CN101865573B - Internal heat exchanger for transcritical CO2 refrigerating system and manufacturing method - Google Patents
Internal heat exchanger for transcritical CO2 refrigerating system and manufacturing method Download PDFInfo
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- CN101865573B CN101865573B CN2010102100665A CN201010210066A CN101865573B CN 101865573 B CN101865573 B CN 101865573B CN 2010102100665 A CN2010102100665 A CN 2010102100665A CN 201010210066 A CN201010210066 A CN 201010210066A CN 101865573 B CN101865573 B CN 101865573B
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- supercritical fluid
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Abstract
The invention relates to an internal heat exchanger used in a transcritical CO2 refrigerating heat pump system. After the internal heat exchanger is adopted in the transcritical CO2 refrigerating system, subcritical CO2 at the inlet of a compressor is further overheated and transcritical CO2 is overcooled before throttling so that the efficiency of refrigerating cycle and refrigerating output can be remarkably improved. A conventional internal heat exchanger has a series of disadvantages. The internal heat exchanger of the invention is characterized in that: a heat exchanging core is formed by laminating three or more parallel micro groove-shaped plates and provided with a subcritical fluid passage and a transcritical fluid passage which are not communicated with each other; the flow directions of subcritical fluid and transcritical fluid in the heat exchanging core are vertical or parallel to each other; brazing materials are arranged among the micro groove-shaped plates; the inlets and the outlets of the subcritical fluid passage and the transcritical fluid passage of the heat exchanging core are not on the same side face and coated with the brazing materials; and the brazing materials are inserted into long grooves milled on an inlet header and an outlet header respectively and fixed so as to perform integral vacuum brazing.
Description
Affiliated technical field
The present invention relates to a kind of critical CO that is used to stride
2The internal exchanger that uses in refrigeration, the heat pump.
Background technology
As far back as 1886, German engineer Windhausen designed CO
2Compressor makes CO
2Refrigeration system is applied.To the forties in last century, thought at that time that the CFCs class of safe cold-producing medium replaced.Delivered the important report that CFC class and HCFC class cold-producing medium can damage the ozone layer to U.S. scientist Molian in 1974 and Rowland.At present, the CFCs cold-producing medium is disabled, and the HCFCs cold-producing medium progressively is eliminated.Therefore, adopt new environment friendly refrigerating fluid imperative.In recent years, CO
2Cold-producing medium is owing to its unique environment-friendly advantage and good macroscopic property, and CO is generally tended to adopt in field of Refrigeration and Air-conditioning in countries in the world
2Deng natural environmental protection type working medium.CO
2Cold-producing medium is used for refrigeration system, has two problems, and the one, if adopt traditional steam compression cycle, then the efficient of system is lower; The 2nd, the operating pressure of system is higher, and the high-pressure side can surpass 1OMPa, makes heat transmission equipment and pipeline have safety problem.
First problem is at first striden critical CO by what preceding chairman professor Lorentzen of International Institute or Refrigeration proposed
2Kind of refrigeration cycle is resolved.CO
2The low critical-temperature of cold-producing medium and high critical pressure use the biggest problem of bringing for it on refrigeration unit, the operating pressure that is refrigeration system will be higher than traditional refrigerated air-conditioning system, therefore, the development energy is high pressure resistant, two devices (condenser and evaporimeter) of high performance-price ratio, is a urgent task.
As everyone knows, the diameter of pipe is more little, and its bearing capacity is big more.So the design of Thermal Performance of Micro Channels element is arisen at the historic moment.The definite definition of micro-channel heat exchanger, relatively more current, classification intuitively is to be divided by the size by its water equivalent diameter that Mehendale.s.s proposes.Usually contain the water equivalent diameter is called micro-channel heat exchanger less than the 1mm heat exchanger.The application of micro-channel heat exchanger in air-conditioning has the following advantages: 1. bearing capacity height; 2. heat transfer efficiency height; 3. improve the EER and the SEER of air-conditioner; 4. dwindle the volume of air-conditioner, alleviate the quality of air-conditioner; 5. reduce the charging amount of cold-producing medium; 6. micro-channel heat exchanger
Efficient height, performance are better than conventional heat exchanger.
Striding critical CO
2In the internal exchanger in the refrigeration system, a side of heat exchanger is that pressure reaches the above supercritical CO of 10MPa
2Liquid, opposite side are the subcritical CO about pressure 4MPa
2Superheated steam.Stride critical CO
2After refrigeration system adopts internal exchanger, make the subcritical CO of compressor inlet
2Further overheated, supercritical CO before the throttling
2Cross coldly, thereby can improve the efficient and the refrigerating capacity of kind of refrigeration cycle significantly.
The existing production technology of internal exchanger has bushing type and squash type.At present, domestic some that finish are striden critical CO
2Refrigeration, heat pump all adopt bushing type.The heat-transfer area density of telescopic overcritical side and subcritical side can reach 667 and 969 respectively, and its compactedness height, but the heat transfer coefficient of both sides is not high because of strengthening in addition because sleeve type structure is too elongated, is furnished with limitation on automobile.The microchannel tubular type structure that extrusion is produced, its compactedness height, heat transfer coefficient is also big, but technology is loaded down with trivial details, complex structure, the production difficulty is big, domesticly still can not produce in batches.Have only Han Jitian etc. to carry out prototype test.
Chinese patent 200510011254.5 discloses and " has been used to stride critical CO
2The microchannel plate-fin internal exchanger of kind of refrigeration cycle ".It is characterized in that the heat exchange core adopts multilayer grooved drum plate bundle structure, the interlayer dividing plate is arranged between every layer of grooved drum plate, one deck supercritical fluid grooved drum plate mates two-layer subcritical fluids grooved drum plate, and two groups of (four) transition end sockets of supercritical fluid and sub-critical flow body and function are with the flow direction of two kinds of fluids of standard.The little dried 3mm of the water equivalent diameter of described groove.
The advantage of Chinese patent 200510011254.5 is to adopt plate-fin structure, has overcome the shortcoming of extrusion, it is said that the heat transfer coefficient in the fluid passage of this invention is more than 2 times of sleeve type structure.But, also there is following shortcoming in it: the import and export of supercritical fluid and subcritical fluids microchannel are in the same side, guarantee not leak between two kinds of fluids, must adopt baroque two groups (four) transition end sockets, and multilayer grooved drum plate bundle also will adopt artificial argon arc welding with four end sockets after soldering; The grooved drum plate interfascicular need be provided with the interlayer dividing plate; Complex structure, manufacturing process be many, be difficult to mechanization, cost height.
Han Jitian etc. carried out prototype test, had adopted the microchannel tubular type CO of Boewe etc.
2The version of internal exchanger is [referring to Han Jitian; Cao Xianqi " carbon dioxide (CO
2) design of refrigeration system internal exchanger " the Shandong refrigeration can best paper selected works in 2008,2008].Described model machine adopts three row's structures, and the centre connects with bend pipe.The appearance and size of internal exchanger is 400x44x30.5mm.Equally also be because the import and export of supercritical fluid and subcritical fluids microchannel in the same side, be guaranteed not leak between two kinds of fluids, must adopt baroque one-sided opening catch box and bilateral opening catch box, also need to connect between three row's heat exchange cores with bend pipe.Complex structure, manufacturing process be many, be difficult to mechanization, cost height.
Summary of the invention
For overcoming the above-mentioned shortcoming of existing internal exchanger, the invention provides a kind of critical CO that is used to stride
2The internal exchanger of refrigeration system and manufacture method.It is by the heat exchange core with subcritical fluids passage and supercritical fluid passage, the subcritical fluids collector, and the supercritical fluid collector is formed.It is characterized in that: described heat exchange core is superimposed with the parallel microchannels template of having of three or more, constitute subcritical fluids passage and the not connected two passes of supercritical fluid passage, the subcritical fluids in the described heat exchange core and the flow direction of supercritical fluid have vertical mutually and are parallel to each other two kinds, between described microchannels template, be laid with cored solder, the subcritical fluids passage of described heat exchange core and the import and export of supercritical fluid passage are not in the same side, superscribe cored solder on the import and export with described subcritical fluids passage and supercritical fluid passage, insert respectively and import and export in the elongated slot that mills out on the collector, after fixing, carry out the overall vacuum soldering.Below in conjunction with accompanying drawing, the invention will be further described.
Description of drawings
Fig. 1 is the stereogram of the internal exchanger heat exchange element of supercritical fluid and the mutual perpendicular flow of subcritical fluids.Fig. 2 be the A of Fig. 1 to view, Fig. 3 be the B of Fig. 1 to view, Fig. 4 is the general assembly drawing of this internal exchanger.Fig. 5 is the vertical view of heat exchange core 1, and Fig. 6 is the front view of Fig. 5, and Fig. 7 is the A-A cutaway view of Fig. 5.Fig. 8 is the vertical view that single face has parallel microchannels template (I type), and Fig. 9 is the front elevation of Fig. 8, and Figure 10 is the A-A cutaway view of Fig. 8, and Figure 11 is the A portion enlarged drawing of Figure 10.Figure 12 is two-sided vertical view with parallel microchannels template (II type), and Figure 13 is the front elevation of Figure 12, and Figure 14 is the A-A cutaway view of Figure 12, and Figure 15 is the B portion enlarged drawing of Figure 14.Figure 16 is the vertical view that supercritical fluid and subcritical fluids are parallel to each other the internal exchanger general assembly mobile.Figure 17 is the front view of Figure 16.Among the figure: 1 heat exchange core, 2 subcritical fluids passages, 3 supercritical fluid passages, 4 subcritical fluids collectors, 5 supercritical fluid collectors, 6 (I type groove template) single face has parallel microchannels template, 7 (II type groove templates) are two-sided to have parallel microchannels template, L heat exchange core is long, and B heat exchange core is wide, and b heat exchange core is thick.
The specific embodiment
Fig. 1 is the stereogram of the internal exchanger heat exchange element of supercritical fluid and the mutual perpendicular flow of subcritical fluids.Fig. 2 be the A of Fig. 1 to view, Fig. 3 is that the B of Fig. 1 is to view.As seen from the figure, heat exchange core 1 outward appearance is a square, the centre of heat exchange core 1 is the parallel supercritical fluid passage 3 of a row, two rows then are that subcritical fluids passage 2, two runners are vertical mutually, and the cross sectional shape of two fluid passages has circle, rectangle and polygon, the water equivalent diameter of overcritical runner is less, the water equivalent slightly larger in diameter of subcritical runner, they be by two models totally four have parallel microchannels template and be superimposed with each other and constitute, between each piece groove template, be laid with cored solder.The groove forming technology of described groove template can be that machine adds, rolling or hydraulic pressure.The material of described groove template can be an aluminium, copper, stainless steel or other metal material.The orthogonal advantage of two runners is that the microchannels template can adopt the high rolling of production efficiency to be shaped, and its shortcoming is that two fluids are the cross-flow heat exchange.
Fig. 4 is the general assembly drawing of square internal exchanger.On subcritical fluids collector 4 and supercritical fluid collector 5, mill on demand the elongated slot that pine is joined, four sides of heat exchange core 1 are superscribed cored solder after, be inserted into respectively in the elongated slot of described subcritical fluids collector 4 and supercritical fluid collector 5, and make it fixing, it is integral braze-welded to go into vacuum drying oven.Like this, all are laid and are enclosed with the commissure of cored solder and realize seam, make heat exchanger become a firm integral body.
Fig. 5 is the vertical view of heat exchange core 1, and Fig. 6 is the front view of Fig. 5, and Fig. 7 is the A-A cutaway view of Fig. 5.As seen from the figure, heat exchange core 1 is a hexagon, the centre of heat exchange core 1 is the parallel supercritical fluid passage 3 of a row, and two rows then are that subcritical fluids passage 2, two runners are parallel to each other, subcritical cold-producing medium enters into two rows subcritical fluids passage 2 from upper right side, after bending, flow from right to left, discharge from the side, lower-left at last, a row supercritical fluid passage 3 in the middle of supercritical refrigerant enters into from upper left side, after bending, flow from left to right, discharge from lower right sides at last.Fig. 8-Figure 15 has then provided the structure of groove template of two kinds of models and the details of stack thereof.The advantage that two runners are parallel to each other is that two fluids are contrary, and its shortcoming is that the microchannels template can not adopt the high rolling of production efficiency to be shaped.
Fig. 8 is the vertical view that single face has parallel microchannels template (I type), and Fig. 9 is the front elevation of Fig. 8, and Figure 10 is the A-A cutaway view of Fig. 8.Figure 11 is the A portion enlarged drawing of Figure 10.
On a hexagon metallic plate, the employing machine adds or the hydroforming processing technology, single-sided process at metallic plate becomes to have parallel microchannels template 6 (I type groove template), this groove is S-shaped, import is in the hexagonal upper right corner, and outlet is in the hexagonal lower left corner, and the groove shown in the figure is semicircle, with (II type groove template) 7 superimposed after, just become the subcritical refrigerant flow path of a circular cross-section.Described groove also can rectangular or multiaspect shape.The material of described groove template can be an aluminium, copper, stainless steel or other metal material.
Figure 12 is two-sided vertical view with parallel microchannels template (II type), and Figure 13 is the front elevation of Figure 12, and Figure 14 is the A-A cutaway view of Figure 12, and Figure 15 is the B portion enlarged drawing of Figure 14.
On a hexagon metallic plate, the employing machine adds or the hydroforming processing technology, two-sided being processed at metallic plate has parallel microchannels template 7 on (II type groove template), it has two micro-channel parallel flow grooves, top is subcritical fluids passage 2 (representing with solid line among Figure 12), and the bottom is supercritical fluid passage 3 (dotting among Figure 12).Two grooves are all S-shaped.Subcritical refrigerant inlet is in the hexagonal upper right corner, and outlet is in the hexagonal lower left corner, and the supercritical refrigerant import is in the hexagonal upper left corner, and outlet is in the hexagonal lower right corner.Groove shown in the figure is semicircle, with (I type groove template) 6 and second (II type groove template) 7 superimposed after, just become the supercritical refrigerant runner of subcritical refrigerant flow path and row's circular cross-section of row's circular cross-section.Described groove also can rectangular or multiaspect shape.The material of described groove template can be an aluminium, copper, stainless steel or other metal material.
Figure 16 is the vertical view that supercritical fluid and subcritical fluids are parallel to each other the internal exchanger general assembly mobile.Figure 17 is the front view of Figure 16.On subcritical fluids collector 4 and supercritical fluid collector 5, mill on demand the elongated slot that pine is joined, the side that four cold-producing mediums of heat exchange core 1 are imported and exported, after superscribing cored solder, be inserted into respectively in the elongated slot of described subcritical fluids collector 4 and supercritical fluid collector 5, and make it fixing, it is integral braze-welded to go into vacuum drying oven.Like this, all are laid and are enclosed with the commissure of cored solder and realize seam, make heat exchanger become a firm integral body.
Beneficial effect
1. it is loaded down with trivial details to have overcome extrusion technology, complex structure, and production difficulty is big, production cost height, the shortcoming that the length L of heat exchange core and width B are limited; 2. overcome extrusion and can only use the limitation of aluminium, can use copper, stainless steel or other metal material, enlarged the space of selection; 3. the import and export of subcritical fluids and supercritical fluid in the prior art have been changed in the version of same end face, original version makes between subcritical fluids and supercritical fluid and leaks easily, be Leakage prevention, have to adopt very complicated four the transition end sockets (Chinese patent 200510011254.5) of structure, with two one-sided opening catch boxs, two bilateral opening catch boxs, and two bridge pieces are (referring to Han Jitian; Cao Xianqi " carbon dioxide (CO2) design of cooling system internal exchanger "). Beneficial effect is: that has stopped to leak between two fluids may simplify connection form with collector, has reduced manufacturing process, reduces significantly manufacturing cost.
Claims (6)
1. one kind is used to stride critical CO
2The internal exchanger of refrigeration system, be by heat exchange core (1) with subcritical fluids passage (2) and supercritical fluid passage (3), the subcritical fluids inlet header, the subcritical fluids outlet header, supercritical fluid inlet header and supercritical fluid outlet header are formed, described heat exchange core (1) is formed by stacking by the parallel microchannels template of having of three or more, it is characterized in that, advance in described subcritical fluids, outlet header and described supercritical fluid advance, be milled with the elongated slot that pine is joined on the outlet header, after four cold-producing mediums of described heat exchange core (1) are imported and exported sides and superscribe cored solder, being inserted into described subcritical fluids respectively advances, outlet header and described supercritical fluid advance, in the elongated slot of outlet header, and make it fixing, it is integral braze-welded to go into vacuum drying oven, like this, all are laid and are enclosed with the commissure of cored solder and realize seam, make described internal exchanger become a firm integral body.
2. one kind as claimed in claim 1ly is used to stride critical CO
2The internal exchanger of refrigeration system is characterized in that, the subcritical fluids in the described heat exchange core (1) and the flow direction of supercritical fluid are mutually vertical or be parallel to each other, and is laid with cored solder between described microchannels template.
3. one kind as claimed in claim 1ly is used to stride critical CO
2The internal exchanger of refrigeration system is characterized in that, the import and export of the subcritical fluids passage (2) of described heat exchange core (1) and the import and export of supercritical fluid passage (3) are not in the same side of described heat exchange core (1).
4. one kind as claimed in claim 1ly is used to stride critical CO
2The internal exchanger of refrigeration system is characterized in that, the water equivalent diameter of the subcritical fluids passage (2) of described heat exchange core (1) is greater than the water equivalent diameter of supercritical fluid passage (3), and the cross sectional shape of two runners is circle or polygon.
5. one kind as claimed in claim 4ly is used to stride critical CO
2The internal exchanger of refrigeration system is characterized in that, described polygon is a rectangle.
6. one kind as claimed in claim 1ly is used to stride critical CO
2The internal exchanger of refrigeration system, it is characterized in that, described groove template be shaped as square or hexagon, described groove template has two kinds on the fluted I type of single face and two-sided fluted II type, the forming technology of described groove template is machined, rolling or shaped by fluid pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102100665A CN101865573B (en) | 2010-06-28 | 2010-06-28 | Internal heat exchanger for transcritical CO2 refrigerating system and manufacturing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102100665A CN101865573B (en) | 2010-06-28 | 2010-06-28 | Internal heat exchanger for transcritical CO2 refrigerating system and manufacturing method |
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| Publication Number | Publication Date |
|---|---|
| CN101865573A CN101865573A (en) | 2010-10-20 |
| CN101865573B true CN101865573B (en) | 2011-09-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010102100665A Expired - Fee Related CN101865573B (en) | 2010-06-28 | 2010-06-28 | Internal heat exchanger for transcritical CO2 refrigerating system and manufacturing method |
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| CN110849200B (en) * | 2019-11-29 | 2022-03-15 | 四川大学 | Supercritical C02Flow guiding structure of pipeline type heat exchanger |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1645027A (en) * | 2005-01-26 | 2005-07-27 | 清华大学 | Microchannel slab internal heat exchanger of overcritical Co2 refrigerating circulation |
| CN201355213Y (en) * | 2009-01-21 | 2009-12-02 | 洛阳隆华制冷设备有限公司 | Detachable all-welded plate heat exchanger |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6892803B2 (en) * | 2002-11-19 | 2005-05-17 | Modine Manufacturing Company | High pressure heat exchanger |
| JP2007333353A (en) * | 2006-06-19 | 2007-12-27 | Univ Of Tsukuba | Micro-channel integrated type laminated structure heat exchanger for super critical refrigerant |
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2010
- 2010-06-28 CN CN2010102100665A patent/CN101865573B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1645027A (en) * | 2005-01-26 | 2005-07-27 | 清华大学 | Microchannel slab internal heat exchanger of overcritical Co2 refrigerating circulation |
| CN201355213Y (en) * | 2009-01-21 | 2009-12-02 | 洛阳隆华制冷设备有限公司 | Detachable all-welded plate heat exchanger |
Non-Patent Citations (2)
| Title |
|---|
| JP特开2007-333353A 2007.12.27 |
| 邓建强，姜培学，李建明.跨临界CO_2制冷系统中换热器结构的进展.《流体机械》.2005,第33卷(第12期),57-60，68. * |
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| CN101865573A (en) | 2010-10-20 |
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