WO2023093287A1 - 换热器、热泵系统和洗碗机 - Google Patents

换热器、热泵系统和洗碗机 Download PDF

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Publication number
WO2023093287A1
WO2023093287A1 PCT/CN2022/122242 CN2022122242W WO2023093287A1 WO 2023093287 A1 WO2023093287 A1 WO 2023093287A1 CN 2022122242 W CN2022122242 W CN 2022122242W WO 2023093287 A1 WO2023093287 A1 WO 2023093287A1
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WO
WIPO (PCT)
Prior art keywords
hollow
fluid
heat exchanger
channel
central tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2022/122242
Other languages
English (en)
French (fr)
Inventor
刘勋伟
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Midea Group Co Ltd
Guangdong Midea White Goods Technology Innovation Center Co Ltd
Original Assignee
Midea Group Co Ltd
Guangdong Midea White Goods Technology Innovation Center Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Midea Group Co Ltd, Guangdong Midea White Goods Technology Innovation Center Co Ltd filed Critical Midea Group Co Ltd
Priority to EP22897373.1A priority Critical patent/EP4283237B1/en
Publication of WO2023093287A1 publication Critical patent/WO2023093287A1/zh
Priority to US18/369,669 priority patent/US12535274B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/026—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 helically coiled the conduits of only one medium being helically coiled and formed by bent members, e.g. plates, the coils having a cylindrical configuration
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/38—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and being staggered to form tortuous fluid passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L15/00—Washing or rinsing machines for crockery or tableware
    • A47L15/42—Details
    • A47L15/4291—Recovery arrangements, e.g. for the recovery of energy or water
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/06—Hollow fins; fins with internal circuits
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B40/00—Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers

Definitions

  • the present application relates to the technical field of heat exchange, in particular to a heat exchanger, a heat pump system and a dishwasher.
  • a heat exchanger is a device that enables two fluids at different temperatures to exchange heat. Heat is transferred from a fluid with a higher temperature to a fluid with a lower temperature, thereby heating or cooling the fluid.
  • the condenser and evaporator in the heat pump system are all types of heat exchangers.
  • the condenser of the heat pump system generally adopts a sleeve-type heat exchanger.
  • the average heat exchange area in the tube of the traditional sleeve-type heat exchanger is too small, and the residence time of the fluid per unit length is too short, resulting in the overall heat exchanger required The length is too long and the volume is too large.
  • the main purpose of this application is to propose a heat exchanger, aiming at solving the problems that the traditional heat exchanger requires too long overall length and takes up too much volume.
  • the heat exchanger proposed by this application includes:
  • At least one set of flow guiding units is arranged in the outer sleeve, and a first fluid is formed between the outer sleeve and the flow guiding unit group for the first fluid to flow from one end of the outer sleeve to the other end.
  • a zigzag channel, the guide unit group includes a first hollow vane, a connecting channel and a second hollow vane arranged in sequence along the axial direction of the outer sleeve, the first hollow vane, the connecting channel and the The second hollow blades are sequentially connected to form a second meandering flow channel for the second fluid to flow from one end to the other end of the outer sleeve.
  • first hollow vane, the connecting channel and the second hollow vane are twisted and inclined relative to the axis of the outer sleeve.
  • first hollow blade and the second hollow blade have the same twist and tilt direction, and the connecting channel and the first hollow blade have a twist and tilt direction opposite to each other.
  • connection channel is attached to the inner wall of the outer casing.
  • the flow guiding unit group further includes a first central pipe and a second central pipe, the first hollow blade is fixed on the outer periphery of the first central pipe, and the first central pipe is far away from the One end of the connecting channel is provided with a fluid inlet, and the other end is closed.
  • the peripheral wall of the first central tube is provided with a first through hole communicating with the first hollow blade; the second hollow blade is fixed to the first hollow blade.
  • one end of the second central tube away from the connecting channel is provided with a fluid outlet, and the other end is closed, and the peripheral wall of the second central tube is provided with a first hole communicating with the second hollow blade.
  • Two through holes are provided on the outer periphery of the two central tubes, one end of the second central tube away from the connecting channel is provided with a fluid outlet, and the other end is closed, and the peripheral wall of the second central tube is provided with a first hole communicating with the second hollow blade.
  • each of the first hollow blades there are a plurality of the first hollow blades, the connecting channels and the second hollow blades in one-to-one correspondence; each of the first hollow blades The vanes are arranged at intervals along the circumferential direction of the first central tube, and the peripheral wall of the first central tube is provided with a plurality of first through holes along the circumferential direction, and the first through holes correspond to the first hollow vanes one by one and communicating with each other; each of the second hollow blades is arranged at intervals along the circumference of the second central tube, and the peripheral wall of the second central tube is provided with a plurality of second through holes along the circumference, and the second through holes are connected with the The second hollow blades are in one-to-one correspondence and connected; each of the connecting channels is connected between the first hollow blades and the second hollow blades in a one-to-one correspondence.
  • both the first central tube and the second central tube are straight tubes extending coaxially with the outer casing, and a plurality of first hollow blades are arranged along the periphery of the first central tube.
  • the plurality of second hollow vanes are spaced and evenly arranged along the circumference of the second central tube.
  • each group of the flow guide unit groups is arranged in an array along the axial direction of the outer casing and communicates with each other in sequence.
  • the present application also proposes a heat pump system, including a compressor, a condenser, a throttle valve, and an evaporator, and the compressor, the condenser, the throttle valve, and the evaporator communicate with each other to form a circulation loop, so
  • the condenser adopts the above-mentioned heat exchanger.
  • the present application also proposes a dishwasher, including the above heat pump system.
  • the technical solution of the present application is to set a guide unit group in the outer casing, wherein the flow guide unit group includes a first hollow blade, a connecting channel and a second hollow blade arranged in sequence along the axial direction of the outer sleeve; the outer sleeve and the guide A first meandering flow channel for the first fluid to flow is formed between the flow unit groups, and the first hollow blade, the connecting channel and the second hollow blade are connected in sequence to form a second meandering flow channel for the second fluid to flow through.
  • the first fluid such as water
  • the second fluid such as refrigerant
  • the first meandering flow channel and the second meandering flow channel are both
  • the meandering structure extends from one end of the outer casing to the other, so that the effective length of the flow channel can be extended as much as possible without increasing the length of the outer casing, and the effective flow path of the fluid can be extended; at the same time, the first hollow blade and the second hollow blade Both are hollow sheet structures, which can effectively increase the contact area between the first fluid and the second fluid, and increase the residence time of the first fluid and the second fluid in the corresponding flow channel, thereby effectively improving the heat exchange efficiency. Therefore, compared with the traditional casing heat exchanger, the technical solution of the present application can effectively shorten the overall length of the heat exchanger, reduce the overall occupied volume of the heat exchanger, and improve the heat exchange efficiency.
  • Fig. 1 is the structural representation of an embodiment of the heat exchanger of the present application
  • Fig. 2 is a schematic diagram of an exploded structure of the heat exchanger in Fig. 1;
  • Fig. 3 is a structural schematic diagram of one of the diversion unit groups
  • Fig. 4 is a partial structural schematic diagram of the diversion unit group in Fig. 3;
  • Fig. 5 is a schematic diagram of the flow of fluid inside the heat exchanger in Fig. 1;
  • Fig. 6 is a structural schematic diagram of a dishwasher with a heat pump system.
  • the directional indication is only used to explain the relationship between the components in a certain posture. If the specific posture changes, the directional indication will also change accordingly.
  • the present application proposes a heat exchanger 10 .
  • the heat exchanger 10 includes an outer casing 11 and at least one set of flow guiding units 12 .
  • the outer casing 11 is provided with two ends open; the flow guiding unit group 12 is arranged in the outer casing 11, and a first The fluid flows through and flows from one end of the outer sleeve 11 to the first meandering flow channel 101 at the other end thereof, and the flow guiding unit group 12 includes first hollow vanes 121 , The connecting channel 122 and the second hollow vane 123, the first hollow vane 121, the connecting channel 122 and the second hollow vane 123 are sequentially connected to form an end for the second fluid to flow through and from the outer sleeve 11 Flow to the second meandering channel 102 at the other end.
  • the outer casing 11 is in a hollow tubular shape, and the two ends of the outer casing 11 are respectively opened.
  • the flow guide unit group 12 is arranged in the outer casing 11.
  • a first meandering flow channel 101 is formed between the surfaces, and the first fluid can flow from one end of the outer sleeve 11 to the other end along the first meandering flow channel 101, and a second meandering flow channel 102 is formed inside the flow guiding unit group 12.
  • the two fluids can flow from one end of the outer sleeve 11 to the other end along the second tortuous flow channel 102 .
  • the first fluid may be water
  • the second fluid may be refrigerant
  • the water and refrigerant are arranged in reverse flow, that is, water enters the first meandering flow channel 101 from the first open end of the outer sleeve 11 inside, and then flow through the first zigzag flow channel 101 to the second open end of the outer sleeve 11 for output, and the refrigerant enters the second zigzag flow channel 102 from the second open end of the outer sleeve 11, and then passes through the second zigzag flow channel 102 flows to the output of the first open end of the outer casing 11, the flow directions of water and refrigerant are opposite, and the water and refrigerant flow in the first meandering flow channel 101 and the second meandering flow channel 102 respectively, and the water Realize heat exchange with refrigerant.
  • the specific number of flow guide unit groups 12 in the outer sleeve 11 can be set according to actual needs, for example, one set of flow guide unit groups 12, two sets of flow guide unit groups 12 can be set, Or more groups of guide unit groups 12 .
  • FIG. 2 there are two sets of flow guide unit groups 12 , of course, this is only one embodiment of the present application, and is not a limitation to the present application.
  • only one set of flow guiding unit groups 12 is taken as an example for description below. Please refer to FIG. 3 and FIG.
  • the flow guide unit set 12 includes a first hollow vane 121 , a connecting channel 122 and a second hollow vane 123 sequentially arranged along the axial direction of the outer sleeve 11 .
  • the first hollow blade 121 and the second hollow blade 123 are in a wider sheet structure, and the connecting channel 122 is in an elongated tubular structure.
  • One end of the connecting channel 122 is connected and communicated with the first hollow blade 121, and the other end of the connecting channel 122 It is connected and communicated with the second hollow vane 123 .
  • the second fluid (such as refrigerant) first enters the first hollow vane 121, then enters the connecting channel 122 through the end of the first hollow vane 121, then flows into the second hollow vane 123 through the connecting channel 122, and finally flows from the second The hollow blade 123 flows out; the entire flow path of the second fluid (that is, the second tortuous flow channel 102) is zigzagging rather than straight, so the effective length of the flow channel can be extended, and the flow path of the second fluid can be extended; and the first The hollow blades 121 and the second hollow blades 123 have a wider sheet structure, which can increase the contact area between the second fluid and the first fluid, thereby improving heat exchange efficiency.
  • a flow guide unit group 12 is provided in the outer sleeve 11, wherein the flow guide unit group 12 includes a first hollow vane 121, a connecting channel 122 and a second hollow blade arranged in sequence along the axial direction of the outer sleeve 11 Two hollow blades 123; the first meandering channel 101 for the first fluid to flow is formed between the outer sleeve 11 and the guide unit group 12, and the first hollow blade 121, the connecting channel 122 and the second hollow blade 123 are sequentially connected to form a supply The second meandering channel 102 through which the second fluid flows.
  • the first fluid such as water
  • the second fluid such as refrigerant
  • the meandering channels 102 extend from one end of the outer casing 11 to the other in a meandering structure, so that the effective length of the flow path can be extended as far as possible without increasing the length of the outer casing 11, and the effective flow distance of the fluid can be extended;
  • Both the first hollow blade 121 and the second hollow blade 123 have a hollow sheet structure, which can effectively increase the contact area between the first fluid and the second fluid, increase the residence time of the first fluid and the second fluid in the corresponding flow channel,
  • the heat exchange efficiency can be effectively improved. Therefore, compared with the traditional tube-and-tube heat exchanger, the technical solution of the present application can effectively shorten the overall length of the heat exchanger 10, reduce the overall occupied volume of the heat exchanger 10, and improve heat
  • first hollow vane 121 , the connecting channel 122 and the second hollow vane 123 are twisted and inclined relative to the axis of the outer sleeve 11 .
  • first hollow blade 121 is twisted and inclined relative to the axis of the outer sleeve 11, that is, the first hollow blade 121 has a certain twist angle relative to the axis of the outer sleeve 11.
  • the first hollow vane 121 extends along the axial direction of the outer sleeve 11 and twists along the circumferential direction of the outer sleeve 11 , so that the first hollow vane 121 presents a twisted shape rather than a completely planar structure.
  • the second hollow vane 123 is also twisted and inclined relative to the axis of the outer sleeve 11 , so that the second hollow vane 123 presents a twisted shape rather than a completely planar structure.
  • the connection channel 122 is twisted and inclined relative to the axis of the outer sleeve 11 , so that the connection channel 122 presents a twisted structure rather than a straight line.
  • the first hollow vane 121 , the connecting channel 122 and the second hollow vane 123 in a twisted shape, when the first fluid flows along the first meandering flow channel 101 , it can sequentially follow the first
  • the rotational movement of the outer surface of the hollow vane 121, the connecting channel 122 and the second hollow vane 123 generates a swirl flow, which is beneficial to increase the flow and residence time of the first fluid, thereby improving the heat exchange efficiency, and can also reduce the flow rate of the first fluid. Flow resistance, thereby reducing energy consumption.
  • the second fluid flows along the second meandering flow channel 102, it can follow the first hollow vane 121, the connecting channel 122 and the inner surface of the second hollow vane 123 to rotate in turn to generate swirling flow, which is beneficial to increase the flow rate of the second fluid. Process and residence time, thereby improving heat transfer efficiency.
  • first hollow vane 121 and the second hollow vane 123 have the same twist and tilt direction
  • the connecting channel 122 and the first hollow vane 121 have a twist and tilt direction opposite to each other.
  • both the first hollow vane 121 and the second hollow vane 123 rotate positively with respect to the axis of the outer sleeve 11
  • the connecting channel 122 rotates counterrotately with respect to the axis of the outer sleeve 11.
  • the first fluid such as water
  • the first fluid flows along the surface of the first hollow vane 121 to generate swirling flow, and after reaching the end of the first hollow vane 121, due to the change of the rotational direction of the connecting channel 122, the The sudden change in the flow of the first fluid is beneficial for the first fluid to scour the outer surface of the connecting channel 122, and the second fluid (such as refrigerant) has a longer residence time when passing through the relatively slender connecting channel 122, so that it can effectively
  • the convective heat exchange between the first fluid and the second fluid is improved, and the heat exchange efficiency is further improved.
  • connection channel 122 is attached to the inner wall surface of the outer sleeve 11 .
  • the connecting channel 122 itself is a slender strip structure, and the connecting channel 122 is attached to the inner wall of the outer sleeve 11.
  • the connecting channel 122 is attached to the inner wall of the outer sleeve 11, which is also conducive to the integral formation of the connecting channel 122 and the outer sleeve 11.
  • the connecting channel 122 can be printed on the inner wall of the outer sleeve 11 by 3D printing technology, which can simplify The production process of the heat exchanger 10 saves costs.
  • the guide unit group 12 also includes a first central tube 124 and a second central tube 125 , and the first hollow blade 121 is fixed on the outer periphery of the first central tube 124
  • One end of the first central tube 124 away from the connecting channel 122 is provided with a fluid inlet 1241, the other end of the first central tube 124 is closed, and the peripheral wall of the first central tube 124 is provided with the
  • the first through hole 1242 communicated with the first hollow vane 121;
  • the second hollow vane 123 is fixed on the outer periphery of the second central tube 125, and the end of the second central tube 125 away from the connecting channel 122 is provided with a fluid
  • the outlet 1251 , the other end of the second central tube 125 is closed, and the peripheral wall of the second central tube 125 is provided with a second through hole 1252 communicating with the second hollow vane 123 .
  • the first central tube 124 is a straight tube extending coaxially with the outer sleeve 11.
  • the first central tube 124 is a hollow tubular structure with one end open and one end closed.
  • One side of the first hollow blade 121 is attached to the first central tube.
  • the outer peripheral surface of 124 is arranged and extends along the first central pipe 124, the opening end of the first central pipe 124 is provided with a fluid inlet 1241, the side wall of the first central pipe 124 is provided with a first through hole 1242, and the second fluid can flow from The fluid inlet 1241 enters into the first central tube 124 , and then flows into the first hollow blade 121 through the first through hole 1242 .
  • the second central tube 125 is a straight tube extending coaxially with the outer sleeve 11.
  • the second central tube 125 is a hollow tubular structure with one end open and one end closed.
  • One side of the second hollow blade 123 is attached to the outer periphery of the second central tube 125.
  • the open end of the second central tube 125 is provided with a fluid outlet 1251
  • the side wall of the second central tube 125 is provided with a second through hole 1252
  • the second fluid can flow from the first hollow
  • the vane 121 flows into the second hollow vane 123 through the connecting channel 122 , then flows into the second central tube 125 through the second through hole 1252 from the second hollow vane 123 , and finally flows out from the fluid outlet 1251 of the second central tube 125 .
  • a plurality of the first hollow blades 121, the connecting passages 122 and the second hollow blades 123 are provided in one-to-one correspondence; each of the first The hollow blades 121 are arranged at intervals along the circumferential direction of the first central tube 124, and the peripheral wall of the first central tube 124 is provided with a plurality of the first through holes 1242 along the circumferential direction, and the first through holes 1242 are connected to the first through holes 1242.
  • One hollow vane 121 is in one-to-one correspondence and connected; each of the second hollow vanes 123 is arranged at intervals along the circumferential direction of the second central tube 125, and the peripheral wall of the second central tube 125 is provided with a plurality of the second central tube 125 along the circumferential direction.
  • Through holes 1252 the second through holes 1252 correspond to and communicate with the second hollow blades 123; each connecting channel 122 is connected to the first hollow blades 121 and the second hollow blades between the blades 123 .
  • a plurality of first hollow vanes 121 are arranged at intervals along the circumferential direction of the first central tube 124, a plurality of second hollow vanes 123 are arranged at intervals along the circumferential direction of the second central tube 125, and a plurality of connecting channels 122 are arranged along the outer sleeve 11.
  • the inner peripheral surface of each connecting channel 122 is arranged at intervals, and one end of each connecting channel 122 is connected and communicated with the end of the first hollow blade 121 near the inner wall surface of the outer casing 11, and the other end of each connecting channel 122 is connected with the second hollow blade 123 near the outer casing 11
  • the ends of the inner walls are connected and communicated.
  • a first channel is formed between any two adjacent first hollow blades 121
  • a second channel is formed between any adjacent two second hollow blades 123
  • an intermediate channel is formed between a plurality of connecting channels 122 .
  • the flow path of the first fluid along the first tortuous channel 101 is generally as follows.
  • the first fluid enters the first channel from one end of the outer casing 11 , then enters the middle channel from the first channel, and then enters the third channel from the middle channel.
  • the flow path of the second fluid along the second tortuous flow channel 102 is generally as follows.
  • the second fluid enters the first central pipe 124 from the fluid inlet 1241 of the first central pipe 124, and then passes through multiple holes on the side wall of the first central pipe 124.
  • a first through hole 1242 shunts into the corresponding first hollow blade 121, and then enters into the corresponding connecting channel 122 at the end of each first hollow blade 121 close to the inner wall surface of the outer sleeve 11, and then enters into the corresponding connecting channel 122 through the connecting channel 122.
  • the flow finally flows into the second central tube 125 through a plurality of second through holes 1252 on the outer peripheral surface of the second central tube 125, and then flows out from the fluid outlet 1251 of the second central tube 125.
  • the second fluid moves in a centrifugal direction; during the process of entering the second central pipe 125 from the plurality of second hollow blades 123, the second fluid makes Converging motion in the centripetal direction.
  • the above design can further increase the contact area between the first fluid and the second fluid, prolong the flow and residence time of the first fluid and the second fluid in the corresponding flow channel, and improve the heat exchange efficiency.
  • both the first central tube 124 and the second central tube 125 are straight tubes extending coaxially with the outer casing 11 , and a plurality of first hollow blades 121 extend along the first central tube 124
  • the plurality of second hollow vanes 123 are spaced and evenly arranged along the circumference of the second central tube 125 . In this way, on the same circumferential section, the spacing between any two adjacent first hollow blades 121 is equal, and the spacing between any adjacent two second hollow blades 123 is equal, so that the flow of the first fluid and the second fluid The distribution is more uniform and the heat exchange between the first fluid and the second fluid is more uniform.
  • each group of the flow guiding unit groups 12 is arranged in an array along the axial direction of the outer sleeve 11 and communicates with each other in sequence.
  • each group of the flow guiding unit groups 12 is arranged in an array along the axial direction of the outer sleeve 11 and communicates with each other in sequence.
  • the heat exchanger 10 includes an outer casing 11 and at least two sets of flow guiding units 12 disposed in the outer casing 11 , wherein each group of flow guiding units 12 It includes a first central tube 124 , a plurality of first hollow vanes 121 , a plurality of connecting channels 122 , a plurality of second hollow vanes 123 , and a second central tube 125 .
  • a plurality of first hollow vanes 121 are spaced and evenly arranged along the circumferential direction of the first central tube 124, a plurality of second hollow vanes 123 are spaced and evenly arranged along the circumferential direction of the second central tube 125, and a plurality of connecting channels 122 are attached to each other.
  • the inner peripheral surface of the outer casing 11 is spaced and uniformly arranged, and one end of each connecting channel 122 is connected and communicated with the first hollow vane 121 , and the other end of each connecting channel 122 is connected and communicated with the second hollow vane 123 .
  • the first hollow vane 121 , the connecting channel 122 and the second hollow vane 123 are twisted and inclined relative to the axis of the outer sleeve 11 .
  • the first hollow vane 121 and the second hollow vane 123 have the same twist and tilt direction, and the connecting channel 122 and the first hollow vane 121 and the second hollow vane 123 have the opposite twist and tilt direction.
  • the first fluid (such as water) enters the first channel between any two adjacent first hollow blades 121 through an opening of the outer casing 11, and then passes through a plurality of first The channel converges to the middle channel defined by the plurality of connecting channels 122 , and then diverges to the second channel between any two adjacent second hollow blades 123 through the middle channel, and finally flows out from another opening of the outer casing 11 .
  • the second fluid and the first fluid are arranged countercurrently.
  • the second fluid (such as refrigerant) enters the first central pipe 124 from the fluid inlet 1241 of the first central pipe 124 , and then passes through a plurality of holes on the side wall of the first central pipe 124 .
  • the first through hole 1242 diverges into the corresponding first hollow blade 121 and makes a divergent movement in the centrifugal direction in the first hollow blade 121, and then enters the corresponding into the connecting channel 122 of the connecting channel 122, and then enters the second hollow blade 123 through the connecting channel 122 and makes a converging flow in the direction of the heart in the second hollow blade 123, and finally passes through a plurality of second channels on the outer peripheral surface of the second central tube 125
  • the holes 1252 converge into the second central pipe 125 , and then flow out from the fluid outlet 1251 of the second central pipe 125 into the next flow guiding unit group 12 .
  • the first hollow blade 121 and the second hollow blade 123 have a sheet structure, which can increase the contact area between the first fluid and the second fluid and improve the heat exchange efficiency; and the first hollow blade 121 and the second
  • the hollow vane 123 has a twisted structure, which can induce the first fluid and the second fluid to generate swirling flow, which is beneficial to increase the flow of the first fluid and the second fluid, increase the residence time, further improve the heat exchange efficiency, and at the same time reduce the flow rate of the second fluid.
  • a fluid flow resistance thereby reducing energy consumption.
  • the first hollow vane 121 and the second hollow vane 123 rotate in opposite directions to the connecting channel 122 , which is beneficial for the first fluid to scour the connecting channel 122 , thereby improving convective heat transfer.
  • the overall length of the heat exchanger 10 of the technical solution is shorter, and the occupied volume is smaller, which is beneficial to the heat pump system 20 miniaturization.
  • the present application also proposes a heat pump system 20.
  • the heat pump system 20 includes a compressor 21, a condenser 22, a throttle valve 23, and an evaporator 24.
  • the compressor 21, the The condenser 22, the throttle valve 23 and the evaporator 24 communicate with each other to form a circulation loop, and the condenser 22 adopts the heat exchanger 10 as described above.
  • the heat pump system 20 of this solution adopts the above-mentioned heat exchanger 10 as the condenser 22 .
  • the heat exchanger 10 includes an outer casing 11 and a flow guiding unit group 12 .
  • the outer casing 11 is provided with two ends open; the flow guiding unit group 12 is arranged in the outer casing 11, and a first The fluid flows through and flows from one end of the outer sleeve 11 to the first meandering flow channel 101 at the other end thereof, and the flow guiding unit group 12 includes first hollow vanes 121 ,
  • the connecting channel 122 and the second hollow vane 123, the first hollow vane 121, the connecting channel 122 and the second hollow vane 123 are sequentially connected to form an end for the second fluid to flow through and from the outer sleeve 11 Flow to the second meandering channel 102 at the other end.
  • the overall length of the heat exchanger 10 of this solution is smaller, and the occupied space is smaller, thereby making the overall heat pump system 20 more compact. It is compact, smaller in size, and has higher heat transfer efficiency.
  • the specific structure of the heat exchanger 10 refers to the above-mentioned embodiments. Since the heat pump system 20 adopts all the technical solutions of all the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments. Let me repeat them one by one.
  • the heat pump system 20 includes multiple condensers 22 (heat exchangers 10 ), and the multiple condensers 22 are connected to the circulation loop of the heat pump system 20 in parallel.
  • each condenser 22 can be controlled independently, and different numbers of condensers 22 can be controlled to work according to actual heat exchange needs.
  • multiple condensers 22 are connected in parallel without increasing the overall length of the heat pump system 20 , so that the heat pump system 20 can maintain a relatively small length while having an efficient heat exchange function.
  • the present application also proposes a dishwasher 200 .
  • the dishwasher 200 includes a body and a heat pump system 20 disposed in the body.
  • the heat pump system 20 includes a compressor 21, a condenser 22, a throttle valve 23 and an evaporator 24, and the compressor 21, the condenser 22, the throttle valve 23 and the evaporator 24 communicate with each other to form a cycle circuit, and the condenser 22 adopts the heat exchanger 10 as described above.
  • the heat exchanger 10 includes an outer casing 11 and a flow guiding unit group 12 .
  • the outer casing 11 is open at both ends; the flow guiding unit group 12 is arranged in the outer casing 11, and a first fluid flow is formed between the outer casing 11 and the flow guiding unit group 12. Passing through and flowing from one end of the outer sleeve 11 to the first meandering flow channel 101 at the other end thereof, the flow guide unit group 12 includes first hollow vanes 121 , connecting passages arranged in sequence along the axial direction of the outer sleeve 11 122 and the second hollow vane 123, the first hollow vane 121, the connecting passage 122 and the second hollow vane 123 are sequentially connected to form a flow for the second fluid to flow through and flow from one end of the outer sleeve 11 to it.
  • the second meandering channel 102 at the other end.
  • the heat pump system 20 is concentrated in the chassis of the dishwasher 200.
  • the heat pump system 20 includes a compressor 21, a condenser 22, a throttle valve 23 and an evaporator 24, wherein the condenser 22 uses the above-mentioned Heater 10.
  • the refrigerant channel of the condenser 22 (that is, the heat exchanger 10 ) (that is, the second zigzagging flow channel 102 of the heat exchanger 10 ) is sequentially connected with the throttle valve 23 , the evaporator 24 and the compressor 21 to form a cycle for the circulation of the refrigerant.
  • the water outlet end of the water channel of the condenser 22 (that is, the heat exchanger 10) (that is, the first meandering flow channel 101 of the heat exchanger 10) is connected with the water inlet of the circulating water pump 26, and the water inlet end of the water channel is connected with the The water return port of the water tank 27 in the cavity is connected, and the water outlet of the circulating water pump 26 is connected with the spray arm 28 in the inner cavity of the dishwasher 200 through a pipeline.
  • the number of spray arms 28 can be set to one, two or more according to actual needs.
  • the circulating water pump 26 provides power to drive circulating water for cleaning.
  • the circulating water pump 26 pumps hot water into the spray arm 28 through the pipeline.
  • the spray arm 28 is located in the inner cavity of the body.
  • the hot water is sprayed on the tableware through a plurality of spray holes, and finally the hot water enters the water tank 27 in the cavity for collection under the action of gravity, and flows out from the water return port and enters the circulating water pump 26 through the condenser 22 .
  • the condenser 22 used in the heat pump system 20 is located between the water return port and the circulating water pump 26.
  • One side of the condenser 22 is a water channel, and the other side is a refrigerant channel.
  • the water heating process is completed in the condenser 22.
  • the condenser 22 can specifically be The heat exchanger 10 in the above-mentioned embodiment is used.
  • the condenser 22 is the high temperature side of the heat pump system 20, used to transfer the heat of the refrigerant to water; the low temperature side of the heat pump system 20 is the evaporator 24, used for heat exchange between the refrigerant and the air.
  • the heat pump system 20 further includes a fan 25 located inside the evaporator 24 .
  • the fan 25 can specifically be an axial flow fan. The components of the entire heat pump system 20 are separated by a fan 25.
  • One side of the fan 25 is the condenser 22 and the compressor 21, which are closer to the circulating water pump 26 for easy connection of water pipes; the other side of the fan 25 is the evaporator 24 and the air duct, which are located on the chassis
  • the front side is convenient to complete heat exchange with the air, wherein the air inlet of the fan 25 is connected to the air inlet duct, the air outlet of the fan 25 is connected to the air outlet duct, and the other end of the air inlet duct is the evaporator 24.
  • the air inlet and the air outlet are all on the front side of the chassis.
  • the dishwasher 200 of this solution adopts the above-mentioned heat pump system 20 , and the heat pump system 20 has a compact overall layout and takes up little space, so that the overall dishwasher 200 can be made more compact and smaller.
  • the specific structure of the heat exchanger 10 refers to the above-mentioned embodiments. Since the dishwasher 200 adopts all the technical solutions of all the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments. Herein I won't repeat them one by one.

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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种换热器（10）、热泵系统（20）和洗碗机（200），其中，换热器（10）包括：外套管（11），呈两端敞口设置；以及至少一组导流单元组（12），设于所述外套管（11）内，所述外套管（11）与所述导流单元组（12）之间形成有供第一流体流过且由所述外套管（11）的一端流向其另一端的第一曲折流道（101），所述导流单元组（12）包括沿所述外套管（11）的轴向依次布置的第一中空叶片（121）、连接通道（122）和第二中空叶片（123），所述第一中空叶片（121）、所述连接通道（122）和所述第二中空叶片（123）依次连通形成有供第二流体流过且由所述外套管（11）的一端流向其另一端的第二曲折流道（102）。

Description

换热器、热泵系统和洗碗机
本申请要求于2021年11月24日申请的、申请号为202111418336.6的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及换热技术领域，特别涉及一种换热器、热泵系统和洗碗机。
 背景技术
换热器是一种使不同温度的两种流体实现热量交换的设备，热量从温度较高的流体传递给温度较低的流体，从而实现流体的加热或者冷却。例如，热泵系统中的冷凝器、蒸发器都是换热器的一种。其中，热泵系统的冷凝器一般采用套管式换热器，然而传统的套管式换热器的管内平均换热面积过小，流体的单位长度停留时间过短，导致换热器整体所需长度过长，占用体积过大。
 技术问题
本申请的主要目的是提出一种换热器，旨在解决传统的换热器整体所需长度过长，占用体积过大的问题。
 技术解决方案
为实现上述目的，本申请提出的换热器，包括：
外套管，呈两端敞口设置；以及
至少一组导流单元组，设于所述外套管内，所述外套管与所述导流单元组之间形成有供第一流体流过且由所述外套管的一端流向其另一端的第一曲折流道，所述导流单元组包括沿所述外套管的轴向依次布置的第一中空叶片、连接通道和第二中空叶片，所述第一中空叶片、所述连接通道和所述第二中空叶片依次连通形成有供第二流体流过且由所述外套管的一端流向其另一端的第二曲折流道。
在一实施例中，所述第一中空叶片、所述连接通道和所述第二中空叶片均相对于所述外套管的轴线呈旋扭倾斜状。
在一实施例中，所述第一中空叶片与所述第二中空叶片的旋扭倾斜方向相同，所述连接通道与所述第一中空叶片的旋扭倾斜方向相反。
在一实施例中，所述连接通道贴合于所述外套管的内壁面设置。
在一实施例中，所述导流单元组还包括第一中心管和第二中心管，所述第一中空叶片固定于所述第一中心管的外周，所述第一中心管远离所述连接通道的一端设有流体入口，另一端呈封闭设置，所述第一中心管的周壁设有与所述第一中空叶片连通的第一通孔；所述第二中空叶片固定于所述第二中心管的外周，所述第二中心管远离所述连接通道的一端设有流体出口，另一端呈封闭设置，所述第二中心管的周壁设有与所述第二中空叶片连通的第二通孔。
在一实施例中，在一组所述导流单元组中，所述第一中空叶片、所述连接通道和所述第二中空叶片一一对应地设置有多个；各所述第一中空叶片沿所述第一中心管的周向间隔布置，所述第一中心管的周壁沿周向设有多个所述第一通孔，所述第一通孔与所述第一中空叶片一一对应并连通；各所述第二中空叶片沿所述第二中心管的周向间隔布置，所述第二中心管的周壁沿周向设有多个所述第二通孔，所述第二通孔与所述第二中空叶片一一对应并连通；各所述连接通道一一对应地连接于所述第一中空叶片和所述第二中空叶片之间。
在一实施例中，所述第一中心管和所述第二中心管均为与所述外套管同轴延伸的直管，多个所述第一中空叶片沿所述第一中心管的周向间隔且均匀排布，多个所述第二中空叶片沿所述第二中心管的周向间隔且均匀排布。
在一实施例中，所述导流单元组设有至少两组，各组所述导流单元组沿所述外套管的轴向阵列排布并依次相通。
本申请还提出一种热泵系统，包括压缩机、冷凝器、节流阀和蒸发器，所述压缩机、所述冷凝器、所述节流阀和所述蒸发器相互连通形成循环回路，所述冷凝器采用如上所述的换热器。
本申请还提出一种洗碗机，包括如上的热泵系统。
 有益效果
本申请的技术方案通过在外套管内设置导流单元组，其中，导流单元组包括沿所述外套管的轴向依次布置的第一中空叶片、连接通道和第二中空叶片；外套管与导流单元组之间形成供第一流体流过的第一曲折流道，第一中空叶片、连接通道及第二中空叶片依次连通形成供第二流体流过的第二曲折流道。换热器工作时，第一流体（例如水）和第二流体（例如冷媒）分别在第一曲折流道和第二曲折流道内逆向流动；第一曲折流道和第二曲折流道均呈曲折状结构从外套管的一端延伸至另一端，从而能够在不增加外套管长度的情况下，尽量延长流道的有效长度，延长流体的有效流动路程；同时第一中空叶片和第二中空叶片均呈中空的片状结构，能够有效增大第一流体和第二流体的接触面积，增大第一流体和第二流体在对应流道内的停留时间，从而能够有效提高换热效率。因此，相较于传统的套管式换热器而言，本申请的技术方案能够有效缩短换热器的整体长度，减小换热器的整体占用体积，提升换热效率。
 附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本申请换热器一实施例的结构示意图；
图2为图1中的换热器的分解结构示意图；
图3为其中一个导流单元组的结构示意图；
图4为图3中的导流单元组的部分结构示意图；
图5为图1中的换热器内部的流体走向示意图；
图6为带有热泵系统的洗碗机的结构示意图。
附图标号说明：
标号 名称 标号 名称
10 换热器 123 第二中空叶片
11 外套管 124 第一中心管
12 导流单元组 1241 流体入口
101 第一曲折流道 1242 第一通孔
102 第二曲折流道 125 第二中心管
121 第一中空叶片 1251 流体出口
122 连接通道 1252 第二通孔
200 洗碗机 24 蒸发器
20 热泵系统 25 风扇
21 压缩机 26 循环水泵
22 冷凝器 27 腔内水槽
23 节流阀 28 喷淋臂
本申请目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
 本发明的实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，若本申请实施例中有涉及方向性指示（诸如上、下、左、右、前、后……），则该方向性指示仅用于解释在某一特定姿态下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，若本申请实施例中有涉及“第一”、“第二”等的描述，则该“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，若全文中出现的“和/或”或者“及/或”，其含义包括三个并列的方案，以“A和/或B”为例，包括A方案、或B方案、或A和B同时满足的方案。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
本申请提出一种换热器10。
请参照图1和图2，在本申请一实施例中，该换热器10包括外套管11和至少一组导流单元组12。其中，所述外套管11呈两端敞口设置；所述导流单元组12设于所述外套管11内，所述外套管11与所述导流单元组12之间形成有供第一流体流过且由所述外套管11的一端流向其另一端的第一曲折流道101，所述导流单元组12包括沿所述外套管11的轴向依次布置的第一中空叶片121、连接通道122和第二中空叶片123，所述第一中空叶片121、所述连接通道122和所述第二中空叶片123依次连通形成有供第二流体流过且由所述外套管11的一端流向其另一端的第二曲折流道102。
具体地，外套管11呈中空的管状，外套管11的两端分别呈敞口设置，导流单元组12设置于外套管11内，外套管11的内周面与导流单元组12的外表面之间形成有第一曲折流道101，第一流体能够沿着第一曲折流道101从外套管11的一端流向另一端，导流单元组12内部形成有第二曲折流道102，第二流体能够沿着第二曲折流道102从外套管11的一端流向另一端。例如，在实际应用中，第一流体可为水，第二流体可为冷媒，水和冷媒采用逆向流动布置，也即，水自外套管11的第一敞口端进入第一曲折流道101内，再经过第一曲折流道101流至外套管11的第二敞口端输出，冷媒自外套管11的第二敞口端进入第二曲折流道102内，再通过第二曲折流道102流至外套管11的第一敞口端输出，水和冷媒的流动方向相反，水和冷媒分别在第一曲折流道101和第二曲折流道102内流动，并且在流动的过程中水与冷媒实现热交换。
需要说明的是，在本实施例中，外套管11内的导流单元组12的具体数量可根据实际需要进行设置，例如可设置一组导流单元组12、两组导流单元组12，或者更多组导流单元组12。如图2中示出了导流单元组12设置有两组，当然，这只是本申请的其中一个实施例，并非是对本申请的限制。为了便于说明，以下仅以其中一组导流单元组12为例进行说明。请结合图3和图4，其中，导流单元组12包括沿外套管11的轴向依次布置的第一中空叶片121、连接通道122和第二中空叶片123。第一中空叶片121和第二中空叶片123呈较宽的片状结构，连接通道122呈细长的管状结构，连接通道122的一端与第一中空叶片121连接并相通，连接通道122的另一端与第二中空叶片123连接并相通。第二流体（例如冷媒）先进入第一中空叶片121内，然后经由第一中空叶片121的末端进入到连接通道122内，再经由连接通道122流入到第二中空叶片123内，最后从第二中空叶片123流出；第二流体的整个流动路径（也即第二曲折流道102）呈曲折状而不是直线状，因此能够延长流道的有效长度，延长第二流体的流动路径；并且第一中空叶片121和第二中空叶片123呈较宽的片状结构，能够增加第二流体与第一流体之间的接触面积，从而提升换热效率。
本申请的技术方案通过在外套管11内设置有导流单元组12，其中，导流单元组12包括沿所述外套管11的轴向依次布置的第一中空叶片121、连接通道122和第二中空叶片123；外套管11与导流单元组12之间形成供第一流体流过的第一曲折流道101，第一中空叶片121、连接通道122及第二中空叶片123依次连通形成供第二流体流过的第二曲折流道102。换热器10工作时，第一流体（例如水）和第二流体（例如冷媒）分别在第一曲折流道101和第二曲折流道102内逆向流动；第一曲折流道101和第二曲折流道102均呈曲折状结构从外套管11的一端延伸至另一端，从而能够在不增加外套管11长度的情况下，尽量延长流道的有效长度，延长流体的有效流动路程；同时第一中空叶片121和第二中空叶片123均呈中空的片状结构，能够有效增大第一流体和第二流体的接触面积，增大第一流体和第二流体在对应流道内的停留时间，从而能够有效提高换热效率。因此，相较于传统的套管式换热器而言，本申请的技术方案能够有效缩短换热器10的整体长度，减小换热器10的整体占用体积，提升换热效率。
进一步地，所述第一中空叶片121、所述连接通道122和所述第二中空叶片123均相对于所述外套管11的轴线呈旋扭倾斜状。具体地，以第一中空叶片121为例，第一中空叶片121相对于外套管11的轴线呈旋扭倾斜状，也即第一中空叶片121相对于外套管11的轴线具有一定的旋扭角度，第一中空叶片121沿着外套管11的轴向延伸的同时还沿着外套管11的周向扭曲，从而使得第一中空叶片121呈现出旋扭状而并非呈完全平面状结构。类似地，第二中空叶片123也相对于外套管11的轴线呈旋扭倾斜状，使得第二中空叶片123呈现出旋扭状而并非呈完全平面状结构。连接通道122相对于外套管11的轴线呈旋扭倾斜状，使得连接通道122呈现出旋扭状而并非直线状结构。
在本实施例中，通过将第一中空叶片121、连接通道122和第二中空叶片123均设置为旋扭状，第一流体沿着第一曲折流道101流动时，能够依次顺着第一中空叶片121、连接通道122及第二中空叶片123的外表面旋向运动产生旋流，有利于增加第一流体的流程和停留时间，从而提高换热效率，并且还能够减小第一流体的流动阻力，从而减小能耗。第二流体沿着第二曲折流道102流动时，能够依次顺着第一中空叶片121、连接通道122及第二中空叶片123的内表面旋向运动产生旋流，有利于增加第二流体的流程和停留时间，从而提高换热效率。
进一步地，所述第一中空叶片121与所述第二中空叶片123的旋扭倾斜方向相同，所述连接通道122与所述第一中空叶片121的旋扭倾斜方向相反。例如，第一中空叶片121和第二中空叶片123均相对于外套管11的轴线正旋，连接通道122相对于外套管11的轴线反旋，需要指出的是，此处的正旋和反旋只是相对而言，表明两者旋向不同。以第一流体（例如水）的流动为例，第一流体沿着第一中空叶片121的表面流动产生旋流，到达第一中空叶片121的末端后，由于连接通道122的旋向改变，使得第一流体的流动产生突变，有利于第一流体冲刷连接通道122的外表面，并且第二流体（例如冷媒）通过相对较为细长的连接通道122时具有较长的停留时间，如此，能够有效提升第一流体和第二流体之间的对流换热量，进一步提升换热效率。
进一步地，所述连接通道122贴合于所述外套管11的内壁面设置。第一流体冲刷连接通道122的外表面时，会对连接通道122产生一定的冲击力，而连接通道122本身为细长条结构，将连接通道122贴合于外套管11的内壁面设置，能够提升连接通道122的结构强度，避免连接通道122在长期冲刷下发生折断损坏，提升换热器10的使用寿命。另外连接通道122贴合于外套管11的内壁面设置，也有利于将连接通道122与外套管11一体成型，例如可通过3D打印技术在外套管11内壁面打印出连接通道122，如此能够简化换热器10的生产工艺，节约成本。
进一步地，请结合图3和图4，所述导流单元组12还包括第一中心管124和第二中心管125，所述第一中空叶片121固定于所述第一中心管124的外周，所述第一中心管124远离所述连接通道122的一端设有流体入口1241，所述第一中心管124的另一端呈封闭设置，所述第一中心管124的周壁设有与所述第一中空叶片121连通的第一通孔1242；所述第二中空叶片123固定于所述第二中心管125的外周，所述第二中心管125远离所述连接通道122的一端设有流体出口1251，所述第二中心管125的另一端呈封闭设置，所述第二中心管125的周壁设有与所述第二中空叶片123连通的第二通孔1252。
具体地，第一中心管124为与外套管11同轴延伸的直管，第一中心管124呈一端开口一端封闭的中空管状结构，第一中空叶片121的一侧贴合于第一中心管124的外周面设置并沿着第一中心管124延伸，第一中心管124的开口端设有流体入口1241，第一中心管124的侧壁设有第一通孔1242，第二流体能够从流体入口1241进入到第一中心管124内，再经由第一通孔1242流入到第一中空叶片121内。第二中心管125为与外套管11同轴延伸的直管，第二中心管125呈一端开口一端封闭的中空管状结构，第二中空叶片123的一侧贴合于第二中心管125的外周面设置并沿着第二中心管125延伸，第二中心管125的开口端设有流体出口1251，第二中心管125的侧壁设有第二通孔1252，第二流体能够从第一中空叶片121经由连接通道122流入到第二中空叶片123，再由第二中空叶片123经由第二通孔1252流入到第二中心管125，最后从第二中心管125的流体出口1251处流出。
进一步地，在一组所述导流单元组12中，所述第一中空叶片121、所述连接通道122和所述第二中空叶片123一一对应地设置有多个；各所述第一中空叶片121沿所述第一中心管124的周向间隔布置，所述第一中心管124的周壁沿周向设有多个所述第一通孔1242，所述第一通孔1242与所述第一中空叶片121一一对应并连通；各所述第二中空叶片123沿所述第二中心管125的周向间隔布置，所述第二中心管125的周壁沿周向设有多个所述第二通孔1252，所述第二通孔1252与所述第二中空叶片123一一对应并连通；各所述连接通道122一一对应地连接于所述第一中空叶片121和所述第二中空叶片123之间。
具体地，多个第一中空叶片121沿第一中心管124的周向间隔布置，多个第二中空叶片123沿第二中心管125的周向间隔布置，多个连接通道122沿外套管11的内周面间隔布置，每一连接通道122的一端与第一中空叶片121靠近外套管11内壁面的端部连接并相通，每一连接通道122的另一端与第二中空叶片123靠近外套管11内壁面的端部连接并相通。任意相邻两个第一中空叶片121之间形成第一通道、任意相邻两个第二中空叶片123之间形成第二通道，多个连接通道122之间形成中间通道。
第一流体沿第一曲折流道101的流动路径大体如下，第一流体自外套管11的一端进入第一通道，再从第一通道进入到中间通道，再由中间通道进入到第三通道。第二流体沿第二曲折流道102的流动路径大体如下，第二流体自第一中心管124的流体入口1241进入到第一中心管124内，再经由第一中心管124侧壁上的多个第一通孔1242分流至对应的第一中空叶片121内，然后在各第一中空叶片121紧贴外套管11内壁面的末端进入到对应的连接通道122内，再经由连接通道122进入到第二中空叶片123内，最后经由第二中心管125外周面的多个第二通孔1252汇流至第二中心管125内，再由第二中心管125的流体出口1251流出，在由第一中心管124进入到多个第一中空叶片121的过程中，第二流体做离心方向的发散运动，在由多个第二中空叶片123进入到第二中心管125的过程中，第二流体做向心方向的汇聚运动。上述设计，能够进一步增大第一流体与第二流体的接触面积，延长第一流体和第二流体在对应流道内的流程和停留时间，提升换热效率。
进一步地，所述第一中心管124和所述第二中心管125均为与所述外套管11同轴延伸的直管，多个所述第一中空叶片121沿所述第一中心管124的周向间隔且均匀排布，多个所述第二中空叶片123沿所述第二中心管125的周向间隔且均匀排布。如此，在同一圆周截面上，任意相邻两个第一中空叶片121之间的间距相等，任意相邻两个第二中空叶片123之间的间距相等，使得第一流体和第二流体的流动分布更为均匀，第一流体与第二流体之间的换热更为均匀。
进一步地，在上述实施例的基础上，所述导流单元组12设有至少两组，各组所述导流单元组12沿所述外套管11的轴向阵列排布并依次相通。如此，第二流体流经第一组导流单元组12的第二曲折流道102后，能够紧接着进入下一组导流单元组12的第二曲折流道102，从而能够进一步提升第二流体的流动路程，实现更好的换热效果。
请结合图1和图2，在一实施例中，该换热器10包括外套管11和设于外套管11内的至少两组导流单元组12，其中，每一组导流单元组12包括第一中心管124、多个第一中空叶片121、多个连接通道122、多个第二中空叶片123，以及第二中心管125。多个第一中空叶片121沿第一中心管124的周向间隔且均匀排布，多个第二中空叶片123沿第二中心管125的周向间隔且均匀排布，多个连接通道122贴合于外套管11的内周面间隔且均匀排布，每一连接通道122的一端与第一中空叶片121连接并相通，每一连接通道122的另一端与第二中空叶片123连接并相通。第一中空叶片121、连接通道122和第二中空叶片123均相对于外套管11的轴线呈旋扭倾斜状。第一中空叶片121与第二中空叶片123的旋扭倾斜方向相同，连接通道122与第一中空叶片121及第二中空叶片123的旋扭倾斜方向相反。
具体地，请结合图1和图5，第一流体（例如水）经由外套管11的一个敞口进入任意相邻两个第一中空叶片121之间的第一通道，再经由多个第一通道汇聚至多个连接通道122限定出的中间通道，再经由中间通道发散到任意相邻两个第二中空叶片123之间的第二通道，最后从外套管11的另一个敞口流出。第二流体与第一流体呈逆流布置，第二流体（例如冷媒）自第一中心管124的流体入口1241进入到第一中心管124内，再经由第一中心管124侧壁上的多个第一通孔1242分流至对应的第一中空叶片121内并在第一中空叶片121内做离心方向的发散运动，然后在各第一中空叶片121紧贴外套管11内壁面的末端进入到对应的连接通道122内，再经由连接通道122进入到第二中空叶片123内并在第二中空叶片123内做向心方向的汇聚流动，最后经由第二中心管125外周面的多个第二通孔1252汇流至第二中心管125内，再由第二中心管125的流体出口1251流出到下一个导流单元组12内。
在本实施例中，第一中空叶片121和第二中空叶片123呈片状结构，能够增大第一流体和第二流体的接触面积，提高换热效率；并且第一中空叶片121与第二中空叶片123呈旋扭结构，能够诱导第一流体及第二流体产生旋流，有利于增加第一流体及第二流体的流程，增加停留时间，进一步提高换热效率，同时还能够减小第一流体的流动阻力，从而减小能耗。第一中空叶片121及第二中空叶片123与连接通道122的旋向相反，有利于第一流体冲刷连接通道122，从而提高对流换热量。总体而言，相较于传统的套管式换热器，在实现相同换热效果的条件下，本技术方案的换热器10的总体长度更短，占用体积更小，有利于热泵系统20的小型化。
请参照图6，本申请还提出一种热泵系统20，在一实施例中，该热泵系统20包括压缩机21、冷凝器22、节流阀23和蒸发器24，所述压缩机21、所述冷凝器22、所述节流阀23和所述蒸发器24相互连通形成循环回路，所述冷凝器22采用如上所述的换热器10。
本方案的热泵系统20采用上述的换热器10作为冷凝器22。其中，换热器10包括外套管11和导流单元组12。其中，所述外套管11呈两端敞口设置；所述导流单元组12设于所述外套管11内，所述外套管11与所述导流单元组12之间形成有供第一流体流过且由所述外套管11的一端流向其另一端的第一曲折流道101，所述导流单元组12包括沿所述外套管11的轴向依次布置的第一中空叶片121、连接通道122和第二中空叶片123，所述第一中空叶片121、所述连接通道122和所述第二中空叶片123依次连通形成有供第二流体流过且由所述外套管11的一端流向其另一端的第二曲折流道102。相较于传统的套管式换热器而言，在实现同等换热效果的情况下，本方案的换热器10的整体长度更小，占用空间更小，进而使得热泵系统20的整体更为紧凑，体积更小，并且换热效率更高。其中，换热器10的具体结构参照上述实施例，由于本热泵系统20采用了上述所有实施例的全部技术方案，因此至少具有上述实施例的技术方案所带来的所有有益效果，在此不再一一赘述。
进一步地，热泵系统20包括多个冷凝器22（换热器10），多个冷凝器22采用并联的方式接入到热泵系统20的循环回路。如此，每个冷凝器22可独立控制，能够根据实际换热需要控制不同数量的冷凝器22工作。并且多个冷凝器22并联，并不会增大热泵系统20的整体长度，使得热泵系统20具有高效换热功能的同时，能够保持较小的长度。
请参照图6，本申请还提出一种洗碗机200，在一实施例中，该洗碗机200包括机体及设于机体内的热泵系统20。该热泵系统20包括压缩机21、冷凝器22、节流阀23和蒸发器24，所述压缩机21、所述冷凝器22、所述节流阀23和所述蒸发器24相互连通形成循环回路，所述冷凝器22采用如上所述的换热器10。其中，换热器10包括外套管11和导流单元组12。所述外套管11呈两端敞口设置；所述导流单元组12设于所述外套管11内，所述外套管11与所述导流单元组12之间形成有供第一流体流过且由所述外套管11的一端流向其另一端的第一曲折流道101，所述导流单元组12包括沿所述外套管11的轴向依次布置的第一中空叶片121、连接通道122和第二中空叶片123，所述第一中空叶片121、所述连接通道122和所述第二中空叶片123依次连通形成有供第二流体流过且由所述外套管11的一端流向其另一端的第二曲折流道102。
具体地，如图6所示，热泵系统20集中于洗碗机200的底盘中，热泵系统20包括压缩机21、冷凝器22、节流阀23和蒸发器24，其中冷凝器22采用上述换热器10。冷凝器22（也即换热器10）的冷媒通道（也即换热器10的第二曲折流道102）与节流阀23、蒸发器24及压缩机21依次连接形成供冷媒流通的循环回路，冷凝器22（也即换热器10）的水通道（也即换热器10的第一曲折流道101）的出水端与循环水泵26的进水口连通，水通道的进水端与腔内水槽27的回水口相连通，循环水泵26的出水口通过管道与洗碗机200内腔中的喷淋臂28连通。其中，喷淋臂28的数量可根据实际需要设置为一个、两个或者更多。
洗碗机200正常工作时，由循环水泵26提供动力以驱动循环水进行清洗，循环水泵26将热水由管道泵入喷淋臂28，喷淋臂28位于机体的内腔中，喷淋臂通过多个喷淋孔将热水喷淋在餐具上，最后热水在重力作用下进入腔内水槽27中进行收集，并由回水口流出经由冷凝器22进入循环水泵26。热泵系统20所用冷凝器22位于回水口和循环水泵26之间，冷凝器22的一侧为水通道，另一侧为冷媒通道，在冷凝器22内完成水加热过程，该冷凝器22具体可采用上述实施例中的换热器10。冷凝器22为热泵系统20的高温侧，用于将冷媒的热量传递给水；热泵系统20的低温侧为蒸发器24，用于冷媒与空气换热。可选地，热泵系统20还包括风扇25，风扇25位于蒸发器24的内侧。风扇25具体可为轴流风扇。整个热泵系统20的组件被风扇25分开，风扇25的一侧为冷凝器22、压缩机21，更靠近循环水泵26，便于连接水管；风扇25的另外一侧为蒸发器24和风道，位于底盘前侧，便于与空气完成换热，其中风扇25的进风口连接进风风道，风扇25的出风口连接出风风道，进风风道的另一端是蒸发器24。与空气换热时，空气经蒸发器24后全部进入进风风道，然后进入风扇25，最后出风风道流出，进风口和出风口均在底盘前侧。本方案的洗碗机200采用了上述的热泵系统20，该热泵系统20整体布局紧凑，占用空间小，从而能够使洗碗机200整体更为紧凑，体积更小。其中，换热器10的具体结构参照上述实施例，由于本洗碗机200采用了上述所有实施例的全部技术方案，因此至少具有上述实施例的技术方案所带来的所有有益效果，在此不再一一赘述。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的发明构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。

Claims (10)

  1. 一种换热器，其中，所述换热器包括：
    外套管，呈两端敞口设置；以及
    至少一组导流单元组，设于所述外套管内，所述外套管与所述导流单元组之间形成有供第一流体流过且由所述外套管的一端流向其另一端的第一曲折流道，所述导流单元组包括沿所述外套管的轴向依次布置的第一中空叶片、连接通道和第二中空叶片，所述第一中空叶片、所述连接通道和所述第二中空叶片依次连通形成有供第二流体流过且由所述外套管的一端流向其另一端的第二曲折流道。
  2. 如权利要求1所述的换热器，其中，所述第一中空叶片、所述连接通道和所述第二中空叶片均相对于所述外套管的轴线呈旋扭倾斜状。
  3. 如权利要求2所述的换热器，其中，所述第一中空叶片与所述第二中空叶片的旋扭倾斜方向相同，所述连接通道与所述第一中空叶片的旋扭倾斜方向相反。
  4. 如权利要求1所述的换热器，其中，所述连接通道贴合于所述外套管的内壁面设置。
  5. 如权利要求1所述的换热器，其中，所述导流单元组还包括第一中心管和第二中心管，所述第一中空叶片固定于所述第一中心管的外周，所述第一中心管远离所述连接通道的一端设有流体入口，另一端呈封闭设置，所述第一中心管的周壁设有与所述第一中空叶片连通的第一通孔；所述第二中空叶片固定于所述第二中心管的外周，所述第二中心管远离所述连接通道的一端设有流体出口，另一端呈封闭设置，所述第二中心管的周壁设有与所述第二中空叶片连通的第二通孔。
  6. 如权利要求5所述的换热器，其中，在一组所述导流单元组中，所述第一中空叶片、所述连接通道和所述第二中空叶片一一对应地设置有多个；各所述第一中空叶片沿所述第一中心管的周向间隔布置，所述第一中心管的周壁沿周向设有多个所述第一通孔，所述第一通孔与所述第一中空叶片一一对应并连通；各所述第二中空叶片沿所述第二中心管的周向间隔布置，所述第二中心管的周壁沿周向设有多个所述第二通孔，所述第二通孔与所述第二中空叶片一一对应并连通；各所述连接通道一一对应地连接于所述第一中空叶片和所述第二中空叶片之间。
  7. 如权利要求6所述的换热器，其中，所述第一中心管和所述第二中心管均为与所述外套管同轴延伸的直管，多个所述第一中空叶片沿所述第一中心管的周向间隔且均匀排布，多个所述第二中空叶片沿所述第二中心管的周向间隔且均匀排布。
  8. 如权利要求1至7中任意一项所述的换热器，其中，所述导流单元组设有至少两组，各组所述导流单元组沿所述外套管的轴向阵列排布并依次相通。
  9. 一种热泵系统，其中，所述热泵系统包括压缩机、冷凝器、节流阀和蒸发器，所述压缩机、所述冷凝器、所述节流阀和所述蒸发器相互连通形成循环回路，所述冷凝器采用如权利要求1至8中任意一项所述的换热器。
  10. 一种洗碗机，其中，所述洗碗机包括如权利要求9所述的热泵系统。
PCT/CN2022/122242 2021-11-24 2022-09-28 换热器、热泵系统和洗碗机 Ceased WO2023093287A1 (zh)

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