WO2017057174A1 - Cold storage heat exchanger - Google Patents
Cold storage heat exchanger Download PDFInfo
- Publication number
- WO2017057174A1 WO2017057174A1 PCT/JP2016/077976 JP2016077976W WO2017057174A1 WO 2017057174 A1 WO2017057174 A1 WO 2017057174A1 JP 2016077976 W JP2016077976 W JP 2016077976W WO 2017057174 A1 WO2017057174 A1 WO 2017057174A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- refrigerant pipe
- cold storage
- joined
- storage material
- Prior art date
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, evaporator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00492—Heating, cooling or ventilating [HVAC] devices comprising regenerative heating or cooling means, e.g. heat accumulators
- B60H1/005—Regenerative cooling means, e.g. cold accumulators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
Definitions
- the present disclosure relates to a compressor that compresses and discharges a refrigerant, a radiator that cools a refrigerant that has reached a high temperature, and a refrigerating heat exchanger that forms a refrigeration cycle apparatus together with a decompressor that decompresses the cooled refrigerant and evaporates the refrigerant. .
- a refrigeration cycle apparatus is used as an air conditioner. Attempts have been made to provide limited cooling even when the refrigeration cycle apparatus is stopped. For example, in a vehicle air conditioner, a refrigeration cycle apparatus is driven by a traveling engine. For this reason, if the engine stops while the vehicle is temporarily stopped, the refrigeration cycle apparatus stops. In order to provide limited cooling during such a temporary stop, a cold storage heat exchanger in which a cold storage material is added to the evaporator of the refrigeration cycle apparatus has been proposed. For example, a cold storage heat exchanger described in Patent Document 1 is known.
- a compressor for compressing and discharging the refrigerant is present on the downstream side of the refrigerant flow with respect to the cold storage heat exchanger.
- the liquid refrigerant returns to the compressor, it causes a failure, and therefore it is generally necessary to completely evaporate the refrigerant at the outlet of the cold storage heat exchanger.
- the regenerative heat exchanger there is a so-called superheat zone where the refrigerant temperature rapidly changes to a high temperature due to the refrigerant becoming a gas monolayer near the outlet of the refrigerant passage and the pressure exceeding the saturated vapor pressure. .
- the regenerative heat exchanger may have an overheat zone at any location on the refrigerant passage.
- This disclosure is intended to provide a cold storage heat exchanger that is less susceptible to the influence of the overheating region and can secure the cold storage performance even when the overheating region exists.
- a cold storage heat exchanger includes a refrigerant passage through which a refrigerant is circulated, a plurality of refrigerant tubes arranged at intervals from each other, a cold storage material adjacent to the plurality of refrigerant tubes, A heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe to the cold storage material in an overheated region of the refrigerant generated in the refrigerant passage.
- This configuration can suppress heat transfer from the refrigerant pipe to the regenerator material in the overheated region of the refrigerant generated in the refrigerant passage, so that the regenerator material is less likely to cool due to the influence of the overheated region where the refrigerant temperature becomes high. Can be avoided. As a result, even when the overheated region exists, it is difficult to be affected by the overheated region, and the cold storage performance can be secured.
- FIG. 1 is a block diagram showing a configuration of a refrigeration cycle apparatus 1 using an evaporator as a cold storage heat exchanger according to the first embodiment.
- FIG. 2 is a plan view of an evaporator as a cold storage heat exchanger in FIG.
- FIG. 3 is a side view of the evaporator as the cold storage heat exchanger in FIG. 1.
- FIG. 4 is a diagram schematically showing the flow of the refrigerant in the evaporator.
- FIG. 5 is a schematic diagram in which the evaporator is disassembled into the windward and leeward sides in the air flow direction.
- FIG. 6 is a plan view schematically illustrating the flow of the refrigerant in the evaporator.
- FIG. 1 is a block diagram showing a configuration of a refrigeration cycle apparatus 1 using an evaporator as a cold storage heat exchanger according to the first embodiment.
- FIG. 2 is a plan view of an evaporator as a cold storage heat exchanger in FIG.
- FIG. 7 is a diagram showing the transition of the refrigerant temperature in the refrigerant passage in the evaporator.
- 8 is a cross-sectional view taken along the line VIII-VIII in FIG. 3, and is a cross-sectional view of the cold storage material container, the refrigerant pipe, and the air passage.
- FIG. 9 is a cross-sectional view schematically showing the shape of the inner fin that functions as a heat transfer suppressing portion.
- 10 is a cross-sectional view taken along line A1-A1 in FIG.
- FIG. 11 is a cross-sectional view schematically showing a modified example of the shape of the inner fin.
- FIG. 12 is a cross-sectional view schematically showing a modification of the shape of the inner fin.
- FIG. 13 is a diagram illustrating an example in which the flow of the refrigerant illustrated in FIG. 4 is different.
- FIG. 14 is a schematic diagram in which the evaporator shown in FIG. 13 is disassembled into the windward and leeward sides in the air flow direction.
- FIG. 15 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG.
- FIG. 16 is a diagram showing the transition of the refrigerant temperature in the refrigerant passage in the evaporator shown in FIG.
- FIG. 17 is a diagram showing an example in which the refrigerant flow shown in FIG. 4 is made different.
- FIG. 18 is a diagram illustrating an example in which the flow of the refrigerant illustrated in FIG. 4 is varied.
- FIG. 19 is a diagram showing an example in which the refrigerant flow shown in FIG. 4 is made different.
- FIG. 20 is a diagram illustrating an example in which the flow of the refrigerant illustrated in FIG. 4 is different.
- FIG. 21 is a cross-sectional view schematically illustrating the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the second embodiment. 22 is a cross-sectional view taken along line A2-A2 in FIG.
- FIG. 23 is a cross-sectional view schematically showing a modification of the shape of the cool storage material container.
- FIG. 24 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the third embodiment.
- FIG. 25 is a cross-sectional view taken along line A3-A3 in FIG.
- FIG. 26 is a cross-sectional view schematically showing a modified example of the shape of the cool storage material container and the inner fin.
- FIG. 27 is a cross-sectional view schematically showing the shape of the inner fin that functions as a heat transfer suppressing unit in the evaporator according to the fourth embodiment.
- 28 is a cross-sectional view taken along line A4-A4 in FIG.
- FIG. 29 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the fifth embodiment.
- 30 is a cross-sectional view taken along line A5-A5 in FIG. FIG.
- FIG. 31 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the sixth embodiment.
- 32 is a cross-sectional view taken along line A6-A6 in FIG.
- FIG. 33 is a diagram schematically showing a refrigerant flow in the evaporator according to the seventh embodiment.
- FIG. 34 is a schematic diagram in which the evaporator shown in FIG. 33 is disassembled into the windward side and the leeward side in the air flow direction.
- FIG. 35 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG. FIG.
- FIG. 36 is a diagram schematically illustrating the refrigerant flow in the evaporator according to the comparative example of the seventh embodiment.
- FIG. 37 is a schematic diagram in which the evaporator shown in FIG. 36 is disassembled into the windward and leeward sides in the air flow direction.
- FIG. 38 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG.
- FIG. 39 is a diagram schematically illustrating the refrigerant flow in the evaporator according to the modification of the seventh embodiment.
- FIG. 40 is a plan view schematically showing the flow of refrigerant in the evaporator shown in FIG.
- FIG. 41 is a diagram schematically illustrating the refrigerant flow in the evaporator according to the modification of the seventh embodiment.
- FIG. 40 is a plan view schematically showing the flow of refrigerant in the evaporator shown in FIG.
- FIG. 41 is a diagram schematically illustrating the refrigerant flow in the
- FIG. 42 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG.
- FIG. 43 is a cross-sectional view schematically showing the shape of the inner fin functioning as a heat transfer suppressing unit in the evaporator according to the eighth embodiment.
- 44 is a cross-sectional view taken along line A7-A7 in FIG. 45 is a cross-sectional view along B7-B7 in FIG.
- FIG. 46 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the ninth embodiment.
- 47 is a cross-sectional view taken along line A8-A8 in FIG. 48 is a cross-sectional view along B8-B8 in FIG.
- FIG. 49 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the tenth embodiment.
- 50 is a cross-sectional view taken along line A9-A9 in FIG. 51 is a cross-sectional view along B9-B9 in FIG.
- FIG. 52 is a plan view schematically showing a refrigerant flow in the evaporator according to the eleventh embodiment.
- FIG. 53 is a plan view schematically showing a refrigerant flow in the evaporator according to the twelfth embodiment.
- FIG. 54 is a plan view schematically showing a refrigerant flow in the evaporator according to the thirteenth embodiment.
- FIG. 55 is a schematic diagram showing the internal configuration of the cool storage material container of the evaporator according to the fourteenth embodiment.
- FIG. 56 is a diagram schematically showing the configuration of the cool storage material container of the evaporator according to the fifteenth embodiment.
- the refrigeration cycle apparatus 1 is used in a vehicle air conditioner. As shown in FIG. 1, the refrigeration cycle apparatus 1 includes a compressor 10, a radiator 20, a decompressor 30, and an evaporator 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path.
- the cold storage heat exchanger according to the first embodiment is applied as the evaporator 40.
- the cold storage heat exchanger 40 according to the present embodiment is also expressed as “evaporator 40”.
- the compressor 10 is driven by an internal combustion engine that is a power source 2 for traveling the vehicle. For this reason, when the power source 2 stops, the compressor 10 also stops. The compressor 10 sucks the refrigerant from the evaporator 40, compresses it, and discharges it to the radiator 20.
- the heat radiator 20 cools the high-temperature refrigerant.
- the radiator 20 is also called a condenser.
- the decompressor 30 decompresses the refrigerant cooled by the radiator 20.
- the decompressor 30 can be provided by a fixed throttle, a temperature expansion valve, or an ejector.
- the evaporator 40 evaporates the refrigerant decompressed by the decompressor 30 and cools the medium.
- the evaporator 40 cools the air supplied to the passenger compartment.
- the refrigeration cycle apparatus 1 can further include an internal heat exchange for exchanging heat between the high-pressure side liquid refrigerant and the low-pressure side gas refrigerant, and a receiver or accumulator tank element that stores excess refrigerant.
- the power source 2 can be provided by an internal combustion engine or an electric motor.
- the vertical direction on the paper surface of FIGS. 2 and 3 is represented as “the height direction”, the upper side thereof is represented as “upper side”, and the lower side is represented as “lower side”.
- the height direction is typically the gravitational direction, but may be another direction.
- the right and left direction on the paper surface of FIG. 2 is represented as “inflow direction” in which the refrigerant flows, the right side thereof is represented as “front side”, and the left side is represented as “back side”.
- the left-right direction on the paper surface of FIG. 3 is represented as “flow direction” in which air flows through the air passage 53, the left side thereof is represented as “windward”, and the right side is represented as “leeward side”.
- the evaporator 40 has a refrigerant passage member branched into a plurality.
- the refrigerant passage member is provided by a metal passage member such as aluminum.
- the refrigerant passage member is provided by a first header 41, a second header 42, a third header 43, a fourth header 44, which are positioned in a pair, and a plurality of refrigerant pipes 45 connecting the headers. Yes.
- the first header 41, the second header 42, the third header 43, and the fourth header 44 are disposed so as to extend along the inflow direction.
- the plurality of refrigerant tubes 45 are arranged so as to extend along a height direction orthogonal to the inflow direction.
- the first header 41 and the second header 42 form a pair, and are arranged in parallel along the inflow direction, separated from each other by a predetermined distance in the height direction.
- the third header 43 and the fourth header 44 also form a pair and are arranged in parallel along the inflow direction with a predetermined distance from each other in the height direction.
- the first header 41 and the third header 43 are arranged on the upper side in the height direction, and the second header 42 and the fourth header 44 are arranged on the lower side in the height direction.
- a plurality of refrigerant tubes 45 are arranged at equal intervals between the first header 41 and the second header 42. Each refrigerant pipe 45 communicates with the corresponding first header 41 and second header 42 at one end thereof.
- a first heat exchanging portion 48 is formed by the first header 41, the second header 42, and a plurality of refrigerant tubes 45 arranged therebetween.
- a plurality of refrigerant tubes 45 are arranged at equal intervals between the third header 43 and the fourth header 44. Each refrigerant pipe 45 communicates with the corresponding third header 43 and fourth header 44 at the other end.
- a second heat exchanging portion 49 is formed by the third header 43, the fourth header 44, and a plurality of refrigerant tubes 45 arranged therebetween.
- the evaporator 40 has a first heat exchange part 48 and a second heat exchange part 49 arranged in two layers.
- the second heat exchanging part 49 is arranged on the leeward side
- the first heat exchanging part 48 is arranged on the leeward side.
- tube 45 is arrange
- a joint as a refrigerant inlet is provided at the end of the first header 41 (the end on the near side in the inflow direction).
- the inside of the first header 41 is partitioned into a first partition and a second partition by a partition plate provided at substantially the center in the length direction (inflow direction).
- the plurality of refrigerant tubes 45 are divided into a first group G1 corresponding to the first section and a second group G2 corresponding to the second section.
- the refrigerant is supplied to the first section of the first header 41.
- the refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the first group G1.
- the refrigerant flows into the second header 42 through the first group G1 and is collected.
- the refrigerant is distributed again from the second header 42 to the plurality of refrigerant tubes 45 belonging to the second group G2.
- the refrigerant flows into the second section of the first header 41 through the second group G2.
- a joint as a refrigerant outlet is provided at the end of the third header 43 (in this embodiment, the end on the near side in the inflow direction, but it may be the back end).
- the inside of the third header 43 is partitioned into a first partition and a second partition by a partition plate provided substantially at the center in the length direction.
- the first section of the third header 43 is adjacent to the second section of the first header 41.
- the first section of the third header 43 and the second section of the first header 41 are in communication.
- the plurality of refrigerant tubes 45 are divided into a third group G3 corresponding to the first section and a fourth group G4 corresponding to the second section.
- the refrigerant flows from the second section of the first header 41 into the first section of the third header 43.
- the refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the third group G3.
- the refrigerant flows into the fourth header 44 through the third group G3 and is collected.
- the refrigerant is distributed again from the fourth header 44 to the plurality of refrigerant tubes 45 belonging to the fourth group G4.
- the refrigerant flows into the second section of the third header 43 through the fourth group G4.
- coolant in a U shape is formed.
- the refrigerant in the second section of the third header 43 flows out from the refrigerant outlet and flows toward the compressor 10.
- the refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages therein.
- the refrigerant tube 45 is also called a flat tube.
- This multi-hole tube can be obtained by an extrusion manufacturing method or a manufacturing method in which a plate is bent.
- the plurality of refrigerant passages extend along the longitudinal direction of the refrigerant pipe 45 and open to both ends of the refrigerant pipe 45.
- the plurality of refrigerant tubes 45 are arranged in a row. In each row, the plurality of refrigerant tubes 45 are arranged so that their main surfaces face each other. As shown in FIG. 8, the plurality of refrigerant pipes 45 are accommodated between two adjacent refrigerant pipes 45 for accommodating an air passage 53 for exchanging heat with air and a cold storage material container 47 described later.
- the section is divided.
- the evaporator 40 includes fin members for increasing the contact area with the air supplied to the passenger compartment.
- the fin member is provided by a plurality of corrugated fins 46.
- the fins 46 are disposed in an air passage 53 defined between two adjacent refrigerant tubes 45.
- the fin 46 is thermally coupled to the two adjacent refrigerant tubes 45.
- the fins 46 are joined to the two adjacent refrigerant tubes 45 by a joining material excellent in heat transfer.
- a brazing material can be used as the bonding material.
- the fin 46 has a shape in which a thin metal plate such as aluminum is bent in a wave shape, and includes an air passage called a louver.
- the evaporator 40 further has a plurality of cold storage material containers 47.
- the cold storage material container 47 is made of metal such as aluminum.
- the cold storage material container 47 has a flat cylindrical shape.
- the cool storage material container 47 divides a room for accommodating the cool storage material 50 inside by combining two middle plates.
- the cool storage material container 47 has a wide main surface on both surfaces. The two main walls that provide these two main surfaces are each arranged in parallel with the refrigerant pipe 45.
- the cool storage material container 47 is disposed between two adjacent refrigerant tubes 45.
- the cold storage material container 47 is disposed between two refrigerant pipes 45 adjacent to each other along the inflow direction.
- the cool storage material container 47 is thermally coupled to two refrigerant tubes 45 disposed on both sides thereof.
- the cool storage material container 47 is joined to the two adjacent refrigerant pipes 45 by a joining material excellent in heat transfer.
- a resin material such as a brazing material or an adhesive can be used.
- the cold storage material container 47 is brazed to the refrigerant pipe 45.
- a brazing material is disposed between the cold storage material container 47 and the refrigerant pipe 45 in order to connect them with a wide cross-sectional area.
- This brazing material can be provided by using a material clad with the brazing material or by arranging a brazing material foil between the cold storage material container 47 and the refrigerant pipe 45.
- the cool storage material container 47 exhibits good heat conduction with the refrigerant pipe 45.
- the surface of the cold storage material container 47 may be uneven, and the protrusion may be joined to the refrigerant pipe 45.
- the plurality of refrigerant tubes 45 are arranged at substantially constant intervals.
- a plurality of gaps are formed between the plurality of refrigerant tubes 45.
- a plurality of fins 46 and a plurality of cool storage material containers 47 are arranged with a predetermined regularity.
- 2 and 8 exemplify a configuration in which two fins 46 (air passages 53) and one cold storage material container 47 are repeatedly arranged in this order, but other arrangements may be employed.
- a part of the gap is an air passage 53.
- the remaining part of the gap is an accommodating part. Fins 46 are disposed in the air passage 53, and a cold storage material container 47 is disposed in the housing portion.
- the two refrigerant tubes 45 located on both sides of the cold storage material container 47 define an air passage for exchanging heat with air on the side opposite to the cold storage material container 47.
- two refrigerant tubes 45 are disposed between the two fins 46, and one cold storage material container 47 is disposed between the two refrigerant tubes 45.
- the cold storage material container 47 and the two refrigerant tubes 45 located on both sides thereof constitute one cold storage unit.
- the evaporator 40 is provided with a plurality of cold storage units having the same configuration. These cold storage units are arranged at equal intervals. Moreover, the some cool storage unit is arrange
- the cold storage material container 47 is joined to both the refrigerant pipes 45 of the first heat exchange unit 48 and the second heat exchange unit 49 along the air flow direction.
- the cold storage material container 47 has an outer shell 47a as shown in FIG.
- the outer shell 47a has a shape obtained by bending a plate material into a flat cylindrical shape.
- a corrugated inner fin 47b is accommodated in the outer shell 47a.
- the inner fins 47b have a shape in which a thin metal plate such as aluminum is bent into a wave shape.
- the plurality of top portions of the inner fins 47b are brazed to the inner surfaces of the main walls (wall portions having a main surface joined to the refrigerant pipe 45 as an outer surface) on both sides in the inflow direction of the outer shell 47a.
- the inner fin 47b extends along the longitudinal direction (height direction) of the cold storage material container 47, and the peaks and valleys of the inner fin 47b extend along the flow direction. According to this configuration, the inner fins 47 b increase the contact area between the cold storage material 50 and the cold storage material container 47. Details of the shape of the inner fin 47b will be described later.
- the first header 41 is also referred to as an inlet-side passage where the inlet of the refrigerant passage is provided.
- the 3rd header 43 is described also as the exit side channel
- the first header 41 and the third header 43 are arranged in parallel along the flow direction at the same position in the height direction, and collectively referred to as a first header tank 51.
- the second header 42 and the fourth header 44 are arranged in parallel along the flow direction at the same position in the height direction, and are collectively referred to as a second header tank 52.
- the refrigerant flowing into the first section of the first header 41 flows into the first section of the second header 42 through the refrigerant pipe 45 of the first group G1 (the first section 41). 1 turn).
- the refrigerant that has flowed into the first section of the second header 42 flows into the second section of the second header 42.
- the refrigerant flowing into the second section of the second header 42 flows into the second section of the first header 41 through the refrigerant pipe 45 of the second group G2 (second turn). Since the second section of the first header 41 and the second section of the third header 43 communicate with each other, the refrigerant flowing into the second section of the first header 41 flows into the second section of the third header 43.
- the refrigerant that has flowed into the second section of the third header 43 flows into the second section of the fourth header 44 through the refrigerant pipe 45 of the third group G3 (third turn).
- the refrigerant that has flowed into the second section of the fourth header 44 flows into the first section of the fourth header 44.
- the refrigerant flowing into the first section of the fourth header 44 flows into the first section of the third header 43 through the refrigerant pipe 45 of the fourth group G4 (fourth turn).
- the refrigerant flowing into the first section of the third header 43 flows out to the outside. That is, the evaporator 40 of this embodiment has a configuration having a so-called four-turn type refrigerant passage.
- the compressor 10 for compressing and discharging the refrigerant exists downstream of the evaporator 40 in the refrigerant flow.
- the liquid refrigerant returns to the compressor 10, it causes a failure, and therefore it is generally necessary to completely evaporate the refrigerant at the outlet of the evaporator 40.
- the refrigerant becomes a gas monolayer, and a portion where the refrigerant temperature rapidly changes to a high temperature due to the pressure exceeding the saturated vapor pressure, a so-called superheat zone S exists.
- FIG. 7 shows an example of the characteristic of the refrigerant temperature in the four-turn type refrigerant passage.
- the horizontal axis in FIG. 7 represents the position of the refrigerant passage, the left side (origin side) of the axis represents the inlet, and the right side represents the outlet.
- the vertical axis in FIG. 7 represents the refrigerant temperature at each flow path position.
- the refrigerant temperature decreases after being introduced into the refrigerant passage, but suddenly changes to a high temperature at a substantially intermediate position of the fourth turn (that is, the fourth group G4). Has occurred.
- the superheat zone S is generated in a substantially half region on the upper side in the height direction in the refrigerant pipe 45 of the fourth group G4.
- the regenerator container 47 is joined to both the refrigerant pipes 45 of the first heat exchange part 48 and the second heat exchange part 49 along the flow direction.
- the conventional cool storage material container 47 only the cool storage material 50 in the contact portion with the refrigerant pipe 45 of the fourth group G4, that is, the upwind side coolant pipe 45 in the flow direction, is hardly stored due to the influence of the superheat zone S. Therefore, a difference arises in how to cool the internal regenerator 50 between the windward side and the leeward side in the flow direction.
- the shape of the inner fin 47 b is configured not to be joined to the cold storage material container 47 in the superheated region S of the refrigerant.
- the inner fin 47b is connected to the inner wall surface of the outer shell 47a of the regenerator container 47 in the portion of the regenerator container 45 that is joined to the refrigerant pipe 45 where the superheat area S is generated. In the part which is not joined and contacts the refrigerant pipe 45 other than the superheated region S, it is joined to the inner wall surface.
- a portion where the top of the inner fin 47 b is joined to the cold storage material container 47 is represented by a solid line, and a portion where the top of the inner fin 47 b is not joined to the cold storage material container 47 is represented by a dotted line.
- the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
- the cool storage material container 47 is formed so as to be joined to the at least two refrigerant tubes 45 arranged along the flow direction.
- the inner fins 47 b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material container 47.
- Inner fin 47b includes a portion in contact with superheat zone S of refrigerant pipe 45 in cold storage material container 47 joined to at least two refrigerant pipes 45 including refrigerant pipe 45 in which superheat zone S is generated, and flows.
- the region overlapping this portion is not joined to the inner wall of the regenerator material container 47, and the other region is joined to the inner wall of the regenerator material container 47.
- the inner fin 47b is not joined to the cold storage material container 47, that is, the refrigerant pipe 45 in the superheat region S, so that the heat from the superheated refrigerant is not easily transmitted to the inside of the cold storage material 50. Further, since the inner fin 47b itself is also disposed (floating) in the regenerator container 47 in the superheat region S, the cold heat of the refrigerant in the non-superheat region is transferred to the regenerator material 50 in the superheat region via the inner fin 47b. Is also reported.
- the cool storage material 50 in the cool storage material container 47 can be cooled well. This eliminates the inconvenience that the regenerator material 50 in the regenerator container 47 in the superheat zone S does not cool and the temperature distribution is allowed to cool in the evaporator (evaporator 40), and that it cannot be stored due to the overheat region. can do.
- the inner fin 47b is not joined to the cold storage material container 47 in the superheat zone S, so that the inner fin 47b is a refrigerant in the superheat zone S generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage. It functions as a “heat transfer suppression unit” that suppresses heat transfer from the tube 45 to the cold storage material 50. And by providing such an inner fin 47b, the heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the cold storage material 50 is affected by the influence of the superheat zone S where the refrigerant temperature becomes high. The situation where it becomes difficult to get cold can be avoided. As a result, the evaporator 40 as the cold storage heat exchanger of the first embodiment is less susceptible to the influence of the superheat zone S even when the superheat zone S exists, and can secure the cold storage performance.
- the joint ratio between the inner fin 471 b and the inner wall surface of the outer shell 471 a of the cold storage material container 471 is relatively low at the portion where the inner fin 471 b contacts the superheated region S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with an inner wall surface may become relatively high in the part which contacts other than the superheat zone S of the refrigerant
- the joining rate is relatively low means that the number of the ridges and valleys of the inner fin 471b that are joined to the inner wall surface of the outer shell 471a is relatively small, and “the joining rate is relatively high”. Means that the number of the ridges and valleys of the inner fin 471b that are joined to the inner wall surface of the outer shell 471a is relatively large.
- the evaporator 401 becomes Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
- the wave shape of the inner fin 47b follows the longitudinal direction (height direction) of the cool storage material container 47, ie, the peak and valley of the inner fin 47b extend along a flow direction.
- the inner fin 47b may have a wave shape continuous in a different direction.
- the wave shape of the inner fin 472b is continuous in the short direction (flow direction) of the cold storage material container 472, that is, the peaks and valleys of the inner fin 472b are in the height direction. It can be set as the structure extended along.
- the ridges and valleys of the inner fins 472b are not joined to the inner wall surface of the outer shell 472a of the regenerator container 472 in the portion that contacts the superheated area S of the refrigerant pipe 45 along the height direction, and the refrigerant pipe 45 is overheated. In the portion that comes into contact with other than the area S, it is joined to the inner wall surface.
- the evaporator 402 can suppress the heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S, and the same effect as the evaporator 40 of the first embodiment can be obtained.
- the four-turn system is exemplified as the configuration of the refrigerant passage inside the evaporator 40, but is not limited thereto.
- the refrigerant flowing into the first header 41A flows into the second header 42A through the refrigerant pipe 45 of the first heat exchanging section 48 (first turn). Since the second header 42A and the fourth header 44A communicate with each other, the refrigerant that has flowed into the second header 42A flows into the fourth header 44A.
- the refrigerant that has flowed into the fourth header 44A flows into the third header 43A through the refrigerant pipe 45 of the second heat exchange section 49 (second turn).
- the refrigerant flowing into the third header 43A flows out to the outside. That is, the regenerator heat exchanger 40A has a so-called two-turn refrigerant path.
- FIG. 16 shows an example of the refrigerant temperature characteristic in the two-turn refrigerant passage.
- the refrigerant temperature decreases after being introduced into the refrigerant passage, but rapidly changes to a high temperature at the second half position of the second turn, and the superheated region S is generated in the subsequent portions.
- the superheat zone S is generated in a region on the upper side in the height direction of the refrigerant pipe 45 of the second heat exchange unit 49.
- the inner fins 47b of the first embodiment can also be applied to those constituting a refrigerant flow such as the cold storage heat exchanger 40A, and can function as a heat transfer suppression unit.
- the cold storage heat exchanger 40A is configured to eliminate the internal sections of the first header 41A, the second header 42A, the third header 43A, and the fourth header 44A, but may be configured to increase the internal sections.
- the first header 41B, the second header 42B, the third header 43B, and the fourth header 44B are each divided into three sections.
- the refrigerant that has flowed into the first section of the first header 41B flows through the refrigerant pipe 45 into the first section of the second header 42B (first turn).
- the refrigerant that has flowed into the first section of the second header 42B flows into the second section of the second header 42B.
- the refrigerant that has flowed into the second section of the second header 42B flows through the refrigerant pipe 45 into the second section of the first header 41B (second turn).
- the refrigerant that has flowed into the second section of the first header 41B flows into the third section of the first header 41B.
- the refrigerant that has flowed into the third section of the first header 41B flows into the third section of the second header 42B through the refrigerant pipe 45 (third turn). Since the third section of the second header 42B and the third section of the fourth header 44B communicate with each other, the refrigerant flowing into the third section of the second header 42B flows into the third section of the fourth header 44B.
- the refrigerant flowing into the third section of the fourth header 44B flows through the refrigerant pipe 45 and into the third section of the third header 43B (fourth turn).
- the refrigerant that has flowed into the third section of the third header 43B flows into the second section of the third header 43B.
- the refrigerant flowing into the second section of the third header 43B flows through the refrigerant pipe 45 and into the second section of the fourth header 44B (fifth turn).
- the refrigerant that has flowed into the second section of the fourth header 44B flows into the first section of the fourth header 44B.
- the refrigerant flowing into the first section of the fourth header 44B flows through the refrigerant pipe 45 and into the first section of the third header 43B (sixth turn).
- the refrigerant that has flowed into the first section of the third header 43B flows out to the outside. That is, the regenerative heat exchanger 40B has a so-called six-turn refrigerant path.
- the inner fins 47b of the first embodiment can also be applied to those constituting a refrigerant flow such as the cold storage heat exchanger 40B, and can function as a heat transfer suppression unit.
- the refrigerant inlet / outlet ports are provided in the first header 41, 41A, 41B and the third header 43, 43A, 43B, which are arranged on the upper side in the direction of gravity (height direction). .
- the form of the refrigerant inlet / outlet is not limited to these, and the top and bottom of the cold storage heat exchangers 40, 40A, 40B may be reversed.
- the first header 41R and the third header 43R are disposed on the lower side in the direction of gravity (height direction), and the second header 42R and the fourth header 44R are disposed on the upper side in the direction of gravity. Is arranged.
- the refrigerant that has flowed into the first section of the first header 41R flows through the refrigerant pipe 45 into the first section of the second header 42R (first turn).
- the refrigerant that has flowed into the first section of the second header 42R flows into the second section of the second header 42R.
- the refrigerant that has flowed into the second section of the second header 42R flows through the refrigerant pipe 45 and into the second section of the first header 41R. (2nd turn)
- the refrigerant flowing into the second section of the first header 41R flows into the second section of the third header 43R.
- the refrigerant that has flowed into the second section of the third header 43R flows through the refrigerant pipe 45 into the second section of the fourth header 44R (third turn).
- the refrigerant that has flowed into the second section of the fourth header 44R flows into the first section of the fourth header 44R.
- the refrigerant that has flowed into the first section of the fourth header 44R flows through the refrigerant pipe 45 into the first section of the third header 43R (fourth turn).
- the refrigerant flowing into the first section of the third header 43R flows out to the outside. That is, the cold storage heat exchanger 40R has a configuration having a so-called four-turn refrigerant passage, and the arrangement of the cold storage heat exchanger 40 in the height direction is changed.
- a cold storage heat exchanger 40RA shown in FIG. 19 is obtained by reversing the cold storage heat exchanger 40A shown in FIG.
- the regenerator heat exchanger 40RA has a so-called two-turn type refrigerant passage, and the first header 41RA and the third header 43RA are arranged on the lower side in the direction of gravity (height direction), and the second header 42RA and the fourth header 44RA is arranged on the upper side in the direction of gravity.
- the cold storage heat exchanger 40RB has a so-called six-turn refrigerant passage, and the first header 41RB and the third header 43RB are arranged on the lower side in the direction of gravity (height direction), and the second header 42RB and the fourth header 44RB is arranged on the upper side in the direction of gravity.
- the second embodiment will be described with reference to FIGS.
- the evaporator 140 of the second embodiment is different from the evaporator 40 of the first embodiment in the configuration of a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S.
- the shape of the regenerator container 147 is a structure that does not join the refrigerant pipe 45 in the refrigerant overheating region S, and the regenerator container 147 having this structure is heated. Functions as a transmission suppression unit.
- the evaporator 140 of 2nd Embodiment differs from the evaporator 40 of 1st Embodiment by the point which does not provide an inner fin in the inside of the cool storage material container 147.
- the regenerator container 147 joined to the refrigerant tube 45 in which the superheat zone S is generated is not joined to the refrigerant tube 45 in the portion (region 147c) in contact with the superheat zone S of the refrigerant tube 45.
- 45 is formed at an interval, and is joined to the refrigerant pipe 45 at a portion (outer shell 147a) in contact with the refrigerant pipe 45 other than the superheat zone S.
- a region 147 c of the outer shell 147 a of the cold storage material container 147 that overlaps the superheated region S is recessed in a direction in which the surface is separated from the refrigerant pipe 45. The shape is illustrated.
- the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
- the cool storage material container 147 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction.
- the cold storage material container 147 joined to at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated includes a portion that contacts the superheat zone S of the refrigerant tube 45 and when viewed from the flow direction. In the region 147c that overlaps with this portion, it is not joined to the refrigerant tube 45 but is spaced from the refrigerant tube 45, and in the other region 147a, it is joined to the refrigerant tube 45.
- the regenerator container 147 since the regenerator container 147 is not joined to the refrigerant pipe 45 in the superheat region S, the heat from the overheated refrigerant is not easily transmitted to the inside of the regenerator 50. Moreover, since the cool storage material container 147 itself is in contact with the non-superheated region, the cold heat of the refrigerant in the non-superheated region is also transmitted to the cool storage material 50 in the superheated region S. Thereby, the evaporator 140 of 2nd Embodiment can have an effect similar to the evaporator 40 of 1st Embodiment.
- the shape of the cool storage material container 147 of 2nd Embodiment is not limited to the above thing,
- tube 45 in the superheat zone S to the cool storage material 50 via the cool storage material container 147 is superheat zone S.
- Any other configuration may be used as long as it is relatively smaller than the heat transfer amount. In other words, it is only necessary that the heat transfer performance of the regenerator container 147 in the superheat zone S can be made relatively lower than the other parts. For example, as shown in FIG.
- the joint ratio with the refrigerant pipe 45 is relatively low in a portion (area 1471 c) where the cold storage material container 1471 contacts the superheated area S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with the refrigerant
- the ratio of the portion joined to the refrigerant pipe 45 in the outer surface of the cool storage material container 1471 is relatively large.
- the evaporator 1401 Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
- the evaporator 240 of the third embodiment is different from the evaporator 40 of the first embodiment in the configuration of a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S.
- the shape of the regenerator container 247 is a structure that does not join the refrigerant pipe 45 in the refrigerant overheating region S, and the regenerator container 247 having this structure is heated. Functions as a transmission suppression unit.
- the evaporator 240 of 3rd Embodiment is an evaporator of 1st Embodiment that the inner fin 247b provided in the inside of the cool storage material container 247 is joined to the inner wall face of the outer shell 247a over the whole area of a longitudinal direction. Different from 40.
- the inner fin 247b is disposed so as to extend along the longitudinal direction (height direction) inside the cold storage material container 247, and is joined to the inner wall of the cold storage material container 247.
- the regenerator container 247 joined to the refrigerant pipe 45 in which the superheat zone S is generated is not joined to the refrigerant pipe 45 at a portion (region 247 c) in contact with the superheat zone S of the refrigerant pipe 45 and spaced from the refrigerant pipe 45. It is formed and joined to the refrigerant pipe 45 at a portion (outer shell 147a) that is in contact with the refrigerant pipe 45 other than the superheat zone S.
- the cool storage material container 247 is formed so as to be joined to at least two refrigerant pipes 45 arranged along the flow direction.
- the inner fins 247b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cool storage material containers 247.
- the regenerator container 247 joined to the at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated includes a portion in contact with the superheat zone S of the refrigerant tube 45 and is viewed from the flow direction. Sometimes, the region 247c overlapping with this portion is not joined to the refrigerant tube 45 but is spaced from the refrigerant tube 45, and the other region 247a is joined to the refrigerant tube 45.
- the regenerator container 247 is not joined to the refrigerant pipe 45 in the superheat zone S, and the inner fins 247b joined inside the regenerator container 247 are also not joined to the refrigerant pipe 45. It becomes difficult for the heat from the refrigerant to be transmitted to the inside of the regenerator 50. Further, since the inner fins 247b themselves are also arranged in the regenerator container 47 in the superheat region S, the cold heat of the refrigerant in the non-superheat region is also transmitted to the regenerator material 50 in the superheat region S via the inner fins 247b.
- the evaporator 240 of 3rd Embodiment can have an effect similar to the evaporator 40 of 1st Embodiment.
- the inner fin 247b is not joined to the inner wall surface of the outer shell 247a of the regenerator container 247 at the portion where the inner fin 247b is in contact with the superheated region S of the refrigerant pipe 45 as in the first embodiment. It is good also as a structure. With this configuration, the inner fin 247b is not joined to the regenerator container 247, that is, the refrigerant pipe 45 in the superheat region S, so that the heat from the overheated refrigerant is more difficult to be transmitted to the inside of the regenerator 50.
- the shape of the cool storage material container 247 of 3rd Embodiment is not limited to the above thing,
- tube 45 in the superheat zone S to the cool storage material 50 via the cool storage material container 247 is superheat zone S.
- Any other configuration may be used as long as it is relatively smaller than the heat transfer amount.
- the joining ratio with the refrigerant pipe 45 is joined so as to be relatively low, and the joining ratio with the refrigerant pipe 45 is relative to the portion (outer shell 2471a) in contact with the refrigerant pipe 45 other than the superheated area S. It can be set as the structure joined so that it may become high.
- the evaporator 2401 Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
- FIG. A configuration similar to that described with reference to the first embodiment can be applied. Specifically, as shown in FIG. 26, in the evaporator 2401, the joint ratio between the inner fin 2471 b and the inner wall surface of the outer shell 2471 a of the regenerator container 2471 is relative to the portion where the inner fin 2471 b contacts the superheated region S of the refrigerant pipe 45.
- the evaporator 2401 can suppress heat transfer from the refrigerant pipe 45 to the cool storage material 50 in the superheat zone S, and The same effect as the evaporator 40 of 1 embodiment is acquired.
- the evaporator 240 in the evaporator 240, a configuration in which the wave shape of the inner fin 247b is continuous in the short direction (flow direction) of the cold storage material container 247, That is, the configuration may be such that the peaks and valleys of the inner fin 247b extend along the height direction. Even in this configuration, the evaporator 240 can suppress heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S, and the same effect as the evaporator 40 of the first embodiment can be obtained.
- a fourth embodiment will be described with reference to FIGS. 27 and 28.
- the evaporator 340 of the fourth embodiment is different from the inner fin 47b in the evaporator 40 of the first embodiment in the shape of the inner fin 347b as a heat transfer suppressing unit.
- the refrigerant pipe 45 when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side.
- the inner fin 347b is different from the first embodiment in that the inner fin 347b is not joined to the cold storage material container 347.
- the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
- the cool storage material container 347 is formed so as to be joined to at least two refrigerant tubes arranged along the flow direction.
- the inner fins 347b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cool storage material containers 347.
- the inner fins 347b are disposed in the entire region in the longitudinal direction in the region of the cold storage material container 347 joined to at least two refrigerant tubes 45 including the refrigerant tubes 45 in which the superheat zone S is generated, in a region overlapping with the refrigerant tubes 45 in which the superheat zone S is not generated. It is joined to the inner wall of the cold storage material container 347 over the whole.
- the evaporator 340 of the fourth embodiment has the same effect as that of the first embodiment. Further, since the inner fin 347b is in contact with the refrigerant tube 45 in the non-superheated region on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the cold storage material 50 can be further suppressed.
- FIG. The evaporator 440 of the fifth embodiment is different from the cold storage material container 147 in the evaporator 140 of the second embodiment in the shape of the cold storage material container 447 as a heat transfer suppression unit. Specifically, as shown in FIGS. 29 and 30, when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side. However, it differs from the second embodiment in that the cold storage material container 447 is not joined to the refrigerant pipe 45.
- At least two refrigerant tubes 45 are arranged in the evaporator 440 along the air flow direction of the air passage 53.
- the cool storage material container 447 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction.
- the regenerator container 447 joined to at least two refrigerant pipes 45 including the refrigerant pipe 45 in which the superheat zone S is generated extends in the extending direction (height direction) in a region overlapping with the refrigerant pipe 45 in which the superheat zone S does not occur.
- the refrigerant pipe 45 is joined over the entire area.
- the portion (region 447c) of the refrigerant tube 45 that is in contact with the superheat zone S is not joined to the refrigerant tube 45 and is spaced from the refrigerant tube 45.
- the other portion 447a is joined to the refrigerant pipe 45.
- the evaporator 440 of the fifth embodiment has the same effects as those of the second embodiment. Further, since the cold storage container 447 is in contact with the refrigerant tube 45 in the non-superheated area on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the cold storage material 50 is further suppressed. it can. Moreover, since the capacity
- the sixth embodiment will be described with reference to FIGS. 31 and 32.
- the evaporator 540 of the sixth embodiment is different from the cold storage material container 247 in the evaporator 240 of the third embodiment in the shape of the cold storage material container 547 as a heat transfer suppression unit.
- the superheat zone S generally occurs on the windward side, and therefore only the windward side.
- the regenerator container 547 is not joined to the refrigerant pipe 45.
- the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
- the cool storage material container 547 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction.
- the inner fins 547b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material containers 547.
- the regenerator container 547 joined to at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated extends in the extending direction (height direction) in a region overlapping with the refrigerant tube 45 in which the superheat zone S does not occur.
- the refrigerant pipe 45 is joined over the entire area. Further, in the region overlapping with the refrigerant tube 45 where the superheat zone S is generated, the portion (region 547c) of the refrigerant tube 45 that is in contact with the superheat zone S is not joined to the refrigerant tube 45 and is formed at an interval from the refrigerant tube 45.
- the other portion 547a is joined to the refrigerant pipe 45.
- the evaporator 540 of the sixth embodiment has the same effects as those of the third embodiment.
- the regenerator container 547 and the inner fins 547b are in contact with the refrigerant tube 45 in the non-superheated area on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the regenerator material 50 It can be further suppressed.
- capacitance of the cool storage material container 547 can be increased from 3rd Embodiment, more cool storage materials 50 can be accommodated.
- the target superheat zone S1 is different from the superheat zone S of the first to sixth embodiments.
- the evaporator 1040 (cold heat storage heat exchanger) according to the seventh embodiment suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 generated due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low.
- the refrigerant flowing into the first header 2041 flows into the second header 2042 through the refrigerant pipe 45 of the first heat exchange unit 48 (first turn). Since the second header 2042 and the fourth header 2044 communicate with each other, the refrigerant flowing into the second header 2042 flows into the fourth header 2044.
- the refrigerant flowing into the fourth header 2044 flows into the third header 2043 through the refrigerant pipe 45 of the second heat exchange unit 49 (second turn).
- the refrigerant flowing into the third header 2043 flows out to the outside.
- the refrigerant when the refrigerant flow rate is low, the refrigerant easily flows only into the refrigerant pipe 45 on the near side in the inflow direction, which is in the vicinity of the inlet of the refrigerant passage, and the refrigerant is hardly supplied to the refrigerant pipe 45 on the far side in the inflow direction. For this reason, when the flow rate of the refrigerant in the refrigerant passage is small, the overheating region S1 exists in the region on the back side in the inflow direction.
- the superheat zone S2 (second superheat zone) shown in FIG. 37 is a superheat zone that occurs in the vicinity of the outlet targeted in the first to sixth embodiments.
- the evaporator 1040 of the seventh embodiment is characterized by the structure of the refrigerant passage so as to be less affected by the superheated region S1 and to ensure the cold storage performance of the cold storage material 50.
- the basic configuration of the evaporator 1040 is the same as that of the evaporator 1040 of the first embodiment, but the configuration of the refrigerant passage is different. More specifically, the first header 1041, the second header 1042, the third header 1043, The internal section of the fourth header 1044 and the communication relationship with each other are different.
- the first header 1041 unlike the first header 41 of the first embodiment, the first section and the second section are communicated. Therefore, the refrigerant supplied to the first header 1041 is distributed to the plurality of refrigerant tubes 45 belonging to the first group G1 and the second group G2. The refrigerant flows into the first section of the second header 1042 through the refrigerant pipe 45 of the first group G1, and flows into the second section of the second header 1042 through the refrigerant pipe 45 of the second group G2.
- the second header 1042 is sealed so that communication between the first section and the second section is impossible, unlike the second header 42 of the first embodiment.
- the 4th header 1044 is sealed between the 1st division and the 2nd division so that communication is impossible.
- the first section of the second header 42 located on the near side in the inflow direction and on the leeward side in the flow direction communicates with the first section of the fourth header 1044 located on the back side in the inflow direction and on the upwind side in the flow direction.
- the second section of the second header 42 located on the rear side in the inflow direction and on the leeward side in the flow direction is communicated with the second section of the fourth header 1044 located on the front side in the inflow direction and on the upwind side in the flow direction.
- the refrigerant flows from the first section of the second header 1042 to the first section of the fourth header 1044 and flows from the second section of the second header 1042 to the second section of the fourth header 1044.
- the first section and the second section are communicated.
- the refrigerant flowing into the first section of the fourth header 1044 is distributed to the plurality of refrigerant tubes 45 belonging to the third group G3, and the refrigerant flowing into the second section of the fourth header 1044 is transferred to the fourth group G4. It is distributed to the plurality of refrigerant tubes 45 to which it belongs.
- the refrigerant flows into the third header 1043 through the refrigerant tubes 45 of the third group G3 and the fourth group G4, and is collected.
- the refrigerant in the third header 1043 flows out from the refrigerant outlet and flows toward the compressor 10.
- the refrigerant passage is positioned in the inflow direction of the refrigerant introduced from the first header 1041 at the upper side in the height direction in the second header tank 52 at the lower side in the height direction.
- the structure which replaces is taken. That is, the refrigerant introduced from the front side in the inflow direction through the refrigerant pipe 45 of the first group G1 is replaced to the back side in the inflow direction, and the refrigerant pipe 45 of the second group G2 is connected from the back side in the inflow direction.
- the refrigerant introduced through is replaced with the front side in the inflow direction. As shown in FIGS.
- the schematic shape of the refrigerant passage in the second header tank 52 is an X-shape when viewed from the height direction, and the schematic shape of the refrigerant passage in the evaporator 1040.
- the typical shape is obtained by intersecting two two-turn refrigerant passages.
- the configuration of the refrigerant passage of the seventh embodiment is referred to as a “replacement flow method”.
- the configuration of the refrigerant flow of the replacement flow method of the seventh embodiment can be expressed as follows.
- the evaporator 1040 includes a first header tank 51 formed so that one end sides of the plurality of refrigerant tubes 45 communicate with each other and the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material container 47 is a longitudinal direction; And a second header tank 52 formed so that the other end side of the tube 45 communicates with the inflow direction as a longitudinal direction.
- the plurality of refrigerant tubes 45 are arranged in two rows so as to form a pair along the air flow direction of the air passage 53.
- the interior of the first header tank 51 is divided into a first header 1041 and a third header 1043.
- the first header 1041 is an inlet-side passage that communicates with the refrigerant pipe 45 disposed on the downstream side in the flow direction among the plurality of refrigerant pipes 45 and has an inlet of the refrigerant passage at one end in the longitudinal direction.
- the third header 1043 is an outlet-side passage that communicates with the refrigerant pipe 45 disposed on the upstream side in the flow direction and that has an outlet of the refrigerant passage at one end (or the other end) in the longitudinal direction.
- the plurality of refrigerant tubes 45 are divided into a first group G1, a second group G2, a third group G3, and a fourth group G4.
- the refrigerant pipe 45 of the first group G1 communicates with the first header 1041 as an inlet side passage, and is disposed on one end side in the longitudinal direction (front side in the inflow direction).
- the refrigerant pipe 45 of the second group G2 communicates with the first header 1041 as an inlet side passage, and is disposed on the other end side in the longitudinal direction (back side in the inflow direction).
- the refrigerant pipe 45 of the third group G3 communicates with a third header 1043 as an outlet side passage and is disposed on the other end side in the longitudinal direction.
- the refrigerant pipe 45 of the fourth group G4 communicates with a third header 1043 serving as an outlet-side passage and is disposed on one end side in the longitudinal direction.
- the second header tank 52 communicates the first group G1 and the third group G3, communicates the second group G2 and the fourth group G4, and extends from the first header 1041 to the near side and the far side in the inflow direction.
- the introduced refrigerant is replaced with the back side and the near side, respectively, and led out to the third header 1043.
- the superheat zone S1 is a superheat zone that occurs in the second group G2 and the fourth group G4 of the plurality of refrigerant tubes 45 due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low. As shown in FIG.
- a single regenerator container 47 is joined to both the second group G2 in which the superheat zone S1 is generated and the third group G3 in which the superheat zone S1 is not generated. Can be realized. Similarly, it is possible to realize a structure in which a single regenerator container 47 is joined to both the first group G1 where the superheat zone S1 does not occur and the fourth group G4 where the superheat zone S1 occurs.
- the first group G1 and the third group G3 A refrigerant flow having a relatively high flow rate can be provided over the entire area in the inflow direction via the refrigerant pipe 45. That is, the refrigerant can be satisfactorily flowed to the back side in the inflow direction even when the refrigerant has a low flow rate.
- the single cool storage material container 47 is joined to two refrigerant pipes 45 arranged in parallel in the flow direction, and a refrigerant having a relatively high flow rate flows through one of these refrigerant pipes 45. Thereby, even if the overheating region S1 occurs in the other of the two refrigerant tubes 45 to which the regenerator container 47 is joined, the cold energy in the non-overheating region can be transmitted to the regenerator material 50 in the overheating region S1.
- the cool storage material 50 in the cool storage material container 47 can be cooled well.
- the refrigerant pipe 45 in which the superheat zone S1 is generated and the refrigerant pipe in which no superheat zone is generated are obtained by changing the position of the refrigerant inflow direction in the second header tank 52 by the refrigerant flow of the replacement flow method.
- the refrigerant passage structure 1045 is characterized in that a single cold storage material container 47 is joined to both of them.
- the refrigerant passage structure 1045 functions as a “heat transfer suppression unit” that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow of the refrigerant passage when the flow rate of the refrigerant is low.
- the evaporator 1040 as the cold storage heat exchanger of the seventh embodiment is less susceptible to the influence of the superheat zone S1 even when the superheat zone S1 exists, and can secure the cold storage performance.
- the surface of the cold storage material container 47 may be uneven, and the protrusion may be joined to the refrigerant pipe 45.
- the refrigerant passage structure 1045 having one set of refrigerant flow in the inflow direction of the refrigerant in the second header tank 52 is illustrated as an example.
- Other configurations may be used as long as they include a replacement flow type refrigerant passage.
- the evaporator 1040A shown in FIG. 39 and FIG. 40 uses a pair of replacement flow methods and a conventional two-turn method in combination.
- the evaporator 1040B shown in FIG. 41 and FIG. 42 is provided along the inflow direction in which two sets of refrigerant passages of a replacement flow method are used in combination.
- a plurality of replacement flow-type refrigerant passages can be provided along the inflow direction.
- the structure of the refrigerant passages of the evaporator 1040A and the evaporator 1040B can also realize the same structure as the refrigerant passage structure 1045 of the seventh embodiment, and thus the same effects as the evaporator 1040 of the seventh embodiment can be achieved. it can.
- the eighth embodiment will be described with reference to FIGS. 43 to 45.
- the evaporator 1140 according to the eighth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 generated due to uneven flow of the refrigerant passage when the refrigerant is at a low flow rate. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the inner fin 1147b in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS.
- the inner fin 1147b is not in contact with the superheat zone S1.
- the evaporator 1040 of the seventh embodiment Different from the evaporator 1040 of the seventh embodiment.
- Inner fins 1147b are arranged so as to extend along the longitudinal direction (height direction) of the cool storage material container 1147 inside the cool storage material container 1147.
- Inner fin 1147b is an inner wall of regenerator container 1147 at the portion where refrigerant storage container 1147 joins second group G2 and fourth group G4 of refrigerant pipe 45 where superheat zone S1 occurs (cross section B7-B7 in FIG. 43). Not joined with. Further, in the portion where the first group G1 and third group G3 of the refrigerant pipe 45 where the superheat zone S1 does not occur and the cool storage material container 1147 contact (cross section A7-A7 in FIG. 43), the inner wall of the cool storage material container 1147 is joined. Is done.
- This inner fin 1147b functions as a heat transfer suppression unit.
- the evaporator 1140 of the eighth embodiment has the same effects as those of the seventh embodiment. Moreover, since the inner fin 1147b is not in contact with the cold storage material container 1147 in the superheat zone S1, the heat in the superheat zone S1 is not easily transmitted to the cold storage material 50 in the cold storage material vessel 1147. For this reason, the cool storage material inside the cool storage material container 1147 can be more suitably cooled by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
- the joining structure of the inner fin 1147b and the cool storage material container 1147 of the eighth embodiment is not limited to the above, and the heat transfer amount from the refrigerant pipe 45 to the cool storage material 50 through the inner fin 1147b in the superheat region S1 is superheated.
- Other configurations may be used as long as they are relatively smaller than the heat transfer amount other than the region S1.
- it is only necessary that the heat transfer performance of the inner fin 1147b in the superheat region S1 can be made relatively lower than other portions.
- the inner fin 1171 b is joined to the inner wall surface of the outer shell 1147 a of the regenerator container 1147 at a portion where the inner fin 1171 b is in contact with the superheated region S 1 of the refrigerant pipe 45. It can be set as the structure joined so that a rate may be relatively low, and in the part which contacts except the overheating area S1 of the refrigerant
- the ridges and valleys of the inner fins 1147b are not joined to the inner wall surface of the outer shell 1147a of the regenerator container 1147 along the flow direction, and are not joined to the superheat region of the refrigerant tube 45. Those in contact with other than S1 are joined to the inner wall surface. Even in this configuration, heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 can be suppressed, and the same effect as the evaporator 1140 of the present embodiment can be obtained.
- FIG. The evaporator 1240 according to the ninth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow rate of the refrigerant passage when the flow rate of the refrigerant is low. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the cool storage material container 1247 in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS.
- the regenerator container 1247 that is in contact with the superheat zone S1 (the leeward side rear side, the windward front side) is not joined to the refrigerant pipe 45 that generates the superheat zone S1.
- the evaporator 1240 of 9th Embodiment differs from the evaporator 1040 of 7th Embodiment by the point which does not provide an inner fin in the inside of the cool storage material container 1247.
- the regenerator container 1247 has a refrigerant in a portion (cross section B8-B8 in FIG. 46, region 1247c) in contact with the second group G2 and the fourth group G4 of the refrigerant pipe 45 in which the superheat zone S1 is generated. It is not joined to the pipe 45 and is formed at a distance from the refrigerant pipe 45. Further, the refrigerant pipe 45 is joined to the refrigerant pipe 45 at a portion (cross section A8-A8 in FIG. 46, outer shell 1247a) of the refrigerant pipe 45 that does not generate the superheat zone S1 and is in contact with the first group G1 and the third group G3.
- This cool storage material container 1247 functions as a heat transfer suppression unit.
- the evaporator 1240 of the ninth embodiment has the same effects as those of the seventh embodiment. Further, since the regenerator container 1247 is not in contact with the refrigerant pipe 45 in the overheat region S1, the heat in the overheat region S1 is not easily transmitted to the regenerator material 50 in the regenerator container 1247. For this reason, the cool storage material 50 inside the cool storage material container 1247 can be cooled more suitably by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
- the shape of the cool storage material container 1247 of 9th Embodiment is not limited to the above thing,
- tube 45 in the superheat zone S1 to the cool storage material 50 via the cool storage material container 1247 is superheat zone S1.
- Any other configuration may be used as long as it is relatively smaller than the heat transfer amount.
- the heat transfer performance of the cool storage material container 1247 in the superheat region S1 only needs to be relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG.
- the joining rate with the refrigerant tube 45 is It is configured to be joined so as to be relatively low, and to be joined so that the joining ratio with the refrigerant pipe 45 is relatively high in a portion (outer shell 1247a) in contact with the refrigerant pipe 45 other than the superheated region S1. it can.
- the refrigerant in the superheat zone S1 can be obtained by relatively reducing the heat transfer amount of the cold storage material container 1247 in the superheat zone S1 or by relatively reducing the joining rate between the cool storage material vessel 1247 and the refrigerant pipe 45. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1240 of this embodiment can be obtained.
- the tenth embodiment will be described with reference to FIGS. 49 to 51.
- the evaporator 1340 of the tenth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow of the refrigerant passage when the refrigerant is at a low flow rate. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the cool storage material container 1247 in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS.
- the regenerator container 1247 that is in contact with the superheat zone S1 (the leeward side rear side, the windward front side) is not joined to the refrigerant pipe 45 that generates the superheat zone S1. This differs from the evaporator 1040 of the seventh embodiment.
- the inner fin 1347b is arranged so as to extend along the longitudinal direction (height direction) of the cold storage material container 1347 inside the cold storage material container 1347, and the inner wall of the cold storage material container 1347 and the entire area in the longitudinal direction. Are joined.
- the regenerator container 1347 is not joined to the refrigerant pipe 45 at a portion (cross section B9-B9 in FIG. 49, region 1347c) of the refrigerant pipe 45 where the superheated area S1 is in contact with the second group G2 and the fourth group G4. It is formed at a distance from the refrigerant pipe 45.
- the refrigerant pipe 45 is joined to the refrigerant pipe 45 at a portion (cross section A9-A9 in FIG. 49, outer shell 1347a) of the refrigerant pipe 45 that does not generate the superheat zone S1 and is in contact with the first group G1 and the third group G3.
- This cool storage material container 1347 functions as a heat transfer suppression unit.
- the evaporator 1340 of the tenth embodiment has the same effects as those of the seventh embodiment. Further, since the regenerator material container 1347 is not in contact with the refrigerant pipe 45 in the overheat region S1, the heat in the overheat region S1 is not easily transmitted to the regenerator material 50 in the regenerator material container 1347. Moreover, since the inner fin 1347b is provided in the inside of the cool storage material container 1347, it is easy to convey the cold on the non-superheated side to the superheated region side. For this reason, the cool storage material 50 inside the cool storage material container 1347 can be more suitably cooled by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
- the inner fin 1347b includes the second group G2 and the fourth group G4 of the refrigerant pipe 45 in which the superheat zone S1 is generated and the cold storage material container 1347. It is good also as a structure which is not joined with the inner wall of the cool storage material container 1347 in the part (area
- the shape of the cool storage material container 1347 of 10th Embodiment is not limited to the said thing,
- tube 45 in the superheat zone S1 to the cool storage material 50 via the cool storage material container 1247 is superheat zone S1.
- Any other configuration may be used as long as it is relatively smaller than the heat transfer amount.
- the heat transfer performance of the cool storage material container 1347 in the superheat region S1 only needs to be relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG.
- the joint ratio with the refrigerant pipe 45 in the portion (region 1347 c) where the cold storage material container 21347 is in contact with the superheated area S ⁇ b> 1 of the refrigerant pipe 45. are connected so as to be relatively low, and in a portion (outer shell 1347a) in contact with the refrigerant pipe 45 other than the superheated region S1, the joining ratio with the refrigerant pipe 45 is relatively high. Can do.
- the refrigerant in the superheat zone S1 can be obtained by relatively reducing the heat transfer amount of the cold storage material container 1347 in the superheat zone S1 or by relatively reducing the joining rate between the cool storage material vessel 1347 and the refrigerant pipe 45. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1340 of this embodiment can be obtained.
- FIG. A configuration similar to that described with reference to the first embodiment can be applied.
- the inner fin 1347b is joined so that the joining ratio with the inner wall surface of the outer shell 1347a of the regenerator container 1347 is relatively low at the portion where the inner fin 1347b is in contact with the superheated region S1 of the refrigerant tube 45. It can be set as the structure joined so that a joining rate with an inner wall surface may become relatively high in the part which contacts other than superheat zone S1.
- the heat transfer from the refrigerant pipe 45 to the cool storage material 50 in the superheated region S1 can be suppressed by relatively reducing the joining rate between the inner fins 1347b and the cool storage material container 1347, and the evaporator according to the present embodiment.
- the same effect as 1340 is obtained.
- the eleventh embodiment will be described with reference to FIG.
- the evaporator 1440 according to the eleventh embodiment includes other portions (the first group in the present embodiment) that are in contact with the second group G2 and the fourth group G4 where the superheat zone S1 is generated, among the plurality of refrigerant tubes 45.
- the high melting point regenerator material 50A having a relatively high melting point compared to G1) is arranged, and further, the high melting point regenerator material 50A is also arranged in the portion that contacts the third group G3 where the superheat zone S2 is generated. This differs from the evaporator 1040 of the seventh embodiment (see FIGS. 33 to 35).
- the refrigerant flow structure 1045 of the replacement flow type in the second group G2 and the fourth group G4 of the plurality of refrigerant pipes 45 due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low.
- An overheating zone S1 occurs.
- the superheat zone S2 is generated by the same mechanism as the superheat zone S of the first to sixth embodiments.
- a high-melting-point regenerator is provided inside the regenerator container 47 in contact with the refrigerant tubes 45 (that is, the second group G2, the third group G3, and the fourth group G4) in which these superheat zones S1 and S2 are generated.
- the material 50A is accommodated.
- the regenerator container 47 that contacts both the first group G1 and the fourth group G4 of the refrigerant pipe 45 is in contact with the first group G1 (half of the leeward side in the flow direction).
- Is filled with a normal regenerator material 50 Is filled with a normal regenerator material 50
- a portion (half of the windward side in the flow direction) in contact with the fourth group G4 is filled with a high-melting regenerator material 50A.
- Such a configuration can be realized, for example, by incorporating a partition plate at a substantially intermediate position in the flow direction of the cool storage material container 47 and partitioning the internal space of the single cool storage material container 47.
- the entire internal space may be simply filled with the high melting point regenerator material 50A.
- the temperature difference from the refrigerant that cools the regenerator material increases, so the regenerator material becomes easier to cool (is more likely to solidify).
- the temperature of the refrigerant in the normal region of the refrigerant pipe 45 is ⁇ 3 ° C.
- the temperature of the refrigerant in the superheated areas S1 and S2 of the refrigerant pipe 45 is 0 ° C.
- a cold storage material that exchanges heat with the refrigerant in the normal region of the refrigerant pipe 45 is used.
- the melting point is assumed to be 5 ° C.
- the melting point of the regenerator material that exchanges heat with the refrigerant in the superheat regions S1 and S2 of the refrigerant pipe 45 is the same as the melting point of the regenerator material in the normal region, the regenerator material is relatively in the overheat regions S1 and S2. It becomes difficult to solidify, and the solidification property of the regenerator material in the superheat regions S1 and S2 is lower than the normal region.
- the melting point of the regenerator material in the superheat regions S1 and S2 is set higher than the melting point of the regenerator material in the normal region by the temperature difference (here, + 3 ° C.) between the refrigerant in the normal region and the superheat regions S1 and S2.
- the solidification property of the regenerator material in the superheat regions S1 and S2 is equivalent to that in the normal region.
- the melting point of the regenerator material in the superheat regions S1 and S2 is higher than the temperature difference between the refrigerant in the normal region and the superheat regions S1 and S2 with respect to the melting point of the regenerator material in the normal region, the regenerator in the superheat regions S1 and S2 The solidification of the material is improved over the normal range.
- the evaporator 1440 of the eleventh embodiment exchanges heat with the regenerator material by arranging the high-melting-point regenerator material 50A in the portion that contacts the refrigerant pipe 45 where the superheat zones S1 and S2 are generated.
- the solidification of the regenerator material can be made uniform without depending on whether the refrigerant is in the superheated region S1, S2 or the normal region. Thereby, it can make it difficult to receive to the influence of overheating region S1, S2, and can improve the thermal storage / radiation performance of the evaporator 1440.
- the high-melting-point regenerator material 50A is filled in the entire height direction of the regenerator container 47 in contact with the third group G3 of the refrigerant pipe 45 in which the superheat zone S2 is generated.
- the configuration has been illustrated, at least a portion in contact with the superheated region S2 may be the high melting point regenerator material 50A.
- it is good also as a structure which accommodates 50 A of high melting-point regenerator materials only in the part which contacts the vicinity of the exit side channel
- a partition plate is built in along a portion (for example, a quarter region on the windward side in the flow direction and on the upper side in the height direction) that overlaps the superheat region S2 of the cold storage material container 47. This can be realized by dividing the internal space of one cold storage material container 47.
- the twelfth embodiment will be described with reference to FIG.
- the evaporator 1540 of the twelfth embodiment is that the high-melting-point regenerator material 50A is disposed in a portion of the plurality of refrigerant tubes 45 that comes into contact with the second group G2 and the fourth group G4 where the superheat zone S1 is generated.
- the evaporator 1040 of the seventh embodiment see FIGS. 33 to 35.
- the high melting point regenerator material 50A is not disposed in the portion that contacts the third group G3 where the overheated region S2 is generated.
- the regenerator container 47 in contact with both the second group G2 and the third group G3 of the refrigerant pipe 45 is, as shown in FIG. 53, a portion in contact with the third group G3 (half of the windward side in the flow direction). ) Is filled with the normal melting point regenerator material 50, and the portion (half on the leeward side in the flow direction) in contact with the second group G2 is filled with the high melting point regenerator material 50A.
- tube 45 is the same as that of the 11th Embodiment demonstrated with reference to FIG.
- the evaporator 1540 of the twelfth embodiment has a configuration in which the high melting point regenerator material 50A is disposed in a portion that contacts the refrigerant pipe 45 in which the superheat zone S1 is generated.
- the solidification property of the regenerator material can be made uniform without depending on whether the refrigerant that exchanges heat with the regenerator material is the superheat region S1 or the normal region. Thereby, it can be made hard to receive the influence of overheating region S1, and there can exist an effect that the heat storage and heat dissipation performance can be improved.
- each of the two types of refrigerating material having the melting points has the same freezing method, and as a result, it is possible to make the blow-off temperature distribution uniform during heat dissipation.
- the thirteenth embodiment will be described with reference to FIG.
- the evaporator 1640 of the thirteenth embodiment differs from the evaporator 40 of the first embodiment in that the portion of the regenerator material in contact with the superheat zone S is the high melting point regenerator material 50A.
- the superheated area S is generated by the evaporation of.
- the high-melting-point regenerator material 50A is accommodated in the regenerator container 47 that comes into contact with the refrigerant pipe 45 (that is, the fourth group G4) in which the superheat zone S is generated.
- At least a portion of the regenerator material in contact with the superheat region S may be the high melting point regenerator material 50A.
- the high melting point regenerator material 50A is the first refrigerating pipe 45 in the superheat region S.
- the structure filled up in the whole height direction of the cool storage material container 47 which contacts the 4th group G4 may be sufficient, and the structure filled only in the part which contacts the superheat zone S may be sufficient.
- the evaporator 1640 of the thirteenth embodiment has a configuration in which the high melting point regenerator material 50A is arranged in a portion that contacts the refrigerant pipe 45 where the superheat zone S is generated, similarly to the evaporator 1440 of the eleventh embodiment. Therefore, in the four-turn type refrigerant passage structure, whether the refrigerant that exchanges heat with the cold storage material is in the superheated region S or the normal region, as in the refrigerant flow structure 1045 of the replacement flow type in the eleventh embodiment.
- the solidification property of the regenerator material can be made uniform without depending on. Thereby, it can be made hard to receive the influence of the superheat zone S, and there can exist an effect that the heat storage and heat dissipation performance can be improved.
- the configuration of the thirteenth embodiment can also be applied to the other second to sixth embodiments related to the four-turn refrigerant passage structure.
- the fourteenth embodiment will be described with reference to FIG.
- the evaporator 1740 of the fourteenth embodiment is provided with a pair of partition plates 47d that divide the internal space along the longitudinal direction (that is, the height direction) that is the direction in which the refrigerant pipe 45 extends, inside the cold storage material container 47. This is different from the above embodiments.
- one of the pair of partition plates 47d (the right side plate in FIG. 55) is an end portion on one side of the cold storage material container 47 in the longitudinal direction (the lower side in the height direction in FIG. 55). Have gaps.
- the other of the pair of partition plates 47d (the left plate in FIG. 55) has a gap at the end of the other side in the longitudinal direction of the cold storage material container 47 (the upper side in the height direction in FIG. 55).
- the partition plates 47d are arranged at substantially equal intervals along the flow direction.
- the cool storage material container 47 is equipped with the cool storage material enclosure pipe 47e in the side wall close
- the cool storage material 50 is enclosed inside via the cool storage material sealing pipe 47e.
- the internal space is not filled with the cool storage material 50 as a countermeasure against freezing and expansion, and the cool storage material container 47 is filled.
- a gap of about 15% is provided on the upper side of the inside.
- a space having a height of about C1 remains at the upper end of the internal space.
- the superheat regions S and S2 described in the above embodiment are mainly generated on the upper side in the height direction of the refrigerant pipe 45. For this reason, in the conventional configuration, the upper side in the height direction of the cold storage material container 47 is difficult to cool, and there is a possibility that a cooling failure may occur.
- the internal space of the cold storage material container 47 is divided into three by a pair of partition plates 47d, and the divided regions are connected in series. For this reason, when the cool storage material 50 is injected so as to provide a gap of about 15% as a measure against freezing and expansion, a space 47f is created only in the region where the cool storage material sealing pipe 47e communicates, as shown in FIG. In the two regions on the back side, the regenerator material 50 is filled over the entire region in the height direction.
- the height c2 from the upper end is larger than the conventional height c1, but if the entire internal space of the cool storage material container 47 is viewed, there is a position where the cool storage material 50 does not exist in the height direction. No longer.
- the cool storage material 50 is disposed over the entire region in the height direction. Thereby, it can prevent that a clearance gap is made in the upper end in the cool storage material container 47, and the cooling remaining part of the height direction upper side of the cool storage material container 47 can be eliminated.
- At least one pair of the pair of partition plates 47d may be provided inside the cold storage material container 47, and a plurality of pairs of partition plates may be provided.
- the fifteenth embodiment will be described with reference to FIG.
- the cold storage material container 47 joined to the refrigerant pipe 45 in which the superheat zone S is generated is not provided in the portion of the refrigerant pipe 45 that contacts the superheat zone S. It differs from the evaporator 40 of 1st Embodiment by the point provided only in the part which contacts except the superheat zone S.
- FIG. 1st Embodiment differs from the evaporator 40 of 1st Embodiment by the point provided only in the part which contacts except the superheat zone S.
- the superheated area S is generated by the evaporation of.
- the refrigerant tube 45 in which the superheat zone S is generated that is, the cold storage container 47 that is in contact with the refrigerant tube 45 of the fourth group G4, is a region in which the superheat zone S is generated ( It is not arranged in the vicinity of the outlet of the refrigerant passage.
- the evaporator 1840 of the fifteenth embodiment can divide the heat exchange between the refrigerant in the superheat zone S and the cold storage material 50, and can improve the cooling efficiency.
- the solidification of the regenerator material 50 is promoted, and the cooling time is made longer than that of the conventional product, so that the off time of the air conditioner can be increased when the vehicle on which the evaporator 1840 is mounted is idled.
- the configuration of the fifteenth embodiment can also be applied to the other second to sixth embodiments related to the four-turn type refrigerant passage structure.
- the method for reducing the influence of cold storage due to the superheat zones S and S2 generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage is the seventh to tenth embodiments. It is also possible to combine with the structure of.
- the regenerator material container 47 is disposed between the two refrigerant tubes 45, joined to the two refrigerant tubes 45, and opposite to the regenerator material container 47 in each refrigerant tube 45.
- the configuration in which the air passage 53 is provided is illustrated, the configuration is not limited to this configuration.
- the refrigerant pipe 45 and the cold storage material container 47 may be formed as an integral member so as to extend in the same direction, and the air passage 53 may be provided in a gap between these members.
- the configuration in which the cold storage material 50 is accommodated in the cold storage material container 47 is illustrated, but is not limited thereto.
- a configuration in which the regenerator material 50 is not accommodated in the regenerator material container 47 and is in direct contact with the refrigerant tube 45 a configuration in which heat transfer from the refrigerant tube 45 to the regenerator material 50 can be performed directly.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air-Conditioning For Vehicles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
An evaporator (40) as a cold storage heat exchanger comprises: a plurality of refrigerant pipes (45) that are arranged by being spaced from one another and that each have a refrigerant passage through which a refrigerant circulates; a cold storage material (50) adjacent to the plurality of refrigerant pipes (45); and an inner fin (47b) that serves as a heat transmission inhibiting section that inhibits heat transmission from the refrigerant pipes (45) to the cold storage material (50) in a refrigerant overheating region (S) created in the refrigerant passage.
Description
本出願は、2015年10月1日に出願された日本国特許出願2015-195818号と、2016年9月6日に出願された日本国特許出願2016-173410号と、に基づくものであって、その優先権の利益を主張するものであり、その特許出願の全ての内容が、参照により本明細書に組み込まれる。
This application is based on Japanese Patent Application No. 2015-195818 filed on October 1, 2015 and Japanese Patent Application No. 2016-173410 filed on September 6, 2016. Claims the benefit of that priority, the entire contents of which are incorporated herein by reference.
本開示は、冷媒を圧縮吐出する圧縮機、高温となった冷媒を冷却する放熱器、及び冷却された冷媒を減圧する減圧器と共に冷凍サイクル装置を構成し、冷媒を蒸発させる蓄冷熱交換器に関する。
The present disclosure relates to a compressor that compresses and discharges a refrigerant, a radiator that cools a refrigerant that has reached a high temperature, and a refrigerating heat exchanger that forms a refrigeration cycle apparatus together with a decompressor that decompresses the cooled refrigerant and evaporates the refrigerant. .
従来、空調装置には、冷凍サイクル装置が用いられている。この冷凍サイクル装置が停止している状態においても、限定された冷房を提供する試みがなされている。例えば、車両用空調装置では、走行用エンジンによって冷凍サイクル装置が駆動される。このため、車両が一時的に停車している間に、エンジンが停止すると、冷凍サイクル装置が停止する。このような一時的な停車中に、限定された冷房を提供するために、冷凍サイクル装置の蒸発器に蓄冷材を付加した蓄冷熱交換器が提案されている。例えば、特許文献1に記載の蓄冷熱交換器が知られている。
Conventionally, a refrigeration cycle apparatus is used as an air conditioner. Attempts have been made to provide limited cooling even when the refrigeration cycle apparatus is stopped. For example, in a vehicle air conditioner, a refrigeration cycle apparatus is driven by a traveling engine. For this reason, if the engine stops while the vehicle is temporarily stopped, the refrigeration cycle apparatus stops. In order to provide limited cooling during such a temporary stop, a cold storage heat exchanger in which a cold storage material is added to the evaporator of the refrigeration cycle apparatus has been proposed. For example, a cold storage heat exchanger described in Patent Document 1 is known.
ここで、一般に冷凍サイクル装置では、蓄冷熱交換器よりも冷媒の流れの下流側に、冷媒を圧縮吐出するための圧縮機が存在する。圧縮機に液状の冷媒が戻ると故障の原因となるため、一般的に蓄冷熱交換器の出口では冷媒を完全に蒸発させる必要がある。蓄冷熱交換器において、冷媒通路の出口近傍では冷媒がガス単層になり、圧力が飽和蒸気圧を超えることに起因して、冷媒温度が急激に高温に遷移する部分、いわゆる過熱域が存在する。また、冷媒の流量が低いときには、蓄冷熱交換器内の冷媒通路の配置によって冷媒の流れ方が不均衡となり、冷媒が流れにくい部分に過熱域が発生する場合がある。このように、蓄冷熱交換器には冷媒通路上のいずれかの箇所に過熱域が存在する場合がある。
Here, in general, in the refrigeration cycle apparatus, a compressor for compressing and discharging the refrigerant is present on the downstream side of the refrigerant flow with respect to the cold storage heat exchanger. When the liquid refrigerant returns to the compressor, it causes a failure, and therefore it is generally necessary to completely evaporate the refrigerant at the outlet of the cold storage heat exchanger. In the regenerative heat exchanger, there is a so-called superheat zone where the refrigerant temperature rapidly changes to a high temperature due to the refrigerant becoming a gas monolayer near the outlet of the refrigerant passage and the pressure exceeding the saturated vapor pressure. . In addition, when the flow rate of the refrigerant is low, the refrigerant flow may become unbalanced due to the arrangement of the refrigerant passage in the cold storage heat exchanger, and an overheated area may be generated in a portion where the refrigerant is difficult to flow. As described above, the regenerative heat exchanger may have an overheat zone at any location on the refrigerant passage.
特許文献1に記載の従来の蓄冷熱交換器では、蓄冷材は冷媒通路を構成する冷媒管と隣接して配置され、冷媒管を流れる冷媒によって冷却されるのが一般的である。発明者の詳細な検討の結果、冷媒管上に過熱域が発生する場合には、過熱域の冷媒温度が高温となるため、過熱域の影響により蓄冷材が冷えにくくなり、蓄冷熱交換器の蓄冷性能が低下する虞があるという課題が見出された。
In the conventional cold storage heat exchanger described in Patent Document 1, it is general that the cold storage material is disposed adjacent to the refrigerant pipe constituting the refrigerant passage and is cooled by the refrigerant flowing through the refrigerant pipe. As a result of detailed investigations by the inventor, when the overheated area is generated on the refrigerant pipe, the refrigerant temperature in the overheated area becomes high. The subject that cold storage performance might fall was discovered.
本開示は、過熱域が存在する場合でも、過熱域の影響を受けにくくし、蓄冷性能を確保できる蓄冷熱交換器を提供することを目的とする。
This disclosure is intended to provide a cold storage heat exchanger that is less susceptible to the influence of the overheating region and can secure the cold storage performance even when the overheating region exists.
本開示の一態様に係る蓄冷熱交換器は、冷媒を流通させる冷媒通路を有し、互いに間隔をあけて配置される複数の冷媒管と、前記複数の冷媒管と隣接する蓄冷材と、前記冷媒通路にて発生する前記冷媒の過熱域における前記冷媒管から前記蓄冷材への熱伝達を抑制する熱伝達抑制部と、を備える。
A cold storage heat exchanger according to an aspect of the present disclosure includes a refrigerant passage through which a refrigerant is circulated, a plurality of refrigerant tubes arranged at intervals from each other, a cold storage material adjacent to the plurality of refrigerant tubes, A heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe to the cold storage material in an overheated region of the refrigerant generated in the refrigerant passage.
この構成により、冷媒通路にて発生する冷媒の過熱域における冷媒管から蓄冷材への熱伝達を抑制することができるので、冷媒温度が高温となる過熱域の影響により蓄冷材が冷えにくくなる状況を回避できる。この結果、過熱域が存在する場合でも、過熱域の影響を受けにくくし、蓄冷性能を確保できる。
This configuration can suppress heat transfer from the refrigerant pipe to the regenerator material in the overheated region of the refrigerant generated in the refrigerant passage, so that the regenerator material is less likely to cool due to the influence of the overheated region where the refrigerant temperature becomes high. Can be avoided. As a result, even when the overheated region exists, it is difficult to be affected by the overheated region, and the cold storage performance can be secured.
本開示によれば、過熱域が存在する場合でも、過熱域の影響を受けにくくし、蓄冷性能を確保できる蓄冷熱交換器を提供することができる。
According to the present disclosure, it is possible to provide a cold storage heat exchanger that is less susceptible to the influence of the overheating area and can secure the cold storage performance even when the overheating area exists.
以下、添付図面を参照しながら本実施形態について説明する。説明の理解を容易にするため、各図面において同一の構成要素に対しては可能な限り同一の符号を付して、重複する説明は省略する。
Hereinafter, the present embodiment will be described with reference to the accompanying drawings. In order to facilitate the understanding of the description, the same constituent elements in the drawings will be denoted by the same reference numerals as much as possible, and redundant description will be omitted.
[第1実施形態]
図1~10を参照して第1実施形態を説明する。冷凍サイクル装置1は、車両用の空調装置に用いられる。図1に示すように、冷凍サイクル装置1は、圧縮機10、放熱器20、減圧器30、および蒸発器40を有する。これら構成部品は、配管によって環状に接続され、冷媒循環路を構成する。この冷凍サイクル装置1において、第1実施形態に係る蓄冷熱交換器は蒸発器40として適用される。以下の説明では本実施形態に係る蓄冷熱交換器40を「蒸発器40」とも表記する。 [First Embodiment]
The first embodiment will be described with reference to FIGS. Therefrigeration cycle apparatus 1 is used in a vehicle air conditioner. As shown in FIG. 1, the refrigeration cycle apparatus 1 includes a compressor 10, a radiator 20, a decompressor 30, and an evaporator 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path. In the refrigeration cycle apparatus 1, the cold storage heat exchanger according to the first embodiment is applied as the evaporator 40. In the following description, the cold storage heat exchanger 40 according to the present embodiment is also expressed as “evaporator 40”.
図1~10を参照して第1実施形態を説明する。冷凍サイクル装置1は、車両用の空調装置に用いられる。図1に示すように、冷凍サイクル装置1は、圧縮機10、放熱器20、減圧器30、および蒸発器40を有する。これら構成部品は、配管によって環状に接続され、冷媒循環路を構成する。この冷凍サイクル装置1において、第1実施形態に係る蓄冷熱交換器は蒸発器40として適用される。以下の説明では本実施形態に係る蓄冷熱交換器40を「蒸発器40」とも表記する。 [First Embodiment]
The first embodiment will be described with reference to FIGS. The
圧縮機10は、車両の走行用の動力源2である内燃機関によって駆動される。このため、動力源2が停止すると、圧縮機10も停止する。圧縮機10は、蒸発器40から冷媒を吸引し、圧縮し、放熱器20へ吐出する。
The compressor 10 is driven by an internal combustion engine that is a power source 2 for traveling the vehicle. For this reason, when the power source 2 stops, the compressor 10 also stops. The compressor 10 sucks the refrigerant from the evaporator 40, compresses it, and discharges it to the radiator 20.
放熱器20は、高温冷媒を冷却する。放熱器20は、凝縮器とも呼ばれる。減圧器30は、放熱器20によって冷却された冷媒を減圧する。減圧器30は、固定の絞り、温度式膨張弁、あるいはエジェクタによって提供されうる。
The heat radiator 20 cools the high-temperature refrigerant. The radiator 20 is also called a condenser. The decompressor 30 decompresses the refrigerant cooled by the radiator 20. The decompressor 30 can be provided by a fixed throttle, a temperature expansion valve, or an ejector.
蒸発器40は、減圧器30によって減圧された冷媒を蒸発させ、媒体を冷却する。蒸発器40は、車室に供給される空気を冷却する。冷凍サイクル装置1は、さらに、高圧側液冷媒と低圧側ガス冷媒とを熱交換する内部熱交換、余剰冷媒を蓄えるレシーバまたはアキュムレータのタンク要素を備えることができる。また、動力源2は、内燃機関あるいは電動機によって提供されうる。
The evaporator 40 evaporates the refrigerant decompressed by the decompressor 30 and cools the medium. The evaporator 40 cools the air supplied to the passenger compartment. The refrigeration cycle apparatus 1 can further include an internal heat exchange for exchanging heat between the high-pressure side liquid refrigerant and the low-pressure side gas refrigerant, and a receiver or accumulator tank element that stores excess refrigerant. The power source 2 can be provided by an internal combustion engine or an electric motor.
図2~10を参照して、第1実施形態に係る蓄冷熱交換器としての蒸発器40の構成を説明する。以下の説明では、図2及び図3の紙面上の上下方向を「高さ方向」と表し、その上側を「上側」、下側を「下側」と表す。なお、高さ方向は典型的には重力方向であるが、他の方向でもよい。また、図2の紙面上の左右方向を、冷媒が流入する「流入方向」と表し、その右側を「手前側」と表し、左側を「奥側」と表す。図3の紙面上の左右方向を、空気が空気通路53を流れる「流れ方向」と表し、その左側を「風上側」、右側を「風下側」と表す。
2 to 10, the configuration of the evaporator 40 as a cold storage heat exchanger according to the first embodiment will be described. In the following description, the vertical direction on the paper surface of FIGS. 2 and 3 is represented as “the height direction”, the upper side thereof is represented as “upper side”, and the lower side is represented as “lower side”. The height direction is typically the gravitational direction, but may be another direction. Further, the right and left direction on the paper surface of FIG. 2 is represented as “inflow direction” in which the refrigerant flows, the right side thereof is represented as “front side”, and the left side is represented as “back side”. The left-right direction on the paper surface of FIG. 3 is represented as “flow direction” in which air flows through the air passage 53, the left side thereof is represented as “windward”, and the right side is represented as “leeward side”.
図2および図3において、蒸発器40は、複数に分岐した冷媒通路部材を有する。この冷媒通路部材は、アルミニウム等の金属製の通路部材によって提供される。冷媒通路部材は、組をなして位置づけられた第1ヘッダ41、第2ヘッダ42、第3ヘッダ43、第4ヘッダ44と、それらヘッダの間を連結する複数の冷媒管45とによって提供されている。第1ヘッダ41、第2ヘッダ42、第3ヘッダ43、第4ヘッダ44は、流入方向に沿って延在するよう配置されている。複数の冷媒管45は、流入方向と直交する高さ方向に沿って延在するよう配置されている。
2 and 3, the evaporator 40 has a refrigerant passage member branched into a plurality. The refrigerant passage member is provided by a metal passage member such as aluminum. The refrigerant passage member is provided by a first header 41, a second header 42, a third header 43, a fourth header 44, which are positioned in a pair, and a plurality of refrigerant pipes 45 connecting the headers. Yes. The first header 41, the second header 42, the third header 43, and the fourth header 44 are disposed so as to extend along the inflow direction. The plurality of refrigerant tubes 45 are arranged so as to extend along a height direction orthogonal to the inflow direction.
図2および図3において、第1ヘッダ41と第2ヘッダ42とは、組をなしており、互いに高さ方向に所定距離だけ離れて、流入方向に沿って平行に配置されている。第3ヘッダ43と第4ヘッダ44とも、組をなしており、互いに高さ方向に所定距離れて、流入方向に沿って平行に配置されている。第1ヘッダ41及び第3ヘッダ43は高さ方向の上側に配置され、第2ヘッダ42及び第4ヘッダ44は高さ方向の下側に配置されている。
2 and 3, the first header 41 and the second header 42 form a pair, and are arranged in parallel along the inflow direction, separated from each other by a predetermined distance in the height direction. The third header 43 and the fourth header 44 also form a pair and are arranged in parallel along the inflow direction with a predetermined distance from each other in the height direction. The first header 41 and the third header 43 are arranged on the upper side in the height direction, and the second header 42 and the fourth header 44 are arranged on the lower side in the height direction.
第1ヘッダ41と第2ヘッダ42との間には、複数の冷媒管45が等間隔に配列さている。各冷媒管45は、その一端部において対応する第1ヘッダ41、第2ヘッダ42内に連通している。これら第1ヘッダ41と、第2ヘッダ42と、それらの間に配置された複数の冷媒管45によって第1熱交換部48が形成されている。
A plurality of refrigerant tubes 45 are arranged at equal intervals between the first header 41 and the second header 42. Each refrigerant pipe 45 communicates with the corresponding first header 41 and second header 42 at one end thereof. A first heat exchanging portion 48 is formed by the first header 41, the second header 42, and a plurality of refrigerant tubes 45 arranged therebetween.
第3ヘッダ43と第4ヘッダ44との間には、複数の冷媒管45が等間隔に配列されている。各冷媒管45は、その他端部において対応する第3ヘッダ43、第4ヘッダ44内に連通している。これら第3ヘッダ43と、第4ヘッダ44と、それらの間に配置された複数の冷媒管45によって第2熱交換部49が形成されている。
A plurality of refrigerant tubes 45 are arranged at equal intervals between the third header 43 and the fourth header 44. Each refrigerant pipe 45 communicates with the corresponding third header 43 and fourth header 44 at the other end. A second heat exchanging portion 49 is formed by the third header 43, the fourth header 44, and a plurality of refrigerant tubes 45 arranged therebetween.
この結果、蒸発器40は、2層に配置された第1熱交換部48と第2熱交換部49とを有する。空気の流れ方向に関して、第2熱交換部49が風上側に配置され、第1熱交換部48が風下側に配置されている。また、複数の冷媒管45は、空気の流れ方向に沿って一対となるように、流入方向に沿って2列に配置されている。
As a result, the evaporator 40 has a first heat exchange part 48 and a second heat exchange part 49 arranged in two layers. Regarding the air flow direction, the second heat exchanging part 49 is arranged on the leeward side, and the first heat exchanging part 48 is arranged on the leeward side. Moreover, the some refrigerant | coolant pipe | tube 45 is arrange | positioned at 2 rows along the inflow direction so that it may become a pair along the flow direction of air.
第1ヘッダ41の端部(流入方向手前側の端部)には、冷媒入口としてのジョイントが設けられている。図4~6に示すように、第1ヘッダ41内は、その長さ方向(流入方向)のほぼ中央に設けられた仕切板によって、第1区画と第2区画とに区画されている。これに対応して、複数の冷媒管45は、第1区画に対応した第1群G1と、第2区画に対応した第2群G2とに区分されている。
A joint as a refrigerant inlet is provided at the end of the first header 41 (the end on the near side in the inflow direction). As shown in FIGS. 4 to 6, the inside of the first header 41 is partitioned into a first partition and a second partition by a partition plate provided at substantially the center in the length direction (inflow direction). Correspondingly, the plurality of refrigerant tubes 45 are divided into a first group G1 corresponding to the first section and a second group G2 corresponding to the second section.
冷媒は、第1ヘッダ41の第1区画に供給される。冷媒は、第1区画から、第1群G1に属する複数の冷媒管45に分配される。冷媒は、第1群G1を通して第2ヘッダ42に流入し、集合される。冷媒は、第2ヘッダ42から、第2群G2に属する複数の冷媒管45に再び分配される。冷媒は、第2群G2を通して第1ヘッダ41の第2区画に流入する。このように、第1熱交換部48においては、冷媒をU字状に流す流路が形成される。
The refrigerant is supplied to the first section of the first header 41. The refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the first group G1. The refrigerant flows into the second header 42 through the first group G1 and is collected. The refrigerant is distributed again from the second header 42 to the plurality of refrigerant tubes 45 belonging to the second group G2. The refrigerant flows into the second section of the first header 41 through the second group G2. Thus, in the 1st heat exchange part 48, the flow path which flows a refrigerant | coolant in a U shape is formed.
第3ヘッダ43の端部(本実施形態では流入方向手前側の端部だが、奥側端部でもよい)には、冷媒出口としてのジョイントが設けられている。図4~6に示すように、第3ヘッダ43内は、その長さ方向のほぼ中央に設けられた仕切板によって、第1区画と第2区画とに区画されている。第3ヘッダ43の第1区画は、第1ヘッダ41の第2区画に隣接している。第3ヘッダ43の第1区画と第1ヘッダ41の第2区画とは連通している。これに対応して、複数の冷媒管45は、第1区画に対応した第3群G3と、第2区画に対応した第4群G4とに区分されている。
A joint as a refrigerant outlet is provided at the end of the third header 43 (in this embodiment, the end on the near side in the inflow direction, but it may be the back end). As shown in FIGS. 4 to 6, the inside of the third header 43 is partitioned into a first partition and a second partition by a partition plate provided substantially at the center in the length direction. The first section of the third header 43 is adjacent to the second section of the first header 41. The first section of the third header 43 and the second section of the first header 41 are in communication. Correspondingly, the plurality of refrigerant tubes 45 are divided into a third group G3 corresponding to the first section and a fourth group G4 corresponding to the second section.
冷媒は、第1ヘッダ41の第2区画から、第3ヘッダ43の第1区画に流入する。冷媒は、第1区画から、第3群G3に属する複数の冷媒管45に分配される。冷媒は、第3群G3を通して第4ヘッダ44に流入し、集合される。冷媒は、第4ヘッダ44から、第4群G4に属する複数の冷媒管45に再び分配される。冷媒は、第4群G4を通して第3ヘッダ43の第2区画に流入する。このように、第2熱交換部49においては、冷媒をU字状に流す流路が形成される。第3ヘッダ43の第2区画内の冷媒は、冷媒出口から流出し、圧縮機10へ向けて流れる。
The refrigerant flows from the second section of the first header 41 into the first section of the third header 43. The refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the third group G3. The refrigerant flows into the fourth header 44 through the third group G3 and is collected. The refrigerant is distributed again from the fourth header 44 to the plurality of refrigerant tubes 45 belonging to the fourth group G4. The refrigerant flows into the second section of the third header 43 through the fourth group G4. Thus, in the 2nd heat exchange part 49, the flow path which flows a refrigerant | coolant in a U shape is formed. The refrigerant in the second section of the third header 43 flows out from the refrigerant outlet and flows toward the compressor 10.
本実施形態では、冷媒管45は、内部に複数の冷媒通路を有する多穴管である。冷媒管45は、扁平管とも呼ばれる。この多穴管は、押出製法や、板を折り曲げて形成する製法によって得ることができる。複数の冷媒通路は、冷媒管45の長手方向に沿って延びており、冷媒管45の両端に開口している。複数の冷媒管45は、列をなして並べられている。各列において、複数の冷媒管45は、その主面が対向するように配置されている。図8に示すように、複数の冷媒管45は、互いに隣接する2つの冷媒管45の間に、空気と熱交換するための空気通路53と、後述する蓄冷材容器47を収容するための収容部とを区画している。
In the present embodiment, the refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages therein. The refrigerant tube 45 is also called a flat tube. This multi-hole tube can be obtained by an extrusion manufacturing method or a manufacturing method in which a plate is bent. The plurality of refrigerant passages extend along the longitudinal direction of the refrigerant pipe 45 and open to both ends of the refrigerant pipe 45. The plurality of refrigerant tubes 45 are arranged in a row. In each row, the plurality of refrigerant tubes 45 are arranged so that their main surfaces face each other. As shown in FIG. 8, the plurality of refrigerant pipes 45 are accommodated between two adjacent refrigerant pipes 45 for accommodating an air passage 53 for exchanging heat with air and a cold storage material container 47 described later. The section is divided.
蒸発器40は、車室へ供給される空気と接触面積を増加させるためのフィン部材を備える。フィン部材は、複数のコルゲート型のフィン46によって提供されている。フィン46は、隣接する2つの冷媒管45の間に区画された空気通路53に配置されている。フィン46は、隣接する2つの冷媒管45と熱的に結合している。フィン46は、熱伝達に優れた接合材によって、隣接する2つの冷媒管45に接合されている。接合材としては、ろう材を用いることができる。フィン46は、薄いアルミニウム等の金属板が波状に曲げられた形状をもっており、ルーバーと呼ばれる空気通路を備える。
The evaporator 40 includes fin members for increasing the contact area with the air supplied to the passenger compartment. The fin member is provided by a plurality of corrugated fins 46. The fins 46 are disposed in an air passage 53 defined between two adjacent refrigerant tubes 45. The fin 46 is thermally coupled to the two adjacent refrigerant tubes 45. The fins 46 are joined to the two adjacent refrigerant tubes 45 by a joining material excellent in heat transfer. A brazing material can be used as the bonding material. The fin 46 has a shape in which a thin metal plate such as aluminum is bent in a wave shape, and includes an air passage called a louver.
蒸発器40は、さらに、複数の蓄冷材容器47を有している。蓄冷材容器47は、アルミニウム等の金属製である。蓄冷材容器47は、扁平な筒状である。蓄冷材容器47は、2枚の最中状のプレートを合わせることで内部に蓄冷材50を収容するための部屋を区画している。蓄冷材容器47は、広い主面を両面に有している。これら2つの主面を提供する2つの主壁は、それぞれが冷媒管45と平行に配置されている。蓄冷材容器47は、隣接する2つの冷媒管45の間に配置されている。
The evaporator 40 further has a plurality of cold storage material containers 47. The cold storage material container 47 is made of metal such as aluminum. The cold storage material container 47 has a flat cylindrical shape. The cool storage material container 47 divides a room for accommodating the cool storage material 50 inside by combining two middle plates. The cool storage material container 47 has a wide main surface on both surfaces. The two main walls that provide these two main surfaces are each arranged in parallel with the refrigerant pipe 45. The cool storage material container 47 is disposed between two adjacent refrigerant tubes 45.
蓄冷材容器47は、流入方向に沿って隣接する2つの冷媒管45の間に配置されている。蓄冷材容器47は、その両側に配置された2つの冷媒管45に熱的に結合している。蓄冷材容器47は、熱伝達に優れた接合材によって、隣接する2つの冷媒管45に接合されている。接合材としては、ろう材または接着剤などの樹脂材料を用いることができる。蓄冷材容器47は、冷媒管45にろう付けされている。蓄冷材容器47と冷媒管45との間には、それらの間を広い断面積によって連結するためにろう材が配置されている。このろう材は、ろう材をクラッドした材料を用いるか、または、蓄冷材容器47と冷媒管45との間にろう材の箔を配置することによって提供することができる。この結果、蓄冷材容器47は、冷媒管45との間で良好な熱伝導を示す。また、蓄冷材容器47の表面には凹凸があり、凸部が冷媒管45に接合されても良い。
The cold storage material container 47 is disposed between two refrigerant pipes 45 adjacent to each other along the inflow direction. The cool storage material container 47 is thermally coupled to two refrigerant tubes 45 disposed on both sides thereof. The cool storage material container 47 is joined to the two adjacent refrigerant pipes 45 by a joining material excellent in heat transfer. As the bonding material, a resin material such as a brazing material or an adhesive can be used. The cold storage material container 47 is brazed to the refrigerant pipe 45. A brazing material is disposed between the cold storage material container 47 and the refrigerant pipe 45 in order to connect them with a wide cross-sectional area. This brazing material can be provided by using a material clad with the brazing material or by arranging a brazing material foil between the cold storage material container 47 and the refrigerant pipe 45. As a result, the cool storage material container 47 exhibits good heat conduction with the refrigerant pipe 45. Further, the surface of the cold storage material container 47 may be uneven, and the protrusion may be joined to the refrigerant pipe 45.
図2,8において、複数の冷媒管45は、ほぼ一定の間隔で配置されている。それら複数の冷媒管45の間には、複数の隙間が形成されている。これら複数の隙間には、複数のフィン46と複数の蓄冷材容器47とが、所定の規則性をもって配置されている。なお、図2,8には、フィン46(空気通路53)が2個、蓄冷材容器47が1個の順で繰り返し配置される構成を例示しているが、これ以外の配置としてもよい。隙間のうちの一部は、空気通路53である。隙間のうちの残部は、収容部である。空気通路53にはフィン46が配置され、収容部には蓄冷材容器47が配置されている。蓄冷材容器47の両側に位置する2つの冷媒管45は、蓄冷材容器47とは反対側において空気と熱交換するための空気通路を区画している。別の観点では、2つのフィン46の間に2つの冷媒管45が配置され、さらにこれら2つの冷媒管45の間にひとつの蓄冷材容器47が配置されている。蓄冷材容器47が2つの冷媒管45の間に配置されることにより、フィン46を流れる空気の熱負荷を受けずに冷媒の熱を蓄冷材50に伝えることができるため、蓄冷効率が良くなる。
2 and 8, the plurality of refrigerant tubes 45 are arranged at substantially constant intervals. A plurality of gaps are formed between the plurality of refrigerant tubes 45. In the plurality of gaps, a plurality of fins 46 and a plurality of cool storage material containers 47 are arranged with a predetermined regularity. 2 and 8 exemplify a configuration in which two fins 46 (air passages 53) and one cold storage material container 47 are repeatedly arranged in this order, but other arrangements may be employed. A part of the gap is an air passage 53. The remaining part of the gap is an accommodating part. Fins 46 are disposed in the air passage 53, and a cold storage material container 47 is disposed in the housing portion. The two refrigerant tubes 45 located on both sides of the cold storage material container 47 define an air passage for exchanging heat with air on the side opposite to the cold storage material container 47. In another aspect, two refrigerant tubes 45 are disposed between the two fins 46, and one cold storage material container 47 is disposed between the two refrigerant tubes 45. By disposing the cold storage material container 47 between the two refrigerant tubes 45, the heat of the refrigerant can be transmitted to the cold storage material 50 without receiving the heat load of the air flowing through the fins 46, so that the cold storage efficiency is improved. .
蓄冷材容器47と、その両側に位置する2つの冷媒管45とがひとつの蓄冷単位を構成している。蒸発器40には、同じ構成をもつ複数の蓄冷単位が配置されている。これらの蓄冷単位は、等間隔に配置されている。また、複数の蓄冷単位は、左右均等に配置されている。また、複数の蓄冷単位は、左右に対称に配置されている。
The cold storage material container 47 and the two refrigerant tubes 45 located on both sides thereof constitute one cold storage unit. The evaporator 40 is provided with a plurality of cold storage units having the same configuration. These cold storage units are arranged at equal intervals. Moreover, the some cool storage unit is arrange | positioned equally right and left. The plurality of cold storage units are arranged symmetrically on the left and right.
蓄冷材容器47は、図10に示すように、空気の流れ方向に沿って、第1熱交換部48及び第2熱交換部49の両方の冷媒管45と接合されている。蓄冷材容器47は、図8に示すように外殻47aを有する。外殻47aは、板材を扁平な筒状に曲げた形状をもつ。外殻47aの中には、コルゲート状のインナフィン47bが収容されている。インナフィン47bは、フィン46と同様に、薄いアルミニウム等の金属板が波状に曲げられた形状である。インナフィン47bの複数の頂部は、外殻47aの流入方向両側の主壁(冷媒管45と接合する主面を外表面とする壁部)の内面にろう付けされている。図9、10に示すように、インナフィン47bは、蓄冷材容器47の長手方向(高さ方向)に沿って延在し、インナフィン47bの峰と谷は、流れ方向に沿って延びている。この構成によると、インナフィン47bが、蓄冷材50と蓄冷材容器47との接触面積を大きくする。インナフィン47bの形状の詳細については後述する。
As shown in FIG. 10, the cold storage material container 47 is joined to both the refrigerant pipes 45 of the first heat exchange unit 48 and the second heat exchange unit 49 along the air flow direction. The cold storage material container 47 has an outer shell 47a as shown in FIG. The outer shell 47a has a shape obtained by bending a plate material into a flat cylindrical shape. A corrugated inner fin 47b is accommodated in the outer shell 47a. Like the fins 46, the inner fins 47b have a shape in which a thin metal plate such as aluminum is bent into a wave shape. The plurality of top portions of the inner fins 47b are brazed to the inner surfaces of the main walls (wall portions having a main surface joined to the refrigerant pipe 45 as an outer surface) on both sides in the inflow direction of the outer shell 47a. As shown in FIGS. 9 and 10, the inner fin 47b extends along the longitudinal direction (height direction) of the cold storage material container 47, and the peaks and valleys of the inner fin 47b extend along the flow direction. According to this configuration, the inner fins 47 b increase the contact area between the cold storage material 50 and the cold storage material container 47. Details of the shape of the inner fin 47b will be described later.
以下では、第1ヘッダ41を、冷媒通路の入口が設けられる入口側通路とも表記する。同様に、第3ヘッダ43を、冷媒通路の出口が設けられる出口側通路とも表記する。第1ヘッダ41及び第3ヘッダ43は、高さ方向の同一位置にて流れ方向に沿って並列に配置されており、これらを纏めて第1ヘッダタンク51と呼ぶ。同様に、第2ヘッダ42及び第4ヘッダ44は、高さ方向の同一位置にて流れ方向に沿って並列に配置されており、これらを纏めて第2ヘッダタンク52と呼ぶ。
Hereinafter, the first header 41 is also referred to as an inlet-side passage where the inlet of the refrigerant passage is provided. Similarly, the 3rd header 43 is described also as the exit side channel | path in which the exit of a refrigerant channel is provided. The first header 41 and the third header 43 are arranged in parallel along the flow direction at the same position in the height direction, and collectively referred to as a first header tank 51. Similarly, the second header 42 and the fourth header 44 are arranged in parallel along the flow direction at the same position in the height direction, and are collectively referred to as a second header tank 52.
図4~6に模式的に示すように、第1ヘッダ41の第1区画に流れ込んだ冷媒は、第1群G1の冷媒管45を通って第2ヘッダ42の第1区画に流れこむ(第1ターン)。第2ヘッダ42の第1区画に流れ込んだ冷媒は、第2ヘッダ42の第2区画に流れ込む。第2ヘッダ42の第2区画に流れ込んだ冷媒は、第2群G2の冷媒管45を通って第1ヘッダ41の第2区画に流れこむ(第2ターン)。第1ヘッダ41の第2区画と第3ヘッダ43の第2区画とは連通しているので、第1ヘッダ41の第2区画に流れ込んだ冷媒は第3ヘッダ43の第2区画に流れこむ。第3ヘッダ43の第2区画に流れ込んだ冷媒は、第3群G3の冷媒管45を通って第4ヘッダ44の第2区画に流れ込む(第3ターン)。第4ヘッダ44の第2区画に流れ込んだ冷媒は、第4ヘッダ44の第1区画に流れ込む。第4ヘッダ44の第1区画に流れ込んだ冷媒は、第4群G4の冷媒管45を通って第3ヘッダ43の第1区画に流れこむ(第4ターン)。第3ヘッダ43の第1区画に流れ込んだ冷媒は外部に流出する。つまり、本実施形態の蒸発器40は、所謂4ターン方式の冷媒通路を有する構成をとる。
As schematically shown in FIGS. 4 to 6, the refrigerant flowing into the first section of the first header 41 flows into the first section of the second header 42 through the refrigerant pipe 45 of the first group G1 (the first section 41). 1 turn). The refrigerant that has flowed into the first section of the second header 42 flows into the second section of the second header 42. The refrigerant flowing into the second section of the second header 42 flows into the second section of the first header 41 through the refrigerant pipe 45 of the second group G2 (second turn). Since the second section of the first header 41 and the second section of the third header 43 communicate with each other, the refrigerant flowing into the second section of the first header 41 flows into the second section of the third header 43. The refrigerant that has flowed into the second section of the third header 43 flows into the second section of the fourth header 44 through the refrigerant pipe 45 of the third group G3 (third turn). The refrigerant that has flowed into the second section of the fourth header 44 flows into the first section of the fourth header 44. The refrigerant flowing into the first section of the fourth header 44 flows into the first section of the third header 43 through the refrigerant pipe 45 of the fourth group G4 (fourth turn). The refrigerant flowing into the first section of the third header 43 flows out to the outside. That is, the evaporator 40 of this embodiment has a configuration having a so-called four-turn type refrigerant passage.
ここで、一般に冷凍サイクル装置1では、図1に示す通り、蒸発器40よりも冷媒の流れの下流側に、冷媒を圧縮吐出するための圧縮機10が存在する。圧縮機10に液状の冷媒が戻ると故障の原因となるため、一般的に蒸発器40の出口では冷媒を完全に蒸発させる必要がある。これにより、冷媒通路の出口近傍では冷媒がガス単層になり、圧力が飽和蒸気圧を超えることに起因して、冷媒温度が急激に高温に遷移する部分、いわゆる過熱域Sが存在する。図7に、4ターン方式の冷媒通路における冷媒温度の特性の一例を示す。図7の横軸は冷媒通路の位置を表し、軸の左側(原点側)が入口、右側が出口を表す。図7の縦軸は各流路位置における冷媒温度を表す。図7に示すように、冷媒温度は冷媒通路に導入後低減していくが、第4ターン(すなわち第4群G4)の略中間位置において急激に高温に遷移し、以降の部分では過熱域Sが発生している。過熱域Sは、例えば図5に示すように第4群G4の冷媒管45における高さ方向上側の略半分の領域に発生する。
Here, in general, in the refrigeration cycle apparatus 1, as shown in FIG. 1, the compressor 10 for compressing and discharging the refrigerant exists downstream of the evaporator 40 in the refrigerant flow. When the liquid refrigerant returns to the compressor 10, it causes a failure, and therefore it is generally necessary to completely evaporate the refrigerant at the outlet of the evaporator 40. Thereby, in the vicinity of the outlet of the refrigerant passage, the refrigerant becomes a gas monolayer, and a portion where the refrigerant temperature rapidly changes to a high temperature due to the pressure exceeding the saturated vapor pressure, a so-called superheat zone S exists. FIG. 7 shows an example of the characteristic of the refrigerant temperature in the four-turn type refrigerant passage. The horizontal axis in FIG. 7 represents the position of the refrigerant passage, the left side (origin side) of the axis represents the inlet, and the right side represents the outlet. The vertical axis in FIG. 7 represents the refrigerant temperature at each flow path position. As shown in FIG. 7, the refrigerant temperature decreases after being introduced into the refrigerant passage, but suddenly changes to a high temperature at a substantially intermediate position of the fourth turn (that is, the fourth group G4). Has occurred. For example, as shown in FIG. 5, the superheat zone S is generated in a substantially half region on the upper side in the height direction in the refrigerant pipe 45 of the fourth group G4.
図10に示したように、蓄冷材容器47は流れ方向に沿って第1熱交換部48及び第2熱交換部49の両方の冷媒管45と接合されている。このため、従来の蓄冷材容器47では、第4群G4の冷媒管45、すなわち流れ方向の風上側の冷媒管45との接触部分の蓄冷材50のみが過熱域Sの影響により蓄冷されにくくなるので、流れ方向の風上側と風下側で内部の蓄冷材50の冷え方に差異が生じてしまう。これにより、放冷時に流入方向の奥側と手前側(すなわち、過熱域Sを含まない領域と過熱域Sを含む領域)との間で、吹出温度に差が生じてしまう可能性がある。
As shown in FIG. 10, the regenerator container 47 is joined to both the refrigerant pipes 45 of the first heat exchange part 48 and the second heat exchange part 49 along the flow direction. For this reason, in the conventional cool storage material container 47, only the cool storage material 50 in the contact portion with the refrigerant pipe 45 of the fourth group G4, that is, the upwind side coolant pipe 45 in the flow direction, is hardly stored due to the influence of the superheat zone S. Therefore, a difference arises in how to cool the internal regenerator 50 between the windward side and the leeward side in the flow direction. Thereby, at the time of standing_to_cool, a difference may arise in blowing temperature between the back | inner side of the inflow direction, and this side (namely, the area | region which does not include the superheat zone S, and the area | region containing the superheat zone S).
この問題に対して本実施形態では、図9、10に示すように、インナフィン47bの形状が、冷媒の過熱域Sにおいて蓄冷材容器47と接合しない構成となっている。言い換えると、インナフィン47bは、過熱域Sが発生する冷媒管45と接合される蓄冷材容器47において、冷媒管45の過熱域Sと接触する部分では蓄冷材容器47の外殻47aの内壁面と接合されず、冷媒管45の過熱域S以外と接触する部分では内壁面と接合される。図10では、インナフィン47bの頂部が蓄冷材容器47と接合されている部分が実線で表され、インナフィン47bの頂部が蓄冷材容器47と接合されていない部分が点線で表されている。
For this problem, in this embodiment, as shown in FIGS. 9 and 10, the shape of the inner fin 47 b is configured not to be joined to the cold storage material container 47 in the superheated region S of the refrigerant. In other words, the inner fin 47b is connected to the inner wall surface of the outer shell 47a of the regenerator container 47 in the portion of the regenerator container 45 that is joined to the refrigerant pipe 45 where the superheat area S is generated. In the part which is not joined and contacts the refrigerant pipe 45 other than the superheated region S, it is joined to the inner wall surface. In FIG. 10, a portion where the top of the inner fin 47 b is joined to the cold storage material container 47 is represented by a solid line, and a portion where the top of the inner fin 47 b is not joined to the cold storage material container 47 is represented by a dotted line.
この構成はさらに以下のように言い換えることができる。蒸発器40において、複数の冷媒管45は、空気通路53の空気の流れ方向に沿って少なくとも2つの冷媒管45が配置される。蓄冷材容器47は、流れ方向に沿って配置されるこれらの少なくとも2つの冷媒管45と接合するよう形成される。このとき、接合部に凹凸があり、凸部が冷媒管45と接合する構成でもよい。インナフィン47bは、冷媒管45及び蓄冷材容器47の配列方向(流入方向)から視るときにこれらの少なくとも2つの冷媒管45と重畳するよう形成される。インナフィン47bは、過熱域Sが発生する冷媒管45を含むこれらの少なくとも2つの冷媒管45と接合される蓄冷材容器47において、冷媒管45の過熱域Sと接触する部分を含み、かつ、流れ方向から視るときにこの部分と重畳する領域では蓄冷材容器47の内壁と接合されず、それ以外の領域では蓄冷材容器47の内壁と接合される。
This configuration can be further rephrased as follows. In the evaporator 40, the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53. The cool storage material container 47 is formed so as to be joined to the at least two refrigerant tubes 45 arranged along the flow direction. At this time, there may be a configuration in which the joint portion is uneven, and the convex portion is joined to the refrigerant pipe 45. The inner fins 47 b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material container 47. Inner fin 47b includes a portion in contact with superheat zone S of refrigerant pipe 45 in cold storage material container 47 joined to at least two refrigerant pipes 45 including refrigerant pipe 45 in which superheat zone S is generated, and flows. When viewed from the direction, the region overlapping this portion is not joined to the inner wall of the regenerator material container 47, and the other region is joined to the inner wall of the regenerator material container 47.
このような構成により、過熱域Sではインナフィン47bが蓄冷材容器47、つまり冷媒管45に接合していないため、過熱冷媒からの温熱が蓄冷材50の内部へ伝わりにくくなる。また、インナフィン47b自体は過熱域Sの蓄冷材容器47内にも配置されている(浮いている)ため、非過熱域の冷媒の冷熱が、インナフィン47bを介して過熱域にある蓄冷材50にも伝えられる。このように、過熱域Sにある蓄冷材50に対して、過熱域の温熱を伝わりにくくできる一方で、非過熱域の冷熱を伝えることができるので、冷媒通路に過熱域Sが存在しても蓄冷材容器47内の蓄冷材50を良好に冷やすことができる。これにより、過熱域Sにある蓄冷材容器47の蓄冷材50が冷えずにエバポレータ(蒸発器40)内で放冷時に温度分布ができたり、そもそも過熱域の影響で蓄冷できないなどの不都合を解消することができる。
With such a configuration, the inner fin 47b is not joined to the cold storage material container 47, that is, the refrigerant pipe 45 in the superheat region S, so that the heat from the superheated refrigerant is not easily transmitted to the inside of the cold storage material 50. Further, since the inner fin 47b itself is also disposed (floating) in the regenerator container 47 in the superheat region S, the cold heat of the refrigerant in the non-superheat region is transferred to the regenerator material 50 in the superheat region via the inner fin 47b. Is also reported. Thus, while it is difficult to transmit the heat of the superheat region to the cold storage material 50 in the superheat region S, it is possible to transmit the cold heat of the non-superheat region, so that even if the superheat region S exists in the refrigerant passage. The cool storage material 50 in the cool storage material container 47 can be cooled well. This eliminates the inconvenience that the regenerator material 50 in the regenerator container 47 in the superheat zone S does not cool and the temperature distribution is allowed to cool in the evaporator (evaporator 40), and that it cannot be stored due to the overheat region. can do.
つまり、第1実施形態では、過熱域Sにおいてインナフィン47bを蓄冷材容器47に接合させない構造とすることで、インナフィン47bが、冷媒通路の出口の近傍において冷媒の蒸発により発生する過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制する「熱伝達抑制部」として機能する。そして、このようなインナフィン47bを設けることにより、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制することができ、冷媒温度が高温となる過熱域Sの影響により蓄冷材50が冷えにくくなる状況を回避できる。この結果、第1実施形態の蓄冷熱交換器としての蒸発器40は、過熱域Sが存在する場合でも、過熱域Sの影響を受けにくくし、蓄冷性能を確保できる。
That is, in the first embodiment, the inner fin 47b is not joined to the cold storage material container 47 in the superheat zone S, so that the inner fin 47b is a refrigerant in the superheat zone S generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage. It functions as a “heat transfer suppression unit” that suppresses heat transfer from the tube 45 to the cold storage material 50. And by providing such an inner fin 47b, the heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the cold storage material 50 is affected by the influence of the superheat zone S where the refrigerant temperature becomes high. The situation where it becomes difficult to get cold can be avoided. As a result, the evaporator 40 as the cold storage heat exchanger of the first embodiment is less susceptible to the influence of the superheat zone S even when the superheat zone S exists, and can secure the cold storage performance.
[第1実施形態の変形例]
図11~図20を参照して第1実施形態の変形例を説明する。第1実施形態では、蒸発器40において、インナフィン47bが、冷媒管45の過熱域Sと接触する部分では蓄冷材容器47の外殻47aの内壁面と接合されず、冷媒管45の過熱域S以外と接触する部分では内壁面と接合される構成を挙げたが、過熱域Sにおける冷媒管45からインナフィン47bを介しての蓄冷材50への伝熱量が過熱域S以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域Sにおけるインナフィン47bの伝熱性能を他の部分より相対的に低くできればよい。例えば図11に示すように、蒸発器401において、インナフィン471bが、冷媒管45の過熱域Sと接触する部分では蓄冷材容器471の外殻471aの内壁面との接合率が相対的に低くなるよう接合され、冷媒管45の過熱域S以外と接触する部分では内壁面との接合率が相対的に高くなるよう接合される構成とすることができる。「接合率が相対的に低い」とは、インナフィン471bの峰及び谷のうち外殻471aの内壁面と接合されるものの数が相対的に少ないことを言い、「接合率が相対的に高い」とは、インナフィン471bの峰及び谷のうち外殻471aの内壁面と接合されるものの数が相対的に多いことを言う。このように、過熱域Sにおけるインナフィン471bを介しての伝熱量を相対的に小さくする、または、インナフィン471bと蓄冷材容器471との接合率を相対的に低くすることにより、蒸発器401は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。 [Modification of First Embodiment]
A modification of the first embodiment will be described with reference to FIGS. In the first embodiment, in theevaporator 40, the inner fin 47 b is not joined to the inner wall surface of the outer shell 47 a of the regenerator container 47 at a portion where the inner fin 47 b is in contact with the superheat region S of the refrigerant tube 45. In the portion that is in contact with other than the superheated region, the configuration in which it is joined to the inner wall surface is given. However, the heat transfer amount from the refrigerant pipe 45 to the cold storage material 50 via the inner fin 47b in the superheat region S Other configurations may be used as long as they are smaller. In other words, it is only necessary that the heat transfer performance of the inner fins 47b in the superheat zone S can be made relatively lower than other portions. For example, as shown in FIG. 11, in the evaporator 401, the joint ratio between the inner fin 471 b and the inner wall surface of the outer shell 471 a of the cold storage material container 471 is relatively low at the portion where the inner fin 471 b contacts the superheated region S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with an inner wall surface may become relatively high in the part which contacts other than the superheat zone S of the refrigerant | coolant pipe | tube 45. “The joining rate is relatively low” means that the number of the ridges and valleys of the inner fin 471b that are joined to the inner wall surface of the outer shell 471a is relatively small, and “the joining rate is relatively high”. Means that the number of the ridges and valleys of the inner fin 471b that are joined to the inner wall surface of the outer shell 471a is relatively large. Thus, by making the amount of heat transfer through the inner fin 471b in the superheat zone S relatively small, or by making the joining rate of the inner fin 471b and the cold storage material container 471 relatively low, the evaporator 401 becomes Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
図11~図20を参照して第1実施形態の変形例を説明する。第1実施形態では、蒸発器40において、インナフィン47bが、冷媒管45の過熱域Sと接触する部分では蓄冷材容器47の外殻47aの内壁面と接合されず、冷媒管45の過熱域S以外と接触する部分では内壁面と接合される構成を挙げたが、過熱域Sにおける冷媒管45からインナフィン47bを介しての蓄冷材50への伝熱量が過熱域S以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域Sにおけるインナフィン47bの伝熱性能を他の部分より相対的に低くできればよい。例えば図11に示すように、蒸発器401において、インナフィン471bが、冷媒管45の過熱域Sと接触する部分では蓄冷材容器471の外殻471aの内壁面との接合率が相対的に低くなるよう接合され、冷媒管45の過熱域S以外と接触する部分では内壁面との接合率が相対的に高くなるよう接合される構成とすることができる。「接合率が相対的に低い」とは、インナフィン471bの峰及び谷のうち外殻471aの内壁面と接合されるものの数が相対的に少ないことを言い、「接合率が相対的に高い」とは、インナフィン471bの峰及び谷のうち外殻471aの内壁面と接合されるものの数が相対的に多いことを言う。このように、過熱域Sにおけるインナフィン471bを介しての伝熱量を相対的に小さくする、または、インナフィン471bと蓄冷材容器471との接合率を相対的に低くすることにより、蒸発器401は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。 [Modification of First Embodiment]
A modification of the first embodiment will be described with reference to FIGS. In the first embodiment, in the
第1実施形態では、蒸発器40において、インナフィン47bの波型形状が蓄冷材容器47の長手方向(高さ方向)に連続する構成、すなわち、インナフィン47bの峰と谷が流れ方向に沿って延びている構成を挙げたが、インナフィン47bの波型形状をこれと異なる方向に連続させる構成としてもよい。例えば図12に示すように、蒸発器402において、インナフィン472bの波型形状が蓄冷材容器472の短手方向(流れ方向)に連続する構成、すなわち、インナフィン472bの峰と谷が高さ方向に沿って延びている構成とすることができる。この場合、インナフィン472bの峰及び谷は、高さ方向に沿って冷媒管45の過熱域Sと接触する部分では蓄冷材容器472の外殻472aの内壁面と接合されず、冷媒管45の過熱域S以外と接触する部分では内壁面と接合される。これにより、蒸発器402は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。
In 1st Embodiment, in the evaporator 40, the wave shape of the inner fin 47b follows the longitudinal direction (height direction) of the cool storage material container 47, ie, the peak and valley of the inner fin 47b extend along a flow direction. However, the inner fin 47b may have a wave shape continuous in a different direction. For example, as shown in FIG. 12, in the evaporator 402, the wave shape of the inner fin 472b is continuous in the short direction (flow direction) of the cold storage material container 472, that is, the peaks and valleys of the inner fin 472b are in the height direction. It can be set as the structure extended along. In this case, the ridges and valleys of the inner fins 472b are not joined to the inner wall surface of the outer shell 472a of the regenerator container 472 in the portion that contacts the superheated area S of the refrigerant pipe 45 along the height direction, and the refrigerant pipe 45 is overheated. In the portion that comes into contact with other than the area S, it is joined to the inner wall surface. Thereby, the evaporator 402 can suppress the heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S, and the same effect as the evaporator 40 of the first embodiment can be obtained.
第1実施形態では蒸発器40の内部の冷媒通路の構成として4ターン方式を例示したがこれに限定されない。例えば図13~図15に示されるように、第1ヘッダ41A、第2ヘッダ42A、第3ヘッダ43A、第4ヘッダ44A内部の区画を無くすような構成にすることができる。図13~図15に示される蓄冷熱交換器40Aでは、第1ヘッダ41Aに流れ込んだ冷媒は、第1熱交換部48の冷媒管45を通って第2ヘッダ42Aに流れ込む(第1ターン)。第2ヘッダ42Aと第4ヘッダ44Aとは連通しているので、第2ヘッダ42Aに流れ込んだ冷媒は第4ヘッダ44Aに流れ込む。第4ヘッダ44Aに流れ込んだ冷媒は、第2熱交換部49の冷媒管45を通って第3ヘッダ43Aに流れこむ(第2ターン)。第3ヘッダ43Aに流れ込んだ冷媒は外部に流出する。つまり、蓄冷熱交換器40Aは、所謂2ターン方式の冷媒通路を有する構成をとる。
In the first embodiment, the four-turn system is exemplified as the configuration of the refrigerant passage inside the evaporator 40, but is not limited thereto. For example, as shown in FIG. 13 to FIG. 15, it is possible to eliminate the internal sections of the first header 41A, the second header 42A, the third header 43A, and the fourth header 44A. In the cold storage heat exchanger 40A shown in FIGS. 13 to 15, the refrigerant flowing into the first header 41A flows into the second header 42A through the refrigerant pipe 45 of the first heat exchanging section 48 (first turn). Since the second header 42A and the fourth header 44A communicate with each other, the refrigerant that has flowed into the second header 42A flows into the fourth header 44A. The refrigerant that has flowed into the fourth header 44A flows into the third header 43A through the refrigerant pipe 45 of the second heat exchange section 49 (second turn). The refrigerant flowing into the third header 43A flows out to the outside. That is, the regenerator heat exchanger 40A has a so-called two-turn refrigerant path.
図16に、2ターン方式の冷媒通路における冷媒温度の特性の一例を示す。図16に示すように、冷媒温度は冷媒通路に導入後低減していくが、第2ターンの後半位置において急激に高温に遷移し、以降の部分では過熱域Sが発生している。過熱域Sは、例えば図14に示すように第2熱交換部49の冷媒管45における高さ方向上側の領域に発生する。
FIG. 16 shows an example of the refrigerant temperature characteristic in the two-turn refrigerant passage. As shown in FIG. 16, the refrigerant temperature decreases after being introduced into the refrigerant passage, but rapidly changes to a high temperature at the second half position of the second turn, and the superheated region S is generated in the subsequent portions. For example, as illustrated in FIG. 14, the superheat zone S is generated in a region on the upper side in the height direction of the refrigerant pipe 45 of the second heat exchange unit 49.
第1実施形態のインナフィン47bは、蓄冷熱交換器40Aのような冷媒の流れを構成するものに対しても適用することができ、熱伝達抑制部として機能することができる。
The inner fins 47b of the first embodiment can also be applied to those constituting a refrigerant flow such as the cold storage heat exchanger 40A, and can function as a heat transfer suppression unit.
蓄冷熱交換器40Aでは、第1ヘッダ41A、第2ヘッダ42A、第3ヘッダ43A、第4ヘッダ44A内部の区画を無くすような構成としたけれども、内部の区画を増やす構成とすることもできる。
The cold storage heat exchanger 40A is configured to eliminate the internal sections of the first header 41A, the second header 42A, the third header 43A, and the fourth header 44A, but may be configured to increase the internal sections.
図17に示される蓄冷熱交換器40Bでは、第1ヘッダ41B、第2ヘッダ42B、第3ヘッダ43B、第4ヘッダ44B内部をそれぞれ3つの区画に区切っている。
In the regenerative heat exchanger 40B shown in FIG. 17, the first header 41B, the second header 42B, the third header 43B, and the fourth header 44B are each divided into three sections.
第1ヘッダ41Bの第1区画に流れ込んだ冷媒は、冷媒管45を通って第2ヘッダ42Bの第1区画に流れこむ(第1ターン)。第2ヘッダ42Bの第1区画に流れ込んだ冷媒は、第2ヘッダ42Bの第2区画に流れ込む。第2ヘッダ42Bの第2区画に流れ込んだ冷媒は、冷媒管45を通って第1ヘッダ41Bの第2区画に流れこむ(第2ターン)。
The refrigerant that has flowed into the first section of the first header 41B flows through the refrigerant pipe 45 into the first section of the second header 42B (first turn). The refrigerant that has flowed into the first section of the second header 42B flows into the second section of the second header 42B. The refrigerant that has flowed into the second section of the second header 42B flows through the refrigerant pipe 45 into the second section of the first header 41B (second turn).
第1ヘッダ41Bの第2区画に流れ込んだ冷媒は、第1ヘッダ41Bの第3区画に流れこむ。第1ヘッダ41Bの第3区画に流れ込んだ冷媒は、冷媒管45を通って第2ヘッダ42Bの第3区画に流れこむ(第3ターン)。第2ヘッダ42Bの第3区画と第4ヘッダ44Bの第3区画とは連通しているので、第2ヘッダ42Bの第3区画に流れ込んだ冷媒は第4ヘッダ44Bの第3区画に流れこむ。第4ヘッダ44Bの第3区画に流れ込んだ冷媒は、冷媒管45を通って第3ヘッダ43Bの第3区画に流れ込む(第4ターン)。
The refrigerant that has flowed into the second section of the first header 41B flows into the third section of the first header 41B. The refrigerant that has flowed into the third section of the first header 41B flows into the third section of the second header 42B through the refrigerant pipe 45 (third turn). Since the third section of the second header 42B and the third section of the fourth header 44B communicate with each other, the refrigerant flowing into the third section of the second header 42B flows into the third section of the fourth header 44B. The refrigerant flowing into the third section of the fourth header 44B flows through the refrigerant pipe 45 and into the third section of the third header 43B (fourth turn).
第3ヘッダ43Bの第3区画に流れ込んだ冷媒は、第3ヘッダ43Bの第2区画に流れ込む。第3ヘッダ43Bの第2区画に流れ込んだ冷媒は、冷媒管45を通って第4ヘッダ44Bの第2区画に流れこむ(第5ターン)。第4ヘッダ44Bの第2区画に流れ込んだ冷媒は、第4ヘッダ44Bの第1区画に流れ込む。第4ヘッダ44Bの第1区画に流れ込んだ冷媒は、冷媒管45を通って第3ヘッダ43Bの第1区画に流れこむ(第6ターン)。第3ヘッダ43Bの第1区画に流れ込んだ冷媒は外部に流出する。つまり、蓄冷熱交換器40Bは、所謂6ターン方式の冷媒通路を有する構成をとる。
The refrigerant that has flowed into the third section of the third header 43B flows into the second section of the third header 43B. The refrigerant flowing into the second section of the third header 43B flows through the refrigerant pipe 45 and into the second section of the fourth header 44B (fifth turn). The refrigerant that has flowed into the second section of the fourth header 44B flows into the first section of the fourth header 44B. The refrigerant flowing into the first section of the fourth header 44B flows through the refrigerant pipe 45 and into the first section of the third header 43B (sixth turn). The refrigerant that has flowed into the first section of the third header 43B flows out to the outside. That is, the regenerative heat exchanger 40B has a so-called six-turn refrigerant path.
第1実施形態のインナフィン47bは、蓄冷熱交換器40Bのような冷媒の流れを構成するものに対しても適用することができ、熱伝達抑制部として機能することができる。
The inner fins 47b of the first embodiment can also be applied to those constituting a refrigerant flow such as the cold storage heat exchanger 40B, and can function as a heat transfer suppression unit.
蓄冷熱交換器40,40A,40Bでは、冷媒の出入口を重力方向(高さ方向)で上側に配置された、第1ヘッダ41,41A,41B及び第3ヘッダ43,43A,43Bに設けている。冷媒の出入口の形態はこれらに限られるものではなく、蓄冷熱交換器40,40A,40Bの天地を逆転させた構成とすることもできる。
In the cold storage heat exchangers 40, 40A, 40B, the refrigerant inlet / outlet ports are provided in the first header 41, 41A, 41B and the third header 43, 43A, 43B, which are arranged on the upper side in the direction of gravity (height direction). . The form of the refrigerant inlet / outlet is not limited to these, and the top and bottom of the cold storage heat exchangers 40, 40A, 40B may be reversed.
図18に示される蓄冷熱交換器40Rは、第1ヘッダ41R及び第3ヘッダ43Rを重力方向(高さ方向)で下側に配置し,第2ヘッダ42R及び第4ヘッダ44Rを重力方向で上側に配置している。
In the regenerator heat exchanger 40R shown in FIG. 18, the first header 41R and the third header 43R are disposed on the lower side in the direction of gravity (height direction), and the second header 42R and the fourth header 44R are disposed on the upper side in the direction of gravity. Is arranged.
第1ヘッダ41Rの第1区画に流れ込んだ冷媒は、冷媒管45を通って第2ヘッダ42Rの第1区画に流れこむ(第1ターン)。第2ヘッダ42Rの第1区画に流れ込んだ冷媒は、第2ヘッダ42Rの第2区画に流れ込む。第2ヘッダ42Rの第2区画に流れ込んだ冷媒は、冷媒管45を通って第1ヘッダ41Rの第2区画に流れこむ。(第2ターン)
The refrigerant that has flowed into the first section of the first header 41R flows through the refrigerant pipe 45 into the first section of the second header 42R (first turn). The refrigerant that has flowed into the first section of the second header 42R flows into the second section of the second header 42R. The refrigerant that has flowed into the second section of the second header 42R flows through the refrigerant pipe 45 and into the second section of the first header 41R. (2nd turn)
第1ヘッダ41Rの第2区画と第3ヘッダ43Rの第2区画とは連通しているので、第1ヘッダ41Rの第2区画に流れ込んだ冷媒は第3ヘッダ43Rの第2区画に流れこむ。第3ヘッダ43Rの第2区画に流れ込んだ冷媒は、冷媒管45を通って第4ヘッダ44Rの第2区画に流れ込む(第3ターン)。
Since the second section of the first header 41R communicates with the second section of the third header 43R, the refrigerant flowing into the second section of the first header 41R flows into the second section of the third header 43R. The refrigerant that has flowed into the second section of the third header 43R flows through the refrigerant pipe 45 into the second section of the fourth header 44R (third turn).
第4ヘッダ44Rの第2区画に流れ込んだ冷媒は、第4ヘッダ44Rの第1区画に流れ込む。第4ヘッダ44Rの第1区画に流れ込んだ冷媒は、冷媒管45を通って第3ヘッダ43Rの第1区画に流れこむ(第4ターン)。第3ヘッダ43Rの第1区画に流れ込んだ冷媒は外部に流出する。つまり、蓄冷熱交換器40Rは、所謂4ターン方式の冷媒通路を有する構成をとり、上記の蓄冷熱交換器40の高さ方向の配置を入れ替えたものである。
The refrigerant that has flowed into the second section of the fourth header 44R flows into the first section of the fourth header 44R. The refrigerant that has flowed into the first section of the fourth header 44R flows through the refrigerant pipe 45 into the first section of the third header 43R (fourth turn). The refrigerant flowing into the first section of the third header 43R flows out to the outside. That is, the cold storage heat exchanger 40R has a configuration having a so-called four-turn refrigerant passage, and the arrangement of the cold storage heat exchanger 40 in the height direction is changed.
図19に示される蓄冷熱交換器40RAは、図16に示される蓄冷熱交換器40Aを天地逆転させたものである。蓄冷熱交換器40RAは、所謂2ターン方式の冷媒通路を有し、第1ヘッダ41RA及び第3ヘッダ43RAを重力方向(高さ方向)で下側に配置し,第2ヘッダ42RA及び第4ヘッダ44RAを重力方向で上側に配置している。
A cold storage heat exchanger 40RA shown in FIG. 19 is obtained by reversing the cold storage heat exchanger 40A shown in FIG. The regenerator heat exchanger 40RA has a so-called two-turn type refrigerant passage, and the first header 41RA and the third header 43RA are arranged on the lower side in the direction of gravity (height direction), and the second header 42RA and the fourth header 44RA is arranged on the upper side in the direction of gravity.
図20に示される蓄冷熱交換器40RBは、図17に示される蓄冷熱交換器40Bを天地逆転させたものである。蓄冷熱交換器40RBは、所謂6ターン方式の冷媒通路を有し、第1ヘッダ41RB及び第3ヘッダ43RBを重力方向(高さ方向)で下側に配置し,第2ヘッダ42RB及び第4ヘッダ44RBを重力方向で上側に配置している。
20 is a regenerative heat exchanger 40RB shown in FIG. 17, which is a reversal of the regenerative heat exchanger 40B shown in FIG. The cold storage heat exchanger 40RB has a so-called six-turn refrigerant passage, and the first header 41RB and the third header 43RB are arranged on the lower side in the direction of gravity (height direction), and the second header 42RB and the fourth header 44RB is arranged on the upper side in the direction of gravity.
[第2実施形態]
図21~図23を参照して第2実施形態を説明する。第2実施形態の蒸発器140は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成が第1実施形態の蒸発器40と異なる。具体的には、図21,図22に示すように、蓄冷材容器147の形状が冷媒の過熱域Sにおいて冷媒管45と接合しない構造となっており、この構造を有する蓄冷材容器147が熱伝達抑制部として機能する。また、第2実施形態の蒸発器140は、蓄冷材容器147の内部にインナフィンを設けない点が第1実施形態の蒸発器40と異なる。 [Second Embodiment]
The second embodiment will be described with reference to FIGS. Theevaporator 140 of the second embodiment is different from the evaporator 40 of the first embodiment in the configuration of a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S. Specifically, as shown in FIGS. 21 and 22, the shape of the regenerator container 147 is a structure that does not join the refrigerant pipe 45 in the refrigerant overheating region S, and the regenerator container 147 having this structure is heated. Functions as a transmission suppression unit. Moreover, the evaporator 140 of 2nd Embodiment differs from the evaporator 40 of 1st Embodiment by the point which does not provide an inner fin in the inside of the cool storage material container 147. FIG.
図21~図23を参照して第2実施形態を説明する。第2実施形態の蒸発器140は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成が第1実施形態の蒸発器40と異なる。具体的には、図21,図22に示すように、蓄冷材容器147の形状が冷媒の過熱域Sにおいて冷媒管45と接合しない構造となっており、この構造を有する蓄冷材容器147が熱伝達抑制部として機能する。また、第2実施形態の蒸発器140は、蓄冷材容器147の内部にインナフィンを設けない点が第1実施形態の蒸発器40と異なる。 [Second Embodiment]
The second embodiment will be described with reference to FIGS. The
この構成を言い換えると、過熱域Sが発生する冷媒管45と接合される蓄冷材容器147は、冷媒管45の過熱域Sと接触する部分(領域147c)では冷媒管45と接合されず冷媒管45と間隔をあけて形成され、冷媒管45の過熱域S以外と接触する部分(外殻147a)において冷媒管45と接合される。図21,図22では、このような構成の一例として、蓄冷材容器147の外殻147aのうち、過熱域Sと重畳する領域147cが、その表面が冷媒管45から離間する方向へ凹んでいる形状が例示されている。
In other words, the regenerator container 147 joined to the refrigerant tube 45 in which the superheat zone S is generated is not joined to the refrigerant tube 45 in the portion (region 147c) in contact with the superheat zone S of the refrigerant tube 45. 45 is formed at an interval, and is joined to the refrigerant pipe 45 at a portion (outer shell 147a) in contact with the refrigerant pipe 45 other than the superheat zone S. In FIG. 21 and FIG. 22, as an example of such a configuration, a region 147 c of the outer shell 147 a of the cold storage material container 147 that overlaps the superheated region S is recessed in a direction in which the surface is separated from the refrigerant pipe 45. The shape is illustrated.
この構成はさらに以下のように言い換えることができる。蒸発器140において、複数の冷媒管45は、空気通路53の空気の流れ方向に沿って少なくとも2つの冷媒管45が配置される。蓄冷材容器147は、流れ方向に沿って配置される少なくとも2つの冷媒管45と接合するよう形成される。過熱域Sが発生する冷媒管45を含む少なくとも2つの冷媒管45と接合される蓄冷材容器147は、冷媒管45の過熱域Sと接触する部分を含み、かつ、流れ方向から視るときにこの部分と重畳する領域147cでは冷媒管45と接合されず冷媒管45と間隔をあけて形成され、それ以外の領域147aでは冷媒管45と接合される。
This configuration can be further rephrased as follows. In the evaporator 140, the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53. The cool storage material container 147 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction. The cold storage material container 147 joined to at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated includes a portion that contacts the superheat zone S of the refrigerant tube 45 and when viewed from the flow direction. In the region 147c that overlaps with this portion, it is not joined to the refrigerant tube 45 but is spaced from the refrigerant tube 45, and in the other region 147a, it is joined to the refrigerant tube 45.
このような構成により、過熱域Sで蓄冷材容器147が冷媒管45に接合していないため、過熱冷媒からの温熱が蓄冷材50の内部へ伝わりにくくなる。また、蓄冷材容器147自体は非過熱域に接触しているため、非過熱域の冷媒の冷熱が過熱域Sにある蓄冷材50にも伝えられる。これにより、第2実施形態の蒸発器140は、第1実施形態の蒸発器40と同様の効果を奏することができる。
With such a configuration, since the regenerator container 147 is not joined to the refrigerant pipe 45 in the superheat region S, the heat from the overheated refrigerant is not easily transmitted to the inside of the regenerator 50. Moreover, since the cool storage material container 147 itself is in contact with the non-superheated region, the cold heat of the refrigerant in the non-superheated region is also transmitted to the cool storage material 50 in the superheated region S. Thereby, the evaporator 140 of 2nd Embodiment can have an effect similar to the evaporator 40 of 1st Embodiment.
なお、第2実施形態の蓄冷材容器147の形状は、上記のものに限定されず、過熱域Sにおける冷媒管45から蓄冷材容器147を介しての蓄冷材50への伝熱量が過熱域S以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域Sにおける蓄冷材容器147の伝熱性能を他の部分より相対的に低くできればよい。例えば図23に示すように、蒸発器1401において、蓄冷材容器1471が、冷媒管45の過熱域Sと接触する部分(領域1471c)では冷媒管45との接合率が相対的に低くなるように接合され、冷媒管45の過熱域S以外と接触する部分(外殻1471a)において冷媒管45との接合率が相対的に高くなるよう接合される構成とすることができる。「接合率が相対的に低い」とは、蓄冷材容器1471の外表面のうち冷媒管45と接合される部分の割合が相対的に少ないことを言い、「接合率が相対的に高い」とは、蓄冷材容器1471の外表面のうち冷媒管45と接合される部分の割合が相対的に多いことを言う。このように、過熱域Sにおける蓄冷材容器1471の伝熱量を相対的に小さくする、または、蓄冷材容器1471と冷媒管45との接合率を相対的に低くすることにより、蒸発器1401は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。
In addition, the shape of the cool storage material container 147 of 2nd Embodiment is not limited to the above thing, The heat transfer amount from the refrigerant | coolant pipe | tube 45 in the superheat zone S to the cool storage material 50 via the cool storage material container 147 is superheat zone S. Any other configuration may be used as long as it is relatively smaller than the heat transfer amount. In other words, it is only necessary that the heat transfer performance of the regenerator container 147 in the superheat zone S can be made relatively lower than the other parts. For example, as shown in FIG. 23, in the evaporator 1401, the joint ratio with the refrigerant pipe 45 is relatively low in a portion (area 1471 c) where the cold storage material container 1471 contacts the superheated area S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with the refrigerant | coolant pipe | tube 45 may become relatively high in the part (outer shell 1471a) joined and the parts other than the superheat zone S of the refrigerant | coolant pipe | tube 45. “The joining rate is relatively low” means that the ratio of the portion of the outer surface of the regenerator container 1471 joined to the refrigerant pipe 45 is relatively small, and “the joining rate is relatively high”. Means that the ratio of the portion joined to the refrigerant pipe 45 in the outer surface of the cool storage material container 1471 is relatively large. Thus, by making the heat transfer amount of the regenerator container 1471 in the superheat zone S relatively small, or by making the joining rate between the regenerator container 1471 and the refrigerant pipe 45 relatively low, the evaporator 1401 Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
[第3実施形態]
図24~図26を参照して第3実施形態を説明する。第3実施形態の蒸発器240は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成が第1実施形態の蒸発器40と異なる。具体的には、図24,図25に示すように、蓄冷材容器247の形状が冷媒の過熱域Sにおいて冷媒管45と接合しない構造となっており、この構造を有する蓄冷材容器247が熱伝達抑制部として機能する。また、第3実施形態の蒸発器240は、蓄冷材容器247の内部に設けられるインナフィン247bが長手方向の全域に亘って外殻247aの内壁面に接合される点が第1実施形態の蒸発器40と異なる。 [Third Embodiment]
A third embodiment will be described with reference to FIGS. Theevaporator 240 of the third embodiment is different from the evaporator 40 of the first embodiment in the configuration of a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S. Specifically, as shown in FIGS. 24 and 25, the shape of the regenerator container 247 is a structure that does not join the refrigerant pipe 45 in the refrigerant overheating region S, and the regenerator container 247 having this structure is heated. Functions as a transmission suppression unit. Moreover, the evaporator 240 of 3rd Embodiment is an evaporator of 1st Embodiment that the inner fin 247b provided in the inside of the cool storage material container 247 is joined to the inner wall face of the outer shell 247a over the whole area of a longitudinal direction. Different from 40.
図24~図26を参照して第3実施形態を説明する。第3実施形態の蒸発器240は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成が第1実施形態の蒸発器40と異なる。具体的には、図24,図25に示すように、蓄冷材容器247の形状が冷媒の過熱域Sにおいて冷媒管45と接合しない構造となっており、この構造を有する蓄冷材容器247が熱伝達抑制部として機能する。また、第3実施形態の蒸発器240は、蓄冷材容器247の内部に設けられるインナフィン247bが長手方向の全域に亘って外殻247aの内壁面に接合される点が第1実施形態の蒸発器40と異なる。 [Third Embodiment]
A third embodiment will be described with reference to FIGS. The
この構成を言い換えると、インナフィン247bは、蓄冷材容器247の内部において長手方向(高さ方向)に沿って延在するよう配置され、蓄冷材容器247の内壁と接合される。過熱域Sが発生する冷媒管45と接合される蓄冷材容器247は、冷媒管45の過熱域Sと接触する部分(領域247c)では冷媒管45と接合されず冷媒管45と間隔をあけて形成され、冷媒管45の過熱域S以外と接触する部分(外殻147a)において冷媒管45と接合される。
In other words, the inner fin 247b is disposed so as to extend along the longitudinal direction (height direction) inside the cold storage material container 247, and is joined to the inner wall of the cold storage material container 247. The regenerator container 247 joined to the refrigerant pipe 45 in which the superheat zone S is generated is not joined to the refrigerant pipe 45 at a portion (region 247 c) in contact with the superheat zone S of the refrigerant pipe 45 and spaced from the refrigerant pipe 45. It is formed and joined to the refrigerant pipe 45 at a portion (outer shell 147a) that is in contact with the refrigerant pipe 45 other than the superheat zone S.
この構成はさらに以下のように言い換えることができる。蒸発器240において、複数の冷媒管45は、空気通路53の空気の流れ方向に沿って少なくとも2つの冷媒管45が配置される。蓄冷材容器247は、流れ方向に沿って配置される少なくとも2つの冷媒管45と接合するよう形成される。インナフィン247bは、冷媒管45及び蓄冷材容器247の配列方向(流入方向)から視るときにこれらの少なくとも2つの冷媒管45と重畳するよう形成される。過熱域Sが発生する冷媒管45を含むこれらの少なくとも2つの冷媒管45と接合される蓄冷材容器247は、冷媒管45の過熱域Sと接触する部分を含み、かつ、流れ方向から視るときにこの部分と重畳する領域247cでは冷媒管45と接合されず冷媒管45と間隔をあけて形成され、それ以外の領域247aでは冷媒管45と接合される。
This configuration can be further rephrased as follows. In the evaporator 240, at least two refrigerant tubes 45 are arranged along the air flow direction of the air passage 53. The cool storage material container 247 is formed so as to be joined to at least two refrigerant pipes 45 arranged along the flow direction. The inner fins 247b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cool storage material containers 247. The regenerator container 247 joined to the at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated includes a portion in contact with the superheat zone S of the refrigerant tube 45 and is viewed from the flow direction. Sometimes, the region 247c overlapping with this portion is not joined to the refrigerant tube 45 but is spaced from the refrigerant tube 45, and the other region 247a is joined to the refrigerant tube 45.
このような構成により、過熱域Sでは蓄冷材容器247が冷媒管45に接合しておらず、また、蓄冷材容器247の内部で接合するインナフィン247bも冷媒管45に接合していないため、過熱冷媒からの温熱が蓄冷材50の内部へ伝わりにくくなる。また、インナフィン247b自体は過熱域Sの蓄冷材容器47内にも配置されているため、非過熱域の冷媒の冷熱が、インナフィン247bを介して過熱域Sにある蓄冷材50にも伝えられる。また、蓄冷材容器247自体は非過熱域に接触しているため、非過熱域の冷媒の冷熱が過熱域Sにある蓄冷材50にも伝えられる。これにより、第3実施形態の蒸発器240は、第1実施形態の蒸発器40と同様の効果を奏することができる。
With such a configuration, the regenerator container 247 is not joined to the refrigerant pipe 45 in the superheat zone S, and the inner fins 247b joined inside the regenerator container 247 are also not joined to the refrigerant pipe 45. It becomes difficult for the heat from the refrigerant to be transmitted to the inside of the regenerator 50. Further, since the inner fins 247b themselves are also arranged in the regenerator container 47 in the superheat region S, the cold heat of the refrigerant in the non-superheat region is also transmitted to the regenerator material 50 in the superheat region S via the inner fins 247b. Moreover, since the cool storage material container 247 itself is in contact with the non-superheated region, the cold heat of the refrigerant in the non-superheated region is also transmitted to the cool storage material 50 in the superheated region S. Thereby, the evaporator 240 of 3rd Embodiment can have an effect similar to the evaporator 40 of 1st Embodiment.
なお、第3実施形態の蒸発器240でも、第1実施形態と同様に、インナフィン247bが、冷媒管45の過熱域Sと接触する部分では蓄冷材容器247の外殻247aの内壁面と接合されない構成としてもよい。この構成により、過熱域Sではインナフィン247bが蓄冷材容器247、つまり冷媒管45に接合していないため、過熱冷媒からの温熱が蓄冷材50の内部へより一層伝わりにくくなる。
In the evaporator 240 of the third embodiment, the inner fin 247b is not joined to the inner wall surface of the outer shell 247a of the regenerator container 247 at the portion where the inner fin 247b is in contact with the superheated region S of the refrigerant pipe 45 as in the first embodiment. It is good also as a structure. With this configuration, the inner fin 247b is not joined to the regenerator container 247, that is, the refrigerant pipe 45 in the superheat region S, so that the heat from the overheated refrigerant is more difficult to be transmitted to the inside of the regenerator 50.
なお、第3実施形態の蓄冷材容器247の形状は、上記のものに限定されず、過熱域Sにおける冷媒管45から蓄冷材容器247を介しての蓄冷材50への伝熱量が過熱域S以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域Sにおける蓄冷材容器247の伝熱性能を他の部分より相対的に低くできればよい。例えば、図23を参照して第2実施形態にて説明した構成と同様に、図26に示すように、蒸発器2401において、蓄冷材容器2471が、冷媒管45の過熱域Sと接触する部分(領域2471c)では冷媒管45との接合率が相対的に低くなるように接合され、冷媒管45の過熱域S以外と接触する部分(外殻2471a)において冷媒管45との接合率が相対的に高くなるよう接合される構成とすることができる。このように、過熱域Sにおける蓄冷材容器2471の伝熱量を相対的に小さくする、または、蓄冷材容器2471と冷媒管45との接合率を相対的に低くすることにより、蒸発器2401は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。
In addition, the shape of the cool storage material container 247 of 3rd Embodiment is not limited to the above thing, The heat transfer amount from the refrigerant | coolant pipe | tube 45 in the superheat zone S to the cool storage material 50 via the cool storage material container 247 is superheat zone S. Any other configuration may be used as long as it is relatively smaller than the heat transfer amount. In other words, it is only necessary that the heat transfer performance of the regenerator container 247 in the superheat zone S can be made relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG. 23, as shown in FIG. 26, a portion in which the cold storage material container 2471 is in contact with the superheated region S of the refrigerant pipe 45 in the evaporator 2401. In (area 2471c), the joining ratio with the refrigerant pipe 45 is joined so as to be relatively low, and the joining ratio with the refrigerant pipe 45 is relative to the portion (outer shell 2471a) in contact with the refrigerant pipe 45 other than the superheated area S. It can be set as the structure joined so that it may become high. Thus, by making the heat transfer amount of the regenerator container 2471 in the superheat zone S relatively small, or by making the joining rate of the regenerator container 2471 and the refrigerant pipe 45 relatively low, the evaporator 2401 Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
さらに、第1実施形態と同様にインナフィン2471bと蓄冷材容器2471との接合構成によって過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制する構成を適用する場合には、図11を参照して第1実施形態にて説明したのと同様の構成を適用できる。具体的には、図26に示すように、蒸発器2401において、インナフィン2471bが、冷媒管45の過熱域Sと接触する部分では蓄冷材容器2471の外殻2471aの内壁面との接合率が相対的に低くなるよう接合され、冷媒管45の過熱域S以外と接触する部分では内壁面との接合率が相対的に高くなるよう接合される構成とすることができる。このように、インナフィン2471bと蓄冷材容器2471との接合率を相対的に低くすることによっても、蒸発器2401は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。
Furthermore, when applying the structure which suppresses the heat transfer from the refrigerant | coolant pipe | tube 45 in the superheat zone S to the cool storage material 50 by the joining structure of the inner fin 2471b and the cool storage material container 2471 like 1st Embodiment, FIG. A configuration similar to that described with reference to the first embodiment can be applied. Specifically, as shown in FIG. 26, in the evaporator 2401, the joint ratio between the inner fin 2471 b and the inner wall surface of the outer shell 2471 a of the regenerator container 2471 is relative to the portion where the inner fin 2471 b contacts the superheated region S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with an inner wall surface may become relatively high in the part contacted except the superheat zone S of the refrigerant | coolant pipe | tube 45 in order to become low. Thus, by making the joining rate of the inner fin 2471b and the cool storage material container 2471 relatively low, the evaporator 2401 can suppress heat transfer from the refrigerant pipe 45 to the cool storage material 50 in the superheat zone S, and The same effect as the evaporator 40 of 1 embodiment is acquired.
また、図12を参照して第1実施形態にて説明した構成と同様に、蒸発器240において、インナフィン247bの波型形状が蓄冷材容器247の短手方向(流れ方向)に連続する構成、すなわち、インナフィン247bの峰と谷が高さ方向に沿って延びている構成としてもよい。この構成でも、蒸発器240は、過熱域Sにおける冷媒管45から蓄冷材50への熱伝達を抑制でき、第1実施形態の蒸発器40と同様の効果が得られる。
Further, similarly to the configuration described in the first embodiment with reference to FIG. 12, in the evaporator 240, a configuration in which the wave shape of the inner fin 247b is continuous in the short direction (flow direction) of the cold storage material container 247, That is, the configuration may be such that the peaks and valleys of the inner fin 247b extend along the height direction. Even in this configuration, the evaporator 240 can suppress heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S, and the same effect as the evaporator 40 of the first embodiment can be obtained.
[第4実施形態]
図27及び図28を参照して第4実施形態を説明する。第4実施形態の蒸発器340は、熱伝達抑制部としてのインナフィン347bの形状が第1実施形態の蒸発器40におけるインナフィン47bと異なる。具体的には、図27,図28に示すように、冷媒管45が流れ方向の風上側と風下側に配置される場合において、一般的に過熱域Sは風上側に生じるため、風上側のみでインナフィン347bが蓄冷材容器347と接合していない点で、第1実施形態と異なる。 [Fourth Embodiment]
A fourth embodiment will be described with reference to FIGS. 27 and 28. Theevaporator 340 of the fourth embodiment is different from the inner fin 47b in the evaporator 40 of the first embodiment in the shape of the inner fin 347b as a heat transfer suppressing unit. Specifically, as shown in FIGS. 27 and 28, when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side. Thus, the inner fin 347b is different from the first embodiment in that the inner fin 347b is not joined to the cold storage material container 347.
図27及び図28を参照して第4実施形態を説明する。第4実施形態の蒸発器340は、熱伝達抑制部としてのインナフィン347bの形状が第1実施形態の蒸発器40におけるインナフィン47bと異なる。具体的には、図27,図28に示すように、冷媒管45が流れ方向の風上側と風下側に配置される場合において、一般的に過熱域Sは風上側に生じるため、風上側のみでインナフィン347bが蓄冷材容器347と接合していない点で、第1実施形態と異なる。 [Fourth Embodiment]
A fourth embodiment will be described with reference to FIGS. 27 and 28. The
この構成を言い換えると、蒸発器340において、複数の冷媒管45は、空気通路53の空気の流れ方向に沿って少なくとも2つの冷媒管45が配置される。蓄冷材容器347は、流れ方向に沿って配置される少なくとも2つの冷媒管と接合するよう形成される。インナフィン347bは、冷媒管45及び蓄冷材容器347の配列方向(流入方向)から視るときにこれらの少なくとも2つの冷媒管45と重畳するよう形成される。インナフィン347bは、過熱域Sが発生する冷媒管45を含む少なくとも2つの冷媒管45と接合される蓄冷材容器347において、過熱域Sが発生しない冷媒管45と重畳する領域では長手方向の全域に亘って蓄冷材容器347の内壁と接合される。また、過熱域Sが発生する冷媒管45と重畳する領域では、冷媒管45の過熱域Sと接触する部分では蓄冷材容器347の内壁と接合されず、それ以外の部分では蓄冷材容器347の内壁と接合される。
In other words, in the evaporator 340, the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53. The cool storage material container 347 is formed so as to be joined to at least two refrigerant tubes arranged along the flow direction. The inner fins 347b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cool storage material containers 347. The inner fins 347b are disposed in the entire region in the longitudinal direction in the region of the cold storage material container 347 joined to at least two refrigerant tubes 45 including the refrigerant tubes 45 in which the superheat zone S is generated, in a region overlapping with the refrigerant tubes 45 in which the superheat zone S is not generated. It is joined to the inner wall of the cold storage material container 347 over the whole. Moreover, in the area | region which overlaps with the refrigerant | coolant pipe | tube 45 where the superheat zone S generate | occur | produces, the part which contacts the superheat zone S of the refrigerant | coolant pipe | tube 45 is not joined with the inner wall of the cool storage material container 347, and in other parts of the cool storage material container 347 Joined to the inner wall.
この構成により、第4実施形態の蒸発器340は、第1実施形態と同様の効果を奏する。また、風下側の非過熱域の冷媒管45にはインナフィン347bが接するため、風上側から風下側へ冷熱を伝えることができ冷媒管45から蓄冷材50への熱伝達をより一層抑制できる。
With this configuration, the evaporator 340 of the fourth embodiment has the same effect as that of the first embodiment. Further, since the inner fin 347b is in contact with the refrigerant tube 45 in the non-superheated region on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the cold storage material 50 can be further suppressed.
また、第4実施形態の蒸発器340は、第1実施形態にて説明した各種の変形例も適用することができる。
Further, the various modifications described in the first embodiment can also be applied to the evaporator 340 of the fourth embodiment.
[第5実施形態]
図29及び図30を参照して第5実施形態を説明する。第5実施形態の蒸発器440は、熱伝達抑制部としての蓄冷材容器447の形状が第2実施形態の蒸発器140における蓄冷材容器147と異なる。具体的には、図29,図30に示すように、冷媒管45が流れ方向の風上側と風下側に配置される場合において、一般的に過熱域Sは風上側に生じるため、風上側のみで蓄冷材容器447が冷媒管45と接合していない点で、第2実施形態と異なる。 [Fifth Embodiment]
The fifth embodiment will be described with reference to FIGS. 29 and 30. FIG. Theevaporator 440 of the fifth embodiment is different from the cold storage material container 147 in the evaporator 140 of the second embodiment in the shape of the cold storage material container 447 as a heat transfer suppression unit. Specifically, as shown in FIGS. 29 and 30, when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side. However, it differs from the second embodiment in that the cold storage material container 447 is not joined to the refrigerant pipe 45.
図29及び図30を参照して第5実施形態を説明する。第5実施形態の蒸発器440は、熱伝達抑制部としての蓄冷材容器447の形状が第2実施形態の蒸発器140における蓄冷材容器147と異なる。具体的には、図29,図30に示すように、冷媒管45が流れ方向の風上側と風下側に配置される場合において、一般的に過熱域Sは風上側に生じるため、風上側のみで蓄冷材容器447が冷媒管45と接合していない点で、第2実施形態と異なる。 [Fifth Embodiment]
The fifth embodiment will be described with reference to FIGS. 29 and 30. FIG. The
この構成を言い換えると、蒸発器440において、複数の冷媒管45は、空気通路53の空気の流れ方向に沿って少なくとも2つの冷媒管45が配置される。蓄冷材容器447は、流れ方向に沿って配置される少なくとも2つの冷媒管45と接合するよう形成される。過熱域Sが発生する冷媒管45を含む少なくとも2つの冷媒管45と接合される蓄冷材容器447は、過熱域Sが発生しない冷媒管45と重畳する領域では延在方向(高さ方向)の全域に亘って冷媒管45と接合される。また、過熱域Sが発生する冷媒管45と重畳する領域では、冷媒管45の過熱域Sと接触する部分(領域447c)では冷媒管45と接合されず冷媒管45と間隔をあけて形成され、それ以外の部分447aでは冷媒管45と接合される。
In other words, in the evaporator 440, at least two refrigerant tubes 45 are arranged in the evaporator 440 along the air flow direction of the air passage 53. The cool storage material container 447 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction. The regenerator container 447 joined to at least two refrigerant pipes 45 including the refrigerant pipe 45 in which the superheat zone S is generated extends in the extending direction (height direction) in a region overlapping with the refrigerant pipe 45 in which the superheat zone S does not occur. The refrigerant pipe 45 is joined over the entire area. Further, in the region overlapping with the refrigerant tube 45 where the superheat zone S is generated, the portion (region 447c) of the refrigerant tube 45 that is in contact with the superheat zone S is not joined to the refrigerant tube 45 and is spaced from the refrigerant tube 45. The other portion 447a is joined to the refrigerant pipe 45.
この構成により、第5実施形態の蒸発器440は、第2実施形態と同様の効果を奏する。また、風下側の非過熱域の冷媒管45には蓄冷材容器447が接するため、風上側から風下側へ冷熱を伝えることができ、冷媒管45から蓄冷材50への熱伝達をより一層抑制できる。また、蓄冷材容器447の容積を、第2実施形態より増大させることができるので、より多くの蓄冷材50を収容できる。
With this configuration, the evaporator 440 of the fifth embodiment has the same effects as those of the second embodiment. Further, since the cold storage container 447 is in contact with the refrigerant tube 45 in the non-superheated area on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the cold storage material 50 is further suppressed. it can. Moreover, since the capacity | capacitance of the cool storage material container 447 can be increased from 2nd Embodiment, more cool storage materials 50 can be accommodated.
また、第5実施形態の蒸発器440は、第2実施形態にて説明した各種の変形例も適用することができる。
Also, the various modifications described in the second embodiment can be applied to the evaporator 440 of the fifth embodiment.
[第6実施形態]
図31及び図32を参照して第6実施形態を説明する。第6実施形態の蒸発器540は、熱伝達抑制部としての蓄冷材容器547の形状が第3実施形態の蒸発器240における蓄冷材容器247と異なる。具体的には、図31,図32に示すように、冷媒管45が流れ方向の風上側と風下側に配置される場合において、一般的に過熱域Sは風上側に生じるため、風上側のみで蓄冷材容器547が冷媒管45と接合していない点で、第3実施形態と異なる。 [Sixth Embodiment]
The sixth embodiment will be described with reference to FIGS. 31 and 32. Theevaporator 540 of the sixth embodiment is different from the cold storage material container 247 in the evaporator 240 of the third embodiment in the shape of the cold storage material container 547 as a heat transfer suppression unit. Specifically, as shown in FIGS. 31 and 32, when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side. However, it differs from the third embodiment in that the regenerator container 547 is not joined to the refrigerant pipe 45.
図31及び図32を参照して第6実施形態を説明する。第6実施形態の蒸発器540は、熱伝達抑制部としての蓄冷材容器547の形状が第3実施形態の蒸発器240における蓄冷材容器247と異なる。具体的には、図31,図32に示すように、冷媒管45が流れ方向の風上側と風下側に配置される場合において、一般的に過熱域Sは風上側に生じるため、風上側のみで蓄冷材容器547が冷媒管45と接合していない点で、第3実施形態と異なる。 [Sixth Embodiment]
The sixth embodiment will be described with reference to FIGS. 31 and 32. The
この構成を言い換えると、蒸発器540において、複数の冷媒管45は、空気通路53の空気の流れ方向に沿って少なくとも2つの冷媒管45が配置される。蓄冷材容器547は、流れ方向に沿って配置される少なくとも2つの冷媒管45と接合するよう形成される。インナフィン547bは、冷媒管45及び蓄冷材容器547の配列方向(流入方向)から視るときに少なくとも2つの冷媒管45と重畳するよう形成される。過熱域Sが発生する冷媒管45を含む少なくとも2つの冷媒管45と接合される蓄冷材容器547は、過熱域Sが発生しない冷媒管45と重畳する領域では延在方向(高さ方向)の全域に亘って冷媒管45と接合される。また、過熱域Sが発生する冷媒管45と重畳する領域では、冷媒管45の過熱域Sと接触する部分(領域547c)では冷媒管45と接合されず冷媒管45と間隔をあけて形成され、それ以外の部分547aでは冷媒管45と接合される。
In other words, in the evaporator 540, the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53. The cool storage material container 547 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction. The inner fins 547b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material containers 547. The regenerator container 547 joined to at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated extends in the extending direction (height direction) in a region overlapping with the refrigerant tube 45 in which the superheat zone S does not occur. The refrigerant pipe 45 is joined over the entire area. Further, in the region overlapping with the refrigerant tube 45 where the superheat zone S is generated, the portion (region 547c) of the refrigerant tube 45 that is in contact with the superheat zone S is not joined to the refrigerant tube 45 and is formed at an interval from the refrigerant tube 45. The other portion 547a is joined to the refrigerant pipe 45.
この構成により、第6実施形態の蒸発器540は、第3実施形態と同様の効果を奏する。また、風下側の非過熱域の冷媒管45には蓄冷材容器547やインナフィン547bが接するため、風上側から風下側へ冷熱を伝えることができ、冷媒管45から蓄冷材50への熱伝達をより一層抑制できる。また、蓄冷材容器547の容積を、第3実施形態より増大させることができるので、より多くの蓄冷材50を収容できる。
With this configuration, the evaporator 540 of the sixth embodiment has the same effects as those of the third embodiment. In addition, since the regenerator container 547 and the inner fins 547b are in contact with the refrigerant tube 45 in the non-superheated area on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the regenerator material 50 It can be further suppressed. Moreover, since the capacity | capacitance of the cool storage material container 547 can be increased from 3rd Embodiment, more cool storage materials 50 can be accommodated.
また、第6実施形態の蒸発器540は、第3実施形態にて説明した各種の変形例も適用することができる。
Also, the various modifications described in the third embodiment can be applied to the evaporator 540 of the sixth embodiment.
[第7実施形態]
図33~図38を参照して第7実施形態を説明する。第7実施形態以降は、対象とする過熱域S1が第1~第6実施形態の過熱域Sと異なる。第7実施形態に係る蒸発器1040(蓄冷熱交換器)は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する。 [Seventh Embodiment]
The seventh embodiment will be described with reference to FIGS. In the seventh and subsequent embodiments, the target superheat zone S1 is different from the superheat zone S of the first to sixth embodiments. The evaporator 1040 (cold heat storage heat exchanger) according to the seventh embodiment suppresses heat transfer from therefrigerant pipe 45 to the cold storage material 50 in the superheat region S1 generated due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low.
図33~図38を参照して第7実施形態を説明する。第7実施形態以降は、対象とする過熱域S1が第1~第6実施形態の過熱域Sと異なる。第7実施形態に係る蒸発器1040(蓄冷熱交換器)は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する。 [Seventh Embodiment]
The seventh embodiment will be described with reference to FIGS. In the seventh and subsequent embodiments, the target superheat zone S1 is different from the superheat zone S of the first to sixth embodiments. The evaporator 1040 (cold heat storage heat exchanger) according to the seventh embodiment suppresses heat transfer from the
まず、図36~図38を参照して、比較例としての従来の2ターン方式の冷媒通路を有する蒸発器2040の課題について説明する。
First, the problem of an evaporator 2040 having a conventional two-turn refrigerant passage as a comparative example will be described with reference to FIGS.
蒸発器2040では、第1ヘッダ2041に流れ込んだ冷媒は、第1熱交換部48の冷媒管45を通って第2ヘッダ2042に流れ込む(第1ターン)。第2ヘッダ2042と第4ヘッダ2044とは連通しているので、第2ヘッダ2042に流れ込んだ冷媒は第4ヘッダ2044に流れ込む。第4ヘッダ2044に流れ込んだ冷媒は、第2熱交換部49の冷媒管45を通って第3ヘッダ2043に流れこむ(第2ターン)。第3ヘッダ2043に流れ込んだ冷媒は外部に流出する。
In the evaporator 2040, the refrigerant flowing into the first header 2041 flows into the second header 2042 through the refrigerant pipe 45 of the first heat exchange unit 48 (first turn). Since the second header 2042 and the fourth header 2044 communicate with each other, the refrigerant flowing into the second header 2042 flows into the fourth header 2044. The refrigerant flowing into the fourth header 2044 flows into the third header 2043 through the refrigerant pipe 45 of the second heat exchange unit 49 (second turn). The refrigerant flowing into the third header 2043 flows out to the outside.
このような蒸発器2040では、低冷媒流量時には、冷媒通路の入口近傍である流入方向手前側の冷媒管45のみに冷媒が流れやすく、流入方向奥側の冷媒管45まで冷媒が供給されにくい。このため、冷媒通路内の冷媒の流量が少ないときには、流入方向奥側の領域に過熱域S1が存在する。なお、図37に示す過熱域S2(第2過熱域)は、第1~第6実施形態で対象とする出口近傍に発生する過熱域である。
In such an evaporator 2040, when the refrigerant flow rate is low, the refrigerant easily flows only into the refrigerant pipe 45 on the near side in the inflow direction, which is in the vicinity of the inlet of the refrigerant passage, and the refrigerant is hardly supplied to the refrigerant pipe 45 on the far side in the inflow direction. For this reason, when the flow rate of the refrigerant in the refrigerant passage is small, the overheating region S1 exists in the region on the back side in the inflow direction. Note that the superheat zone S2 (second superheat zone) shown in FIG. 37 is a superheat zone that occurs in the vicinity of the outlet targeted in the first to sixth embodiments.
第7実施形態の蒸発器1040は、このような過熱域S1の影響を受けにくくし、蓄冷材50の蓄冷性能を確保すべく、冷媒通路の構造に特徴を持たせている。蒸発器1040は、その基本構成は第1実施形態の蒸発器1040と同様であるが、冷媒通路の構成が異なり、より詳細には、第1ヘッダ1041、第2ヘッダ1042、第3ヘッダ1043、第4ヘッダ1044の内部の区画、及び、相互の連通関係が異なる。
The evaporator 1040 of the seventh embodiment is characterized by the structure of the refrigerant passage so as to be less affected by the superheated region S1 and to ensure the cold storage performance of the cold storage material 50. The basic configuration of the evaporator 1040 is the same as that of the evaporator 1040 of the first embodiment, but the configuration of the refrigerant passage is different. More specifically, the first header 1041, the second header 1042, the third header 1043, The internal section of the fourth header 1044 and the communication relationship with each other are different.
図33~図35に示すように、第1ヘッダ1041内は、第1実施形態の第1ヘッダ41とは異なり、第1区画と第2区画とは連通されている。したがって、第1ヘッダ1041に供給された冷媒は、第1群G1及び第2群G2に属する複数の冷媒管45に分配される。冷媒は、第1群G1の冷媒管45を通して第2ヘッダ1042の第1区画に流入し、第2群G2の冷媒管45を通して第2ヘッダ1042の第2区画に流入する。
As shown in FIGS. 33 to 35, in the first header 1041, unlike the first header 41 of the first embodiment, the first section and the second section are communicated. Therefore, the refrigerant supplied to the first header 1041 is distributed to the plurality of refrigerant tubes 45 belonging to the first group G1 and the second group G2. The refrigerant flows into the first section of the second header 1042 through the refrigerant pipe 45 of the first group G1, and flows into the second section of the second header 1042 through the refrigerant pipe 45 of the second group G2.
第2ヘッダ1042は、第1実施形態の第2ヘッダ42と異なり、第1区画と第2区画との間が連通不能に封止されている。同様に、第4ヘッダ1044は、第1実施形態の第4ヘッダ44と異なり、第1区画と第2区画との間が連通不能に封止されている。流入方向手前側かつ流れ方向風下側に位置する第2ヘッダ42の第1区画は、流入方向奥側かつ流れ方向風上側に位置する第4ヘッダ1044の第1区画と連通されている。流入方向奥側かつ流れ方向風下側に位置する第2ヘッダ42の第2区画は、流入方向手前側かつ流れ方向風上側に位置する第4ヘッダ1044の第2区画と連通されている。これに対応して、冷媒は、第2ヘッダ1042の第1区画から第4ヘッダ1044の第1区画に流入し、第2ヘッダ1042の第2区画から第4ヘッダ1044の第2区画に流入する。
The second header 1042 is sealed so that communication between the first section and the second section is impossible, unlike the second header 42 of the first embodiment. Similarly, unlike the 4th header 44 of 1st Embodiment, the 4th header 1044 is sealed between the 1st division and the 2nd division so that communication is impossible. The first section of the second header 42 located on the near side in the inflow direction and on the leeward side in the flow direction communicates with the first section of the fourth header 1044 located on the back side in the inflow direction and on the upwind side in the flow direction. The second section of the second header 42 located on the rear side in the inflow direction and on the leeward side in the flow direction is communicated with the second section of the fourth header 1044 located on the front side in the inflow direction and on the upwind side in the flow direction. Correspondingly, the refrigerant flows from the first section of the second header 1042 to the first section of the fourth header 1044 and flows from the second section of the second header 1042 to the second section of the fourth header 1044. .
第3ヘッダ1043内は、第1実施形態の第3ヘッダ43とは異なり、第1区画と第2区画とは連通されている。第4ヘッダ1044の第1区画に流入された冷媒は、第3群G3に属する複数の冷媒管45に分配され、第4ヘッダ1044の第2区画に流入された冷媒は、第4群G4に属する複数の冷媒管45に分配される。冷媒は、第3群G3及び第4群G4の冷媒管45を通して第3ヘッダ1043に流入し、集合される。第3ヘッダ1043内の冷媒は、冷媒出口から流出し、圧縮機10へ向けて流れる。
In the third header 1043, unlike the third header 43 of the first embodiment, the first section and the second section are communicated. The refrigerant flowing into the first section of the fourth header 1044 is distributed to the plurality of refrigerant tubes 45 belonging to the third group G3, and the refrigerant flowing into the second section of the fourth header 1044 is transferred to the fourth group G4. It is distributed to the plurality of refrigerant tubes 45 to which it belongs. The refrigerant flows into the third header 1043 through the refrigerant tubes 45 of the third group G3 and the fourth group G4, and is collected. The refrigerant in the third header 1043 flows out from the refrigerant outlet and flows toward the compressor 10.
このように、第7実施形態の蒸発器1040では、冷媒通路が、高さ方向下側の第2ヘッダタンク52において、高さ方向上側の第1ヘッダ1041から導入された冷媒の流入方向の位置を入れ替える構成をとる。つまり、流入方向の手前側から第1群G1の冷媒管45を介して導入された冷媒が流入方向の奥側へ入れ替えられ、また、流入方向の奥側から第2群G2の冷媒管45を介して導入された冷媒が流入方向の手前側に入れ替えられる。図33,図35に示すように、第2ヘッダタンク52内の冷媒通路の模式的な形状は、高さ方向から視たときにX字形状となり、また、蒸発器1040内の冷媒通路の模式的な形状は、2つの2ターン方式の冷媒通路を交差させたものとなる。第7実施形態の冷媒通路の構成を便宜的に「入替流れ方式」と表記する。
Thus, in the evaporator 1040 according to the seventh embodiment, the refrigerant passage is positioned in the inflow direction of the refrigerant introduced from the first header 1041 at the upper side in the height direction in the second header tank 52 at the lower side in the height direction. The structure which replaces is taken. That is, the refrigerant introduced from the front side in the inflow direction through the refrigerant pipe 45 of the first group G1 is replaced to the back side in the inflow direction, and the refrigerant pipe 45 of the second group G2 is connected from the back side in the inflow direction. The refrigerant introduced through is replaced with the front side in the inflow direction. As shown in FIGS. 33 and 35, the schematic shape of the refrigerant passage in the second header tank 52 is an X-shape when viewed from the height direction, and the schematic shape of the refrigerant passage in the evaporator 1040. The typical shape is obtained by intersecting two two-turn refrigerant passages. For the sake of convenience, the configuration of the refrigerant passage of the seventh embodiment is referred to as a “replacement flow method”.
第7実施形態の入替流れ方式の冷媒通路の構成は以下のように表すことができる。蒸発器1040は、複数の冷媒管45の一端側が連通し、冷媒管45及び蓄冷材容器47の配列方向(流入方向)を長手方向とするよう形成される第1ヘッダタンク51と、複数の冷媒管45の他端側が連通し、流入方向を長手方向とするよう形成される第2ヘッダタンク52と、を備える。複数の冷媒管45は、空気通路53の空気の流れ方向に沿って一対となるように2列に配置されている。第1ヘッダタンク51の内部は、第1ヘッダ1041と第3ヘッダ1043に区分される。第1ヘッダ1041は、複数の冷媒管45のうち流れ方向の下流側に配置される冷媒管45と連通され、長手方向の一端部に冷媒通路の入口が設けられる入口側通路である。第3ヘッダ1043は、流れ方向の上流側に配置される冷媒管45と連通され、長手方向の一端部(または他端部)に冷媒通路の出口が設けられる出口側通路である。
The configuration of the refrigerant flow of the replacement flow method of the seventh embodiment can be expressed as follows. The evaporator 1040 includes a first header tank 51 formed so that one end sides of the plurality of refrigerant tubes 45 communicate with each other and the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material container 47 is a longitudinal direction; And a second header tank 52 formed so that the other end side of the tube 45 communicates with the inflow direction as a longitudinal direction. The plurality of refrigerant tubes 45 are arranged in two rows so as to form a pair along the air flow direction of the air passage 53. The interior of the first header tank 51 is divided into a first header 1041 and a third header 1043. The first header 1041 is an inlet-side passage that communicates with the refrigerant pipe 45 disposed on the downstream side in the flow direction among the plurality of refrigerant pipes 45 and has an inlet of the refrigerant passage at one end in the longitudinal direction. The third header 1043 is an outlet-side passage that communicates with the refrigerant pipe 45 disposed on the upstream side in the flow direction and that has an outlet of the refrigerant passage at one end (or the other end) in the longitudinal direction.
複数の冷媒管45は、第1群G1、第2群G2、第3群G3、第4群G4に区分される。第1群G1の冷媒管45は、入口側通路としての第1ヘッダ1041と連通され、かつ、長手方向の一端部側(流入方向手前側)に配置される。第2群G2の冷媒管45は、入口側通路としての第1ヘッダ1041と連通され、かつ、長手方向の他端部側(流入方向奥側)に配置される。第3群G3の冷媒管45は、出口側通路としての第3ヘッダ1043と連通され、かつ、長手方向の他端部側に配置される。第4群G4の冷媒管45は、出口側通路としての第3ヘッダ1043と連通され、かつ、長手方向の一端部側に配置される。
The plurality of refrigerant tubes 45 are divided into a first group G1, a second group G2, a third group G3, and a fourth group G4. The refrigerant pipe 45 of the first group G1 communicates with the first header 1041 as an inlet side passage, and is disposed on one end side in the longitudinal direction (front side in the inflow direction). The refrigerant pipe 45 of the second group G2 communicates with the first header 1041 as an inlet side passage, and is disposed on the other end side in the longitudinal direction (back side in the inflow direction). The refrigerant pipe 45 of the third group G3 communicates with a third header 1043 as an outlet side passage and is disposed on the other end side in the longitudinal direction. The refrigerant pipe 45 of the fourth group G4 communicates with a third header 1043 serving as an outlet-side passage and is disposed on one end side in the longitudinal direction.
第2ヘッダタンク52は、第1群G1と第3群G3とを連通し、第2群G2と第4群G4とを連通して、第1ヘッダ1041から流入方向の手前側及び奥側に導入された冷媒をそれぞれ奥側及び手前側に入れ替えて第3ヘッダ1043に導出するよう構成される。過熱域S1は、冷媒の低流量時に冷媒通路の流量むらによって複数の冷媒管45の第2群G2及び第4群G4において発生する過熱域である。上記の冷媒通路の構成によって、図35に示すように、過熱域S1が発生する第2群G2と、過熱域S1が発生しない第3群G3との両方に単一の蓄冷材容器47が接合される構造を実現できる。同様に、過熱域S1が発生しない第1群G1と、過熱域S1が発生する第4群G4との両方に単一の蓄冷材容器47が接合される構造を実現できる。
The second header tank 52 communicates the first group G1 and the third group G3, communicates the second group G2 and the fourth group G4, and extends from the first header 1041 to the near side and the far side in the inflow direction. The introduced refrigerant is replaced with the back side and the near side, respectively, and led out to the third header 1043. The superheat zone S1 is a superheat zone that occurs in the second group G2 and the fourth group G4 of the plurality of refrigerant tubes 45 due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low. As shown in FIG. 35, a single regenerator container 47 is joined to both the second group G2 in which the superheat zone S1 is generated and the third group G3 in which the superheat zone S1 is not generated. Can be realized. Similarly, it is possible to realize a structure in which a single regenerator container 47 is joined to both the first group G1 where the superheat zone S1 does not occur and the fourth group G4 where the superheat zone S1 occurs.
このような入替流れ方式の冷媒通路の構成により、冷媒低流量時など第1ヘッダ1041に導入された冷媒が流入方向の奥側に流れにくい状況においても、第1群G1及び第3群G3の冷媒管45を介して、比較的流量の多い冷媒の流れを流入方向の全域に亘って提供できる。つまり冷媒低流量時でも流入方向奥側に冷媒を良好に流すことができる。単一の蓄冷材容器47は、流れ方向に並列される2つの冷媒管45と接合されるが、これらの冷媒管45の一方には比較的流量の多い冷媒が流れる。これにより、蓄冷材容器47が接合される2つの冷媒管45の他方に過熱域S1が発生したとしても、過熱域S1にある蓄冷材50に対して非過熱域の冷熱を伝えることができるので、蓄冷材容器47内の蓄冷材50を良好に冷やすことができる。
With such a configuration of the refrigerant flow of the replacement flow method, even when the refrigerant introduced into the first header 1041 is difficult to flow to the back side in the inflow direction, such as when the refrigerant has a low flow rate, the first group G1 and the third group G3 A refrigerant flow having a relatively high flow rate can be provided over the entire area in the inflow direction via the refrigerant pipe 45. That is, the refrigerant can be satisfactorily flowed to the back side in the inflow direction even when the refrigerant has a low flow rate. The single cool storage material container 47 is joined to two refrigerant pipes 45 arranged in parallel in the flow direction, and a refrigerant having a relatively high flow rate flows through one of these refrigerant pipes 45. Thereby, even if the overheating region S1 occurs in the other of the two refrigerant tubes 45 to which the regenerator container 47 is joined, the cold energy in the non-overheating region can be transmitted to the regenerator material 50 in the overheating region S1. The cool storage material 50 in the cool storage material container 47 can be cooled well.
つまり、第7実施形態では、入替流れ方式の冷媒通路によって第2ヘッダタンク52において冷媒の流入方向の位置を入れ替えることにより、過熱域S1が発生する冷媒管45と、過熱域が発生しない冷媒管45との両方に単一の蓄冷材容器47が接合されるという冷媒通路構造1045に特徴がある。この冷媒通路構造1045が、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する「熱伝達抑制部」として機能する。そして、このような冷媒通路構造1045を設けることにより、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制することができ、冷媒温度が高温となる過熱域S1の影響により蓄冷材50が冷えにくくなる状況を回避できる。この結果、第7実施形態の蓄冷熱交換器としての蒸発器1040は、過熱域S1が存在する場合でも、過熱域S1の影響を受けにくくし、蓄冷性能を確保できる。
That is, in the seventh embodiment, the refrigerant pipe 45 in which the superheat zone S1 is generated and the refrigerant pipe in which no superheat zone is generated are obtained by changing the position of the refrigerant inflow direction in the second header tank 52 by the refrigerant flow of the replacement flow method. The refrigerant passage structure 1045 is characterized in that a single cold storage material container 47 is joined to both of them. The refrigerant passage structure 1045 functions as a “heat transfer suppression unit” that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow of the refrigerant passage when the flow rate of the refrigerant is low. By providing such a refrigerant passage structure 1045, heat transfer from the refrigerant pipe 45 to the regenerator material 50 in the overheat region S1 can be suppressed, and the regenerator material is affected by the overheat region S1 where the refrigerant temperature becomes high. It is possible to avoid a situation where 50 becomes difficult to cool. As a result, the evaporator 1040 as the cold storage heat exchanger of the seventh embodiment is less susceptible to the influence of the superheat zone S1 even when the superheat zone S1 exists, and can secure the cold storage performance.
また、蓄冷材容器47の表面には凹凸があり、凸部が冷媒管45と接合する構成でもよい。
Further, the surface of the cold storage material container 47 may be uneven, and the protrusion may be joined to the refrigerant pipe 45.
[第7実施形態の変形例]
図39~図42を参照して第7実施形態の変形例について説明する。第7実施形態では一組の入替流れ方式の冷媒通路、すなわち、第2ヘッダタンク52において冷媒の流入方向の位置の入れ替わりが1か所である冷媒通路構造1045を例示したが、少なくとも一組の入替流れ方式の冷媒通路を含めば他の構成としてもよい。例えば図39、図40に示される蒸発器1040Aは、一組の入替流れ方式と、従来の2ターン方式とを併用している。図41,図42に示される蒸発器1040Bは、二組の入替流れ方式の冷媒通路が併用され、流入方向に沿って設けられている。さらに、複数組の入替流れ方式の冷媒通路を流入方向に沿って設けることもできる。蒸発器1040Aや蒸発器1040Bの冷媒通路の構成によっても、第7実施形態の冷媒通路構造1045と同様の構造を実現できるので、第7実施形態の蒸発器1040と同様の作用効果を奏することができる。 [Modification of the seventh embodiment]
A modification of the seventh embodiment will be described with reference to FIGS. In the seventh embodiment, therefrigerant passage structure 1045 having one set of refrigerant flow in the inflow direction of the refrigerant in the second header tank 52 is illustrated as an example. Other configurations may be used as long as they include a replacement flow type refrigerant passage. For example, the evaporator 1040A shown in FIG. 39 and FIG. 40 uses a pair of replacement flow methods and a conventional two-turn method in combination. The evaporator 1040B shown in FIG. 41 and FIG. 42 is provided along the inflow direction in which two sets of refrigerant passages of a replacement flow method are used in combination. Furthermore, a plurality of replacement flow-type refrigerant passages can be provided along the inflow direction. The structure of the refrigerant passages of the evaporator 1040A and the evaporator 1040B can also realize the same structure as the refrigerant passage structure 1045 of the seventh embodiment, and thus the same effects as the evaporator 1040 of the seventh embodiment can be achieved. it can.
図39~図42を参照して第7実施形態の変形例について説明する。第7実施形態では一組の入替流れ方式の冷媒通路、すなわち、第2ヘッダタンク52において冷媒の流入方向の位置の入れ替わりが1か所である冷媒通路構造1045を例示したが、少なくとも一組の入替流れ方式の冷媒通路を含めば他の構成としてもよい。例えば図39、図40に示される蒸発器1040Aは、一組の入替流れ方式と、従来の2ターン方式とを併用している。図41,図42に示される蒸発器1040Bは、二組の入替流れ方式の冷媒通路が併用され、流入方向に沿って設けられている。さらに、複数組の入替流れ方式の冷媒通路を流入方向に沿って設けることもできる。蒸発器1040Aや蒸発器1040Bの冷媒通路の構成によっても、第7実施形態の冷媒通路構造1045と同様の構造を実現できるので、第7実施形態の蒸発器1040と同様の作用効果を奏することができる。 [Modification of the seventh embodiment]
A modification of the seventh embodiment will be described with reference to FIGS. In the seventh embodiment, the
[第8実施形態]
図43~図45を参照して第8実施形態を説明する。第8実施形態の蒸発器1140は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成として、第7実施形態の構成に加えて、さらにインナフィン1147bによる機能も追加している点で、第7実施形態の蒸発器1040と異なる。具体的には、図43~図45に示すように、過熱域S1(風下側奥側、風上側手前側)に接する蓄冷材容器1147において、インナフィン1147bがこの過熱域S1と接していない点が第7実施形態の蒸発器1040と異なる。 [Eighth Embodiment]
The eighth embodiment will be described with reference to FIGS. 43 to 45. Theevaporator 1140 according to the eighth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 generated due to uneven flow of the refrigerant passage when the refrigerant is at a low flow rate. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the inner fin 1147b in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS. 43 to 45, in the cold storage material container 1147 that is in contact with the superheat zone S1 (the leeward rear side, the windward front side), the inner fin 1147b is not in contact with the superheat zone S1. Different from the evaporator 1040 of the seventh embodiment.
図43~図45を参照して第8実施形態を説明する。第8実施形態の蒸発器1140は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成として、第7実施形態の構成に加えて、さらにインナフィン1147bによる機能も追加している点で、第7実施形態の蒸発器1040と異なる。具体的には、図43~図45に示すように、過熱域S1(風下側奥側、風上側手前側)に接する蓄冷材容器1147において、インナフィン1147bがこの過熱域S1と接していない点が第7実施形態の蒸発器1040と異なる。 [Eighth Embodiment]
The eighth embodiment will be described with reference to FIGS. 43 to 45. The
この構成を言い換えると、インナフィン1147bは、蓄冷材容器1147の内部において蓄冷材容器1147の長手方向(高さ方向)に沿って延在するよう配置される。インナフィン1147bは、過熱域S1が発生する冷媒管45の第2群G2及び第4群G4と蓄冷材容器1147とが接合する部分(図43中のB7-B7断面)では蓄冷材容器1147の内壁と接合されない。また、過熱域S1が発生しない冷媒管45の第1群G1及び第3群G3と蓄冷材容器1147とが接触する部分(図43中のA7-A7断面)では蓄冷材容器1147の内壁と接合される。このインナフィン1147bは、熱伝達抑制部として機能する。
In other words, the inner fins 1147b are arranged so as to extend along the longitudinal direction (height direction) of the cool storage material container 1147 inside the cool storage material container 1147. Inner fin 1147b is an inner wall of regenerator container 1147 at the portion where refrigerant storage container 1147 joins second group G2 and fourth group G4 of refrigerant pipe 45 where superheat zone S1 occurs (cross section B7-B7 in FIG. 43). Not joined with. Further, in the portion where the first group G1 and third group G3 of the refrigerant pipe 45 where the superheat zone S1 does not occur and the cool storage material container 1147 contact (cross section A7-A7 in FIG. 43), the inner wall of the cool storage material container 1147 is joined. Is done. This inner fin 1147b functions as a heat transfer suppression unit.
この構成により、第8実施形態の蒸発器1140は、第7実施形態と同様の効果を奏する。また、過熱域S1でインナフィン1147bが蓄冷材容器1147と接していないため、過熱域S1の温熱が蓄冷材容器1147内の蓄冷材50に伝わりにくくなる。このため、過熱域S1の温熱の影響を受けずに非過熱域の冷熱で蓄冷材容器1147の内部の蓄冷材をより一層好適に冷やすことができる。
With this configuration, the evaporator 1140 of the eighth embodiment has the same effects as those of the seventh embodiment. Moreover, since the inner fin 1147b is not in contact with the cold storage material container 1147 in the superheat zone S1, the heat in the superheat zone S1 is not easily transmitted to the cold storage material 50 in the cold storage material vessel 1147. For this reason, the cool storage material inside the cool storage material container 1147 can be more suitably cooled by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
なお、第8実施形態のインナフィン1147bと蓄冷材容器1147との接合構造は上記のものに限定されず、過熱域S1における冷媒管45からインナフィン1147bを介しての蓄冷材50への伝熱量が過熱域S1以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域S1におけるインナフィン1147bの伝熱性能を他の部分より相対的に低くできればよい。例えば図11を参照して第1実施形態にて説明したのと同様に、インナフィン1171bが、冷媒管45の過熱域S1と接触する部分では蓄冷材容器1147の外殻1147aの内壁面との接合率が相対的に低くなるよう接合され、冷媒管45の過熱域S1以外と接触する部分では内壁面との接合率が相対的に高くなるよう接合される構成とすることができる。このように、過熱域S1におけるインナフィン1147bを介しての伝熱量を相対的に小さくする、または、インナフィン1147bと蓄冷材容器1147との接合率を相対的に低くすることにより、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制でき、本実施形態の蒸発器1140と同様の効果が得られる。
In addition, the joining structure of the inner fin 1147b and the cool storage material container 1147 of the eighth embodiment is not limited to the above, and the heat transfer amount from the refrigerant pipe 45 to the cool storage material 50 through the inner fin 1147b in the superheat region S1 is superheated. Other configurations may be used as long as they are relatively smaller than the heat transfer amount other than the region S1. In other words, it is only necessary that the heat transfer performance of the inner fin 1147b in the superheat region S1 can be made relatively lower than other portions. For example, as described in the first embodiment with reference to FIG. 11, the inner fin 1171 b is joined to the inner wall surface of the outer shell 1147 a of the regenerator container 1147 at a portion where the inner fin 1171 b is in contact with the superheated region S 1 of the refrigerant pipe 45. It can be set as the structure joined so that a rate may be relatively low, and in the part which contacts except the overheating area S1 of the refrigerant | coolant pipe | tube 45, a joining rate with an inner wall surface may become relatively high. In this way, the refrigerant in the superheated region S1 can be obtained by relatively reducing the amount of heat transfer through the inner fins 1147b in the superheated region S1 or by relatively reducing the joining rate between the inner fins 1147b and the cold storage material container 1147. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1140 of the present embodiment can be obtained.
また、図12を参照して第1実施形態にて説明した構成と同様に、インナフィン1147bの波型形状が蓄冷材容器1147の短手方向(流れ方向)に連続する構成、すなわち、インナフィン1147bの峰と谷が高さ方向に沿って延びている構成としてもよい。この場合、インナフィン1147bの峰及び谷は、流れ方向に沿って冷媒管45の過熱域S1と接触するものは蓄冷材容器1147の外殻1147aの内壁面と接合されず、冷媒管45の過熱域S1以外と接触するものは内壁面と接合される。この構成でも、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制でき、本実施形態の蒸発器1140と同様の効果が得られる。
Further, similarly to the configuration described in the first embodiment with reference to FIG. 12, the configuration in which the wave shape of the inner fin 1147b is continuous in the short direction (flow direction) of the cold storage material container 1147, that is, the inner fin 1147b. It is good also as a structure where the peak and trough are extended along the height direction. In this case, the ridges and valleys of the inner fins 1147b are not joined to the inner wall surface of the outer shell 1147a of the regenerator container 1147 along the flow direction, and are not joined to the superheat region of the refrigerant tube 45. Those in contact with other than S1 are joined to the inner wall surface. Even in this configuration, heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 can be suppressed, and the same effect as the evaporator 1140 of the present embodiment can be obtained.
[第9実施形態]
図46~図48を参照して第9実施形態を説明する。第9実施形態の蒸発器1240は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成として、第7実施形態の構成に加えて、さらに蓄冷材容器1247による機能も追加している点で、第7実施形態の蒸発器1040と異なる。具体的には、図46~図48に示すように、過熱域S1(風下側奥側、風上側手前側)に接する蓄冷材容器1247が、この過熱域S1を発生させる冷媒管45に接合しない点で第7実施形態の蒸発器1040と異なる。また、第9実施形態の蒸発器1240は、蓄冷材容器1247の内部にインナフィンを設けない点が第7実施形態の蒸発器1040と異なる。 [Ninth Embodiment]
The ninth embodiment will be described with reference to FIGS. 46 to 48. FIG. Theevaporator 1240 according to the ninth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow rate of the refrigerant passage when the flow rate of the refrigerant is low. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the cool storage material container 1247 in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS. 46 to 48, the regenerator container 1247 that is in contact with the superheat zone S1 (the leeward side rear side, the windward front side) is not joined to the refrigerant pipe 45 that generates the superheat zone S1. This differs from the evaporator 1040 of the seventh embodiment. Moreover, the evaporator 1240 of 9th Embodiment differs from the evaporator 1040 of 7th Embodiment by the point which does not provide an inner fin in the inside of the cool storage material container 1247. FIG.
図46~図48を参照して第9実施形態を説明する。第9実施形態の蒸発器1240は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成として、第7実施形態の構成に加えて、さらに蓄冷材容器1247による機能も追加している点で、第7実施形態の蒸発器1040と異なる。具体的には、図46~図48に示すように、過熱域S1(風下側奥側、風上側手前側)に接する蓄冷材容器1247が、この過熱域S1を発生させる冷媒管45に接合しない点で第7実施形態の蒸発器1040と異なる。また、第9実施形態の蒸発器1240は、蓄冷材容器1247の内部にインナフィンを設けない点が第7実施形態の蒸発器1040と異なる。 [Ninth Embodiment]
The ninth embodiment will be described with reference to FIGS. 46 to 48. FIG. The
この構成を言い換えると、蓄冷材容器1247は、過熱域S1が発生する冷媒管45の第2群G2及び第4群G4と接触する部分(図46中のB8-B8断面、領域1247c)では冷媒管45と接合されず冷媒管45と間隔をあけて形成される。また、過熱域S1が発生しない冷媒管45の第1群G1及び第3群G3と接触する部分(図46中のA8-A8断面、外殻1247a)において冷媒管45と接合される。この蓄冷材容器1247が熱伝達抑制部として機能する。
In other words, the regenerator container 1247 has a refrigerant in a portion (cross section B8-B8 in FIG. 46, region 1247c) in contact with the second group G2 and the fourth group G4 of the refrigerant pipe 45 in which the superheat zone S1 is generated. It is not joined to the pipe 45 and is formed at a distance from the refrigerant pipe 45. Further, the refrigerant pipe 45 is joined to the refrigerant pipe 45 at a portion (cross section A8-A8 in FIG. 46, outer shell 1247a) of the refrigerant pipe 45 that does not generate the superheat zone S1 and is in contact with the first group G1 and the third group G3. This cool storage material container 1247 functions as a heat transfer suppression unit.
この構成により、第9実施形態の蒸発器1240は、第7実施形態と同様の効果を奏する。また、過熱域S1で蓄冷材容器1247が冷媒管45と接していないため、過熱域S1の温熱が蓄冷材容器1247内の蓄冷材50に伝わりにくくなる。このため、過熱域S1の温熱の影響を受けずに非過熱域の冷熱で蓄冷材容器1247の内部の蓄冷材50をより一層好適に冷やすことができる。
With this configuration, the evaporator 1240 of the ninth embodiment has the same effects as those of the seventh embodiment. Further, since the regenerator container 1247 is not in contact with the refrigerant pipe 45 in the overheat region S1, the heat in the overheat region S1 is not easily transmitted to the regenerator material 50 in the regenerator container 1247. For this reason, the cool storage material 50 inside the cool storage material container 1247 can be cooled more suitably by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
なお、第9実施形態の蓄冷材容器1247の形状は、上記のものに限定されず、過熱域S1における冷媒管45から蓄冷材容器1247を介しての蓄冷材50への伝熱量が過熱域S1以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域S1における蓄冷材容器1247の伝熱性能を他の部分より相対的に低くできればよい。例えば図23を参照して第2実施形態にて説明した構成と同様に、蓄冷材容器1247が、冷媒管45の過熱域S1と接触する部分(領域1247c)では冷媒管45との接合率が相対的に低くなるように接合され、冷媒管45の過熱域S1以外と接触する部分(外殻1247a)において冷媒管45との接合率が相対的に高くなるよう接合される構成とすることができる。このように、過熱域S1における蓄冷材容器1247の伝熱量を相対的に小さくする、または、蓄冷材容器1247と冷媒管45との接合率を相対的に低くすることにより、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制でき、本実施形態の蒸発器1240と同様の効果が得られる。
In addition, the shape of the cool storage material container 1247 of 9th Embodiment is not limited to the above thing, The heat transfer amount from the refrigerant | coolant pipe | tube 45 in the superheat zone S1 to the cool storage material 50 via the cool storage material container 1247 is superheat zone S1. Any other configuration may be used as long as it is relatively smaller than the heat transfer amount. In other words, the heat transfer performance of the cool storage material container 1247 in the superheat region S1 only needs to be relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG. 23, in the portion (region 1247 c) where the cold storage material container 1247 is in contact with the superheated region S <b> 1 of the refrigerant tube 45, the joining rate with the refrigerant tube 45 is It is configured to be joined so as to be relatively low, and to be joined so that the joining ratio with the refrigerant pipe 45 is relatively high in a portion (outer shell 1247a) in contact with the refrigerant pipe 45 other than the superheated region S1. it can. In this way, the refrigerant in the superheat zone S1 can be obtained by relatively reducing the heat transfer amount of the cold storage material container 1247 in the superheat zone S1 or by relatively reducing the joining rate between the cool storage material vessel 1247 and the refrigerant pipe 45. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1240 of this embodiment can be obtained.
[第10実施形態]
図49~図51を参照して第10実施形態を説明する。第10実施形態の蒸発器1340は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成として、第7実施形態の構成に加えて、さらに蓄冷材容器1247による機能も追加している点で、第7実施形態の蒸発器1040と異なる。具体的には、図49~図51に示すように、過熱域S1(風下側奥側、風上側手前側)に接する蓄冷材容器1247が、この過熱域S1を発生させる冷媒管45に接合しない点で第7実施形態の蒸発器1040と異なる。 [Tenth embodiment]
The tenth embodiment will be described with reference to FIGS. 49 to 51. Theevaporator 1340 of the tenth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow of the refrigerant passage when the refrigerant is at a low flow rate. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the cool storage material container 1247 in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS. 49 to 51, the regenerator container 1247 that is in contact with the superheat zone S1 (the leeward side rear side, the windward front side) is not joined to the refrigerant pipe 45 that generates the superheat zone S1. This differs from the evaporator 1040 of the seventh embodiment.
図49~図51を参照して第10実施形態を説明する。第10実施形態の蒸発器1340は、冷媒の低流量時に冷媒通路の流量むらにより発生する過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する熱伝達抑制部の構成として、第7実施形態の構成に加えて、さらに蓄冷材容器1247による機能も追加している点で、第7実施形態の蒸発器1040と異なる。具体的には、図49~図51に示すように、過熱域S1(風下側奥側、風上側手前側)に接する蓄冷材容器1247が、この過熱域S1を発生させる冷媒管45に接合しない点で第7実施形態の蒸発器1040と異なる。 [Tenth embodiment]
The tenth embodiment will be described with reference to FIGS. 49 to 51. The
この構成を言い換えると、インナフィン1347bは、蓄冷材容器1347の内部において蓄冷材容器1347の長手方向(高さ方向)に沿って延在するよう配置され、蓄冷材容器1347の内壁と長手方向の全域に亘って接合される。蓄冷材容器1347は、過熱域S1が発生する冷媒管45の第2群G2及び第4群G4と接触する部分(図49中のB9-B9断面、領域1347c)では冷媒管45と接合されず冷媒管45と間隔をあけて形成される。また、過熱域S1が発生しない冷媒管45の第1群G1及び第3群G3と接触する部分(図49中のA9-A9断面、外殻1347a)において冷媒管45と接合される。この蓄冷材容器1347が熱伝達抑制部として機能する。
In other words, the inner fin 1347b is arranged so as to extend along the longitudinal direction (height direction) of the cold storage material container 1347 inside the cold storage material container 1347, and the inner wall of the cold storage material container 1347 and the entire area in the longitudinal direction. Are joined. The regenerator container 1347 is not joined to the refrigerant pipe 45 at a portion (cross section B9-B9 in FIG. 49, region 1347c) of the refrigerant pipe 45 where the superheated area S1 is in contact with the second group G2 and the fourth group G4. It is formed at a distance from the refrigerant pipe 45. In addition, the refrigerant pipe 45 is joined to the refrigerant pipe 45 at a portion (cross section A9-A9 in FIG. 49, outer shell 1347a) of the refrigerant pipe 45 that does not generate the superheat zone S1 and is in contact with the first group G1 and the third group G3. This cool storage material container 1347 functions as a heat transfer suppression unit.
この構成により、第10実施形態の蒸発器1340は、第7実施形態と同様の効果を奏する。また、過熱域S1で蓄冷材容器1347が冷媒管45と接していないため、過熱域S1の温熱が蓄冷材容器1347内の蓄冷材50に伝わりにくくなる。また、蓄冷材容器1347の内部にインナフィン1347bが設けられるので、非過熱側の冷熱を過熱域側に伝えやすい。このため、過熱域S1の温熱の影響を受けずに非過熱域の冷熱で蓄冷材容器1347の内部の蓄冷材50をより一層好適に冷やすことができる。
With this configuration, the evaporator 1340 of the tenth embodiment has the same effects as those of the seventh embodiment. Further, since the regenerator material container 1347 is not in contact with the refrigerant pipe 45 in the overheat region S1, the heat in the overheat region S1 is not easily transmitted to the regenerator material 50 in the regenerator material container 1347. Moreover, since the inner fin 1347b is provided in the inside of the cool storage material container 1347, it is easy to convey the cold on the non-superheated side to the superheated region side. For this reason, the cool storage material 50 inside the cool storage material container 1347 can be more suitably cooled by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
なお、第10実施形態の蒸発器1340でも、第8実施形態と同様に、インナフィン1347bが、過熱域S1が発生する冷媒管45の第2群G2及び第4群G4と蓄冷材容器1347とが接合する部分(領域1347c)では蓄冷材容器1347の内壁と接合されない構成としてもよい。この構成により、過熱域S1ではインナフィン1347bが蓄冷材容器1347、つまり冷媒管45に接合していないため、過熱冷媒からの温熱が蓄冷材50の内部へより一層伝わりにくくなる。
In the evaporator 1340 of the tenth embodiment, as in the eighth embodiment, the inner fin 1347b includes the second group G2 and the fourth group G4 of the refrigerant pipe 45 in which the superheat zone S1 is generated and the cold storage material container 1347. It is good also as a structure which is not joined with the inner wall of the cool storage material container 1347 in the part (area | region 1347c) to join. With this configuration, the inner fin 1347b is not joined to the regenerator container 1347, that is, the refrigerant pipe 45, in the superheat region S1, so that the heat from the superheated refrigerant is more difficult to be transmitted to the inside of the regenerator 50.
なお、第10実施形態の蓄冷材容器1347の形状は、上記のものに限定されず、過熱域S1における冷媒管45から蓄冷材容器1247を介しての蓄冷材50への伝熱量が過熱域S1以外の伝熱量より相対的に小さくなれば他の構成でもよい。言い換えると、過熱域S1における蓄冷材容器1347の伝熱性能を他の部分より相対的に低くできればよい。例えば、図23を参照して第2実施形態にて説明した構成と同様に、蓄冷材容器21347が、冷媒管45の過熱域S1と接触する部分(領域1347c)では冷媒管45との接合率が相対的に低くなるように接合され、冷媒管45の過熱域S1以外と接触する部分(外殻1347a)において冷媒管45との接合率が相対的に高くなるよう接合される構成とすることができる。このように、過熱域S1における蓄冷材容器1347の伝熱量を相対的に小さくする、または、蓄冷材容器1347と冷媒管45との接合率を相対的に低くすることにより、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制でき、本実施形態の蒸発器1340と同様の効果が得られる。
In addition, the shape of the cool storage material container 1347 of 10th Embodiment is not limited to the said thing, The heat transfer amount from the refrigerant | coolant pipe | tube 45 in the superheat zone S1 to the cool storage material 50 via the cool storage material container 1247 is superheat zone S1. Any other configuration may be used as long as it is relatively smaller than the heat transfer amount. In other words, the heat transfer performance of the cool storage material container 1347 in the superheat region S1 only needs to be relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG. 23, the joint ratio with the refrigerant pipe 45 in the portion (region 1347 c) where the cold storage material container 21347 is in contact with the superheated area S <b> 1 of the refrigerant pipe 45. Are connected so as to be relatively low, and in a portion (outer shell 1347a) in contact with the refrigerant pipe 45 other than the superheated region S1, the joining ratio with the refrigerant pipe 45 is relatively high. Can do. In this way, the refrigerant in the superheat zone S1 can be obtained by relatively reducing the heat transfer amount of the cold storage material container 1347 in the superheat zone S1 or by relatively reducing the joining rate between the cool storage material vessel 1347 and the refrigerant pipe 45. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1340 of this embodiment can be obtained.
さらに、第8実施形態と同様にインナフィン1347bと蓄冷材容器1347との接合構成によって過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制する構成を適用する場合には、図11を参照して第1実施形態にて説明したのと同様の構成を適用できる。具体的には、インナフィン1347bが、冷媒管45の過熱域S1と接触する部分では蓄冷材容器1347の外殻1347aの内壁面との接合率が相対的に低くなるよう接合され、冷媒管45の過熱域S1以外と接触する部分では内壁面との接合率が相対的に高くなるよう接合される構成とすることができる。このように、インナフィン1347bと蓄冷材容器1347との接合率を相対的に低くすることによっても、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制でき、本実施形態の蒸発器1340と同様の効果が得られる。
Furthermore, when applying the structure which suppresses the heat transfer from the refrigerant | coolant pipe | tube 45 in the superheat zone S1 to the cool storage material 50 by the joining structure of the inner fin 1347b and the cool storage material container 1347 similarly to 8th Embodiment, FIG. A configuration similar to that described with reference to the first embodiment can be applied. Specifically, the inner fin 1347b is joined so that the joining ratio with the inner wall surface of the outer shell 1347a of the regenerator container 1347 is relatively low at the portion where the inner fin 1347b is in contact with the superheated region S1 of the refrigerant tube 45. It can be set as the structure joined so that a joining rate with an inner wall surface may become relatively high in the part which contacts other than superheat zone S1. Thus, the heat transfer from the refrigerant pipe 45 to the cool storage material 50 in the superheated region S1 can be suppressed by relatively reducing the joining rate between the inner fins 1347b and the cool storage material container 1347, and the evaporator according to the present embodiment. The same effect as 1340 is obtained.
また、図12を参照して第1実施形態にて説明した構成と同様に、インナフィン1347bの波型形状が蓄冷材容器1347の短手方向(流れ方向)に連続する構成、すなわち、インナフィン1347bの峰と谷が高さ方向に沿って延びている構成としてもよい。この構成でも、過熱域S1における冷媒管45から蓄冷材50への熱伝達を抑制でき、本実施形態の蒸発器1340と同様の効果が得られる。
Further, similarly to the configuration described in the first embodiment with reference to FIG. 12, a configuration in which the wave shape of the inner fin 1347b is continuous in the short direction (flow direction) of the cold storage material container 1347, that is, the inner fin 1347b It is good also as a structure where the peak and trough are extended along the height direction. Even in this configuration, heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 can be suppressed, and the same effect as the evaporator 1340 of the present embodiment can be obtained.
[第11実施形態]
図52を参照して第11実施形態を説明する。第11実施形態の蒸発器1440は、複数の冷媒管45のうち、過熱域S1が発生する第2群G2及び第4群G4と接触する部分に、他の部分(本実施形態では第1群G1)と比較して相対的に融点の高い高融点蓄冷材50Aが配置され、さらに、過熱域S2が発生する第3群G3と接触する部分にも高融点蓄冷材50Aが配置される点で、第7実施形態の蒸発器1040(図33~図35参照)と異なる。 [Eleventh embodiment]
The eleventh embodiment will be described with reference to FIG. Theevaporator 1440 according to the eleventh embodiment includes other portions (the first group in the present embodiment) that are in contact with the second group G2 and the fourth group G4 where the superheat zone S1 is generated, among the plurality of refrigerant tubes 45. The high melting point regenerator material 50A having a relatively high melting point compared to G1) is arranged, and further, the high melting point regenerator material 50A is also arranged in the portion that contacts the third group G3 where the superheat zone S2 is generated. This differs from the evaporator 1040 of the seventh embodiment (see FIGS. 33 to 35).
図52を参照して第11実施形態を説明する。第11実施形態の蒸発器1440は、複数の冷媒管45のうち、過熱域S1が発生する第2群G2及び第4群G4と接触する部分に、他の部分(本実施形態では第1群G1)と比較して相対的に融点の高い高融点蓄冷材50Aが配置され、さらに、過熱域S2が発生する第3群G3と接触する部分にも高融点蓄冷材50Aが配置される点で、第7実施形態の蒸発器1040(図33~図35参照)と異なる。 [Eleventh embodiment]
The eleventh embodiment will be described with reference to FIG. The
図34を参照して説明したように、入替流れ形式の冷媒流路構造1045では、冷媒の低流量時に冷媒通路の流量むらによって、複数の冷媒管45の第2群G2及び第4群G4において過熱域S1が発生する。また、複数の冷媒管45の第3群G3の出口近傍には、第1~第6実施形態の過熱域Sと同様の仕組みによって過熱域S2が発生する。第11実施形態では、これらの過熱域S1,S2が発生する冷媒管45(すなわち第2群G2、第3群G3、第4群G4)と接触する蓄冷材容器47の内部には高融点蓄冷材50Aが収容されている。
As described with reference to FIG. 34, in the refrigerant flow structure 1045 of the replacement flow type, in the second group G2 and the fourth group G4 of the plurality of refrigerant pipes 45 due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low. An overheating zone S1 occurs. Further, in the vicinity of the outlet of the third group G3 of the plurality of refrigerant tubes 45, the superheat zone S2 is generated by the same mechanism as the superheat zone S of the first to sixth embodiments. In the eleventh embodiment, a high-melting-point regenerator is provided inside the regenerator container 47 in contact with the refrigerant tubes 45 (that is, the second group G2, the third group G3, and the fourth group G4) in which these superheat zones S1 and S2 are generated. The material 50A is accommodated.
ここで、冷媒管45の第1群G1及び第4群G4の両方と接触する蓄冷材容器47は、図52に示すように、第1群G1と接触する部分(流れ方向の風下側の半分)に通常の融点の蓄冷材50が充填され、第4群G4と接触する部分(流れ方向の風上側の半分)には高融点蓄冷材50Aが充填されている。このような構成は、例えば蓄冷材容器47の流れ方向の略中間の位置に仕切り板を内蔵させ、単一の蓄冷材容器47の内部空間を区分することにより実現できる。なお、冷媒管45の第2群G2及び第3群G3の両方と接触する蓄冷材容器47では、単に内部空間の全体に高融点蓄冷材50Aを充填すればよい。
Here, as shown in FIG. 52, the regenerator container 47 that contacts both the first group G1 and the fourth group G4 of the refrigerant pipe 45 is in contact with the first group G1 (half of the leeward side in the flow direction). ) Is filled with a normal regenerator material 50, and a portion (half of the windward side in the flow direction) in contact with the fourth group G4 is filled with a high-melting regenerator material 50A. Such a configuration can be realized, for example, by incorporating a partition plate at a substantially intermediate position in the flow direction of the cool storage material container 47 and partitioning the internal space of the single cool storage material container 47. In the regenerator container 47 that contacts both the second group G2 and the third group G3 of the refrigerant pipe 45, the entire internal space may be simply filled with the high melting point regenerator material 50A.
高融点蓄冷材50Aを適用して蓄冷材の融点が高くすると、蓄冷材を冷やす冷媒との温度差が大きくなるため、蓄冷材がより冷えやすくなる(凝固しやすくなる)。例えば、冷媒管45の通常の領域における冷媒の温度を-3℃、冷媒管45の過熱域S1,S2における冷媒の温度を0℃、冷媒管45の通常領域の冷媒と熱交換する蓄冷材の融点を5℃と仮定する。このとき、冷媒管45の過熱域S1,S2の冷媒と熱交換する蓄冷材の融点が、通常領域における蓄冷材の融点と同一の場合には、過熱域S1,S2では相対的に蓄冷材が凝固しにくくなり、過熱域S1,S2における蓄冷材の凝固性は通常領域より低くなる。一方、過熱域S1,S2における蓄冷材の融点を、通常領域における蓄冷材の融点に対して、通常領域と過熱域S1,S2の冷媒間の温度差(ここでは+3℃)の分だけ高くすれば、過熱域S1,S2における蓄冷材の凝固性は通常領域と同等となる。また、過熱域S1,S2の蓄冷材の融点を、通常領域における蓄冷材の融点に対して通常領域と過熱域S1,S2の冷媒間の温度差より高くすれば、過熱域S1,S2における蓄冷材の凝固性は通常領域より向上する。
If the high-melting-point regenerator material 50A is used to increase the melting point of the regenerator material, the temperature difference from the refrigerant that cools the regenerator material increases, so the regenerator material becomes easier to cool (is more likely to solidify). For example, the temperature of the refrigerant in the normal region of the refrigerant pipe 45 is −3 ° C., the temperature of the refrigerant in the superheated areas S1 and S2 of the refrigerant pipe 45 is 0 ° C., and a cold storage material that exchanges heat with the refrigerant in the normal region of the refrigerant pipe 45 is used. The melting point is assumed to be 5 ° C. At this time, when the melting point of the regenerator material that exchanges heat with the refrigerant in the superheat regions S1 and S2 of the refrigerant pipe 45 is the same as the melting point of the regenerator material in the normal region, the regenerator material is relatively in the overheat regions S1 and S2. It becomes difficult to solidify, and the solidification property of the regenerator material in the superheat regions S1 and S2 is lower than the normal region. On the other hand, the melting point of the regenerator material in the superheat regions S1 and S2 is set higher than the melting point of the regenerator material in the normal region by the temperature difference (here, + 3 ° C.) between the refrigerant in the normal region and the superheat regions S1 and S2. For example, the solidification property of the regenerator material in the superheat regions S1 and S2 is equivalent to that in the normal region. In addition, if the melting point of the regenerator material in the superheat regions S1 and S2 is higher than the temperature difference between the refrigerant in the normal region and the superheat regions S1 and S2 with respect to the melting point of the regenerator material in the normal region, the regenerator in the superheat regions S1 and S2 The solidification of the material is improved over the normal range.
このように、第11実施形態の蒸発器1440は、過熱域S1,S2が発生する冷媒管45と接触する部分に高融点蓄冷材50Aを配置する構成とすることにより、蓄冷材と熱交換する冷媒が過熱域S1,S2のものか通常領域のものかに依存することなく、蓄冷材の凝固性を均一にすることができる。これにより、過熱域S1,S2の影響を受けにくくすることができ、蒸発器1440の蓄放熱性能を高めることができる。
Thus, the evaporator 1440 of the eleventh embodiment exchanges heat with the regenerator material by arranging the high-melting-point regenerator material 50A in the portion that contacts the refrigerant pipe 45 where the superheat zones S1 and S2 are generated. The solidification of the regenerator material can be made uniform without depending on whether the refrigerant is in the superheated region S1, S2 or the normal region. Thereby, it can make it difficult to receive to the influence of overheating region S1, S2, and can improve the thermal storage / radiation performance of the evaporator 1440. FIG.
[第11実施形態の変形例]
なお、第11実施形態では、過熱域S2が発生する冷媒管45の第3群G3と接触する蓄冷材容器47の高さ方向の全体に亘って、その内部に高融点蓄冷材50Aを充填する構成を例示したが、少なくとも過熱域S2と接触する部分を高融点蓄冷材50Aとすればよい。例えば、冷媒管45の第3群G3と接触する蓄冷材容器47のうち、過熱域S2が発生する出口側通路側の近傍に接触する部分のみに高融点蓄冷材50Aを収容する構成としてもよい。このような構成は、例えば蓄冷材容器47の過熱域S2と重畳する部分(例えば流れ方向風上側、かつ、高さ方向上側の四分の一の領域)に沿って仕切り板を内蔵させ、単一の蓄冷材容器47の内部空間を区分することにより実現できる。 [Modification of Eleventh Embodiment]
In the eleventh embodiment, the high-melting-point regenerator material 50A is filled in the entire height direction of the regenerator container 47 in contact with the third group G3 of the refrigerant pipe 45 in which the superheat zone S2 is generated. Although the configuration has been illustrated, at least a portion in contact with the superheated region S2 may be the high melting point regenerator material 50A. For example, it is good also as a structure which accommodates 50 A of high melting-point regenerator materials only in the part which contacts the vicinity of the exit side channel | path side which superheat zone S2 generate | occur | produces among the regenerator containers 47 which contact the 3rd group G3 of the refrigerant | coolant pipe | tube 45. . In such a configuration, for example, a partition plate is built in along a portion (for example, a quarter region on the windward side in the flow direction and on the upper side in the height direction) that overlaps the superheat region S2 of the cold storage material container 47. This can be realized by dividing the internal space of one cold storage material container 47.
なお、第11実施形態では、過熱域S2が発生する冷媒管45の第3群G3と接触する蓄冷材容器47の高さ方向の全体に亘って、その内部に高融点蓄冷材50Aを充填する構成を例示したが、少なくとも過熱域S2と接触する部分を高融点蓄冷材50Aとすればよい。例えば、冷媒管45の第3群G3と接触する蓄冷材容器47のうち、過熱域S2が発生する出口側通路側の近傍に接触する部分のみに高融点蓄冷材50Aを収容する構成としてもよい。このような構成は、例えば蓄冷材容器47の過熱域S2と重畳する部分(例えば流れ方向風上側、かつ、高さ方向上側の四分の一の領域)に沿って仕切り板を内蔵させ、単一の蓄冷材容器47の内部空間を区分することにより実現できる。 [Modification of Eleventh Embodiment]
In the eleventh embodiment, the high-melting-
[第12実施形態]
図53を参照して第12実施形態を説明する。第12実施形態の蒸発器1540は、複数の冷媒管45のうち、過熱域S1が発生する第2群G2及び第4群G4と接触する部分に高融点蓄冷材50Aが配置される点で、第7実施形態の蒸発器1040(図33~図35参照)と異なる。言い換えると、過熱域S2が発生する第3群G3と接触する部分に高融点蓄冷材50Aが配置されない点で、第11実施形態の蒸発器1440(図52参照)と異なる。 [Twelfth embodiment]
The twelfth embodiment will be described with reference to FIG. Theevaporator 1540 of the twelfth embodiment is that the high-melting-point regenerator material 50A is disposed in a portion of the plurality of refrigerant tubes 45 that comes into contact with the second group G2 and the fourth group G4 where the superheat zone S1 is generated. Different from the evaporator 1040 of the seventh embodiment (see FIGS. 33 to 35). In other words, it differs from the evaporator 1440 (see FIG. 52) of the eleventh embodiment in that the high melting point regenerator material 50A is not disposed in the portion that contacts the third group G3 where the overheated region S2 is generated.
図53を参照して第12実施形態を説明する。第12実施形態の蒸発器1540は、複数の冷媒管45のうち、過熱域S1が発生する第2群G2及び第4群G4と接触する部分に高融点蓄冷材50Aが配置される点で、第7実施形態の蒸発器1040(図33~図35参照)と異なる。言い換えると、過熱域S2が発生する第3群G3と接触する部分に高融点蓄冷材50Aが配置されない点で、第11実施形態の蒸発器1440(図52参照)と異なる。 [Twelfth embodiment]
The twelfth embodiment will be described with reference to FIG. The
ここで、冷媒管45の第2群G2及び第3群G3の両方と接触する蓄冷材容器47は、図53に示すように、第3群G3と接触する部分(流れ方向の風上側の半分)に通常の融点の蓄冷材50が充填され、第2群G2と接触する部分(流れ方向の風下側の半分)には高融点蓄冷材50Aが充填されている。なお、冷媒管45の第1群G1及び第4群G4の両方と接触する蓄冷材容器47の構成は、図52を参照して説明した第11実施形態のものと同様である。
Here, the regenerator container 47 in contact with both the second group G2 and the third group G3 of the refrigerant pipe 45 is, as shown in FIG. 53, a portion in contact with the third group G3 (half of the windward side in the flow direction). ) Is filled with the normal melting point regenerator material 50, and the portion (half on the leeward side in the flow direction) in contact with the second group G2 is filled with the high melting point regenerator material 50A. In addition, the structure of the cool storage material container 47 which contacts both the 1st group G1 and the 4th group G4 of the refrigerant | coolant pipe | tube 45 is the same as that of the 11th Embodiment demonstrated with reference to FIG.
第12実施形態の蒸発器1540は、第11実施形態の蒸発器1440と同様に、過熱域S1が発生する冷媒管45と接触する部分に高融点蓄冷材50Aを配置する構成であるので、第11実施形態と同様に、蓄冷材と熱交換する冷媒が過熱域S1のものか通常領域のものかに依存することなく、蓄冷材の凝固性を均一にすることができる。これにより、過熱域S1の影響を受けにくくすることができ蓄放熱性能を高めることができるという効果を奏することができる。
Similarly to the evaporator 1440 of the eleventh embodiment, the evaporator 1540 of the twelfth embodiment has a configuration in which the high melting point regenerator material 50A is disposed in a portion that contacts the refrigerant pipe 45 in which the superheat zone S1 is generated. Similarly to the eleventh embodiment, the solidification property of the regenerator material can be made uniform without depending on whether the refrigerant that exchanges heat with the regenerator material is the superheat region S1 or the normal region. Thereby, it can be made hard to receive the influence of overheating region S1, and there can exist an effect that the heat storage and heat dissipation performance can be improved.
さらに、第12実施形態の蒸発器1540では、2種類の融点の蓄冷材(蓄冷材50及び高融点蓄冷材50A)が、冷媒温度の分布(流れ方向に沿った通常→過熱域S1の順の分布)に対応して左右均等(流れ方向に沿って同量ずつ)に蓄冷材容器47内に保持された状態となる。この構成により、2種類の融点の蓄冷材のそれぞれの凍り方が同等となり、この結果、放熱時の吹出し温度分布を均一化することができる。
Furthermore, in the evaporator 1540 of the twelfth embodiment, two types of refrigerating material (cold regenerator material 50 and high melting point regenerator material 50A) are distributed in the refrigerant temperature distribution (normal to superheated region S1 along the flow direction). Corresponding to (distribution), it will be in a state where it is held in the cold storage material container 47 equally in the left and right direction (the same amount along the flow direction). With this configuration, each of the two types of refrigerating materials having the melting points has the same freezing method, and as a result, it is possible to make the blow-off temperature distribution uniform during heat dissipation.
[第13実施形態]
図54を参照して第13実施形態を説明する。第13実施形態の蒸発器1640は、過熱域Sと接触する部分の蓄冷材が高融点蓄冷材50Aである点で、第1実施形態の蒸発器40と異なる。 [Thirteenth embodiment]
The thirteenth embodiment will be described with reference to FIG. Theevaporator 1640 of the thirteenth embodiment differs from the evaporator 40 of the first embodiment in that the portion of the regenerator material in contact with the superheat zone S is the high melting point regenerator material 50A.
図54を参照して第13実施形態を説明する。第13実施形態の蒸発器1640は、過熱域Sと接触する部分の蓄冷材が高融点蓄冷材50Aである点で、第1実施形態の蒸発器40と異なる。 [Thirteenth embodiment]
The thirteenth embodiment will be described with reference to FIG. The
図5を参照して説明したように、所謂4ターン方式の冷媒通路構造では、第4群G4の冷媒管45における高さ方向上側の略半分の領域、すなわち冷媒通路の出口の近傍において、冷媒の蒸発により過熱域Sが発生する。第13実施形態では、この過熱域Sが発生する冷媒管45(すなわち第4群G4)と接触する蓄冷材容器47の内部には高融点蓄冷材50Aが収容されている。
As described with reference to FIG. 5, in the so-called four-turn type refrigerant passage structure, the refrigerant in the fourth group G4 in the refrigerant pipe 45 in the upper half of the height direction, that is, in the vicinity of the outlet of the refrigerant passage. The superheated area S is generated by the evaporation of. In the thirteenth embodiment, the high-melting-point regenerator material 50A is accommodated in the regenerator container 47 that comes into contact with the refrigerant pipe 45 (that is, the fourth group G4) in which the superheat zone S is generated.
なお、第13実施形態では、少なくとも過熱域Sと接触する部分の蓄冷材が高融点蓄冷材50Aであればよく、例えば、高融点蓄冷材50Aが、過熱域Sが発生する冷媒管45の第4群G4と接触する蓄冷材容器47の高さ方向の全体に亘って充填される構成でもよいし、過熱域Sと接触する部分のみに充填される構成でもよい。
In the thirteenth embodiment, at least a portion of the regenerator material in contact with the superheat region S may be the high melting point regenerator material 50A. For example, the high melting point regenerator material 50A is the first refrigerating pipe 45 in the superheat region S. The structure filled up in the whole height direction of the cool storage material container 47 which contacts the 4th group G4 may be sufficient, and the structure filled only in the part which contacts the superheat zone S may be sufficient.
第13実施形態の蒸発器1640は、第11実施形態の蒸発器1440と同様に、過熱域Sが発生する冷媒管45と接触する部分に高融点蓄冷材50Aを配置する構成である。このため、4ターン方式の冷媒通路構造においても、第11実施形態の入替流れ形式の冷媒流路構造1045と同様に、蓄冷材と熱交換する冷媒が過熱域Sのものか通常領域のものかに依存することなく、蓄冷材の凝固性を均一にすることができる。これにより、過熱域Sの影響を受けにくくすることができ蓄放熱性能を高めることができるという効果を奏することができる。なお、第13実施形態の構成は、4ターン方式の冷媒通路構造に関する他の第2~第6実施形態にも適用できる。
The evaporator 1640 of the thirteenth embodiment has a configuration in which the high melting point regenerator material 50A is arranged in a portion that contacts the refrigerant pipe 45 where the superheat zone S is generated, similarly to the evaporator 1440 of the eleventh embodiment. Therefore, in the four-turn type refrigerant passage structure, whether the refrigerant that exchanges heat with the cold storage material is in the superheated region S or the normal region, as in the refrigerant flow structure 1045 of the replacement flow type in the eleventh embodiment. The solidification property of the regenerator material can be made uniform without depending on. Thereby, it can be made hard to receive the influence of the superheat zone S, and there can exist an effect that the heat storage and heat dissipation performance can be improved. The configuration of the thirteenth embodiment can also be applied to the other second to sixth embodiments related to the four-turn refrigerant passage structure.
[第14実施形態]
図55を参照して第14実施形態を説明する。第14実施形態の蒸発器1740は、蓄冷材容器47の内部に、冷媒管45の延在方向である長手方向(すなわち高さ方向)に沿って内部空間を区切る一対の仕切り板47dが設けられる点で、上記の各実施形態と異なる。 [Fourteenth embodiment]
The fourteenth embodiment will be described with reference to FIG. Theevaporator 1740 of the fourteenth embodiment is provided with a pair of partition plates 47d that divide the internal space along the longitudinal direction (that is, the height direction) that is the direction in which the refrigerant pipe 45 extends, inside the cold storage material container 47. This is different from the above embodiments.
図55を参照して第14実施形態を説明する。第14実施形態の蒸発器1740は、蓄冷材容器47の内部に、冷媒管45の延在方向である長手方向(すなわち高さ方向)に沿って内部空間を区切る一対の仕切り板47dが設けられる点で、上記の各実施形態と異なる。 [Fourteenth embodiment]
The fourteenth embodiment will be described with reference to FIG. The
図55に示すように、一対の仕切り板47dのうちの一方(図55では右側の板)は、蓄冷材容器47の長手方向の一方側(図55では、高さ方向下側)の端部に間隙を有する。また、一対の仕切り板47dのうちの他方(図55では左側の板)は、蓄冷材容器47の長手方向の他方側(図55では、高さ方向上側)の端部に間隙を有する。仕切り板47dは、流れ方向に沿って略等間隔に配置されている。また、蓄冷材容器47は、流れ方向の側壁のうち一方の仕切り板に近いほうの側壁に、蓄冷材封入パイプ47eを備える。
As shown in FIG. 55, one of the pair of partition plates 47d (the right side plate in FIG. 55) is an end portion on one side of the cold storage material container 47 in the longitudinal direction (the lower side in the height direction in FIG. 55). Have gaps. The other of the pair of partition plates 47d (the left plate in FIG. 55) has a gap at the end of the other side in the longitudinal direction of the cold storage material container 47 (the upper side in the height direction in FIG. 55). The partition plates 47d are arranged at substantially equal intervals along the flow direction. Moreover, the cool storage material container 47 is equipped with the cool storage material enclosure pipe 47e in the side wall close | similar to one partition board among the side walls of a flow direction.
蓄冷材容器47では、蓄冷材封入パイプ47eを介して内部に蓄冷材50が封入されるが、その際に、凍結膨張対策として内部空間を蓄冷材50で満杯にはせず、蓄冷材容器47の内部の上側に15%程度の隙を設けているのが一般的である。例えば、図55に示すように内部空間の上端に高さC1程度の空間が残ることになる。ここで、上記実施形態で説明した過熱域S,S2は、主に冷媒管45の高さ方向上側で発生する。このため、従来の構成では、蓄冷材容器47の高さ方向上側が冷えにくくなり、冷え不具合が発生する虞がある。
In the cool storage material container 47, the cool storage material 50 is enclosed inside via the cool storage material sealing pipe 47e. At that time, the internal space is not filled with the cool storage material 50 as a countermeasure against freezing and expansion, and the cool storage material container 47 is filled. Generally, a gap of about 15% is provided on the upper side of the inside. For example, as shown in FIG. 55, a space having a height of about C1 remains at the upper end of the internal space. Here, the superheat regions S and S2 described in the above embodiment are mainly generated on the upper side in the height direction of the refrigerant pipe 45. For this reason, in the conventional configuration, the upper side in the height direction of the cold storage material container 47 is difficult to cool, and there is a possibility that a cooling failure may occur.
第14実施形態の構成では、一対の仕切り板47dによって蓄冷材容器47の内部空間が3つに区切られ、これらの区切られた領域が直列に連なる構成となる。このため、従来と同様に、凍結膨張対策として15%程度の隙を設けるように蓄冷材50を注入すると、図55に示すように、蓄冷材封入パイプ47eが連通する領域のみに空間47fができ、奥側の2つの領域では蓄冷材50が高さ方向の全域に亘り充填される。つまり、空間47fだけ見れば、上端からの高さc2は従来の高さc1より増えるものの、蓄冷材容器47の内部空間の全体をみれば、高さ方向では蓄冷材50が存在しない位置が存在しなくなる。言い換えると、流れ方向から蓄冷材容器47の内部空間を視たときに、高さ方向の全域に亘って蓄冷材50が配置される。これにより、蓄冷材容器47内の上端に隙ができるのを防止でき、蓄冷材容器47の高さ方向上側の冷え残り部を解消することができる。
In the configuration of the fourteenth embodiment, the internal space of the cold storage material container 47 is divided into three by a pair of partition plates 47d, and the divided regions are connected in series. For this reason, when the cool storage material 50 is injected so as to provide a gap of about 15% as a measure against freezing and expansion, a space 47f is created only in the region where the cool storage material sealing pipe 47e communicates, as shown in FIG. In the two regions on the back side, the regenerator material 50 is filled over the entire region in the height direction. That is, if only the space 47f is seen, the height c2 from the upper end is larger than the conventional height c1, but if the entire internal space of the cool storage material container 47 is viewed, there is a position where the cool storage material 50 does not exist in the height direction. No longer. In other words, when the internal space of the cool storage material container 47 is viewed from the flow direction, the cool storage material 50 is disposed over the entire region in the height direction. Thereby, it can prevent that a clearance gap is made in the upper end in the cool storage material container 47, and the cooling remaining part of the height direction upper side of the cool storage material container 47 can be eliminated.
なお、一対の仕切り板47dは、少なくとも一対が蓄冷材容器47の内部に設けられればよく、複数対の仕切り板を設ける構成としてもよい。
Note that at least one pair of the pair of partition plates 47d may be provided inside the cold storage material container 47, and a plurality of pairs of partition plates may be provided.
[第15実施形態]
図56を参照して第15実施形態を説明する。第15実施形態の蒸発器1840は、過熱域Sが発生する冷媒管45と接合される蓄冷材容器47が、冷媒管45の過熱域Sと接触する部分には設けられず、冷媒管45の過熱域S以外と接触する部分のみに設けられる点で、第1実施形態の蒸発器40と異なる。 [Fifteenth embodiment]
The fifteenth embodiment will be described with reference to FIG. In theevaporator 1840 of the fifteenth embodiment, the cold storage material container 47 joined to the refrigerant pipe 45 in which the superheat zone S is generated is not provided in the portion of the refrigerant pipe 45 that contacts the superheat zone S. It differs from the evaporator 40 of 1st Embodiment by the point provided only in the part which contacts except the superheat zone S. FIG.
図56を参照して第15実施形態を説明する。第15実施形態の蒸発器1840は、過熱域Sが発生する冷媒管45と接合される蓄冷材容器47が、冷媒管45の過熱域Sと接触する部分には設けられず、冷媒管45の過熱域S以外と接触する部分のみに設けられる点で、第1実施形態の蒸発器40と異なる。 [Fifteenth embodiment]
The fifteenth embodiment will be described with reference to FIG. In the
図5を参照して説明したように、所謂4ターン方式の冷媒通路構造では、第4群G4の冷媒管45における高さ方向上側の略半分の領域、すなわち冷媒通路の出口の近傍において、冷媒の蒸発により過熱域Sが発生する。第15実施形態では、図56に示すように、この過熱域Sが発生する冷媒管45、すなわち第4群G4の冷媒管45と接触する蓄冷材容器47は、過熱域Sは発生する領域(冷媒通路の出口の近傍)には配置されていない。
As described with reference to FIG. 5, in the so-called four-turn type refrigerant passage structure, the refrigerant in the fourth group G4 in the refrigerant pipe 45 in the upper half of the height direction, that is, in the vicinity of the outlet of the refrigerant passage. The superheated area S is generated by the evaporation of. In the fifteenth embodiment, as shown in FIG. 56, the refrigerant tube 45 in which the superheat zone S is generated, that is, the cold storage container 47 that is in contact with the refrigerant tube 45 of the fourth group G4, is a region in which the superheat zone S is generated ( It is not arranged in the vicinity of the outlet of the refrigerant passage.
第15実施形態の蒸発器1840は、この構成により、過熱域Sの冷媒と蓄冷材50との間の熱交換を分断することができ、冷却効率の改善を図ることができる。これにより、蓄冷材50の凝固を促進させ、従来製品に対して放冷時間を長くする事で、この蒸発器1840が搭載される車両のアイドルストップ時に、エアコンのオフ時間を長くして、更なる燃費改善を図ることができる。なお、第15実施形態の構成は、4ターン方式の冷媒通路構造に関する他の第2~第6実施形態にも適用できる。
With this configuration, the evaporator 1840 of the fifteenth embodiment can divide the heat exchange between the refrigerant in the superheat zone S and the cold storage material 50, and can improve the cooling efficiency. As a result, the solidification of the regenerator material 50 is promoted, and the cooling time is made longer than that of the conventional product, so that the off time of the air conditioner can be increased when the vehicle on which the evaporator 1840 is mounted is idled. Can improve fuel efficiency. The configuration of the fifteenth embodiment can also be applied to the other second to sixth embodiments related to the four-turn type refrigerant passage structure.
以上、具体例を参照しつつ本実施形態について説明した。しかし、本開示はこれらの具体例に限定されるものではない。すなわち、これら具体例に、当業者が適宜設計変更を加えたものも、本開示の特徴を備えている限り、本開示の範囲に包含される。例えば、前述した各具体例が備える各要素及びその配置、材料、条件、形状、サイズなどは、例示したものに限定されるわけではなく適宜変更することができる。また、前述した各実施形態が備える各要素は、技術的に可能な限りにおいて組み合わせることができ、これらを組み合わせたものも本開示の特徴を含む限り本開示の範囲に包含される。
The embodiment has been described above with reference to specific examples. However, the present disclosure is not limited to these specific examples. That is, those specific examples modified by appropriate design by those skilled in the art are also included in the scope of the present disclosure as long as they have the features of the present disclosure. For example, the elements included in each of the specific examples described above and their arrangement, materials, conditions, shapes, sizes, and the like are not limited to those illustrated, and can be changed as appropriate. Moreover, each element with which each embodiment mentioned above is provided can be combined as long as technically possible, and the combination of these is also included in the scope of the present disclosure as long as it includes the features of the present disclosure.
例えば、上記の第1~第6実施形態において説明した、冷媒通路の出口の近傍において冷媒の蒸発により発生する過熱域S,S2による蓄冷の影響を低減する手法を、第7~第10実施形態の構成に組み合わせることも可能である。
For example, as described in the first to sixth embodiments, the method for reducing the influence of cold storage due to the superheat zones S and S2 generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage is the seventh to tenth embodiments. It is also possible to combine with the structure of.
上記実施形態では、蒸発器40において、蓄冷材容器47が2つの冷媒管45の間に配置され、これら2つの冷媒管45と接合され、それぞれの冷媒管45における蓄冷材容器47と反対側に空気通路53が設けられる構成を例示したが、この構成に限られない。例えば、冷媒管45と蓄冷材容器47とが同一方向に延在するよう一体的な部材として形成され、空気通路53がこれらの部材の隙間に設けられる構成でもよい。
In the above embodiment, in the evaporator 40, the regenerator material container 47 is disposed between the two refrigerant tubes 45, joined to the two refrigerant tubes 45, and opposite to the regenerator material container 47 in each refrigerant tube 45. Although the configuration in which the air passage 53 is provided is illustrated, the configuration is not limited to this configuration. For example, the refrigerant pipe 45 and the cold storage material container 47 may be formed as an integral member so as to extend in the same direction, and the air passage 53 may be provided in a gap between these members.
上記実施形態では、蓄冷材50が蓄冷材容器47に収容される構成を例示したが、これに限られない。例えば、蓄冷材50が蓄冷材容器47に収容されず、冷媒管45と直接接触する構成として、冷媒管45から蓄冷材50に対して熱伝達を直接行う構成とすることもできる。
In the above-described embodiment, the configuration in which the cold storage material 50 is accommodated in the cold storage material container 47 is illustrated, but is not limited thereto. For example, as a configuration in which the regenerator material 50 is not accommodated in the regenerator material container 47 and is in direct contact with the refrigerant tube 45, a configuration in which heat transfer from the refrigerant tube 45 to the regenerator material 50 can be performed directly.
Claims (37)
- 冷媒を流通させる冷媒通路を有し、互いに間隔をあけて配置される複数の冷媒管(45)と、
前記複数の冷媒管と隣接する蓄冷材(50)と、
前記冷媒通路にて発生する前記冷媒の過熱域(S、S1,S2)における前記冷媒管から前記蓄冷材への熱伝達を抑制する熱伝達抑制部(47b,471b,147、1471,247,2471,347b,447,547,1045,1147b,1247,1347)と、
を備える蓄冷熱交換器(40,401,140,1401,240,2401,340,440,540,1040,1140,1240,1340,1440,1540,1640,1740,1840)。 A plurality of refrigerant pipes (45) having a refrigerant passage for circulating the refrigerant and arranged at intervals from each other;
A regenerator material (50) adjacent to the plurality of refrigerant tubes;
Heat transfer suppression portions (47b, 471b, 147, 1471, 247, 2471) that suppress heat transfer from the refrigerant pipe to the cold storage material in the refrigerant overheating region (S, S1, S2) generated in the refrigerant passage. , 347b, 447, 547, 1045, 1147b, 1247, 1347),
Cold storage heat exchanger (40, 401, 140, 1401, 240, 2401, 340, 440, 540, 1040, 1140, 1240, 1340, 1440, 1540, 1640, 1740, 1840). - 前記複数の冷媒管と隣接し、前記蓄冷材を収容する複数の蓄冷材容器(47,471,147,1471,247,2471,347,447,547,1147,1247,1347)を備える、
請求項1に記載の蓄冷熱交換器。 A plurality of regenerator containers (47, 471, 147, 1471, 247, 2471, 347, 447, 547, 1147, 1247, 1347) that are adjacent to the plurality of refrigerant tubes and store the regenerator material are provided.
The cold storage heat exchanger according to claim 1. - 前記複数の蓄冷材容器のそれぞれは、前記冷媒管の延在方向を長手方向として前記複数の冷媒管のうちの2つの冷媒管の間に配置され、前記2つの冷媒管と接合され、
前記複数の蓄冷材容器のそれぞれと接合される前記2つの冷媒管における前記蓄冷材容器と反対側に、前記複数の冷媒管のうちの他の冷媒管との隙間に形成され、前記隙間を流れる空気と前記冷媒との間で熱交換する空気通路(53)を備える、
請求項2に記載の蓄冷熱交換器。 Each of the plurality of cool storage material containers is disposed between two refrigerant tubes among the plurality of refrigerant tubes with the extending direction of the refrigerant tubes as a longitudinal direction, and is joined to the two refrigerant tubes,
The two refrigerant pipes joined to each of the plurality of cold storage material containers are formed on a side opposite to the cold storage material container in a gap with another refrigerant pipe among the plurality of refrigerant pipes, and flow through the gap. An air passage (53) for exchanging heat between air and the refrigerant,
The cold storage heat exchanger according to claim 2. - 前記熱伝達抑制部(47b,471b,147,1471,247,2471,347b,447,547)は、前記冷媒通路の出口の近傍において前記冷媒の蒸発により発生する前記過熱域(S)における前記冷媒管から前記蓄冷材への熱伝達を抑制する、
請求項3に記載の蓄冷熱交換器(40,401,140,1401,240,2401,340,440,540,1640,1840)。 The heat transfer suppression unit (47b, 471b, 147, 1471, 247, 2471, 347b, 447, 547) is configured to be used in the superheat zone (S) generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage. Suppresses heat transfer from the tube to the cold storage material,
The regenerative heat exchanger according to claim 3 (40, 401, 140, 1401, 240, 2401, 340, 440, 540, 1640, 1840). - 前記蓄冷材容器の内部において前記冷媒管の延在方向である長手方向に沿って延在するよう配置されるインナフィン(47b,471b,347b)を備え、
前記インナフィンは、前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器において、前記冷媒管の前記過熱域と接触する部分では、前記冷媒管から前記蓄冷材への前記インナフィンを介した伝熱量が相対的に小さく、前記冷媒管の前記過熱域以外と接触する部分では、前記冷媒管から前記蓄冷材への前記インナフィンを介した伝熱量が相対的に大きく、
前記熱伝達抑制部は前記インナフィンを含む、
請求項4に記載の蓄冷熱交換器(40,401,340)。 Inner fins (47b, 471b, 347b) arranged to extend along the longitudinal direction that is the extending direction of the refrigerant pipe inside the cold storage material container,
In the cold storage container that is joined to the refrigerant pipe in which the superheat zone is generated, the inner fin is connected to the superheat zone of the refrigerant pipe via the inner fin from the refrigerant pipe to the cold storage material. The amount of heat transfer is relatively small, and the heat transfer amount through the inner fin from the refrigerant tube to the cold storage material is relatively large in the portion that is in contact with the refrigerant tube other than the overheated region,
The heat transfer suppression unit includes the inner fin,
The regenerative heat exchanger (40, 401, 340) according to claim 4. - 前記インナフィン(471b)は、前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器において、前記冷媒管の前記過熱域と接触する部分では前記蓄冷材容器の内壁との接合率が相対的に低く、前記冷媒管の前記過熱域以外と接触する部分では前記蓄冷材容器の内壁との接合率が相対的に高い、
請求項5に記載の蓄冷熱交換器(401)。 The inner fin (471b) has a relative joining ratio with the inner wall of the regenerator container in a portion of the refrigerant pipe that contacts the superheat region in the regenerator container that is joined to the refrigerant tube in which the overheat region is generated. Is relatively low, the contact ratio with the inner wall of the cold storage material container is relatively high in the portion of the refrigerant pipe that comes into contact with other than the superheated area,
The cold storage heat exchanger (401) according to claim 5. - 前記インナフィン(47b,347b)は、前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器において、前記冷媒管の前記過熱域と接触する部分では前記蓄冷材容器の内壁と接合されず、前記冷媒管の前記過熱域以外と接触する部分では前記蓄冷材容器の内壁と接合される、
請求項5に記載の蓄冷熱交換器(40,340)。 The inner fins (47b, 347b) are not joined to the inner wall of the cold storage material container in the cold storage material container joined to the refrigerant pipe in which the superheat zone is generated, in the portion of the refrigerant pipe that contacts the superheat zone. The portion of the refrigerant pipe that comes into contact with other than the superheat zone is joined to the inner wall of the cold storage material container.
The cold storage heat exchanger (40, 340) according to claim 5. - 前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って少なくとも2つの冷媒管が配置され、
前記蓄冷材容器は、前記空気の流れ方向に沿って配置される前記少なくとも2つの冷媒管と接合するよう形成され、
前記インナフィン(47b)は、前記冷媒管及び前記蓄冷材容器の配列方向から視るときに前記少なくとも2つの冷媒管と重畳するよう形成され、
前記インナフィンは、前記過熱域が発生する冷媒管を含む前記少なくとも2つの冷媒管と接合される前記蓄冷材容器において、前記冷媒管の前記過熱域と接触する部分を含み、かつ、前記空気の流れ方向から視るときに、前記冷媒管の前記過熱域と接触する前記部分と重畳する領域では前記蓄冷材容器の内壁と接合されず、それ以外の領域では前記蓄冷材容器の内壁と接合される、
請求項7に記載の蓄冷熱交換器(40)。 The plurality of refrigerant tubes are arranged with at least two refrigerant tubes along the air flow direction of the air passage,
The cold storage material container is formed so as to be joined to the at least two refrigerant tubes arranged along the air flow direction,
The inner fin (47b) is formed so as to overlap with the at least two refrigerant pipes when viewed from the arrangement direction of the refrigerant pipe and the cold storage material container,
The inner fin includes a portion in contact with the superheat area of the refrigerant pipe in the cold storage material container joined to the at least two refrigerant pipes including the refrigerant pipe in which the superheat area is generated, and the air flow When viewed from the direction, it is not joined to the inner wall of the regenerator material container in the region overlapping with the portion of the refrigerant pipe that contacts the superheated region, and is joined to the inner wall of the regenerator material container in other regions. ,
The cold storage heat exchanger (40) according to claim 7. - 前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って少なくとも2つの冷媒管が配置され、
前記蓄冷材容器は、前記空気の流れ方向に沿って配置される前記少なくとも2つの冷媒管と接合するよう形成され、
前記インナフィン(347b)は、前記冷媒管及び前記蓄冷材容器の配列方向から視るときに前記少なくとも2つの冷媒管と重畳するよう形成され、
前記インナフィンは、前記過熱域が発生する冷媒管を含む前記少なくとも2つの冷媒管と接合される前記蓄冷材容器において、前記過熱域が発生しない冷媒管と重畳する領域では前記冷媒管の延在方向である前記長手方向の全域に亘って前記蓄冷材容器の内壁と接合され、前記過熱域が発生する冷媒管と重畳する領域では、前記冷媒管の前記過熱域と接触する部分では前記蓄冷材容器の内壁と接合されず、それ以外の部分では前記蓄冷材容器の内壁と接合される、
請求項7に記載の蓄冷熱交換器(340)。 The plurality of refrigerant tubes are arranged with at least two refrigerant tubes along the air flow direction of the air passage,
The cold storage material container is formed so as to be joined to the at least two refrigerant tubes arranged along the air flow direction,
The inner fin (347b) is formed so as to overlap with the at least two refrigerant tubes when viewed from the arrangement direction of the refrigerant tube and the cold storage material container,
In the cold storage material container joined to the at least two refrigerant tubes including the refrigerant tube in which the superheat region is generated, the inner fin extends in the region overlapping the refrigerant tube in which the overheat region does not occur. In the region that is joined to the inner wall of the cold storage material container over the entire region in the longitudinal direction and overlaps with the refrigerant pipe in which the superheat region is generated, the cold storage material container is in a portion that contacts the superheat region of the refrigerant tube It is not joined to the inner wall of the other, and the other part is joined to the inner wall of the cold storage material container,
The regenerative heat exchanger (340) according to claim 7. - 前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器(147,1471,447)は、前記冷媒管の前記過熱域と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に小さく、前記冷媒管の前記過熱域以外と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に大きく、
前記熱伝達抑制部は前記蓄冷材容器を含む、
請求項4~9のいずれか1項に記載の蓄冷熱交換器(140,1401,440)。 The cold storage container (147, 1471, 447) joined to the refrigerant pipe in which the superheat zone is generated is connected to the superheat zone of the refrigerant pipe from the refrigerant pipe through the cold storage container. The heat transfer amount to the regenerator material is relatively small, and the heat transfer amount from the refrigerant tube to the regenerator material through the regenerator material container is relatively small at the portion of the refrigerant tube that is in contact with the area other than the superheat region. Big,
The heat transfer suppression unit includes the cold storage material container,
The cold storage heat exchanger (140, 1401, 440) according to any one of claims 4 to 9. - 前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器(1471)は、前記冷媒管の前記過熱域と接触する部分では前記冷媒管との接合率が相対的に低く、前記冷媒管の前記過熱域以外と接触する部分では前記冷媒管との接合率が相対的に高い、
請求項10に記載の蓄冷熱交換器(1401)。 The regenerator container (1471) joined to the refrigerant pipe in which the superheated area is generated has a relatively low joining ratio with the refrigerant pipe at a portion in contact with the superheated area of the refrigerant pipe. The contact ratio with the refrigerant pipe is relatively high in the part that is in contact with other than the overheated area,
The cold storage heat exchanger (1401) according to claim 10. - 前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器(147,447)は、前記冷媒管の前記過熱域と接触する部分では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、前記冷媒管の前記過熱域以外と接触する部分において前記冷媒管と接合される、
請求項10に記載の蓄冷熱交換器(140,440)。 The regenerator container (147, 447) joined to the refrigerant pipe in which the superheat zone is generated is not joined to the refrigerant pipe at a portion in contact with the superheat zone of the refrigerant pipe, and is spaced from the refrigerant pipe. Formed in a portion that is in contact with the refrigerant pipe other than the superheat zone, and is joined to the refrigerant pipe.
The cold storage heat exchanger (140, 440) according to claim 10. - 前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って少なくとも2つの冷媒管が配置され、
前記蓄冷材容器は、前記空気の流れ方向に沿って配置される前記少なくとも2つの冷媒管と接合するよう形成され、
前記過熱域が発生する冷媒管を含む前記少なくとも2つの冷媒管と接合される前記蓄冷材容器(147)は、前記冷媒管の前記過熱域と接触する部分を含み、かつ、前記空気の流れ方向から視るときに、前記冷媒管の前記過熱域と接触する前記部分と重畳する領域では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、それ以外の領域では前記冷媒管と接合される、
請求項12に記載の蓄冷熱交換器(140)。 The plurality of refrigerant tubes are arranged with at least two refrigerant tubes along the air flow direction of the air passage,
The cold storage material container is formed so as to be joined to the at least two refrigerant tubes arranged along the air flow direction,
The cold storage container (147) joined to the at least two refrigerant pipes including the refrigerant pipe in which the superheat zone is generated includes a portion in contact with the superheat zone of the refrigerant pipe, and the air flow direction When viewed from above, the refrigerant pipe is formed not to be joined to the refrigerant pipe in a region overlapping with the portion that contacts the superheated area of the refrigerant pipe, and is spaced apart from the refrigerant pipe. Joined,
A regenerative heat exchanger (140) according to claim 12. - 前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って少なくとも2つの冷媒管が配置され、
前記蓄冷材容器は、前記空気の流れ方向に沿って配置される前記少なくとも2つの冷媒管と接合するよう形成され、
前記過熱域が発生する冷媒管を含む前記少なくとも2つの冷媒管と接合される前記蓄冷材容器(447)は、前記過熱域が発生しない冷媒管と重畳する領域では前記延在方向の全域に亘って前記冷媒管と接合され、前記過熱域が発生する冷媒管と重畳する領域では、前記冷媒管の前記過熱域と接触する部分では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、それ以外の部分では前記冷媒管と接合される、
請求項12に記載の蓄冷熱交換器(440)。 The plurality of refrigerant tubes are arranged with at least two refrigerant tubes along the air flow direction of the air passage,
The cold storage material container is formed so as to be joined to the at least two refrigerant tubes arranged along the air flow direction,
The cold storage container (447) joined to the at least two refrigerant pipes including the refrigerant pipe in which the superheat zone is generated extends over the entire extending direction in a region overlapping with the refrigerant pipe in which the superheat zone does not occur. In the region that is joined to the refrigerant pipe and overlaps with the refrigerant pipe in which the overheated region is generated, the portion of the refrigerant pipe that is in contact with the superheated region is not joined to the refrigerant pipe and is spaced from the refrigerant pipe. In other parts, the refrigerant pipe is joined.
A regenerative heat exchanger (440) according to claim 12. - 前記蓄冷材容器の内部において前記冷媒管の延在方向である前記長手方向に沿って延在するよう配置され、前記蓄冷材容器の内壁と接合されるインナフィンを備え、
前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器(247,2471,547)は、前記冷媒管の前記過熱域と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に小さく、前記冷媒管の前記過熱域以外と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に大きく、
前記熱伝達抑制部は前記蓄冷材容器を含む、
請求項4に記載の蓄冷熱交換器(240,2401,540)。 An inner fin that is arranged so as to extend along the longitudinal direction, which is the extending direction of the refrigerant pipe, inside the cold storage material container, and is joined to an inner wall of the cold storage material container;
The cold storage container (247, 2471, 547) joined to the refrigerant pipe in which the superheat zone is generated is connected to the superheat zone of the refrigerant pipe from the refrigerant pipe through the cold storage container. The heat transfer amount to the regenerator material is relatively small, and the heat transfer amount from the refrigerant tube to the regenerator material through the regenerator material container is relatively small at the portion of the refrigerant tube that is in contact with the area other than the superheat region. Big,
The heat transfer suppression unit includes the cold storage material container,
The regenerative heat exchanger (240, 2401, 540) according to claim 4. - 前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器(2471)は、前記冷媒管の前記過熱域と接触する部分では前記冷媒管との接合率が相対的に低く、前記冷媒管の前記過熱域以外と接触する部分では前記冷媒管との接合率が相対的に高い、
請求項15に記載の蓄冷熱交換器(2401)。 The regenerator container (2471) joined to the refrigerant pipe in which the superheat zone is generated has a relatively low joining ratio with the refrigerant pipe at a portion of the refrigerant pipe that contacts the superheat zone, and the refrigerant pipe The contact ratio with the refrigerant pipe is relatively high in the part that is in contact with other than the overheated area,
The cold-storage heat exchanger (2401) according to claim 15. - 前記過熱域が発生する前記冷媒管と接合される前記蓄冷材容器(247,547)は、前記冷媒管の前記過熱域と接触する部分では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、前記冷媒管の前記過熱域以外と接触する部分において前記冷媒管と接合される、
請求項15に記載の蓄冷熱交換器(240,540)。 The regenerator container (247, 547) joined to the refrigerant pipe in which the superheat zone is generated is not joined to the refrigerant pipe at a portion in contact with the superheat zone of the refrigerant pipe, and is spaced from the refrigerant pipe. Formed in a portion that is in contact with the refrigerant pipe other than the superheat zone, and is joined to the refrigerant pipe.
The cold storage heat exchanger (240, 540) according to claim 15. - 前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って少なくとも2つの冷媒管が配置され、
前記蓄冷材容器は、前記空気の流れ方向に沿って配置される前記少なくとも2つの冷媒管と接合するよう形成され、
前記インナフィンは、前記冷媒管及び前記蓄冷材容器の配列方向から視るときに前記少なくとも2つの冷媒管と重畳するよう形成され、
前記過熱域が発生する冷媒管を含む前記少なくとも2つの冷媒管と接合される前記蓄冷材容器(247)は、前記冷媒管の前記過熱域と接触する部分を含み、かつ、前記空気の流れ方向から視るときに、前記冷媒管の前記過熱域と接触する前記部分と重畳する領域では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、それ以外の領域では前記冷媒管と接合される、
請求項17に記載の蓄冷熱交換器(240)。 The plurality of refrigerant tubes are arranged with at least two refrigerant tubes along the air flow direction of the air passage,
The cold storage material container is formed so as to be joined to the at least two refrigerant tubes arranged along the air flow direction,
The inner fin is formed so as to overlap with the at least two refrigerant tubes when viewed from the arrangement direction of the refrigerant tube and the cold storage material container,
The cold storage container (247) joined to the at least two refrigerant tubes including the refrigerant tube in which the superheat zone is generated includes a portion in contact with the superheat zone of the refrigerant tube, and the air flow direction When viewed from above, the refrigerant pipe is formed not to be joined to the refrigerant pipe in a region overlapping with the portion that contacts the superheated area of the refrigerant pipe, and is spaced apart from the refrigerant pipe. Joined,
The regenerative heat exchanger (240) according to claim 17. - 前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って少なくとも2つの冷媒管が配置され、
前記蓄冷材容器は、前記空気の流れ方向に沿って配置される前記少なくとも2つの冷媒管と接合するよう形成され、
前記インナフィンは、前記冷媒管及び前記蓄冷材容器の配列方向から視るときに前記少なくとも2つの冷媒管と重畳するよう形成され、
前記過熱域が発生する冷媒管を含む前記少なくとも2つの冷媒管と接合される前記蓄冷材容器(547)は、前記過熱域が発生しない冷媒管と重畳する領域では前記延在方向の全域に亘って前記冷媒管と接合され、前記過熱域が発生する冷媒管と重畳する領域では、前記冷媒管の前記過熱域と接触する部分では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、それ以外の部分では前記冷媒管と接合される、
請求項17に記載の蓄冷熱交換器(540)。 The plurality of refrigerant tubes are arranged with at least two refrigerant tubes along the air flow direction of the air passage,
The cold storage material container is formed so as to be joined to the at least two refrigerant tubes arranged along the air flow direction,
The inner fin is formed so as to overlap with the at least two refrigerant tubes when viewed from the arrangement direction of the refrigerant tube and the cold storage material container,
The cold storage container (547) joined to the at least two refrigerant pipes including the refrigerant pipe in which the superheat zone is generated extends over the entire extending direction in a region overlapping with the refrigerant pipe in which the superheat zone does not occur. In the region that is joined to the refrigerant pipe and overlaps with the refrigerant pipe in which the overheated region is generated, the portion of the refrigerant pipe that is in contact with the superheated region is not joined to the refrigerant pipe and is spaced from the refrigerant pipe. In other parts, the refrigerant pipe is joined.
The regenerative heat exchanger (540) according to claim 17. - 前記過熱域(S)が発生する前記冷媒管と接合される前記蓄冷材容器は、前記冷媒管の前記過熱域と接触する部分には設けられず、前記冷媒管の前記過熱域以外と接触する部分のみに設けられる、請求項4~19のいずれか1項に記載の蓄冷熱交換器(1840)。 The cold storage material container joined to the refrigerant pipe in which the superheat zone (S) is generated is not provided in a portion of the refrigerant pipe that contacts the superheat zone, and is in contact with a portion other than the superheat zone of the refrigerant pipe. The regenerative heat exchanger (1840) according to any one of claims 4 to 19, which is provided only in the portion.
- 少なくとも前記過熱域(S)と接触する部分の前記蓄冷材は、他の部分と比較して相対的に融点の高い高融点蓄冷材(50A)である、
請求項1~19のいずれか1項に記載の蓄冷熱交換器(1640)。 The regenerator material at least in the part in contact with the superheat zone (S) is a high melting point regenerator material (50A) having a relatively high melting point compared to other parts.
The regenerative heat exchanger (1640) according to any one of the preceding claims. - 前記複数の冷媒管の一端側が連通し、前記冷媒管及び前記蓄冷材容器の配列方向を長手方向とするよう形成される第1ヘッダタンク(51)と、
前記複数の冷媒管の他端側が連通し、前記配列方向を長手方向とするよう形成される第2ヘッダタンク(52)と、
を備え、
前記複数の冷媒管は、前記空気通路の前記空気の流れ方向に沿って一対となるように2列に配置されており、
前記第1ヘッダタンクの内部は、前記複数の冷媒管のうち前記空気の流れ方向の下流側に配置される冷媒管と連通され、前記冷媒管の延在方向である前記長手方向の一端部に前記冷媒通路の入口が設けられる入口側通路(1041)と、前記空気の流れ方向の上流側に配置される冷媒管と連通され、前記冷媒管の延在方向である前記長手方向の一端部または他端部に前記冷媒通路の出口が設けられる出口側通路(1043)とに区分され、
前記複数の冷媒管は、前記入口側通路と連通され、かつ、前記冷媒管の延在方向である前記長手方向の前記一端部側に配置される第1群(G1)と、前記入口側通路と連通され、かつ、前記冷媒管の延在方向である前記長手方向の前記他端部側に配置される第2群(G2)と、前記出口側通路と連通され、かつ、前記冷媒管の延在方向である前記長手方向の前記他端部側に配置される第3群(G3)と、前記出口側通路と連通され、かつ、前記冷媒管の延在方向である前記長手方向の前記一端部側に配置される第4群(G4)と、に区分され、
前記第2ヘッダタンクは、前記第1群と前記第3群とを連通し、前記第2群と前記第4群とを連通して、前記入口側通路から前記冷媒管の延在方向である前記長手方向の前記一端部側及び前記他端部側に導入された前記冷媒をそれぞれ前記他端部側及び前記一端部側に入れ替えて前記出口側通路に導出するよう構成され、
前記過熱域(S1)は、前記複数の冷媒管の前記第2群及び前記第4群において発生する過熱域であり、
前記熱伝達抑制部(1045,1147b,1247,1347)は、前記過熱域が発生する前記第2群と、前記過熱域が発生しない前記第3群との両方に前記蓄冷材容器が接合される構造と、前記過熱域が発生しない前記第1群と、前記過熱域が発生する前記第4群との両方に前記蓄冷材容器が接合される構造と、を有する冷媒通路構造(1045)を含む、
請求項2または3に記載の蓄冷熱交換器(1040,1140,1240,1340,1440,1540)。 A first header tank (51) formed so that one end side of the plurality of refrigerant pipes communicates, and an arrangement direction of the refrigerant pipes and the cold storage material containers is a longitudinal direction;
A second header tank (52) formed so that the other end sides of the plurality of refrigerant tubes communicate with each other and have the arrangement direction as a longitudinal direction;
With
The plurality of refrigerant tubes are arranged in two rows so as to form a pair along the air flow direction of the air passage,
The inside of the first header tank communicates with a refrigerant pipe disposed downstream of the plurality of refrigerant pipes in the air flow direction, and is disposed at one end of the longitudinal direction, which is an extending direction of the refrigerant pipe. An inlet-side passage (1041) provided with an inlet of the refrigerant passage and a refrigerant pipe disposed on the upstream side in the air flow direction and one end portion in the longitudinal direction which is an extending direction of the refrigerant pipe or It is divided into an outlet side passage (1043) in which the outlet of the refrigerant passage is provided at the other end,
The plurality of refrigerant tubes communicate with the inlet-side passage and are arranged on the one end side in the longitudinal direction, which is the extending direction of the refrigerant tube, and the inlet-side passage And the second group (G2) arranged on the other end portion side in the longitudinal direction, which is the extending direction of the refrigerant pipe, and the outlet side passage, and The third group (G3) disposed on the other end side in the longitudinal direction, which is the extending direction, communicates with the outlet-side passage, and the longitudinal direction is the extending direction of the refrigerant pipe. And a fourth group (G4) arranged on one end side,
The second header tank communicates the first group and the third group, communicates the second group and the fourth group, and extends in the direction of the refrigerant pipe from the inlet side passage. The refrigerant introduced to the one end side and the other end side in the longitudinal direction is replaced with the other end side and the one end side, respectively, and led out to the outlet side passage,
The superheat zone (S1) is a superheat zone generated in the second group and the fourth group of the plurality of refrigerant tubes,
In the heat transfer suppression unit (1045, 1147b, 1247, 1347), the cold storage material container is joined to both the second group in which the overheating region is generated and the third group in which the overheating region is not generated. A refrigerant passage structure (1045) having a structure, and a structure in which the cold storage material container is joined to both the first group in which the overheat region does not occur and the fourth group in which the overheat region occurs. ,
The regenerative heat exchanger (1040, 1140, 1240, 1340, 1440, 1540) according to claim 2 or 3. - 前記蓄冷材容器の内部において前記冷媒管の延在方向である前記長手方向に沿って延在するよう配置されるインナフィン(1147b)を備え、
前記インナフィンは、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と前記蓄冷材容器とが接合する部分では、前記冷媒管から前記蓄冷材への前記インナフィンを介した伝熱量が相対的に小さく、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と前記蓄冷材容器とが接触する部分では、前記冷媒管から前記蓄冷材への前記インナフィンを介した伝熱量が相対的に大きく、
前記熱伝達抑制部は前記インナフィンを含む、
請求項22に記載の蓄冷熱交換器(1140)。 An inner fin (1147b) disposed so as to extend along the longitudinal direction, which is the extending direction of the refrigerant pipe, inside the cold storage material container;
The inner fin is transferred from the refrigerant pipe to the regenerator material via the inner fin at a portion where the second group and the fourth group of the refrigerant pipe where the superheat zone is generated and the regenerator material container are joined. In the portion where the first group and the third group of the refrigerant tubes where the amount of heat is relatively small and the superheat zone does not occur and the cold storage material container are in contact, the inner fin from the refrigerant tube to the cold storage material is The amount of heat transferred through the
The heat transfer suppression unit includes the inner fin,
A cold storage heat exchanger (1140) according to claim 22. - 前記インナフィンは、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と前記蓄冷材容器とが接合する部分では前記蓄冷材容器の内壁との接合率が相対的に低く、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と前記蓄冷材容器とが接触する部分では前記蓄冷材容器の内壁との接合率が相対的に高い、
請求項23に記載の蓄冷熱交換器。 The inner fin has a relatively low bonding rate with the inner wall of the cold storage material container at a portion where the second group and the fourth group of the refrigerant pipe where the superheat zone is generated and the cold storage material container are bonded, In the portion where the first group and the third group of the refrigerant pipes where the overheating region does not occur and the cold storage material container are in contact with each other, the joint ratio with the inner wall of the cold storage material container is relatively high,
The cold storage heat exchanger according to claim 23. - 前記インナフィンは、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と前記蓄冷材容器とが接合する部分では前記蓄冷材容器の内壁と接合されず、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と前記蓄冷材容器とが接触する部分では前記蓄冷材容器の内壁と接合される、
請求項23に記載の蓄冷熱交換器。 The inner fin is not joined to the inner wall of the cold storage material container at the portion where the second and fourth groups of the refrigerant pipe where the superheat zone is generated and the cold storage material container are joined, and the overheat zone is generated. In the part where the first group and the third group of the refrigerant pipe and the cool storage material container are in contact with each other, the inner wall of the cool storage material container is joined,
The cold storage heat exchanger according to claim 23. - 前記蓄冷材容器(1247)は、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に小さく、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に大きく、
前記熱伝達抑制部は前記蓄冷材容器を含む、
請求項22~25のいずれか1項に記載の蓄冷熱交換器(1240)。 The regenerator material container (1247) is connected to the regenerator material from the refrigerant tube via the regenerator material container in a portion that contacts the second group and the fourth group of the refrigerant tube in which the overheating region is generated. The portion of the refrigerant pipe that contacts the first group and the third group where the heat transfer amount is relatively small and the superheated area does not occur is transferred from the refrigerant pipe to the cold storage material via the cold storage container. Heat transfer amount is relatively large,
The heat transfer suppression unit includes the cold storage material container,
The regenerative heat exchanger (1240) according to any one of claims 22 to 25. - 前記蓄冷材容器は、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と接触する部分では前記冷媒管との接合率が相対的に低く、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と接触する部分では前記冷媒管との接合率が相対的に高い、
請求項26に記載の蓄冷熱交換器。 The cold storage material container has a relatively low bonding rate with the refrigerant pipe at a portion in contact with the second group and the fourth group of the refrigerant pipe where the overheat area is generated, and the overheat area is not generated. In the portion of the refrigerant pipe that contacts the first group and the third group, the bonding rate with the refrigerant pipe is relatively high,
The cold storage heat exchanger according to claim 26. - 前記蓄冷材容器は、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と接触する部分では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と接触する部分において前記冷媒管と接合される、
請求項26に記載の蓄冷熱交換器。 The regenerator container is formed at a distance from the refrigerant pipe without being joined to the refrigerant pipe at a portion in contact with the second group and the fourth group of the refrigerant pipe in which the overheating region is generated. The refrigerant pipe is joined to the refrigerant pipe at a portion in contact with the first group and the third group of the refrigerant pipe where no region is generated.
The cold storage heat exchanger according to claim 26. - 前記蓄冷材容器の内部において前記冷媒管の延在方向である前記長手方向に沿って延在するよう配置され、前記蓄冷材容器の内壁と接合されるインナフィンを備え、
前記蓄冷材容器(1347)は、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に小さく、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と接触する部分では、前記冷媒管から前記蓄冷材容器を介しての前記蓄冷材への伝熱量が相対的に大きく、
前記熱伝達抑制部は前記蓄冷材容器を含む、
請求項22に記載の蓄冷熱交換器(1340)。 An inner fin that is arranged so as to extend along the longitudinal direction, which is the extending direction of the refrigerant pipe, inside the cold storage material container, and is joined to an inner wall of the cold storage material container;
The regenerator material container (1347) is connected to the regenerator material from the refrigerant tube via the regenerator material container at a portion that contacts the second group and the fourth group of the refrigerant tube where the overheated region is generated. The portion of the refrigerant pipe that contacts the first group and the third group where the heat transfer amount is relatively small and the superheated area does not occur is transferred from the refrigerant pipe to the cold storage material via the cold storage container. Heat transfer amount is relatively large,
The heat transfer suppression unit includes the cold storage material container,
A cold storage heat exchanger (1340) according to claim 22. - 前記蓄冷材容器は、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と接触する部分では前記冷媒管との接合率が相対的に低く、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と接触する部分では、前記冷媒管との接合率が相対的に高い、
請求項29に記載の蓄冷熱交換器。 The cold storage material container has a relatively low bonding rate with the refrigerant pipe at a portion in contact with the second group and the fourth group of the refrigerant pipe where the overheat area is generated, and the overheat area is not generated. In the portion of the refrigerant pipe that contacts the first group and the third group, the bonding rate with the refrigerant pipe is relatively high.
The cold storage heat exchanger according to claim 29. - 前記蓄冷材容器は、前記過熱域が発生する前記冷媒管の前記第2群及び前記第4群と接触する部分では前記冷媒管と接合されず前記冷媒管と間隔をあけて形成され、前記過熱域が発生しない前記冷媒管の前記第1群及び前記第3群と接触する部分において前記冷媒管と接合される、
請求項29に記載の蓄冷熱交換器。 The regenerator container is formed at a distance from the refrigerant pipe without being joined to the refrigerant pipe at a portion in contact with the second group and the fourth group of the refrigerant pipe in which the overheating region is generated. The refrigerant pipe is joined to the refrigerant pipe at a portion in contact with the first group and the third group of the refrigerant pipe where no region is generated.
The cold storage heat exchanger according to claim 29. - 前記熱伝達抑制部として含まれる前記冷媒通路構造が、前記冷媒管の延在方向である前記長手方向に沿って複数設けられる、請求項22~31のいずれか1項に記載の蓄冷熱交換器(1040B)。 The regenerative heat exchanger according to any one of claims 22 to 31, wherein a plurality of the refrigerant passage structures included as the heat transfer suppression unit are provided along the longitudinal direction, which is an extending direction of the refrigerant pipe. (1040B).
- 少なくとも前記過熱域(S1)と接触する部分の前記蓄冷材は、他の部分と比較して相対的に融点の高い高融点蓄冷材(50A)である、
請求項22~32のいずれか1項に記載の蓄冷熱交換器(1440,1540)。 The regenerator material at least in the part that comes into contact with the superheat zone (S1) is a high melting point regenerator material (50A) having a relatively high melting point compared to other parts.
The cold storage heat exchanger (1440, 1540) according to any one of claims 22 to 32. - 前記過熱域は、前記複数の冷媒管の前記第3群のうち前記出口側通路側の近傍において発生する第2過熱域(S2)を含み、
前記複数の冷媒管のうち前記過熱域(S1)が発生する前記第2群及び第4群と接触する部分に前記高融点蓄冷材が配置され、前記第2過熱域(S2)が発生する前記第3群と接触する部分に前記高融点蓄冷材が配置される、
請求項33に記載の蓄冷熱交換器(1440)。 The superheat zone includes a second superheat zone (S2) generated in the vicinity of the outlet side passage side in the third group of the plurality of refrigerant tubes,
The high-melting-point regenerator material is disposed in a portion in contact with the second group and the fourth group where the superheat zone (S1) is generated among the plurality of refrigerant tubes, and the second superheat zone (S2) is generated. The high-melting-point regenerator material is disposed in a portion that comes into contact with the third group.
A regenerative heat exchanger (1440) according to claim 33. - 前記過熱域は、前記複数の冷媒管の前記第3群のうち前記出口側通路側の近傍において発生する第2過熱域(S2)を含み、
前記複数の冷媒管のうち前記過熱域(S1)が発生する前記第2群及び前記第4群と接触する部分に前記高融点蓄冷材が配置され、
前記複数の冷媒管の前記第3群のうち前記第2過熱域(S2)が発生する前記出口側通路側の近傍に接触する部分に前記高融点蓄冷材が配置される、
請求項33に記載の蓄冷熱交換器(1440)。 The superheat zone includes a second superheat zone (S2) generated in the vicinity of the outlet side passage side in the third group of the plurality of refrigerant tubes,
The high-melting-point regenerator material is disposed in a portion in contact with the second group and the fourth group where the superheat zone (S1) is generated among the plurality of refrigerant tubes,
The high-melting-point regenerator material is disposed in a portion of the third group of the plurality of refrigerant tubes that contacts the vicinity of the outlet side passage side where the second superheat zone (S2) is generated.
A regenerative heat exchanger (1440) according to claim 33. - 前記複数の冷媒管のうち前記過熱域(S1)が発生する前記第2群及び前記第4群と接触する部分に前記高融点蓄冷材が配置される、
請求項33に記載の蓄冷熱交換器(1540)。 The high-melting-point regenerator material is disposed in a portion in contact with the second group and the fourth group where the superheat zone (S1) is generated among the plurality of refrigerant tubes.
A regenerative heat exchanger (1540) according to claim 33. - 前記蓄冷材容器の内部に、前記冷媒管の延在方向である前記長手方向に沿って内部空間を区切る少なくとも一対の仕切り板(47d)が設けられ、前記一対の仕切り板の一方は、前記蓄冷材容器の長手方向の一方側の端部に間隙を有し、前記一対の仕切り板の他方は、前記蓄冷材容器の前記長手方向の他方側の端部に間隙を有する、
請求項2~36のいずれか1項に記載の蓄冷熱交換器(1740)。 At least a pair of partition plates (47d) for partitioning an internal space along the longitudinal direction, which is the extending direction of the refrigerant pipe, is provided inside the cold storage material container, and one of the pair of partition plates is the cold storage material. A gap at one end in the longitudinal direction of the material container, and the other of the pair of partition plates has a gap at the other end in the longitudinal direction of the cold storage material container,
The regenerative heat exchanger (1740) according to any one of claims 2 to 36.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/765,101 US10696128B2 (en) | 2015-10-01 | 2016-09-23 | Cold storage heat exchanger |
DE112016004451.8T DE112016004451B8 (en) | 2015-10-01 | 2016-09-23 | cold storage heat exchanger |
CN201680057193.1A CN108139173B (en) | 2015-10-01 | 2016-09-23 | Cold storage heat exchanger |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015-195818 | 2015-10-01 | ||
JP2015195818 | 2015-10-01 | ||
JP2016-173410 | 2016-09-06 | ||
JP2016173410A JP6409836B2 (en) | 2015-10-01 | 2016-09-06 | Cold storage heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017057174A1 true WO2017057174A1 (en) | 2017-04-06 |
Family
ID=58427420
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2016/077976 WO2017057174A1 (en) | 2015-10-01 | 2016-09-23 | Cold storage heat exchanger |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112016004451B8 (en) |
WO (1) | WO2017057174A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11073342B2 (en) | 2016-06-01 | 2021-07-27 | Denso Corporation | Regenerative heat exchanger |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005195316A (en) * | 2003-12-08 | 2005-07-21 | Showa Denko Kk | Heat exchanger |
JP2006029697A (en) * | 2004-07-16 | 2006-02-02 | Denso Corp | Refrigerant evaporator |
JP2007113904A (en) * | 2005-09-20 | 2007-05-10 | Denso Corp | Cold storage tank apparatus and refrigeration cycle apparatus using the same |
JP2013217573A (en) * | 2012-04-09 | 2013-10-24 | Denso Corp | Vehicle heat exchanger with cold storage function |
JP2013256262A (en) * | 2012-06-14 | 2013-12-26 | Denso Corp | Cold storage heat exchanger |
JP2015007518A (en) * | 2013-06-26 | 2015-01-15 | サンデン株式会社 | Cold storage heat exchanger |
JP2015010740A (en) * | 2013-06-27 | 2015-01-19 | サンデン株式会社 | Cold storage heat exchanger and its process of manufacture |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5444782B2 (en) | 2008-09-12 | 2014-03-19 | 株式会社デンソー | Cold storage heat exchanger |
JP6115896B2 (en) | 2013-06-26 | 2017-04-19 | サンデンホールディングス株式会社 | Cold storage material container |
JP2015195818A (en) | 2014-03-31 | 2015-11-09 | 株式会社大一商会 | Game machine |
JP2016173410A (en) | 2015-03-16 | 2016-09-29 | 株式会社リコー | Image formation device |
-
2016
- 2016-09-23 DE DE112016004451.8T patent/DE112016004451B8/en not_active Expired - Fee Related
- 2016-09-23 WO PCT/JP2016/077976 patent/WO2017057174A1/en active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005195316A (en) * | 2003-12-08 | 2005-07-21 | Showa Denko Kk | Heat exchanger |
JP2006029697A (en) * | 2004-07-16 | 2006-02-02 | Denso Corp | Refrigerant evaporator |
JP2007113904A (en) * | 2005-09-20 | 2007-05-10 | Denso Corp | Cold storage tank apparatus and refrigeration cycle apparatus using the same |
JP2013217573A (en) * | 2012-04-09 | 2013-10-24 | Denso Corp | Vehicle heat exchanger with cold storage function |
JP2013256262A (en) * | 2012-06-14 | 2013-12-26 | Denso Corp | Cold storage heat exchanger |
JP2015007518A (en) * | 2013-06-26 | 2015-01-15 | サンデン株式会社 | Cold storage heat exchanger |
JP2015010740A (en) * | 2013-06-27 | 2015-01-19 | サンデン株式会社 | Cold storage heat exchanger and its process of manufacture |
Also Published As
Publication number | Publication date |
---|---|
DE112016004451T5 (en) | 2018-07-26 |
DE112016004451B4 (en) | 2022-06-02 |
DE112016004451B8 (en) | 2022-11-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP4078766B2 (en) | Heat exchanger | |
JP6409836B2 (en) | Cold storage heat exchanger | |
WO2015045344A1 (en) | Cold-storage heat exchanger | |
US20150168047A1 (en) | Cold storage heat exchanger | |
US9719732B2 (en) | Cold storage heat exchanger | |
JP5274175B2 (en) | Cold storage heat exchanger | |
WO2016170751A1 (en) | Cold storage heat exchanger | |
JP5764335B2 (en) | Evaporator with cool storage function | |
JP5552309B2 (en) | Evaporator with cool storage function | |
JP5717436B2 (en) | Evaporator with cool storage function | |
WO2014017021A1 (en) | Cold storage heat exchanger | |
JP5849883B2 (en) | Cold storage heat exchanger | |
JP2012126149A (en) | Evaporator with cool storage function | |
WO2019111849A1 (en) | Heat exchanger | |
WO2017057174A1 (en) | Cold storage heat exchanger | |
JP6589790B2 (en) | Combined heat exchanger | |
JP2010243066A (en) | Cold storage heat exchanger | |
WO2020110639A1 (en) | Heat exchanger | |
JP6214242B2 (en) | Heat exchanger | |
JP6327386B2 (en) | Cold storage heat exchanger | |
JP7151560B2 (en) | cold storage heat exchanger | |
JP2018096568A (en) | Heat exchanger | |
JP6599121B2 (en) | Heat exchanger and waste heat recovery device | |
JP2017132427A (en) | Cool storage heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 16851348 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15765101 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112016004451 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 16851348 Country of ref document: EP Kind code of ref document: A1 |