JP2005320936A - Heating element cooling device and cooling/heating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the lowering of the seal performance of a shaft seal member in a pump in a heating element cooling device circulating a fluid in two circuits with a pressure difference by the pump having blades in first and second pump chambers, rotating shafts positioned in both pump chambers, and a shaft seal member sealing between both pump chambers. <P>SOLUTION: This heating element cooling device comprises the electric appliance cooling circuit 11 radiating, from a radiator 13, heat absorbed from electric appliances 15, 17, and 18, the engine cooling circuit 21 radiating, from a radiator 27, heat absorbed from an engine 24, a heater passage 22 having a heater 25 heating an air for air-conditioning, and the mechanical pump 23 circulating the fluid in the engine cooling circuit and the heater passage 22 by the power of the engine 24. The first pump chamber 12c of the pump 12 is disposed on the downstream side of the heater 25 in the heater passage 22, and the second pump chamber 12d is disposed on the downstream side of the electric appliances 15, 17, and 18 in the electric appliance cooling circuit 11 in the fluid flow direction and on the upstream side of the radiator 13. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heating element cooling device and a cooling / heating device for cooling a heating element, and is suitable for cooling a heating element such as an internal combustion engine (engine) or an electric motor mounted on a vehicle.

  Conventionally, a pump having two pump chambers in a pump housing and rotating blades in each pump chamber by a common drive unit is known from Patent Document 1 (hereinafter referred to as a conventional example).

  In the pump of the conventional example, a partition portion that partitions the first and second pump chambers is formed in the pump housing. And the rotating shaft which penetrates a partition part and the blade | wing in each pump chamber is arrange | positioned, and the shaft sealing member which is arrange | positioned at a penetration part and seals between both pump chambers are provided.

In the conventional example, as shown in FIG. 7, the coolant flow absorbed from the engine branches into a front seat side passage 52 that flows to the front seat heat exchanger 54 and a rear seat side passage 53 that flows to the rear seat heat exchanger 55. The first pump chamber 12 c is disposed in the front seat side passage 52, and the second pump chamber 12 d is disposed in the rear seat side passage 53. Therefore, the wing 32 in the first pump chamber 12c and the wing 33 in the second pump chamber 12d can be rotated to allow cooling water to flow through the front seat side passage 52 and the rear seat side passage 53.
Japanese Patent No. 3014991

  In the conventional example, since the two pump chambers are disposed in the front seat side passage 52 and the rear seat side passage 53 having substantially the same pressure, a pressure difference between the pump chambers does not occur and a problem occurs in the sealing performance of the shaft seal member. Absent. As shown in FIG. 1 described later, the present inventors have a heater circuit 22 having a heater 25 in which cooling water absorbed from an engine 24 mounted on a hybrid vehicle heats air for air conditioning, an electric motor 17 and an electric device 15. It was considered that the pump chambers 12c and 12d were disposed in the 18 cooling circuits 11 to circulate the cooling water of the circuits 11 and 22, respectively. Here, the cooling water in the heater circuit 22 is circulated by a mechanically driven pump 23 driven by power from the engine 24 in addition to the blades 32 of the first pump chamber 12c.

  According to this, since the pressure of the heater circuit 22 becomes higher than the pressure of the electric equipment cooling circuit 11, the shaft seal member that seals between the first pump chamber 12c and the second pump chamber 12d due to the pressure difference is large. Power is applied. When the time elapses in such a state, in the worst case, the shaft seal member is deformed or cracked, and the sealing performance is lowered, so that the fluid in the first pump chamber 12c and the fluid in the second pump chamber 12d It has been found by the present inventors that there is a case where they are mixed.

  In view of the above, the present invention provides a pump having blades of the first and second pump chambers, a rotating shaft located in the first and second pump chambers, and a shaft seal member that seals between the pump chambers. An object of the present invention is to reduce a decrease in the sealing performance of a shaft seal member in a pump in a heating element cooling device that circulates fluid in two circuits having a pressure difference.

In order to achieve the above object, according to the first aspect of the present invention, the partition member (12i) for partitioning the inside of the pump housing (12a) into the first pump chamber (12c) and the second pump chamber (12d), and each pump The wings (32, 33) arranged in the chambers (12c, 12d), the wings (32, 33) are arranged, the rotating shaft (31) penetrating the partition member (12i), and the partition member (12i) Heat absorption from the first pump means (12) disposed in the penetrating portion and having a shaft sealing member (34) for sealing between the two pump chambers (12c, 12d) and the first heating element (15, 17, 18) The first cooling circuit (11) through which the fluid radiating heat from the first radiator (13) flows, and the second fluid through which the fluid radiating heat from the second radiator (27) flows by absorbing heat from the second heating element (24). The cooling circuit (21) and the second cooling circuit (21) are arranged in the second cooling circuit (21). And a circuit second pump means for circulating the fluid (21) (23),
The blade (32) of the first pump chamber (12c) circulates the fluid in the second cooling circuit (21), and the blade (33) of the second pump chamber (12d) is the fluid in the first cooling circuit (11). The fluid discharged from the second pump means (23) flows into the second heat radiator (27) and then flows into the first pump chamber (12c).

  By the way, when the first pump means (12) and the second pump means (23) are operated simultaneously, the fluid flowing through the second cooling circuit (21) receives pressure from both pump means (12, 23). The first pump chamber (12c) disposed in the second cooling circuit (21) has a higher pressure than the second pump chamber (12d).

  However, according to the present invention, since the first pump chamber (12c) is disposed downstream of the second radiator (27), the fluid pressure increased to allow the second pump means (23) to flow is the second. It is low due to the pressure loss when passing through the radiator (27). Therefore, the pressure difference between the first pump chamber (12c) and the second pump chamber (12d) can be reduced.

  According to this, since the force applied to the shaft seal member (34) for sealing between the two pump chambers (12c, 12d) can be reduced, the deformation of the shaft seal member (34) and the occurrence of cracks over time can be reduced. That is, the deterioration of the sealing performance of the shaft seal member (34) can be reduced.

  The first pump chamber (12c) is arranged in the second cooling circuit (21) in order to circulate the cooling water in the second cooling circuit (21) even when the second pump means (23) is stopped. It is.

In the invention according to claim 2, in the heating element cooling device, the partition member (12i) for partitioning the inside of the pump housing (12a) into the first pump chamber (12c) and the second pump chamber (12d), The blades (32, 33) disposed in the pump chamber (12c, 12d), the rotating shaft (31) in which the blades (32, 33) are disposed and penetrating the partition member (12i), and the partition member (12i) A first pump means (12) having a shaft sealing member (34) disposed in the through-hole and sealing between the two pump chambers (12c, 12d), and a first heating element (15, 17, 18). The first cooling circuit (11) that absorbs heat and the fluid that radiates heat from the first radiator (13) flows, and the fluid that absorbs heat from the second heat generator (24) and radiates heat from the second radiator (27) flows. 2 heat absorption from the cooling circuit (21) and the second heating element (24) The fluid that has reached the state flows, and is disposed in the heater circuit (22) having the heater (25) that heats the object to be heated by the fluid, and the second cooling circuit (21), and the second cooling circuit (21) and the heater circuit A second pump means (23) for circulating fluid in (22),
The blade (32) of the first pump chamber (12c) circulates the fluid in the heater circuit (22), and the blade (33) of the second pump chamber (12d) circulates the fluid in the first cooling circuit (11). In the heater circuit (22), the first pump chamber (12c) is arranged at a location downstream of the heater (25) in the fluid flow.

  By the way, when fluid is circulated in all of the first cooling circuit (11), the second cooling circuit (21), and the heater circuit (22), the first pump means (12) and the second pump means (23) are simultaneously operated. Let At this time, the first pump means (12) circulates the fluid in the first cooling circuit (11) and the heater circuit (22), and the second pump means (23) is in the second cooling circuit (21) and the heater circuit (22). ) Circulating fluid.

  At this time, since the fluid flowing through the heater circuit (22) receives pressure from both pump means (12, 23), the first pump chamber (12c) disposed in the heater circuit (22) is the second pump chamber (12d). ) Pressure is higher than

  However, according to the present invention, the first pump chamber (12c) is disposed downstream of the heater (25), so that the fluid pressure increased to allow the second pump means (23) to flow fluid causes the heater (25) to have a high fluid pressure. Lower due to pressure loss during passage. Therefore, the pressure difference between the first pump chamber (12c) and the second pump chamber (12d) can be reduced.

  According to this, since the force applied to the shaft seal member (34) for sealing between the two pump chambers (12c, 12d) can be reduced, the deformation of the shaft seal member (34) and the occurrence of cracks over time can be reduced. That is, the deterioration of the sealing performance of the shaft seal member (34) can be reduced.

  The first pump chamber (12c) is arranged in the heater circuit (22) because the cooling water of the heater circuit (22) is circulated to generate the second heat generation even when the second pump means (23) is stopped. This is to cause the heater (25) to exhibit the heating performance by the residual heat of the body (24) and the fluid.

In the invention according to claim 3, in the heating element cooling device, the partition member (12i) for partitioning the inside of the pump housing (12a) into the first pump chamber (12c) and the second pump chamber (12d), The blades (32, 33) disposed in the pump chamber (12c, 12d), the rotating shaft (31) in which the blades (32, 33) are disposed and penetrating the partition member (12i), and the partition member (12i) A first pump means (12) having a shaft sealing member (34) disposed in the through-hole and sealing between the two pump chambers (12c, 12d), and a first heating element (15, 17, 18). Absorbs heat and absorbs heat from the first cooling circuit (11) through which the fluid radiated by the first radiator (13) flows and the first heating element (15, 17, 18), and radiates heat by the second radiator (27). The second cooling circuit (21) through which the fluid flows and the second heating element (24) A fluid that has absorbed heat and flows into a high temperature flows, and is disposed in a heater circuit (22) having a heater (25) that heats the object to be heated by the fluid, and a second cooling circuit (21), and the second cooling circuit (21 ) And second pump means (23) for circulating fluid in the heater circuit (22),
The blade (32) of the first pump chamber (12c) circulates the fluid in the heater circuit (22), and the blade (33) of the second pump chamber (12d) circulates the fluid in the first cooling circuit (11). A fluid having a temperature higher than that of the first cooling circuit (11) flows through the second cooling circuit (21) and the heater circuit (22), and the second pump chamber (12d) serves as the first cooling circuit. In (11), the first heat generating element (15, 17, 18) is disposed downstream of the fluid flow, and the fluid radiator is disposed upstream of the first radiator (13).

  In the present invention, since a fluid having a temperature higher than that of the first cooling circuit (11) flows through the second cooling circuit (21) and the heater circuit (22), the first pump chamber (12c) is disposed. A temperature difference is generated between the fluid in the heater circuit (22) and the fluid in the first cooling circuit (11) in which the second pump chamber (12d) is disposed.

  However, in claim 3, the second pump chamber (12d) is located downstream of the first heating element (15, 17, 18) in the fluid flow and upstream of the first radiator (13), That is, it is arranged at a position where the temperature of the fluid is highest in the first cooling circuit (11) after absorbing heat from the first heating element (15, 17, 18). Therefore, the temperature difference between the first pump chamber (12c) and the second pump chamber (12d) can be reduced.

  According to this, since the thermal stress due to the temperature difference generated in the shaft seal member (34) for sealing between the two pump chambers (12c, 12d) can be reduced, the shaft seal member (34) is deformed and cracked over time. Can be reduced. That is, the deterioration of the sealing performance of the shaft seal member (34) can be reduced.

  The first pump chamber (12c) is arranged in the heater circuit (22) because the cooling water of the heater circuit (22) is circulated to generate the second heat generation even when the second pump means (23) is stopped. This is to cause the heater (25) to exhibit the heating performance by the residual heat of the body (24) and the fluid.

  Further, as in the invention according to claim 4, in the heating element cooling apparatus according to claim 3, the first pump chamber (12c) is arranged in the heater circuit (25) so that the fluid flow is downstream of the heater (25). If it arrange | positions in a site | part, while being able to make small the thermal stress which generate | occur | produces in the shaft sealing member (34) described in Claim 3, it is the 1st pump chamber (12c) and 2nd pump chamber (12d) for the same reason as Claim 2. ) Can be reduced.

  Together, these can reduce the deformation and cracking of the shaft sealing member (34) over time, and can further reduce the deterioration of the sealing performance of the shaft sealing member (34).

  In addition, the fluid flow downstream part from the heater (25) heats the object to be heated by the heater (25), that is, the fluid dissipated heat to the object to be heated flows. Therefore, the first pump chamber (12c) and the second pump chamber ( The temperature difference from 12d) can be reduced.

  According to a fifth aspect of the present invention, in the heating element cooling device according to any one of the second to fourth aspects, the first heating element includes at least a motor (17) for driving the vehicle. 17, 18), the second heating element is an internal combustion engine (24) mounted on a vehicle, and the second pump means is a mechanically driven pump (23) driven by receiving power from the internal combustion engine (24). If the heater (25) heats the air-conditioning air flowing into the passenger compartment of the vehicle, a heating element cooling device having the effects described in claims 2 to 4 can be specifically configured.

  The first pump chamber (12c) is disposed in the heater passage (22) because the internal combustion engine (24) is stopped, that is, when the mechanically driven pump (23) is stopped. This is because the air for air conditioning is heated by the heater (25) using the remaining heat of the fluid.

In the invention according to claim 6, in the cooling and heating device, the partition member (12i) for partitioning the inside of the pump housing (12a) into the first pump chamber (12c) and the second pump chamber (12d), and each pump The wings (32, 33) arranged in the chambers (12c, 12d), the wings (32, 33) are arranged, the rotating shaft (31) penetrating the partition member (12i), and the partition member (12i) The first pump means (12), which is disposed in the penetrating portion and has a shaft seal member (34) for sealing between the two pump chambers (12c, 12d), and the cooling means (45) absorbs heat to be in a low temperature state. A low-temperature fluid circuit (46) having a cooler (47) that cools an object to be cooled by the fluid, and a cooling circuit that absorbs heat from the heating element (24) and radiates heat from the radiator (27) ( 21) and a heating element (24 The fluid that has absorbed heat from the fluid flows into the heater circuit (22) having the heater (25) that heats the object to be heated by the fluid, and the cooling circuit (21). Second pump means (23) for circulating fluid in the circuit (22),
The blade (32) in the first pump chamber (12c) circulates the fluid in the heater circuit (22), and the blade (33) in the second pump chamber (12d) circulates the fluid in the cryogenic fluid circuit (11). In the heater circuit (22), the first pump chamber (12c) is arranged at a site downstream of the fluid flow from the heater (25).

  In the present invention, when fluid is circulated in all of the cooling circuit (21), the heater circuit (22), and the low temperature fluid circuit (46), the first pump means (12) and the second pump means (22) are driven simultaneously. At this time, the first pump means (12) flows the fluid of the first cooling circuit (11) and the heater circuit (22), and the second pump means (23) is the second cooling circuit (21) and the heater circuit (22). Of fluid.

  At this time, since the fluid flowing through the heater circuit (22) receives pressure from both pump means (12, 23), the first pump chamber (12c) disposed in the heater circuit (22) is the second pump chamber (12d). ) Pressure is higher than

  However, according to the present invention, the first pump chamber (12c) is disposed downstream of the heater (25), so that the fluid pressure increased to allow the second pump means (23) to flow fluid causes the heater (25) to have a high fluid pressure. Lower due to pressure loss during passage. Therefore, the pressure difference between the first pump chamber (12c) and the second pump chamber (12d) can be reduced.

  According to this, since the force applied to the shaft seal member (34) for sealing between the two pump chambers (12c, 12d) can be reduced, the deformation of the shaft seal member (34) and the occurrence of cracks over time can be reduced. That is, the deterioration of the sealing performance of the shaft seal member (34) can be reduced.

  The first pump chamber (12c) is arranged in the heater circuit (22) because the cooling water of the heater circuit (22) is circulated to generate the second heat generation even when the second pump means (23) is stopped. This is because the heater (25) exhibits heating performance with the residual heat of the body (24) and the fluid.

According to a seventh aspect of the present invention, there is provided a vehicle air conditioner comprising the cooling and heating device according to the sixth aspect, wherein the refrigerant is circulated in a closed circuit by the compressor (42). 41)
An internal combustion engine (24) in which the cooling means is disposed in the refrigeration cycle (41) and is configured as a heat exchanger (45) that absorbs heat from the fluid of the low-temperature fluid circuit (46) and evaporates the low-pressure refrigerant. And the second pump means as a mechanically driven pump (23) driven by receiving power from the internal combustion engine (24) has the effects described in claim 6, and the cooler (47) has a vehicle interior. A vehicle air conditioner that cools the air-conditioning air flowing to the vehicle and further heats the air-conditioning air that the heater (25) flows into the vehicle interior of the vehicle may be specifically configured.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
FIG. 1 shows a first embodiment in which a heating element cooling device according to the present invention is applied to a hybrid vehicle having two travel drive sources, an engine and a travel motor. In general, there is a difference between the heat resistance temperature (referring to a temperature at which operation is possible without malfunction) of the electric motor that operates the motor for traveling and the motor suitable for engine operation. The temperature suitable for engine operation is about 100 ° C., and the heat resistance temperature of the electric equipment is about 65 ° C.

  Therefore, the heating element cooling device of the first embodiment includes a first cooling circuit 11 (hereinafter referred to as an electric equipment cooling circuit) that cools electric equipment such as the traveling motor 17, the generator 18, and the inverter 15 that are the first heating elements. And a second cooling circuit 21 for cooling the engine 24, which is a second heating element (indicated by a bold line in FIG. 1, hereinafter referred to as an engine cooling circuit). Cooling water, which is a heat medium that moves heat, flows through the cooling circuits 11 and 21.

  First, the electric equipment cooling circuit 11 will be described along the flow of cooling water. The cooling water is circulated in the electronic device cooling circuit 11 by a pump 12 which is a first pump means disposed in the electric device cooling circuit 11. The structure of the pump 12 will be described later.

  The cooling water discharged from the pump 12 flows into the electric equipment radiator 13 which is a first radiator. In the electric device radiator 13, the cooling water radiates heat to the air blown from the blower 13a, in other words, the cooling water is cooled by the blown air.

  The cooling water radiated by the electric equipment radiator 13 flows to the inverter 15 and absorbs the heat of the inverter 15. As is well known, the inverter 15 converts the DC voltage of the vehicle power supply into an AC voltage, and supplies power to, for example, the traveling motor 17 and controls the rotational speed of the motor 17 and the like by changing the frequency of the AC voltage. It is. The inverter 15 has a lower heat-resistant temperature than the other electronic devices 17 and 18, and therefore is arranged immediately downstream of the electric device radiator 13, so that the low-temperature cooling water immediately after heat radiation cools the inverter 15. It has become.

  The cooling water that has absorbed heat from the inverter 15 flows into the reservoir tank 16, and the reservoir tank 16 stores excess cooling water of the electric equipment cooling circuit 11. The cooling water flowing out of the reservoir tank 16 flows to the traveling motor 17 and the generator 18 and absorbs heat from the traveling motor 17 and the generator 18. Here, the traveling motor 17 moves the vehicle by driving with electric power, and the generator 18 mainly generates electricity to supply power to the traveling motor 13.

  The cooling water that has absorbed heat from the traveling motor 17 and the generator 18 is again sucked and discharged to the pump 12 and circulates in the electric equipment cooling circuit 11.

  Next, the engine cooling circuit 21 will be described. The engine cooling circuit 21 has the same configuration as a well-known engine cooling circuit, and the engine cooling circuit 21 is provided with a mechanical pump 23 that receives power from the engine 24 and drives it. Has been.

  The cooling water discharged from the mechanical pump 23 flows into the engine 24 and absorbs the heat of the engine 24. The flow of cooling water that has absorbed heat from the engine 24 branches into a heater passage 22 that goes to the heater 25 and an engine cooling circuit 21 that goes to the engine radiator 27. The cooling water flowing into the heater passage 22 heats the air flowing into the vehicle interior by the blower 26 by the heater 25, that is, radiates heat to the air in the vehicle interior, and then the engine radiator 27 and the mechanical pump 23 in the engine cooling circuit 21. The engine is joined to the engine cooling circuit 21 at an intermediate position, and is sucked and discharged again to the mechanical pump 23. In the present embodiment, the pump 12 is disposed in the heater passage 22 at a downstream side of the cooling water flow of the heater 25.

  On the other hand, the cooling water that has flowed through the engine cooling circuit 21 radiates heat to the air blown from the blower 27 a by the engine radiator 27. In the engine cooling circuit 21, the cooling water flows to the engine radiator 27 (engine cooling circuit 21) when the cooling water is above a certain temperature, and when the cooling water is lower than the certain temperature, the cooling water is sent to the engine radiator. There is provided a thermostat 28 for flowing only the heater passage 22 without flowing to 27 (engine cooling circuit 21).

  As is well known, when the temperature of the engine 24, that is, the cooling water is low, such as when the engine is started after parking for a long time, the operating efficiency (for example, fuel consumption) of the engine 24 is low. However, when the cooling water is lower than a certain temperature by the thermostat 28, the cooling water is not radiated by the engine radiator 27, so the engine 24 is quickly warmed to a temperature with high operating efficiency (hereinafter referred to as warm-up temperature). The warm-up time of the engine 24 can be shortened. On the other hand, when the cooling water temperature is higher than the predetermined temperature, the heat of the cooling water absorbed from the engine 24 can be radiated by the engine radiator 27.

  Next, the structure of the pump 12 will be described with reference to FIG. 2. In the pump housing 12a that is a case of the pump 12, a motor unit 12b that is driving means and first and second pump chambers 12c, 12d is arranged. In the present embodiment, the first pump chamber 12c is disposed in the heater passage 22, and the second pump chamber 12d is disposed in the electric equipment cooling circuit 11 (see FIG. 1).

  The pump structure of the present embodiment will be described in more detail with reference to FIG. 2. A space in the pump housing 12a is divided into right and left in FIG. 2 by a partition wall 12h. The partition wall 12h is formed of, for example, a non-magnetic material such as resin, and is fixed to the pump housing 12a.

  In the left space in FIG. 2, the motor unit 12 b is arranged. The motor unit 12b of the present embodiment is provided with a coil 12e that is a magnetic field generating means. In addition, 12f is a drive circuit of the motor part 12b.

  In the space on the right side in FIG. 2, first and second pump chambers 12c and 12d are arranged. A pump chamber partition plate 12i is disposed between the first and second pump chambers 12c and 12d. The pump chamber partition plate 12i has a hole into which the rotary shaft 31 is rotatably fitted. Further, the first and second pump chambers 12c and 12d have inlets 12j and 12m through which cooling water flows, outlets 12k and 12n through which cooling water flows out, and blades 32 and 33 integrated with the rotary shaft 31, respectively. Has been placed. A blade 32 is disposed in the first pump chamber 12c, and a blade 33 is disposed in the second pump chamber 12d.

  The blades 32 and 33 discharge the cooling water (arrows E and F) flowing in from the rotation axis direction R from the rotation direction (centrifugal direction) of the rotation shaft 31 (arrows G and H). It has a wing shape. A magnet portion 33a having a shape surrounding the motor portion 12b is formed on the blade 33 of the second pump chamber 12d near the motor portion 12b side. A magnetized member such as a magnet is disposed in the magnet portion 33a.

  A shaft seal member 34 is provided between the first pump chamber 12c and the second pump chamber 12d to seal between the pump chambers 12c and 12d. As the shaft sealing member, an O-ring, a member that presses a sealing material against a rotating shaft by a pressure difference of a pump chamber as described in Patent Document 1, Japanese Patent Laid-Open No. 2001-132634, or Japanese Patent Laid-Open No. 2003-307224 is disclosed. As long as it can seal between the first and second pump chambers 12c and 12d, such as the lip-type seal described in (1), the rotary shaft 31 may be rotatable.

  In addition, 12p is a bracket for fixing the pump 12. In this embodiment, the electronic control unit (ECU, not shown) controls the rotational speed of the pump 12, the blower amounts of the blowers 13 a and 27 a, and the blower 26. Further, sensor signals from the temperature sensors 14 and 29 are also input to the ECU.

  Next, the operation of the pump 12 of the present embodiment in the above configuration will be described. When a signal from the ECU is input to the drive circuit 12f via the connector 12g, a current flows in the coil 12e and a magnetic field (magnetic force) is generated. . When this magnetic force is received by the magnet portion 33a of the blade 33, the blade 33 rotates about the rotation shaft 31. Further, the blade 32 integrated with the rotating shaft 31 also rotates.

  By the rotation of the blades 32 and 33, the cooling water is sucked into the pump chambers 12c and 12d from the inlets 12j and 12m (arrows E and F), and the outlet 12k positioned in the rotation direction (centrifugal direction) of the rotary shaft 31. , 12n (arrows G and H). By such an operation of the pump 12, the cooling water of the electric equipment cooling circuit 11 and the cooling water of the heater passage 22 are circulated.

  The cooling water of the electric equipment cooling circuit 11 absorbs heat from the traveling motor 17, the generator 18, and the inverter 15, and this heat is radiated by the electronic equipment radiator 13. As a result, the traveling motor 17, the generator 18, and the inverter 15 are prevented from exceeding the heat-resistant temperature due to heat generated by operation. In addition, ECU controls the ventilation volume (heat load to the radiator 13) of the air blower 13a so that the temperature detected by the water temperature sensor 14 upstream of the cooling water flow of the inverter 15 does not exceed the heat resistance temperature of the inverter 17.

  In the engine cooling circuit 21, when the temperature of the cooling water is low and the thermostat 28 closes the passage, the cooling water flows only through the heater passage 22. On the other hand, when the temperature of the cooling water is high and the thermostat 28 opens the passage, the cooling water flows through the heater passage 22 and the engine cooling circuit 21. As a result, the engine 24 is prevented from having an inefficient low temperature or a temperature optimum for driving. The ECU controls the amount of air blown by the blower 27a (heat load on the radiator 27) so that the temperature detected by the water temperature sensor 29 upstream of the coolant flow of the engine 24 does not exceed the optimum temperature for the operation of the engine 24. Yes.

  Next, the effects of the first embodiment will be listed. (1) In the heater passage 22, the pump 12 (first pump chamber 12c) is disposed at a lower pressure position, so the first pump chamber 12c and the second pump. It is possible to reduce the pressure difference in the chamber 12d and reduce the deterioration of the sealing performance of the shaft seal member 34.

  In the present embodiment, even when the engine is stopped, that is, when the mechanical pump 23 is stopped, the heater circuit 22 is electrically driven to heat the air-conditioning air by the heater 25 using the residual heat of the engine 24 and the cooling water. A pump 12 (first pump chamber 12c) is arranged.

  Therefore, when the cooling water is circulated in all of the electric equipment cooling circuit 11, the engine cooling circuit 21, and the heater circuit 22, the pump 12 and the mechanical pump 23 are driven simultaneously. At this time, the pump 12 flows the cooling water of the electric equipment cooling circuit 11 and the heater circuit 22, and the mechanical pump 23 flows the fluid of the engine cooling circuit 21 and the heater circuit 22.

  At this time, since the fluid flowing through the heater circuit 22 receives pressure from both the pumps 12 and 23, the pressure in the first pump chamber 12c disposed in the heater circuit 22 is higher than that in the second pump chamber 12d.

  Here, FIG. 3 shows the relationship between the heater passage position where the first pump chamber 12c is disposed and the pressure applied to the shaft seal member 34. The cooling water pressurized by the mechanical pump 23 loses pressure when passing through the engine 24, the heater 25, the piping connecting them, and the like. Therefore, the pressure at the most downstream portion (point B in FIG. 1) in the heater circuit 22 is lower than the pressure at point A in FIG. 1 (immediately after passing through the engine 24). That is, the value of ΔPB is smaller than the pressure difference ΔPA with respect to the cooling water of the electrical equipment cooling circuit 11.

Note that P _{21 in} FIG. 3 is a system pressure (88 kPa as an example) applied to the engine cooling circuit 21 (heater passage 22) in which the first pump chamber 12c is disposed. This system pressure raises the boiling point of the cooling water in the engine cooling circuit 21 (heater passage 22). Also, _{P 21} in FIG. 3 is a system pressure applied to the electrical device cooling circuit 11 in which the second pump chamber 12d is arranged (29 kPa as an example). Since the heat-resistant temperature of the electric equipment is generally lower than the boiling point of the cooling water, the system pressure of the electric equipment cooling circuit 11 becomes low.

  However, according to the present embodiment, the first pump chamber 12 c is arranged at a position where the pressure is low in the heater circuit 22. Therefore, the pressure difference between the first pump chamber 12c and the second pump chamber 12d can be minimized.

  According to this, since the force applied to the shaft seal member 34 that seals between the pump chambers 12c and 12d can be reduced, deformation of the shaft seal member 34 and generation of cracks over time can be reduced. That is, the deterioration of the sealing performance of the shaft sealing member 34 can be reduced.

  (2) Since the pump 12 is disposed at a higher temperature position in the electrical equipment cooling circuit 11, the temperature difference between the first pump chamber 12c and the second pump chamber 12d is reduced to reduce the sealing performance of the shaft seal member 34. Can be reduced.

  As described above, there is a difference between the optimum operating temperature (about 100 ° C.) of the engine 24 and the heat resistance temperature (about 65 ° C.) of the electric equipment. That is, the cooling water flowing through the engine cooling circuit 21 and the heater circuit 22 has a higher temperature than the cooling water flowing through the electrical equipment cooling circuit 11.

FIG. 4 shows the relationship between the heater passage position where the first pump chamber 12c is disposed and the coolant temperature. The water temperature rises due to heat absorption by the engine 24 and falls due to heat radiation by the heater 25 (heating of the heating target). Therefore, the temperature at the most downstream portion (point B in FIG. 1) in the heater circuit 22 is lower than the temperature at point A in FIG. 1 (immediately after passing through the engine 24). That is, the value of ΔTB is smaller than the temperature difference ΔTA with the cooling water of the electrical equipment cooling circuit 11. Incidentally, T ₁₁ in FIG. 4 is a heat-resistant temperature of the electric device cooling circuit 11 in which the second pump chamber 12d is placed (about 65 ° C.), and described in for comparison between the temperature of the engine cooling circuit 21 Yes.

FIG. 5 shows the relationship between the position of the electric equipment cooling circuit 11 where the second pump chamber 12d is arranged and the cooling water temperature. The water temperature rises due to heat absorption by the electric devices 15, 17, and 18 and decreases due to heat dissipation by the electric device radiator 13. Therefore, the temperature at the point D (immediately after passing through the electrical equipment radiator 13) in FIG. 1 is lower than the temperature at the point D (immediately after passing through the electrical equipment 15, 17, 18) in FIG. That is, the value of ΔTD is smaller than the temperature difference ΔTC with respect to the cooling water in the heater passage 22. Incidentally, T ₂₂ in FIG. 5, (optimum operating temperature of the engine 24, about 100 ° C.) the temperature of the heater passage 22 to the first pump chamber 12c is disposed a, comparison between the temperature of the electrical device cooling circuit 11 It is described for the purpose.

  In the present embodiment, the first pump chamber 12c is disposed at a low temperature portion in the heater passage 22, that is, a fluid flow downstream portion of the heater 25, and the second pump chamber 12d is disposed at a high temperature portion in the electric device cooling circuit 11, that is, the electric device 15. , 17 and 18 on the downstream side of the fluid flow and upstream of the electrical equipment radiator 13. Therefore, the temperature difference between the first pump chamber 12c and the second pump chamber 12d can be minimized.

  According to this, since the thermal stress generated due to the temperature difference can be reduced in the shaft seal member 34 that seals between the pump chambers 12c and 12d, deformation of the shaft seal member 34 and generation of cracks over time can be reduced. That is, the deterioration of the sealing performance of the shaft sealing member 34 can be reduced.

  (3) Since the pump 12 driven by electricity is arranged in the heater passage 22, even if the mechanical pump 23 driven by the power of the engine 24 is stopped, the cooling water and the engine 24 are circulated by circulating the cooling water in the heater passage 22. Due to this residual heat, the heater 25 can exhibit heating performance.

  (4) The pump 12 rotates the blades 32 and 33 disposed in the two pump chambers 12c and 12d in the pump housing 12a by the single motor unit 12b to cool the independent electronic device cooling circuit 11 and the heater passage 22, respectively. Circulating water. Therefore, the number of pumps can be halved compared to the case where pumps are arranged in the cooling circuit 11 and the heater passage 22 respectively. Thereby, the cost as the whole heat generating body cooling device can be reduced.

  Moreover, since the number of pumps has been reduced by half, the mounting space as the heating element cooling device can be reduced, that is, the mounting property can be improved. Thereby, a heat generating body cooling device can be arrange | positioned in a narrower space.

  (5) Since the piping of the electrical equipment cooling circuit 11 and the piping of the heater circuit 22 are collected in the pump 12, the pumps are arranged in the circuits 11 and 22, and the piping is compared with the case where the pumps are separated from each other. Can be easily assembled.

  (6) The motor unit 12b is disposed in the sealed space by the partition plate 12h, and the wing 33 (magnet unit 33a) is rotated through the partition plate 12h by the magnetic force generated by the coil unit e of the motor unit 12b. . For this reason, the motor part 12b can be driven in the sealed space sealed more reliably. Thereby, it is possible to prevent the cooling water from flowing into the motor unit 12b having electric components that are sensitive to moisture and damaging the motor unit 12b.

(Second Embodiment)
In the present embodiment, as shown in FIG. 6, the first pump chamber 12c of the pump 12 is disposed in the heater passage 22, and the second pump chamber 12d is disposed in the cooling / cooling water circuit 46 that is a low-temperature fluid circuit. The engine cooling circuit 21, the heater passage 22, the configuration of the pump 12, and the location of the pump 12 in the heater passage 22 are the same as in the first embodiment.

  First, the refrigeration cycle circuit 41 will be described. The refrigeration cycle circuit 41 forms a known refrigeration cycle, and the compressor 42 receives power from the engine 24 or the like and sucks and compresses the refrigerant in the circuit 41. The compressed refrigerant radiates heat to the air from the blower 43 a by the radiator 43. The radiated refrigerant is depressurized by the decompressor 44 to be in a liquid phase and flows into the water refrigerant heat exchanger 45. In the water / refrigerant heat exchanger 45, the refrigerant in the refrigeration cycle circuit 41 absorbs the heat of water flowing through the cooling / cooling water circuit 46. This heat absorption causes the refrigerant to evaporate into a gas phase. The evaporated refrigerant is sucked and compressed again by the compressor 42.

  Water absorbed (cooled) by the refrigerant in the water / refrigerant heat exchanger 45 is circulated in the circuit 46 by the second pump chamber 12d disposed in the cooling / cooling water circuit 46. The cooled water flows into the cooler 47. In the cooler 47, water absorbs heat from the air flowing into the vehicle interior space by the blower 26. In other words, the air flowing into the passenger compartment is cooled by water.

  In the present embodiment, the cooler 47 corresponds to a cooler in the claims, and the water refrigerant heat exchanger 45 corresponds to a cooling means. The engine 24 corresponds to a heating element.

  The cooler 47 and the heater 25 are disposed in an air conditioning case 49 that forms an air passage that flows into the vehicle interior. The air mix door 48 changes the temperature of the air that passes through the heater 25 after being cooled by the cooler 47 and the air that bypasses the heater 25, thereby changing the temperature of the air that is blown out into the vehicle interior. ing.

  According to this, since the pump 12 is disposed at a lower pressure position in the heater passage 22, the pressure difference between the first pump chamber 12c and the second pump chamber 12d is reduced to reduce the deterioration of the sealing performance of the shaft seal member 34. can do.

  In the present embodiment, even when the engine is stopped, that is, when the mechanical pump 23 is stopped, the heater circuit 22 is electrically driven to heat the air-conditioning air by the heater 25 using the residual heat of the engine 24 and the cooling water. A pump 12 (first pump chamber 12c) is arranged.

  Accordingly, when the cooling water is circulated in all of the engine cooling circuit 21, the heater circuit 22, and the cooling / cooling water circuit 46, the pump 12 and the mechanical pump 22 are simultaneously driven. At this time, the pump 12 flows cooling water from the heater circuit 22 and the cooling / cooling water circuit 46, and the mechanical pump 23 flows fluid from the engine cooling circuit 21 and the heater circuit 22. At this time, since the fluid flowing through the heater circuit 22 receives pressure from both the pumps 12 and 23, the pressure in the first pump chamber 12c disposed in the heater circuit 22 is higher than that in the second pump chamber 12d.

  However, according to the present embodiment, the first pump chamber 12c is arranged at a position where the pressure in the heater circuit 22 is low (point B in FIGS. 1 and 3). Therefore, the pressure difference between the first pump chamber 12c and the second pump chamber 12d can be minimized. According to this, since the force applied to the shaft seal member 34 that seals between the pump chambers 12c and 12d can be reduced, deformation of the shaft seal member 34 and generation of cracks over time can be reduced. That is, the deterioration of the sealing performance of the shaft sealing member 34 can be reduced.

  In addition, the pump 12 rotates the blades 32 and 33 disposed in the two pump chambers 12c and 12d in the pump housing 12a by one motor unit 12b, respectively, so that the cooling water in the independent heater passage 22 and the cooling / cooling water circuit 46 is supplied. Circulating. Therefore, the number of pumps can be halved compared to the case where pumps are arranged in the heater passage 22 and the cooling / cooling water circuit 46, respectively. Thereby, the cost as the whole heat generating body cooling device can be reduced.

  Moreover, since the number of pumps has been reduced by half, the mounting space as a vehicle air conditioner can be reduced, that is, the mounting performance can be improved. Thereby, the vehicle air conditioner can be arranged in a narrower space.

  In addition, since the piping of the heater circuit 22 and the piping of the cooling / cooling water circuit 46 are concentrated in the pump 12, the pumps are arranged in the circuits 22 and 46, and the piping is easier than in the case where the positions of the pumps are separated. Can be assembled.

  In addition, since the pump 12 is driven by electricity, the water in the cooling / cooling water circuit 46 is circulated even when the compressor 42 is stopped when the engine is stopped, and the heat capacity of the water causes the air from flowing into the vehicle compartment in the cooler 47. It can exhibit endothermic ability. Further, since the pump 12 driven by electricity is disposed in the heater passage 22, even if the mechanical pump 23 driven by the power of the engine 24 is stopped, the cooling water and the engine 24 are circulated by circulating the cooling water in the heater passage 22. Due to the residual heat, the heater 25 can exhibit heating performance.

  In this embodiment, the operational effect (6) described in the first embodiment can be exhibited.

(Other embodiments)
In the above-described embodiment, an example in which the electric device is the generator 18 and the inverter 15 has been described. However, the electric device may be a device that generates heat by operation, such as a DC-DC converter that is a transformer that converts voltage. Further, heat may be absorbed from a heating element that generates heat by driving with an electric device such as a transmission gear for switching the number of rotations of the motor.

  Moreover, although the example which cools the heat-generation source of a vehicle was shown in the above-mentioned embodiment, this invention cools not only the heat-generation source mounted in moving bodies, such as a vehicle, but the heat-source fixed by the cooling fluid. Even if the cooling water of the two cooling circuits is circulated by the pump 12, the effect can be exhibited. Heat sources that are cooled by the cooling fluid include heat generation due to physical changes such as refrigeration cycle radiators, desiccant adsorption heat generation, heat generation due to chemical reactions such as combustors and fuel cells, and various types of secondary batteries and electrical components. There are various heat generation such as conversion loss.

  Further, in the above-described embodiment, the electronic devices are arranged in series in the cooling circuit 11, but devices having close heat resistance temperatures may be arranged in parallel.

  In the above-described embodiment, the blades 32 and 33 of the pump 12 have a centrifugal shape in which the fluid from the axial direction R flows in the centrifugal direction. However, the flow-through shape in which the fluid from the centrifugal direction flows in the centrifugal direction. It may be.

  In the above-described embodiment, the example in which the motor unit 12b is disposed in the space sealed by the partition wall 12h and the blade 33 is rotated through the partition wall 12h is shown. However, the blades 32 and 33 are integrally coupled to a rotating shaft that penetrates the partition wall 12h, and a shaft sealing means (seal member) that seals between the pump chamber and the motor space is disposed on the rotating shaft to provide a motor portion 12b (motor space). ) To prevent the cooling water from entering.

It is a schematic diagram which shows the heat generating body cooling device which concerns on 1st Embodiment of this invention. It is a schematic diagram which shows the structure of the pump of 1st Embodiment. It is a figure which shows the relationship between the position in the heater channel | path of FIG. 1, and the pressure concerning a seal part. It is a figure which shows the relationship between the position in the heater channel | path of FIG. 1, and the temperature of cooling water. It is a figure which shows the relationship between the position in the electric equipment cooling circuit of FIG. 1, and the temperature of a cooling water. It is a schematic diagram which shows the vehicle air conditioner which concerns on 2nd Embodiment of this invention. It is a circuit diagram which shows the prior art example which used the pump which concerns on patent document 1 for the circulation of the cooling water which flows into a heat exchanger.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 ... Electric equipment cooling circuit (1st cooling circuit), 12 ... Pump (1st pump means),
12a ... pump housing, 12c ... first pump chamber, 12d ... second pump chamber,
12i ... Pump chamber partition plate (partition member), 13 ... Electric equipment radiator (first radiator),
15 ... Inverter (first heating element, electric device), 17 ... Driving motor (first heating element),
18 ... Generator (first heating element, electrical device),
21 ... Engine cooling circuit (first cooling circuit, cooling circuit),
23 ... Mechanically driven pump (second pump means),
24 ... Engine (second heating element, heating element, internal combustion engine), 25 ... Heater,
27 ... engine radiator (second radiator, radiator), 31 ... rotating shaft,
32, 33 ... Wings, 34 ... Shaft seal members.

Claims (7)

A partition member (12i) that partitions the pump housing (12a) into a first pump chamber (12c) and a second pump chamber (12d), and blades (32, 33) disposed in each pump chamber (12c, 12d) ), The blades (32, 33), the rotating shaft (31) penetrating the partition member (12i), the penetrating portion of the partition member (12i), and the pump chambers (12c, A first pump means (12) having a shaft sealing member (34) for sealing between 12d);
A first cooling circuit (11) through which a fluid that absorbs heat from the first heating element (15, 17, 18) and radiates heat from the first radiator (13) flows;
A second cooling circuit (21) through which a fluid that absorbs heat from the second heating element (24) and radiates heat from the second radiator (27) flows;
A second pump means (23) disposed in the second cooling circuit (21) for circulating the fluid of the second cooling circuit (21);
The blade (32) of the first pump chamber (12c) circulates the fluid in the second cooling circuit (21);
The blade (33) of the second pump chamber (12d) circulates the fluid in the first cooling circuit (11);
The fluid discharged from the second pump means (23) flows into the second heat radiator (27) and then flows into the first pump chamber (12c). Body cooling device. A partition member (12i) that partitions the pump housing (12a) into a first pump chamber (12c) and a second pump chamber (12d), and blades (32, 33) disposed in each pump chamber (12c, 12d) ), The blades (32, 33), the rotating shaft (31) penetrating the partition member (12i), the penetrating portion of the partition member (12i), and the pump chambers (12c, A first pump means (12) having a shaft sealing member (34) for sealing between 12d);
A first cooling circuit (11) through which a fluid that absorbs heat from the first heating element (15, 17, 18) and radiates heat from the first radiator (13) flows;
A second cooling circuit (21) through which a fluid that absorbs heat from the second heating element (24) and radiates heat from the second radiator (27) flows;
A heater circuit (22) having a heater (25) that heats the object to be heated by the fluid as the fluid that has absorbed heat from the second heating element (24) flows and flows;
A second pump means (23) disposed in the second cooling circuit (21) for circulating fluid through the second cooling circuit (21) and the heater circuit (22);
The blade (32) of the first pump chamber (12c) circulates the fluid in the heater circuit (22);
The blade (33) of the second pump chamber (12d) circulates the fluid in the first cooling circuit (11);
The heating element cooling device according to claim 1, wherein the first pump chamber (12c) is disposed in a portion of the heater circuit (22) on the downstream side of the fluid flow with respect to the heater (25). A partition member (12i) that partitions the pump housing (12a) into a first pump chamber (12c) and a second pump chamber (12d), and blades (32, 33) disposed in each pump chamber (12c, 12d) ), The blades (32, 33), the rotating shaft (31) penetrating the partition member (12i), the penetrating portion of the partition member (12i), and the pump chambers (12c, A first pump means (12) having a shaft sealing member (34) for sealing between 12d);
A first cooling circuit (11) through which a fluid that absorbs heat from the first heating element (15, 17, 18) and radiates heat from the first radiator (13) flows;
A second cooling circuit (21) through which a fluid that absorbs heat from the first heating element (15, 17, 18) and radiates heat by the second radiator (27) flows;
A heater circuit (22) having a heater (25) that heats the object to be heated by the fluid as the fluid that has absorbed heat from the second heating element (24) flows and flows;
A second pump means (23) disposed in the second cooling circuit (21) for circulating fluid through the second cooling circuit (21) and the heater circuit (22);
The blade (32) of the first pump chamber (12c) circulates the fluid in the heater circuit (22);
The blade (33) of the second pump chamber (12d) circulates the fluid in the first cooling circuit (11);
The fluid having a temperature higher than that of the first cooling circuit (11) flows through the second cooling circuit (21) and the heater circuit (22),
The second pump chamber (12d) is located downstream of the first heating element (15, 17, 18) in the first cooling circuit (11) and more fluid than the first radiator (13). A heating element cooling device, wherein the heating element cooling device is disposed at a site upstream of the flow. The heating element cooling device according to claim 3, wherein the first pump chamber (12c) is disposed in a fluid flow downstream side of the heater (25) in the heater circuit (25). The first heating element is an electric device (15, 17, 18) mounted on a vehicle,
The second heating element is an internal combustion engine (24) mounted on a vehicle,
The second pump means is a mechanically driven pump (23) driven by receiving power from the internal combustion engine (24),
The heating element cooling device according to any one of claims 2 to 4, wherein the heater (25) heats the air-conditioning air flowing into the vehicle interior of the vehicle. A partition member (12i) that partitions the pump housing (12a) into a first pump chamber (12c) and a second pump chamber (12d), and blades (32, 33) disposed in each pump chamber (12c, 12d) ), The blades (32, 33), the rotating shaft (31) penetrating the partition member (12i), the penetrating portion of the partition member (12i), and the pump chambers (12c, A first pump means (12) having a shaft sealing member (34) for sealing between 12d);
A low-temperature fluid circuit (46) having a cooler (47) for cooling the object to be cooled by the fluid that has been absorbed by the cooling means (45) and is in a low-temperature state;
A cooling circuit (21) through which a fluid that absorbs heat from the heating element (24) and radiates heat from the radiator (27) flows;
A heater circuit (22) having a heater (25) that heats the object to be heated by the fluid flowing through the fluid that has absorbed heat from the heating element (24);
A second pump means (23) disposed in the cooling circuit (21) for circulating fluid through the cooling circuit (21) and the heater circuit (22);
The blade (32) of the first pump chamber (12c) circulates the fluid of the heater circuit (22);
The blade (33) of the second pump chamber (12d) circulates the fluid of the cryogenic fluid circuit (11);
The cooling and heating apparatus, wherein the first pump chamber (12c) is disposed in a portion of the heater circuit (22) on the downstream side of the fluid flow with respect to the heater (25). A vehicle air conditioner comprising the cooling and heating device according to claim 6,
A refrigeration cycle (41) in which refrigerant is circulated in a closed circuit by a compressor (42);
The cooling means is a heat exchanger (45) that is disposed in the refrigeration cycle (41) and absorbs heat from the fluid of the low-temperature fluid circuit (46) to evaporate a low-pressure refrigerant.
The heating element is an internal combustion engine (24) mounted on a vehicle,
The second pump means is a mechanically driven pump (23) driven by receiving power from the internal combustion engine (24),
The cooler (47) cools the air-conditioning air flowing into the vehicle interior of the vehicle;
Further, the vehicle air conditioner is characterized in that the heater (25) heats air for air conditioning flowing into the vehicle interior of the vehicle.

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