CN112082402A - Micro-channel heat exchanger and heat pump system - Google Patents
Micro-channel heat exchanger and heat pump system Download PDFInfo
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- CN112082402A CN112082402A CN202011038358.5A CN202011038358A CN112082402A CN 112082402 A CN112082402 A CN 112082402A CN 202011038358 A CN202011038358 A CN 202011038358A CN 112082402 A CN112082402 A CN 112082402A
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- 239000003507 refrigerant Substances 0.000 claims abstract description 97
- 230000009977 dual effect Effects 0.000 claims description 33
- 241001635479 Coris bulbifrons Species 0.000 claims description 29
- 238000002347 injection Methods 0.000 claims description 17
- 239000007924 injection Substances 0.000 claims description 17
- 125000006850 spacer group Chemical group 0.000 claims description 16
- 238000003780 insertion Methods 0.000 claims description 3
- 230000037431 insertion Effects 0.000 claims description 3
- 230000005484 gravity Effects 0.000 description 7
- 239000007791 liquid phase Substances 0.000 description 7
- 230000009286 beneficial effect Effects 0.000 description 6
- 239000000243 solution Substances 0.000 description 6
- 239000012071 phase Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 239000002826 coolant Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000011148 porous material Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 239000012141 concentrate Substances 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
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Classifications
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- 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
- F28D1/04—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 tubular conduits
- F28D1/053—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 tubular conduits the conduits being straight
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05325—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
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- 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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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- 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 micro-channel heat exchanger and a heat pump system, relates to the technical field of heat pump systems, and solves the technical problem that when the micro-channel heat exchanger is used as an evaporator in the prior art, refrigerant entering a flat pipe is unevenly distributed. The microchannel heat exchanger comprises a double collecting pipe and an open-hole inner inserting pipe, wherein the open-hole inner inserting pipe penetrates through the double collecting pipe and is contacted with the inner wall surface of the double collecting pipe, at least an inner inserting pipe upper hole, an inner inserting pipe lower hole and an inner inserting pipe jet hole are arranged on the open-hole inner inserting pipe, and a refrigerant in the open-hole inner inserting pipe enters the double collecting pipe through the inner inserting pipe upper hole and the inner inserting pipe jet hole and then is mixed with the refrigerant entering the double collecting pipe through the inner inserting pipe lower hole. According to the micro-channel heat exchanger and the heat pump system, the refrigerant is uniformly distributed in the cavity of the double-collecting pipe, so that the refrigerant can be uniformly distributed in the flat pipe, and the heat exchange performance of the micro-channel heat exchanger can be improved.
Description
Technical Field
The invention relates to the technical field of heat pump systems, in particular to a micro-channel heat exchanger and a heat pump system comprising the same.
Background
When the microchannel heat exchanger is used as an evaporator, an inlet refrigerant is generally in a gas-liquid two-phase state, a collecting pipe of the traditional microchannel heat exchanger has no flow dividing measure, and the gas-liquid two-phase refrigerant is obviously layered after entering the collecting pipe, so that the refrigerant entering a flat pipe is unevenly distributed, and the heat exchange performance of the heat exchanger is poor.
Patent JPA2019074287 provides a dual collecting pipe of a microchannel heat exchanger, wherein an inner pipe and an outer pipe of the dual collecting pipe are on the same axis, a gas-liquid two-phase refrigerant enters the collecting pipe from the bottom of the inner pipe, and enters the cavity of the outer pipe through an opening or a gap of the inner pipe of the dual collecting pipe, so that the distribution uniformity of the refrigerant is improved. However, in the scheme provided by this patent, the coolant in the upper flat tube is still less, and the coolant in the lower flat tube is more, which is not favorable for improving the problem of uneven distribution of the coolant in the cavity. The specific reasons are as follows: the liquid-phase refrigerant in the gas-liquid two-phase refrigerant entering the cavity body descends under the action of gravity, so that the upper space refrigerant and the lower space refrigerant in the cavity body are less and more; correspondingly, less refrigerant enters the upper flat tube, and more refrigerant enters the lower flat tube.
Therefore, providing a heat exchanger capable of uniformly distributing the refrigerant in the flat tubes to improve the heat exchange performance of the heat exchanger becomes a technical problem to be solved by those skilled in the art.
Disclosure of Invention
The invention provides a micro-channel heat exchanger and a heat pump system, and solves the technical problem that when the micro-channel heat exchanger is used as an evaporator in the prior art, refrigerant entering a flat pipe is unevenly distributed. The various technical effects that can be produced by the preferred technical solution of the present invention are described in detail below.
In order to achieve the purpose, the invention provides the following technical scheme:
the microchannel heat exchanger comprises a double collecting pipe and an open-hole inner inserting pipe, wherein the open-hole inner inserting pipe penetrates through the double collecting pipe and is in contact with the inner wall surface of the double collecting pipe, at least an inner inserting pipe upper hole, an inner inserting pipe lower hole and an inner inserting pipe jet hole are formed in the open-hole inner inserting pipe, and a refrigerant in the open-hole inner inserting pipe enters the double collecting pipe through the inner inserting pipe upper hole and the inner inserting pipe jet hole and then is mixed with the refrigerant entering the double collecting pipe through the inner inserting pipe lower hole.
According to a preferred embodiment, the double collecting pipe is provided with N spacer grooves, and the double collecting pipe is divided into N +1 chambers by the spacers positioned on the spacer grooves, and N +1 internal tubes of the openings respectively penetrate through the double collecting pipe of the N +1 chambers and are in contact with the inner wall surface of the double collecting pipe; wherein N is an integer of 1 or more.
According to a preferred embodiment, the double header comprises a double header outer tube and a double header inner tube, the outer diameter of the double header inner tube is smaller than the inner diameter of the double header outer tube, and the double header inner tube is located inside the double header outer tube.
According to a preferred embodiment, the inner tube upper hole and the inner tube lower hole are respectively disposed on the upper surface and the lower surface of the inner tube in the cavity of the dual manifold, and the inner tube injection hole is disposed on the upper surface of the inner tube in the cavity of the outer tube in the dual manifold, so that the refrigerant in the inner tube in the opening enters the inner tube in the dual manifold through the inner tube upper hole and the inner tube lower hole, and then enters the cavity of the outer tube in the dual manifold through the inner tube in the dual manifold.
According to a preferred embodiment, the wall surfaces at two ends of the inner tube of the dual collecting pipe in the N +1 chambers are respectively provided with a first inner tube refrigerant port and a second inner tube refrigerant port, so that the refrigerant flows out of or enters the cavity of the inner tube of the dual collecting pipe through the first inner tube refrigerant port and the second inner tube refrigerant port.
According to a preferred embodiment, the outer diameter of the inner tube of the double manifold is larger than the outer diameter of the inner tube of the open-pored insert tube.
According to a preferred embodiment, the diameter of the upper hole of the inner insert tube is larger than the diameter of the lower hole of the inner insert tube, and the diameter of the injection hole of the inner insert tube is 0.1 to 5 mm.
According to a preferred embodiment, the microchannel heat exchanger further comprises a flat pipe and a gas pipe collecting pipe, wherein the double collecting pipe and the gas pipe collecting pipe are respectively provided with a first flat pipe groove and a second flat pipe groove, and two ends of the flat pipe are respectively inserted into the first flat pipe groove and the second flat pipe groove and are communicated with the double collecting pipe and the gas pipe collecting pipe.
According to a preferred embodiment, the flat tube is inserted into the double manifold to a depth of not less than half of the inner diameter of the cavity of the double manifold.
The heat pump system comprises the micro-channel heat exchanger in any technical scheme of the invention.
The micro-channel heat exchanger and the heat pump system provided by the invention at least have the following beneficial technical effects:
the microchannel heat exchanger comprises a double collecting pipe and an open-pore inner inserting pipe, wherein the open-pore inner inserting pipe is at least provided with an inner inserting pipe upper hole, an inner inserting pipe lower hole and an inner inserting pipe jet hole, so that a refrigerant entering the open-pore inner inserting pipe can be divided into three paths to enter a cavity of the double collecting pipe, wherein two paths of refrigerants respectively enter the cavity of the double collecting pipe from the upper direction and the lower direction through the inner inserting pipe upper hole and the inner inserting pipe lower hole, a third path of refrigerant enters the cavity of the double collecting pipe through the inner inserting pipe jet hole in a jet mode, and the three paths of refrigerants are converged in the cavity of the double collecting pipe to ensure that the refrigerant is uniformly distributed in a flat pipe, thereby improving the heat exchange performance of the microchannel heat exchanger.
In the microchannel heat exchanger, the refrigerant enters the cavity of the double collecting pipe through multiple paths and is converged in the cavity of the double collecting pipe, so that the problem of uneven refrigerant distribution in the cavity of the collecting pipe in the prior art can be solved, and the technical problem of uneven refrigerant distribution in the flat pipe when the microchannel heat exchanger is used as an evaporator in the prior art is solved.
In addition, the preferable technical scheme of the invention also has the following beneficial technical effects:
the double collecting pipe of the preferred technical scheme of the invention is provided with N spacer grooves, the double collecting pipe is divided into N +1 chambers by the spacers positioned on the spacer grooves, the N +1 open-hole inserted pipes respectively pass through the double collecting pipe of the N +1 chambers and are contacted with the inner wall surface of the double collecting pipe, namely the double collecting pipe is divided into N +1 sections, and the refrigerant entering each chamber of the double collecting pipe through the open-hole inserted pipes flows in each chamber, thereby shortening the descending stroke of the liquid-phase refrigerant, reducing the influence of the gravity on the liquid-phase refrigerant, avoiding the liquid-phase refrigerant from descending under the action of the gravity and concentrating on the lower part of the double collecting pipe, further improving the distribution uniformity of the refrigerant in the double collecting pipe, and further improving the heat exchange performance of the microchannel heat exchanger.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a schematic diagram of a preferred embodiment of a microchannel heat exchanger according to the invention;
FIG. 2 is a schematic view of a preferred embodiment of the dual manifold and open-bore insert tube of the present invention;
FIG. 3 is a front cross-sectional view of a preferred embodiment of the dual manifold and open-bore insert tube of the present invention;
FIG. 4 is an enlarged view of a portion of FIG. 3;
FIG. 5 is a side cross-sectional view of a preferred embodiment of the dual manifold and open-bore insert tube of the present invention;
FIG. 6 is a cross-sectional view of a preferred embodiment of the open-celled insert of the present invention;
fig. 7 is a schematic diagram of a preferred embodiment of a heat pump system.
In the figure: 1. a microchannel heat exchanger; 10. inserting a pipe in the hole; 101. an upper hole of the inner inserting tube; 102. a lower hole of the inner inserting tube; 103. an inner insertion tube injection hole; 11. a spacer groove; 12. a double collecting pipe outer pipe; 13. the double collecting pipe inner pipe; 131. a first inner tube refrigerant port; 132. a second inner tube refrigerant port; 14. flat tubes; 15. a gas pipe collecting pipe; 16. a first flat tube slot; 17. an air inlet pipe and an air outlet pipe; 2. a four-way valve; 3. a compressor; 4. a heat exchanger; 5. a throttling device; 6. a flow divider.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be described in detail below. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the examples given herein without any inventive step, are within the scope of the present invention.
The microchannel heat exchanger and the heat pump system of the invention are described in detail below with reference to the accompanying drawings 1 to 7 and examples 1 and 2 of the specification.
Example 1
This embodiment will be described in detail with reference to fig. 1 to 6 of the specification.
The microchannel heat exchanger 1 of the present embodiment includes a double manifold and an inner open-hole tube 10, as shown in fig. 1 to 5. Preferably, the inner open pipe 10 passes through the double headers and contacts the inner wall surface of the double headers, and at least an upper inner pipe hole 101, a lower inner pipe hole 102 and an inner pipe injection hole 103 are formed in the inner open pipe 10, and the refrigerant in the inner open pipe 10 enters the double headers through the upper inner pipe hole 101 and the inner pipe injection hole 103 and then is mixed with the refrigerant entering the double headers through the lower inner pipe hole 102, as shown in fig. 3, 4 or 6.
In the microchannel heat exchanger 1 of this embodiment, the inner insert tube 10 is at least provided with an upper inner insert tube hole 101, a lower inner insert tube hole 102 and an inner insert tube injection hole 103, so that the refrigerant entering the inner insert tube 10 can be divided into three paths to enter the cavity of the dual manifold, wherein the two paths of refrigerant enter the cavity of the dual manifold from the upper and lower directions through the upper inner insert tube hole 101 and the lower inner insert tube hole 102, respectively, the third path of refrigerant enters the cavity of the dual manifold through the inner insert tube injection hole 103 in an injection manner, and the three paths of refrigerant join in the cavity of the dual manifold, so that the refrigerant is uniformly distributed in the cavity of the dual manifold, and thus the refrigerant is uniformly distributed in the flat tubes 14, and further the heat exchange performance of the microchannel heat exchanger.
That is, in the microchannel heat exchanger 1 of this embodiment, the refrigerant enters the cavity of the dual collecting pipe through multiple paths and joins in the cavity of the dual collecting pipe, so that the problem of uneven refrigerant distribution in the cavity of the collecting pipe in the prior art can be solved, and the technical problem of uneven refrigerant distribution in the flat pipe 14 when the microchannel heat exchanger 1 is used as an evaporator in the prior art is solved.
According to a preferred embodiment, the double collecting pipe is provided with N spacer grooves 11, and the double collecting pipe is divided into N +1 chambers by the spacers positioned on the spacer grooves 11, and the N +1 inner open-hole inserting pipes 10 respectively penetrate through the double collecting pipes of the N +1 chambers and contact with the inner wall surface of the double collecting pipe, as shown in fig. 1 to 5. Wherein N is an integer of 1 or more. As shown in fig. 1 to 5, the double collecting pipe is provided with 2 spacer grooves 11, which can divide the double collecting pipe into 3 chambers, and each chamber is inserted with an inner insertion tube 10. Preferably, the septum is a structure having an opening so that the respective chambers can communicate. Preferably, the septum may be provided without openings, thereby completely isolating the chambers.
The preferred technical scheme of this embodiment separates the double collecting pipe for N +1 cavity through the spacer that is located on spacer groove 11, be about to double collecting pipe divide into N +1 section, insert the refrigerant that intubate 10 got into each cavity of double collecting pipe through the trompil, flow in each cavity, thereby can shorten the stroke that the liquid phase refrigerant descends, reduce the influence of action of gravity to the liquid phase refrigerant, avoid the liquid phase refrigerant to descend and concentrate in the lower part of double collecting pipe under the action of gravity, further improve the homogeneity of refrigerant distribution in the cavity of double collecting pipe, thereby can further promote the heat transfer performance of microchannel heat exchanger 1.
According to a preferred embodiment, the double header includes a double header outer tube 12 and a double header inner tube 13, the outer diameter of the double header inner tube 13 is smaller than the inner diameter of the double header outer tube 12, and the double header inner tube 13 is located inside the double header outer tube 12, as shown in fig. 1 to 5. Preferably, the double header outer pipe 12 and the double header inner pipe 13 may be coaxial or internally tangent, or may have a structure in which a certain distance is provided between the inner surface of the double header outer pipe 12 and the outer surface of the double header inner pipe 13.
The double collecting pipe of the preferred technical scheme of this embodiment includes the double collecting pipe outer pipe 12 and the double collecting pipe inner pipe 13, and the double collecting pipe inner pipe 13 is located in the double collecting pipe outer pipe 12, so that the refrigerant can flow into the chamber of the double collecting pipe outer pipe 12 after passing through the chamber of the double collecting pipe inner pipe 13, which is beneficial to the disturbance of the refrigerant in the double collecting pipe, thereby being beneficial to the refrigerant shunting uniformity.
According to a preferred embodiment, the inner tube upper hole 101 and the inner tube lower hole 102 are respectively disposed on the upper and lower surfaces of the inner tube 10 in the cavity of the dual manifold inner tube 13, and the inner tube injection hole 103 is disposed on the upper surface of the inner tube 10 in the cavity of the outer tube 12, so that the refrigerant in the inner tube 10 enters the inner tube 13 through the inner tube upper hole 101 and the inner tube lower hole 102, and then enters the cavity of the outer tube 12 through the inner tube 13, as shown in fig. 2 to 6.
According to a preferred embodiment, the wall surfaces at two ends of the inner tube 13 of the dual header in the N +1 chambers are respectively provided with a first inner tube refrigerant port 131 and a second inner tube refrigerant port 132, so that the refrigerant flows out from the first inner tube refrigerant port 131 and the second inner tube refrigerant port 132 or enters the cavity of the inner tube 13 of the dual header, as shown in fig. 3 to 5.
Referring to fig. 4, the flow direction of the refrigerant in the double manifold is as follows: the refrigerant in the inner inserting tube 10 with the opening is divided into three paths to enter the cavity of the outer tube 12 of the double collecting tube, specifically, the first path of refrigerant enters the cavity of the inner tube 13 of the double collecting tube through the upper hole 101 of the inner inserting tube and flows upwards to enter the cavity of the outer tube 12 of the double collecting tube through the refrigerant port 131 of the first inner tube; the second refrigerant enters the cavity of the inner tube 13 of the dual collecting pipe through the lower hole 102 of the inner insert tube and flows downwards to enter the cavity of the outer tube 12 of the dual collecting pipe through the refrigerant port 132 of the second inner tube; the third path of refrigerant enters the cavity of the outer pipe 12 of the double collecting main in a spraying mode through the inner inserting pipe injection holes 103. One part of the first path of refrigerant and the third path of refrigerant is sucked into the flat pipe 14 communicated with the cavity of the outer pipe 12 of the double collecting pipe, and the other part of the first path of refrigerant and the third path of refrigerant continuously flows downwards under the action of gravity and is mixed with the second path of refrigerant, so that the uniformity of refrigerant distribution in the cavity of the outer pipe 12 of the double collecting pipe is ensured.
According to a preferred embodiment, the outer diameter of the inner tube 13 of the double manifold is larger than the outer diameter of the inner open-bore tube 10. In the preferred embodiment of the present invention, the outer diameter of the inner tube 13 of the dual collecting pipe is larger than the outer diameter of the inner tube 10 of the opening, so as to ensure that the inner tube 10 of the opening can pass through the inner tube 13 of the dual collecting pipe.
According to a preferred embodiment, the inner insert tube upper hole 101 has a larger diameter than the inner insert tube lower hole 102, and the inner insert tube injection hole 103 has a diameter of 0.1 to 5 mm. In the preferred technical scheme of the embodiment, the diameter of the upper hole 101 of the inner inserting pipe is larger than that of the lower hole 102 of the inner inserting pipe, so that more refrigerant flows upwards than downwards, and even if the refrigerant falls to the lower part of the cavity under the action of gravity, the refrigerant does not gather too much at the lower part of the cavity. In the preferred technical scheme of the embodiment, the diameter of the inner insert injection hole 103 is 0.1-5 mm, and the diameter is small, so that when the pressure in the inner insert tube 10 with the hole is large enough, the refrigerant in the inner insert tube 10 with the hole can enter the cavity of the outer tube 12 of the dual collecting pipe in an upward injection manner, and the uniformity of refrigerant mixing in the cavity of the outer tube 12 of the dual collecting pipe can be further improved.
According to a preferred embodiment, the microchannel heat exchanger 1 further comprises flat tubes 14 and a gas tube header 15, as shown in fig. 1. Preferably, the double collecting pipe and the gas pipe collecting pipe 15 are respectively provided with a first flat pipe groove 16 and a second flat pipe groove, and two ends of the flat pipe 14 are respectively inserted into the first flat pipe groove 16 and the second flat pipe groove and are communicated with the double collecting pipe and the gas pipe collecting pipe 15, as shown in fig. 1 to 4. Preferably, the flat tube 14 is inserted into the double manifold to a depth of not less than half the inner diameter of the double manifold cavity. More preferably, the flat tubes 14 are inserted into the interior of the double manifold to a depth that is half that of the outer tubes 12 of the double manifold. The flat tube 14 of the preferred technical scheme of this embodiment is located in the middle of the cavity of the outer tube 12 of the dual collecting pipe, which is beneficial to enhancing the disturbance of the refrigerant in the cavity of the outer tube 12 of the dual collecting pipe, thereby being beneficial to the uniformity of refrigerant distribution.
According to a preferred embodiment, the microchannel heat exchanger 1 further comprises a gas inlet and outlet tube 17, as shown in fig. 1. The gas inlet and outlet pipe 17 is disposed on the gas collecting pipe 15 and is communicated with the gas collecting pipe 15, so that the gas-phase refrigerant can flow out of the gas inlet and outlet pipe 17 or enter the cavity of the gas collecting pipe 15.
Example 2
This embodiment will be described in detail with reference to fig. 7 of the specification.
The heat pump system of this embodiment includes the microchannel heat exchanger 1 according to any one of the technical solutions in embodiment 1, and further includes a four-way valve 2, a compressor 3, a heat exchanger 4, a throttling device 5, and a flow divider 6, as shown in fig. 7. The heat pump system of this embodiment, with the microchannel heat exchanger 1 according to any one of the technical solutions of embodiment 1, can improve the heat exchange performance of the heat pump system.
When the microchannel heat exchanger 1 is used as a condenser, the tube a of the four-way valve 2 is communicated with the tube b, the tube c is communicated with the tube d, a refrigerant discharged from the compressor 3 enters the microchannel heat exchanger 1 after passing through the four-way valve 2 to be condensed and released, then flows out through the N +1 paths of the double collecting pipes on the right side, enters the throttling device 5 to be throttled after being converged by the flow divider 6, then enters the heat exchanger 4 to be evaporated and absorbed, finally returns to the compressor 3 through the four-way valve 2, and completes circulation.
When the microchannel heat exchanger 1 is used as an evaporator, the tube a of the four-way valve 2 is communicated with the tube c, the tube b is communicated with the tube d, a refrigerant discharged from the compressor 3 enters the heat exchanger 4 through the four-way valve 2 to be condensed and released, then enters the throttling device 5 to be throttled, then is shunted into N +1 paths through the shunt 6 to enter the microchannel heat exchanger 1 to be evaporated and absorbed, then flows out from the outlet of the left air pipe collecting pipe 15, finally returns to the compressor 3 through the four-way valve 2, and circulation is completed.
In the description of the present invention, it is to be noted that, unless otherwise specified, "a plurality" means two or more; the terms "upper", "lower", "left", "right", "inner", "outer", "front", "rear", "head", "tail", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are only for convenience in describing and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, should not be construed as limiting the invention. Furthermore, the terms "first," "second," "third," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should also be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the present invention can be understood as appropriate to those of ordinary skill in the art.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.
Claims (10)
1. The microchannel heat exchanger is characterized by comprising a double collecting pipe and an inner open-hole pipe (10), wherein the inner open-hole pipe (10) penetrates through the double collecting pipe and is in contact with the inner wall surface of the double collecting pipe, at least an upper inner pipe hole (101), a lower inner pipe hole (102) and an inner pipe injection hole (103) are formed in the inner open-hole pipe (10), and a refrigerant in the inner open-hole pipe (10) enters the double collecting pipe through the upper inner pipe hole (101) and the inner pipe injection hole (103) and then is mixed with the refrigerant entering the double collecting pipe through the lower inner pipe hole (102).
2. The microchannel heat exchanger according to claim 1, wherein the double collecting pipe is provided with N spacer grooves (11), and the double collecting pipe is divided into N +1 chambers by spacers located on the spacer grooves (11), and N +1 of the inner insertion pipes (10) for opening respectively pass through the double collecting pipes of the N +1 chambers and contact with the inner wall surface of the double collecting pipe;
wherein N is an integer of 1 or more.
3. The micro-channel heat exchanger according to claim 1 or 2, wherein the double header comprises a double header outer tube (12) and a double header inner tube (13), the double header inner tube (13) has an outer diameter smaller than the inner diameter of the double header outer tube (12), and the double header inner tube (13) is located inside the double header outer tube (12).
4. The microchannel heat exchanger of claim 3, wherein the inner tube upper hole (101) and the inner tube lower hole (102) are respectively disposed on the upper and lower surfaces of the inner tube (10) in the cavity of the inner tube (13), and the inner tube injection hole (103) is disposed on the upper surface of the inner tube (10) in the cavity of the outer tube (12) such that the inner tube (10) in the cavity is disposed on the upper surface of the inner tube in the cavity of the outer tube (12)
And the refrigerant in the inner pipe (10) with the hole enters the double collecting pipe inner pipe (13) through the inner pipe upper hole (101) and the inner pipe lower hole (102), and then enters the cavity of the double collecting pipe outer pipe (12) through the double collecting pipe inner pipe (13).
5. The micro-channel heat exchanger according to claim 4, wherein the wall surfaces at two ends of the inner tube (13) of the double collecting pipe in the N +1 chambers are respectively provided with a first inner tube refrigerant port (131) and a second inner tube refrigerant port (132), so that the refrigerant flows out from the first inner tube refrigerant port (131) and the second inner tube refrigerant port (132) or enters the chamber of the double collecting pipe inner tube (13).
6. The microchannel heat exchanger of claim 3, wherein the outer diameter of the inner tube (13) of the double manifold is larger than the outer diameter of the inner tube (10) of the open-bore.
7. The microchannel heat exchanger of claim 1, wherein the inner tube upper hole (101) has a larger diameter than the inner tube lower hole (102), and the inner tube injection hole (103) has a diameter of 0.1 to 5 mm.
8. The micro-channel heat exchanger according to claim 1, further comprising a flat pipe (14) and a gas pipe header (15), wherein the dual header and the gas pipe header (15) are respectively provided with a first flat pipe groove (16) and a second flat pipe groove, and two ends of the flat pipe (14) are respectively inserted into the first flat pipe groove (16) and the second flat pipe groove and are communicated with the dual header and the gas pipe header (15).
9. The microchannel heat exchanger of claim 8, wherein the flat tubes (14) are inserted into the interior of the manifold to a depth of no less than half the internal diameter of the manifold cavity.
10. A heat pump system comprising a microchannel heat exchanger as claimed in any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011038358.5A CN112082402A (en) | 2020-09-28 | 2020-09-28 | Micro-channel heat exchanger and heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011038358.5A CN112082402A (en) | 2020-09-28 | 2020-09-28 | Micro-channel heat exchanger and heat pump system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112629307A (en) * | 2021-01-05 | 2021-04-09 | 珠海格力电器股份有限公司 | Interpolation injection pipe subassembly and microchannel heat exchanger |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112629307A (en) * | 2021-01-05 | 2021-04-09 | 珠海格力电器股份有限公司 | Interpolation injection pipe subassembly and microchannel heat exchanger |
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