CN100575854C - Loop heat pipe and waste heat recovery equipment - Google Patents
Loop heat pipe and waste heat recovery equipment Download PDFInfo
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- CN100575854C CN100575854C CN200710110014.9A CN200710110014A CN100575854C CN 100575854 C CN100575854 C CN 100575854C CN 200710110014 A CN200710110014 A CN 200710110014A CN 100575854 C CN100575854 C CN 100575854C
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- evaporimeter
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- 238000011084 recovery Methods 0.000 title claims abstract description 77
- 239000002918 waste heat Substances 0.000 title abstract description 17
- 239000003507 refrigerant Substances 0.000 claims abstract description 122
- 239000012530 fluid Substances 0.000 claims abstract description 74
- 239000007788 liquid Substances 0.000 claims abstract description 74
- 239000002826 coolant Substances 0.000 claims description 67
- 238000009833 condensation Methods 0.000 claims description 37
- 230000005494 condensation Effects 0.000 claims description 37
- 239000002912 waste gas Substances 0.000 claims description 25
- 238000003860 storage Methods 0.000 claims description 24
- 238000001704 evaporation Methods 0.000 claims description 14
- 230000008020 evaporation Effects 0.000 claims description 12
- 238000001816 cooling Methods 0.000 claims description 5
- 239000000446 fuel Substances 0.000 claims description 5
- 238000002485 combustion reaction Methods 0.000 claims description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 27
- 238000011144 upstream manufacturing Methods 0.000 description 21
- 238000010438 heat treatment Methods 0.000 description 15
- 238000004891 communication Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 241000274582 Pycnanthus angolensis Species 0.000 description 3
- 230000004888 barrier function Effects 0.000 description 3
- 239000003054 catalyst Substances 0.000 description 3
- 239000011521 glass Substances 0.000 description 3
- 239000011087 paperboard Substances 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 238000009835 boiling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 241000196324 Embryophyta Species 0.000 description 1
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 239000012212 insulator Substances 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 238000003475 lamination Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000002688 persistence Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
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- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
一种环形热管，包括：蒸发器(14)，所述蒸发器被设置用来通过与作为热源的第一流体进行热交换来蒸发所述制冷剂；和冷凝器(15)，所述冷凝器被设置用来通过与要加热的第二流体进行热交换来液化和冷凝被蒸发的蒸汽制冷剂。所述冷凝器具有：制冷剂冷凝侧，被冷凝的液体制冷剂在该侧流动；和制冷剂未冷凝侧，冷凝之前的蒸汽制冷剂在该侧流动。此外，所述环形热管设置有流动限制部(21，22)，用于使所述第二流体从所述制冷剂冷凝侧流向所述制冷剂未冷凝侧。例如，所述环形热管可以适合地用于废热回收设备。
An annular heat pipe comprising: an evaporator (14) configured to evaporate the refrigerant by exchanging heat with a first fluid as a heat source; and a condenser (15) configured to Arranged to liquefy and condense vaporized refrigerant by heat exchange with a second fluid to be heated. The condenser has: a refrigerant condensing side, on which condensed liquid refrigerant flows; and a refrigerant non-condensing side, on which vapor refrigerant before condensing flows. Furthermore, the annular heat pipe is provided with a flow restricting portion (21, 22) for making the second fluid flow from the side where the refrigerant condenses to the side where the refrigerant does not condense. For example, the loop heat pipe can be suitably used in waste heat recovery equipment.
Description
Technical field
The present invention relates to a kind of annular heat pipe, cold-producing medium is by being evaporated from the heat as the first fluid of thermal source in described heat pipe, and the vapor refrigerant that is evaporated is cooled by second fluid that will heat, and described like this second fluid is heated by the condensation latent heat of vapor refrigerant.For example, described annular heat pipe can be used for exhaust heat recovery apparatus aptly.
Background technology
Usually, for example, annular heat pipe has been described in JP-A-4-45393.This annular heat pipe is provided with: be used to heat the evaporimeter with vaporized refrigerant; And condenser, described condenser is used to cool off and the described vapor refrigerant that is evaporated of condensation.In addition, the operation of described annular heat pipe is controlled by switch valve (valves of opening and closing).Described switch valve is provided for opening and closing passage, and the liquid refrigerant that is condensed in condenser returns described evaporimeter by described passage.In addition, described annular heat pipe is provided with the liquid refrigerant storage part at the upstream side (condenser side just) of switch valve, to store described liquid refrigerant therein.In addition, described liquid refrigerant storage part and switch valve are set at the outside of condenser.
Described condenser is set in the case (tank), and second fluid that heat flows in described case, introduces the vapor refrigerant in the condenser like this and second fluid that flows in described case carries out heat exchange, thereby heats described second fluid.However, but in this annular heat pipe, the heating properties that always improves described second fluid that will heat by simple structure is difficult.
Summary of the invention
Consider aforesaid problem, a target of the present invention provides a kind of annular heat pipe, and described annular heat pipe can improve the efficient of heat pump effectively.
Another target of the present invention provides a kind of exhaust heat recovery apparatus, and described exhaust heat recovery apparatus can improve heat recovery efficiency effectively.
According to example of the present invention, the annular heat pipe that has cold-producing medium to circulate therein comprises: evaporimeter, described evaporimeter are provided for evaporating described cold-producing medium by carrying out heat exchange with first fluid as thermal source; And condenser, described condenser is provided for by carrying out the vapor refrigerant that heat exchange is liquefied and condensation is evaporated with second fluid that will heat.Described condenser has: the condensation of refrigerant side, and the liquid refrigerant that is condensed is in this side flow; With the uncooled side of cold-producing medium, the vapor refrigerant before the condensation is in this side flow.In addition, described annular heat pipe is provided with liquid refrigerant storage part and movement restriction device, described liquid refrigerant storage part is provided for storing the liquid refrigerant that is condensed, described movement restriction device be used to make described second fluid from liquid refrigerant storage part effluent to the uncooled side of described cold-producing medium.Therefore, because the temperature difference between described cold-producing medium and described second fluid is all strengthened in described condensation of refrigerant side and the uncooled side of described cold-producing medium, the liquid refrigerant that is condensed can be cooled to low temperature effectively.Therefore, the temperature that is supplied to the liquid refrigerant of evaporimeter can be lowered, and the amount of heat absorption of cold-producing medium can be increased in the described evaporimeter.As a result, the heat pump efficiency of described annular heat pipe can be improved effectively, and has therefore improved the heating properties of second fluid that will heat.
Described liquid refrigerant storage part can be the part of described condenser.
Alternatively, but the setting operation arresting stop is used for stopping the evaporation of cold-producing medium in the described evaporimeter.For example, described operation arresting stop can be a switch valve, and described switch valve is set in the condenser to open and close passage, and wherein, the liquid refrigerant that is condensed in described condenser flows to described evaporimeter by described passage; Perhaps, described operation arresting stop can be a flow control apparatus, is used for controlling described first fluid and flows to the evaporation of the flow of described evaporimeter with cold-producing medium in the control evaporimeter.In addition, described annular heat pipe can compatibly be used for retrieving the used heat from the waste gas of engine.In this case, described first fluid is the waste gas of engine, and described second fluid is a cooling agent, and described cooling agent is used for the coolant circuit of described engine, and described evaporimeter and described condenser are provided for reclaiming used heat from described waste gas.
According to another example of the present invention, exhaust heat recovery apparatus comprises: annular heat pipe, described annular heat pipe comprises evaporimeter and condenser, described evaporimeter is provided for coming vaporized refrigerant by the heat exchange of execution and first fluid, and described condenser is provided for cooling off the vapor refrigerant that is evaporated from described evaporimeter with condensation; First fluid flow portion, described first fluid flow therein with evaporimeter in the cold-producing medium that flows carry out heat exchange; The second fluid flow portion, described second fluid flow therein, with condenser in the cold-producing medium that flows carry out heat exchange; Inlet tube, described inlet tube is introduced the described second fluid flow portion with described second fluid; And discharge pipe, second fluid that described discharge pipe will pass through after the described second fluid flow portion is discharged from the described second fluid flow portion.In addition, described condenser has: the condensation of refrigerant side, and the liquid refrigerant that is condensed is in this side flow; With the uncooled side of cold-producing medium, the vapor refrigerant before the condensation is in this side flow.In addition, described inlet tube is connected to the described second fluid flow portion in the condensation of refrigerant side of described condenser, and described discharge pipe is connected to the described second fluid flow portion in the uncooled side of the cold-producing medium of described condenser.In addition, annular heat pipe is provided with the liquid refrigerant storage part, and described liquid refrigerant storage part is provided for storing the liquid refrigerant that is condensed, and inlet tube and discharge pipe make second fluid from liquid refrigerant storage part effluent to the uncooled side of cold-producing medium.Therefore, because the temperature difference between described cold-producing medium and described second fluid all is increased in described condensation of refrigerant side and the uncooled side of described cold-producing medium, the liquid refrigerant that is condensed can be cooled to low temperature effectively.Therefore, the temperature that is supplied to the liquid refrigerant of described evaporimeter can be lowered, and the amount of heat absorption of cold-producing medium can be increased in the described evaporimeter.As a result, the heat recovery efficiency of described exhaust heat recovery apparatus (heat pump efficiency) can be improved effectively.
Description of drawings
Additional purpose of the present invention and advantage will be from becoming more apparent the detailed description of the preferred embodiment in conjunction with the accompanying drawings subsequently.Wherein:
Fig. 1 is the schematic diagram of the annular heat pipe that uses in the exhaust heat recovery apparatus that illustrates according to first embodiment of the invention;
Fig. 2 is the schematic diagram that illustrates according to the exhaust heat recovery apparatus of the car engine of first embodiment;
Fig. 3 is the schematic diagram of the annular heat pipe that uses in the exhaust heat recovery apparatus that illustrates according to second embodiment of the invention; And
Fig. 4 is the schematic diagram of the annular heat pipe that uses in the exhaust heat recovery apparatus that illustrates according to third embodiment of the invention.
Specific embodiment
(first embodiment)
Now with reference to Fig. 1 and 2 first embodiment is described.In this embodiment, annular heat pipe typically is applied to exhaust heat recovery apparatus.
At first, the basic structure to described exhaust heat recovery apparatus is described.The burning that engine (internal combustion engine) 1 is provided for by fuel is that vehicle operating produces rotation output.Described engine 1 is provided with usually: coolant circuit, the heat that produces in its control engine 1; And blast pipe 2, it is expelled to waste gas in the atmosphere.
Described coolant circuit comprises radiator loop 3, heater loop 4 and waste heat recovering loop 5.In addition, catalyst 6 and the exhaust heat recovery apparatus 7 that is used for purifying described waste gas is set in the blast pipe 2.
Then, will the described coolant circuit that comprise radiator loop 3, heater loop 4 and waste heat recovering loop 5 be described.
Self-operated thermostatic controller 11 is regulated by the amount of coolant of radiator 9 with by the ratio between the amount of coolant of radiator bypass channel 10, thereby the temperature of described cooling agent is controlled in the certain temperature range (as 80 ℃ to 100 ℃).For example, when the temperature of described cooling agent when engine heats is hanged down, be supplied to the amount of coolant of radiator bypass channel 10 to be increased, thereby when described engine heats, promote described engine heating operation.
Heater loop 4 is connected to engine 1, thereby described cooling agent is flowed out from engine 1 from the position that the engine that is different from radiator loop 3 exports, and is connected in the waste heat recovering loop 5 in exhaust heat recovery apparatus 7 downstreams.Heater core 12 is set in the heater loop 4 to be used to adding hot fluid from the heat of described cooling agent.For example, heater core 12 is set in the air duct of vehicle air conditioning, thereby makes in air duct flow air and described cooling agent carry out heat exchange.Therefore, the air that is blown into vehicle car is heated by heater core 12.
Waste heat recovering loop 5 is being come out from radiator loop 3 branches 9 the passage from engine 1 to radiator, and waste heat recovering loop 5 is connected to water pump 8.Therefore, described cooling agent is by the circulation in the waste heat recovering loop 5 that operates in of water pump 8.The water tank 13 (fluid tank) that is arranged in the exhaust heat recovery apparatus 7 is connected on the passage of waste heat recovering loop 5.
Then, will be described exhaust heat recovery apparatus 7.Exhaust heat recovery apparatus 7 is provided for by utilizing described annular heat pipe to reclaim heat and heating flowing coolant (second fluid that will heat) in waste heat recovering loop 5 that described waste gas (as the first fluid of thermal source) produces, and described annular heat pipe is because heat transmission (heat pump) is carried out in the condensation of the evaporation of cold-producing medium and cold-producing medium.In this embodiment, exhaust heat recovery apparatus 7 utilizes the heat by the waste gas after the catalyst 6 to heat described cold-producing medium.
In this embodiment, evaporimeter 14 and the condenser 15 that is contained in the case 13 (for example, cooling fluid tank) is integrally formed to constitute described annular heat pipe.In addition, as the switch valve of differential pressure control valve 16 and so on be provided for according to as described in the operation of annular heat pipe as described in the interior pressure-controlled of annular heat pipe.
For example, the evaporimeter 14 and the condenser 15 that are contained in the case 13 are made by anticorrosive (as stainless steel), and use the joining technique joint as soldering and so on to be one.Behind the joint, differential pressure control valve 16 be assembled into evaporimeter 14 and condenser 15 in the integrated member, thereby be formed for the annular heat pipe of exhaust heat recovery apparatus 7.
Exhaust heat recovery apparatus 7 has sealing (not drawing).Be evacuated in the inside of exhaust heat recovery apparatus 7 and after cold-producing medium (operating fluid) was filled in wherein, described sealing was sealed.
In this embodiment, water is used as an example of described cold-producing medium.The boiling point of water under 1 standard atmospheric pressure (atm) is 100 ℃.Because the inside of exhaust heat recovery apparatus 7 is depressurized and is evacuated to for example 0.01 standard atmospheric pressure, so the boiling point of the water in the exhaust heat recovery apparatus 7 is in 5 ℃-10 ℃ scope.As cold-producing medium, except water, may be utilized as operating fluid as alcohol, fluorocarbon, freon etc.
For example, heat exchange department 17 is laminated-types, and conduit 17a and fin 17b replace the stratum pressure on laminating direction therein.Heat exchange department 17 is installed on the vehicle, thereby the portrait orientation that makes conduit 17a is on the above-below direction of vehicle.In heat exchange department 17, can omit fin 17b.In this case, although cold-producing medium evaporation capacity is reduced, exhaust efficiency in heat exchange department 17 (exhaust efficiency) and persistence can be enhanced.
When exhaust heat recovery apparatus 7 was installed on the vehicle, nowel 18 was set at the downside of heat exchange department 17.Differential pressure control valve 16 is set in the nowel 18, thereby the condensed water of coming from differential pressure control valve 16 supplies is assigned to the conduit 17 by nowel 18.When exhaust heat recovery apparatus 7 was installed on the vehicle, top box 19 was set at the upside of heat exchange department 17, thereby the vapor refrigerant that is evaporated that rises in conduit 17a is collected in top box 19.The vapor refrigerant that is evaporated that be collected in top box 19, described is introduced in condenser 15.
In this embodiment, when exhaust heat recovery apparatus 7 was installed on the vehicle, cold-producing medium upstream case 24 was set at the upside of heat exchange department 23, and cold-producing medium downstream tank 25 is set at the downside of heat exchange department 23.Therefore, the vapor refrigerant that is supplied to cold-producing medium upstream case 24 from the top box 19 of evaporimeter 14 is assigned to the conduit 23a with by cooling of flowing coolant in case 13 and condensation.Then, be collected in the cold-producing medium downstream tank 25 from the liquid refrigerant that is condensed of conduit 23a and be introduced into differential pressure control valve 16.
Then, will be described differential pressure control valve 16, differential pressure control valve 16 is used as the operation arresting stop, so that stop the evaporation of cold-producing medium in the evaporimeter 14.Differential pressure control valve 16 is examples that open and close valve-type, and is set in the communication passage, and the liquid refrigerant that is condensed in condenser 15 is introduced in the evaporimeter 14 by described circulation passage.
When the interior pressure of exhaust heat recovery apparatus 7 was added to greater than first value, differential pressure control valve 16 was closed with the connection between the cold-producing medium downstream tank 25 of nowel 18 that turn-offs evaporimeter 14 and condenser 15, thereby prevented that the excessive pressure in the exhaust heat recovery apparatus 7 from increasing.On the contrary, when the interior pressure of exhaust heat recovery apparatus 7 is reduced to less than second value, when wherein second value is less than first value, differential pressure control valve 16 is opened with the communication passage between the cold-producing medium downstream tank 25 of the nowel 18 of opening evaporimeter 14 and condenser 15, thereby restarts the Waste Heat Recovery operation of exhaust heat recovery apparatus 7.
In this embodiment, differential pressure control valve 16 is to open and close valves (switch valve), and it is based on the interior pressure of exhaust heat recovery apparatus 7 and the differential pressure between the atmospheric pressure, carries out connection or shutoff between the nowel 18 of the cold-producing medium downstream tank 25 of condenser 15 and evaporimeter 14.If atmospheric pressure is constant, when the interior pressure of exhaust heat recovery apparatus 7 was added to valve closing presure Pc, the connection between the nowel 18 of evaporimeter 14 and the cold-producing medium downstream tank 25 of condenser 15 was turned off.On the contrary, when the interior pressure of exhaust heat recovery apparatus 7 is reduced to valve when opening pressure P o, make by differential pressure control valve 16 between the cold-producing medium downstream tank 25 of the nowel 18 of evaporimeter 14 and condenser 15 being interconnected, wherein valve is opened pressure P o and is lower than valve closing presure Pc.
Fig. 1 shows the example structure of differential pressure control valve 16.As shown in Figure 1, differential pressure control valve 16 comprises cover body 26, valve body 27, barrier film (diaphragm) 28 and back-moving spring (not drawing).
The inner space 26a of cover body 26 and the nowel 18 of evaporimeter 14 are opened port 26c by valve and are communicated with, and described valve is opened port 26c and opened and closed by valve body 27.Therefore, when valve was opened port 26c and opened by valve body 27, the liquid refrigerant among the 26a of inner space was opened port 26c by valve and is flowed into nowel 18.
Valve body 27 is maintained in the cover body 26, and it is axially movable along it.Valve body 27 is provided with valve clock (valve bell) 27a, and described valve clock 27a opens port 26c according to valve body 27 displacement opening and closing valve vertically.Barrier film 28 is configured to come mobile valve 27 vertically based on the interior pressure of exhaust heat recovery apparatus 7 and the differential pressure between the atmospheric pressure, and prevents the pulsation (panting) of differential pressure control valve 16 by deflection (reflection) operation of barrier film 28.
Described back-moving spring (not drawing) is a spring member, and described spring member is opened the direction biasing to valve body 27 from atmospheric side to valve.By regulating the bias force of described back-moving spring, valve from direction moving regulator 28 to valve that open is opened pressure P o and can be conditioned to the valve closing presure Pc of valve closing direction moving regulator 28.
As an example, after and then finishing the engine heating, under the temperature (as 70 ℃) of cooling agent, when the service load of engine 1 was half-section current load (half throttle load), valve was opened the interior pressure that pressure P o is set at exhaust heat recovery apparatus 7.In addition, and then finish engine heating after, under the temperature (as 70 ℃) of cooling agent, during engine idling (zero load operation), valve is opened the interior pressure that pressure P o is set at exhaust heat recovery apparatus 7.
Then, will the operation of exhaust heat recovery apparatus 7 be described.When engine 1 start-up operation, water pump 8 operations make cooling agent circulate in radiator loop 3, heater loop 4 and waste heat recovering loop 5.Simultaneously, the waste gas that produces with the fuel combustion of engine 1 flows into blast pipe 2, catalyst 6 and the evaporimeter 14 of exhaust heat recovery apparatus 7, and then is discharged in the atmosphere.
In this example, water is used as the cold-producing medium that circulates in the annular heat pipe between evaporimeter 14 and condenser 15.Therefore, from engine 1 waste gas by blast pipe 2 water as cold-producing medium by heating fumigators 14 in the evaporimeter 14.Water in the evaporimeter 14 is boiled and is evaporated by absorbing from the heat of waste gas, and the water vapour that is evaporated in conduit 17a on flow to be collected in the top box 19.Then, described water vapour flows into the cold-producing medium upstream case 24 of condenser 15 from the top box 19 of evaporimeter 14.The water vapour (refrigerant vapour) that is introduced into condenser 15 is by cooling of flowing coolant in case 13 and condensation.
And then engine 1 starts after its operation, and the interior pressure of exhaust heat recovery apparatus 7 is not increased to valve closing presure Pc.In this case, differential pressure control valve 16 is opened, and therefore is cooled to pass through the nowel 18 of differential pressure control valve 16 Returning evaporimeters 14 with the condensed water of condensation in condenser 15.Like this, can in exhaust heat recovery apparatus 7, repeat the Waste Heat Recovery circulation.
Therefore, the heat of waste gas is delivered to the cold-producing medium (as water) in the evaporimeter 14.Therefore, described water is evaporated in evaporimeter 14 by absorbing from the heat of waste gas as cold-producing medium, and the heat that comprises in the water as cold-producing medium is depleted as condensation latent heat when being condensed, thus heating coolant circulating in waste heat recovering loop 5.Here, the part heat of waste gas is delivered to the member of forming evaporimeter 14 and condenser 15, and by those member heating flowing coolant in waste heat recovering loop 5.
As a result, when engine start, can promote the heating of engine 1, and promote fuel increase time (auto chock operational ratio (auto choke operation ratio)) of engine heating to be shortened, therefore improve fuel consumption efficiency.
After engine 1 operation start, when the temperature of waste gas increases according to the increase of engine load, be used in the heating fumigators 14 being increased as the waste-gas heat of the water of cold-producing medium, and the quantity of steam that produces in evaporimeter 14 is increased, and therefore increases the interior pressure of annular heat pipe in the exhaust heat recovery apparatus 7.When the interior pressure of annular heat pipe in the exhaust heat recovery apparatus 7 increased to valve closing presure Pc, differential pressure control valve 16 was closed, and the water that is condensed in condenser 15 can not be got back in the evaporimeter 14 like this.Therefore, water is not supplied to evaporimeter 14 from condenser 15, and the evaporation in the evaporimeter 14 is reduced, so the Waste Heat Recovery circulation is stopped.On the contrary, because the condensation of water vapour is performed in the condenser 15, the interior pressure of annular heat pipe is lowered in the exhaust heat recovery apparatus 7.
When the interior pressure of annular heat pipe in the exhaust heat recovery apparatus 7 was lowered to valve and opens pressure P o, differential pressure control valve 16 was opened, and the water that is condensed in condenser 15 is by the nowel 18 of differential pressure control valve 16 inflow evaporators 14.Therefore, in evaporimeter 14, be evaporated once more, and the Waste Heat Recovery circulation is started once more as the water of cold-producing medium.
According to the first embodiment of the present invention, exhaust heat recovery apparatus 7 is provided with movement restriction device (flowlimitation means), so that carry out cooling agent (just from the condensation of refrigerant side, cold-producing medium downstream tank 25 sides) flowing to the uncooled side of cold-producing medium (cold-producing medium upstream case 24 sides just).Here, described condensation of refrigerant side is that the liquid refrigerant that is condensed stops or a mobile side, and the uncooled side of described cold-producing medium is a side that stopped or flowed before vapor refrigerant is condensed.In other words, as movement restriction device, the cooling agent inlet tube 21 of cooling agent leading-in box 13 is set at the downstream (condensation of refrigerant side) of condenser 15 along the flow of refrigerant direction, will have passed through coolant discharge pipe 22 that the cooling agent of case 13 discharges is set at condenser 15 along the flow of refrigerant direction upstream side (the uncooled side of cold-producing medium).In the device of Fig. 1, cooling agent inlet tube 21 is set at the bottom of case 13, and coolant discharge pipe 22 is set at the top of case 13, thereby forms movement restriction device.
In first embodiment, because cooling agent inlet tube 21 is set at the bottom of case 13 and the top that coolant discharge pipe 22 is set at case 13, described cooling agent is along from the condensation of refrigerant side (just, cold-producing medium downstream tank 25 sides) direction towards the uncooled side of described cold-producing medium (cold-producing medium upstream case 24 sides just) flows.Therefore, the liquid refrigerant that in condenser 15, is condensed can by be heated or mild heat before cooling agent be cooled to low relatively temperature.Therefore, will be supplied to the liquid refrigerant of evaporimeter 14 can be cooled to low relatively temperature, thereby by cold excessively (super-cooled).
Therefore in this way, the temperature that turns back to the liquid refrigerant of evaporimeter 14 is lowered, and has increased the temperature difference between the vapor refrigerant of evaporation in the liquid refrigerant of Returning evaporimeter 14 and the evaporimeter 14.Like this, the heat that the waste gas of increase from evaporimeter 14 obtains is possible, has therefore improved the heat recovery efficiency (heat pump efficiency) in the exhaust heat recovery apparatus 7.
In addition, in first embodiment, described vapor refrigerant has high temperature after and then being introduced in condenser 15, and its temperature is lowered along with further carrying out of condensation.In other words, cold-producing medium has high temperature in the uncooled side of cold-producing medium (just, cold-producing medium upstream case 24 sides), and the temperature of cold-producing medium is along with cold-producing medium moves and is lowered to condensation of refrigerant side (cold-producing medium downstream tank 25 sides just).On the contrary, as mentioned above, cooling agent inlet tube 21 is set at the bottom of case 13, coolant discharge pipe 22 is set at the top of case 13, thereby make cooling agent along (just from the condensation of refrigerant side, cold-producing medium downstream tank 25 sides) direction towards the uncooled side of cold-producing medium (cold-producing medium upstream case 24 sides just) flows.Therefore, had the warmed-up cooling agent of condensed fluid cold-producing medium of lower temperature, can further be had the uncondensed vapor cold-producing medium heating of higher temperature.Therefore, be condensed in by case 13 temperature of cooling agent of device 15 heating can be improved effectively.
In addition, in the exhaust heat recovery apparatus 7 of described first embodiment, when the interior pressure of the annular heat pipe in the exhaust heat recovery apparatus 7 was increased, differential pressure control valve 16 was closed.Therefore, it can prevent exhaust heat recovery apparatus 7 by superheated in summer during the high engine load, thereby prevents that exhaust heat recovery apparatus 7 is damaged.In addition, being used for storing the cold-producing medium upstream side that the liquid refrigerant storage part 29 of the liquid refrigerant that is condensed opens port 26c at the valve of differential pressure control valve 16 is arranged in the condenser 15.Therefore, when differential pressure control valve 16 was closed, the liquid refrigerating dosage that is stored in the liquid refrigerant storage part 29 was increased.
On the other hand, when differential pressure control valve 16 was opened, the liquid refrigerant of condenser 15 was by the difference inflow evaporator 14 between the liquid height (the liquid surface position of cold-producing medium in the evaporimeter 14) that utilizes liquid height (the liquid surface position of cold-producing medium in the condenser 15) in the liquid refrigerant storage part 29 and evaporimeter 14.Therefore, even when differential pressure control valve 16 is opened, the liquid refrigerant storage part 29 of the liquid refrigerant that is condensed of storage can be formed on the cold-producing medium upstream side position that the valve of the position, cold-producing medium downstream of condenser 15 and differential pressure control valve 16 is opened port 26c.
The exhaust heat recovery apparatus 7 of this embodiment is provided with: liquid refrigerant storage part 29, and it is used for storing liquid refrigerant into bottom at condenser 15; And movement restriction device, its be used to make described cooling agent from liquid refrigerant storage part 29 effluents to the uncooled portion of the cold-producing medium of condenser 15.Therefore, the cooling agent of cooling agent that the liquid refrigerant that is condensed in condenser 15 can not heated or relative low temperature is cold excessively, thereby makes the liquid refrigerant of Returning evaporimeter 14 be cooled to low temperature exactly.
(second embodiment)
With reference to Fig. 3 second embodiment is described.In a second embodiment, indicate with identical Reference numeral with the member that above-mentioned those members of first embodiment have identical function.
In the exhaust heat recovery apparatus 7 of above-mentioned first embodiment, the conduit 23a of condenser 15 vertically extends, so when exhaust heat recovery apparatus 7 was installed on the vehicle, liquid refrigerant moved down under the effect of self gravitation.In other words, in above-mentioned first embodiment, when exhaust heat recovery apparatus 7 was installed on the vehicle, condenser 15 was set at the side of evaporimeter 14, thereby made the conduit 17a of evaporimeter 14 and the conduit 23a of condenser 15 be arranged in parallel to each other vertically extend.However, but in a second embodiment, condenser 15 is configured to like this, make condenser 15 conduit 23a vertically approximately perpendicular to the conduit 17a of evaporimeter 14 vertically.
As shown in Figure 3, in the exhaust heat recovery apparatus 7 of described second embodiment, when exhaust heat recovery apparatus 7 is installed on the vehicle, condenser 15 is set at the place, top of evaporimeter 14, the conduit 23a of condenser 15 extends along the vehicle horizontal direction like this, and the conduit 17a of evaporimeter 14 extends along the vehicle vertical direction.
The cold-producing medium upstream case 24 of condenser 15 is connected to the top box 19 of evaporimeter 14, directly is communicated with the top box 19 with evaporimeter 14.Differential pressure control valve 16 is set in the cold-producing medium downstream tank 25 of condenser 15, with regulate cold-producing medium from cold-producing medium downstream tank 25 to evaporimeter 14 flow, this is similar to above-mentioned first embodiment.
The outlet of opening of differential pressure control valve 16 is connected on the nowel 18 of evaporimeter 14 by liquid refrigerant passage 31.Liquid refrigerant passage 31 can make up in evaporimeter 14 outsides, or evaporimeter 14 inboard structures.When liquid refrigerant passage 31 is structured in evaporimeter 14 inboard by a part of using conduit 17a, heat insulator is used to the conduit 17a as liquid refrigerant passage 31, so liquid refrigerant can not be evaporated in by liquid refrigerant passage 31.
In the time of on being installed to vehicle, the conduit 23a of condenser 15 approximately horizontally extends.Even in this case, flow to cold-producing medium downstream tank 25 under the pressure effect of the vapor refrigerant that the cold-producing medium in the conduit 23a of condenser 15 is 24 that provide at cold-producing medium upstream case, be evaporated, so the liquid refrigerant that is condensed is collected in the cold-producing medium downstream tank 25.
Therefore, even be configured to along continuous straight runs when elongation as the conduit 23a of condenser 15, be supplied to the liquid refrigerant of evaporimeter 14 can be collected into a side of the cold-producing medium downstream tank 25 of condenser 15.In a second embodiment, exhaust heat recovery apparatus 7 is provided with movement restriction device, and cooling agent is along from condensation of refrigerant side (cold-producing medium downstream tank 25 sides just) towards the uncooled side of cold-producing medium (just like this, cold-producing medium upstream case 24 sides) direction flows, and this is similar to above-mentioned first embodiment.Particularly, cooling agent inlet tube 21 is connected on the case 13 in cold-producing medium downstream tank 25 sides, and coolant discharge pipe 22 is connected on the case 13 in cold-producing medium upstream case 24 sides, thereby forms described movement restriction device.
In a second embodiment, other parts can manufacture similar to those parts of above-mentioned first embodiment.
(the 3rd embodiment)
Now with reference to Fig. 4 the 3rd embodiment is described.In above-mentioned first and second embodiment, differential pressure control valve 16 is used as an example of the operation arresting stop of exhaust heat recovery apparatus 7, to open and close communication passage, wherein, the liquid refrigerant that is condensed in condenser 15 flows to evaporimeter 14 by described communication passage.But, in the exhaust heat recovery apparatus 7 of described the 3rd embodiment, as shown in Figure 4, differential pressure control valve 16 is not set.In the 3rd embodiment, made up the operation arresting stop that is used for stopping the cold-producing medium evaporation in the evaporimeter 14, and do not used differential pressure regulation device 16.For example, be provided with fluid control device and control waste gas (first fluid that the is used to heat) supply that is incorporated into evaporimeter 14 by blast pipe 2, so that stop the evaporation of cold-producing medium in the evaporimeter 14.
For example, described fluid control device is to be used for the switching device of switch exhaust passage, waste gas by described exhaust passage by evaporimeter 14.By using described fluid control device to control by exhausted air quantity evaporimeter 14, that carry out heat exchange with cold-producing medium, the evaporation capacity of cold-producing medium can be controlled in the evaporimeter 14.
In addition, even during the differential pressure regulation device of describing in first and second embodiment are not set 16, the liquid refrigerant that will get back to evaporimeter 14 also is collected into the cold-producing medium downstream portion of condenser 15.Therefore, in the 3rd embodiment, exhaust heat recovery apparatus 7 is provided with movement restriction device, cooling agent (second fluid that will heat) is along from the condensation of refrigerant side (just like this, cold-producing medium downstream tank 25 sides) (just towards the uncooled side of cold-producing medium, cold-producing medium upstream case 24 sides) direction flows, and this is similar to above-mentioned first embodiment.Particularly, cooling agent inlet tube 21 is connected on the case 13 in cold-producing medium downstream tank 25 sides, and coolant discharge pipe 22 is connected on the case 13 in cold-producing medium upstream case 24 sides, thereby forms described movement restriction device.
In the example of Fig. 4, evaporimeter 14 and condenser 15 form by drawing glass type heat exchanger to make up.But evaporimeter 14 and condenser 15 can be made up by the heat exchanger of other types, for example, and laminated-type heat exchanger and straight pipe type heat exchanger.
In the example of Fig. 4, the cold-producing medium upstream case of the top box 19 of evaporimeter 14 and condenser 15 24 is connected by vapor refrigerant passage 32, and the cold-producing medium downstream tank 25 of the nowel 18 of evaporimeter 14 and condenser 15 is connected by liquid refrigerant passage 31.However, but the cold-producing medium upstream case 24 of the top box 19 of evaporimeter 14 and condenser 15 can directly be connected, and the cold-producing medium downstream tank 25 of the nowel 18 of evaporimeter 14 and condenser 15 can directly be connected.In addition, choke valve (throttle) can be set in the passage between the cold-producing medium downstream tank 25 of the nowel 18 of evaporimeter 14 and condenser 15.
In the 3rd embodiment, other parts can be manufactured into similar to those parts of above-mentioned first embodiment.
(other embodiment)
Although fully described the present invention in conjunction with the preferred embodiments of the present invention and with reference to accompanying drawing, it is pointed out that different variations and revise will be apparent to those skilled in the art.
For example, in above-mentioned first and second embodiment, described differential pressure control valve 16 is used as the example of switch valve (opening and closing valve).However, still, according to coolant temperature open and close its valve thermal valve, also can be used as switch valve by control module (ECU) based on the electric valve (as magnetic valve) that mode of operation (as detected value, predetermined value) opens and closes.
In above-mentioned first and second embodiment, switch valve (as differential pressure control valve 16) is set at the inboard of the cold-producing medium downstream tank 25 of condenser 15, the outside of condenser 15.However, but described switch valve can be set at condenser 15 below.Even in this case, described switch valve is configured to constitute the part of liquid refrigerant storage part 29, and described movement restriction device is so constructed, and makes described cooling agent from an effluent of the described switch valve side to the cold-producing medium downstream tank 25 of condenser 15.
In the above-described embodiments, waste gas is used as the thermal source first fluid.But, can be used as the thermal source first fluid as other used heat of battery used heat, inverter used heat and intercooler used heat and so on and be used.
In the above-described embodiments, the annular heat pipe that is made of evaporimeter 14 and condenser 15 is normally used for the exhaust heat recovery apparatus of vehicle.But for example, annular heat pipe of the present invention can be used for other purposes of permanent plant.
In the above-described embodiments, the waste gas of engine is used as the example of heat source fluid (first fluid), and cooling agent is used as the example of the fluid (second fluid) that will heat.But, can not use waste gas and use any other heat source fluid, and any other fluid that is used for the heater heating agent can be used as the fluid that will heat.In addition, other operating fluids can be by compatibly as the cold-producing medium of circulation between evaporimeter 14 in annular heat pipe and the condenser 15.
Such variation and modification should be understood to be in protection scope of the present invention, and the protection domain of being invented is limited to the appended claims.
Claims (14)
1. annular heat pipe, cold-producing medium circulates in described annular heat pipe, and described annular heat pipe comprises:
Evaporimeter (14), described evaporimeter are provided for evaporating described cold-producing medium by carrying out heat exchange with first fluid as thermal source;
Condenser (15), described condenser are provided for by carrying out the vapor refrigerant that heat exchange is liquefied and condensation is evaporated with second fluid that will heat, and described condenser has: the condensation of refrigerant side, and the liquid refrigerant that is condensed is in this side flow; With the uncooled side of cold-producing medium, the vapor refrigerant before the condensation is in this side flow;
Liquid refrigerant storage part (29), described liquid refrigerant storage part is provided for storing the liquid refrigerant that is condensed; And
Movement restriction device (21,22), described movement restriction device be used to make described second fluid from liquid refrigerant storage part effluent to the uncooled side of described cold-producing medium.
2. annular heat pipe as claimed in claim 1, wherein, described liquid refrigerant storage part (29) is the part of described condenser.
3. annular heat pipe as claimed in claim 1 further comprises:
The operation arresting stop, described operation arresting stop is used for stopping the evaporation of cold-producing medium in the described evaporimeter.
4. annular heat pipe as claimed in claim 3, wherein, described operation arresting stop is switch valve (16), and described switch valve is set in the described condenser to open and close passage, wherein, the liquid refrigerant that is condensed in described condenser flows to described evaporimeter by described passage.
5. annular heat pipe as claimed in claim 3, wherein, described operation arresting stop is a flow control apparatus, is used for controlling described first fluid and flows to the flow of described evaporimeter to control the evaporation of described evaporimeter cold-producing medium.
6. as any described annular heat pipe among the claim 1-5, wherein:
Described first fluid is the waste gas of engine, and described waste gas is produced by fuel combustion in engine;
Described second fluid is a cooling agent, and described cooling agent is used for the coolant circuit of described engine; And
Described evaporimeter and described condenser are provided for reclaiming used heat from described waste gas.
7. as any described annular heat pipe among the claim 1-5, wherein:
Described evaporimeter comprises a plurality of evaporimeter conduits (17a), and described cold-producing medium flows in described a plurality of evaporimeter conduits, and described evaporimeter conduit is set to be parallel to each other;
Described condenser comprises a plurality of condenser delivery tubes (23a), and described a plurality of condenser delivery tubes are set to be parallel to each other and extend between described condensation of refrigerant side and the uncooled side of described cold-producing medium; And
The bearing of trend of described evaporimeter conduit is parallel to the bearing of trend of described condenser delivery tube.
8. as any described annular heat pipe among the claim 1-5, wherein:
Described evaporimeter comprises a plurality of evaporimeter conduits (17a), and described a plurality of evaporimeter conduits are set to be parallel to each other;
Described condenser comprises a plurality of condenser delivery tubes (23a), and described cold-producing medium flows in described a plurality of condenser delivery tubes, and described condenser delivery tube (23a) is set to be parallel to each other and extends between described condensation of refrigerant side and the uncooled side of described cold-producing medium;
Described condenser is set at the upside of described evaporimeter; And
The bearing of trend of described evaporimeter conduit is perpendicular to the bearing of trend of described condenser delivery tube.
9. exhaust heat recovery apparatus comprises:
Annular heat pipe, described annular heat pipe comprises: evaporimeter (14), described evaporimeter are provided for coming vaporized refrigerant by the heat exchange of execution and first fluid; And condenser (15), described condenser is provided for cooling off the vapor refrigerant that is evaporated from described evaporimeter with condensation;
First fluid flow portion (2), described first fluid flow therein with evaporimeter in cold-producing medium carry out heat exchange;
The second fluid flow portion (13), described second fluid flow therein with condenser in cold-producing medium carry out heat exchange;
Inlet tube (21), described inlet tube is introduced the described second fluid flow portion with described second fluid; And
Second fluid that discharge pipe (22), described discharge pipe will pass through after the described second fluid flow portion is discharged from the described second fluid flow portion, wherein:
Described condenser has: the condensation of refrigerant side, and the liquid refrigerant that is condensed is in this side flow; With the uncooled side of cold-producing medium, the vapor refrigerant before the condensation is in this side flow;
Described inlet tube is connected to the described second fluid flow portion in the condensation of refrigerant side of described condenser, and described discharge pipe is connected to the described second fluid flow portion in the uncooled side of the cold-producing medium of described condenser;
Described annular heat pipe is provided with liquid refrigerant storage part (29), and described liquid refrigerant storage part is provided for storing the liquid refrigerant that is condensed; And
Described inlet tube and described discharge pipe make described second fluid from liquid refrigerant storage part effluent to the uncooled side of described cold-producing medium.
10. exhaust heat recovery apparatus as claimed in claim 9, wherein:
Described evaporimeter comprises a plurality of evaporimeter conduits (17a), and described cold-producing medium flows in described a plurality of evaporimeter conduits, and described evaporimeter conduit is set to be parallel to each other;
Described condenser comprises a plurality of condenser delivery tubes (23a), and described cold-producing medium flows in described a plurality of condenser delivery tubes, and described a plurality of condenser delivery tubes are set to be parallel to each other and extend between described condensation of refrigerant side and the uncooled side of described cold-producing medium; And
The bearing of trend of described evaporimeter conduit is parallel to the bearing of trend of described condenser delivery tube.
11. exhaust heat recovery apparatus as claimed in claim 10, further comprise switch valve (16), described switch valve is set in the described condenser, is positioned at the downside of described condenser delivery tube, to open and close passage, wherein said liquid refrigerant flows to described evaporimeter by described passage.
12., further comprise as claim 9 or 10 described exhaust heat recovery apparatus:
Flow control apparatus, described flow control apparatus are used for controlling the flow that described first fluid flows to described evaporimeter.
13. exhaust heat recovery apparatus as claimed in claim 9, wherein:
Described evaporimeter comprises a plurality of evaporimeter conduits (17a), and described cold-producing medium flows in described a plurality of evaporimeter conduits, and described evaporimeter conduit is set to be parallel to each other;
Described condenser comprises a plurality of condenser delivery tubes (23a), and described cold-producing medium flows in described a plurality of condenser delivery tubes, and described condenser delivery tube is set to be parallel to each other and extends between described condensation of refrigerant side and the uncooled side of described cold-producing medium;
Described condenser is set at the upside of described evaporimeter; And
The bearing of trend of described evaporimeter conduit is perpendicular to the bearing of trend of described condenser delivery tube.
14. exhaust heat recovery apparatus as claimed in claim 13, further comprise switch valve (16), described switch valve is set in the described condenser, be positioned at the downstream of condenser delivery tube described in the cold-producing medium stream, described switch valve opens and closes passage, and wherein said liquid refrigerant flows to described evaporimeter by described passage.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006165177 | 2006-06-14 | ||
| JP2006165177A JP2007333293A (en) | 2006-06-14 | 2006-06-14 | Loop type heat pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101089540A CN101089540A (en) | 2007-12-19 |
| CN100575854C true CN100575854C (en) | 2009-12-30 |
Family
ID=38860444
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200710110014.9A Expired - Fee Related CN100575854C (en) | 2006-06-14 | 2007-06-12 | Loop heat pipe and waste heat recovery equipment |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20070289721A1 (en) |
| JP (1) | JP2007333293A (en) |
| CN (1) | CN100575854C (en) |
| DE (1) | DE102007027108A1 (en) |
Families Citing this family (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8046998B2 (en) | 2008-10-01 | 2011-11-01 | Toyota Motor Engineering & Manufacturing North America, Inc. | Waste heat auxiliary power unit |
| JP5195381B2 (en) * | 2008-12-11 | 2013-05-08 | 株式会社デンソー | Exhaust heat recovery device |
| JP5326577B2 (en) * | 2009-01-05 | 2013-10-30 | トヨタ自動車株式会社 | Engine waste heat utilization device |
| US8330285B2 (en) * | 2009-07-08 | 2012-12-11 | Toyota Motor Engineering & Manufacturing North America, Inc. | Method and system for a more efficient and dynamic waste heat recovery system |
| US7891186B1 (en) * | 2010-01-12 | 2011-02-22 | Primlani Indru J | System and method of waste heat recovery and utilization |
| JP5316452B2 (en) * | 2010-03-23 | 2013-10-16 | 株式会社デンソー | Exhaust heat recovery device |
| CN101929814A (en) * | 2010-09-19 | 2010-12-29 | 刘至国 | Heat pipe |
| US8714288B2 (en) | 2011-02-17 | 2014-05-06 | Toyota Motor Engineering & Manufacturing North America, Inc. | Hybrid variant automobile drive |
| DE102011085961A1 (en) * | 2011-11-08 | 2013-05-08 | Behr Gmbh & Co. Kg | Cooling circuit |
| WO2013160993A1 (en) * | 2012-04-23 | 2013-10-31 | トヨタ自動車株式会社 | Heat transport device |
| CN104456908A (en) * | 2013-09-12 | 2015-03-25 | 珠海格力电器股份有限公司 | Heat exchange equipment and dehumidifier with same |
| DE102014205086B3 (en) * | 2014-03-19 | 2015-07-23 | Areva Gmbh | Passive two-phase cooling circuit |
| JP6380563B2 (en) * | 2015-02-09 | 2018-08-29 | 富士通株式会社 | Cooling device and electronic equipment |
| JP6605819B2 (en) * | 2015-03-06 | 2019-11-13 | 株式会社東芝 | Cooling system |
| EP3185664A1 (en) * | 2015-12-22 | 2017-06-28 | ABB Technology Oy | A cooling apparatus |
| DE102016001373A1 (en) * | 2016-02-08 | 2017-08-10 | KAMAX GmbH | Method and device for transmitting heat energy to a heat consumer of a heating system |
| JP6638169B2 (en) * | 2016-07-19 | 2020-01-29 | 本田技研工業株式会社 | Vehicle air conditioner |
| JP6341239B2 (en) * | 2016-08-05 | 2018-06-13 | マツダ株式会社 | Engine exhaust heat recovery device |
| JP6939034B2 (en) * | 2017-04-05 | 2021-09-22 | 富士通株式会社 | Cooling systems, cooling devices, and electronic systems |
| JP6733630B2 (en) * | 2017-09-13 | 2020-08-05 | 株式会社デンソー | Thermo siphon |
| WO2019056114A1 (en) * | 2017-09-22 | 2019-03-28 | Dana Canada Corporation | Localized reinforcement of stacked dish plate heat exchangers |
| CN109489303A (en) * | 2018-11-12 | 2019-03-19 | 北京工业大学 | A kind of adjustable heat pump of working medium charging amount/heat pipe combined heating plant |
| JP2020106210A (en) | 2018-12-27 | 2020-07-09 | 川崎重工業株式会社 | Evaporator and loop heat pipe |
| CN217715008U (en) * | 2022-05-06 | 2022-11-01 | 天津大学滨海工业研究院有限公司 | Waste heat recovery device for boiler equipment |
| CN117379973B (en) * | 2023-12-11 | 2024-03-29 | 中船重工天禾船舶设备江苏有限公司 | Refrigerant detects integrated recovery unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5966610U (en) * | 1982-10-28 | 1984-05-04 | 日産自動車株式会社 | Rapid heating device for automobiles |
| JPS59146203U (en) * | 1983-03-22 | 1984-09-29 | 日産自動車株式会社 | Vehicle thermal storage heating system |
| JPH02115015U (en) * | 1989-03-02 | 1990-09-14 | ||
| JPH0440969Y2 (en) * | 1989-03-02 | 1992-09-25 | ||
| JPH02310117A (en) * | 1989-05-24 | 1990-12-25 | Nissan Motor Co Ltd | Heating apparatus for vehicle |
-
2006
- 2006-06-14 JP JP2006165177A patent/JP2007333293A/en active Pending
-
2007
- 2007-06-12 CN CN200710110014.9A patent/CN100575854C/en not_active Expired - Fee Related
- 2007-06-13 US US11/818,257 patent/US20070289721A1/en not_active Abandoned
- 2007-06-13 DE DE102007027108A patent/DE102007027108A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| DE102007027108A1 (en) | 2008-02-14 |
| US20070289721A1 (en) | 2007-12-20 |
| JP2007333293A (en) | 2007-12-27 |
| CN101089540A (en) | 2007-12-19 |
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