[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

WO2022152033A1 - 蒸发器 - Google Patents

蒸发器 Download PDF

Info

Publication number
WO2022152033A1
WO2022152033A1 PCT/CN2022/070481 CN2022070481W WO2022152033A1 WO 2022152033 A1 WO2022152033 A1 WO 2022152033A1 CN 2022070481 W CN2022070481 W CN 2022070481W WO 2022152033 A1 WO2022152033 A1 WO 2022152033A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
exchange tube
tube group
baffle
evaporator
Prior art date
Application number
PCT/CN2022/070481
Other languages
English (en)
French (fr)
Inventor
苏秀平
王勇
Original Assignee
约克（无锡）空调冷冻设备有限公司
江森自控泰科知识产权控股有限责任合伙公司
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 约克（无锡）空调冷冻设备有限公司, 江森自控泰科知识产权控股有限责任合伙公司 filed Critical 约克（无锡）空调冷冻设备有限公司
Priority to US18/272,037 priority Critical patent/US20240085069A1/en
Priority to EP22738914.5A priority patent/EP4279854A4/en
Priority to KR1020237027060A priority patent/KR20230130067A/ko
Publication of WO2022152033A1 publication Critical patent/WO2022152033A1/zh

Links

Images

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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/1607—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 in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C23/00—Alloys based on magnesium
    • C22C23/02—Alloys based on magnesium with aluminium as the next major constituent
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C23/00—Extruding metal; Impact extrusion
    • B21C23/02—Making uncoated products
    • B21C23/20—Making uncoated products by backward extrusion
    • B21C23/205—Making products of generally elongated shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/001—Continuous casting of metals, i.e. casting in indefinite lengths of specific alloys
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C1/00—Making non-ferrous alloys
    • C22C1/02—Making non-ferrous alloys by melting
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22F—CHANGING THE PHYSICAL STRUCTURE OF NON-FERROUS METALS AND NON-FERROUS ALLOYS
    • C22F1/00—Changing the physical structure of non-ferrous metals or alloys by heat treatment or by hot or cold working
    • C22F1/06—Changing the physical structure of non-ferrous metals or alloys by heat treatment or by hot or cold working of magnesium or alloys based thereon
    • 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
    • F25B39/02—Evaporators
    • 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
    • F28D3/00—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 flows in a continuous film, or trickles freely, over the conduits
    • F28D3/02—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 flows in a continuous film, or trickles freely, over the conduits with tubular conduits
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/163—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F25/00—Component parts of trickle coolers
    • F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
    • F28F25/04—Distributing or accumulator troughs
    • 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
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit

Definitions

  • the present application relates to an evaporator, in particular to an evaporator with high heat exchange efficiency.
  • the present application provides an evaporator with high heat exchange efficiency.
  • the evaporator in this application includes: a casing, a first heat exchange tube group and a second heat exchange tube group, a first side heat exchange tube baffle device and a second side heat exchange tube baffle device, and a redistribution device,
  • the shell has a cavity, and the cavity has a length direction, a width direction and a height direction; the heat exchange tubes in the first heat exchange tube group and the second heat exchange tube group extend along the length direction of the cavity , and are arranged along the width direction and height direction of the cavity, the first heat exchange tube group is located above the second heat exchange tube group, wherein, in the width direction of the cavity, the The number of columns of the first heat exchange tube group is greater than the number of columns of the second heat exchange tube group; the width of the first side heat exchange tube baffle device and the second side heat exchange tube baffle device in the cavity They are respectively arranged on opposite sides of the first heat exchange tube group and the second heat exchange tube group in the direction, and along the outside of the first heat exchange tube group and the second heat exchange
  • the redistribution device is arranged between the first heat exchange tube group and the second heat exchange tube group, and the two ends of the redistribution device in the width direction of the cavity are respectively connected with the first heat exchange tube group.
  • the side heat exchange tube baffle device is connected to the second side heat exchange tube baffle device, wherein the redistribution device extends along the length direction of the cavity to cover the top of the second heat exchange tube group, and There is a certain distance from the lower part of the first heat exchange tube group, the redistribution device is provided with several rows of holes, and each row of holes in the several rows of holes is arranged along the extension direction of the heat exchange tubes, Each row of holes in the rows of holes is aligned with a corresponding row of heat exchange tubes in the second heat exchange tube group.
  • the first heat exchange tube group and the second heat exchange tube group are respectively arranged symmetrically with respect to the central interface extending in the height direction of the cavity.
  • the widths of the first heat exchange tube group and the second heat exchange tube group are the same.
  • the first heat exchange tube group has an upper part of the first heat exchange tube group and a lower part of the first heat exchange tube group, and in the width direction of the cavity, the upper part of the first heat exchange tube group is The width is greater than the width of the second heat exchange tube group.
  • the width of the lower part of the first heat exchange tube group is gradually reduced from top to bottom, and the width of the top of the lower part of the first heat exchange tube group is the same as the width of the upper part of the first heat exchange tube group, The bottom of the lower part of the first heat exchange tube group is the same as the width of the second heat exchange tube group.
  • the sizes of the holes on the redistribution device gradually decrease from the middle of the redistribution device to the two sides.
  • the above evaporator further includes: a third heat exchange tube group, the third heat exchange tube group is located at the bottom of the cavity and below the second heat exchange tube group, the third heat exchange tube group There is a certain distance between the heat exchange tube group and the second heat exchange tube group to form a circulation space, so that the gaseous refrigerant flowing out from the second heat exchange pipe group can flow through the circulation space to the casing disposed in the casing. on the refrigerant outlet.
  • the first side heat exchange tube baffle device and the second side heat exchange tube baffle device respectively comprise at least one baffle exhaust passage, and in the height direction of the cavity, the A baffle exhaust passage is located above the second heat exchange tube bank, and the at least one baffle exhaust passage is configured to discharge gaseous refrigerant in the first heat exchange tube bank.
  • the first side heat exchange tube baffle device and the second side heat exchange tube baffle device respectively comprise a first side upper baffle lower section and a second side upper baffle lower section
  • the first The lower section of the upper side baffle and the lower section of the second upper baffle are arranged on both sides of the lower part of the first heat exchange tube group
  • the lower section of the first upper baffle and the lower section of the second upper baffle are respectively provided with several exhaust holes
  • each of the plurality of exhaust holes forms a baffle exhaust channel
  • the plurality of exhaust holes are arranged along the length direction of the cavity
  • the plurality of exhaust holes Each of the exhaust holes in the holes is formed into a long strip in the direction from the upper part of the first heat exchange tube group to the second heat exchange tube group.
  • the first heat exchange tube group has a heat exchange tube exhaust passage, and the heat exchange tube exhaust passage is formed between the heat exchange tubes of the first heat exchange tube group, and the heat exchange tube
  • the tube exhaust channel extends inwardly and upwardly from both sides of the lower part of the first heat exchange tube group, and on a cross section of the cavity perpendicular to the length direction, the width of the heat exchange tube exhaust channel is larger than the width of the heat exchange tube exhaust channel. The gap between the heat exchange tubes above the exhaust passages of the heat exchange tubes.
  • each of the first side heat exchange tube baffle device and the second side heat exchange tube baffle device includes an upper baffle and a lower baffle, and the upper baffle is provided at the place.
  • the lower baffle includes a main body section and an extension section, the main body section is arranged on one side of the second heat exchange tube group, and the extension section extends from the main body section It extends upward, and the extending section and the upper baffle at least partially overlap, and the baffle exhaust passage is formed between the upper baffle and the extending section.
  • each of the first side heat exchange tube baffle device and the second side heat exchange tube baffle device further comprises at least one transverse baffle, and the at least one transverse baffle is arranged at the In the baffle exhaust passage, the at least one transverse baffle extends transversely to the extending section of the lower baffle, and the at least one transverse baffle is provided with several openings to allow the gaseous refrigerant to pass through.
  • the number of the at least one transverse baffle is two, which are arranged along the extending direction of the exhaust passage of the baffle, and the openings on the two transverse baffles are arranged in a staggered manner.
  • the falling film heat exchange tube group of the evaporator in the present application has two parts with different numbers of columns, wherein the number of columns of the upper heat exchange tube group is greater than the number of columns of the lower heat exchange tube group.
  • a redistribution device is arranged between the two parts of the heat exchange tube groups, so that the heat exchange tubes of the lower heat exchange tube group can obtain a sufficient amount of liquid refrigerant flow.
  • the arrangement of the falling film heat exchange tube group in the present application can improve the heat exchange efficiency of the evaporator.
  • FIG. 1 is a schematic block diagram of a refrigeration system 100
  • FIG. 2 is a perspective view of the first embodiment of the evaporator 130 in FIG. 1;
  • Fig. 3 is a radial cross-sectional schematic diagram of the evaporator in Fig. 2;
  • FIG. 4 is a schematic diagram of the main distribution device 330 and part of the falling film heat exchange tube group 310 in FIG. 3;
  • FIG. 5 is a perspective view of the first embodiment of the redistribution device 350 in FIG. 3;
  • FIG. 6 is a top view of the second embodiment of the redistribution device 350 of FIG. 3;
  • Figure 7 is a schematic view of a radial cross-section of a second embodiment of the evaporator in the present application.
  • Fig. 8A is a partial enlarged view of part A in Fig. 7A;
  • FIG. 8B is a top view of the lower section of the first side upper baffle in FIG. 7;
  • FIG. 9A is a schematic diagram of a radial cross-section of a third embodiment of the evaporator in the present application.
  • Fig. 9B is a partial enlarged view of part B in Fig. 8A;
  • 10A is a partial enlarged view of a radial cross-sectional view of a fourth embodiment of an evaporator in the present application.
  • Figure 10B is a top view of the transverse baffle in Figure 10A;
  • FIG. 11 is a schematic radial cross-sectional view of a fifth embodiment of the evaporator in the present application.
  • first and second used in this application are only used for distinguishing and identifying, and do not have any other meanings. Unless otherwise specified, they do not represent a specific order or have a specific association. sex. For example, the term “first element” by itself does not imply the presence of a “second element,” nor does the term “second element” by itself imply the presence of a "first element.”
  • FIG. 1 is a schematic block diagram of a refrigeration system 100 .
  • the refrigeration system 100 includes a compressor 110 , a condenser 120 , a throttling device 140 and an evaporator 130 , which are connected by pipes to form a refrigerant circulation circuit, and the circuit is filled with refrigerant.
  • the refrigerant flows through the compressor 110 , the condenser 120 , the throttling device 140 and the evaporator 130 in sequence, and then enters the compressor 110 again.
  • the throttling device 140 throttles the high-pressure liquid refrigerant from the condenser 120 to reduce its pressure; the low-pressure refrigerant exchanges heat with the object to be cooled in the evaporator 130, absorbs the heat of the object to be cooled, and reduces its pressure. Evaporation; the refrigerant vapor produced by the vaporization is inhaled by the compressor 110, and discharged at high pressure after being compressed; the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 110 exchanges heat with the ambient medium in the condenser 120, releases heat and condenses into a liquid state Refrigerant; high temperature liquid refrigerant flows through the throttling device 140 again to reduce pressure. This cycle is repeated, resulting in a continuous cooling effect.
  • FIG. 2 is a perspective view of the first embodiment of the evaporator 130 in FIG. 1.
  • the evaporator 130 has a casing 201.
  • the casing 201 includes a cylindrical main body 204 and a pair of tube sheets 208 and 209.
  • the cylindrical body 204 is a cylindrical shape with two openings at both ends, and a pair of tube sheets 208 and 209 are respectively placed on both ends of the cylindrical body 204 to seal the openings at both ends of the cylindrical body 204 .
  • the cylindrical body 204 and the pair of tube sheets 208 and 209 enclose a cavity 305 (see FIG. 3 ), and the cavity 305 is used for accommodating the heat exchange tubes. Referring to the position shown in FIG.
  • the evaporator 130 has a height direction H, a length direction L and a width direction W, and the height direction, length direction and width direction of the cavity 305 are consistent with the direction of the evaporator 130 .
  • the cylindrical body 204 is provided with a refrigerant inlet 211 and a refrigerant outlet 212 , wherein the refrigerant inlet 211 and the refrigerant outlet 212 are both located at the upper part of the evaporator 130 in the height direction.
  • the liquid refrigerant or gas-liquid mixed refrigerant in the refrigeration system 100 enters the evaporator 130 from the refrigerant inlet 211 , absorbs heat in the evaporator 130 and becomes a gaseous refrigerant, and is discharged from the refrigerant outlet 212 .
  • FIG. 3 is a schematic diagram of a radial cross-section of the evaporator in FIG. 2.
  • a cavity 305 is formed inside the casing 201, and the cavity 305 is provided with a falling film heat exchange tube group 310 and a flooded heat exchange tube.
  • the refrigerant inlet 211 and the refrigerant outlet 212 are both above the casing 201 .
  • the refrigerant inlet 211 is located in the middle of the evaporator 130 in the length direction and the width direction, so as to facilitate the uniform distribution of the refrigerant.
  • the refrigerant outlet 212 and the refrigerant inlet 211 are staggered in the radial direction.
  • the main distribution device 330 is disposed above the falling film heat exchange tube group 310 and communicated with the refrigerant inlet 211 to distribute the refrigerant received by the refrigerant inlet 211 evenly and then send it to the falling film heat exchange tube group 310.
  • the mist eliminator 340 extends outward from the edge of the main dispensing device 330 until it connects with the inner wall of the housing 201 .
  • the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352 are respectively disposed on both sides of the falling film heat exchange tube group 310 .
  • the flooded heat exchange tube group 320 is disposed at the bottom of the cavity 305 and has a certain distance from the bottom of the falling film heat exchange tube group 310 .
  • the redistribution device 350 is provided in the falling film heat exchange tube group 310 .
  • the falling film heat exchange tube group 310 and the flooded heat exchange tube group 320 are heat exchange tube bundles formed by a plurality of heat exchange tubes arranged in sequence. Each heat exchange tube in the heat exchange tube bundle extends along the length direction L of the cavity 305 . A fluid channel is formed inside each heat exchange tube for the circulation of water or other media. The gap between each heat exchange tube and the adjacent heat exchange tube forms a refrigerant passage for circulating the refrigerant. The medium in the fluid channel exchanges heat with the refrigerant in the refrigerant channel through the tube wall of the heat exchange tube.
  • the flooded heat exchange tube group 320 is arranged upward from the inner wall of the bottom of the cavity shell 201 , and the flooded heat exchange tube group 320 has a top portion 312 and a bottom portion 313 .
  • the bottom portion 313 is substantially adjacent to and arranged along the inner wall of the housing 201, and the height of the top portion 312 is substantially the same.
  • the outline of the bottom 313 of the flooded heat exchange tube group 320 is approximately arc-shaped, the outline of the top 312 is approximately a horizontal straight line, and the two ends of the bottom 313 and the top 312 Connected at both ends.
  • the falling film heat exchange tube group 310 includes a first heat exchange tube group 301 and a second heat exchange tube group 302 , wherein the first heat exchange tube group 301 is disposed on the upper portion of the second heat exchange tube group 302 .
  • the second heat exchange tube group 302 is disposed above the flooded heat exchange tube group 320 and has a certain distance from the flooded heat exchange tube group 320, thereby forming a circulation space 361, so that the The gaseous refrigerant easily passes through the circulation space 361 .
  • the flooded heat exchange tube group is the third heat exchange tube group.
  • the heat exchange tubes in the first heat exchange tube group 301 and the second heat exchange tube group 302 are uniformly arranged in rows respectively, and the distances between the heat exchange tubes in each row and the heat exchange tubes in adjacent rows are equal.
  • the number of columns of heat exchange tubes in the first heat exchange tube group 301 is C1
  • the number of columns of heat exchange tubes in the second heat exchange tube group 302 is C2, wherein the number of columns C1 of heat exchange tubes in the first heat exchange tube group 301 is greater than that of the first heat exchange tube group 301.
  • the number of columns C2 of heat exchange tubes in the second heat exchange tube group 302 are uniformly arranged in rows respectively, and the distances between the heat exchange tubes in each row and the heat exchange tubes in adjacent rows are equal.
  • the number of columns of heat exchange tubes in the first heat exchange tube group 301 is C1
  • the number of columns of heat exchange tubes in the second heat exchange tube group 302 is C2 wherein the number of columns C1 of heat exchange tubes in the first heat exchange tube group 301 is greater than
  • the spacing between adjacent columns of the first heat exchange tube group 301 is equal to the spacing between adjacent columns of the second heat exchange tube group 302 , so that in the width direction of the cavity 305 , the maximum width of the first heat exchange tube group 301 is greater than the maximum width of the second heat exchange tube group 302 .
  • the first heat exchange tube group 301 includes an upper portion 341 of the first heat exchange tube group and a lower portion 342 of the first heat exchange tube group. In the width direction of the cavity 305 , the upper part 341 of the first heat exchange tube group and the second heat exchange tube group 302 are respectively the same width from top to bottom, and the width of the lower part 342 of the first heat exchange tube group is gradually width from top to bottom Zoom out.
  • the width of the top 316 of the lower part 342 of the first heat exchange tube group is equal to the width of the upper part 341 of the first heat exchange tube group, and the width of the bottom 317 of the lower part 342 of the first heat exchange tube group is equal to the width of the second heat exchange tube group 302 .
  • the outlines of the upper part 341 of the first heat exchange tube group and the outer sides of the second heat exchange tube group 302 are substantially planes extending along the vertical direction, and the outline of the lower part of the lower part 342 of the first heat exchange tube group
  • the outer contour forms an incline that slopes inward from top to bottom.
  • a first side heat exchange tube baffle device 351 and a second side heat exchange tube baffle device 352 are respectively provided on both sides of the falling film heat exchange tube group 310 .
  • the baffle device 351 and the second side heat exchange tube baffle device 352 are immediately adjacent to both sides of the falling film heat exchange tube group 310 in the width direction.
  • the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352 are arranged along the outer contour of the falling film heat exchange tube group 310 .
  • the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352 respectively include a first side upper baffle 381 and a second side upper baffle 382 located on both sides of the first heat exchange tube group 301 , And the first side lower baffle 383 and the second side lower baffle 384 located on both sides of the second heat exchange tube group 302 .
  • the first side upper baffle 381 includes the first side upper baffle upper section 385 and the first side upper baffle lower section 387 located on one side of the upper part 341 of the first heat exchange tube group
  • the second side upper baffle 382 includes the first side upper baffle plate 382.
  • the cavity 305 extends in the height direction and the length direction.
  • the distance between the upper section 385 of the first side upper baffle and the upper section 386 of the second upper side baffle is larger than the distance between the first lower baffle 383 and the second lower baffle 384 .
  • Both ends of the lower section 387 of the first side upper baffle are respectively connected to the upper section 385 of the first side upper baffle and the first lower baffle 383, and both ends of the lower section 388 of the second side upper baffle are respectively connected to the second upper baffle
  • the upper section 386 and the second side lower baffle 384 are connected such that the first side upper baffle lower section 387 and the second side upper baffle lower section 388 slope toward each other from top to bottom.
  • the side circulation space 360 is used to circulate the gaseous refrigerant.
  • the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352 are used to guide the refrigerant to flow from the first heat exchange tube group 301 to the second heat exchange tube group 302 from top to bottom, so as to The liquid refrigerant is prevented from entering the side flow space 360 .
  • the main distribution device 330 is arranged above the falling film heat exchange tube group 310 , and the redistribution device 350 is arranged between the first heat exchange tube group 301 and the second heat exchange tube group 302 .
  • the main distribution device 330 and the redistribution device 350 evenly distribute the liquid refrigerant to each row of heat exchange tubes.
  • the mist eliminator 340 extends from the outer edge of the main dispensing device 330 to connect with the inner wall of the housing 201 . Thereby, the mist eliminator 340 and the main distribution device 330 partition the chamber 305 into an upper space 391 and a lower space 392 .
  • the mist eliminator 340 is a mesh structure with a plurality of holes, and the upper space 391 and the lower space 392 are in fluid communication through the holes in the mist eliminator 340 .
  • the refrigerant outlet 212 and the refrigerant inlet 211 are both disposed on the casing 201 at the upper space 391 , and the refrigerant inlet 211 communicates with the main distribution device 330 .
  • FIG. 4 is a schematic diagram of the main distribution device 330 and part of the falling film heat exchange tube group 310 in FIG. 3 , as shown in FIG. , wherein the bottom plate 401 and the top plate 402 extend along the width and length directions of the cavity 305 , and a pair of side plates 403 and 404 extend along the height and length directions of the cavity 305 .
  • the bottom plate 401 , the side plate 403 , the top plate 402 and the side plate 404 are connected in sequence to form a chamber 408 .
  • the top plate 402 is provided with a guide tube hole 413 , one end of the guide tube 414 is communicated with the guide tube hole 413 , and the other end is communicated with the refrigerant inlet 211 .
  • the bottom plate 401 is provided with several rows of holes 419 , each row of holes 419 includes a plurality of holes, and the holes in each row of holes 419 are arranged along the extending direction of the heat exchange tubes.
  • the number of rows of holes on the bottom plate 401 is equal to the number of rows of the first heat exchange tube group 301 , and each row of holes 419 in the rows of holes 419 is aligned with a corresponding row of heat exchange tubes in the first heat exchange tube group 301 .
  • the liquid refrigerant entering the main distribution device 330 from the refrigerant inlet 211 flows along the length and width directions of the cavity 305 to be uniformly distributed on the bottom plate 401 .
  • the refrigerant in the main distribution device 330 flows to each corresponding row of heat exchange tubes in the first heat exchange tube group 301 through each row of holes 419 on the bottom plate.
  • the refrigerant is evenly distributed to each row of heat exchange tubes through the main distribution device 330 in liquid refrigerant entering from the refrigerant inlet 211 .
  • the number and area of holes on the bottom plate 401 are configured to match the flow rate of the refrigerant entering the evaporator 130, so that the refrigerant level in the main distribution device 330 is maintained within a certain range .
  • FIG. 5 is a perspective view of the first embodiment of the redistribution device 350 in FIG. 3 .
  • the redistribution device is a flat plate with a plurality of holes. Similar to the structure of the bottom plate 401 of the main distribution device 330 shown in FIG. 4 , the redistribution device 350 is provided with several rows of holes 519 , each row of holes 519 includes a plurality of holes, and the holes in each row of holes 519 are along the cavity.
  • the length direction of 305 that is, the extension direction of the heat exchange tube is arranged.
  • the number of rows of holes on the main distribution device 330 is equal to the number of rows of the second heat exchange tube group 302 (FIG.
  • each row of holes 519 in the number of rows of holes 519 is the same as the number of rows of holes 519 in the number of rows of holes 519.
  • a corresponding row of heat exchange tubes in a heat exchange tube group 301 is aligned.
  • the two ends 511 and 512 in the width direction of the redistribution device 350 are respectively connected with the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352, and the two ends 514 and 515 in the length direction are respectively connected. It is connected with the tube sheet to separate the first heat exchange tube group 301 and the second heat exchange tube group 302 .
  • the number and area of the holes on the redistribution device 350 are configured to match the flow rate of the liquid refrigerant after heat exchange by the first heat exchange tube group 301 , so that the refrigerant level of the liquid refrigerant on the redistribution device 350 is matched.
  • the height is kept within a certain range.
  • the ratio of the number of heat exchange tubes in the upper part 341 of the first heat exchange tube group, the lower part 342 of the first heat exchange tube group and the second heat exchange tube group is 492:184: 310.
  • the ratio of the number of columns between the upper part 341 of the first heat exchange tube group and the lower part 342 of the first heat exchange tube group is 37:23.
  • the liquid refrigerant enters the main distribution device 330 from the refrigerant inlet 211 , and then enters the first heat exchange tube group 301 for heat exchange after being evenly distributed by the main distribution device 330 .
  • the first heat exchange tube group 301 a part of the liquid refrigerant undergoes heat exchange and becomes a gaseous refrigerant, and a part of the liquid refrigerant continues to flow downward.
  • the amount of liquid refrigerant at the bottom of the first heat exchange tube group 301 is less than the amount of liquid refrigerant at the top of the first heat exchange tube group 301, the first The liquid refrigerant at the bottom of the heat exchange tube group 301 is redistributed by the redistribution device 350 and then enters the second heat exchange tube group 302 for heat exchange.
  • the second heat exchange tube group 302 continues to convert a part of the liquid refrigerant into a gaseous refrigerant, while the other part of the refrigerant is still in liquid state, and the liquid refrigerant enters the flooded heat exchange tube group 320 to continue heat exchange.
  • the liquid refrigerant in the falling film heat exchange tube group 310 flows from bottom to bottom, and is blocked by the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352, and cannot spread to the side Circulation space 360.
  • a part of the refrigerant is converted into gaseous refrigerant.
  • the gaseous refrigerant generated by the heat exchange between the falling film heat exchange tube group 310 and the flooded heat exchange tube group 320 flows out from the refrigerant outlet 212 in sequence through the circulation space 361 , the side circulation space 360 , the mist eliminator 340 and the upper space 391 .
  • the mist eliminator 340 can remove small droplets mixed in the gaseous refrigerant.
  • gaseous refrigerant mentioned in this article means that the gas in the refrigerant accounts for the vast majority, and it is not excluded that the gaseous refrigerant contains a small amount of droplets.
  • the heat exchange tubes in the flooded heat exchange tube group 320 are submerged by the refrigerant liquid, and the height of the refrigerant liquid is approximately equal to the height of the flooded heat exchange tube group 320 during the operation of the evaporator.
  • the number of columns of the first heat exchange tube group 301 matches the flow rate of the liquid refrigerant distributed by the main distribution device 330
  • the number of columns of the second heat exchange tube group 302 is matched with the flow rate of the liquid refrigerant distributed by the redistribution device 350 .
  • the flow of liquid refrigerant is matched.
  • the falling film heat exchange tube group 310 is provided as two sections with different numbers of columns, which is beneficial to improve the heat exchange efficiency of the evaporator 130 .
  • FIG. 6 is a top view of a second embodiment of the redistribution device 350 of FIG. 3, similar to the embodiment shown in FIG. 5, except that the diameters in each row of holes on the redistribution device 350 are different.
  • the holes in the redistribution device 350 have multiple rows in the width direction, and each hole in each row of holes has the same diameter, but a different diameter from the holes of the other rows.
  • the diameter of each hole in the row of holes 621 located in the middle in the width direction is the largest, and the diameter of each hole in the two rows of holes 625 and 626 located on both sides in the width direction is the smallest.
  • the diameter of each hole in each row of holes is gradually reduced from the middle to both sides in the width direction.
  • the width of the lower part 342 of the first heat exchange tube group is gradually narrowed, and the lower sections of the first side upper baffle plate matching the shape of the lower part of the first heat exchange tube group are provided on both sides of the lower part 342 of the first heat exchange tube group 387 and the second side upper baffle lower section 388, the first side upper baffle lower section 387 and the second side upper baffle lower section 388 are inclined inwardly inclined surfaces.
  • the flow rate of liquid refrigerant at both sides of the bottom of the first heat exchange tube group lower part 342 is larger than that of the first heat exchange tube group
  • both the gaseous and liquid refrigerants generated by the first heat exchange tube group 301 flow to the second heat exchange tube group 302 .
  • the liquid refrigerant generated by the first heat exchange tube group 301 can continue to exchange heat in the second heat exchange tube group 302, while the gaseous refrigerant basically no longer participates in heat exchange.
  • the gaseous refrigerant generated in the first heat exchange tube group 301 is discharged in time, which is beneficial to improve the heat exchange efficiency of the second heat exchange tube group 302 .
  • FIG. 7 is a schematic radial cross-sectional view of the second embodiment of the evaporator in the present application
  • FIG. 8A is a partial enlarged view of part A in FIG. 7A
  • FIG. 8B is a top view of the lower section of the first side upper baffle in FIG. 7 .
  • the first heat exchange tube group 301 in FIG. 7 has a heat exchange tube exhaust passage 729 , a first side heat exchange tube baffle device 351 and a second side heat exchange tube baffle device 351 .
  • the heat pipe baffle device 352 is provided with a baffle exhaust passage.
  • the first side heat exchange tube baffle device 351 and the second side heat exchange tube baffle device 352 of the evaporator 700 respectively include two Side first side upper baffle lower section 787 and second side upper baffle lower section 788.
  • the first side upper baffle lower section 787 and the second side upper baffle lower section 788 are respectively provided with a plurality of exhaust holes 705 , and each exhaust hole 705 in the plurality of exhaust holes 705 forms a baffle exhaust channel 708 .
  • the baffle exhaust passage 708 can discharge the gaseous refrigerant generated in the first heat exchange tube group 701 in time.
  • each of the several exhaust holes 705 is located from the upper part 741 of the first heat exchange tube group.
  • a long strip is formed in the direction of the second heat exchange tube group 302 .
  • the plurality of elongated exhaust holes 705 are used to prevent excessive liquid refrigerant from flowing into the circulation space 760 from the exhaust holes 705 .
  • the first heat exchange tube group 701 is provided with a heat exchange tube exhaust passage 729, and the heat exchange tube exhaust passage rises from both sides of the lower part 742 of the first heat exchange tube group and faces the first heat exchange tube group.
  • the central interface in the width direction of the heat exchange tube group 701 extends obliquely.
  • the width of the heat exchange tube exhaust passage 729 is larger than the gap between the heat exchange tubes above the heat exchange tube exhaust passage 729 .
  • the heat exchange tube exhaust channel 729 is formed by vacating several heat exchange tubes along the extension direction of the heat exchange tube exhaust channel 729, then the width of the heat exchange tube exhaust channel 729 slightly larger than the diameter of the heat exchange tube.
  • the gaseous refrigerant generated in the first heat exchange tube group 701 can enter the baffle exhaust passage 708 through the heat exchange tube exhaust passage 729 .
  • the heat exchange tube exhaust passage 729 and the baffle exhaust passage 708 facilitate the rapid discharge of gaseous refrigerant to the circulation space 760, so as to avoid excessive gaseous refrigerant from entering the second heat exchange tube group 702 and impacting the second heat exchange tube
  • the refrigerant liquid film on the group 702 affects the heat exchange efficiency of the second heat exchange tube group 702 .
  • the vibration caused by the impact of the gaseous refrigerant on the second heat exchange tube group 702 is reduced.
  • FIG. 9A is a schematic diagram of a radial cross-section of the third embodiment of the evaporator in the present application
  • FIG. 9B is a partial enlarged view of part B in FIG. 9A . Similar to the embodiment shown in FIG. 7 , the difference is the arrangement of the baffle exhaust passages.
  • the first side heat exchange tube baffle device 951 includes a first side upper baffle 971 and a first side lower baffle 972
  • the second side heat exchange tube baffle device 952 includes a second side baffle Upper baffle 973 and lower baffle 974.
  • the first side upper baffle 971 includes an upper section 981 and a lower section 982
  • the second side upper baffle 973 includes an upper section 983 and a lower section 984 .
  • the upper sections 981 and 983 are arranged on both sides of the upper part 941 of the first heat exchange tube group
  • the lower sections 982 and 984 are arranged on both sides of the lower part 942 of the first heat exchange tube group.
  • the first side lower baffle 972 includes a main body section 985 and an extension section 986
  • the lower baffle 974 includes a main body section 987 and an extension section 988 .
  • the main body section 985 and the main body section 987 are arranged on both sides of the second heat exchange tube group 902, and the extension section 986 and the extension section 988 are respectively from the tops of the main body section 985 and the main body section 987 along the direction substantially parallel to the lower section 982 and the lower section 984, respectively. The direction goes up and out.
  • the extension section 986 and the extension section 988 exceed the bottoms of the lower section 982 and the lower section 984 in the height direction of the cavity 305 so as to at least partially overlap the first side upper baffle 971 and the second side upper baffle 973 .
  • the gaseous refrigerant generated in the first heat exchange tube group 901 can be discharged through the exhaust passage 908 and the exhaust passage 909 .
  • the liquid refrigerant in this embodiment is less likely to flow out of the exhaust passages 908 and 909 .
  • FIG. 10A is a partial enlarged view of a radial cross-sectional view of a fourth embodiment of the evaporator in the present application
  • FIG. 10B is a top view of the transverse baffle in FIG. 10A
  • the baffle exhaust passage in FIG. 10A also includes a transverse baffle.
  • an exhaust passage 1008 is formed between the extending section 1087 of the lower baffle 1072 and the lower section 1082 of the upper baffle 1071 , and transverse baffles 1001 and 1002 are arranged in the exhaust passage 1008 .
  • the transverse baffles 1001 and 1002 extend transversely to the extension 1087 of the lower baffle 1072 , that is to say, the transverse baffles 1001 and 1002 are perpendicular to the extension 1087 of the lower baffle 1072 , or between the extension 1087 of the lower baffle 1072 form a certain angle. As shown in FIG.
  • the transverse baffles 1001 and 1002 have a plurality of openings 1009 which are capable of allowing the passage of bulk refrigerant.
  • the opening 1009 may be a hole passing through the lateral baffles 1001 and 1002, or a concave portion formed by indenting one side edge of the lateral baffles 1001 and 1002 inward.
  • the openings 1009 of the transverse baffle 1001 and the openings 1009 of the transverse baffle 1002 are arranged alternately, so that the gaseous refrigerant can pass through smoothly, and most of the liquid refrigerant can be blocked by the transverse baffles 1001 and 1002 .
  • this embodiment can further prevent the liquid refrigerant from flowing out of the baffle exhaust passage.
  • FIG. 11 is a schematic diagram of a radial cross-section of the fifth embodiment of the evaporator in the present application, which is similar to the embodiment shown in FIG. 3 except for the widths of the first heat exchange tube group 1101 and the second heat exchange tube group 1102 same.
  • the first heat exchange tube group 1101 and the second heat exchange tube group 1102 respectively have uniform widths
  • the second heat exchange tube group 1102 is disposed at the lower part of the first heat exchange tube group 1101 .
  • the widths of the first heat exchange tube group 1101 and the second heat exchange tube group 1102 are substantially the same.
  • the number of columns of the first heat exchange tube group 1101 is less than the number of columns of the second heat exchange tube group 1102 , that is to say, in the width direction of the cavity 305 , the heat exchange tubes in the first heat exchange tube group 1101 are smaller than those in the second heat exchange tube group 1101 .
  • the heat exchange tubes in the second heat exchange tube group 1102 are arranged more densely.
  • the number and position of the holes on the redistribution device 1150 correspond to the second heat exchange tube group 1102 , and the liquid refrigerant can also be uniformly distributed into the second heat exchange tube group 1102 , achieving the technology of the embodiment shown in FIG. 3 . Effect.
  • the upper baffle 1171 and the lower baffle 1172 both extend in the vertical direction, and the lower section 1182 of the upper baffle 1171 and the extension section 1186 of the lower baffle 1172 are in the height direction of the cavity 305
  • the upper part overlaps, and transverse baffles 1111 and 1112 are arranged between the baffle exhaust passages 1108, which can also achieve the technical effect shown in the embodiment of FIG. 10A.
  • the falling film heat exchange tube group, the baffle device with the first side heat exchange tube and the second side heat exchange tube baffle device are all symmetrical with respect to the central interface in the width direction of the cavity .
  • the falling film heat exchange tube group, the baffle device of the first side heat exchange tube and the baffle device of the second side heat exchange tube may also be asymmetric with respect to the central interface in the width direction of the cavity, It is only necessary that the number of columns of the first heat exchange tube group in the falling film heat exchange tube group is greater than the number of columns of the second heat exchange tube group.
  • the first side of the second heat exchange tube group is flush with the first side of the first heat exchange tube group
  • the second side of the second heat exchange tube group is flush with the first heat exchange tube group
  • the second side of the group is staggered.
  • the refrigerant liquid entering the evaporator from the refrigerant inlet is distributed by the main distribution device and evenly distributed to the surface of the heat exchange tube at the top of the falling film heat exchange tube group to form a liquid film for heat exchange.
  • Part of the liquid refrigerant is transformed into a gaseous state after evaporation and heat exchange, and the other part of the unevaporated liquid refrigerant will drip onto the lower heat exchange tubes and continue to evaporate.
  • the top to bottom of the heat exchange tube group gradually decreases.
  • the relationship between the falling film evaporation heat transfer coefficient " hr " and the liquid refrigerant flow rate "m 1 " flowing through the falling film heat exchange tube is as follows: when the liquid refrigerant flow rate is greater than the critical flow rate "m 2 ", The falling-film evaporation heat transfer coefficient " hr " basically does not change with the flow of liquid refrigerant. When the liquid refrigerant flow is less than the critical flow "m 2 ", the falling-film evaporation heat transfer coefficient " hr " decreases with the flow of liquid refrigerant. and decay rapidly.
  • the flow rate of the liquid refrigerant at the heat exchange tube at the bottom of the falling film heat exchange tube group will reach the critical flow "m 2 ". And a certain proportion of flooded heat exchange tube bundles will be set at the bottom of the evaporator to exchange heat with the liquid refrigerant at the bottom of the falling film heat exchange tube group.
  • the refrigerant needs to submerge the flooded heat exchange tube bank.
  • the number of columns of falling film heat exchange tube groups is uniform.
  • the ratio of heat exchange tubes in the falling film heat exchange tube group and the flooded heat exchange tube group is usually 1:1.
  • the falling film heat exchange tube group includes two parts with different numbers of columns. After the first heat exchange tube group exchanges heat with the liquid refrigerant, a part of the liquid refrigerant is converted into gas, and the heat exchange tube at the heat exchange tube is converted into gas. The flow of liquid refrigerant gradually decreases from top to bottom. The liquid refrigerant flow rate of the heat exchange tubes at the bottom of the first heat exchange tube group has reached the critical flow rate "m 2 ".
  • the liquid refrigerant flow rate at the increased heat exchange tubes will be less than the critical flow rate “m 2 ”, which will result in an increased heat exchange rate.
  • the falling film evaporation heat transfer coefficient " hr " of the heat pipe decreases, which affects the heat transfer efficiency of the evaporator. Therefore, in the present application, a redistribution device and a second heat exchange tube group with fewer columns are added to continue heat exchange for the liquid refrigerant at the bottom of the first heat exchange tube group.
  • the redistribution device collects the liquid refrigerant at the bottom of the first heat exchange tube group and distributes it again, and the number of rows of holes in the redistribution device corresponds to the number of columns of the second heat exchange tube group. Since the number of columns of the second heat exchange tube group is less than the number of columns of the first heat exchange tube group, the liquid refrigerant flow rate of the heat exchange tubes at the top of the second heat exchange tube group will be greater than that at the bottom of the first heat exchange tube group The flow rate of the heat exchange tube, that is to say, the liquid refrigerant flow rate of the heat exchange tube at the top of the second heat exchange tube group exceeds the critical flow "m 2 ", and the second heat exchange tube group can maintain a high falling film evaporation exchange rate. The heat coefficient " hr ", so that the second heat exchange tube group can also maintain a high heat exchange efficiency.
  • the flooded heat exchange tube group is used to exchange heat for the refrigerant that has not been vaporized after being exchanged by the falling film heat exchange tube group.
  • the heat exchange coefficient of the heat exchange tubes of the flooded heat exchange tube group is smaller than that of the falling film heat exchange tube group.
  • the heat transfer coefficient of the heat pipe is conducive to improving the efficiency of the evaporator. heat transfer efficiency.
  • the falling film heat exchange tube group by arranging the falling film heat exchange tube group to include two sections with different numbers of columns, and disposing the redistribution device at the same time, when the flow rate of the heat exchange tubes at the bottom of the first heat exchange tube group has reached the critical flow rate,
  • the refrigerant is redistributed through the reassembly device, thereby increasing the flow of liquid refrigerant at each row of heat exchange tubes in the second heat exchange tube group, thereby satisfying the flow of liquid refrigerant in the heat exchange tubes in the second heat exchange tube group Greater than or equal to the critical flow "m 2 ".
  • the flow rate at each heat exchange tube is close to or equal to the critical flow rate.
  • the evaporator in this application has fewer columns of heat exchange tubes in the second heat exchange tube group compared with the traditional evaporator, so The total amount of liquid refrigerant at the bottom of the second group of heat exchange tube groups is less, thereby reducing the required number of heat exchange tubes in the flooded heat exchange tube group.
  • the ratio of the number of heat exchange tubes in the falling film heat exchange tube group to the total number of heat exchange tubes in the present application is larger, so the evaporator in the present application has higher heat exchange efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Organic Chemistry (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Manufacture And Refinement Of Metals (AREA)

Abstract

本申请提供一种蒸发器，包括：壳体、第一换热管组、第二换热管组、第一侧换热管挡板装置、第二侧换热管挡板装置和再分配装置，所述第一换热管组位于所述第二换热管组上方，所述第一换热管组的列数大于所述第二换热管组的列数；所述第一侧换热管挡板装置和第二侧换热管挡板装置分别设置在所述第一换热管组和所述第二换热管组的相对的两侧，并沿着所述第一换热管组和所述第二换热管组的外轮廓布置，以引导制冷剂从所述第一换热管组流向第二换热管组；所述再分配装置设置在第一换热管组和第二换热管组之间，以向第二换热管组均匀地分配制冷剂。本申请中的蒸发器具有较高的换热效率。

Description

蒸发器 技术领域
本申请涉及一种蒸发器，尤其是涉及一种换热效率高的蒸发器。
背景技术
传统的制冷系统具有蒸发器、冷凝器、节流装置和压缩机。低温的制冷剂液体通过蒸发器时，与外界进行热量交换，吸收外界的热量，从而降低外界温度，达到制冷的效果，外界可以为空气，也可以为冷却水。换热后制冷剂液体气化变为气态制冷剂进入压缩机。蒸发器的换热效率受到多方面因素影响。
发明内容
本申请提供一种蒸发器，该蒸发器的换热效率较高。
本申请中的蒸发器，包括：壳体、第一换热管组和第二换热管组、第一侧换热管挡板装置和第二侧换热管挡板装置以及再分配装置，所述壳体具有容腔，所述容腔具有长度方向、宽度方向和高度方向；第一换热管组和第二换热管组中的换热管沿着所述容腔的长度方向延伸，并且沿着所述容腔的宽度方向和高度方向排布，所述第一换热管组位于所述第二换热管组上方，其中，在所述容腔的宽度方向上，所述第一换热管组的列数大于所述第二换热管组的列数；所述第一侧换热管挡板装置和第二侧换热管挡板装置在所述容腔的宽度方向上分别设置在所述第一换热管组和所述第二换热管组的相对的两侧，并沿着所述第一换热管组和所述第二换热管组的外轮廓布置；所述再分配装置设置在第一换热管组和第二换热管组之间，并且所述再分配装置在所述容腔的宽度方向上的两端分别与所述第一侧换热管挡板装置和第二侧换热管挡板装置连接，其中，所述再分配装置沿着所述容腔的长度方向延伸以覆盖所述第二换热管组的顶部，并与所述第一换热管组下部之间具有一定间距，所述再分配装置上设有数排孔，所述数排孔中的每一 排孔沿着所述换热管的延伸方向布置，所述数排孔中的每排孔与第二换热管组中相应的一列换热管对齐。
如上所述的蒸发器，所述第一换热管组和所述第二换热管组分别相对于所述容腔的沿高度方向延伸的中心分界面对称布置。
如上所述的蒸发器，所述第一换热管组和所述第二换热管组的宽度相同。
如上所述的蒸发器，所述第一换热管组具有第一换热管组上部和第一换热管组下部，在所述容腔的宽度方向上，第一换热管组上部的宽度大于所述第二换热管组的宽度。
如上所述的蒸发器，所述第一换热管组下部的宽度自上而下逐渐缩小，第一换热管组下部的顶部的宽度与所述第一换热管组上部的宽度相同，所述第一换热管组下部的底部与所述第二换热管组的宽度相同。
如上所述的蒸发器，在所述容腔的宽度方向上，所述再分配装置上的数个孔的尺寸从所述再分配装置的中间向两侧逐渐缩小。
如上所述的蒸发器，还包括：第三换热管组，所述第三换热管组位于所述容腔的底部，并位于所述第二换热管组的下方，所述第三换热管组与所述第二换热管组之间具有一定间距以形成流通空间，从而使得从第二换热管组流出的气态制冷剂能够通过所述流通空间流向设置在所述壳体上的制冷剂出口。
如上所述的蒸发器，所述第一侧换热管挡板装置和第二侧换热管挡板装置分别包括至少一个挡板排气通道，在所述容腔的高度方向上，所述挡板排气通道位于第二换热管组上方，所述至少一个挡板排气通道被配置为将所述第一换热管组中的气态制冷剂排出。
如上所述的蒸发器，所述第一侧换热管挡板装置和第二侧换热管挡板装置分别包括第一侧上部挡板下段和第二侧上部挡板下段，所述第一侧上部挡板下段和第二侧上部挡板下段设置在所述第一换热管组下部的两侧，所述第一侧上部挡板下段和第二侧上部挡板下段上分别设有数个排气孔，所述数个排气孔中的每个排气孔形成一个挡板排气通道，所述数个排气孔沿着所述容腔的长度方向排列，所 述数个排气孔中的每个排气孔在从所述第一换热管组上部向所述第二换热管组的方向上形成长条状。
如上所述的蒸发器，所述第一换热管组具有换热管排气通道，所述换热管排气通道形成在第一换热管组的换热管之间，所述换热管排气通道从所述第一换热管组下部的两侧向内并向上延伸，在所述容腔的垂直于长度方向的截面上，所述换热管排气通道的宽度大于所述换热管排气通道上方的换热管之间的间隙。
如上所述的蒸发器，所述第一侧换热管挡板装置和第二侧换热管挡板装置中的每一个包括上部挡板和和下部挡板，所述上部挡板设置在所述第一换热管组的一侧，所述下部挡板包括主体段和延伸段，所述主体段设置在所述第二换热管组的一侧，所述延伸段自所述主体段段向上延伸，并且所述延伸段和所述上部挡板至少部分地重叠，所述上部挡板和所述延伸段之间形成所述挡板排气通道。
如上所述的蒸发器，所述第一侧换热管挡板装置和第二侧换热管挡板装置中的每一个还包括至少一个横向挡板，所述至少一个横向挡板设置在所挡板排气通道中，所述至少一个横向挡板横向于下部挡板的延伸段延伸，所述至少一个横向挡板上设有数个开口，以使得气态制冷剂能够通过。
如上所述的蒸发器，所述至少一个横向挡板的数量为两个，并沿着挡板排气通道的延伸方向布置，所两个横向挡板上的开口交错布置。
本申请中的蒸发器的降膜换热管组具有列数不同的两部分，其中上部换热管组的列数大于下部换热管组的列数。在两部分换热管组之间设有再分配装置，以使得下部换热管组的换热管的能够获得足量的液态制冷剂流量。本申请中的降膜换热管组的设置能够提高蒸发器的换热效率。
附图说明
图1是制冷系统100的示意框图；
图2是图1中蒸发器130的第一实施例立体图；
图3是图2中蒸发器的一个径向截面示意图；
图4是图3中主分配装置330和部分降膜换热管组310示意图；
图5是图3中再分配装置350第一实施例的立体图；
图6是图3中再分配装置350的第二实施例的俯视图；
图7是本申请中蒸发器的第二实施例的径向截面示意图；
图8A是图7A中A部的局部放大图；
图8B是图7中第一侧上部挡板下段的俯视图；
图9A是本申请中蒸发器的第三实施例的径向截面示意图；
图9B是图8A中B部的局部放大图；
图10A是本申请中蒸发器的第四实施例的径向截面图的局部放大图；
图10B是图10A中横向挡板的俯视图；
图11是本申请中蒸发器的第五实施例的径向截面示意图。
具体实施方式
下面将参考构成本说明书一部分的附图对本申请的各种具体实施方式进行描述。应该理解的是，虽然在本申请中使用表示方向的术语，诸如“前”、“后”、“上”、“下”、“左”、“右”、“内”、“外”、“顶”、“底”、“正”、“反”、“近端”、“远端”、“横向”、“纵向”等描述本申请的各种示例结构部分和元件，但是在此使用这些术语只是为了方便说明的目的，这些术语是基于附图中显示的示例性方位而确定的。由于本申请所公开的实施例可以按照不同的方向设置，所以这些表示方向的术语只是作为说明而不应视作为限制。
本申请中所使用的诸如“第一”和“第二”等序数词仅仅用于区分和标识，而不具有任何其他含义，如未特别指明则不表示特定的顺序，也不具有特定的关联性。例如，术语“第一部件”本身并不暗示“第二部件”的存在，术语“第二部件”本身也不暗示“第一部件”的存在。
图1是制冷系统100的示意框图。如图1所示，制冷系统100包括压缩机110、冷凝器120、节流装置140和蒸发器130，它们由管道连接成一个制冷剂循环回路，并在回路中充注有制冷剂。如图1中的箭头方向所示，制冷剂依次流经压缩机110、冷凝器120、节流装置140和蒸发器130，再次进入压缩机110。在制冷过程中，节流装置140将由冷凝器120来的高压液态制冷剂节流，使其压力降低；低压制冷剂在蒸发器130内与被冷却对象发生热交换，吸收被冷却对象的热量而汽化；汽化产生的制冷剂蒸汽被压缩机110吸入，经压缩后以高压排出；压缩机110排出的高温高压气态制冷剂在冷凝器120内与环境介质进行热交换，释放出热量并凝结成液态制冷剂；高温液态制冷剂再次流经节流装置140而降压。如此周而复始，产生连续制冷效应。
图2是图1中蒸发器130的第一实施例立体图，如图2所示，蒸发器130具有壳体201，壳体201包括圆筒形的主体204和一对管板208和209，圆筒形主体204为两端开口的筒状，一对管板208和209分别置在圆筒形的主体204的两端，以封住圆筒形主体204两端的开口。圆筒形的主体204和一对管板208和209围成容腔305(参见图3)，容腔305用于容纳换热管。参见图2中所示的位置，蒸发器130具有高度方向H，长度方向L和宽度方向W，容腔305的高度方向，长度方向和宽度方向与蒸发器130的方向一致。圆筒形的主体204上设有制冷剂入口211和制冷剂出口212，其中制冷剂入口211和制冷剂出口212均位于蒸发器130的高度方向上的上部。制冷系统100中的液态制冷剂或气液混合制冷剂从制冷剂入口211进入蒸发器130，在蒸发器130中吸热后变为气态制冷剂，由制冷剂出口212排出。
图3是图2中蒸发器的一个径向剖面示意图，如图3所示，壳体201的内部形成容腔305，容腔305内设有降膜换热管组310、满液换热管组320、主分配装置330、除雾器340、再分配装置350、第一侧换热管挡板装置351和第二侧换热管挡板装置352。结合图2和图3所示，制冷剂入口211和制冷剂出口212均在壳体201的上方。其中，制冷剂入口211位于蒸发器130的长度方向和宽度方向上的中部，以利于制冷剂的均匀分配。制冷剂出口212和制冷剂入口211在径向方向上错开布置。主分配装置330设置在降膜换热管组310的上方，并与制 冷剂入口211连通，以将从而制冷剂入口211接收到的制冷剂均匀分配后送入降膜换热管组310。除雾器340自主分配装置330的边缘向外延伸直至与壳体201的内壁连接。第一侧换热管挡板装置351和第二侧换热管挡板装置352分别设置在降膜换热管组310的两侧。满液换热管组320设置在容腔305的底部，并与降膜换热管组310的底部之间具有一定间距。再分配装置350设置在降膜换热管组310中。
降膜换热管组310和满液换热管组320分别是由多根换热管依次排列形成的换热管束。换热管束中的每个换热管沿着容腔305的长度方向L延伸。每个换热管内部形成流体通道，用于流通水或其它介质。每个换热管与相邻的换热管之间的间隙形成制冷剂通道，用于流通制冷剂。流体通道内的介质与制冷剂通道内的制冷剂通过换热管的管壁进行热量交换。满液换热管组320由容腔壳体201的底部的内壁向上排列，满液换热管组320具有顶部312和底部313。底部313大致紧邻并沿着壳体201的内壁布置，顶部312的高度基本一致。从蒸发器130的一个径向截面上看去，满液换热管组320的底部313的轮廓大致为圆弧形，顶部312的轮廓大致为水平的直线，底部313的两端与顶部312的两端相接。
降膜换热管组310包括第一换热管组301和第二换热管组302，其中第一换热管组301设置在第二换热管组302的上部。在容腔305的宽度方向上，第二换热管组302设置在满液换热管组320上方，并与满液换热管组320之间具有一定间距，从而形成流通空间361，以使得气态制冷剂易于从流通空间361通过。在本申请中，满液换热管组即为第三换热管组。第一换热管组301和第二换热管组302中的换热管分别按列均匀布置，每一列换热管与相邻列的换热管之间的间距相等。第一换热管组301换热管的列数为C1，第二换热管组302中换热管的列数为C2，其中第一换热管组301换热管的列数C1大于第二换热管组302中换热管的列数C2。在本实施例中，第一换热管组301的相邻的列之间的间距与第二换热管组302的相邻的列之间的间距相等，从而在容腔305的宽度方向上，第一换热管组301的最大宽度大于第二换热管组302的最大宽度。其中，第一换热管组301包括第一换热管组上部341和第一换热管组下部342。在容腔305的宽度方向上，第一换热管组上部341和第二换热管组302分别自上而下为同一宽度， 第一换热管组下部342的宽度自上而下宽度逐渐缩小。第一换热管组下部342的顶部316的宽度与第一换热管组上部341的宽度相等，第一换热管组下部342的底部317的宽度与第二换热管组302的宽度相等。在容腔305的宽度方向上，第一换热管组上部341和第二换热管组302的外侧的轮廓大致为沿着竖直方向延伸的平面，第一换热管组下部342下部的外侧轮廓形成自上而下向内倾斜的斜面。
在容腔305的宽度方向上，降膜换热管组310的两侧分别设有第一侧换热管挡板装置351和第二侧换热管挡板装置352，第一侧换热管挡板装置351和第二侧换热管挡板装置352紧邻降膜换热管组310在宽度方向上的两侧。第一侧换热管挡板装置351和第二侧换热管挡板装置352沿着降膜换热管组310的外轮廓布置。第一侧换热管挡板装置351和第二侧换热管挡板装置352分别包括位于第一换热管组301两侧的第一侧上部挡板381和第二侧上部挡板382，以及位于第二换热管组302两侧的第一侧下部挡板383和第二侧下部挡板384。第一侧上部挡板381包括位于第一换热管组上部341一侧的第一侧上部挡板上段385和第一侧上部挡板下段387，第二侧上部挡板382包括位于第一换热管组上部341另一侧的第二侧上部挡板上段386和第二侧上部挡板下段388。与降膜换热管组310的外轮廓一致，第一侧上部挡板上段385、第二侧上部挡板上段386、第一侧下部挡板383和第二侧下部挡板384分别沿着容腔305高度方向和长度方向延伸。第一侧上部挡板上段385和第二侧上部挡板上段386之间的间距大于第一侧下部挡板383和第二侧下部挡板384之间的间距。第一侧上部挡板下段387的两端分别与第一侧上部挡板上段385和第一侧下部挡板383连接，第二侧上部挡板下段388的两端分别与第二侧上部挡板上段386和第二侧下部挡板384连接，从而第一侧上部挡板下段387和第二侧上部挡板下段388自上而下朝向彼此倾斜。
第一侧换热管挡板装置351和第二侧换热管挡板装置352与降膜换热管组310存在较小的间隙。第一侧换热管挡板装置351和第二侧换热管挡板装置352与壳体201之间具有间距，以形成侧部流通空间360。侧部流通空间360用于流通气态制冷剂。第一侧换热管挡板装置351和第二侧换热管挡板装置352用于引导制冷剂自上而下从所述第一换热管组301流向第二换热管组302，以避免液态制冷剂进入侧部流通空间360。
主分配装置330设置在降膜换热管组310的上方，再分配装置350设置在第一换热管组301和第二换热管组302之间。主分配装置330和再分配装置350将液态的制冷剂均匀分配至每列换热管。除雾器340自主分配装置330的外侧边缘延伸至与壳体201的内壁连接。从而除雾器340和主分配装置330将容腔305分隔成上部空间391和下部空间392。除雾器340为具有多个孔的网状结构，上部空间391和下部空间392通过除雾器340上的孔流体连通。其中制冷剂出口212和制冷剂入口211设置均在上部空间391处的壳体201上，制冷剂入口211与主分配装置330连通。
图4是图3中主分配装置330和部分降膜换热管组310示意图，如图4所示，主分配装置330包括底板401，顶板402、一对侧板403和404和导流管414，其中底板401，顶板402沿着容腔305的宽度方向和长度方向延伸，一对侧板403和404沿着容腔305的高度和长度方向延伸。底板401、侧板403、顶板402和侧板404依次连接，围成腔室408。顶板402上设有导流管孔413，导流管414的一端与导流管孔413连通，另一端与制冷剂入口211连通。底板401上设有数排孔419，每一排孔419包含多个孔，每一排孔419中的孔沿着所述换热管的延伸方向布置。底板401上的孔的排数与第一换热管组301的列数相等，并且数排孔419中的每排孔419与第一换热管组301中相应的一列换热管对齐。从制冷剂入口211进入主分配装置330的液态制冷剂沿着容腔305的长度方向和宽度方向流动从而均匀分布在底板401上。主分配装置330中的制冷剂通过底板上的每排孔419流向第一换热管组301中相应的每一列换热管。制冷剂通过主分配装置330将从制冷剂入口211进入的液态制冷剂均匀地分配到每一列换热管。在本申请的一些实施例中，底板401上的孔的数量和面积被配置为与进入蒸发器130的制冷剂的流速匹配，以使得主分配装置330中的制冷剂液位高度保持在一定范围。
图5是图3中再分配装置350第一实施例的立体图，如图5所示，再分配装置为具有多个孔的平板。与图4中所示的主分配装置330的底板401的结构类似，再分配装置350设有数排孔519，每一排孔519包含多个孔，每一排孔519中的孔沿着容腔305的长度方向，也就是换热管的延伸方向布置。主分配装置330 上的孔的排数与第二换热管组302的列数相等(图5为示意性视图，仅示了一部分孔)，并且数排孔519中的每排孔519与第一换热管组301中相应的一列换热管对齐。再分配装置350的宽度方向上的两端511和512分别与第一侧换热管挡板装置351和第二侧换热管挡板装置352连接，其长度方向上的两端514和515分别与管板连接，从而将第一换热管组301和第二换热管组302分隔开。再分配装置350上的孔的数量和面积被配置为与经第一换热管组301换热后的液态制冷剂的流速匹配，以使得液态制冷剂在再分配装置350上的制冷剂液位高度保持在一定范围。
在图3所示的实施例的一种应用中，第一换热管组上部341、第一换热管组下部342和第二换热管组中的换热管数量比为492:184:310。第一换热管组上部341和第一换热管组下部342的列数比为37：23。
在图3所示的实施例中，液态制冷剂从制冷剂入口211进入主分配装置330，经主分配装置330均匀分配后进入第一换热管组301进行换热。在第一换热管组301中，一部分液态制冷剂发生热量交换而变为气态制冷剂，一部分液态制冷剂继续向下流动。由于第一换热管组301中部分制冷剂变为气态，在第一换热管组301的底部的液态制冷剂的量少于第一换热管组301顶部液态制冷剂的量，第一换热管组301的底部的液态制冷剂经再分配装置350再次分配后进入第二换热管组302中进行换热。第二换热管组302继续将一部分液态制冷剂转化为气态制冷剂，另一部分制冷剂依然为液态，液态制冷剂进入满液换热管组320继续换热。降膜换热管组310中的液态制冷剂自下而下流动，并且被第一侧换热管挡板装置351和第二侧换热管挡板装置352所阻挡，而不能扩散至侧部流通空间360。在满液换热管组中，一部分制冷剂转化为气态制冷剂。由降膜换热管组310和满液换热管组320换热而产生的气态制冷剂依次流通空间361、侧部流通空间360、除雾器340和上部空间391后从制冷剂出口212流出。除雾器340能够除去混在气态制冷剂中的小液滴。
本文说所述的气态制冷剂是指制冷剂中气体占绝大部分，不排除气态制冷剂中含有少量液滴。
在本申请中，满液换热管组320中的换热管被制冷剂液体浸没，在蒸发器工作过程中，制冷剂液体的高度大致与满液换热管组320的高度齐平。
在本申请中，第一换热管组301的列数与经主分配装置330分配后的液态制冷剂的流量匹配，第二换热管组302的列数与经再分配装置350分配后的液态制冷剂的流量匹配。在本申请中，将降膜换热管组310设置为具有不同列数的两段，有利于提高蒸发器130的换热效率。
图6是图3中再分配装置350的第二实施例的俯视图，与图5中所示的实施例类似，所不同的是，再分配装置350上的每排孔中的直径不同。再分配装置350中的孔在宽度方向上有多排，每一排孔中的每个孔直径相同，但与其它的排的孔的直径不同。位于宽度方向上的中间的一排孔621中的每个孔直径最大，位于宽度方向上的两侧的两排孔625，626的中的每个孔直径最小。每排孔的中的每个孔直径自宽度方向上的中间向两侧逐渐缩小。图6中的再分配装置350也适用于图3所示的实施例。在图3所示的实施例中，第一换热管组下部342的宽度逐渐收窄，并且第一换热管组下部342的两侧设有与其形状相匹配的第一侧上部挡板下段387和第二侧上部挡板下段388，第一侧上部挡板下段387和第二侧上部挡板下段388为向内倾斜的斜面。由于倾斜的第一侧上部挡板下段387和第二侧上部挡板下段388的引导，在第一换热管组下部342的底部的两侧处的液态制冷剂的流量自大于第一换热管组下部342的底部的中间的液态制冷剂的流量。采用如图6所示的再分配装置350能够使得制冷剂较为均匀地分配到第二换热管组302中。
在图3所示的实施例中，第一换热管组301产生的气态和液态制冷剂均流向第二换热管组302。其中第一换热管组301产生的液态制冷剂能够在第二换热管组302中继续换热，而气态制冷剂基本不再参与换热。在一些实施例中，及时将第一换热管组301中产生的气态制冷剂及时排出，有利于提高第二换热管组302的换热效率。
图7是本申请中蒸发器的第二实施例的径向截面示意图，图8A是图7A中A部的局部放大图，图8B是图7中第一侧上部挡板下段的俯视图。与图3所示 的实施例相似，所不同的是，图7中的第一换热管组301具有换热管排气通道729，第一侧换热管挡板装置351和第二侧换热管挡板装置352中设有挡板排气通道。
如图7、图8A和图8B所示，蒸发器700的第一侧换热管挡板装置351和第二侧换热管挡板装置352分别包括位于第一换热管组下部742的两侧的第一侧上部挡板下段787和第二侧上部挡板下段788。第一侧上部挡板下段787和第二侧上部挡板下段788上分别设有数个排气孔705，数个排气孔705中的每个排气孔705形成一个挡板排气通道708。挡板排气通道708能够将第一换热管组701中产生的气态制冷剂及时排出。
如7和图8B所示，数个排气孔705沿着容腔305的长度方向排列，数个排气孔705中的每个排气孔705在从所述第一换热管组上部741向所述第二换热管组302的方向上形成长条状。长条状的数个排气孔705用于避免过多的液态制冷剂从排气孔705流入到流通空间760。
如图7和图8A所示，第一换热管组701中设有换热管排气通道729，换热管排气通道自第一换热管组下部742的两侧向上并朝向第一换热管组701的宽度方向上中心分界面倾斜延伸。在所述容腔305的垂直于长度方向的截面上，换热管排气通道729的宽度大于换热管排气通道729上方的换热管之间的间隙。在本申请的一个实施例中，换热管排气通道729由沿着换热管排气通道729的延伸方向空出若干根换热管的位置形成，则换热管排气通道729的宽度稍大于换热管直径。第一换热管组701中产生的气态制冷剂能够通过换热管排气通道729进入挡板排气通道708。
换热管排气通道729和挡板排气通道708有利于气态制冷剂的迅速排出到流通空间760，以避免过多的气态制冷剂进入第二换热管组702，冲击第二换热管组702上的制冷剂液膜，影响第二换热管组702的换热效率。并且同时减少气态制冷剂冲击第二换热管组702而产生的振动。
图9A是本申请中蒸发器的第三实施例的径向截面示意图，图9B是图9A中B部的局部放大图。与图7所示的实施例相似，所不同的是挡板排气通道的设置方式。
如图9A和图9B所示，第一侧换热管挡板装置951包括第一侧上部挡板971和第一侧下部挡板972，第二侧换热管挡板装置952包括第二侧上部挡板973和和下部挡板974。第一侧上部挡板971包括上段981和下段982，第二侧上部挡板973包括上段983和下段984。上段981和983设置在所述第一换热管组上部941的两侧，下段982和984设置在第一换热管组下部942的两侧。第一侧下部挡板972包括主体段985和延伸段986，下部挡板974包括主体段987和延伸段988。主体段985和主体段987设置在第二换热管组902的两侧，延伸段986和延伸段988分别自主体段985和主体段987的顶部沿着大致分别平行于下段982和下段984的方向向上并向外延伸。延伸段986和延伸段988在容腔305的高度方向上超过下段982和下段984的底部，从而至少部分地与第一侧上部挡板971和第二侧上部挡板973重叠。延伸段986与第一侧上部挡板971的下段982之间具有一定间距从而形成排气通道908，延伸段988与第二侧上部挡板973的下段984之间具有一定间距从而形成排气通道909。第一换热管组901中产生的气态制冷剂能够通过排气通道908和排气通道909排出。与图7所示的实施例相比，本实施例中的液态制冷剂不易从排气通道908和909中流出。
图10A是本申请中蒸发器的第四实施例径向截面图的局部放大图，图10B是图10A中横向挡板的俯视图。与图9A所示的实施例类似，不同的是，图10A中的挡板排气通道中还包括横向挡板。
如图10A和图10B所示，下部挡板1072的延伸段1087与上部挡板1071的下段1082之间形成排气通道1008，排气通道1008中设有横向挡板1001和1002。横向挡板1001和1002横向于下部挡板1072的延伸段1087延伸，也就是说横向挡板1001和1002垂直于下部挡板1072的延伸段1087，或与下部挡板1072的延伸段1087之间形成一定夹角。如图10B所示，横向挡板1001和1002上具有多个开口1009，开口1009能够允许体制冷剂通过。开口1009可以是贯穿横向 挡板1001和1002的孔，或者是自横向挡板1001和1002的一侧边缘向内凹陷而形成的凹部。其中横向挡板1001的开口1009与横向挡板1002的开口1009交错布置，以使得气态制冷剂能够顺利通过，而大部份液态制冷剂能够被横向挡板1001和1002阻挡。与图9A所示的实施例相比，本实施例能够进一步防止液态制冷剂从挡板排气通道流出。
图11是本申请中蒸发器的第五实施例的径向截面示意图，与图3所示的实施例类似，所不同的是第一换热管组1101和第二换热管组1102的宽度相同。如图11所示，第一换热管组1101和第二换热管组1102分别具有均匀的宽度，第二换热管组1102设置在第一换热管组1101的下部。第一换热管组1101和第二换热管组1102的宽度基本相同。但第一换热管组1101的列数少于第二换热管组1102的列数，也就是说在容腔305的宽度方向上，第一换热管组1101中的换热管比第二换热管组1102中的换热管的布置得更密。再分配装置1150上的孔的排数与位置与第二换热管组1102对应，也能将液态制冷剂均匀分布到第二换热管组1102中，达到图3所示的实施例的技术效果。
在图11所示的实施例中，上部挡板1171和下部挡板1172均沿着竖直方向延伸，上部挡板1171的下段1182与下部挡板1172的延伸段1186在容腔305的高度方向上部分重叠，挡板排气通道1108之间设置横向挡板1111和1112，也能达到如图10A的实施例所示的技术效果。
在本申请的上述实施例中，降膜换热管组、有第一侧换热管挡板装置和第二侧换热管挡板装置均相对于容腔的宽度方向上的中心分界面对称。在其它实施例中，降膜换热管组、有第一侧换热管挡板装置和第二侧换热管挡板装置也可以相对于容腔的宽度方向上的中心分界面不对称，只需降膜换热管组中的第一换热管组的列数大于第二换热管组的列数即可。例如，在容腔的宽度方向上，第二换热管组的第一侧与第一换热管组的第一侧齐平，第二换热管组的第二侧与第一换热管组的第二侧错开。
在降膜蒸发器中，从制冷剂入口进入蒸发器的制冷剂液体经主分配装置分配后均匀分布到降膜换热管组的顶部的换热管表面，形成液膜进行换热。一部分液 态制冷剂经蒸发换热后转化为气态，另一部分未蒸发的液态制冷剂将滴落到下排换热管上继续蒸发，流过降膜换热管组的液态制冷剂流量由降膜换热管组的顶部到底部逐渐降低。
一般地，降膜蒸发换热系数“h r”和流过降膜换热管的液态制冷剂流量“m 1”之间如下的关系：当液态制冷剂流量大于临界流量“m 2”时，降膜蒸发换热系数“h r”基本不随液态制冷剂流量变化而变化，当液态制冷剂流量小于临界流量“m 2”时，降膜蒸发换热系数“h r”随液态制冷剂流量降低而迅速衰减。在降膜蒸发器设计时，为防止降膜换热系数衰减，会保证降膜换热管组的底部的换热管处的液态制冷剂流量达到临界流量“m 2”。并且会在蒸发器底部设置一定比例的满液换热管束，以对降膜换热管组的底部的液态制冷剂进行换热。
为保证满液换热管组区域的换热性能，制冷剂需要淹没满液换热管组。在一般的设计中，降膜换热管组的列数为均一的，在这种设计中，通常降膜换热管组和满液换热管组中的换热管的比例达到1：1时，整个蒸发器的换热效率较高。
在本申请的蒸发器中，降膜换热管组包括列数不同的两部分，第一换热管组与液态制冷剂换热后，一部液态制冷剂转化为气体，换热管处的液态制冷剂的流量自上而下逐渐减小。其中第一换热管组的底部的换热管的液态制冷剂流量已经达到临界流量“m 2”。在此情况下，如果继续在第一换热管组的底部增加列数相同的换热管，则增加的换热管处液态制冷剂流量小于临界流量“m 2”，则会导致增加的换热管的降膜蒸发换热系数“h r”降低，影响蒸发器的换热效率。因此，本申请中增加了再分配装置和列数更少的第二换热管组对第一换热管组底部的液态制冷剂进行继续换热。再分配装置将第一换热管组底部的液态制冷剂收集后再次分配，再分配装置的孔的排数与第二换热管组的列数对应。由于第二换热管组的列数少于第一换热管组的列数，则第二换热管组的顶部的换热管的液态制冷剂流量将大于第一换热管组的底部的换热管的流量，也就是说第二换热管组的顶部的换热管的液态制冷剂流量超过临界流量“m 2”，第二换热管组能够维持较高的降膜蒸发换热系数“h r”，从而第二换热管组也能够维持较高的换热效率。
在降膜蒸发器中，满液换热管组用于对经降膜换热管组换热后未能气化的制冷剂进行换热，但在满液换热管组的换热管浸没在制冷剂液体中，降膜换热管组中的换热管的液体流量大于临界流量m 2时，满液换热管组的换热管的换热系数小于降膜换热管组的换热管的换热系数。因此，在满足上述对降膜换热管的流量要求的前提下，提高降膜换热管组中的换热管数量占蒸发器中总的换热管数量的比例，有利于提高蒸发器的换热效率。
在本申请中，通过将降膜换热管组设置为包括两段列数不同部分，同时设置再分配装置，能够在第一换热管组底部的换热管的流量已达到临界流量时，通过再配装装置再次分配制冷剂，从而增大第二换热管组中每列换热管处的液态制冷剂的流量，从而满足了第二换热管组中换热管液态制冷剂流量大于或等于临界流量“m 2”。在第二换热管组的底部，每个换热管处的流量接近或等于临界流量。由于降膜换热管组底部的换热管一般均设置为能够达到临界流量，本申请中的蒸发器与传统蒸发器相比，第二换热管组换热管的列数较少，则第二组换热管组底部的液态制冷剂的总量较少，从而减少满液换热管组中换热管所需的数量。与传统的降膜蒸发器相比，本申请中降膜换热管组中换热管数量占换热管总数量的比值较大，从而本申请中的蒸发器具有较高的换热效率。
尽管本文中仅对本申请的一些特征进行了图示和描述，但是对本领域技术人员来说可以进行多种改进和变化。因此应该理解，所附的权利要求旨在覆盖所有落入本申请实质精神范围内的上述改进和变化。

Claims (13)

  1. 一种蒸发器，其特征在于包括：
    壳体(201)，所述壳体(201)具有容腔(305)，所述容腔(305)具有长度方向(L)、宽度方向(W)和高度方向(H)；
    第一换热管组和第二换热管组，第一换热管组和第二换热管组中的换热管沿着所述容腔(305)的长度方向延伸，并且沿着所述容腔(305)的宽度方向(W)和高度方向(L)排布，所述第一换热管组位于所述第二换热管组上方，其中，在所述容腔(305)的宽度方向上，所述第一换热管组的列数大于所述第二换热管组的列数；
    第一侧换热管挡板装置和第二侧换热管挡板装置，所述第一侧换热管挡板装置和第二侧换热管挡板装置在所述容腔(305)的宽度方向上分别设置在所述第一换热管组和所述第二换热管组的相对的两侧，并沿着所述第一换热管组和所述第二换热管组的外轮廓布置；
    再分配装置(350)，所述再分配装置(350)设置在第一换热管组和第二换热管组之间，并且所述再分配装置(350)在所述容腔(305)的宽度方向(W)上的两端分别与所述第一侧换热管挡板装置和第二侧换热管挡板装置连接，其中，所述再分配装置(350)沿着所述容腔(305)的长度方向(L)延伸以覆盖所述第二换热管组的顶部，并与所述第一换热管组下部之间具有一定间距，所述再分配装置(350)上设有数排孔，所述数排孔中的每一排孔沿着所述换热管的延伸方向布置，所述数排孔中的每排孔与第二换热管组中相应的一列换热管对齐。
  2. 如权利要求1所述的蒸发器，其特征在于：
    所述第一换热管组和所述第二换热管组分别相对于所述容腔(305)的沿高度方向延伸的中心分界面对称布置。
  3. 如权利要求2所述的蒸发器，其特征在于：
    所述第一换热管组和所述第二换热管组的宽度相同。
  4. 如权利要求3所述的蒸发器，其特征在于：
    所述第一换热管组具有第一换热管组上部和第一换热管组下部，在所述容腔(305)的宽度方向上，第一换热管组上部的宽度大于所述第二换热管组的宽度。
  5. 如权利要求4所述的蒸发器，其特征在于：
    所述第一换热管组下部的宽度自上而下逐渐缩小，第一换热管组下部的顶部的宽度与所述第一换热管组上部的宽度相同，所述第一换热管组下部的底部与所述第二换热管组的宽度相同。
  6. 如权利要求4所述的蒸发器，其特征在于：
    在所述容腔(305)的宽度方向(W)上，所述再分配装置(350)上的数个孔的尺寸从所述再分配装置(350)的中间向两侧逐渐缩小。
  7. 如权利要求1所述的蒸发器，其特征在于还包括：
    第三换热管组(320)，所述第三换热管组(320)位于所述容腔(305)的底部，并位于所述第二换热管组的下方，所述第三换热管组(320)与所述第二换热管组之间具有一定间距以形成流通空间(361)，从而使得从第二换热管组流出的气态制冷剂能够通过所述流通空间(361)流向设置在所述壳体(201)上的制冷剂出口(212)。
  8. 如权利要求1所述的蒸发器，其特征在于：
    所述第一侧换热管挡板装置和第二侧换热管挡板装置分别包括至少一个挡板排气通道，在所述容腔(305)的高度方向上，所述挡板排气通道位于第二换热管组上方，所述至少一个挡板排气通道被配置为将所述第一换热管组中的气态制冷剂排出。
  9. 如权利要求8所述的蒸发器，其特征在于：
    所述第一侧换热管挡板装置和第二侧换热管挡板装置分别包括第一侧上部挡板下段和第二侧上部挡板下段，所述第一侧上部挡板下段和第二侧上部挡板下段设置在所述第一换热管组下部的两侧，所述第一侧上部挡板下段和第二侧上部挡板下段上分别设有数个排气孔，所述数个排气孔中的每个排气孔形成一个挡板排气通道，
    所述数个排气孔沿着所述容腔(305)的长度方向排列，所述数个排气孔中的每个排气孔在从所述第一换热管组上部向所述第二换热管组的方向上形成长条状。
  10. 如权利要求9所述的蒸发器，其特征在于：
    所述第一换热管组具有换热管排气通道，所述换热管排气通道形成在第一换热管组的换热管之间，所述换热管排气通道从所述第一换热管组下部的两侧向内并向上延伸，在所述容腔的垂直于长度方向的截面上，所述换热管排气通道的宽度大于所述换热管排气通道上方的换热管之间的间隙。
  11. 如权利要求10所述的蒸发器，其特征在于：
    所述第一侧换热管挡板装置和第二侧换热管挡板装置中的每一个包括上部挡板和和下部挡板，所述上部挡板设置在所述第一换热管组的一侧，所述下部挡板包括主体段和延伸段，所述主体段设置在所述第二换热管组的一侧，所述延伸段自所述主体段段向上延伸，并且所述延伸段和所述上部挡板至少部分地重叠，所述上部挡板和所述延伸段之间形成所述挡板排气通道。
  12. 如权利要求10所述的蒸发器，其特征在于：
    所述第一侧换热管挡板装置和第二侧换热管挡板装置中的每一个还包括至少一个横向挡板，所述至少一个横向挡板设置在所挡板排气通道中，所述至少一个横向挡板横向于下部挡板的延伸段延伸，所述至少一个横向挡板上设有数个开口，以使得气态制冷剂能够通过。
  13. 如权利要求11所述的蒸发器，其特征在于：
    所述至少一个横向挡板的数量为两个，并沿着挡板排气通道的延伸方向布置，所两个横向挡板上的开口交错布置。
PCT/CN2022/070481 2021-01-13 2022-01-06 蒸发器 WO2022152033A1 (zh)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US18/272,037 US20240085069A1 (en) 2021-01-13 2022-01-06 Evaporator
EP22738914.5A EP4279854A4 (en) 2021-01-13 2022-01-06 EVAPORATOR
KR1020237027060A KR20230130067A (ko) 2021-01-13 2022-01-06 증발기

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202110040801.0A CN114763947B (zh) 2021-01-13 2021-01-13 蒸发器
CN202110040801.0 2021-01-13

Publications (1)

Publication Number Publication Date
WO2022152033A1 true WO2022152033A1 (zh) 2022-07-21

Family

ID=82364407

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/070481 WO2022152033A1 (zh) 2021-01-13 2022-01-06 蒸发器

Country Status (6)

Country Link
US (2) US20240085069A1 (zh)
EP (1) EP4279854A4 (zh)
KR (1) KR20230130067A (zh)
CN (1) CN114763947B (zh)
TW (1) TW202242334A (zh)
WO (1) WO2022152033A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117168192A (zh) * 2023-10-17 2023-12-05 河北航研制冷设备有限公司 一种可提高制冷剂流动速度的满液式管壳蒸发装置
CN118028671A (zh) * 2023-12-25 2024-05-14 鞍钢股份有限公司 一种拉深性能良好的稀土镁合金板带及其制备方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080073059A1 (en) * 2006-09-21 2008-03-27 Kees Weel Heat exchanger
CN104764258A (zh) * 2014-01-02 2015-07-08 约克（无锡）空调冷冻设备有限公司 壳管式冷凝器
CN109282531A (zh) * 2018-12-03 2019-01-29 珠海格力电器股份有限公司 降膜式蒸发器及空调器
CN109357441A (zh) * 2018-12-14 2019-02-19 珠海格力电器股份有限公司 降膜式蒸发器和空调
CN111213022A (zh) * 2017-10-20 2020-05-29 江森自控科技公司 降膜热交换器
US20200200478A1 (en) * 2018-12-19 2020-06-25 Daikin Applied Americas Inc. Heat exchanger

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9658003B2 (en) * 2013-07-11 2017-05-23 Daikin Applied Americas Inc. Heat exchanger
CN104748448B (zh) * 2013-12-27 2017-08-11 约克（无锡）空调冷冻设备有限公司 壳管式冷凝器
CN104457040B (zh) * 2014-11-13 2017-09-22 广东申菱环境系统股份有限公司 一种喷淋降膜式蒸发器及其液位控制方法
JP2017190926A (ja) * 2016-04-15 2017-10-19 三菱重工サーマルシステムズ株式会社 蒸発器、これを備えたターボ冷凍装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080073059A1 (en) * 2006-09-21 2008-03-27 Kees Weel Heat exchanger
CN104764258A (zh) * 2014-01-02 2015-07-08 约克（无锡）空调冷冻设备有限公司 壳管式冷凝器
CN111213022A (zh) * 2017-10-20 2020-05-29 江森自控科技公司 降膜热交换器
CN109282531A (zh) * 2018-12-03 2019-01-29 珠海格力电器股份有限公司 降膜式蒸发器及空调器
CN109357441A (zh) * 2018-12-14 2019-02-19 珠海格力电器股份有限公司 降膜式蒸发器和空调
US20200200478A1 (en) * 2018-12-19 2020-06-25 Daikin Applied Americas Inc. Heat exchanger

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117168192A (zh) * 2023-10-17 2023-12-05 河北航研制冷设备有限公司 一种可提高制冷剂流动速度的满液式管壳蒸发装置
CN117168192B (zh) * 2023-10-17 2024-03-19 河北航研制冷设备有限公司 一种可提高制冷剂流动速度的满液式管壳蒸发装置
CN118028671A (zh) * 2023-12-25 2024-05-14 鞍钢股份有限公司 一种拉深性能良好的稀土镁合金板带及其制备方法

Also Published As

Publication number Publication date
EP4279854A1 (en) 2023-11-22
KR20230130067A (ko) 2023-09-11
EP4279854A4 (en) 2024-11-13
US20240060159A1 (en) 2024-02-22
CN114763947A (zh) 2022-07-19
US20240085069A1 (en) 2024-03-14
CN114763947B (zh) 2023-05-16
TW202242334A (zh) 2022-11-01

Similar Documents

Publication Publication Date Title
US7421855B2 (en) Gas trap distributor for an evaporator
ES2810865T3 (es) Intercambiador de calor
JP3056151B2 (ja) 熱交換器
WO2022152033A1 (zh) 蒸发器
US20180128525A1 (en) Ultra narrow channel ultra low refrigerant charge evaporative condenser
CN212390655U (zh) 一种蒸发器及制冷系统
CN117628741A (zh) 冷凝器及包括其的吸收式制冷机组
CN214120898U (zh) 一种扁管蒸发冷凝换热器
US20240377112A1 (en) Evaporator and Refrigeration System Comprising Same
WO2023036004A1 (zh) 蒸发器及包括其的制冷系统
WO2022179511A1 (zh) 冷凝器
CN212431408U (zh) 蒸发器及制冷系统
CN114076424A (zh) 一种蒸发器及制冷系统
JPH02293595A (ja) 冷媒凝縮器
CN112815744B (zh) 三维冷却蒸发冷凝换热器
CN221425440U (zh) 喷雾式楔形换热装置
CN111271999B (zh) 换热器
CN114076425A (zh) 蒸发器及制冷系统
CN112577354A (zh) 一种扁管蒸发冷凝换热器
US20200340748A1 (en) Ultra narrow channel ultra low refrigerant charge evaporative condenser
CN117366917A (zh) 蒸发器
CN118602637A (zh) 冷凝器
CN117663838A (zh) 换热装置和换热系统
CN113357850A (zh) 蒸发器及冷水机组
CN116045551A (zh) 一种带回热器的干式蒸发器及制冷系统

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22738914

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 18272037

Country of ref document: US

ENP Entry into the national phase

Ref document number: 20237027060

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 1020237027060

Country of ref document: KR

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2022738914

Country of ref document: EP

Effective date: 20230814