b.

(Fourth embodiment)
In the first embodiment and the second embodiment, the first fluid passage 19 and the second fluid passage 20 are provided in the inner casing 7a at the same time. However, in the fourth embodiment, the inside of the inner casing 7a is provided as necessary. Is switched to the first fluid passage 19b or the second fluid passage 20b.

  As shown in FIG. 12A, the heat storage device 5C of the fourth embodiment has a structure in which a heat storage means 12d is provided inside the inner casing 7a. As shown in FIG. 12A, the heat storage means 12d has a circular shape with projections added thereto, and the height (the length in the direction perpendicular to the paper surface in FIG. 12A) is that of the inner casing 7a. About the same height. The heat storage means 12d is formed of a heat storage material that stores or radiates heat using latent heat during melting and solidification, for example, sodium acetate hydrate.

  This heat storage material can take a supercooled state in which it does not solidify to a certain temperature even if it is below the freezing point. In the process from the supercooled state to solidification, solidification can be started at once by further cooling or applying an impact from the outside, and at that time, heat is released as solidification heat.

  In addition, a valve body 8a of a rotary valve including a peripheral wall 16f that is a partitioning structure and a pressurizing protrusion 16e is provided inside the inner casing 7a. The peripheral wall 16f is large enough to close at least one of the pipes 9, 10, and 11. When the valve body 8a of the rotary valve is stopped at the position shown in FIG. 10 and 11 also have a size that does not close. The pressure protrusion 16e is a quadrangular prism and has a height approximately the same as that of the peripheral wall 16f. The pressure protrusion 16e is attached to one end of the peripheral wall 16f.

  When heat storage is performed, the valve body 8a of the rotary valve is stopped at a position where the pressurizing projection 16e and the heat storage means 12d do not contact each other, for example, the position shown in FIG. At this time, when the water temperature of the cooling water flowing in from any of the pipes 9, 10, 11 is higher than the melting point, the heat storage unit 12 d performs only heat storage for sensible heat and does not perform heat storage due to latent heat. Here, when the temperature of the cooling water flowing in decreases, and when the temperature falls below the melting point of the heat storage material, the heat storage material can be in a supercooled state without solidifying. By adjusting the material and setting the melting point of the heat storage material to a value (for example, 55 ° C.) that is slightly higher than the lower limit water temperature value (for example, 50 ° C.) that can be heated at the minimum by the heater core 4, the water temperature is reduced. When it falls below 55 ° C., it becomes supercooled.

  Here, when the cooling water temperature falls below 50 ° C., it is necessary to continue heating, and thus the cooling water is heated using heat storage. The heat storage material needs to be given an opportunity to change from the liquid phase to the solid phase. Specifically, the valve body 8a of the rotary valve is rotated in the direction indicated by the solid line arrow in FIG. The heat storage means 12d is pressed against the part 16e to pressurize the heat storage means 12d. Thereby, the supercooled state of the heat storage means 12d is released, and the temperature of the cooling water can be increased by dissipating heat to the surroundings. In this way, with a simple structure, the cooling water can selectively flow into either the first fluid passage 19b or the second fluid passage 20b. Moreover, in this structure, since the inside of the casing 7 becomes the first fluid passage 19b or the second fluid passage 20b depending on the situation, it is not necessary to provide both the passages 19b and 20b at the same time. Compared to the case of the form and the second embodiment, it can be made smaller.

(Fifth embodiment)
In the first embodiment, the switching means is constituted by the valve body 8 of the rotary valve. However, in the heat storage device 5D of the fifth embodiment, the switching means 30 is an inflow / outflow port as shown in FIG. It is composed of a bimetal that is a temperature-sensitive member that expands and contracts in accordance with the temperature of the cooling water flowing in from a certain second pipe 10 and third pipe 11 and operates in accordance with the expansion and contraction. As shown in FIG. 13, in the fifth embodiment, the first pipe 9 is not provided. A columnar heat storage means 12 e is provided at the center inside the casing 7. Further, as shown in FIG. 13, the inner casing 7a has a height approximately the same as the heat storage means 12e (the length in the direction perpendicular to the paper surface in FIG. 13), and the circumference of the heat storage means 12e is substantially the same. A fixed partition plate 29c having a size covering half is provided. A first fluid passage 19c and a second fluid passage 20c are formed by the fixed partition plate 29c, the inner casing 7a, and the heat storage means 12e.

  Further, a bimetal partition plate 30 is provided inside the inner casing 7a. As shown in FIG. 13, the bimetal partition plate 30 is provided in a portion of the fixed partition plate 29 c facing the third pipe 11 side. In this way, by providing the bimetal partition plate 30 at the junction where the first fluid passage 19c and the second fluid passage 20c join together, it is not affected by the heat of the heat storage means 12e and is based on the temperature of the cooling water itself. The bimetal partition plate 30 can be operated. Therefore, when storing heat based on the temperature of the cooling water, when radiating heat, it is possible to switch between the case where neither heat storage nor heat dissipation is performed. The bimetal partition plate 30 is formed by bonding two types of metal plates 30a and 30b having different coefficients of thermal expansion, one metal plate 30a is opposed to the first fluid passage 19c, and the other metal plate 30b is the second fluid passage. 20c.

  The metal plate 30b has a larger amount of elongation than the metal plate 30a at a predetermined temperature, for example, a temperature higher than the lower limit cooling water temperature (50 ° C.) necessary for air passing through the heater core to heat the vehicle interior to an appropriate temperature. Thus, the component composition, the cross-sectional shape, the thickness, and the like that are configured are designed. Further, the component composition, the cross-sectional shape, the thickness, and the like of the metal plate 30a are designed so that the elongation amount is larger than that of the metal plate 30b at a temperature lower than the predetermined temperature.

  With such a configuration, when the temperature of the cooling water flowing from the third pipe 11 into the inner casing 7a is equal to or higher than a predetermined temperature, the metal plate 30b expands more than the metal plate 30a. Therefore, the bimetal partition plate 30 is curved to close the first fluid passage 19c and open the second fluid passage 20c. When the temperature is lower than the predetermined temperature, the metal plate 30a expands more than the metal plate 30b. Therefore, the bimetal partition plate 30 is curved, opens the first fluid passage 19c, and closes the second fluid passage 20c.

  In this way, by using the bimetal partition plate 30, the cooling water can selectively flow into either the first fluid passage 19c or the second fluid passage 20c without using the drive means for driving the switching means. . Therefore, the cost required for the driving means can be reduced.

(Sixth embodiment)
In the second embodiment, the vehicle thermal management system 1 </ b> A is composed of one heat storage device 5 having three pipes 9, 10, 11 and a plurality of circuits 110, 120, 130. The vehicle thermal management system 1E includes two heat storage devices 5E and 5F having four pipes 9, 10, 11, and 31 and a plurality of circuits 110a, 120a, and 130.
The circuit 110a is a circuit including a water-cooled capacitor 21 described later, the circuit 120a is a circuit including a chiller 22 described later, and the circuit 130 is the cooling circuit described in the second embodiment.

  As shown in FIG. 15, each heat storage device 5E, 5F is provided with a first pipe 9, a second pipe 10, a third pipe 11, and a fourth pipe 31, respectively. The second pipe 10 of the heat storage device 5E is connected to a water-cooled inverter 54 through a cooling water passage 50a. The inverter 54 is connected to the third pipe 11 of the heat storage device 5F via the cooling water passage 50b. A branch passage 51 is provided in the cooling water passage 50 a and is connected to the cooling water passage 50 b via the radiator 3. The cooling water passage 50 a and the branch passage 51 are connected via a three-way valve 53. The third pipe 11 of the heat storage device 5E is connected to the water-cooled battery 56 through the cooling water passage 50c. The water-cooled battery 56 is connected to the second pipe 10 of the heat storage device 5F via the cooling water passage 50d.

  The first pipe 9 of the heat storage device 5E is connected to the heater core 4 via the cooling water passage 50e. The heater core 4 is connected to the water-cooled condenser 21 through the cooling water passage 50f. The water-cooled condenser 21 is connected to the first pipe 9 of the heat storage device 5F via the cooling water passage 50g. The fourth pipe 31 of the heat storage device 5E is connected to the cooler core 23 via the cooling water passage 50h. The cooler core 23 is connected to the chiller 22 via the cooling water passage 50i. The chiller 22 is connected to the fourth pipe 31 of the heat storage device 5F through the cooling water passage 50j. In addition, the chiller 22 and the water-cooled condenser 21 constitute a refrigerant circuit 130 together with a compressor 24 and an expansion valve 25 (not shown). Further, fluid circulation pumps 55a and 55b are provided in the cooling water passages 50g and 50j, respectively. The fluid circulation pump 55a is driven to flow cooling water from the first pipe 9 of the heat storage device 5F toward the water-cooled condenser 21, and the fluid circulation pump 55b is driven to drive the chiller 22 from the fourth pipe 31 of the heat storage device 5F. Flow cooling water toward

  Next, the structure of the heat storage devices 5E and 5F will be described. Since the two heat storage devices 5E and 5F have the same structure, the structure of the heat storage device 5E will be described below. As shown in FIG. 14, among the four pipes 9, 10, 11, 31, the second pipe 10 and the third pipe 11 are arranged on a straight line, and the first pipe 9 and the fourth pipe 31 are mutually connected. It is arranged on a straight line. The first pipe 9 and the fourth pipe 31 protrude in a direction perpendicular to the straight line formed by the second pipe 10 and the third pipe 11. The valve body 8b of the rotary valve of the present embodiment rotates to communicate the first pipe 9 and the second pipe 10, and to communicate the third pipe 11 and the fourth pipe 31, This is a rotary four-way valve that selectively switches between a state in which the pipe 10 and the fourth pipe 31 are communicated and a state in which the first pipe 9 and the third pipe 11 are communicated.

  As shown in FIG. 14, four peripheral walls 32 a, 32 b, 32 c, and 32 d are provided and are spaced apart from each other at an interval of about 90 degrees with respect to the center point of the side wall 14. Accordingly, four openings 33, 34, 35, 36 are formed by the peripheral walls 32 a, 32 b, 32 c, 32 d and the side walls 14, 15. The sizes of the openings 33, 34, 35, and 36 are all approximately the same, and the sizes of the openings 33, 34, 35, and 36 can be opened simultaneously by all the openings 33, 34, 35, and 36. is there.

  The lateral width of the partition structure 37 is substantially equal to the distance between the opposed peripheral walls 32b and 32d, and the height of the partition structure 37 is approximately equal to the distance between the side walls 14 and 15. The partition structure 37 is provided in the valve body 8b of the rotary valve so that the left and right ends are in contact with the peripheral walls 32b and 32d and the upper and lower ends are in contact with the side walls 14 and 15. With such a structure, the opening 33 and the opening 34 communicate with each other, and the opening 35 and the opening 36 communicate with each other. Further, a partition structure 38 is provided in the space provided between the opening 35 and the opening 36, and the opening 35 is divided into two small openings 35a and 35b having substantially the same size. . The upper and lower ends of the partition structure 38 are in contact with the side walls 14 and 15, one end 38 a extending in the direction of the opening 35 in the left and right ends extends to the outer periphery of the side walls 14 and 15, and the other end 38 b is the outer periphery of the side walls 14 and 15. It extends to the front. The heat storage means 12f is provided on the opposing surfaces of the two partition structures 37 and 38, respectively.

  With the above configuration, the first fluid passage 19d is formed between the small opening 35b and the opening 36, and the second fluid passage 20d is formed between the small opening 35a and the opening 36. The second fluid passage 20e is formed between the opening 33 and the opening 34. Therefore, when the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5E depicted in the upper part of FIG. 15, the first pipe 9, the second fluid passage 20d, and the second pipe 10 communicate with each other. The third pipe 11, the second fluid passage 20e, and the fourth pipe 31 are communicated with each other. When the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5F depicted below in FIG. 15, the first pipe 9, the second fluid passage 20d, and the third pipe 11 communicate with each other. The two pipes 10, the second fluid passage 20e, and the fourth pipe 31 are communicated. When the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5E depicted in the upper part of FIG. 16, the first pipe 9, the second fluid passage 20e, and the third pipe 11 communicate with each other. The two pipes 10, the second fluid passage 20d, and the fourth pipe 31 are communicated.

  When the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5E depicted in the upper part of FIG. 17, the first pipe 9, the first fluid passage 19d, and the second pipe 10 communicate with each other. The three pipes 11, the second fluid passage 20 e, and the fourth pipe 31 are communicated. When the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5F depicted below in FIG. 17, the first pipe 9, the first fluid passage 19d, and the third pipe 11 communicate with each other. The two pipes 10, the second fluid passage 20e, and the fourth pipe 31 are communicated. When the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5E depicted in the upper part of FIG. 18, the first pipe 9, the second fluid passage 20e, and the second pipe 10 communicate with each other. The three pipes 11, the first fluid passage 19 d, and the fourth pipe 31 are communicated. When the valve body 8b of the rotary valve stops at the position shown in the heat storage device 5F depicted in the lower part of FIG. 18, the first pipe 9, the second fluid passage 20e, and the third pipe 11 communicate with each other. The two pipes 10, the first fluid passage 19d and the fourth pipe 31 are communicated.

  With the above configuration, cooling water can be flowed as follows. By driving the fluid circulation pumps 55a and 55b and stopping the valve bodies 8b of the rotary valves of the heat storage devices 5E and 5F at the positions shown in FIG. 15, the cooling water flowing out from the heater core 4 is cooled to the cooling water passage 50e, Via the second fluid passage 20d of the heat storage device 5E, the cooling water passage 50a, the inverter 54, the cooling water passage 50b, the second fluid passage 20d of the heat storage device 5F, the cooling water passage 50g, the water-cooled condenser 21 and the cooling water passage 50f. It flows into the heater core 4 again (solid line arrow in FIG. 15). A part of the cooling water flowing through the cooling water passage 50 a flows into the cooling water passage 50 b through the branch passage 51 and the radiator 3. The cooling water flowing out of the cooler core 23 is the cooling water passage 50h, the second fluid passage 20e of the heat storage device 5E, the cooling water passage 50c, the water-cooled battery 56, the cooling water passage 50d, and the second fluid passage 20e of the heat storage device 5F. Then, it flows again into the cooler core 23 through the cooling water passage 50j, the chiller 22 and the cooling water passage 50i (broken arrows in FIG. 15).

  The fluid circulating pumps 55a and 55b are driven, and the valve bodies 8b of the rotary valves of the heat storage devices 5E and 5F are stopped at the positions shown in FIG. 16, respectively. A second fluid passage 20e, a cooling water passage 50c, a water cooling battery 56, a cooling water passage 50d, a second fluid passage 20d, a cooling water passage 50g, a cooling water passage 50g, a water cooling condenser 21 and a cooling water passage 50f of the heat storage device 5E are provided. And again flows into the heater core 4 (solid arrow in FIG. 16). In addition, the cooling water flowing out of the cooler core 23 is the cooling water passage 50h, the second fluid passage 20d of the heat storage device 5E, the cooling water passage 50a, the inverter 54, the cooling water passage 50b, the second fluid passage 20e of the heat storage device 5F, and the cooling. It flows again into the cooler core 23 through the water passage 50j, the chiller 22 and the cooling water passage 50i (broken arrows in FIG. 16). A part of the cooling water flowing through the cooling water passage 50 a flows into the cooling water passage 50 b through the branch passage 51 and the radiator 3.

  The fluid circulating pumps 55a and 55b are driven, and the valve bodies 8b of the rotary valves of the heat storage devices 5E and 5F are stopped at the positions shown in FIG. Again through the first fluid passage 19d of the heat storage device 5E, the cooling water passage 50a, the inverter 54, the cooling water passage 50b, the first fluid passage 19d of the heat storage device 5F, the cooling water passage 50g, the water-cooled condenser 21 and the cooling water passage 50f. It flows into the heater core 4 (solid arrow in FIG. 17). The cooling water flowing out of the cooler core 23 is the cooling water passage 50h, the second fluid passage 20e of the heat storage device 5E, the cooling water passage 50c, the water-cooled battery 56, the cooling water passage 50d, and the second fluid passage 20e of the heat storage device 5F. Then, it flows again into the cooler core 23 through the cooling water passage 50j, the chiller 22 and the cooling water passage 50i (broken arrows in FIG. 17).

  By driving the fluid circulation pumps 55a and 55b and stopping the valve bodies 8b of the rotary valves of the heat storage devices 5E and 5F at the positions shown in FIG. 18 respectively, the cooling water flowing out from the heater core 4 is supplied to the cooling water passage 50e, Via the second fluid passage 20e of the heat storage device 5E, the cooling water passage 50a, the inverter 54, the cooling water passage 50b, the second fluid passage 20e of the heat storage device 5F, the cooling water passage 50g, the water-cooled condenser 21 and the cooling water passage 50f. It flows into the heater core 4 again (solid line arrow in FIG. 18). A part of the cooling water flowing through the cooling water passage 50 a flows into the cooling water passage 50 b through the branch passage 51 and the radiator 3. The cooling water flowing out of the cooler core 23 is the cooling water passage 50h, the first fluid passage 19d of the heat storage device 5E, the cooling water passage 50c, the water cooling battery 56, the cooling water passage 50d, and the first fluid passage 19d of the heat storage device 5F. Then, it flows again into the cooler core 23 through the cooling water passage 50j, the chiller 22 and the cooling water passage 50i (broken arrows in FIG. 18).

  Next, the outline of the operation of the present embodiment in the above configuration will be described. The vehicle thermal management system 1E is switched between the first mode to the fourth mode described below according to the situation by control signals from various sensors (not shown).

  The first mode is a mode used when the temperature of the cooling water flowing into the cooler core 23 is not sufficient to cool the passenger compartment. In the first mode, the fluid circulation pumps 55a and 55b are driven, the three-way valve 53 is operated so that the cooling water flows through the radiator 3, and the valve body 8b of the rotary valve of the heat storage devices 5E and 5F is positioned as shown in FIG. Stop at. Thereby, the circuits 110a and 120a are configured, and the cooling water flows as indicated by the solid and broken arrows in FIG. The cooling water flowing into the chiller 22 is cooled to about 1 ° C. by exchanging heat with the refrigerant flowing through the chiller 22, and flows into the cooler core 23 and the water-cooled battery 56. The refrigerant flowing through the chiller 22 that has absorbed the heat from the cooling water flows through a cooling circuit 130 (not shown) and exchanges heat with the cooling water flowing into the water-cooled condenser 21. The cooling water that has absorbed the heat from the refrigerant by the water-cooled condenser 21 flows into the radiator 3 and radiates heat to the outside air in the radiator 3. In this manner, the air in the passenger compartment can be cooled using the cooler core 23 using the cooling water cooled by the chiller 22. Further, the water-cooled battery 56 can be cooled using the cooling water cooled by the chiller 22. Furthermore, the heat of the chiller 22 can be radiated to the outside air via the radiator 3.

  The second mode is a mode used when the temperature of the cooling water flowing into the heater core 4 cannot sufficiently heat the passenger compartment. In the second mode, the fluid circulation pumps 55a and 55b are driven, the three-way valve 53 is operated so that the cooling water flows into the radiator 3, and the valve body 8b of the rotary valve of the heat storage devices 5E and 5F is positioned as shown in FIG. Stop at. As a result, the circuits 110a and 120a are configured, and the cooling water flows as shown by the solid and broken arrows in FIG. The cooling water cooled by the chiller 22 passes through the cooler core 23 and then flows into the inverter 54 and the radiator 3. The cooling water absorbs the heat from the inverter 54 in order to cool the inverter 54. The cooling water absorbs heat from the outside air in the radiator 3. Thereafter, the absorbed cooling water flows into the chiller 22 and performs a heat exchanger with the refrigerant. The refrigerant that has absorbed the heat from the cooling water flows through the cooling circuit 130 and exchanges heat with the cooling water flowing into the water-cooled condenser 21. The cooling water that has absorbed the heat from the refrigerant by the water-cooled condenser 21 flows into the heater core 4. In this way, the temperature of the cooling water flowing into the heater core 4 can be increased using the warm heat of the inverter 54 and the radiator 3.

  The third mode is a mode in which warm heat is accumulated in the heat storage devices 5E and 5F, and the temperature of the cooling water flowing into the heater core 4 is increased using the warm heat. In the third mode, the fluid circulation pumps 55a and 55b are driven, the three-way valve 53 is operated so that the cooling water does not flow into the radiator 3, and the valve body 8b of the rotary valve of the heat storage devices 5E and 5F is shown in FIG. Stop at position. Thereby, the circuits 110a and 120a are configured, and the cooling water flows as shown by the solid line arrows and the broken line arrows in FIG.

  When the cooling water is sufficiently heated by the water-cooled condenser 21, when the cooling water heated by the water-cooled condenser 21 passes through the first fluid passages 19d of the heat storage devices 5E and 5F, the heat storage means 12f. To dissipate heat. In this way, heat is stored in the heat storage means 12f. When the cooling water is not sufficiently heated by the water-cooled condenser 21, for example, when driving of the compressor 24 is restricted from the viewpoint of noise or the like in the idling stop mode, heat can be radiated from the heat storage means 12f to the cooling water. Thereby, the cooling water which flows in into the heater core 4 can be heated using heat storage.

  The fourth mode is a mode in which cold heat is accumulated in the heat storage devices 5E and 5F, and the cooling water flowing into the cooler core 23 is cooled using the cold heat. In the fourth mode, the fluid circulation pumps 55a and 55b are driven, the three-way valve 53 is operated so that the cooling water flows through the radiator 3, and the valve body 8b of the rotary valve of the heat storage devices 5E and 5F is positioned as shown in FIG. Stop at. Thereby, the circuits 110a and 120a are configured, and the cooling water flows as shown by the solid line arrows and the broken line arrows in FIG.

  When the cooling water is sufficiently cooled by the chiller 22, when the cooling water cooled by the chiller 22 passes through the first fluid passages 19d of the heat storage devices 5E and 5F, the cooling heat is released to the heat storage means 12f. To do. In this way, heat is stored in the heat storage means 12f. When the cooling water is not sufficiently cooled by the chiller 22, for example, when the driving of the compressor 24 is restricted from the viewpoint of noise or the like in the idling stop mode, the cooling heat can be released from the heat storage means 12f to the cooling water. Thereby, the cooling water which flows into the cooler core 23 can be cooled using the accumulated cold energy.

  As described above, by changing the passage through which the cooling water flows using the heat storage devices 5E and 5F, the heat storage means 12f stores heat from the cooling water, dissipates heat to the cooling water, and does not perform either heat storage or heat dissipation. Can be realized. Further, the cooling water flowing into the heater core 4 can be heated using the heat generated in the inverter 54 and the chiller 22 and the heat stored in the heat storage means 12f. Furthermore, the heat of the chiller 22 can be radiated to the outside air via the radiator 3, or the cooling water flowing into the cooler core 23 can be cooled using the cold energy stored in the heat storage means 12f. Thus, the heat discharged from the device can be used for cooling water that requires heating. Further, when there is no cooling water that requires heating or cooling, heat can be temporarily stored in the heat storage devices 5E and 5F, and can be used when it becomes necessary next time.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above embodiment, the gap 7b formed between the casing 7 and the inner casing 7a is vacuum insulated. However, the present invention is not limited to such a structure. The provided structure may be used.

  (2) In the above embodiment, the vehicle thermal management system is composed of a single heat storage device 5, 5B, 5C, 5D, 5E, 5F, but the heat storage device 5, 5B, 5C, 5D, 5E having the same shape. A plurality of 5Fs may be arranged in parallel. In this case, the pipes 9, 10, and 11 of the heat storage devices 5, 5B, 5C, 5D, 5E, and 5F are respectively connected to a common fluid pipe and communicated with the cooling water passage through the common fluid pipe. Further, as a driving means for driving each heat storage device 5, 5 B, 5 C, 5 D, 5 E, 5 F, a single drive motor and power such as a plurality of gears that transmit the driving force to the rotating shaft 18 of each heat storage device 5. It is comprised from a transmission member.

  (3) In the first embodiment, the second embodiment, the third embodiment, the fifth embodiment, and the sixth embodiment, the heat storage means 12a, 12b, 12c, 12e, and 12f are composed of paraffin and an aluminum plate. However, in addition to paraffin, a material capable of latent heat, such as a hydrate or nanoparticles, may be inserted.

  (4) In the first embodiment, the second embodiment, the third embodiment, the fifth embodiment, and the sixth embodiment, the heat storage means 12a, 12b, 12c, 12e, and 12f are paraffin-made cases made of an aluminum plate. The built-in configuration allows the cooling water to contact the heat storage means 12a, 12b, 12c, 12e, and 12f, thereby enabling heat storage and heat dissipation. However, the present invention is not limited to this, and a configuration may be adopted in which a plurality of fine holes are provided in the aluminum plate case, and paraffin is stored and radiated in the aluminum plate case by passing cooling water through the holes.

DESCRIPTION OF SYMBOLS 1 ... Vehicle thermal management system 5 ... Thermal storage apparatus 7 ... Casing 9 ... 1st piping 10 ... 2nd piping 11 ... 3rd piping 12a, 12b ... Thermal storage means 17 ... Partition structure 19 ... First fluid passage 20 ... Second fluid passage

Claims (18)

A casing (7) having a fluid passage (19, 20) therein and at least two inflow / outflow ports (9, 10, 11) through which fluid flows in or out or both inflow and outflow;
A partition structure (17) provided inside the casing (7) to change the flow path of the fluid,
Inside the casing (7), heat storage means (12a, 12b) for transferring heat to and from the fluid flowing in from the inflow / outflow ports (9, 10, 11) is provided,
The partition structure (17) includes a case where the heat storage means (12a, 12b) transfers heat to the fluid flowing in from the inflow / outflow ports (9, 10, 11), and heat to the fluid. The heat storage device is characterized in that the flow path of the fluid is changed so that it is possible to carry out a case where no fluid is exchanged. The fluid passages (19, 20) are formed by the partition structure (17) into a first fluid passage (19) and a second fluid passage (20),
In the first fluid passage (19), the fluid flowing in from one inflow / outflow port (9, 10, 11) out of the inflow / outflow ports (9, 10, 11) enters the heat storage means (12a, 12b). A passage configured to come into contact and to flow out of the other inflow / outflow ports (9, 10, 11) of the outflow / inflow ports (9, 10, 11);
In the second fluid passage (20), the fluid flowing in from one inflow / outflow port (9, 10, 11) of the outflow / inflow ports (9, 10, 11) enters the heat storage means (12a, 12b). A passage configured to flow out from the other inflow / outflow ports (9, 10, 11) of the inflow / outflow ports (9, 10, 11) without contact;
The partition structure (17) is configured such that the fluid flowing in from the inflow / outflow ports (9, 10, 11) is selectively selected from the first fluid passage (19) and the second fluid passage (20). The heat storage device according to claim 1, wherein switching means (8) for switching the flow path of the fluid so as to flow in is configured.   The heat storage device according to claim 2, wherein the partition structure (17) is a movable structure. The switching means (8) includes a side wall (14, 15) opposed to each other provided in the casing (7), a peripheral wall (16) formed between the side walls (14, 15), and the partition structure ( 17) is a valve body (8) of a rotary valve composed of
The first fluid passage (19) and the second fluid passage (20) are formed by the casing (7), the valve body (8) of the rotary valve, and heat storage means (12a, 12b),
A rotary shaft (18) extending in a direction connecting the side walls (14, 15) is provided on the valve body (8) of the rotary valve,
The valve body (8) of the rotary valve rotates integrally with the rotating shaft (18),
By controlling the rotation angle of the rotating shaft (18), the valve body (8) of the rotary valve allows the fluid flowing in from the inflow / outflow ports (9, 10, 11) to pass through the first fluid passage ( 19. The heat storage device according to claim 3, wherein the flow path of the fluid is switched so as to selectively flow into any one of 19) and the second fluid passage (20). The valve body (8) of the rotary valve is provided with an opening (16b) formed by the side walls (14, 15) and the peripheral wall (16).
The opening (16b) is divided into a plurality of small openings (16c, 16d) by the partition structure (17), and one small opening (16c, 16d) is an inlet of the first fluid passage (19). The heat storage device according to claim 4, wherein the other small opening (16c, 16d) forms an outlet of the first fluid passage (19). At least one of the small openings (16c, 16d) has a size capable of opening two of the inflow / outflow ports (9, 10, 11) simultaneously,
The heat storage device according to claim 5, wherein the peripheral wall (16) has a size capable of closing all the inflow / outflow ports (9, 10, 11) simultaneously.   The switching means (9b, 10b, 11b) is provided outside the casing (7), and opens and closes a passage communicating with the first fluid passage (19a) and the second fluid passage (20a). The heat storage device according to claim 2. The switching means (30) is a structure having a temperature-sensitive member that expands and contracts according to the temperature of the fluid and operates in accordance with the expansion and contraction.
When the temperature of the fluid is within a predetermined temperature range, the switching means (30) opens the first fluid passage (19c) by the operation of the temperature sensing member, and the second fluid passage (20c). Move to the position to close
When the temperature of the fluid is not within the predetermined temperature range, the first fluid passage (19c) is closed by the operation of the temperature sensing member, and the second fluid passage (20c) is opened. The heat storage device according to claim 3.   The switching means (30) is provided in the casing (7), and is provided in a junction where the first fluid passage (19) and the second fluid passage (20) join. The heat storage device according to claim 8. The heat storage means (12d) is formed of a supercooling heat storage material having a characteristic of solidifying when it is cooled to a temperature below the freezing point and does not solidify, and when the external cooling force is applied, the supercooling state is released. ,
The partition structure (16f) is movable,
A state in which the protrusion (16e) provided on the partition structure (16f) does not contact the heat storage means (12d);
The heat storage device according to claim 1, wherein the protrusion (16e) is movable so as to switch between a state in which the protrusion (16e) abuts on the heat storage means (12d). Inside the casing (7) is provided an inner casing (7a) that constitutes a double structure with the casing (7),
There is a gap (7b) between the casing (7) and the inner casing (7a).
Is provided,
Inside the inner casing (7a), the fluid passages (19, 20) and a partition structure (17) are provided,
The heat storage device according to any one of claims 1 to 10, wherein the gap (7b) has a vacuum structure or a structure in which a member having a heat insulating property is incorporated.   The heat storage device according to any one of claims 4 to 10, wherein the side walls (14, 15) and the peripheral wall (16) are formed of a heat-insulating material. A heat storage device (5) according to any one of claims 2 to 7,
A first fluid circulation circuit comprising a first fluid circulation pump (6c) and a thermal source body (21) for supplying heat to the circulating fluid through which the fluid is circulated by the first fluid circulation pump (6c); 110)
The second fluid circulation circuit (120) includes a second fluid circulation pump (6d), and includes a cold heat source body (22) that cools the circulating fluid through the second fluid circulation pump (6d). )When,
A temperature adjusting device (26) in which the fluid circulating through at least one of the first fluid circulation circuit (110) and the second fluid circulation circuit (120) is circulated and temperature-adjusted (26).
The inflow / outflow ports (9, 10, 11) include a first inflow port (10), a second inflow port (11), and an outflow port (9),
The first inflow port (10) is connected to a portion through which the fluid heated by the heat source body (21) flows in the first fluid circulation circuit (110),
The second inflow port (11) is connected to a portion through which the fluid cooled by the cold heat source body (22) flows in the second fluid circulation circuit (120),
The temperature control device (26) has a fluid inflow port (26a) and a fluid outflow port (26b),
The fluid inlet port (26a) communicates with the outlet port (9);
The fluid outflow port (26b) communicates with the first fluid circulation circuit (110) and the second fluid circulation circuit (120), or a valve device that controls a communication state,
The switching means (8) includes the fluid circulating in the first fluid circulation circuit (110) in either the first fluid passage (19) or the second fluid passage (20), or the first fluid passage (19). 2. A vehicle thermal management system, wherein a flow path of the fluid is switched so that the fluid circulating through the two-fluid circulation circuit (120) is selectively introduced. A heat storage device (5) according to any one of claims 2 to 7,
A first fluid circulation circuit comprising a first fluid circulation pump (6c), and a heat source body (21) for supplying heat to the circulating fluid through which the fluid circulates by the first fluid circulation pump (6c) (110),
A second fluid circulation circuit comprising a second fluid circulation pump (6d), and comprising a cold heat source body (22) for cooling the fluid circulating and circulating the fluid by the second fluid circulation pump (6d). 120),
A temperature adjusting device (26) for adjusting the temperature by circulating the fluid circulating through at least one of the first fluid circulation circuit (110) and the second fluid circulation circuit (120),
The inflow / outflow ports (9, 10, 11) include a first inflow port (10), a second inflow port (11), and an outflow port (9),
The first inflow port (10) is connected to a portion through which the fluid heated by the heat source body (21) flows in the first fluid circulation circuit (110),
The second inflow port (11) is connected to a portion through which the fluid cooled by the cold heat source body (22) flows in the second fluid circulation circuit (120),
The temperature control device (26) has a fluid inflow port (26a) and a fluid outflow port (26b),
The fluid inlet port (26a) communicates with the outlet port (9);
The fluid outflow port (26b) communicates with the first fluid circulation circuit (110) and the second fluid circulation circuit (120), or a valve device for controlling the communication state,
The switching means (8) communicates the first inflow port (10) and the first fluid passage (19), and communicates the second inflow port (11) and the first fluid passage (19). The vehicle thermal management system, wherein the state to be switched is switched based on a predetermined condition. The heat storage device (5) according to any one of claims 2 to 7, a circuit in which the fluid circulates, a heat source body (2) that gives heat to the fluid, and air that is blown into the passenger compartment is caused by the fluid. A fluid circuit (100) including a heating heat exchanger (4) for heating,
In the heat storage state in which the heat storage means (12a, 12b) stores the heat of the fluid, the switching means (8) receives the fluid supplied from the heat source body (2) as the inflow / outflow port ( 9) flows into the first fluid passageway (19) and radiates heat to the heat storage means (12a, 12b), then flows out of the casing (7) from the inlet / outlet port (10),
In other states, the fluid supplied with heat from the heat source body (2) flows in from the inflow / outflow port (9), passes through the second fluid passage (20), and then flows into the inflow / outflow. The vehicle thermal management system, wherein the fluid path is switched so as to flow out of the casing (7) from the port (10). The heat storage device (5) according to any one of claims 2 to 7, a circuit in which the fluid circulates, an engine (2) that is a heat source, and heating that heats the air blown into the passenger compartment by the fluid. A fluid circuit (100) including a heat exchanger for use (4),
The heat storage device (5) includes a first pipe (9), a second pipe (10), and a third pipe (11) constituting the inflow / outflow port,
The first pipe (9) communicates with the engine (2), the second pipe (10) communicates with the heating heat exchanger (4), and the third pipe (11) communicates with the engine (2). ) And the heating heat exchanger (4),
The switching means (8) is driven by the engine (2) when the engine (2) is driven and the heat storage means (12a, 12b) stores the heat of the fluid. The fluid flows into the first fluid passage (19) through the first pipe (9), radiates heat to the heat storage means (12a, 12b), and then the casing through the second pipe (10). Out of (7),
When the engine (2) is driven and the heat storage means (12a, 12b) does not store heat of the fluid, the fluid supplied with heat from the engine (2) is the first pipe. Flows through the second fluid passage (20) via (9), flows out of the casing (7) via the second pipe (10),
In the engine stop state in which the engine (2) is stopped, the fluid flow of all of the first pipe (9), the second pipe (10) and the third pipe (11) is shut off,
An engine pre-warm-up state in which the engine (2) is warmed up before the engine (2) is driven in a state where the engine (2) is stopped, or the water temperature of the engine (2) is equal to or lower than a predetermined temperature. In this case, the fluid flowing into the first fluid passage (19) through the third pipe (11) absorbs heat from the heat storage means (12a, 12b) and then passes through the first pipe (9). The vehicle heat management system is characterized in that the fluid path is switched so as to flow out of the casing (7) and into the engine (2). Further, the switching means (8) is required to perform heating of the vehicle interior in an idling stop state in which the engine (2) automatically pauses when the vehicle is temporarily stopped.
In the switching means (8), the fluid flowing out from the heating heat exchanger (4) passes through the first fluid passage (19) via the second pipe (10) and the heat storage means (12a, 12b). ) Or after passing through the second fluid passage (20) and flowing into the engine (2) through the first pipe (9) and absorbing heat from the engine (2), the heat exchange for heating. The vehicle thermal management system according to claim 16, wherein the fluid path is switched so as to flow into the vessel (4).   In the switching means (8), the temperature of the fluid flowing into the heating heat exchanger (4) is lower than a predetermined temperature in a state where the idling stop state is released and the engine (2) is driven. In this case, the fluid flows from the heating heat exchanger (4) into the engine (2), flows into the first fluid passage (19) through the first pipe (9), and the heat storage means. 18. The fluid path is switched so as to flow into the heating heat exchanger (4) through the second pipe (10) after absorbing heat from (12a, 12b). Vehicle thermal management system.

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