CN107606822B - Evaporator with cold accumulation function - Google Patents
Evaporator with cold accumulation function Download PDFInfo
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- CN107606822B CN107606822B CN201710560796.XA CN201710560796A CN107606822B CN 107606822 B CN107606822 B CN 107606822B CN 201710560796 A CN201710560796 A CN 201710560796A CN 107606822 B CN107606822 B CN 107606822B
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- 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
Abstract
The invention provides an evaporator with a cold accumulation function, which can prolong the cold energy release time on the basis of restraining the reduction of the cooling performance in the normal refrigeration. A heat exchange core (4) of an evaporator with a cold accumulation function has an arrangement part (17) formed by arranging outer heat dissipation fins (16), a 2 nd refrigerant circulation tube (12B), a cold accumulation material container (15), a 1 st refrigerant circulation tube (12A), a cold accumulation material container (15), a 2 nd refrigerant circulation tube (12B) and the outer heat dissipation fins (16) in this order. In the arrangement portion (17), the contact area between the cold storage material container (15) and the 2 nd refrigerant circulation tube (12B) is less than or equal to, for example, 30 to 80% of the contact area between the cold storage material container (15) and one surface of the 1 st refrigerant circulation tube (12A).
Description
Technical Field
The present invention relates to an evaporator with a cold storage function used in an in-vehicle air conditioner for a vehicle that temporarily stops an engine as a drive source of a compressor when the vehicle is stopped.
In the present specification and claims, the top, bottom, left, and right (top, bottom, left, and right in fig. 1) viewed from the downstream side in the ventilation direction indicated by the arrow X in the drawings are referred to as top, bottom, left, and right.
Background
In recent years, for the purpose of environmental protection, improvement of fuel efficiency of automobiles, and the like, automobiles in which an engine is automatically stopped while waiting for a stop at a traffic light or the like have been proposed.
However, in a general vehicle-mounted air conditioner, when the engine is stopped, the compressor using the engine as a driving source is stopped, and therefore, there is a problem that the refrigerant cannot be supplied to the evaporator, and the cooling capacity is rapidly reduced.
Therefore, in order to solve such a problem, it is conceivable to provide the evaporator with a cold storage function, and to cool the vehicle interior by releasing cold energy stored in the evaporator when the engine is stopped and the compressor is stopped.
As such an evaporator with a cold storage function, an evaporator with a cold storage function has been proposed which has a heat exchange core portion having: a plurality of flat refrigerant circulation tubes, the length direction of which is directed vertically and the width direction of which is directed widthwise to the ventilation direction; a cold storage material container in which a cold storage material is sealed; and a corrugated outer heat dissipation sheet including crest portions extending in the ventilation direction, trough portions extending in the ventilation direction, and connection portions connecting the crest portions and the trough portions, in the heat exchange core, a plurality of refrigerant flow tubes are arranged at intervals in the left-right direction, whereby gaps are formed between the refrigerant flow tubes adjacent in the left-right direction, a cold storage material container is arranged in a part of the gaps and among the gaps so as to be in contact with the refrigerant flow tubes, outer heat dissipation fins are arranged in the remaining gaps, which are the gaps, so as to be in contact with the refrigerant flow tubes, the gaps in which the outer heat dissipation fins are arranged are located on both left and right sides of the gaps in which the cold storage material container is arranged, and one of left and right surfaces of the refrigerant flow tubes sandwiched between the cold storage material container and the outer heat dissipation fins is in contact with the cold storage material container and the other of the left and right surfaces is in contact with the outer heat dissipation fins (see patent document 1).
According to the evaporator with a cold accumulation function described in patent document 1, during normal cooling in which the compressor operates, cold energy of the refrigerant flowing through the refrigerant flow pipes on both sides of the cold accumulation material container is transferred to the cold accumulation material in the cold accumulation material container, and the cold energy is accumulated in the cold accumulation material. On the other hand, when the compressor is stopped, the cold energy stored in the cold storage material container is transmitted to the refrigerant flow tube through both side surfaces of the cold storage material container, transmitted from the refrigerant flow tube to the outer heat dissipation fins disposed in the gaps adjacent to both sides of the gap in which the cold storage material container is disposed, and released from the outer heat dissipation fins to the air flowing in the gaps.
In the evaporator with a cold storage function described in patent document 1, in order to extend the cold energy release time when the compressor is stopped, it is effective to increase the number of cold storage material containers to increase the amount of cold storage material, or to increase the fin pitch of all the outer fins to reduce the heat transfer area of the outer fins.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent application No. 2010-91250
Disclosure of Invention
An object of the present invention is to solve the above-described problems and provide an evaporator with a cold storage function that can extend the cold energy release time while suppressing a decrease in cooling performance during normal cooling.
The present invention is configured as follows to achieve the above object.
1) An evaporator with cold storage function has a heat exchange core having: a plurality of flat refrigerant circulation tubes, the length direction of which is directed vertically and the width direction of which is directed widthwise to the ventilation direction; a cold storage material container in which a cold storage material is sealed; and an outer heat radiation fin disposed in the heat exchange core portion so that the plurality of refrigerant flow tubes are arranged with a left-right direction spacing interval therebetween, whereby gaps are formed between the refrigerant flow tubes adjacent in the left-right direction, the cold storage material container is disposed in a part of and among the plurality of gaps so as to be in contact with the refrigerant flow tubes, the outer heat radiation fin is disposed in the remaining plurality of gaps as all the gaps so as to be in contact with the refrigerant flow tubes, in the evaporator with a cold storage function,
the heat exchange core has at least one arrangement part in which outer heat radiation fins, refrigerant circulation tubes, cold storage material containers, refrigerant circulation tubes, and outer heat radiation fins are arranged in this order, and in the arrangement part, if a refrigerant circulation tube sandwiched between two cold storage material containers and having both left and right side surfaces in contact with a cold storage material container is a 1 st refrigerant circulation tube, and a refrigerant circulation tube sandwiched between a cold storage material container and an outer heat radiation fin and having either left or right side surface in contact with a cold storage material container and other left or right side surface in contact with an outer heat radiation fin is a 2 nd refrigerant circulation tube, a contact area between the cold storage material container and the 2 nd refrigerant circulation tube becomes equal to or smaller than a contact area between the cold storage material container and one side of the 1 st refrigerant circulation tube.
2) In the evaporator with a cold storage function according to 1) above, a contact area between the cold storage material container and the 2 nd refrigerant flow tube is 30 to 80% of a contact area between the cold storage material container and one surface of the 1 st refrigerant flow tube.
3) In the evaporator with a cold storage function according to 1), the cold storage material container is provided with a cold storage material enclosing section, and the cold storage material is enclosed in the cold storage material enclosing section, a plurality of condensate water drainage grooves having a fixed flow path length in the vertical direction are formed at intervals in the ventilation direction on both left and right side surfaces of a portion of the cold storage material enclosing section of the cold storage material container which is located within the ventilation direction range of the heat exchange core section, each condensate water drainage groove is formed between two drainage groove protrusions which are provided at intervals in the ventilation direction on both left and right side surfaces of the cold storage material enclosing section of the cold storage material container and protrude outward, and at least a part of the protruding end walls of the drainage groove protrusions is in contact with the refrigerant flow pipe.
4) In the evaporator with a cold storage function according to 1) above, the outer heat dissipation fins are corrugated, each of which is composed of a crest portion extending in the ventilation direction, a trough portion extending in the ventilation direction, and a connecting portion connecting the crest portion and the trough portion, and the fin pitch of the outer heat dissipation fins is 1.0 to 2.0 mm.
Here, the fin pitch of the outer fin means a pitch between the wave crests or a pitch between the wave troughs adjacent in the vertical direction.
5) In the evaporator with a cold storage function described in the above 1), a plurality of tube groups each including two refrigerant circulation tubes arranged at an interval in the ventilation direction are arranged at an interval in the left-right direction in the heat exchange core, thereby, a gap is formed between the adjacent tube groups in the left-right direction, the cold storage material container and the outer heat dissipation fin are arranged in the gap so as to straddle two refrigerant circulation tubes of the tube groups, two 1 st refrigerant flow tubes are arranged in a row along a ventilation direction between the two cool storage material containers of the arrangement portion, and both left and right side surfaces of the two 1 st refrigerant flow tubes are in contact with the cool storage material containers, two No. 2 refrigerant circulation pipes are arranged between the cold accumulation material container and the two outer heat dissipation plates in the arrangement part along the ventilation direction, and one of the left and right surfaces of the two 2 nd refrigerant circulation tubes is in contact with the cold storage material container and the other surface thereof is in contact with the outer fin.
Effects of the invention
The evaporator with a cold accumulation function according to 1) to 5) above, wherein the heat exchange core has at least one arrangement portion in which the outer heat radiation fins, the refrigerant flow tubes, the cold accumulation material containers, the refrigerant flow tubes, and the outer heat radiation fins are arranged in this order, and in the arrangement portion, if the refrigerant flow tube sandwiched between the two cold accumulation material containers and having both left and right side surfaces in contact with the cold accumulation material containers is the 1 st refrigerant flow tube, and the refrigerant flow tube sandwiched between the cold accumulation material containers and the outer heat radiation fins and having either left or right side surface in contact with the cold accumulation material containers and the other left or right side surface in contact with the outer heat radiation fins is the 2 nd refrigerant flow tube, a contact area between the cold accumulation material containers and the 2 nd refrigerant flow tubes becomes equal to or smaller than a contact area between the cold accumulation material containers and one side surfaces of the 1 st, therefore, when the compressor is stopped, in the arrangement portion, the cold energy stored in the cold storage material container is transmitted to the 2 nd refrigerant circulation tube through one of the left and right side surfaces of the cold storage material container, transmitted from the 2 nd refrigerant circulation tube to the outer fins, and released from the outer fins to the air flowing through the gaps where the outer fins are arranged. Therefore, in the arrangement portion, the cooling energy per unit time transmitted from the cold storage material in each cold storage material container to the outer fins via the 2 nd refrigerant circulation tubes when the compressor is stopped is reduced as compared with the cooling energy per unit time transmitted from the cold storage material in the cold storage material container to the outer fins on both sides via the refrigerant circulation tubes on both sides when the compressor is stopped in the evaporator with a cold storage function described in patent document 1. As a result, the time for releasing the cooling energy from the cooling material in the cooling material container can be extended as compared with the evaporator with a cooling function described in patent document 1. Further, it is not necessary to increase the number of cold storage material containers to increase the amount of cold storage material or to increase the fin pitch of all the outer heat dissipation fins to reduce the heat transfer area of the outer heat dissipation fins, and a decrease in cooling performance during normal cooling can be suppressed.
Further, when the compressor is operated, in the arrangement portion, cold energy is transmitted from the refrigerant flowing through the 1 st and 2 nd refrigerant flow tubes to the cold storage material in the cold storage material container, and therefore, the time for storing cold in the cold storage material container is suppressed from being prolonged.
In addition, when the contact area between the cold storage material container and the 2 nd refrigerant circulation tube is smaller than the contact area between the cold storage material container and one surface of the 1 st refrigerant circulation tube, the cold energy per unit time transmitted from the cold storage material in each cold storage material container to the outer fins via the 2 nd refrigerant circulation tube when the compressor is stopped can be further reduced, and therefore the cold energy release time from the outer fins to the air passing through the gaps where the outer fins are arranged can be effectively extended.
According to the evaporator with a cold accumulation function of the above 2), the cold energy per unit time transmitted from the cold accumulation material in each cold accumulation material container to the outer fins via the 2 nd refrigerant circulation tube when the compressor is stopped can be further reduced, and therefore the cold energy release time from the outer fins to the air passing through the gaps where the outer fins are arranged can be effectively extended. Further, the shortage of cooling energy transferred from the refrigerant flowing through the 2 nd refrigerant flow tube to the cold storage material in the cold storage material container can be suppressed during the operation of the compressor.
According to the evaporator with a cold storage function of the above 4), the cooling energy release time when the compressor is stopped can be effectively extended while suppressing the decrease in cooling performance and the increase in ventilation resistance during normal cooling.
Drawings
Fig. 1 is a partially omitted perspective view showing the overall structure of the evaporator with a cold storage function according to the present invention.
Fig. 2 is an enlarged cross-sectional view taken along line a-a of fig. 1 showing the refrigerant flow tube and the outer fin on phantom lines.
Fig. 3 is a view along line B-B of fig. 2 showing the header tank and the refrigerant circulating tube in phantom lines.
Fig. 4 is a C-C line view of fig. 2 showing the header tank and the refrigerant circulating tube in phantom lines.
Detailed Description
Embodiments of the present invention are described below with reference to the drawings.
In the following description, the term "aluminum" includes aluminum alloys in addition to pure aluminum.
Fig. 1 shows the overall structure of an evaporator with a cold storage function of the present invention, and fig. 2 to 4 show the structures of the main portions thereof.
In fig. 1 and 2, an evaporator 1 with a cold storage function includes an upper aluminum header 2 and a lower aluminum header 3 arranged at an interval in the vertical direction with the longitudinal direction thereof directed to the left and right direction and the width direction thereof directed to the ventilation direction, and a heat exchange core 4 provided between the two headers 2, 3.
The upper header tank 2 includes a leeward upper header portion 5 located on the leeward side and an windward upper header portion 6 located on the windward side and integrated with the leeward upper header portion 5. A refrigerant inlet 7 is provided at the left end of the leeward upper header 5, and a refrigerant outlet 8 is provided at the left end of the windward upper header 6. The lower header tank 3 has a leeward lower header 9 located on the leeward side and an windward lower header 11 located on the windward side and integrated with the leeward lower header 9.
In the heat exchange core 4, a plurality of aluminum flat refrigerant circulation tubes 12 having a longitudinal direction oriented in the vertical direction and a width direction oriented in the ventilation direction are arranged at intervals in the left-right direction between the windward upper header 6 and the windward lower header 11 and between the leeward upper header 5 and the leeward lower header 9, respectively, the upper ends of the refrigerant circulation tubes 12 arranged on the windward side are connected to the windward upper header 6 and the lower ends thereof are connected to the windward lower header 11, and the upper ends of the refrigerant circulation tubes 12 arranged on the leeward side are connected to the leeward upper header 5 and the lower ends thereof are connected to the leeward lower header 9. The refrigerant circulation tubes 12 arranged on the windward side and the refrigerant circulation tubes 12 arranged on the leeward side are at the same positions in the left-right direction, and the tube group 13 is configured by two refrigerant circulation tubes 12 arranged in the ventilation direction, and gaps 14A, 14B are formed between the tube groups 13 adjacent in the left-right direction.
In a plurality of 1 st gaps 14A out of all the gaps 14A, 14B in the heat exchange core 4, a cold storage material container 15 made of aluminum is disposed so as to straddle two refrigerant flow tubes 12 constituting each tube group 13, and the cold storage material container 15 is joined to the two refrigerant flow tubes 12 via a brazing material in a state of being in contact therewith. Hereinafter, the joining via the brazing material is referred to as brazing. In the heat exchange core 4, a corrugated outer heat dissipation sheet 16 is arranged so as to straddle the two refrigerant flow tubes 12 constituting each tube group 13 among the remaining plurality of 2 nd gaps 14B out of all the gaps 14A, 14B, the corrugated outer heat dissipation sheet 16 is made of an aluminum brazing sheet having a brazing material layer on both surfaces, and is made up of a crest portion extending in the air flow direction, a trough portion extending in the air flow direction, and a connecting portion connecting the crest portion and the trough portion, and the outer heat dissipation sheet 16 is brazed in contact with the two refrigerant flow tubes 12. Further, the outer fins 16 are also disposed so as to straddle the two refrigerant flow tubes 12 constituting the tube group 13 outside the tube groups 13 at the left and right ends, and are brazed in contact with the two refrigerant flow tubes 12, and aluminum side plates 20 are disposed outside the outer fins 16 at the left and right ends, and are brazed to the outer fins 16.
In the case of the evaporator 1 of the present embodiment, the refrigerant passes through the refrigerant inlet 7, enters the leeward upper header 5 of the evaporator 1, passes through all the refrigerant circulation tubes 12 and the two lower headers 9 and 11, and flows out from the refrigerant outlet 8 of the windward upper header 6, and the air passes through the 2 nd gap 14B in the direction indicated by the arrow X in the drawing.
The heat exchange core 4 has at least one, and here, has a plurality of arrangement portions 17 formed by arranging outer heat radiation fins 16, refrigerant flow tubes 12, cold storage material containers 15, refrigerant flow tubes 12, and outer heat radiation fins 16 in this order. Hereinafter, in the arrangement portion 17, a refrigerant flow tube sandwiched between two cool storage material containers 15 and having both left and right side surfaces in contact with the cool storage material containers 15 is referred to as a 1 st refrigerant flow tube 12A, and a refrigerant flow tube sandwiched between the cool storage material containers 15 and the outer heat dissipation fins 16 and having one of left and right surfaces in contact with the cool storage material containers 15 and the other of left and right surfaces in contact with the outer heat dissipation fins 16 is referred to as a 2 nd refrigerant flow tube 12B. That is, one tube group 13 is formed by two 1 st refrigerant flow tubes 12A arranged in the ventilation direction between the two cool storage material containers 15 of the arrangement portion 17, and both left and right side surfaces of the two 1 st refrigerant flow tubes 12A of the tube group 13 are in contact with the cool storage material containers 15. Further, between the two cool storage material containers 15 and the two outer heat dissipation fins 16 of the arrangement portion 17, a tube group 13 is formed by two 2 nd refrigerant circulation tubes 12B arranged in the ventilation direction, and one of the right and left surfaces of the two 2 nd refrigerant circulation tubes 12B of the tube group 13 is in contact with the cool storage material container 15 and the other of the right and left surfaces is in contact with the outer heat dissipation fins 16.
As shown in fig. 2 to 4, the cool storage material container 15 is a substantially vertically long rectangular flat hollow shape with the longitudinal direction directed vertically and the width direction directed in the ventilation direction. The cold storage material container 15 is formed by pressing an aluminum brazing sheet having a brazing material layer on both surfaces thereof, and is composed of two substantially rectangular aluminum container structure plates 18 and 19 in which band- shaped portions 18a and 19a having peripheral edges of a fixed width are brazed to each other. In the cool storage material container 15, the portions of the two container structure plates 18 and 19 excluding the strip portions 18a and 19a are bulged outward to form a hollow cool storage material sealing portion 21, and the cool storage material is placed in the cool storage material sealing portion 21.
A plurality of condensate drain grooves 23 are formed on both left and right side surfaces of the cool storage material enclosing section 21 of the cool storage material container 15, that is, on outer surfaces of the left and right side walls 22 at intervals in the ventilation direction, and each of the plurality of condensate drain grooves 23 has a fixed flow path length in the vertical direction and is open at both upper and lower ends, and the condensate flows downward from above and is discharged through a lower end opening. Each condensate drain groove 23 is formed between two drain groove convex portions 24 provided on both left and right side walls 22 of the cool storage material enclosing section 21 of the cool storage material container 15 and bulging outward, and the two adjacent condensate drain grooves 23 share the drain groove convex portion 24 positioned between the two condensate drain grooves 23. At least a part of the condensate drain groove 23 and the drain groove convex portion 24 is inclined linearly upward toward the leeward side. The projection heights of all the drain groove projection portions 24 on the left and right side walls 22 of each cold storage material container 15 are equal to each other, and at least a part of the projection end walls of all the drain groove projection portions 24 is brazed in a state of being in contact with the two refrigerant circulation tubes 12 constituting the left and right tube groups 13 forming the 1 st gap 14A. A slight amount of air also flows through the condensate drain groove 23.
Here, the contact area between one surface of the cool storage material container 15 and one surface of the 2 nd refrigerant circulation tube 12B is equal to or smaller than the contact area between one surface of the cool storage material container 15 and one surface of the 1 st refrigerant circulation tube 12A. Preferably, a contact area between one surface of the cool storage material container 15 and one surface of the 2 nd refrigerant circulation tube 12B is 30 to 80% of a contact area between one surface of the cool storage material container 15 and one surface of the 1 st refrigerant circulation tube 12A. For example, as shown in detail in fig. 3 and 4, the widths of the convex portions 24 for drain grooves provided on the outer surfaces of the left and right side walls 22 of the cool storage material enclosing section 21 of the right cool storage material container 15 are equal to each other, and the number of the convex portions 24 for drain grooves provided on the outer surface of the right side wall 22 of the cool storage material enclosing section 21 of the right cool storage material container 15 (the outer surface of the side wall 22 on the 2 nd refrigerant circulation tube 12B side) is smaller than the number of the convex portions 24 for drain grooves provided on the outer surface of the left side wall 22 (the outer surface of the side wall 22 on the 1 st refrigerant circulation tube 12A side), whereby the contact area between one surface of the cool storage material container 15 and one surface of the 2 nd refrigerant circulation tube 12B becomes 30 to 80% of the contact area between one surface of the cool storage material container 15 and. If the contact area between one surface of the cold storage material container 15 and one surface of the 2 nd refrigerant flow tube 12B is smaller than the contact area between one surface of the cold storage material container 15 and one surface of the 1 st refrigerant flow tube 12A, there is a possibility that the cold energy transferred from the refrigerant flowing in the 2 nd refrigerant flow tube 12B to the cold storage material in the cold storage material container 15 during the operation of the compressor may be insufficient, whereas if it is too large, the cold energy per unit time transferred from the cold storage material in each cold storage material container 15 to the outer fins 16 via the 2 nd refrigerant flow tube 12B during the stop of the compressor may not be effectively reduced.
Although not shown in detail, the widths of the drain groove projections 24 provided on the outer surfaces of the left and right side walls 22 of the cool storage material enclosing section 21 of the left side cool storage material container 15 are equal to each other, and the number of the drain groove projections 24 provided on the outer surface of the left side wall 22 of the cool storage material enclosing section 21 of the left side cool storage material container 15 (the outer surface of the side wall 22 on the 2 nd refrigerant flow tube 12B side) is smaller than the number of the drain groove projections 24 provided on the outer surface of the right side wall 22 (the outer surface of the side wall 22 on the 1 st refrigerant flow tube 12A side).
In the cool storage material enclosing section 21 of the cool storage material container 15, an aluminum inner fin 25 is disposed in a shifted (offset) shape over substantially the entire range in the vertical direction. The inner fin 25 is formed by a plurality of corrugated band plates 26 arranged in the vertical direction and integrally connected to each other, wherein each of the corrugated band plates 26 is composed of a crest portion extending in the vertical direction, a trough portion extending in the vertical direction, and a connecting portion connecting the crest portion and the trough portion, and the crest portion and the trough portion of two adjacent corrugated band plates 26 in the vertical direction are displaced from each other in the ventilation direction.
The outer heat dissipation fins 16 are composed of crests extending in the ventilation direction, troughs extending in the ventilation direction, and coupling portions coupling the crests and the troughs, and are disposed in the 2 nd gaps 14B so as to straddle the two refrigerant circulation tubes 12 of the tube groups 13 on the left and right sides constituting the 2 nd gaps 14B, and are brazed in a state of being in contact with the two refrigerant circulation tubes 12. Preferably, the interval between the outer fins 16 is 1.0 to 2.0 mm. If the fin pitch of the outer fins 16 is less than 1.0mm, the ventilation resistance may increase, and if it exceeds 2.0mm, the cooling performance during normal cooling may be reduced although the cooling energy release time during compressor stop can be extended.
The evaporator 1 with a cold storage function described above constitutes a refrigeration cycle together with a compressor that uses an engine of a vehicle as a drive source, a condenser (refrigerant cooler) that cools refrigerant discharged from the compressor, and an expansion valve (decompressor) that decompresses refrigerant that has passed through the condenser, and is mounted as a vehicle-mounted air conditioner on a vehicle, such as an automobile, that temporarily stops the engine that is the drive source of the compressor when the vehicle is stopped.
When the compressor is operated, the low-pressure two-phase gas-liquid mixed refrigerant compressed by the compressor and passed through the condenser and the expansion valve passes through the refrigerant inlet 7, enters the leeward upper header 5 of the evaporator 1 with a cold storage function, passes through all of the refrigerant flow pipes 12, 12A, and 12B and the two lower headers 9 and 11, and flows out of the refrigerant outlet 8 of the windward upper header 6. While the refrigerant flows through the refrigerant flow tubes 12, 12A, 12B, the refrigerant exchanges heat with the air passing through the 2 nd gaps 14B disposed in the outer heat dissipation fins 16 of the evaporator 1 with a cold storage function, and the refrigerant flows out as a gas phase. That is, the cooling energy of the refrigerant flowing through the refrigerant flow tubes 12 and 12B of the tube groups 13 positioned on the left and right sides of the 2 nd gap 14B is transmitted to the air passing through the 2 nd gap 14B via the outer fins 16, and the air is cooled, and the cooled air is supplied to the cooling of the vehicle interior.
When the compressor is operated, the cold energy of the refrigerant flowing through the 1 st refrigerant flow tube 12A and the 2 nd refrigerant flow tube 12B of the arrangement portion 17 is directly transmitted to the cold storage material in the cold storage material sealing portion 21 of the cold storage material container 15 via the expanded end walls of the drain groove protrusions 24 provided on the left and right side walls 22 of the cold storage material sealing portion 21 of the cold storage material container 15, and is transmitted from the expanded end walls of the drain groove protrusions 24 to the whole cold storage material in the cold storage material sealing portion 21 of the cold storage material container 15 via the portions of the left and right side walls 22 that are not brazed to the 1 st and 2 nd refrigerant flow tubes 12A and 12B and the inner fins 25, whereby the cold energy is stored in the cold storage material.
During the operation of the compressor, condensate is generated on the surface of the cold storage material container 15, and the condensate enters the condensate drain grooves 23 and is accumulated in the condensate drain grooves 23 along the drain groove convex portions 24 on both sides of the condensate drain grooves 23 by surface tension. When the amount of the accumulated condensed water increases, the gravity acting on the accumulated condensed water is greater than the surface tension, and flows down in the condensed water drain groove 23 to be discharged downward.
When the compressor is stopped, the cold energy stored in the cold storage material container 15 of the arrangement portion 17 is directly transmitted to the 2 nd refrigerant circulation tube 12B via the expanded end wall of the drain groove convex portion 24 (wherein the drain groove convex portion 24 is provided on the side wall on the 2 nd refrigerant circulation tube 12B side (the left side wall 22 in the right cold storage material container 15 and the right side wall 22 in the left cold storage material container 15) out of the left and right side walls 22 of the cold storage material enclosure portion 21 of the cold storage material container 15), and is transmitted from the 2 nd refrigerant circulation tube 12B to the outer radiation fin 16 brazed on the side surface on the opposite side to the cold storage material container 15 in the 2 nd refrigerant circulation tube 12B. The cooling energy transmitted to the outer heat dissipation fins 16 is transmitted to the air passing through the 2 nd gap 14B where the outer heat dissipation fins 16 are arranged. Therefore, even if the temperature of the wind passing through the evaporator 1 with the cold storage function rises, the wind is cooled, and therefore, a rapid decrease in cooling capacity is prevented.
In addition, when the contact area between one surface of the cool storage material container 15 and one surface of the 2 nd refrigerant circulation tube 12B is smaller than the contact area between one surface of the cool storage material container 15 and one surface of the 1 st refrigerant circulation tube 12A, the cold energy per unit time transmitted from the cool storage material in each cool storage material container 15 to each outer heat dissipation fin 16 via the 2 nd refrigerant circulation tube 12B at the arrangement portion 17 when the compressor is stopped can be further reduced, and therefore, the cold energy release time from the outer heat dissipation fin 16 to the air passing through the gap 14B where the outer heat dissipation fin 16 is arranged can be effectively extended.
Industrial applicability
The evaporator with a cold storage function of the present invention is preferably used in a refrigeration cycle constituting a vehicle-mounted air conditioner of a vehicle in which an engine as a drive source of a compressor is temporarily stopped at the time of parking.
Claims (5)
1. An evaporator with cold storage function has a heat exchange core having: a plurality of flat refrigerant circulation tubes, the length direction of which is directed vertically and the width direction of which is directed widthwise to the ventilation direction; a cold storage material container in which a cold storage material is sealed; and an outer heat dissipation fin disposed in the heat exchange core, the plurality of refrigerant flow tubes being disposed at a left-right interval, whereby gaps are formed between the refrigerant flow tubes adjacent in the left-right direction, the cold storage material container being disposed in a part of and among the plurality of gaps so as to be in contact with the refrigerant flow tubes, the outer heat dissipation fin being disposed in the remaining plurality of gaps that are all the gaps so as to be in contact with the refrigerant flow tubes, the evaporator with a cold storage function being characterized in that,
the heat exchange core has at least one arrangement part formed by arranging outer heat radiation pieces, refrigerant circulation tubes, cold storage material containers, refrigerant circulation tubes, and outer heat radiation pieces in this order, in the arrangement part, the refrigerant circulation tube held between two cold storage material containers and having both left and right side surfaces in contact with the cold storage material container is set as a 1 st refrigerant circulation tube, and the refrigerant circulation tube held between the cold storage material container and the outer heat radiation pieces and having either left or right side surface in contact with the cold storage material container and the other left or right side surface in contact with the outer heat radiation pieces is set as a 2 nd refrigerant circulation tube, and the contact area between the cold storage material container and the 2 nd refrigerant circulation tube becomes equal to or less than the contact area between the cold storage material container and one side of the 1 st refrigerant circulation tube.
2. The evaporator with cold storage function according to claim 1,
the contact area between the cold storage material container and the 2 nd refrigerant circulation tube is 30-80% of the contact area between the cold storage material container and one surface of the 1 st refrigerant circulation tube.
3. The evaporator with cold storage function according to claim 1,
a cold storage material enclosing section is provided in a cold storage material container, a cold storage material is enclosed in the cold storage material enclosing section, a plurality of condensate water drainage grooves having a fixed flow path length in the vertical direction are formed at intervals in the ventilation direction on both left and right side surfaces of a portion of the cold storage material enclosing section of the cold storage material container which is located within the range of the ventilation direction of a heat exchange core section, each condensate water drainage groove is formed between two drainage groove protrusions which are provided at intervals in the ventilation direction on both left and right side surfaces of the cold storage material enclosing section of the cold storage material container and bulge outward, and at least a part of the bulging end walls of the drainage groove protrusions is in contact with a refrigerant flow pipe.
4. The evaporator with cold storage function according to claim 1,
the outer heat dissipation sheet is corrugated and comprises crest portions extending in the ventilation direction, trough portions extending in the ventilation direction, and connecting portions connecting the crest portions and the trough portions, and the fin pitch of the outer heat dissipation sheet is 1.0-2.0 mm.
5. The evaporator with cold storage function according to claim 1,
in the heat exchange core, a plurality of tube groups each composed of two refrigerant flow tubes arranged at intervals in the ventilation direction are arranged at intervals in the left-right direction, thereby, a gap is formed between the adjacent tube groups in the left-right direction, the cold storage material container and the outer heat dissipation fin are arranged in the gap so as to straddle two refrigerant circulation tubes of the tube groups, two 1 st refrigerant circulation tubes are arranged in a row along a ventilation direction between the two cold storage material containers of the arrangement portion, and both left and right side surfaces of the two 1 st refrigerant circulation tubes are in contact with the cold storage material containers, two No. 2 refrigerant circulation pipes are arranged between the cold accumulation material container and the two outer heat dissipation plates of the arrangement part along the ventilation direction, and one of the left and right surfaces of the two No. 2 refrigerant circulating pipes is in contact with the cold storage material container and the other of the left and right surfaces is in contact with the outer radiating fin.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016137514A JP2018009719A (en) | 2016-07-12 | 2016-07-12 | Evaporator with cold storage function |
| JP2016-137514 | 2016-07-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107606822A CN107606822A (en) | 2018-01-19 |
| CN107606822B true CN107606822B (en) | 2020-07-07 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710560796.XA Expired - Fee Related CN107606822B (en) | 2016-07-12 | 2017-07-11 | Evaporator with cold accumulation function |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2018009719A (en) |
| CN (1) | CN107606822B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2878613A1 (en) * | 2004-11-30 | 2006-06-02 | Valeo Climatisation Sa | Heat exchanger for air-conditioning of motor vehicle, has reservoirs and tubes, interposed in heat exchange separators, where each separator has side contacting with related tubes and related reservoirs |
| CN201133739Y (en) * | 2007-11-27 | 2008-10-15 | 翁国梁 | Heat exchange system high power energy-saving reservoir |
| JP2009113625A (en) * | 2007-11-06 | 2009-05-28 | Showa Denko Kk | Evaporator |
| CN201449096U (en) * | 2009-03-16 | 2010-05-05 | 黄洪滔 | Wavy fin type cold-accumulation heat exchanger |
| CN204555437U (en) * | 2015-02-05 | 2015-08-12 | 南方英特空调有限公司 | Cold storage evaporimeter |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6073561B2 (en) * | 2012-02-23 | 2017-02-01 | サンデンホールディングス株式会社 | Cold storage heat exchanger |
| JP5920087B2 (en) * | 2012-07-23 | 2016-05-18 | 株式会社デンソー | Cold storage heat exchanger |
-
2016
- 2016-07-12 JP JP2016137514A patent/JP2018009719A/en active Pending
-
2017
- 2017-07-11 CN CN201710560796.XA patent/CN107606822B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2878613A1 (en) * | 2004-11-30 | 2006-06-02 | Valeo Climatisation Sa | Heat exchanger for air-conditioning of motor vehicle, has reservoirs and tubes, interposed in heat exchange separators, where each separator has side contacting with related tubes and related reservoirs |
| JP2009113625A (en) * | 2007-11-06 | 2009-05-28 | Showa Denko Kk | Evaporator |
| CN201133739Y (en) * | 2007-11-27 | 2008-10-15 | 翁国梁 | Heat exchange system high power energy-saving reservoir |
| CN201449096U (en) * | 2009-03-16 | 2010-05-05 | 黄洪滔 | Wavy fin type cold-accumulation heat exchanger |
| CN204555437U (en) * | 2015-02-05 | 2015-08-12 | 南方英特空调有限公司 | Cold storage evaporimeter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107606822A (en) | 2018-01-19 |
| JP2018009719A (en) | 2018-01-18 |
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