CN108716791B - Double pipe type heat exchanger with two working states for automobile - Google Patents
Double pipe type heat exchanger with two working states for automobile Download PDFInfo
- Publication number
- CN108716791B CN108716791B CN201810749600.6A CN201810749600A CN108716791B CN 108716791 B CN108716791 B CN 108716791B CN 201810749600 A CN201810749600 A CN 201810749600A CN 108716791 B CN108716791 B CN 108716791B
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- Prior art keywords
- gaseous refrigerant
- wall surface
- valve body
- discharge pipe
- heat exchanger
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Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 154
- 239000007788 liquid Substances 0.000 claims abstract description 46
- 210000005239 tubule Anatomy 0.000 claims abstract description 36
- 230000008602 contraction Effects 0.000 claims description 3
- 238000004781 supercooling Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 244000025254 Cannabis sativa Species 0.000 description 1
- 235000012766 Cannabis sativa ssp. sativa var. sativa Nutrition 0.000 description 1
- 235000012765 Cannabis sativa ssp. sativa var. spontanea Nutrition 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 235000009120 camo Nutrition 0.000 description 1
- 235000005607 chanvre indien Nutrition 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000011487 hemp Substances 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/04—Desuperheaters
-
- 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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a double-pipe heat exchanger for an automobile, which has two working states, wherein one end of a shell is provided with a liquid refrigerant inlet and a first gaseous refrigerant outlet, the other end of the shell is provided with a liquid refrigerant outlet and a second gaseous refrigerant outlet, and the outer wall of the shell is provided with a gaseous refrigerant inlet; a center tubule provided inside the housing, and having a plurality of annular openings provided at one end thereof; a spiral tube group wound outside the central tubule, a first gaseous refrigerant discharge tube having one end connected to the first gaseous refrigerant outlet; a second gaseous refrigerant discharge pipe having one end communicating with the second gaseous refrigerant outlet; a gas collecting chamber disposed between the first gaseous refrigerant discharge pipe and the second gaseous refrigerant discharge pipe; wherein, set up first valve body on first gaseous refrigerant discharge pipe, set up the second valve body on the second gaseous refrigerant discharge pipe. Different working states are realized by controlling the opening and closing of the valve body.
Description
Technical Field
The invention relates to the technical field of heat exchangers, in particular to an automobile double pipe heat exchanger with two working states.
Background
A double pipe heat exchanger is a type of heat exchanger that is used to improve system performance. The gas and liquid refrigerants can flow in the heat exchanger at the same time, and the heat exchanger can exchange heat to improve the supercooling degree and the superheating degree, so that the performance of the system is improved. The device is a component with low cost, simple structure and excellent effect for improving the system performance.
The double-pipe heat exchanger can be placed in an automobile air conditioning system to play a role in improving the supercooling degree of liquid refrigerant and the superheat degree of gas refrigerant at the outlet of the condenser, so that the double-pipe heat exchanger has great application in the automobile industry.
Most of the existing sleeve type heat exchangers are in a concentric sleeve type, an inner tube in the concentric sleeve is used as a heat transfer element, two kinds of tubes with different diameters are sleeved together to form the concentric sleeve, and each section of sleeve is a 'one-pass'. Heat is transferred from one fluid to another through the inner tube wall. The existing double-pipe heat exchanger is simple in structure, and the length of each heat transfer pipe is limited, so that the heat dissipation capacity is limited, and the heat exchange efficiency is affected. In addition, most of the existing double pipe heat exchangers only have one working mode, and the heat exchange effect is poor.
Disclosure of Invention
The invention designs and develops a double pipe heat exchanger for an automobile with two working states, and the heat exchanger has working states with different supercooling degrees and superheating degrees by controlling the opening and closing of a valve body.
Another object of the invention: by increasing the length of each heat transfer tube, the heat exchange area is increased, and the heat exchange efficiency is improved.
Another object of the invention: the flow of the gaseous refrigerant is controlled, so that the heat exchange effect is better.
The technical scheme provided by the invention is as follows:
a double pipe heat exchanger for an automobile having two operating states, comprising:
the shell is internally provided with a cavity, one end of the shell is provided with a liquid refrigerant inlet and a first gaseous refrigerant outlet, the other end of the shell is provided with a liquid refrigerant outlet and a second gaseous refrigerant outlet, and the outer wall of the shell is provided with a gaseous refrigerant inlet;
a center tubule provided inside the housing, and provided with a plurality of annular openings along a circumference at one end thereof;
the spiral tube group is wound outside the central thin tube, one end of the spiral tube group is communicated with the liquid refrigerant inlet, and the other end of the spiral tube group is communicated with the liquid refrigerant outlet;
a first gaseous refrigerant discharge pipe having one end communicating with the first gaseous refrigerant outlet;
a second gaseous refrigerant discharge pipe having one end communicating with the second gaseous refrigerant outlet;
the gas collecting cavity is arranged between the first gaseous refrigerant discharge pipe and the second gaseous refrigerant discharge pipe and is provided with a gaseous refrigerant total outlet;
wherein, a first valve body is arranged on the first gaseous refrigerant discharge pipe, and a second valve body is arranged on the second gaseous refrigerant discharge pipe; when the first valve body is opened and the second valve body is closed, gaseous refrigerant is discharged from the first gaseous refrigerant; when the first valve body is closed and the second valve body is opened, the gaseous refrigerant is discharged from the second gaseous refrigerant discharge pipe through the center tubule.
Preferably, the method further comprises:
a first wall surface sleeved outside the central thin tube and arranged at one end of the central thin tube, wherein the first wall surface is abutted against the inner wall of the shell;
the second wall surface is arranged in parallel with the first wall surface, sleeved outside the central thin tube and arranged at the other end of the central thin tube, and is abutted against the inner wall of the shell;
the first cavity is formed between the first wall surface and the inner wall surface at one end of the shell, the second cavity is formed between the first wall surface and the second wall surface, and the third cavity is formed between the second wall surface and the inner wall surface at the other end of the shell.
Preferably, one end of the spiral tube group passes through the first wall surface to be communicated with the first cavity, and the other end passes through the second wall surface to be communicated with the third cavity; and
the liquid refrigerant inlet communicates with the first cavity and the liquid refrigerant outlet communicates with the third cavity.
Preferably, the coil group includes:
a first coil group including at least two first coils arranged side by side;
the second spiral pipe group is arranged opposite to the first spiral pipe group and comprises at least two second spiral pipes arranged side by side.
Preferably, the liquid refrigerant inlet includes a first liquid refrigerant inlet and a second liquid refrigerant inlet symmetrically disposed thereto.
Preferably, the plurality of annular openings are equally spaced on the central tubule.
Preferably, the first valve body and the second valve body are solenoid valves.
Preferably, after the gaseous refrigerant enters the annular opening, the empirical formula of the flow Q satisfies:
wherein pi is the circumference ratio, r is the radius of the discharge pipe, s is the number of annular openings, A is the cross-sectional area of the annular openings, L is the distance of flow of the gaseous refrigerant, e is the natural logarithmic base, I W For steady state current of working valve body, I 0 Initial current, k of working valve body 1 For correction factor, lambda is the coefficient of contraction, c is the compensation maturity, P 0 Is the initial pressure of the gaseous refrigerant, P 1 Is the pressure of the gaseous refrigerant after it has entered the annular opening.
The beneficial effects of the invention are as follows: the invention comprises two liquid refrigerant inlets, which can lead the flow distribution of the liquid refrigerant to be more uniform. The tubes for circulating the liquid refrigerant are arranged like a hemp pattern, and each part of spiral tube comprises two spiral tubes side by side, so that the space utilization rate of the double-tube heat exchanger is greatly improved, the heat exchange area of the gas-liquid two-phase refrigerant is effectively increased, and the heat exchange efficiency is greatly improved. The invention has two gaseous refrigerant outlets, and two pipelines with outlets connected to the cavity are respectively provided with an electromagnetic stop valve. By controlling the on-off state of the electromagnetic stop valve, the gaseous refrigerant can only flow through one branch. By means of the mode that whether the gaseous refrigerant flows through the central tubule or not, the double-pipe heat exchanger has the working states with different supercooling degrees and superheating degrees. The heat exchanger has better heat exchange effect and higher heat exchange efficiency by controlling the flow of the gaseous refrigerant.
Drawings
FIG. 1 is a schematic view of the overall structure of a double pipe heat exchanger according to the present invention
Fig. 2 is a left side view of the double pipe heat exchanger according to the present invention.
FIG. 3 is a schematic view of a coil assembly according to the present invention
Fig. 4 is a schematic structural view of the central tubule according to the present invention.
Fig. 5 is a schematic view of an open pore structure on a central tubule according to the present invention.
Detailed Description
The present invention is described in further detail below with reference to the drawings to enable those skilled in the art to practice the invention by referring to the description.
As shown in fig. 1 to 5, the present invention provides a double pipe heat exchanger for an automobile having two working states, comprising a housing 100 having a cavity therein, in which a center tubule 110 is provided, one end of which is connected to an inner wall surface of one end of the housing 100, and the other end of which is connected to an inner wall surface of the other end of the housing 100; a first liquid refrigerant inlet 152 and a second liquid refrigerant inlet 151 are provided at one end of the outer wall of one end of the casing 100, a first gaseous refrigerant outlet 160 is provided at the central position of the outer wall of one end of the casing 100, a second gaseous refrigerant outlet 170 is provided at the central position of the other end of the casing, and a liquid refrigerant outlet 153 is also provided at the outer wall of the other end of the casing 100.
The gaseous refrigerant inlet 180 is provided at a lower portion of one side of the housing, wherein the first gaseous refrigerant outlet 160 is communicated with the first gaseous refrigerant discharge pipe 220, and a first valve body 210 is provided thereon, the second gaseous refrigerant outlet 170 is communicated with the second gaseous refrigerant discharge pipe 240, and the first gaseous refrigerant discharge pipe 220 and the second gaseous refrigerant discharge pipe 240 are communicated through the gas collecting chamber 231. Wherein, on the central tubule 110, a plurality of annular openings 111 are opened, and when the first valve body 210 is opened and the second valve body 230 is closed, the gaseous refrigerant is discharged from the first gaseous refrigerant discharge pipe 220; when the first valve body 210 is closed and the second valve body 230 is opened, the gaseous refrigerant is discharged from the second gaseous refrigerant discharge pipe 240 through the center tubule 110, thereby affecting the supercooling degree and the superheating degree of the refrigerant, and allowing the heat exchanger to have two different operating states.
Inside the casing 100, the center tubule 110 is outside, is close to one end of the center tubule 110, and is sleeved with a first wall surface 130, which is abutted against the inner wall surface of the casing 100, and a second wall surface 140 is parallel to the first wall surface 130, is sleeved outside the center tubule 110, and is abutted against the inner wall surface of the casing 100, and is close to the other end of the center tubule 110, and the first wall surface 130 and the second wall surface 140 divide the inside of the casing 100 into three cavities, namely: a first cavity is formed between one end wall surface of the housing and the first wall surface 130, a second cavity is formed between the first wall surface 130 and the second wall surface 140, and a third cavity is formed between the second wall surface 140 and the other end inner wall surface of the housing 100.
In the second chamber, a coil tube group 120 is further wound around the outside of the center tubule 110, and one end of the coil tube group 120 passes through the first wall 130 to communicate with the first chamber, and the other end passes through the second wall 140 to communicate with the third chamber.
The coil group 120 includes a first coil group and a second coil group disposed opposite thereto, wherein the two coil groups are disposed centering around the central tubule 110 in a central symmetry manner, and each coil group includes at least two coils, so that the liquid refrigerant can be distributed more uniformly in the flowing process.
In the present invention, preferably, each coil group includes two coils disposed side by side.
The first liquid refrigerant inlet 152 is communicated with the first cavity, the second liquid refrigerant inlet 151 is arranged at one side of the first liquid refrigerant inlet 152, is symmetrically arranged with the first liquid refrigerant inlet 152 and is communicated with the first cavity 110; the first liquid refrigerant outlet 153 is provided on the other end outer wall surface of the housing 100 below the second gaseous refrigerant outlet 170, and communicates with the third chamber.
The gaseous refrigerant inlet 180 is disposed at a lower portion of the outer wall surface 100 of the housing, and is disposed at a lower portion of the second chamber near the second wall surface 18, and communicates with the second chamber. The first gaseous refrigerant outlet 160 is provided on an outer wall surface of one end of the housing 100, one end of which communicates with one end of the center tubule 110, and the other end of which communicates with the first gaseous refrigerant discharge pipe 220, and the second gaseous refrigerant outlet 170 is provided on an outer wall surface of the other end of the housing, one end of which communicates with the other end of the center tubule 110, and the other end of which communicates with the second gaseous refrigerant discharge pipe 250. The first gaseous refrigerant discharge pipe 220 and the second gaseous refrigerant discharge pipe 250 are connected through the gas collecting chamber 230, one end of the gas collecting chamber 230 is communicated with the other end of the first gaseous refrigerant discharge pipe 220, the other end of the gas collecting chamber 230 is communicated with the other end of the second gaseous refrigerant discharge pipe 230, and a gaseous refrigerant total outlet 231 is further arranged at the lower part of the gas collecting chamber. A first valve body is disposed on the first gaseous refrigerant discharge pipe 220, a second valve body is disposed on the second gaseous refrigerant discharge pipe 250, a plurality of annular openings 111 are formed on one side of the center tubule 110 near the first wall surface 130, and the plurality of annular openings 111 are arranged on the outer circumference of the center tubule 110 at equal intervals.
In the present invention, it is preferable that the plurality of annular openings 111 are arrayed at an angle of 45 ° on the center tubule 110.
In the present invention, the number of the plurality of annular openings 111 is preferably eight.
In the present invention, preferably, the first valve body and the second valve body are the same valve body, and electromagnetic valves are selected.
In operation, liquid refrigerant enters the double pipe heat exchanger through the first liquid refrigerant inlet 152 and the second liquid refrigerant inlet 151 and enters the spiral pipe stack 120 through the first cavity, and gaseous refrigerant enters the double pipe heat exchanger through the gaseous refrigerant inlet 180 and flows in the second cavity and exchanges heat with the liquid refrigerant in the spiral pipe stack 120 to increase the superheat degree. The gaseous refrigerant can enter the central tubule 110 through the annular opening 111.
The gaseous refrigerant introduced into the center tubule 110 may select different flow paths by controlling the first valve body 210 and the second valve body 240. When the first valve body 210 is opened and the second valve body 240 is closed, the gaseous refrigerant flows out of the casing of the double pipe heat exchanger through the first gaseous refrigerant outlet 160, and at this time, the part of the gaseous refrigerant does not flow through the part of the central tubule 110 located in the double pipe heat exchanger, so that the degree of superheat of the gaseous refrigerant and the degree of supercooling of the liquid refrigerant which can be generated by the double pipe heat exchanger at this time are low. When the second valve body 240 is opened and the first valve body 210 is closed, the gaseous refrigerant flows out of the double pipe heat exchanger housing through the second gaseous refrigerant outlet 170, and during this process, the part of the gaseous refrigerant needs to flow through the center tubule 110 and exchange heat with the gaseous refrigerant in the coil group 120, further increasing the degree of superheat and also increasing the degree of supercooling of the liquid refrigerant.
After the gaseous refrigerant enters the annular opening, the empirical formula of the flow rate Q satisfies:
wherein pi is the circumference ratio, r is the radius of the discharge pipe, the unit is mm, s is the number of annular openings, A is the cross-sectional area of the annular openings, and the unit is m 2 L is the distance of the gaseous refrigerant flowing, the unit is cm, e is the natural logarithmic base number, I W Is the steady-state current of the electromagnetic valve, and the unit is A and I 0 Initial current of electromagnetic valve with unit of A, k 1 For correction coefficient, lambda is contraction coefficient, c is compensation constant, the value range is 0-10, P 0 Is the initial pressure of the gaseous refrigerant, and has the unit of MPa and P 1 Is the pressure of the gaseous refrigerant after entering the annular opening, and has the unit of MPa.
No matter which outlet the gaseous refrigerant flows out, the part of the gaseous refrigerant finally flows out from the gaseous refrigerant total outlet 231 through the gaseous refrigerant collecting chamber 230, and the whole process is completed.
As can be seen from fig. 2, the first liquid refrigerant inlet 152 and the second liquid refrigerant inlet 151 are arranged on an end wall surface of the housing and are symmetrically distributed in the center, thereby ensuring a relatively uniform flow distribution of the liquid refrigerant.
The structure of the coil group 120 in the double pipe heat exchanger is shown in fig. 3. The spiral tube group consists of four spiral tubes. Wherein the coils 121a and 121b are arranged side by side to form a first group. The coils 122a and 122b are disposed side-by-side to form a second set. The first and second sets of coils are oppositely rotated and together form a coil assembly 120. The two ends of the coil group 120 are respectively communicated with the first cavity and the second cavity of the double pipe heat exchanger. By adopting the arrangement mode, the space inside the double-pipe heat exchanger can be efficiently utilized, and the heat exchange area of the gaseous refrigerant and the liquid refrigerant is increased, so that the heat exchange efficiency of the double-pipe heat exchanger is improved.
The structure of the central tubule 110 in the double pipe heat exchanger is shown in figure 4. The central tubule 110 is a long circular straight tube and a series of annular holes 111 are opened in a left position so that the gaseous refrigerant can enter the central tubule 7 through the holes.
As shown in fig. 5, the side view structure of the holes 6 formed in the shape of a ring is shown, and the holes are formed in the wall surface of the center tubule 110 in a uniform annular array at an angle of 45 ° so that the gas refrigerant can uniformly flow into the center tubule.
For the double pipe heat exchanger, the opening and closing adjustment of the electromagnetic valve can be controlled, so that the double pipe heat exchanger has two working modes suitable for two common working conditions, and the double pipe heat exchanger can meet wider requirements.
Although embodiments of the present invention have been disclosed above, it is not limited to the details and embodiments shown and described, it is well suited to various fields of use for which the invention would be readily apparent to those skilled in the art, and accordingly, the invention is not limited to the specific details and illustrations shown and described herein, without departing from the general concepts defined in the claims and their equivalents.
Claims (5)
1. A double pipe heat exchanger for an automobile having two operating states, comprising:
the shell is internally provided with a cavity, one end of the shell is provided with a liquid refrigerant inlet and a first gaseous refrigerant outlet, the other end of the shell is provided with a liquid refrigerant outlet and a second gaseous refrigerant outlet, and the outer wall of the shell is provided with a gaseous refrigerant inlet;
a center tubule provided inside the housing, and provided with a plurality of annular openings along a circumference at one end thereof;
the spiral tube group is wound outside the central thin tube, one end of the spiral tube group is communicated with the liquid refrigerant inlet, and the other end of the spiral tube group is communicated with the liquid refrigerant outlet;
a first gaseous refrigerant discharge pipe having one end communicating with the first gaseous refrigerant outlet;
a second gaseous refrigerant discharge pipe having one end communicating with the second gaseous refrigerant outlet;
the gas collecting cavity is arranged between the first gaseous refrigerant discharge pipe and the second gaseous refrigerant discharge pipe and is provided with a gaseous refrigerant total outlet;
wherein, a first valve body is arranged on the first gaseous refrigerant discharge pipe, and a second valve body is arranged on the second gaseous refrigerant discharge pipe; when the first valve body is opened and the second valve body is closed, gaseous refrigerant is discharged from the first gaseous refrigerant; when the first valve body is closed and the second valve body is opened, gaseous refrigerant is discharged from the second gaseous refrigerant discharge pipe through the center tubule;
a first wall surface sleeved outside the central thin tube and arranged at one end of the central thin tube, wherein the first wall surface is abutted against the inner wall of the shell;
the second wall surface is arranged in parallel with the first wall surface, sleeved outside the central thin tube and arranged at the other end of the central thin tube, and is abutted against the inner wall of the shell;
a first cavity is formed between the first wall surface and the inner wall surface at one end of the shell, a second cavity is formed between the first wall surface and the second wall surface, and a third cavity is formed between the second wall surface and the inner wall surface at the other end of the shell;
one end of the spiral tube group penetrates through the first wall surface to be communicated with the first cavity, and the other end of the spiral tube group penetrates through the second wall surface to be communicated with the third cavity; and
the liquid refrigerant inlet is communicated with the first cavity, and the liquid refrigerant outlet is communicated with the third cavity;
the liquid refrigerant inlet comprises a first liquid refrigerant inlet and a second liquid refrigerant inlet which is symmetrically arranged with the first liquid refrigerant inlet;
the central tubule is provided with a plurality of annular openings on one side close to the first wall surface, and the annular openings are distributed on the periphery circle of the central tubule at equal intervals.
2. The double pipe heat exchanger for an automobile having two operating states according to claim 1, wherein the coil group includes:
a first coil group including at least two first coils arranged side by side;
the second spiral pipe group is arranged opposite to the first spiral pipe group and comprises at least two second spiral pipes arranged side by side.
3. The double pipe heat exchanger for an automobile having two operating states according to claim 2, wherein the plurality of annular openings are provided at equal intervals on the center tubule.
4. A double pipe heat exchanger for an automobile having two operating states according to claim 3, wherein the first valve body and the second valve body are solenoid valves.
5. The double pipe heat exchanger for an automobile having two operating states according to claim 4, wherein the empirical formula of the flow rate Q after the gaseous refrigerant enters the annular opening satisfies:
wherein pi is the circumferential rate, r is the radius of the refrigerant discharge pipe, s is the number of annular openings, A is the cross-sectional area of the annular openings, L is the distance of the gaseous refrigerant flowing, and e is the natural pairNumber base, I W For steady state current of working valve body, I 0 Initial current, k of working valve body 1 For correction factor, lambda is the coefficient of contraction, c is the compensation constant, P 0 Is the initial pressure of the gaseous refrigerant, P 1 Is the pressure of the gaseous refrigerant after it has entered the annular opening.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810749600.6A CN108716791B (en) | 2018-07-10 | 2018-07-10 | Double pipe type heat exchanger with two working states for automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810749600.6A CN108716791B (en) | 2018-07-10 | 2018-07-10 | Double pipe type heat exchanger with two working states for automobile |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108716791A CN108716791A (en) | 2018-10-30 |
| CN108716791B true CN108716791B (en) | 2024-04-16 |
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ID=63914208
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810749600.6A Active CN108716791B (en) | 2018-07-10 | 2018-07-10 | Double pipe type heat exchanger with two working states for automobile |
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| Country | Link |
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| CN (1) | CN108716791B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201297802Y (en) * | 2008-08-19 | 2009-08-26 | 郑引河 | Flexible diversion double spiral sleeve type heat exchanger |
| CN203501139U (en) * | 2013-07-15 | 2014-03-26 | 上海华向节能环保科技有限公司 | Double-pipe phase change heat exchanger |
| CN106969558A (en) * | 2017-04-21 | 2017-07-21 | 美的集团股份有限公司 | The heat-exchange method of refrigeration system and refrigeration system |
| KR20170109463A (en) * | 2016-03-21 | 2017-09-29 | 주식회사 평산 | Double pipe heat exchanger method of maufacturing and the double pipe |
| CN208487848U (en) * | 2018-07-10 | 2019-02-12 | 吉林大学 | There are two types of the automobile double pipe heat exchangers of working condition for a kind of tool |
-
2018
- 2018-07-10 CN CN201810749600.6A patent/CN108716791B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201297802Y (en) * | 2008-08-19 | 2009-08-26 | 郑引河 | Flexible diversion double spiral sleeve type heat exchanger |
| CN203501139U (en) * | 2013-07-15 | 2014-03-26 | 上海华向节能环保科技有限公司 | Double-pipe phase change heat exchanger |
| KR20170109463A (en) * | 2016-03-21 | 2017-09-29 | 주식회사 평산 | Double pipe heat exchanger method of maufacturing and the double pipe |
| CN106969558A (en) * | 2017-04-21 | 2017-07-21 | 美的集团股份有限公司 | The heat-exchange method of refrigeration system and refrigeration system |
| CN208487848U (en) * | 2018-07-10 | 2019-02-12 | 吉林大学 | There are two types of the automobile double pipe heat exchangers of working condition for a kind of tool |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108716791A (en) | 2018-10-30 |
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