CN109564067A - Heat exchanger and the refrigeration system for using it - Google Patents

Heat exchanger and the refrigeration system for using it Download PDF

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Publication number
CN109564067A
CN109564067A CN201780047793.4A CN201780047793A CN109564067A CN 109564067 A CN109564067 A CN 109564067A CN 201780047793 A CN201780047793 A CN 201780047793A CN 109564067 A CN109564067 A CN 109564067A
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CN
China
Prior art keywords
flow path
entrance
plate fin
outlet
heat exchanger
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Granted
Application number
CN201780047793.4A
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Chinese (zh)
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CN109564067B (en
Inventor
奥村拓也
山本宪昭
名越健二
大城崇裕
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Classifications

    • 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
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Abstract

Heat exchanger of the invention includes plate fin laminated body, the 1st end plate and the 2nd end plate, the 1st entrance connecting tube, the 1st outlet connecting pipe, the 2nd entrance connecting tube and the 2nd outlet connecting pipe that multiple plate fins are laminated and constitute, and folds the 2nd fluid of interflow in plate fin.Heat exchange is carried out between the 1st fluid and the 2nd fluid.Internal diameter of the internal diameter of entrance side collector flow path less than the 1st entrance connecting tube and the 2nd entrance connecting tube.Internal diameter of the internal diameter of outlet-side header flow path less than the 1st outlet connecting pipe and the 2nd outlet connecting pipe.

Description

Heat exchanger and the refrigeration system for using it
Technical field
The present invention relates to heat exchanger and use its refrigeration system.The present invention is more particularly directed to the plates that will flow refrigerant The stacking of plate fin and the heat exchanger of plate fin laminated type that constitutes and use its refrigeration system.
Background technique
In general, with refrigeration systems such as air conditioner and refrigeration machines by making to be existed by the refrigerant after compressor compresses It is recycled with heat exchangers such as condenser and evaporators and carries out cooling supply or heating with heat exchange is carried out by heat-exchange fluid.? In the refrigeration system, performance and energy saving as system are substantially controlled by the heat exchanger effectiveness of heat exchanger.Therefore, heat is handed over Parallel operation is strongly required high efficiency.
Among these, the fin-and-tube type that the heat exchanger of refrigeration system is generally used for fins set perforation heat-transfer pipe and constitutes is warm Exchanger.Then, by realizing that the downsizing of heat-transfer pipe promotes the raising and miniaturization of heat exchanger effectiveness.
But there are limits for the downsizing of above-mentioned heat-transfer pipe, so the raising and miniaturization of heat exchanger effectiveness are increasingly By near limit.
On the other hand, in the heat exchanger for exchanging thermal energy, it is known to which the plate fin with fluid flowing path is laminated And the plate fin laminated type heat exchanger constituted.
The plate fin laminated type heat exchanger flowing in the flow path formed among plate fin the 1st fluid and flowing in Heat exchange is carried out as between the 2nd fluid by heat-exchange fluid between the plate fin being laminated.Therefore, in for motor vehicle sky It is widely used (referring to patent document 1) in controlled atmosphere section machine.
Figure 33, Figure 34 indicate the plate fin laminated type heat exchanger that above patent document 1 is recorded.In heat exchanger 100, The plate fin 102 with the flow path 101 of the 1st fluid of flowing is laminated and constitutes plate fin laminated body 103.In plate fin laminated body 103 both sides are laminated with end plate 104.
Existing technical literature
Patent document
Patent document 1: No. 3192719 bulletin of utility model registration
Summary of the invention
The plate fin laminated type heat exchanger that above patent document 1 is recorded passes through in the stamping concave groove of plate fin 102 And flow path 101 is formed, so having the advantages that the sectional area of flow path 101 can be made more smaller than the heat-transfer pipe of fin-and-tube type.
But the area of the collector flow path 105 of each flow path 101 of refrigerant flow direction is very big compared with the area of each flow path 101, So the pressure in the refrigerant of 105 part of collector flow path becomes larger.There is the portion with collector flow path 105 of end plate 102 as a result, The problem of dividing (with the top and the bottom of the X plate fin laminated type heat exchanger indicated in Figure 33, Figure 34) outside dilatancy.
The dilatancy in 105 part of collector flow path refrigeration dose in the case where the heat exchanger of air conditioner for automobile machine Less and refrigerant pressure is less high, so by end plate 104 rigidity inhibit.Therefore, not as problem identification.
But according to the experiment of inventor, as home-use air-conditioning and enterprise's air-conditioning etc. with air conditioner for automobile machine In the case where heat exchanger more than the refrigeration dose used, in the pressure and vapour of the dilatancy of 105 part of collector flow path Vehicle air conditioner is big compared to very, it is difficult to inhibit the dilatancy in 105 part of collector flow path.Further, distinguished according to feelings Condition has that end plate 104 can outside dilatancy.
Moreover, also distinguished because the relationship of such dilatancy etc. and in the stacking direction size of plate fin 102 There is also limitations, it is difficult to the heat exchanger as the width dimensions for being suitable for home-use air-conditioning and enterprise's air-conditioning etc..
In addition, nearest air conditioner is in research global warming potential (GWP) from the viewpoint of preventing global warming The functionization of small R1123 (1,1,2- trifluoro-ethylene) and R1132 (1,2- difluoroethylene) refrigerant.These refrigerants with it is existing R410A refrigerant compared to its pressure it is higher, it is envisaged that using when such refrigerant in the expansion of 105 part of collector flow path Deformation can become significant.Certain dilatancy braking measures must be taken as a result,.
The invention completed the present invention be directed to be led to the problem of when such opinion and environmental measures, to home-use and enterprise Heat exchanger used in industry air-conditioning etc. is also able to suppress the dilatancy in collector circuit portion.Thereby, it is possible to provide heat Exchange efficiency also high heat exchanger and the high performance refrigeration system using it.
In order to achieve the above object, heat exchanger of the invention includes: the flow path that stacking is respectively provided with the 1st fluid of flowing Multiple plate fins and the plate fin laminated body constituted；It is respectively arranged at the 1st of the stacking direction both ends of above-mentioned plate fin laminated body the End plate and the 2nd end plate；The 1st entrance connecting tube flowed into above-mentioned 1st end plate connection, above-mentioned 1st fluid；With above-mentioned 1st end plate 1st outlet connecting pipe of connection, the outflow of above-mentioned 1st fluid；It is connected to above-mentioned 2nd end plate connection, with above-mentioned 1st entrance connecting tube The 2nd entrance connecting tube；With with above-mentioned 2nd end plate connection, the 2nd outlet connecting pipe being connected to above-mentioned 1st outlet connecting pipe.? The plate fin of above-mentioned plate fin laminated body folds the 2nd fluid of interflow, carries out between above-mentioned 1st fluid and above-mentioned 2nd fluid Heat exchange.Above-mentioned multiple plate fins respectively include the flow passage region with multiple 1st fluid flowing paths for flowing above-mentioned 1st fluid And have and the header areas of above-mentioned multiple 1st fluid flowing paths and the collector flow path being connected to.Above-mentioned collector flow path includes in connection State the 1st entrance connecting tube and the entrance side collector flow path of above-mentioned 2nd entrance connecting tube and be connected to above-mentioned 1st outlet connecting pipe with it is upper State the outlet-side header flow path of the 2nd outlet connecting pipe.Above-mentioned 1st fluid flowing path is by being respectively arranged at the recessed of above-mentioned multiple plate fins Shape slot is constituted.The internal diameter of above-mentioned entrance side collector flow path is less than the interior of above-mentioned 1st entrance connecting tube and above-mentioned 2nd entrance connecting tube Diameter.The internal diameter of above-mentioned outlet-side header flow path is less than the internal diameter of above-mentioned 1st outlet connecting pipe and above-mentioned 2nd outlet connecting pipe.This Place, the internal diameter of collector flow path refer to the internal diameter of largest portion in the diameter of collector flow path.
In the header areas corresponding part of the 1st end plate, it is applied to from the 1st Fluid pressure of collector flow path side and comes from 1st Fluid pressure of the 1st entrance connecting tube and the 1st outlet connecting pipe side.Equally, in the header areas corresponding part of the 2nd end plate, It is applied to the 1st from the 1st Fluid pressure of collector flow path side and from the 2nd entrance connecting tube and the 2nd outlet connecting pipe side Fluid pressure.In the present invention, the internal diameter of entrance side collector flow path is less than in the 1st entrance connecting tube and the 2nd entrance connecting tube Diameter.In addition, internal diameter of the internal diameter of outlet-side header flow path less than the 1st outlet connecting pipe and the 2nd outlet connecting pipe.Therefore, it comes from 1st entrance connecting tube and the 1st Fluid pressure of the 1st outlet connecting pipe side are bigger than the 1st Fluid pressure from collector flow path side, The influence of the 1st Fluid pressure from collector flow path side can be offset.Equally, from the 2nd entrance connecting tube and the 2nd outlet connection 1st Fluid pressure of pipe side is bigger than the 1st Fluid pressure from collector flow path side, can offset from collector flow path side The influence of 1 Fluid pressure.Thereby, it is possible to inhibit the outside dilatancy of header areas corresponding part.Therefore, it is able to suppress this The dilatancy of sample, while further mentioning for the heat exchanger effectiveness of heat exchanger is realized by the downsizing of the 1st fluid flowing path It is high.Thus the high-performance refrigeration system that offer minimizes and energy saving is high.
According to above structure, the present invention is also able to suppress collection to heat exchanger used in home-use and enterprise air-conditioning etc. The dilatancy of area under control domain part.Thereby, it is possible to provide small-sized and efficient heat exchanger and the system high using its energy saving Cooling system.
Detailed description of the invention
Fig. 1 is the perspective view for indicating the appearance of plate fin laminated type heat exchanger of embodiments of the present invention 1.
Fig. 2 is the Section A-A figure of Fig. 1.
Fig. 3 is the stereoscopic figure for indicating the plate fin laminated body of plate fin laminated type heat exchanger of the embodiment 1.
Fig. 4 is the exploded perspective view for indicating more than the plate fin laminated body lower isolated state.
Fig. 5 is the exploded perspective view of the plate fin laminated body.
Fig. 6 is the side view for indicating the plate fin laminated arrangement of the plate fin laminated body.
Fig. 7 is the skeleton diagram for indicating the section B-B of Fig. 3.
Fig. 8 is the skeleton diagram for indicating the section C-C of Fig. 3.
Fig. 9 is to indicate that the A-A of Fig. 1 puts heavy in section skeleton diagram.
Figure 10 is by the interconnecting piece of each connecting tube of the entrance and exit of the plate fin laminated body of embodiments of the present invention 1 Divide the sum aggregate tube opening part perspective view that truncation indicates.
Figure 11 is by the refrigerant flow path group part truncated table of the plate fin laminated body of the plate fin laminated type heat exchanger The perspective view shown.
Figure 12 is the perspective view for indicating the refrigerant flow path group part truncation of the plate fin laminated type heat exchanger.
Figure 13 is by the positioning boss bore portion truncated table of the plate fin laminated body of the plate fin laminated type heat exchanger The perspective view shown.
Figure 14 is to indicate the collector opening portion truncation of the plate fin laminated body of the plate fin laminated type heat exchanger Perspective view.
Figure 15 is the top view for constituting the plate fin of plate fin laminated body of the plate fin laminated type heat exchanger.
Figure 16 is the enlarged plan view for indicating the header areas of the plate fin.
Figure 17 is the exploded view for indicating the structure division amplification of the plate fin.
Figure 18 A is the top view of the 1st plate fin.
Figure 18 B is the top view of the 2nd plate fin.
The top view of state when Figure 18 C is for illustrating that the 1st, the 2nd two wing plate is overlapped.
Figure 19 is for illustrating that the refrigerant of the plate fin flows the figure made.
Figure 20 is the amplification stereogram for indicating the protrusion being arranged in the flow passage region of the plate fin.
Figure 21 is to indicate that the amplification for the protrusion being arranged in the u turn side end of the refrigerant flow path of the plate fin is three-dimensional Figure.
Figure 22 is the appearance for indicating the plate fin laminated body of plate fin laminated type heat exchanger of embodiments of the present invention 2 Perspective view.
Figure 23 is the top view for indicating to constitute the plate fin of the plate fin laminated body.
Figure 24 is the exploded view for indicating the structure division amplification of the plate fin of the plate fin laminated type heat exchanger.
Figure 25 is by the refrigerant flow path group part truncated table of the plate fin laminated body of the plate fin laminated type heat exchanger The perspective view shown.
Figure 26 is the appearance for indicating the plate fin laminated body of plate fin laminated type heat exchanger of embodiments of the present invention 3 Perspective view.
Figure 27 is the perspective view for indicating the state after removing flow-dividing control pipe from the plate fin laminated body.
Figure 28 is the perspective view for indicating the flow-dividing control pipe insertion portion of the plate fin laminated body.
Figure 29 is the perspective view of the flow-dividing control pipe of the plate fin laminated type heat exchanger.
Figure 30 is the skeleton diagram for indicating the section of flow-dividing control tube portion of the plate fin laminated type heat exchanger.
Figure 31 is the refrigeration cycle diagram using the air conditioner of wing plate laminated type heat exchanger of the invention.
Figure 32 is the summary sectional view of the air conditioner.
Figure 33 is the skeleton diagram for indicating the section of existing plate fin laminated type heat exchanger.
Figure 34 is the top view of the plate fin of the existing plate fin laminated type heat exchanger.
Specific embodiment
The heat exchanger of 1st invention includes: the multiple plate fins for the flow path that stacking is respectively provided with the 1st fluid of flowing and constitutes Plate fin laminated body；It is respectively arranged at the 1st end plate and the 2nd end plate at the stacking direction both ends of above-mentioned plate fin laminated body；With The 1st entrance connecting tube that above-mentioned 1st end plate connection, above-mentioned 1st fluid flow into；With above-mentioned 1st end plate connection, above-mentioned 1st fluid 1st outlet connecting pipe of outflow；With above-mentioned 2nd end plate connection, the 2nd entrance connecting tube being connected to above-mentioned 1st entrance connecting tube； With with above-mentioned 2nd end plate connection, the 2nd outlet connecting pipe being connected to above-mentioned 1st outlet connecting pipe.In above-mentioned plate fin laminated body Plate fin fold the 2nd fluid of interflow, carry out heat exchange between above-mentioned 1st fluid and above-mentioned 2nd fluid.Above-mentioned multiple plates The flow passage region of fin respectively included with multiple 1st fluid flowing paths for flowing above-mentioned 1st fluid and have with it is above-mentioned multiple The header areas of 1st fluid flowing path and the collector flow path being connected to.Above-mentioned collector flow path include be connected to above-mentioned 1st entrance connecting tube with The entrance side collector flow path and above-mentioned 1st outlet connecting pipe of connection of above-mentioned 2nd entrance connecting tube and above-mentioned 2nd outlet connecting pipe Outlet-side header flow path.Above-mentioned 1st fluid flowing path is made of the concave groove for being respectively arranged at above-mentioned multiple plate fins.Above-mentioned entrance The internal diameter of side collector flow path is less than the internal diameter of above-mentioned 1st entrance connecting tube and above-mentioned 2nd entrance connecting tube.Above-mentioned outlet-side header The internal diameter of flow path is less than the internal diameter of above-mentioned 1st outlet connecting pipe and above-mentioned 2nd outlet connecting pipe.Herein, the internal diameter of collector flow path Refer to the internal diameter of largest portion in the diameter of collector flow path.
In the header areas corresponding part of the 1st end plate, it is applied to from the 1st Fluid pressure of collector flow path side and comes from 1st Fluid pressure of the 1st entrance connecting tube and the 1st outlet connecting pipe side.Equally, in the header areas corresponding part of the 2nd end plate, It is applied to the 1st from the 1st Fluid pressure of collector flow path side and from the 2nd entrance connecting tube and the 2nd outlet connecting pipe side Fluid pressure.In the present invention, the internal diameter of entrance side collector flow path is less than in the 1st entrance connecting tube and the 2nd entrance connecting tube Diameter.In addition, internal diameter of the internal diameter of outlet-side header flow path less than the 1st outlet connecting pipe and the 2nd outlet connecting pipe.Therefore, it comes from 1st entrance connecting tube and the 1st Fluid pressure of the 1st outlet connecting pipe side are bigger than the 1st Fluid pressure from collector flow path side, The influence of the 1st Fluid pressure from collector flow path side can be offset.Equally, from the 2nd entrance connecting tube and the 2nd outlet connection 1st Fluid pressure of pipe side is bigger than the 1st Fluid pressure from collector flow path side, can offset from collector flow path side The influence of 1 Fluid pressure.Thereby, it is possible to inhibit the outside dilatancy of header areas corresponding part.Therefore, it is able to suppress this The dilatancy of sample, while further mentioning for the heat exchanger effectiveness of heat exchanger is realized by the downsizing of the 1st fluid flowing path It is high.Thus the high-performance refrigeration system that offer minimizes and energy saving is high.
In the 2nd invention, the above-mentioned internal diameter of above-mentioned entrance side collector flow path is less than above-mentioned 1st entrance connecting tube and above-mentioned the The outer diameter of 2 entrance connecting tubes.The above-mentioned internal diameter of above-mentioned outlet-side header flow path is less than above-mentioned 1st outlet connecting pipe and the above-mentioned 2nd The outer diameter of outlet connecting pipe.
Thereby, it is possible to bear the refrigerant pressure from collector flow path side with the tube wall of connecting tube.
In the 3rd invention, the u-shaped composition of difference of above-mentioned multiple 1st fluid flowing paths.Above-mentioned entrance side collector flow path and Above-mentioned outlet-side header flow arrangement is in above-mentioned multiple respective one end sides of plate fin.In entering for above-mentioned entrance side collector flow path Mouth opening and exit opening have been respectively communicated with above-mentioned 1st entrance connecting tube and the 2nd entrance connecting tube.In above-mentioned outlet-side header stream The entrance opening and exit opening on road have been respectively communicated with the 1st outlet connecting pipe and the 2nd outlet connecting pipe.
Increase refrigerant thereby, it is possible to not keep the 1st fluid flowing path long with increasing (making length ruler modest ability) plate fin Heat exchange amount further increases heat exchanger effectiveness.And miniaturization can be promoted.Moreover, because by entrance side collector flow path and Outlet-side header flow path concentrates on the one end of plate fin, even if the 1st fluid flow of header areas part becomes more, the 1st fluid The pressure of flow path is got higher, and can also be utilized above-mentioned counteracted by pressure effect, is reliably prevented the expansion of header areas corresponding part Deformation.
In the 4th invention, the shunting control being inserted into above-mentioned collector flow path is connected in the entrance opening of above-mentioned 1st end plate Tubulation.Above-mentioned 1st end plate is by making potential difference between above-mentioned flow-dividing control pipe and above-mentioned 1st entrance connecting tube or above-mentioned Above-mentioned flow-dividing control pipe is connect by the potential difference ratio between flow-dividing control pipe and above-mentioned 1st outlet connecting pipe with above-mentioned 1st entrance The small material of potential difference when pipe is directly connected to or is directly connected to above-mentioned flow-dividing control pipe and above-mentioned 1st outlet connecting pipe It is formed.
The variety classes that thereby, it is possible to prevent from generating in the case where flow-dividing control pipe and inflow and outflow pipe to be directly connected to Metal contact corrosion can greatly improve reliability when used for a long time.
In the 5th invention, have multiple above-mentioned plate fin laminated bodies.Above-mentioned plate fin laminated body passes through above-mentioned 2nd entrance Connecting tube and above-mentioned 2nd outlet connecting pipe are interconnected.
Thereby, it is possible to increase the dimension width of the plate fin stacking direction of entire heat exchanger, expansion can inhibited to become The heat exchanger for being suitable for the long size of home-use air-conditioning and enterprise's air-conditioning etc. is realized while shape.
6th invention is to have the refrigeration system of above-mentioned heat exchanger.
Refrigeration system has the dilatancy for inhibiting header areas part, small-sized and efficient heat exchanger as a result,.Cause This, can be realized the high high-performance refrigeration system of energy saving.
Hereinafter, the embodiments of the present invention will be described with reference to the drawings.
In addition, heat exchanger of the invention is not limited to the plate fin laminated type heat recorded in the following embodiments and the accompanying drawings friendship The structure of parallel operation, and include the structure with the same heat exchanger of technical idea illustrated in the following embodiments and the accompanying drawings.
In addition, embodiments described below only indicates an example of the invention, structure, function shown in embodiment Energy, movement etc. are only to illustrate, and are not limited of the invention.
(embodiment 1)
Fig. 1 is the appearance for indicating the plate fin laminated type heat exchanger (hreinafter referred to as heat exchanger) 1 of present embodiment Perspective view.Fig. 2 is the Section A-A figure of Fig. 1.Fig. 3 is the plate wing for indicating the plate fin laminated type heat exchanger of the embodiment 1 The stereoscopic figure of laminate.Fig. 4 is the exploded perspective view for indicating more than the plate fin laminated body lower isolated state.Figure 5 be the exploded perspective view of the plate fin laminated body.Fig. 6 is the side view for indicating the plate fin laminated arrangement of the plate fin laminated body Figure.
As shown in Figure 1, the heat exchanger 1 of present embodiment connects multiple plate fin laminated bodies 2 and constitutes.
As shown in Figure 3, Figure 4, plate fin laminated body 2 multiple has by being laminated between the 1st end plate 3a and the 2nd end plate 3b Flow the refrigerant flow path group (refrigeration about the plate fin 2a comprising the refrigerant flow path group of the refrigerant as the 1st fluid Agent flow passage structure later be described in detail) plate fin 2a and constitute.The 1st end plate 3a and the 2nd end plate 3b use heat exchanger as When condenser, the entrance connecting tube 4 that refrigerant flows into and the outlet that the refrigerant of the flow path in plate fin 2a is discharged Connecting tube 5 is connected and fixes.
The refrigerant flow path group of the refrigerant of flow plate fin 2a u-shaped (including substantially U-shaped) is formed.With refrigerant The connected entrance connecting tube 4 of flow path group, 5 centralized configuration of outlet connecting pipe are in the one end side of plate fin laminated body 2.
In addition, 2 (the lowermost shown in FIG. 1 of plate fin laminated body of the least significant end in the flow direction for becoming refrigerant Plate fin laminated body 2) the 2nd end plate 3b be not provided with entrance connecting tube 4, outlet connecting pipe 5, become closed state.
In addition, being set to the two sides (the upper side and lower side in Fig. 1) of the stacking direction of plate fin laminated body 2, overlooking and plate wing Piece 2a is the 1st of roughly the same shape the, the 2nd end plate 3a, 3b is formed by the plate with rigidity, such as by being ground to aluminium, aluminium Alloy, stainless steel and other metal materials carry out intermetallic composite coating and are formed.
Moreover, plate fin laminated body 2, the 1st end plate 3a and the 2nd end plate 3b are with the state being laminated is brazed engagement and is formed as One.Other fixing means with heat resistance, for example chemical joint element can be used also to engage in they.
In addition, corresponding in the header areas for the 1st end plate 3a and the 2nd end plate 3b for being configured at the two sides of plate fin laminated body 2 Partial outer surface is configured with stiffening plate 16a, 16b as shown in figs. 3 and 5.Herein, " header areas corresponding part " is Refer to the header areas H (referring to Fig.1 5) when the 1st, the 2nd end plate 3a, 3b and plate fin 2a coincide together, with plate fin 2a Be overlapped the 1st, a part (predetermined region of end plate) of the 2nd end plate.Screw bolt and nut or riveting by run-through board fin laminated body 2 Stiffening plate 16a, 16b is linked and is fixed by the linking parts such as pin shaft 9.That is, the 1st end plate 3a and the 2nd end of 2 two sides of plate fin laminated body Plate 3b clips plate fin laminated body 2, plate fin laminated body 2 is mechanically linked to fixation.
In addition, stiffening plate 16a, 16b are as end plate 3a, 3b by having the plate, such as stainless steel, aluminium alloy etc. of rigidity Metal material is formed.
As shown in Figure 1, the plate fin laminated body 2 constituted as described above is connected by entrance connecting tube 4, outlet connecting pipe 5 Knot connection is multiple.Heat exchanger is constituted as a result,.The refrigerant flowed into from the entrance connecting tube 4 of the plate fin laminated body 2 of topmost Other plate fin laminated bodies 2 of flow direction connection connection.Moreover, returning to the plate fin layer of topmost from other plate fin laminated bodies 2 The refrigerant of stack 2 is discharged outside 5 heat exchanger 1 of outlet connecting pipe.Herein, in each plate fin laminated body, refrigerant is each The flow path group of the inside of plate fin 2a flows parallel along its length, carries out u turn and turns back.On the other hand, as the 2nd stream The air of body is passed through from the gap formed between the lamination for constituting the plate fin 2a of each plate fin laminated body 2.Thus conduct is carried out The heat exchange of the refrigerant of 1st fluid and the air as the 2nd fluid.
Then, the plate fin 2a for constituting plate fin laminated body 2 is illustrated, which constitutes heat exchange The main body of device 1.
Fig. 7~Figure 14 is the perspective view for indicating a part truncation of plate fin laminated body 2.Figure 15~Figure 21 is display plate The figure of the structure of fin 2a.
As shown in figure 11, the stacking of plate fin laminated body 2 has plate fin 2a (the 1st plate fin the 6, the 2nd of 2 kinds of flow passage structures Plate fin 7) and constitute.
As shown in figure 17, the 1st plate fin 6 of plate fin 2a and the 2nd plate fin 7 by stamping respectively by having later 1st plate-shaped member 6a of the refrigerant flow path structure of detailed description with and the face the 1st plate-shaped member 6a structure identical 2nd plate-shaped member 6b Opposite soldered joint and constitute.1st plate-shaped member 6a and the 2nd plate-shaped member 6b are respectively provided with concave groove, by making the 1st plate Component 6a and the 2nd plate-shaped member 6b are relatively affixed, constitute refrigerant flow path.1st plate-shaped member 6a and the 2nd plate-shaped member 6b by The rectangular sheet metal such as aluminium, aluminium alloy, stainless steel is constituted.
Hereinafter, being illustrated to the flow passage structure formed in plate fin 2a.
In addition, because plate fin 2a the 1st plate fin 6 and the 2nd plate fin 7 in addition to aftermentioned refrigerant flow path 11 dislocation It is identical with external structure, so being illustrated and being illustrated to the case where the 1st plate fin 6 in Figure 15~Figure 17 etc..
As shown in figure 15, plate fin 2a (6,7) is formed with collection in an end (being left side in Figure 15) for length direction Area under control domain H, other regions become flow passage region P.Moreover, collection tube opening 8a and outlet in the header areas inflow side HXing Chengyou The collection tube opening 8b of side.Entrance connecting tube has been respectively communicated in the collection tube opening 8a of inflow side and the collection tube opening 8b of outlet side 4 and outlet connecting pipe 5.
In addition, flow passage region P is formed with refrigerant as 1st fluid of multiple flowings from collection tube opening 8a parallel 1st fluid flowing path (hereinafter referred to as refrigerant flow path) 11.11 groups of refrigerant flow path the other end (figures in plate fin 2a (6,7) Near 15 right-hand end) it turns back, it is connected with the collection tube opening 8b of outlet side.Specifically, 11 groups of refrigerant flow path by with stream Enter the collection tube opening 8a outlet side flow path portion 11a being connected of side and the return road side flow path portion being connected with the collection tube opening 8b of outlet side 11b is constituted, and is become in the shape that substantially U-shaped is turned back.The refrigerant flowed into from the collection tube opening 8a of inflow side is from outlet effluent Road portion 11a flows to the collection tube opening 8b of outlet side to the flow path portion 11b u turn of return road side.
In addition, as amplification indicates in Figure 16, being formed with from collector around the collection tube opening 8a of inflow side 11 groups of refrigerant flow direction refrigerant flow path of the collector flow path 10 of opening 8a.Collector flow path 10 includes outside collection tube opening 8a Week bulging mode formed peripheral flow path 10a, to 11 groups of sides of refrigerant flow path of peripheral flow path 10a extend one connection The flow path 10b and multiple-limb flow path 10c that the connection flow path 10b is connected with 11 groups of refrigerant flow path of each flow path.
In addition, the peripheral flow path 10a of collector flow path 10, connection flow path 10b are compared with multiple-limb flow path 10c in flow passage region Each refrigerant flow path 11 that P is set side by side is formed widerly.In collector flow path 10, the vertical sectional shape orthogonal with flow direction For rectangular shape.
In addition, the opening diameter of the collection tube opening 8a of inflow side diameter compared with the opening diameter of the collection tube opening 8b of outlet side Greatly.This is because in the case where heat exchanger is used as condenser, the volume and heat exchange of the refrigerant after heat exchange The volume of refrigerant before, which is compared, to become smaller.
In addition, with the number of the collection tube opening 8b of the outlet side return road side flow path portion 11b being connected than the collection from inflow side The number for the outlet side flow path portion 11a that the refrigerant of tube opening 8a flows into is few.This is because the diameter with collection tube opening 8a, 8b Different reasons is identical, and the volume of the refrigerant after heat exchange becomes smaller compared with the volume of the refrigerant before heat exchange.
In the present embodiment, the number for illustrating outlet side flow path portion 11a is 7, and the number of return road side flow path portion 11b is 2, but it's not limited to that.
In addition, the entrance of refrigerant is opposite with above-mentioned structure in the case where heat exchanger is used as evaporator.
Be located at the two sides of plate fin laminated body 2 constituted as described above the 1st, the 2nd end plate 3a, 3b, as shown in Figure 9 Like that, entrance is formed in the part opposite with collection tube opening 8a, the collection tube opening 8b of outlet side of entrance side of plate fin 2a Be open 8aa, exit opening 8bb.Moreover, in a manner of covering entrance opening 8aa, exit opening 8bb, the 1st, the 2nd end plate 3a, 3b is connected with entrance connecting tube 4, outlet connecting pipe 5.
In the heat exchanger 1 of present embodiment, as illustrated in figs 1 and 9, refrigerant is from the 1st entrance connecting with the 1st end plate 3a Connecting tube 4a is flowed into plate fin laminated body 2, be connected to entrance side collector flow path 10 and entrance side collector flow path 10, and the 2nd The plate fin laminated body 2 of 2nd entrance connecting tube 4b, Xiang Xianglin of end plate 3b connection is discharged.In addition, passing through each plate fin laminated body The refrigerant of return flows into plate fin laminated body 2 from the 2nd outlet connecting pipe 5b connecting with the 2nd end plate 3b, warp and outlet side The 1st outlet connecting pipe 5a that collector flow path 14 and outlet-side header flow path 14 are connected to, connect with the 1st end plate 3b, heat exchanger 1 Outer discharge.
Herein, the internal diameter L1 and entrance opening 8aa of the internal diameter L1 and the 2nd entrance connecting tube 4b of the 1st entrance connecting tube 4a Opening diameter is comparably major diameter.In addition, the internal diameter L2 of the internal diameter L2 and the 2nd outlet connecting pipe 5b of the 1st outlet connecting pipe 5a and outlet The opening diameter of opening 8bb is comparably major diameter.
In addition, the internal diameter L1 of the internal diameter L1 and the 2nd entrance connecting tube 4b of the 1st entrance connecting tube 4a be greater than by end plate 3a, The stacking of 3b and the internal diameter M1 of entrance side collector flow path 10 formed.In addition, the internal diameter L2 and the 2nd of the 1st outlet connecting pipe 5a goes out The internal diameter L2 (referring to Fig. 9, Figure 16) of mouth connecting tube 5b is greater than the outlet-side header flow path 14 of the stacking formation by end plate 3a, 3b Internal diameter M2 (referring to Fig. 9, Figure 16).
Further, in the present embodiment, the outer diameter of the outer diameter L3 and the 2nd entrance connecting tube 4b of the 1st entrance connecting tube 4a L3 is greater than the internal diameter of the entrance side collector flow path 10 formed by the stacking of entrance opening 8aa, exit opening 8bb and plate fin 2a M1.In addition, the outer diameter L3 of the outer diameter L3 and the 2nd outlet connecting pipe 5b of the 1st outlet connecting pipe 5a are greater than outlet-side header flow path 14 Internal diameter M2.In short, the size of internal diameter M1, M2 are big slighter than internal diameter L1, the size of L2 and outer diameter L3, L4.
In addition, in plate fin 2a (6,7), in the outlet that the refrigerant for being formed with the collection tube opening 8a from inflow side flows into The region of side flow path portion 11a and being formed with flows between the region of the collection return road tube opening 8b side flow path portion 11b of outlet side, such as schemes 15, it shown in Figure 16 etc. like that, is configured in order to which the mutual heat transfer of refrigerant in plate fin 2a (6,7) is reduced (heat-insulated) Slit 15.
Moreover, the collector flow path 10 of entrance side connection flow path 10b outlet side flow path portion 11a, be biased to return road side The partly setting of flow path portion 11b opposite side.That is, as shown in Figure 19, from the center line O of connection flow path 10b to return road side The width V of the flow path 11a-1 at the end of the side flow path portion 11b is greater than to the flow path 11a-2 with return road side flow path portion 11b opposite side one end Width W.Moreover, being formed with shunting in the end of connection flow path 10b, i.e. with the opening portion being connected outlet side flow path portion 11a Impact walls 17.Outlet side circuit portion on the extended line of connection flow path 10b becomes non-flow path portion 18.Therefore, from company It connects the refrigerant of flow path 10b and shunts the collision of impact walls 17 and shunt (being to shunt in Figure 19 up and down), through under connection flow path 10b The upper and lower each flow path group for the outlet side flow path portion 11a that the multiple-limb flow path 10c flow direction of trip side is divided into non-flow path portion 18.
In addition, the collection tube opening 8b in outlet side is also formed with collector flow path 14.Collector flow path 14 is touched in addition to not having to shunt Wall 17 is hit, is formed with the essentially identical shape of collector flow path 10 for the collection tube opening 8a for being set to entrance side.Moreover, in this implementation In mode, the number of 11 groups of refrigerant flow path of return road side flow path portion 11b is few to two, so connection flow path 10b is set to and returns On the approximate centre line of trackside flow path portion 11b group.
In the plate fin 2a (6,7) constituted as described above, in the 1st plate fin 6, as shown in Figure 18 A like that, in flow path area Domain P is formed with multiple protrusions 12 (the 1st protrusion: 12a, 12aa, the 2nd protrusion: 12b) across specified interval in the longitudinal direction.
Figure 18 A indicates the 1st plate fin 6.Figure 18 B indicates the 2nd plate fin 7.Figure 18 C is indicated two plate fin 2a (6,7) The state of overlapping (for indicating the figure of 11 groups of refrigerant flow path of dislocation).
As shown in Figure 18 A~C, the 1st protrusion 12a (is the long side of the left and right sides in Figure 18 A in plate fin long side edge portion Edge part) flat end 19a formed.Flat end 19b of the 1st protrusion 12aa in the two sides edge of slit 15 is formed.Such as Fig. 8 Shown, the 1st protrusion 12a is connected to the flat end in the long side edge portion of the 2nd adjacent to and opposite in the stacking direction plate fin 7 19a.1st protrusion 12aa is connected to the two sides edge for being located at the slit 15 of the 2nd adjacent to and opposite in the stacking direction plate fin 7 Flat end 19b.The folded interfloor distance between the 1st plate fin 6 and the 2nd adjacent plate fin 7 is limited to defined length as a result, Degree.Moreover, the 1st protrusion 12a be located at gone inwardly from the ora terminalis in each long side edge portion, for example go inwardly from ora terminalis 1mm with The mode of the position of upper (11 side of refrigerant flow path) is formed.
By Figure 18 A it is found that the 2nd protrusion 12b is between 11 groups of refrigerant flow path of flow path, in the present embodiment for as non- The recession plane portion 20 of flow path portion 18 is formed across specified interval.2nd protrusion 12b is connected to shown in Figure 18 B in stacking direction The recession plane portion 20 of upper the 2nd adjacent plate fin 7.The 2nd protrusion 12b is in the same manner as the 1st protrusion 12a, 12aa by the 1st as a result, Folded interfloor distance between plate fin 6 and the 2nd plate fin 7 is limited to defined length.
In addition, as shown in figure 20, each protrusion 12 (12a, 12aa, 12b) by by the flat end 19a of the 1st plate fin 6, The a part in 19b and recession plane portion 20 is cut forming and is formed.Hereinafter, sometimes protrusion 12 (12a, 12aa, 12b) is known as cutting It is split into shape protrusion.The incision for cutting forming protrusion shapes ora terminalis Y with the 2nd fluid of the folded interflow in plate fin 2a with arrow The flow direction that head indicates is opposite, cuts forming standing piece Z (referring to Figure 20) along the 2nd fluid flow direction.In this embodiment party In formula, cutting forming protrusion is in towards the such section substantially U-shaped of the 2nd fluid flow direction opening (substantially U-shaped) It cuts forming and is formed.
Moreover, each plate fin 2a (6,7), end plate 3 (3a, 3b) soldered joint when, it is each cut forming protrusion 12 (12a, 12aa, 12b) each top surface be fixed in adjacent plate fin 2a (6,7).Thus each plate fin 2a (6,7) is integrally linked.
In addition, in the present embodiment the 1st cut forming protrusion 12a, 12aa and the 2nd cut forming protrusion 12b with along The flow direction of 2nd fluid (air) becomes linear mode and configures, and can also configure with being staggered.
In addition, as shown in figure 21, plate fin 2a (6) is in the side of turning back of the flow passage region P of 11 groups of u turns of refrigerant flow path The fin planar portions 21 of end be also formed with multiple protrusions 22 (22a, 22b).Protrusion 22 (22a, 22b) is put down also by by fin Face 21 cuts forming and forms (hereinafter, protrusion 22 (22a, 22b) is also known as cut to forming protrusion sometimes), and it is prominent to cut forming Play the mobile phase pair of incision forming the ora terminalis Y and the 2nd fluid of 22 (22a, 22b).In addition, cutting forming protrusion 22 (22a, 22b) It is set to the downstream side of positioning boss hole 13.The nearest incision forming protrusion 22a in the downstream side of positioning boss hole 13 is to incite somebody to action The shape of the fluid stream contraction in the downstream side of positioning boss hole 13, such as the 2nd fluid flow direction cross sectional shape of direction are in Ha The mode of font (inverted v-shaped) opening is cut forming and is formed.Moreover, each protrusion 22b of further downstream divides compared with protrusion 22a It is not interconnected in such a way that the center line of its center line and next protrusion 22b in downstream side is staggered.
In addition, it is each cut forming protrusion 22 (22a, 22b) also with cut forming protrusion 12 (the 1st cuts forming protrusion: 12a, 12aa, the 2nd cuts forming protrusion: 12b) equally, cut each top surface for shaping protrusion 22 (22a, 22b) and adjacent plate fin 2a (7) it abuts affixed.As a result, by the gap between adjacent plate fin 2a be limited to as defined in length and by each plate fin 2a that This connection.
In addition, as shown in Figure 13 etc., in header areas, the end of H is formed with as positioning in plate fin 2a (6,7) Through hole (hereinafter referred to as positioning boss hole) 13.The two sides for being laminated in plate fin 2a (6,7) the 1st, the 2nd end plate 3a, 3b and stiffening plate 16a, 16b are also formed with positioning boss hole 13.Moreover, it is more to be equipped with stacking in positioning boss hole 13 Positioning pin fixture when a (6,7) plate fin 2a.Thereby, it is possible to carry out the high-precision stacking of multiple plate fin 2a.In this reality It applies in mode, (the ginseng of linking parts 9 such as bolt of stiffening plate 16a, 16b of link plate fin laminated body 2 and the 1st, the 2nd end plate 3a, 3b According to Fig. 5) also serve as positioning pin fixture.
Further, the outer peripheral portion of boss hole 13, upper and lower shape are used in the positioning for being set to the both ends of plate fin 2a (6,7) At hole peripheral part (the hereinafter referred to as positioning boss hole peripheral part) 13a for having bulging.Positioning is formed with boss hole peripheral part 13a The space different from the flowing flow path of refrigerant.As shown in Figure 13, positioning is with boss hole peripheral part 13a and in stacking direction Upper adjacent plate fin 2a (6,7) is abutted, and becomes the header areas supporting part in the lamination gap of holding plate fin 2a.
Moreover, the positioning formed around positioning boss hole 13 with boss hole peripheral part 13a with shown in Figure 14 Header areas H-shaped at entrance, export the collector flow path 10,14 (10a, 10b, 10c) of both sides together, soldering is fixed in and is being laminated The collector flow path 10,14 of opposite plate fin 2a (6,7) and positioning boss hole peripheral part 13a on direction.As a result, by plate fin The header areas part connection of 2a (6,7) is integral.
In addition, being in refrigerant flow path 11 of the invention, such as by the cross sectional shape orthogonal with the direction that refrigerant flows Circular shape is illustrated, but it's not limited to that.The cross sectional shape of refrigerant flow path 11 also wraps other than circular shape Include rectangular shape etc..
In addition, in the present embodiment, refrigerant flow path 11 is pressed with the two side directions shape outstanding to stacking direction It is illustrated, but may be only to the side of stacking direction shape outstanding.In addition, in the present invention, circular shape is also Including compound curve shape that is round, oval and being formed by closed curve.
The heat exchanger of present embodiment is constituted as described above, is illustrated below to its function and effect.
Firstly, illustrating the flowing and heat exchange action of refrigerant.
Refrigerant is opened from the entrance connecting tube 4 that connect with the one end side of each plate fin laminated body 2, the collector through inflow side Mouth 8a is flowed to the collector flow path 10 of each plate fin 2a.Then, refrigerant is collected the peripheral flow path 10a around tube opening 8a, is connected Flow path 10b, multiple-limb flow path 10c are met to 11 groups of flowings of refrigerant flow path.It flow to 11 groups of refrigerant flow path of each plate fin 2a Refrigerant is turned back from outlet side flow path portion 11a to return road side flow path portion 11b.Then, collector flow path 14 of the refrigerant through outlet side, Refrigerant circuit flowing of the collection tube opening 8b of outlet side from outlet connecting pipe 5 to refrigeration system.
Moreover, when refrigerant flow path 11 flows, refrigerant and between the plate fin 2a lamination of each plate fin laminated body 2 By air carry out heat exchange.
At this point, in each plate fin laminated body 2, collector with entrance side collector flow path 10 and outlet-side header flow path 14 Region H is applied with the strong pressure of refrigerant, connect with atmosphere the 1st, the header areas corresponding part of the 2nd end plate 3a, 3b want swollen Bulging deformation.
That is, as indicated by the arrows in fig. 9, being applied in the header areas corresponding part of the 1st end plate 3a from entrance side The refrigerant pressure of 14 side of collector flow path 10 and outlet-side header flow path (to upward arrow in figure).
But it in the heat exchanger of present embodiment, is not only applied in the header areas corresponding part of the 1st end plate 3a System is applied with from the refrigerant pressure of collector flow path side and also from the 1st entrance side connecting tube 4a and the 1st side outlet connecting pipe 5a Refrigerant pressure (downward arrow in figure).Moreover, the internal diameter M1 (referring to Fig. 9, Figure 16) of entrance side collector flow path 10 enters less than the 1st The internal diameter L1 of mouth connecting tube 4a, in addition, the internal diameter M2 (referring to Fig. 9, Figure 16) of outlet-side header flow path 14 is less than the 1st outlet connection The internal diameter L2 of pipe 5a.Therefore, compared with the refrigerant pressure from collector flow path 10,14 sides, the 1st side entrance connecting tube 4a is come from It is with the refrigerant pressure of the 1st side outlet connecting pipe 5a bigger, from entrance side collector flow path 10,14 side of outlet-side header flow path The influence of refrigerant pressure is cancelled.Equally, in the header areas corresponding part of the 2nd end plate 3b, the 2nd entrance connecting tube 4b is come from The refrigerant pressure of side and the 2nd side outlet connecting pipe 5b is also bigger than the refrigerant pressure from collector flow path 10,14 sides, comes from The influence of the refrigerant pressure of 10 side of entrance side collector flow path, 14 side of outlet-side header flow path is cancelled.
Further, in the present embodiment, the 1st, the outer diameter L3 and the 1st of the 2nd entrance connecting tube 4a, 4b, the 2nd outlet connection The internal diameter M2 of the outer diameter L4 of pipe 5a, 5b and the internal diameter M1 of entrance side collector flow path 10 and outlet-side header flow path 14 is comparably greatly Diameter.Therefore, it can be come from using the tube wall receiving of the 1st, the 2nd entrance connecting tube 4a, 4b and the 1st, the 2nd outlet connecting pipe 5a, 5b The refrigerant pressure of 10 side of collector flow path.
Thus inhibit the dilatancy of the header areas corresponding part of the 1st, the 2nd end plate 3a, 3b gone outward.
In addition, in the present embodiment, being provided with stiffening plate in the outer surface of the header areas corresponding part of end plate 3a, 3b 16a, 16b, it is by linking part 9 that stiffening plate 16a, 16b is connected to each other.Therefore, it can more reliably inhibit header areas corresponding Partial dilatancy.
In addition, in the present embodiment, being set to the refrigerant flow path 11 of plate fin 2a in substantially U-shaped u turn, entering Mouth side collector flow path 10 and outlet-side header flow path 14 concentrate on the one end side of plate fin laminated body 2.Therefore, in plate fin layer Dual-pressure of the one end side of stack 2 by entrance side and outlet side.But structure according to the present embodiment, Neng Gouke Inhibit dilatancy by ground.
In addition, the header areas of plate fin laminated body 2, the flow path area of entrance side collector flow path 10 is maximum.Therefore, entrance The refrigerant pressure of 10 part of side collector flow path also highest.But because entrance side collector flow path 10 and adjacent entrance side collection Pipe flow path 10 connects and is brazed, so dilatancy can be effectively prevented.As a result, collector can be more reliably prevented from The dilatancy of region corresponding part.
In addition, the linking parts such as bolt 9 can as plywood fin 2a, the 1st, the 2nd end plate 3a, 3b and stiffening plate 16a, Guidance pin (fixture) when 16b uses.Thereby, it is possible to improve stacking precision, and productivity can also be improved.
Additionally, there are the strong pressures of the refrigerant for the header areas H for being applied to each plate fin laminated body 2 to make header areas H Entrance side collector flow path 10 the section peripheral flow path 10a occur compressing deformation the problem of.The periphery of entrance side collector flow path 10 The outer wall top surface of flow path 10a is the peripheral flow path 10a with adjacent other collector flow paths 10 in the stacking direction in stacking direction It is upper abutting and be brazed state.Therefore, the collector flow path 10 of header areas H will not deform, and the heat that can be realized high reliablity is handed over Parallel operation.
As described above, the heat exchanger of present embodiment is high for the heat exchanger more than refrigeration dose or using compression ratio Environment correspond to the refrigerant of type in the case where, plywood fin laminated body 2,2 can be prevented and the plate fin laminated body 2 that constitutes Header areas part dilatancy.It then, can as a result, can be used with the higher state of the pressure of refrigerant Realize high-efficient heat exchanger.
Moreover, in the heat exchanger, by making in the section of the concave groove of the plate fin 2a refrigerant flow path formed The small downsizing to realize 11 groups of refrigerant flow path of each flow path of product.Thereby, it is possible to improve heat exchanger effectiveness and realize small Type.
In short, refrigeration can be realized while preventing in the dilatancy of the header areas part of plate fin laminated body 2 The downsizing of the flow path cross sectional area of agent flow path 11 improves heat exchanger effectiveness.
Moreover, the heat exchanger of present embodiment connects multiple plate fin laminated bodies 2 as described above and constitutes, so energy Enough make the dimension width of plate fin stacking direction big.Inhibit dilatancy in short, can be realized and be suitable for home-use air-conditioning With the heat exchanger of the strip of enterprise air-conditioning etc..In addition, in the present embodiment, connect multiple plate fin laminated bodies 2 and Heat exchanger 1 is constituted, but heat exchanger 1 can also be constituted by 1 plate fin laminated body 2.
As described above, the heat exchanger of present embodiment by the diameter of the collector flow path of plate fin laminated body 2 and can enter Mouthful, the size of the diameter of outlet connecting pipe prevent dilatancy caused by refrigerant pressure.The heat exchanger of present embodiment is also With following such effect.
That is, 11 groups of refrigerant flow path in plate fin 2a setting are in as described above in the heat exchanger of present embodiment Substantially U-shaped is formed and is turned back.Therefore, plate fin 2a can not be increased it make refrigerant flow path length.
Thereby, it is possible to improve the heat exchanger effectiveness of refrigerant and air, reliably make refrigerant become supercooling state and Improve the efficiency of refrigeration system.Further, additionally it is possible to promote the miniaturization of heat exchanger.
In addition, in the present embodiment, air and the heat exchange of interflow are folded with the plate fin in plate fin laminated body 2 Refrigerant from the collector flow path 10 of entrance side flow to connection flow path 10b, multiple-limb flow path 10c, 11 groups of refrigerant flow path.This Place is provided in the downstream side for connecting flow path 10b and shunts impact walls 17, and refrigerant is with the collision of shunting impact walls 17 and to upper and lower point Stream.Moreover, the refrigerant after shunting up and down is further shunted from multiple-limb flow path 10c to each refrigerant flow path 11.Thereby, it is possible to Prevent refrigerant from advancing with being extremely biased in the flow path of part on the extended line of connection flow path 10b.
In addition, in the present embodiment, 11 groups of u-shaped formation of refrigerant flow path, refrigerant flow path has return portion.Cause This, as from Figure 19 it will be appreciated that as, 11 groups of refrigerant flow path of each flow path length be more in periphery further away from U-shaped, In other words the side flow path 11a-2 of slit 15 is longer.Then, due to generating bias current by the difference of the flow path length.
But in the present embodiment, the connection flow path 10b from collector flow path 10 is relative to 11 groups of refrigerant flow path The center line O of outlet side flow path portion 11a is arranged with being biased to anti-return road flow path portion side.Therefore, it is able to suppress bias current, keeps each flow path big Refrigerant is equably flowed in cause.
That is, in the present embodiment, even if due to 11 groups of u-shaped compositions of refrigerant flow path, from 11 groups of refrigerant flow path Each flow path entrance side collector flow path 10 to outlet-side header flow path 14 flow path length it is different and flow path resistance changes, Refrigerant can also equably shunted to 11 groups of refrigerant flow path of each flow path.This is because because of the collector from entrance side The connection flow path 10b that flow path 10 rises is located at the position for being biased to the anti-return road side flow path portion side of outlet side flow path portion 11a, so from even The length for connecing the shunting road of flow path 10b to each outlet side flow path portion 11a is longer closer to return road side flow path portion 11b, to offset The difference of resistance.
Therefore, the shunting that can shunt the realization of impact walls 17 by 11 groups of refrigerant flow path of u turn and utilization is equal Homogenized synergistic effect obtains heat exchanger effectiveness higher heat exchanger while promoting miniaturization.
Moreover, being formed with slit between 11 groups of refrigerant flow path of outlet side flow path portion 11a and return road side flow path portion 11b 15, separated by heat.Thus it prevents to move from the heat of 11 groups of refrigerant flow path of outlet side flow path portion 11a to return road side flow path portion 11b It is dynamic, it can be efficiently by refrigerant supercooling.As a result, heat exchanger effectiveness further increases.
In addition, being provided with multiple incisions in the flow passage region P of plate fin laminated body 2 in the heat exchanger of present embodiment It shapes protrusion 12 (12a, 12aa, 12b), improves the heat exchanger effectiveness of flow passage region P.
Specifically, the incision forming ora terminalis Y of forming protrusion 12 (12a, 12aa, 12b) is cut and in the folded of plate fin 2a The fluid flow direction of 2nd fluid of interflow is opposite.The interval between plate fin lamination is fixed as a result,.Further, often exist The dead water region for cutting the downstream side generation of forming protrusion 12 (12a, 12aa, 12b) is minimum, and shapes ora terminalis Y portion cutting Generate leading edge effect.Moreover, because cutting forming protrusion (12a, 12aa, 12b) in the mode opposite with the 2nd fluid flow direction Forming is cut, so the flow resistance relative to the 2nd fluid can also be made small.It therefore, can be in suppressing plate fin laminated body 2 The flow path resistance of flow passage region P greatly improves the heat exchanger effectiveness of heat exchanger while increase.
In addition, plate fin 2a setting incision forming protrusion 12 (12a, 12aa, 12b) configuration structure consider relative to 2nd fluid is in being staggered or the various structures such as more form than weather side in downwind side.As long as according to the rule of heat exchanger Lattice, structure and the expectation of user select to improve the optimal structure of heet transfer rate.
In addition, each sky for cutting forming protrusion 12 (12a, 12aa, 12b) to flow in the gap of plate fin laminated body 2 The mode of the flow direction opening of gas cuts forming.It therefore, there is no need to intersect from the direction that air flows, i.e. with refrigerant flow path Direction refrigerant flow path between recession plane portion 20 make thinner thickness.Therefore, forming protrusion 12b and cylindrical protrusion will be cut The mode of formation is swelled Deng like that compare, enable recession plane portion 20 between refrigerant flow path with do not need The size of thickness of making thinner correspondingly narrows.Can correspondingly make with the amount for making recession plane portion 20 narrow plate fin 2a width, In other words minimize heat exchanger.
Moreover, in the ora terminalis of the long side part of plate fin 2a, pass through the alternating dislocation configuration (ginseng of refrigerant flow path 11 According to Fig. 8) and form narrow plane 20a and wide cut plane 20b.It is formed in the wide cut side plane 20b and cuts forming protrusion 12a, cut The top surface of forming protrusion 12a is fixed in the narrow plane 20a of adjacent plate fin 2a.Accordingly it is also possible to not by narrow plane 20a The width of side is widened to form protrusion.That is, being dashed forward by being arranged to cut to shape in wide cut planar side using wide cut plane 20b Rise and the narrow plane 20a of the plate fin 2a adjacent with the protrusion abut it is affixed.It therefore, can not be by plate fin long side part The width of narrow planar side is widened and constant directly as narrow plane, and the miniaturization of heat exchanger can be promoted.
In addition, each plate fin 2a, end plate 3a, 3b soldered joint when, cut forming protrusion 12 each top surface be fixed in Adjacent plate fin 2a.Each plate fin 2a connection is integral as a result,.As a result, can be improved the rigid of plate fin laminated body 2 Property.
Especially in the present embodiment, it is partially constituted on the extended line of 11 groups of refrigerant flow path of connection flow path 10b non- Flow path portion 18 cuts forming protrusion 12b using a part of non-flow path portion 18 setting protrusion 12 (12a, 12aa, 12b), the i.e. the 2nd. It is certain thereby, it is possible to which distance maintaining reliably is laminated in the plate fin of 11 groups of parts of refrigerant flow path.Thereby, it is possible to make to freeze The air-flow of the air of 11 groups of parts of agent flow path is uniform and stable, to improve heat exchanger effectiveness.
In addition, plate fin laminated body 2 long leg set up separately set the 1st cut forming protrusion 12a make in intensity be easy change The intensity in the long side edge portion of weak plate fin laminated body 2 improves.Especially it is set to the two of the slit 15 of plate fin laminated body 2 Forming protrusion 12aa is cut in the 1st of side edge portions, makes by the way that the slit edge point that slit 15 is separated, intensity declines is arranged Intensity improve.It is thus possible to which enough realizing the deformation prevented near slit 5 while the raising of heat exchanger effectiveness.
It can also be narrow to cross in addition, shaping protrusion 12aa in the 1st incision that the both side edges part of above-mentioned slit 15 is arranged The mode of seam 15 is arranged one.In this case, there is the outlet side flow path portion 11a at 11 groups of refrigerant flow path and return road side Occur heat transfer between flow path portion 11b, the problem of the heat insulation decline of slit 15.But in the present embodiment, because The both side edges part of slit 15 has been provided separately protrusion 12aa, so the problem of heat transfer of such heat transfer occurs disappears. In addition, the 1st incision forming protrusion 12aa also can be set in the place for leaving slit.
In addition, the in the two side portions setting of the long side part and slit 15 of plate fin laminated body 2 the 1st cuts forming protrusion 12a, 12aa are set to the position for leaving the ora terminalis of plate fin long side of plate fin laminated body 2.Therefore, in plate fin laminated body 2 Plate fin 2a generate dew, the dew along plate fin 2a ora terminalis flow discharge when, utilize the 1st cut forming protrusion 12a, 12aa stop the water flow of dew, can prevent dew from cutting caused by the part accumulation of forming protrusion 12a, 12aa Various problems are in possible trouble.Therefore, it is capable of providing the heat exchanger of high reliablity.
In addition, also being set in the heat exchanger of present embodiment in the refrigerant flow path u turn side end of plate fin 2a It is equipped with incision forming protrusion 22 (22a, 22b).Therefore, it can be improved the u turn of the plate fin 2a of no refrigerant flow path 11 The heat exchange contribution degree of side end.Therefore, heat exchanger effectiveness can be improved in the flow passage region overall length of plate fin 2a, improves heat and hands over The thermal efficiency of parallel operation.
Especially in the u turn side end of plate fin 2a, there is positioning boss hole 13, positioning is used under boss hole 13 Swimming side becomes dead water region, so heat exchange contribution degree is extremely low.In the present embodiment, because in positioning under boss hole 13 Trip side is provided with multiple incision formings protrusion 22 (22a, 22b), so can be improved 13 downstream side universe of positioning boss hole Heat exchange contribution degree.
Positioning boss is shunk with the nearest incision forming protrusion 22a in the downstream side of boss hole 13 in addition, being set to positioning The fluid stream in the downstream side in hole 13.Therefore the stagnant water that the heat exchange contribution degree generated in positioning screw hole downstream side can be made low Region is minimum.As a result, heat exchanger effectiveness can be further increased.
Moreover, it is each cut forming protrusion 22 (22a, 22b) with flow passage region P setting protrusion 12 (12a, 12aa, Forming 12b) is equally cut, it is opposite with the 2nd fluid stream to cut forming ora terminalis Y.Thereby, it is possible to cut forming end edge portion point production Edge effect before death can correspondingly further increase heat exchanger effectiveness.
Moreover, becoming phase in multiple incisions forming protrusion 22 (22a, 22b) that the downstream side of positioning boss hole 13 is arranged For being staggered for the 2nd fluid stream serpentine arrangement.Thereby, it is possible to effectively play heat exchange function, heat exchange contribution is improved Degree.
Moreover, further, each cut is fixed in adjacent plate fin 2a at the top of forming protrusion 22 (22a, 22b).According to The structure, the short side part of plate fin 2a is linked with laminated arrangement fixes, so can be improved the rigidity of plate fin laminated body 2.
In addition, the incision forming protrusion 22 being arranged recently in the downstream side of positioning boss hole 13 in the present embodiment with Cross sectional shape as being open towards the 2nd fluid flow direction in Ha font (inverted v-shaped) cuts forming ground and is formed.It does not limit In this, cutting forming protrusion 22 can also form with shaping in incision generally L-shaped, which is shaped protrusion with a pair of pairs of Aspectant mode is arranged.As long as that is, becoming the shape for shrinking the fluid stream in the positioning downstream side of boss hole 13, so that it may be Arbitrary shape.
(embodiment 2)
As shown in Figure 22~Figure 25, the shape sum aggregate tube opening of the refrigerant flow path group of the heat exchanger of present embodiment It is different from the heat exchanger of embodiment 1 that position is set.To the part with function identical with the heat exchanger of embodiment 1 Identical appended drawing reference is marked, is illustrated centered on having different parts below.
Figure 22 is the perspective view for indicating to constitute an appearance of the plate fin laminated body of the heat exchanger of embodiment 2.Figure 23 be the top view for constituting the plate fin of the plate fin laminated body.Figure 24 is that the structure of the plate fin is amplified a part of carry out table The exploded perspective view shown.Figure 25 is the perspective view for indicating the refrigerant flow path group part truncation of the plate fin laminated body.
In Figure 22~Figure 25,11 groups of the refrigerant flow path for being set to plate fin 2a of the heat exchanger of present embodiment is straight It is linear.11 groups of refrigerant flow path of one end side is provided with the collection tube opening 8a of entrance side, is provided with out in the other end side The collection tube opening 8b of mouth side.Moreover, the collection tube opening 8a in entrance side is connected with entrance connecting tube 4, opened in the collector of outlet side Mouth 8b is connected with outlet connecting pipe 5, and refrigerant linearly flows out to the other end side from the one end side of plate fin 2a.
In addition, the collector flow path 10 formed around the collection tube opening 8a of entrance side is by the parameatal peripheral flow path of collector 10a, connection flow path 10b and multiple-limb flow path 10c are constituted.Flow path 10b is connected with the short side from peripheral flow path 10a along plate fin 2a After the mode that direction extends is formed, it is connected with multiple-limb flow path 10c.Outlet-side header flow path 14 also with the entrance side collector stream The identical mode in road 10 is constituted, and the two becomes symmetrical shape.
In addition, end plate 3a, 3b of 2 two sides of plate fin laminated body are connected without using stiffening plate 16a, 16b by linking part 9 Knot.Thus the dilatancy of the header areas corresponding part at the both ends end plate 3a, 3b is prevented.
The heat exchanger constituted like that above is in addition to enabling 11 groups of refrigerant flow path to be linear, the knot including detail section Structure, effect are identical as the heat exchanger illustrated in embodiment 1 inside, thus omit the description.
In addition, in the embodiment 1, in the incision forming protrusion 22 that the u turn side end of plate fin 2a is arranged at this It is suitably set in embodiment in the header areas of entrance side and outlet side.Such as in the collector stream for becoming dead water region The downstream side on road 10, which is formed, cuts forming protrusion 22.
(embodiment 3)
Present embodiment heat exchanger is adapted as the entrance and exit and 1 phase of embodiment of the refrigerant of heat exchanger The case where anti-evaporator uses.In the present embodiment, such as Figure 26~as shown in Figure 30, in the collector stream as outlet side Road 14 is provided with the flow-dividing control pipe 24 of refrigerant.
In addition, in the present embodiment the heat exchanger of the structure of embodiment 1 to be used as evaporator the case where For be illustrated.
Figure 26 is the perspective view for indicating the appearance of plate fin laminated body of the heat exchanger of embodiment 3.Figure 27 is to indicate From the plate fin laminated body remove flow-dividing control pipe after state perspective view.Figure 28 is the shunting for indicating the plate fin laminated body Control the perspective view of pipe insertion portion.Figure 29 is the perspective view of the flow-dividing control pipe.Figure 30 indicates the plate fin laminated body The skeleton diagram in the section of flow-dividing control tube portion.
In Figure 26~Figure 30, flow-dividing control pipe 24 is inserted into the collection for being set to the outlet side of the evaporation outlet as refrigerant In the collector flow path 14 of tube opening 8b, i.e. outlet side.The front end of flow-dividing control pipe 24 as shown in figure 30, extends to and does not set Set the end plate 3b of the side of collection tube opening.It is closed by the end plate 3b front end of flow-dividing control pipe 24.Moreover, flow-dividing control pipe 24 It is made of the pipe of the path compared with the internal diameter of collection tube opening 8b.It is formed between flow-dividing control pipe 24 and collection tube opening inner surface Gap 25 is used in refrigerant circulation.The length direction of flow-dividing control pipe 24, i.e. plate fin 2a stacking direction on substantially at equal intervals Ground is formed with multiple diffluence pass 26.
Multiple diffluence pass 26 with its aperture with the collection tube opening 8b in the direction flowed to refrigerant, i.e. outlet side it is close and The mode to become smaller is formed.
In addition, flow-dividing control pipe 24 such as Figure 27, be installed on stiffening plate 16a as shown in Figure 29.By the way that stiffening plate 16a is tight It is fixed in the end plate 3a of 2 two sides of plate fin laminated body and the insertion of flow-dividing control pipe 24 is set in collection tube opening 8b.Moreover, shunting Controlling pipe 24 has the 2nd of plate fin laminated body 2 the of (opposite side) farthest in the multiple plate fin laminated bodies 2 for reaching connection connection the The length of plate fin 7.
In the stiffening plate 16a for being equipped with flow-dividing control pipe 24, the face opposite with flow-dividing control pipe 24 be fixedly connected with into Mouth connecting tube 4.
In addition, being fixedly connected with outlet connecting pipe 5 in stiffening plate 16a.In addition, flow-dividing control pipe 24 can also be to close it The mode of front end is abutted with end plate 3b.
In the heat exchanger constituted above, from the collection tube opening 8a as entrance side through 11 groups of streams of refrigerant flow path To the collector flow path 14 as outlet side refrigerant gas as shown in the arrow of Figure 30, from refrigerant circulation gap 25 Multiple diffluence pass 26 (26a, 26b) through being formed in the tube wall of flow-dividing control pipe 24 are flowed into flow-dividing control pipe 24.Then, it makes Cryogen flows out to outlet connecting pipe 5 from the collection tube opening 8b of outlet side.
Herein, the diffluence pass 26 of flow-dividing control pipe 24 is set to its aperture as the collection tube opening 8b to outlet side is close And the mode to become smaller is formed.Therefore the refrigeration dose of each flow path at 11 groups of refrigerant flow path can be made uniform.
That is, making refrigerant and by 11 downsizing of refrigerant flow path in the heat exchanger of present embodiment Crushing compares collector flow path 14 big several times of the collector flow path 10 in outlet side of entrance side.On the other hand, the shunting of refrigerant by The larger impact of the distribution situation of crushing.Even if flow-dividing control pipe 24 is set to entering as common sense in the prior art as a result, The collector flow path 10 of mouth side, the crushing of the collector flow path 14 of outlet side is also up to several times than entrance side, so becoming in refrigerant Crushing of the refrigerant that flow path 11 flows dependent on the collector flow path 14 of outlet side.It is thus impossible to be shunted as design.
But in the heat exchanger of present embodiment, flow-dividing control pipe 24 is set to the collector of the high outlet side of crushing Flow path 14.The crushing for shunting the axis direction in the big influence of generation, outlet side collector flow path 14 is distributed as a result, equal It is even.Thereby, it is possible to keep the refrigerant shunt volume of each flow path at 11 groups of refrigerant flow path uniform.
In addition, the collector that the refrigerant that the slave entrance connecting tube 4 of the heat exchanger of present embodiment flows into passes through entrance side Be open 8a, is imported into the refrigerant flow path 11 of the inside of each plate fin, is flowed into the collection tube opening 8b of outlet side.Then, freeze Agent is flowed out from outlet connecting pipe 5.
At this point, due to the crushing generated in each flow path, with the refrigerant flow path 11 of the plate fin remote from entrance connecting tube 4 (in Figure 30 for closer to right side plate fin refrigerant flow path) compare, in the system of the plate fin close from entrance connecting tube 4 Refrigerant line 11 (in Figure 30 for closer to left side plate fin refrigerant flow path) be easier flowing refrigerant.In other words, A possibility that in the presence of unevenness is generated in the flow of refrigerant.
Then, in the present embodiment, flow-dividing control pipe 24 is inserted into inside the collection tube opening 8b of outlet side, makes to separate out The nearest diffluence pass 26a in mouthful side (in Figure 30 for closer to the part in left side) and the anti-outlet side of flow-dividing control pipe 24 (are being schemed In 30 for closer to right side part) diffluence pass compare more path.Thus make the refrigerant passed through from the diffluence pass of outlet side Crushing increase.As a result, the bias current of refrigerant flow can be prevented, make the 1st fluid flowing path 11 of the inside of each plate fin Refrigeration dose it is uniform, improve heat exchanger effectiveness.
As a result, the heat exchanger of present embodiment can be improved the heat exchange effect in 11 groups of parts of refrigerant flow path Rate provides the thermal efficiency higher heat exchanger.
Further, the homogenization structure that refrigerant shunts is only to punch the simple knot of diffluence pass 26 in flow-dividing control pipe 24 Structure, so heat exchanger can be provided inexpensively.
Moreover, flow-dividing control pipe 24 is integrally set to stiffening plate 16a.Therefore, installation stiffening plate 16a can only be passed through Just the insertion of flow-dividing control pipe 24 is set in outlet-side header flow path 14.As a result, can prevent additional by welding etc. Plate fin caused by the brazing filler metal melts of the inferior plate fin brazed of problems part of the case where installing flow-dividing control pipe 24 connects It is bad to close the qualities such as the refrigerant leakage of bad and adjoint generation, is capable of providing high-quality and efficient heat exchanger.
In addition, stiffening plate 16a is less than with its potential difference between flow-dividing control pipe 24 and outlet connecting pipe 5 will shunt control Tubulation 24 be directly connected to outlet connecting pipe 5 in the case where potential difference between the two material (stiffening plate 16a be it is stainless Steel, flow-dividing control pipe 24 are aluminium, and outlet connecting pipe 5 is copper) it is formed.Thereby, it is possible to prevent by flow-dividing control pipe 24 and outlet The generation for the different metal contact corrosion that connecting tube 5 generates in the case where being directly connected to.As a result, can greatly improve long-term The reliability used.Especially is utilizing copper pipe to constitute entrance connecting tube 4 and outlet connecting pipe 5 more, shunted using compositions such as aluminium In the air conditioner heat exchanger for controlling pipe 24, significant effect can be expected.
In addition, flow-dividing control pipe 24 is set to stiffening plate 16a in the present embodiment, but it's not limited to that.It shunts Control pipe 24 also can be set in the side end plate 3a, in addition, do not use stiffening plate 16a type in the case where, can also with End plate 3a opposite face setting flow-dividing control pipe 24 and outlet connecting pipe 5.
In addition, in the present embodiment, being not limited to 11 groups of refrigerant flow path has U-shaped.Also it can be used the 2nd 11 groups of the linear refrigerant flow path illustrated in embodiment.
(embodiment 4)
Embodiment 4 is the refrigeration system that the heat exchanger of each embodiment shown in use before is constituted.
In the present embodiment, air conditioner is illustrated as an example of refrigeration system.Figure 31 is conduct The refrigeration cycle diagram of the air conditioner.Figure 32 is the summary sectional view for indicating the indoor unit of the air conditioner.
In Figure 31, Tu32Zhong, which is made of outdoor unit 51 and the indoor unit connecting with outdoor unit 51 52. The four-way valve of refrigerant circuit when outdoor unit 51 is configured with compressor 53, the switching cooling supply warming operation for compressing refrigerant 54, the pressure reducer 56 for exchanging the outdoor heat exchanger 55 of the heat of refrigerant and outside air and refrigerant being depressurized.In addition, Indoors in machine 52, the indoor heat exchanger 57 and indoor fan 58 of the heat configured with exchange refrigerant and room air.Moreover, Compressor 53, four-way valve 54, indoor heat exchanger 57, pressure reducer 56 are connected with outdoor heat exchanger 55 by refrigerant circuit It ties and forms heat pump type refrigerating circulation.
In the refrigerant circuit of present embodiment, use is basic ingredient with tetrafluoropropene or trifluoro propene, by difluoro first Alkane or pentafluoroethane or tetrafluoroethane so that global warming potential be 5 or more, 750 modes below, preferably 350 hereinafter, Further preferably 150 modes below are mixed, and refrigerant obtained from 3 kinds of ingredients of 2 kinds of ingredients or mixing is mixed.
In air conditioner, four-way valve 54 is switched to discharge side and the outdoor of connection compressor 53 when for blowdown firing Heat exchanger 55.The refrigerant for becoming high temperature and pressure by the compressed refrigerant of compressor 53 as a result, is sent by four-way valve 54 To outdoor heat exchanger 55.Then, refrigerant carries out heat exchange with outside air and radiates, and becomes the liquid refrigerant of high pressure, It is sent to pressure reducer 56.It is depressurized and is become the two-phase system cryogen of low-temp low-pressure in pressure reducer 56, is sent to indoor unit 52.In room Interior machine 52, refrigerant enter the room heat exchanger 57, carry out heat exchange with room air and absorb heat, and evaporation gasifies and becomes low temperature Gas refrigerant.At this time room air it is cooled and to indoor carry out cooling supply.Further, refrigerant returns to outdoor unit 51, warp Compressor 53 is returned to by four-way valve 54.
When carrying out warming operation, four-way valve 54 is switched to the discharge side and indoor unit 52 of connection compressor 53.As a result, The refrigerant for becoming high temperature and pressure by the compressed refrigerant of compressor 53, is sent to indoor unit 52 by four-way valve 54.High temperature The refrigerant of high pressure enters the room heat exchanger 57, carries out heat exchange with room air and radiates, and is cooled and becomes high pressure Liquid refrigerant.At this point, room air is heated, heat to interior.Later, refrigerant is sent to pressure reducer 56, is subtracting Depressor 56 is depressurized and becomes the two-phase system cryogen of low-temp low-pressure.Then, refrigerant is sent to outdoor heat exchanger 55, with outside Air carries out heat exchange and evaporates gasification.Further, refrigerant returns to compressor 53 via four-way valve 54.
Refrigeration system configured as described uses above-mentioned each implementation in outdoor heat exchanger 55 or indoor heat exchanger 57 Heat exchanger shown in mode.Thus, it is possible to realize the high high-performance refrigeration system of energy saving.
Utilization possibility in industry
The present invention by diameter and the entrance of the collector flow path of setting plate fin laminated body, the diameter of outlet connecting pipe it is big It is small, even heat exchanger used in home-use and enterprise's air-conditioning etc. can also eliminate the expansion change in header areas part Shape provides small-sized and efficient heat exchanger and the high-performance refrigeration system high using its energy saving.Thereby, it is possible to be in Front yard with and enterprise's air conditioner etc. used in widely utilize in heat exchanger and various freezing equipments etc., the value of industry It is very big.
Description of symbols
1 heat exchanger
2 plate fin laminated bodies
2a plate fin
3a, 3b end plate
4 entrance connecting tubes (inlet header)
The 1st entrance connecting tube of 4a
The 2nd entrance connecting tube of 4b
5 outlet connecting pipes (outlet header)
The 1st outlet connecting pipe of 5a
The 2nd outlet connecting pipe of 5b
6 the 1st plate fins
The 1st plate-shaped member of 6a
The 2nd plate-shaped member of 6b
7 the 2nd plate fins
8,8a, 8b collection tube opening
9 linking parts (screw bolt and nut)
10 collector flow paths (entrance side collector flow path)
10a peripheral flow path
10b connection flow path
10c multiple-limb flow path
11 refrigerant flow paths (the 1st fluid flowing path)
The outlet 11a side flow path portion
The return road 11b side flow path portion
13 through holes (positioning boss hole)
The hole 13a peripheral part (positioning boss hole peripheral part)
14 collector flow paths (outlet-side header flow path)
15 slits
16a, 16b stiffening plate
17 shunt impact walls
18 non-flow path portions
19a, 19b flat end
20 recession plane portions
The narrow plane of 20a
20b wide cut plane
21 fin planar portions
22 (22a, 22b) protrusions (cut forming protrusion)
24 flow-dividing control pipes
Gap is used in the circulation of 25 refrigerants
26,26a, 26b diffluence pass
51 outdoor units
52 indoor units
53 compressors
54 four-way valves
55 outdoor heat exchangers
56 pressure reducers
57 indoor heat exchangers
58 indoor fans.

Claims (6)

1. a kind of heat exchanger characterized by comprising
The plate fin laminated body for being respectively provided with multiple plate fins for the flow path of the 1st fluid flowing and constituting is laminated；
It is respectively arranged at the 1st end plate and the 2nd end plate at the stacking direction both ends of the plate fin laminated body；
The 1st entrance connecting tube flowed into the 1st end plate connection, described 1st fluid；
With the 1st outlet connecting pipe of the 1st end plate connection, the described 1st fluid outflow；
With the 2nd end plate connection, and the 2nd entrance connecting tube being connected to the 1st entrance connecting tube；With
With the 2nd end plate connection, and the 2nd outlet connecting pipe being connected to the 1st outlet connecting pipe,
2nd fluid folds interflow in the plate fin of the plate fin laminated body, thus in the 1st fluid and the 2nd stream Heat exchange is carried out between body, wherein
The flow passage region of the multiple plate fin respectively included with multiple 1st fluid flowing paths for flowing the 1st fluid and Header areas with the collector flow path being connected to the multiple 1st fluid flowing path,
The collector flow path includes the entrance side collector flow path for being connected to the 1st entrance connecting tube and the 2nd entrance connecting tube With the outlet-side header flow path for being connected to the 1st outlet connecting pipe and the 2nd outlet connecting pipe,
1st fluid flowing path is made of the concave groove for being respectively arranged at the multiple plate fin,
The internal diameter of the entrance side collector flow path is less than the internal diameter of the 1st entrance connecting tube and the 2nd entrance connecting tube,
The internal diameter of the outlet-side header flow path is less than the internal diameter of the 1st outlet connecting pipe and the 2nd outlet connecting pipe.
2. heat exchanger as described in claim 1, it is characterised in that:
The internal diameter of the entrance side collector flow path is less than the outer of the 1st entrance connecting tube and the 2nd entrance connecting tube Diameter,
The internal diameter of the outlet-side header flow path is less than the 1st outlet connecting pipe and the 2nd outlet connecting pipe Outer diameter.
3. heat exchanger as claimed in claim 1 or 2, it is characterised in that:
The multiple 1st fluid flowing path is respectively formed as U-shaped,
The entrance side collector flow path and the outlet-side header flow arrangement in the respective one end side of the multiple plate fin,
The 1st entrance connecting tube and the 2nd entrance the connecting tube entrance opening and outlet with the entrance side collector flow path respectively Open communication,
1st outlet connecting pipe and the 2nd the outlet connecting pipe entrance opening and exit opening with the outlet-side header flow path respectively Connection.
4. the heat exchanger as described in any one of claims 1 to 3, it is characterised in that:
It is connected with the flow-dividing control pipe being inserted into the collector flow path in the entrance opening of the 1st end plate,
1st end plate is by making the potential difference between the flow-dividing control pipe and the 1st entrance connecting tube or described point Potential difference ratio between flow control tubulation and the 1st outlet connecting pipe is by the flow-dividing control pipe and the 1st entrance connecting tube The small material shape of potential difference when being directly connected to or being directly connected to the flow-dividing control pipe and the 1st outlet connecting pipe At.
5. the heat exchanger as described in any one of Claims 1 to 4, it is characterised in that:
Including multiple plate fin laminated bodies,
The plate fin laminated body is interconnected by the 2nd entrance connecting tube and the 2nd outlet connecting pipe.
6. a kind of refrigeration system, it is characterised in that:
Including heat exchanger described in any one of Claims 1 to 5.
CN201780047793.4A 2016-10-21 2017-10-13 Heat exchanger and refrigeration system using the same Active CN109564067B (en)

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MY195134A (en) 2023-01-11
CN109564067B (en) 2020-06-23

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