WO2024078274A1 - 罐式换热器和空调系统 - Google Patents

罐式换热器和空调系统 Download PDF

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Publication number
WO2024078274A1
WO2024078274A1 PCT/CN2023/119689 CN2023119689W WO2024078274A1 WO 2024078274 A1 WO2024078274 A1 WO 2024078274A1 CN 2023119689 W CN2023119689 W CN 2023119689W WO 2024078274 A1 WO2024078274 A1 WO 2024078274A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
cylinder
tank
liquid
tube
Prior art date
Application number
PCT/CN2023/119689
Other languages
English (en)
French (fr)
Inventor
卢杏斌
胡海利
岳清学
王小勇
Original Assignee
珠海格力电器股份有限公司
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Filing date
Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2024078274A1 publication Critical patent/WO2024078274A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • 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
    • 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
    • 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 disclosure relates to the technical field of air conditioning, and in particular to a tank type heat exchanger and an air conditioning system.
  • the falling film evaporator is widely used in water-cooled units due to its advantages such as small refrigerant charge, small static pressure difference, high heat exchange efficiency and convenient oil return.
  • its performance on units less than 100RT is not ideal. Therefore, generally only low-efficiency dry evaporators or shell-and-tube heat exchangers can be used on these units.
  • some falling film evaporators are equipped with a liquid equalizing device to receive the liquid refrigerant flowing from above, and evenly distribute it and then flow it to the coils in the falling film area below.
  • the refrigerant entering the evaporator may not be pure liquid, and the liquid refrigerant often contains a certain amount of gaseous refrigerant. After the liquid refrigerant passes through the heat exchange coil above the liquid equalizing plate for evaporation and heat exchange, a part of gaseous refrigerant is produced.
  • the density of gaseous refrigerant is much lower than that of liquid refrigerant, which greatly increases the average flow rate through the holes or seams on the liquid equalizing plate, which not only increases the pressure drop on the fluorine side of the heat exchanger, but also makes it easy for the liquid refrigerant to sputter and deviate, which is not conducive to the liquid distribution and falling film evaporation of the liquid refrigerant in the heat exchange coil below the liquid equalizing device.
  • An object of the present disclosure is to provide a tank type heat exchanger and an air conditioning system.
  • a first aspect of the present disclosure provides a tank-type heat exchanger, which is provided with a working medium inlet and a working medium outlet, and the tank-type heat exchanger comprises:
  • An inner cylinder is connected to the outer cylinder, the outer cylinder is arranged parallel to the axis of the inner cylinder and an annular space is formed between the inner cylinders;
  • a first heat exchange tube is coiled in the outer tube
  • a liquid balancing plate is fixedly arranged in the annular space relative to the outer tube and the inner tube and is located on a side of the first heat exchange tube close to the axial first end of the tank heat exchanger, wherein the radial outer end of the liquid balancing plate forms a gas passage with the wall of the outer tube, and/or the radial inner end of the liquid balancing plate forms a gas passage with the wall of the inner tube;
  • the shielding portion is fixedly arranged in the annular space relative to the outer tube and the inner tube and forms an axial gap with the liquid equalizing disk.
  • the shielding portion includes a shielding body corresponding to the gas channel.
  • the shielding body is located on the side of the liquid equalizing disk facing the axial first end of the tank type heat exchanger, and along the radial direction of the tank type heat exchanger, the shielding body completely covers the corresponding gas channel.
  • One of the radial inner end and the radial outer end of the shielding body is sealed with one of the cylinder wall of the inner tube and the cylinder wall of the outer tube, and the other forms a gap with the cylinder wall of the inner tube and the cylinder wall of the outer tube.
  • one of the radial inner end and the radial outer end of the liquid balancing disk forms a seal with one of the cylinder wall of the outer cylinder and the cylinder wall of the inner cylinder, and the other of the radial inner end and the radial outer end of the liquid balancing disk forms the gas channel with the other of the cylinder wall of the outer cylinder and the cylinder wall of the inner cylinder.
  • the radial outer end of the liquid balancing disk is sealed to the inner wall of the outer cylinder, and the radial inner end of the liquid balancing disk and the outer wall of the inner cylinder form the gas channel;
  • the radial inner end of the shielding body is fixedly connected to the outer wall of the inner cylinder.
  • the gas channel in a cross section perpendicular to the axial direction of the tank type heat exchanger, is annular.
  • the shielding body is a baffle perpendicular to the axial direction of the tank heat exchanger.
  • the shielding portion further includes an edge plate, wherein the edge plate is connected to the free end of the shielding body and extends toward the axial second end of the tank heat exchanger.
  • the shielding body is a baffle extending from the connecting end to the free end in a direction close to the liquid equalizing disk.
  • the baffle is a flat plate or a curved plate.
  • a plurality of guide portions are further included, and the plurality of guide portions are arranged at intervals on the edge of the shielding portion on a side close to the liquid equalizing plate, and extend in a direction close to the liquid equalizing plate.
  • the liquid balancing plate is in a groove structure that is recessed from the axial first end to the axial second end of the tank-type heat exchanger;
  • the guide portion partially extends into the groove structure, or the edge of the guide portion close to the axial second end of the tank heat exchanger is aligned with the edge of the groove structure close to the axial first end of the tank heat exchanger along the axial direction of the tank heat exchanger.
  • the inner cylinder is a circular cylinder or a polygonal cylinder.
  • a U-shaped tube is further included, wherein the plane where the center line of the U-shaped tube is located is arranged along the radial direction of the tank heat exchanger, the first end of the U-shaped tube is arranged in the inner cylinder and connected to the inner cylinder, and the second end of the U-shaped tube is used to be connected to a gaseous working fluid pipeline to import or export the gaseous working fluid.
  • the working medium inlet comprises a liquid inlet provided at the first axial end of the outer cylinder for introducing a liquid working medium
  • the working medium outlet comprises a gaseous working medium outlet communicated with the inner cylinder for conducting out a gaseous working medium
  • the working medium inlet comprises a gaseous working medium port communicated with the inner cylinder for introducing a gaseous working medium
  • the working medium outlet comprises a liquid outlet disposed at the second axial end of the outer cylinder for conducting a liquid working medium
  • a second heat exchange tube is coiled in the outer tube and is located on a side of the shielding portion away from the liquid equalizing plate;
  • the third heat exchange tube is coiled in the outer tube and is located on a side of the first heat exchange tube away from the liquid equalizing plate.
  • the outer cylinder includes a cylinder body, a first end cover and a second end cover, the cylinder body is disassembled along the radial direction of the tank heat exchanger, the first end cover is closed at the axial first end of the cylinder body, the second end cover is closed at the axial second end of the cylinder body, and the axial first end of the inner cylinder is connected to the first end cover.
  • a second aspect of the present disclosure is an air conditioning system, comprising the tank heat exchanger described in the first aspect of the present disclosure.
  • the tank-type heat exchanger provided by the embodiment of the present disclosure has a state in which liquid and gaseous two-phase working fluids flow inside, wherein the gaseous working fluid can flow up and down through the axial spacing between the shielding part and the liquid balancing plate and the gas channel, wherein the liquid working fluid can flow down through the liquid balancing plate, and the gaseous working fluid has an independent flow space, so the average flow rate of the liquid working fluid can be reduced, thereby playing a role in reducing the pressure drop of the working fluid in the heat exchanger.
  • the shielding part can play a role in recovering the liquid working fluid flowing down from the cylinder wall, and guide the liquid working fluid flowing down from the cylinder wall into the liquid balancing plate, thereby reducing the waste of falling film liquid and helping to improve the heat exchange efficiency.
  • the air conditioning system provided by the embodiment of the present disclosure has the advantages of the tank type heat exchanger provided by the embodiment of the present disclosure.
  • FIG. 1 is a schematic structural diagram of a tank-type heat exchanger according to some embodiments of the present disclosure.
  • FIG. 2 is a schematic diagram of the cross-sectional structure of the tank type heat exchanger shown in FIG. 1 .
  • FIG3 is a schematic diagram of a partially enlarged structure of the tank type heat exchanger shown in FIG2 in position.
  • FIG. 4 is a schematic structural diagram of a shielding portion of a tank-type heat exchanger according to some embodiments of the present disclosure.
  • FIG. 5 is a schematic structural diagram of a shielding portion of a tank type heat exchanger according to other embodiments of the present disclosure.
  • FIG. 6 is a schematic structural diagram of a flow guide portion of a tank-type heat exchanger according to some embodiments of the present disclosure.
  • FIG. 7 is a schematic structural diagram of a tank type heat exchanger according to some other embodiments of the present disclosure.
  • some embodiments of the present disclosure provide a tank type heat exchanger, which is provided with a working fluid inlet and a working fluid outlet.
  • the tank type heat exchanger includes an outer tube 1, an inner tube 2, a first heat exchange tube 31, a liquid equalizing pan 4 and a shielding portion 5.
  • the inner cylinder 2 is connected to the outer cylinder 1 .
  • the outer cylinder 1 and the inner cylinder 2 are arranged parallel to each other and an annular space is formed between the inner cylinders 2 .
  • the first heat exchange tube 31 is coiled in the outer tube 1 .
  • the liquid balancing plate 4 is fixedly arranged in the annular space relative to the outer tube 1 and the inner tube 2 and is located on the side of the first axial end of the tank-type heat exchanger close to the first heat exchange tube 31.
  • the radial outer end of the liquid balancing plate 4 forms a gas channel G with the wall of the outer tube 1, and/or the radial inner end of the liquid balancing plate 4 forms a gas channel G with the wall of the inner tube 2.
  • the shielding portion 5 is fixedly arranged in the annular space relative to the outer tube 1 and the inner tube 2 and forms an axial gap with the liquid equalizing disk 4.
  • the shielding portion 5 includes a shielding body corresponding to the gas channel G.
  • the shielding body is located on the side of the liquid equalizing disk 4 facing the axial first end of the tank heat exchanger, and along the radial direction of the tank heat exchanger, the shielding body completely covers the corresponding gas channel G.
  • One of the radial inner end and the radial outer end of the shielding body is a connecting end, and the other is a free end.
  • the connecting end is sealedly connected to one of the barrel wall of the inner tube 2 and the barrel wall of the outer tube 1, and the free end forms a gap with the barrel wall of the inner tube 2 and the barrel wall of the outer tube 1.
  • the axial direction of the outer cylinder 1 is the up and down direction
  • the axial first end of the outer cylinder 1 is the top end
  • the axial second end is the bottom end.
  • the tank heat exchanger disclosed in the present invention may be a falling film heat exchanger, a flooded heat exchanger or other forms of heat exchangers, and may be used as an evaporator or a condenser.
  • the tank heat exchanger may be used in an air conditioning system, but is not limited to an air conditioning system.
  • the working medium may be a refrigerant.
  • the dimensions of the outer tube 1 and the inner tube 2 along the axial direction of the tank heat exchanger may be the same or different.
  • the axial ends of the outer tube 1 are closed, the dimension of the inner tube 2 along the axial direction of the tank heat exchanger may be smaller than the dimension of the outer tube 1 along the axial direction of the tank heat exchanger, the first axial end of the inner tube 2 is connected to the first axial end of the outer tube 1, and the second axial end of the inner tube 2 is connected to the outer tube 1.
  • the dimensions of the outer tube 1 and the inner tube 2 along the axial direction of the tank heat exchanger may also be the same, the axial ends of the inner tube 2 are connected to the outer tube 1, and the inner tube 2 and the outer tube 1 may be connected through an opening on the inner tube 2 or a pipe or other structure.
  • the working fluid inlet and the working fluid outlet can be set at different positions of the tank heat exchanger according to the selection requirements of the heat exchanger, such as the axial first end and the axial second end of the outer tube 1 or the inner tube 2.
  • the working fluid inlet when the tank heat exchanger is used as an evaporator, can be connected to the axial first end of the outer tube 1 and used to introduce liquid working fluid, and the working fluid outlet can be connected to the inner tube 2 and used to export gaseous working fluid; in other embodiments, when the tank heat exchanger is used as a condenser, the working fluid inlet can be connected to the inner tube 2 and used to introduce gaseous working fluid, and the working fluid outlet can be connected to the axial second end of the outer tube 1 and used to export liquid working fluid.
  • the same working fluid port can be used as a working fluid inlet when the tank-type heat exchanger is used as an evaporator, and as a working fluid outlet when the tank-type heat exchanger is used as a condenser, and vice versa.
  • the liquid balancing plate 4 is fixedly arranged relative to the outer tube and the inner tube, and may be directly fixedly connected to at least one of the outer tube and the inner tube, or other components are used to keep the liquid balancing plate relatively fixed to the outer tube and the inner tube.
  • the shielding part 5 is fixedly arranged relative to the outer tube and the inner tube, and may be directly fixedly connected to at least one of the outer tube and the inner tube, or other components are used to keep the shielding part relatively fixed to the outer tube and the inner tube.
  • the structure on the liquid balancing plate for allowing the fluid to pass through can be a plurality of liquid balancing holes 40 evenly spaced along the tank heat exchanger and arranged at the bottom of the liquid balancing plate 4.
  • the structure for allowing the fluid to pass through is not limited to a hole shape, and can also be a slit shape or other shapes, as long as the liquid working medium can form a plurality of uniform liquid columns or droplets after passing through the liquid balancing plate.
  • the gas channel G can be arranged on the radial inner side or radial outer side of the liquid balancing disk 4, or on both the radial inner side and radial outer side of the liquid balancing disk 4. Accordingly, the number of shielding parts 5 can be one or two.
  • the radial inner end of the shielding body corresponding to the gas channel G is sealed with the wall of the inner tube 2, and the radial outer end forms a gap with the wall of the outer tube 1;
  • the radial inner end of the shielding body corresponding to the gas channel G is sealed with the wall of the inner tube 2, and the radial outer end forms a gap with the wall of the outer tube 1. 1 is connected with the cylinder wall seal.
  • the liquid working medium can be introduced into the tank heat exchanger through the liquid inlet 10 arranged at the first axial end of the outer cylinder 1, and the inner cylinder can be connected to the gaseous working medium pipeline so that the gaseous working medium can be introduced into or exported from the inner cylinder of the tank heat exchanger. Therefore, the tank heat exchanger can be used as both an evaporator and a condenser.
  • the liquid working medium can flow from the working medium inlet through the liquid balancing plate 4 to the first heat exchange tube 31 below the liquid balancing plate 4; in the process of the liquid working medium flowing downward, even if part of the working medium droplets fly onto the walls of the inner and outer cylinders due to deviation or sputtering, they can directly flow into the liquid balancing plate 4, or be blocked by the shielding part 5 and introduced into the liquid balancing plate 4 by the shielding part 5, so as to recover the liquid working medium.
  • the gaseous working medium that enters the tank heat exchanger through the liquid inlet 10 with the liquid working medium, or the gaseous working medium that is vaporized after absorbing heat from the heat exchange tube in the tank heat exchanger, can flow down smoothly from the space above the liquid balancing plate 4 and the shielding part 5 through the axial spacing between the shielding part 5 and the liquid balancing plate 4 and the gas channel G.
  • the influence of the pressure increase of the gaseous working fluid on the flow rate of the liquid working fluid can be eliminated, and the average flow rate of the liquid working fluid when passing through the holes or slits on the liquid balancing plate 4 can be reduced, thereby reducing the pressure drop of the working fluid in the heat exchanger.
  • the tank-type heat exchanger When the tank-type heat exchanger is used as a condenser, after the gaseous working medium flows from the working medium inlet through the inner tube into the annular space formed between the outer tube and the inner tube, it can flow smoothly through the axial gap between the gas channel G and the shielding part, and is convenient for flowing to the top of the liquid equalizing plate 4 and the shielding part 5 for condensation and heat exchange; the liquid working medium produced by the condensation of the gaseous working medium can flow down from the liquid equalizing plate 4 and be stored at the bottom of the tank-type heat exchanger.
  • the tank-type heat exchanger Whether used as an evaporator or a condenser, the tank-type heat exchanger provided by the embodiment of the present disclosure has a state in which liquid and gaseous two-phase working fluids flow inside, wherein the gaseous working fluid can flow up and down through the axial spacing between the shielding portion and the liquid balancing plate and the gas channel, wherein the liquid working fluid can flow down through the liquid balancing plate, and the gaseous working fluid has an independent flow space, so the average flow rate of the liquid working fluid can be reduced, thereby playing a role in reducing the pressure drop of the working fluid in the heat exchanger.
  • the shielding portion can play a role in recovering the liquid working fluid flowing down from the cylinder wall, and guide the liquid working fluid flowing down from the cylinder wall into the liquid balancing plate, thereby reducing the waste of falling film liquid and helping to improve heat exchange efficiency.
  • the radial ends of the liquid balancing plate 4 can be connected to the cylinder walls of the inner cylinder and the outer cylinder respectively, and a gas passage is only required to be left between the liquid balancing plate and the cylinder wall of at least one of the inner cylinder and the outer cylinder.
  • the inventor found that since the outer cylinder and the inner cylinder form a sleeve structure at the first end of the tank heat exchanger, it is very difficult for the liquid balancing plate to be connected to the cylinder walls of the outer cylinder and the inner cylinder at the same time, which is not conducive to the assembly of the entire tank heat exchanger.
  • one of the radial inner end and the radial outer end of the liquid balancing disk 4 forms a seal with the cylinder wall of the outer cylinder 1 and the cylinder wall of the inner cylinder 2, and the radial inner end and the radial outer end of the liquid balancing disk 4 form a seal with the cylinder wall of the outer cylinder 1 and the cylinder wall of the inner cylinder 2.
  • One forms a gas channel G with the cylinder wall of the outer cylinder 1 and the cylinder wall of the inner cylinder 2
  • the other forms a gas channel G with the cylinder wall of the outer cylinder 1 and the cylinder wall of the inner cylinder 2.
  • the tank type heat exchanger of the above embodiment can not only provide a gaseous working medium channel, reduce the working medium pressure drop and recover the liquid working medium, but also the liquid equalizing plate only needs to be connected to one side of the cylinder wall of the outer cylinder and the inner cylinder, which can reduce the difficulty of assembling the tank type heat exchanger, improve the assembly efficiency and reduce the manufacturing cost.
  • the gas channel G can be arranged between the radial inner side of the liquid balancing disk 4 and the outer wall of the inner cylinder.
  • the radial outer end of the liquid balancing disk 4 is sealed with the inner wall of the outer cylinder 1, and the radial inner end of the liquid balancing disk 4 and the outer wall of the inner cylinder 2 form the gas channel G; the radial inner end of the shielding body is fixedly connected to the outer wall of the inner cylinder 2.
  • the gas channel G in a cross section perpendicular to the axial direction of the tank type heat exchanger, is annular.
  • the gas channel G runs through the circumference of the tank-type heat exchanger, the flow area of the gaseous working medium is larger, and the flow effect is better, so the effect of reducing the working medium pressure drop is also better.
  • the gas channel G may be discontinuous along the circumference of the tank heat exchanger, as long as the conditions for the gaseous working medium to flow are met.
  • the gas channel G may be present as several discontinuous fan rings.
  • the shielding body is a baffle 51 that is perpendicular to the axial direction of the tank heat exchanger.
  • the baffle 51 when the tank heat exchanger is in use, the baffle 51 is arranged horizontally.
  • the radial inner end of the baffle 51 is fixedly connected to the outer wall of the inner tube 2 to form a seal.
  • the shielding portion 5 further includes an edge plate 52 , which is connected to the free end of the shielding body and extends toward the axial second end of the tank heat exchanger.
  • the baffle 51 when the tank heat exchanger is in use, the baffle 51 is arranged horizontally, and the edge plate 52 can be arranged vertically with the baffle 51 or at a certain angle with the baffle 51, and can play a certain role in guiding the flow.
  • the radial inner end of the baffle 51 is fixedly connected to the outer wall of the inner tube 2 and forms a seal
  • the edge plate 52 is connected to the radial outer end of the baffle 51 and is arranged vertically with the baffle 51
  • the shielding portion 5 is L-shaped as a whole.
  • the shielding body is a baffle 51 extending from the connecting end to the free end in a direction close to the liquid balancing tray 4 .
  • the baffle 51 when the tank heat exchanger is in use, the baffle 51 extends from top to bottom and the upper end is sealed and connected to the cylinder wall, forming a structure similar to the shape of an eave, which facilitates the accumulated liquid working medium on the cylinder wall to flow to the liquid balancing pan, thereby playing a good role in guiding and recycling.
  • the baffle 51 is a flat plate or a curved plate.
  • the baffle 51 is a flat plate, and the radial inner end of the baffle 51 is fixed to the outer wall of the inner tube 2.
  • the baffle 51 extends obliquely from the radial inner end to the radial outer end from top to bottom.
  • the baffle 51 can also be a curved plate.
  • the baffle 51 can be a curved plate with a circular arc or parabolic cross section along the radial direction of the tank heat exchanger.
  • the tank heat exchanger further includes a plurality of guide portions 6 , which are spaced apart at the edge of the shielding portion 5 on the side close to the liquid equalizing pan 4 and extend toward the direction close to the liquid equalizing pan 4 .
  • the guide portion extends from the edge of the side of the shielding portion close to the liquid equalizing disk toward the direction close to the liquid equalizing disk.
  • the guide portion 6 may be a columnar structure extending vertically up and down.
  • the guide portion may also be arranged at an angle.
  • the guide portion can prevent the working medium droplets on the radial edge of the shielding portion from being blown into the gas channel G by the gaseous working medium during the dripping process when the gaseous working medium flows, thereby further reducing the waste of liquid working medium.
  • the liquid balancing plate 4 is in a groove structure that is recessed from the first axial end to the second axial end of the tank heat exchanger, wherein the flow guide 6 partially extends into the groove structure, or the edge of the flow guide 6 close to the second axial end of the tank heat exchanger is aligned with the edge of the groove structure close to the first axial end of the tank heat exchanger along the axial direction of the tank heat exchanger.
  • the bottom edge of the guide portion 6 is not higher than the top edge of the side wall of the groove structure, which can further enhance the blocking effect of the guide portion and better prevent the gaseous working fluid from blowing working fluid droplets into the gas channel.
  • the inner cylinder 2 is a cylinder or a polygonal cylinder.
  • Figures 1 and 2 show the case where the inner cylinder is a cylinder
  • Figure 7 shows the case where the inner cylinder is a polygonal cylinder.
  • the polygonal tube may be a quadrilateral tube, such as a rectangular tube or a square tube, or may be a pentagonal tube, a hexagonal tube, an octagonal tube, etc.
  • the tank heat exchanger also includes a U-shaped tube 7, the plane where the center line of the U-shaped tube 7 is located is arranged along the radial direction of the tank heat exchanger, the first end of the U-shaped tube 7 is arranged in the inner tube 2 and connected to the inner tube 2, and the second end of the U-shaped tube 7 is used to connect with the gaseous working medium pipeline to import or export the gaseous working medium.
  • the polygonal inner tube In order to fit the U-shaped tube with the same radius of the curved tube section into the inner tube, the polygonal inner tube requires a smaller axial cross-sectional area than the circular inner tube. Therefore, by setting the inner tube as a polygonal tube, it is beneficial to increase the flow area of the gas channel G and reduce the pressure drop of the working medium. Considering that the gas flow rate in the U-shaped tube will be too high if the diameter is too small, The diameter of the U-shaped tube is limited by the radius of the bend section. By setting the inner tube as a polygonal tube, the diameter of the U-shaped tube can be made as large as possible without reducing the radius of the bend section, which is beneficial to reducing the flow rate of the gaseous working medium and improving the heat exchange performance.
  • installing the U-shaped tube into a polygonal tube has a smaller axial cross-sectional area, which reduces the flow rate of the gaseous medium in the gas channel G.
  • the working fluid inlet includes a liquid inlet 10 arranged at the first axial end of the outer cylinder 1 for introducing a liquid working fluid
  • the working fluid outlet includes a gaseous working fluid port 70 connected to the inner cylinder 2 for exporting a gaseous working fluid
  • the working fluid inlet includes a gaseous working fluid port 70 connected to the inner cylinder 2 for introducing a gaseous working fluid
  • the working fluid outlet includes a liquid outlet 13 arranged at the second axial end of the outer cylinder 1 for exporting a liquid working fluid.
  • the gaseous medium inlet 70 may be located at the second end of the U-shaped tube 7 .
  • the tank type heat exchanger may of course also include more heat exchange tubes provided at different positions along the axial direction of the tank type heat exchanger.
  • the tank heat exchanger further includes a second heat exchange tube 32 and/or a third heat exchange tube 9.
  • the second heat exchange tube 32 is coiled in the outer tube 1 and is located on a side of the shielding portion 5 away from the liquid equalizing pan 4.
  • the third heat exchange tube 9 is coiled in the outer tube 1 and is located on a side of the first heat exchange tube 31 away from the liquid equalizing pan 4.
  • the tank heat exchanger includes a first heat exchange tube 31, a second heat exchange tube 32 and a third heat exchange tube 9, and the tank heat exchanger also includes a liquid distributor 8.
  • the liquid distributor 8, the second heat exchange tube 32, the shielding portion 5, the liquid balancing plate 4, the first heat exchange tube 31 and the third heat exchange tube 9 are arranged in sequence from top to bottom.
  • the first heat exchange tube 31 and the second heat exchange tube 32 together constitute the falling film zone heat exchange tube 3, and the third heat exchange tube 9 constitutes the full liquid zone heat exchange tube.
  • the liquid working medium enters the outer tube 1 through the liquid inlet 10 and the liquid distributor 8, and after heat exchange with the second heat exchange tube 32, the gaseous working medium generated by the evaporation of the liquid working medium flows through the axial interval between the shielding portion 5 and the liquid balancing plate 4 and the gas channel G to the inner tube 2 and the U-shaped tube 7, and is discharged from the gaseous working medium port 70, and the remaining liquid working medium flows through the liquid balancing plate 4 to the first heat exchange tube 31 and the third heat exchange tube 9 to continue heat exchange; the tank heat exchanger When the heat exchanger is used as a condenser, the gaseous working medium enters the outer tube 1 through the gaseous working medium port 70, the U-shaped tube 7, and the inner tube 2.
  • the liquid working medium generated by the condensation of the gaseous working medium is stored at the bottom of the tank heat exchanger and can be discharged from the liquid outlet 13.
  • the remaining gaseous working medium flows from the axial interval between the gas channel G, the shielding portion 5 and the liquid equalizing plate 4 to the annular area between the outer tube 1 and the inner tube 2, and continues to exchange heat with the second heat exchange tube 32.
  • the outer cylinder 1 includes a cylinder body 11, a first end cover 12 and a second end cover 14.
  • the cylinder body 11 is disassembled along the radial direction of the tank heat exchanger.
  • the first end cover 12 is closed at the axial first end of the cylinder body 11, and the second end cover 14 is closed at the axial second end of the cylinder body 11.
  • the axial first end of the inner cylinder 2 is connected to the first end cover 12.
  • the liquid equalizing pan 4 only needs to be sealed and connected to the outer cylinder 1, and the inner cylinder 2 is connected to the first end cover 12 but not to the liquid equalizing pan 4. Therefore, when the inner cylinder 2 is installed, it only needs to extend into the cylinder body 11 from top to bottom together with the first end cover 12, thereby further reducing the difficulty of installing the liquid equalizing pan.
  • a tank heat exchanger is, for example, a falling film evaporator.
  • Some embodiments of the present disclosure also provide an air conditioning system, comprising the above-mentioned tank-type heat exchanger.
  • the air conditioning system provided by the embodiments of the present disclosure correspondingly has the advantages of the above-mentioned tank-type heat exchanger.

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Abstract

一种罐式换热器和空调系统。罐式换热器包括：外筒（1）；内筒（2），外筒（1）与内筒（2）轴线平行地设置且与内筒（2）之间形成环状空间；第一换热管（31）；均液盘（4），位于第一换热管（31）的靠近罐式换热器的轴向第一端的一侧，均液盘（4）的径向外端与外筒（1）的筒壁形成气体通道，和/或，均液盘（4）的径向内端与内筒（2）的筒壁形成气体通道（G）；和遮挡部（5），与均液盘（4）形成轴向间隔，遮挡部（5）包括遮挡主体，遮挡主体位于均液盘（4）的朝向罐式换热器的轴向第一端的一侧，且沿罐式换热器的径向，遮挡主体完全覆盖对应的气体通道（G），遮挡主体的径向内端和径向外端之一为连接端，另一为自由端，所述连接端与内筒（2）的筒壁和外筒（1）的筒壁之一密封连接，所述自由端与内筒（2）的筒壁和外筒（1）的筒壁另一形成间隔。

Description

罐式换热器和空调系统
相关申请的交叉引用
本公开是以申请号为202211246064.0，申请日为2022年10月12日，发明名称为“罐式换热器和空调系统”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及空调技术领域，特别涉及一种罐式换热器和空调系统。
背景技术
降膜蒸发器作为一种新型高效节能设备，以其冷媒充注量小、静液压差小、换热效率高以及回油方便等优点被广泛运用于水冷机组。然而，其由于结构的限制在小于100RT的机组上表现并不理想。所以，一般在这些机组上只能使用能效较低的干式蒸发器或套管换热器。
相关技术中，一些降膜蒸发器设有均液装置，用以接收上方流来的液体冷媒，并使其均分然后流至下方降膜区的盘管。然而，进入蒸发器的冷媒可能并不是纯液态的，液态冷媒中往往会带有一定量的气态冷媒。液态冷媒在经过均液盘上方换热盘管进行蒸发换热后，又产生了一部分气态冷媒。气态冷媒密度远低于液态冷媒，这使得通过均液盘上孔或缝的平均流速大大增加，不但增大了换热器内氟侧压降，还容易让液态冷媒溅射和偏流，不利于液态冷媒在均液装置下方的换热盘管布液和降膜蒸发。
发明内容
本公开的目的在于提供一种罐式换热器和空调系统。
本公开的第一方面提供一种罐式换热器，设置有工质入口和工质出口，所述罐式换热器包括：
外筒；
内筒，连通于所述外筒，所述外筒与所述内筒轴线平行地设置且所述内筒之间形成环状空间；
第一换热管，盘绕于所述外筒内；
均液盘，相对于所述外筒和所述内筒固定地设置于所述环状空间且位于所述第一换热管的靠近所述罐式换热器的轴向第一端的一侧，所述均液盘的径向外端与所述外筒的筒壁形成气体通道，和/或，所述均液盘的径向内端与所述内筒的筒壁形成气体通道；和
遮挡部，相对于所述外筒和所述内筒固定地设置于所述环状空间且与所述均液盘形成轴向间隔，所述遮挡部包括与所述气体通道对应的遮挡主体，所述遮挡主体位于所述均液盘的朝向所述罐式换热器的轴向第一端的一侧，且沿所述罐式换热器的径向，所述遮挡主体完全覆盖对应的所述气体通道，所述遮挡主体的径向内端和径向外端之一与所述内筒的筒壁和所述外筒的筒壁之一密封连接，另一与所述内筒的筒壁和所述外筒的筒壁另一形成间隔。
根据本公开的一些实施例，所述均液盘的径向内端和径向外端之一与所述外筒的筒壁和所述内筒的筒壁之一形成密封，所述均液盘的径向内端和径向外端另一与所述外筒的筒壁和所述内筒的筒壁中另一形成所述气体通道。
根据本公开的一些实施例，
所述均液盘的径向外端与所述外筒的内壁密封连接，所述均液盘的径向内端与所述内筒的外壁形成所述气体通道；
所述遮挡主体的径向内端与所述内筒的外壁固定连接。
根据本公开的一些实施例，在垂直于所述罐式换热器的轴向的截面上，所述气体通道为环形。
根据本公开的一些实施例，所述遮挡主体为垂直于所述罐式换热器的轴向的挡板。
根据本公开的一些实施例，所述遮挡部还包括边缘板，所述边缘板连接于所述遮挡主体的所述自由端，且向所述罐式换热器的轴向第二端延伸。
根据本公开的一些实施例，所述遮挡主体为从所述连接端向所述自由端朝向靠近所述均液盘的方向延伸的挡板。
根据本公开的一些实施例，所述挡板为平板或弧形板。
根据本公开的一些实施例，还包括多个导流部，多个所述导流部间隔地设置于所述遮挡部的靠近所述均液盘的一侧的边缘，且向靠近所述均液盘的方向延伸。
根据本公开的一些实施例，
所述均液盘呈从所述罐式换热器的轴向第一端向轴向第二端凹入的凹槽结构；
其中，所述导流部部分地延伸至所述凹槽结构内，或，所述导流部的靠近所述罐式换热器的轴向第二端的边缘与所述凹槽结构的靠近所述罐式换热器的轴向第一端的边缘沿所述罐式换热器的轴向对齐。
根据本公开的一些实施例，所述内筒为圆筒或多边形筒。
根据本公开的一些实施例，还包括U形管，所述U形管的管中心线所在的平面沿所述罐式换热器的径向设置，所述U形管的第一端设置于所述内筒内且连通于所述内筒，所述U形管的第二端用于与气态工质管路连接以导入或导出气态工质。
根据本公开的一些实施例，
所述工质入口包括设置于所述外筒的轴向第一端的用于导入液态工质的进液口，所述工质出口包括与所述内筒连通的用于导出气态工质的气态工质口；和/或
所述工质入口包括与所述内筒连通的用于导入气态工质的气态工质口，所述工质出口包括设置于所述外筒的轴向第二端的用于导出液态工质的出液口。
根据本公开的一些实施例，还包括：
第二换热管，盘绕于所述外筒内且位于所述遮挡部的远离所述均液盘的一侧；和/或
第三换热管，盘绕于所述外筒内且位于所述第一换热管的远离所述均液盘的一侧。
根据本公开的一些实施例，所述外筒包括筒体、第一端盖和第二端盖，所述筒体沿所述罐式换热器的径向可剖分地设置，所述第一端盖封闭于所述筒体的轴向第一端，所述第二端盖封闭于所述筒体轴向第二端，所述内筒的轴向第一端连接于所述第一端盖。
本公开的第二方面一种空调系统，包括本公开第一方面所述的罐式换热器。
本公开的实施例提供的罐式换热器在内部具有液态和气态两相的工质流动的状态下，其中的气态工质可通过遮挡部和均液盘之间的轴向间隔以及气体通道上下流动，其中的液态工质可通过均液盘流下，气态工质具有独立的流动空间，因此可以降低液态工质的平均流速，从而起到降低工质在换热器内的压降的作用。并且，遮挡部可以起到回收筒壁上流下的液态工质的作用，并将筒壁上流下的液态工质导入均液盘中，从而能够减少降膜液体的浪费，利于提升换热效率。
本公开的实施例提供的空调系统具有本公开的实施例提供的罐式换热器所具有的优点。
通过以下参照附图对本公开的示例性实施例的详细描述，本公开的其它特征及其优点将会变得清楚。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本申请的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1为本公开的一些实施例的罐式换热器的结构示意图。
图2为图1所示的罐式换热器的剖面结构示意图。
图3为图2所示的罐式换热器在位置的局部放大结构示意图。
图4为本公开的一些实施例的罐式换热器的遮挡部的结构示意图。
图5为本公开的另一些实施例的罐式换热器的遮挡部的结构示意图。
图6为本公开的一些实施例的罐式换热器的导流部的结构示意图。
图7为本公开的另一些实施例的罐式换热器的结构示意图。
图1至图6中，各附图标记分别代表：
1、外筒；10、进液口；11、筒体；12、第一端盖；13、出液口；14、第二端盖；2、内筒；3、降膜区换热管；31、第一换热管；32、第二换热管；4、均液盘；40、均液孔；5、遮挡部；51、挡板；52、边缘板；6、导流部；7、U形管；70、气态工质口；8、布液器；9、第三换热管。G、气体通道。
具体实施方式
下面将结合本公开实施例中的附图，对本公开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公开一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。基于本公开中的实施例，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，都属于本公开保护的范围。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本公开的范围。同时，应当明白，为了便于描述，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，这些技术、方法和设备应 当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以具有不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
在本公开的描述中，需要理解的是，使用“第一”、“第二”等词语来限定零部件，仅仅是为了便于对相应零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本公开保护范围的限制。
在本公开的描述中，需要理解的是，方位词如“前、后、上、下、左、右”、“横向、竖向、垂直、水平”和“顶、底”等所指示的方位或位置关系通常是基于附图所示的方位或位置关系，仅是为了便于描述本公开和简化描述，在未作相反说明的情况下，这些方位词并不指示和暗示所指的装置或元件必须具有特定的方位或者以特定的方位构造和操作，因此不能理解为对本公开保护范围的限制；方位词“内、外”是指相对于各部件本身的轮廓的内外。
如图1至图7所示，本公开的一些实施例提供一种罐式换热器，罐式换热器设置有工质入口和工质出口，罐式换热器包括外筒1、内筒2、第一换热管31、均液盘4和遮挡部5。
内筒2连通于外筒1，外筒1与内筒2轴线平行地设置且内筒2之间形成环状空间。
第一换热管31盘绕于外筒1内。
均液盘4，相对于外筒1和内筒2固定地设置于环状空间且位于第一换热管31的靠近罐式换热器的轴向第一端的一侧，均液盘4的径向外端与外筒1的筒壁形成气体通道G，和/或，均液盘4的径向内端与内筒2的筒壁形成气体通道G。
遮挡部5，相对于外筒1和内筒2固定地设置于环状空间且与均液盘4形成轴向间隔，遮挡部5包括与气体通道G对应的遮挡主体，遮挡主体位于均液盘4的朝向罐式换热器的轴向第一端的一侧，且沿罐式换热器的径向，遮挡主体完全覆盖对应的气体通道G，遮挡主体的径向内端和径向外端之一为连接端，另一为自由端，所述连接端与内筒2的筒壁和外筒1的筒壁之一密封连接，所述自由端与内筒2的筒壁和外筒1的筒壁另一形成间隔。
在本公开的以下描述中，可以理解，在罐式换热器的使用状态，外筒1的轴向为上下方向，外筒1的轴向第一端为顶端，轴向第二端为底端。
本公开的罐式换热器可以是降膜式换热器、满液式换热器或者其它形式的换热器，并且可以用作蒸发器或者冷凝器。该罐式换热器可以用于空调系统，但并不限于空调系统。该罐式换热器用于空调系统中时，工质可以是冷媒。
外筒1和内筒2沿罐式换热器的轴向的尺寸可以相同也可以不同，例如，图1和图2所示的实施例中，外筒1的轴向两端封闭，内筒2沿罐式换热器的轴向的尺寸可以小于外筒1沿罐式换热器的轴向的尺寸，内筒2的轴向第一端连接于外筒1的轴向第一端，内筒2的轴向第二端与外筒1连通。在一些未图示的实施例中，外筒1和内筒2沿罐式换热器的轴向的尺寸也可以是相同的，内筒2的轴向两端均连接于外筒1，内筒2和外筒1可通过内筒2上的开口或管道等结构连通。
工质入口和工质出口可以根据换热器的选型需求设置于罐式换热器的不同位置，例如外筒1或内筒2的轴向第一端和轴向第二端。在一些实施例中，该罐式换热器用作蒸发器时，工质入口可以连通于外筒1的轴向第一端，并用于导入液态工质，工质出口可以连通于内筒2，并用于导出气态工质；在另一些实施例中，该罐式换热器用作冷凝器时，工质入口可以连通于内筒2，并用于导入气态工质，工质出口可以连通于外筒1的轴向第二端，并用于导出液态工质。
并且，同一个工质口可在该罐式换热器用作蒸发器时作为工质入口，在该罐式换热器用作冷凝器时作为工质出口，反之亦然。
均液盘4相对于外筒和内筒固定地设置，可以是直接与外筒和内筒中至少之一固定连接，也可以是通过其它部件使均液盘与外筒和内筒保持相对固定。同理，遮挡部5相对于外筒和内筒固定地设置，可以是直接与外筒和内筒中至少之一固定连接，也可以是通过其它部件使遮挡部与外筒和内筒保持相对固定。
均液盘上用于使流体通过的结构可以是多个沿罐式换热器均匀间隔地设置于均液盘4的底部的均液孔40。当然，该用于使流体通过的结构并不限于孔状，也可以是缝状或其它形状，只要能够使液态工质通过均液盘后形成多个均匀液柱或液滴即可。
气体通道G可以设置于均液盘4的径向内侧或径向外侧，或者同时设置于均液盘4的径向内侧和径向外侧，相应地，遮挡部5的数目可以是一个或两个。对于形成于均液盘4的径向内端与内筒2的筒壁之间的气体通道G，相应地，与该气体通道G对应的遮挡主体的径向内端与内筒2的筒壁密封连接，径向外端与外筒1的筒壁形成间隔；对于形成于均液盘4的径向外端与外筒1的筒壁之间的气体通道G，相应地，与该气体通道G对应的遮挡主体的径向内端与内筒2的筒壁形成间隔，径向外端与外筒 1的筒壁密封连接。
本公开的实施例的罐式换热器中，液态工质可以由设置于外筒1的轴向的第一端的进液口10导入罐式换热器，内筒可以与气态工质管路连通以使气态工质能够从罐式换热器的内筒导入或导出，因此该罐式换热器既可作为蒸发器，又可作为冷凝器。
该罐式换热器作为蒸发器时，液态工质可以由工质入口经过均液盘4流向均液盘4的下方的第一换热管31；在液态工质向下流动的过程中，即使由于偏流或溅射等原因，部分工质液滴飞到内筒和外筒的筒壁上，也可以直接流入均液盘4，或者受到遮挡部5的阻挡，由遮挡部5导入均液盘4，起到回收液态工质的作用。而随液态工质经进液口10进入罐式换热器的气态工质，或在罐式换热器内从换热管吸热后汽化形成的气态工质，可以由均液盘4和遮挡部5上方的空间经过遮挡部5和均液盘4之间的轴向间隔、气体通道G顺畅地流下。因此，通过设置均液盘4和遮挡部5，并使两者之间形成可供气体流通的空间，可以消除气态工质的压力上升对液态工质流速的影响，降低液态工质在经过均液盘4上的孔或缝时的平均流速，从而起到降低工质在换热器内的压降的作用。
该罐式换热器作为冷凝器时，气态工质由工质入口经内筒流入外筒和内筒之间形成的环状空间后，可以通过气体通道G和遮挡部之间的轴向间隔顺畅地流动，便于流至均液盘4和遮挡部5的上方冷凝换热；气态工质冷凝产生的液态工质则可以由均液盘4流下，并储存于罐式换热器的底部。
无论是作为蒸发器还是冷凝器，本公开的实施例提供的罐式换热器在内部具有液态和气态两相的工质流动的状态下，其中的气态工质可通过遮挡部和均液盘之间的轴向间隔以及气体通道上下流动，其中的液态工质可通过均液盘流下，气态工质具有独立的流动空间，因此可以降低液态工质的平均流速，从而起到降低工质在换热器内的压降的作用。并且，遮挡部可以起到回收筒壁上流下的液态工质的作用，并将筒壁上流下的液态工质导入均液盘中，从而能够减少降膜液体的浪费，利于提升换热效率。
均液盘4的径向的两端可以分别与内筒和外筒的筒壁连接，只须在均液盘与内筒和外筒中至少之一的筒壁留出气体通道即可。然而，在实现本公开的过程中，发明人发现，由于外筒与内筒在罐式换热器的第一端形成套筒结构，均液盘要实现同时与外筒和内筒的筒壁连接十分困难，不利于整个罐式换热器的组装。
在一些实施例中，如图1、图2和图7所示，均液盘4的径向内端和径向外端之一与外筒1的筒壁和内筒2的筒壁之一形成密封，均液盘4的径向内端和径向外端另 一与外筒1的筒壁和内筒2的筒壁另一形成气体通道G。
上述实施例的罐式换热器不仅能够起到提供气态工质通道、减小工质压降和回收液态工质的作用，而且，均液盘只须与外筒和内筒中的一个的筒壁单侧连接，可以减小罐式换热器的组装难度，提高组装效率，降低制造成本。
具体地，气体通道G可以设置于均液盘4的径向内侧与内筒的外壁之间。在一些实施例中，如图1至图3所示，均液盘4的径向外端与外筒1的内壁密封连接，均液盘4的径向内端与内筒2的外壁形成气体通道G；遮挡主体的径向内端与内筒2的外壁固定连接。
在一些实施例中，在垂直于罐式换热器的轴向的截面上，气体通道G为环形。
上述实施例中，气体通道G贯穿罐式换热器的周向，气态工质的通流面积较大、通流效果更好，因此，减小工质压降的效果也更好。
当然，在另一些实施例中，沿罐式换热器的周向，气体通道G也可以是不连续的，只须满足能够使气态工质流通的条件即可。例如，在垂直于罐式换热器的轴向的截面上，气体通道G可以呈现为几个不连续的扇环形。
在一些实施例中，如图3所示，遮挡主体为垂直于罐式换热器的轴向的挡板51。
根据以上设置，在罐式换热器的使用状态下，挡板51水平地设置。图3所示的实施例中，挡板51的径向内端与内筒2的外壁固定连接且形成密封。
在一些实施例中，如图4所示，遮挡部5还包括边缘板52，边缘板52连接于遮挡主体的所述自由端，且向罐式换热器的轴向第二端延伸。
根据以上设置，在罐式换热器的使用状态下，挡板51水平地设置，边缘板52可以与挡板51垂直设置或与挡板51呈一定夹角，且能够起到一定的导流作用。图4所示的实施例中，挡板51的径向内端与内筒2的外壁固定连接且形成密封，边缘板52连接于挡板51的径向外端且与挡板51垂直设置，遮挡部5整体上呈L形。
在一些实施例中，遮挡主体为从连接端向自由端朝向靠近均液盘4的方向延伸的挡板51。
根据以上设置，在罐式换热器的使用状态下，挡板51自上而下地延伸且位于上方的一端与筒壁密封连接，形成类似于屋檐形状的结构，便于筒壁上的积聚的液态工质流向均液盘，从而起到良好的导流和回收作用。在一些实施例中，挡板51为平板或曲面板。
图5所示的实施例中，挡板51为平板，挡板51的径向内端与内筒2的外壁固定 连接且形成密封，挡板51从径向内端向径向外端自上而下地倾斜延伸。在一些未图示的实施例中，挡板51当然也可以采用曲面板，例如，挡板51可以是沿罐式换热器的径向的截面为圆弧形、抛物线形的曲面板。
在一些实施例中，如图6所示，罐式换热器还包括多个导流部6，多个导流部6间隔地设置于遮挡部5的靠近均液盘4的一侧的边缘，且向靠近均液盘4的方向延伸。
上述实施例中，导流部由遮挡部的靠近均液盘的一侧的边缘向靠近均液盘的方向延伸，例如，图6所示的实施例中，导流部6可以呈现为上下竖直延伸的柱状结构，在一些未图示的实施例中，导流部也可以是倾斜设置的。通过设置向靠近均液盘的方向延伸的多个间隔的导流部，通过遮挡部回收的液态工质可以在导流部的引导下流入均液盘，起到良好的导流作用，并且沿罐式换热器的径向，能够起到一定的阻挡作用。因此，导流部可以防止气态工质在流动时，遮挡部的径向边缘的工质液滴在滴落过程中被气态工质吹入气体通道G，从而可以进一步减少液态工质的浪费。
在一些实施例中，均液盘4呈从罐式换热器的轴向第一端向轴向第二端凹入的凹槽结构。其中，导流部6部分地延伸至凹槽结构内，或，导流部6的靠近罐式换热器的轴向第二端的边缘与凹槽结构的靠近罐式换热器的轴向第一端的边缘沿罐式换热器的轴向对齐。
根据上述设置，在罐式换热器的使用状态下，导流部6的底缘不高于凹槽结构侧壁的顶缘，可以进一步增强导流部的阻挡作用，更好地防止气态工质将工质液滴吹入气体通道。
在一些实施例中，内筒2为圆筒或多边形筒。其中，图1和图2示出了内筒为圆筒时的情形，图7示出了内筒为多边形筒时的情形。
多边形筒可以是四边形筒，例如长方形筒或正方形筒，也可以是五边形筒、六边形筒、八边形筒等。
在一些实施例中，如图1、图2和图7所示，罐式换热器还包括U形管7，U形管7的管中心线所在的平面沿罐式换热器的径向设置，U形管7的第一端设置于内筒2内且连通于内筒2，U形管7的第二端用于与气态工质管路连接以导入或导出气态工质。
为了将弯管段的半径相同的U形管装入内筒，相比于圆形的内筒，多边形的内筒所需的轴向截面的面积更小。因此，通过将内筒设置为多边形筒，利于增大气体通道G的通流面积，利于减小工质压降。考虑到U形管的管径过小时管内气体流速会过高， 而U形管的管径受弯管段的半径的限制，通过将内筒设置为多边形筒，可以在不减小弯管段的半径的前提下，使U形管的管径尽可能大，利于降低气态工质的流速，提升换热性能。
相比于将U形管装入圆形筒，将U形管装入多边形筒的轴向截面的面积更小。降低气态工质在气体通道G内的流速。
在一些实施例中，如图1、图2和图7所示，工质入口包括设置于外筒1的轴向第一端的用于导入液态工质的进液口10，工质出口包括与内筒2连通的用于导出气态工质的气态工质口70，和/或，工质入口包括与内筒2连通的用于导入气态工质的气态工质口70，工质出口包括设置于外筒1的轴向第二端的用于导出液态工质的出液口13。
以上实施例中，气态工质口70可以位于U形管7的第二端。
在设置第一换热管31的基础上，罐式换热器当然也可以包括设置于沿罐式换热器的轴向的不同位置的更多的换热管。
在一些实施例中，罐式换热器还包括第二换热管32和/或第三换热管9。第二换热管32盘绕于外筒1内且位于遮挡部5的远离均液盘4的一侧。第三换热管9盘绕于外筒1内且位于第一换热管31的远离均液盘4的一侧。
图1、图2和图7所示的实施例中，罐式换热器包括第一换热管31、第二换热管32和第三换热管9，且罐式换热器还包括布液器8。沿罐式换热器的轴向，布液器8、第二换热管32、遮挡部5、均液盘4、第一换热管31和第三换热管9自上而下依次设置。第一换热管31和第二换热管32共同构成降膜区换热管3，第三换热管9构成满液区换热管。
图1、图2和图7所示的实施例中，该罐式换热器用作蒸发器时，液态工质由进液口10、布液器8进入外筒1，与第二换热管32换热后，液态工质蒸发产生的气态工质由遮挡部5和均液盘4之间的轴向间隔、气体通道G流向内筒2和U形管7，由气态工质口70导出，其余液态工质经过均液盘4流向第一换热管31和第三换热管9继续换热；该罐式换热器用作冷凝器时，气态工质由气态工质口70、U形管7、内筒2进入外筒1，在外筒1与第三换热管9和第一换热管31换热后，气态工质冷凝产生的液态工质储存于罐式换热器的底部，并且可以由出液口13导出，其余气态工质由气体通道G、遮挡部5和均液盘4之间的轴向间隔流向外筒1和内筒2之间的环形区域，与第二换热管32继续换热。
在一些实施例中，如图1、图2和图7所示，外筒1包括筒体11、第一端盖12和第二端盖14，筒体11沿罐式换热器的径向可剖分地设置，第一端盖12封闭于筒体11的轴向第一端，第二端盖14封闭于筒体11轴向第二端，内筒2的轴向第一端连接于第一端盖12。
对于具有图1、图2和图7所示的结构的罐式换热器，罐式换热器在组装时，根据发明人已知的相关技术，为了将盘绕的换热管安装至外筒内，一般需要将外筒的筒体11沿图1、图2和图7所示的剖面剖分为两个半壳体，将换热管一端的管口塞入其中一个半壳体上对应的开孔，而后将另一个半壳体盖上并与前一个半壳体固定连接，最后将两个端盖封闭连接于筒体的轴向两端。因此，均液盘很难同时与内筒与外筒密封连接。
基于本公开上述实施例的方案，均液盘4只需与外筒1密封连接，而内筒2因为与第一端盖12连接，而不与均液盘4连接，因此内筒2安装时只需随第一端盖12一同由上至下伸入筒体11即可，从而可以进一步降低均液盘的安装难度。
罐式换热器例如为降膜蒸发器。
本公开的一些实施例还提供一种空调系统，包括前述罐式换热器。本公开的实施例提供的空调系统相应地具有前述罐式换热器的优点。
最后应当说明的是：以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (16)

  1. 一种罐式换热器，设置有工质入口和工质出口，所述罐式换热器包括：
    外筒(1)；
    内筒(2)，连通于所述外筒(1)，所述外筒(1)与所述内筒(2)轴线平行地设置且与所述内筒(2)之间形成环状空间；
    第一换热管(31)，盘绕于所述外筒(1)内；
    均液盘(4)，相对于所述外筒(1)和所述内筒(2)固定地设置于所述环状空间且位于所述第一换热管(31)的靠近所述罐式换热器的轴向第一端的一侧，所述均液盘(4)的径向外端与所述外筒(1)的筒壁形成气体通道(G)，和/或，所述均液盘(4)的径向内端与所述内筒(2)的筒壁形成气体通道(G)；和
    遮挡部(5)，相对于所述外筒(1)和所述内筒(2)固定地设置于所述环状空间且与所述均液盘(4)形成轴向间隔，所述遮挡部(5)包括与所述气体通道(G)对应的遮挡主体，所述遮挡主体位于所述均液盘(4)的朝向所述罐式换热器的轴向第一端的一侧，且沿所述罐式换热器的径向，所述遮挡主体完全覆盖对应的所述气体通道(G)，所述遮挡主体的径向内端和径向外端之一为连接端，另一为自由端，所述连接端与所述内筒(2)的筒壁和所述外筒(1)的筒壁之一密封连接，所述自由端与所述内筒(2)的筒壁和所述外筒(1)的筒壁另一形成间隔。
  2. 根据权利要求1所述的罐式换热器，其中，所述均液盘(4)的径向内端和径向外端之一与所述外筒(1)的筒壁和所述内筒(2)的筒壁之一形成密封，所述均液盘(4)的径向内端和径向外端另一与所述外筒(1)的筒壁和所述内筒(2)的筒壁中另一形成所述气体通道(G)。
  3. 根据权利要求2所述的罐式换热器，其中，
    所述均液盘(4)的径向外端与所述外筒(1)的内壁密封连接，所述均液盘(4)的径向内端与所述内筒(2)的外壁形成所述气体通道(G)；
    所述遮挡主体的径向内端与所述内筒(2)的外壁固定连接。
  4. 根据前述权利要求中任一项所述的罐式换热器，其中，在垂直于所述罐式换 热器的轴向的截面上，所述气体通道(G)为环形。
  5. 根据前述权利要求中任一项所述的罐式换热器，其中，所述遮挡主体为垂直于所述罐式换热器的轴向的挡板(51)。
  6. 根据权利要求5所述的罐式换热器，其中，所述遮挡部(5)还包括边缘板(52)，所述边缘板(52)连接于所述遮挡主体的所述自由端，且向所述罐式换热器的轴向第二端延伸。
  7. 根据前述权利要求中任一项所述的罐式换热器，其中，所述遮挡主体为从所述连接端向所述自由端朝向靠近所述均液盘(4)的方向延伸的挡板(51)。
  8. 根据权利要求7所述的罐式换热器，其中，所述挡板(51)为平板或曲面板。
  9. 根据前述权利要求中任一项所述的罐式换热器，还包括多个导流部(6)，多个所述导流部(6)间隔地设置于所述遮挡部(5)的靠近所述均液盘(4)的一侧的边缘，且向靠近所述均液盘(4)的方向延伸。
  10. 根据权利要求9所述的罐式换热器，其中，
    所述均液盘(4)呈从所述罐式换热器的轴向第一端向轴向第二端凹入的凹槽结构；
    其中，所述导流部(6)部分地延伸至所述凹槽结构内，或，所述导流部(6)的靠近所述罐式换热器的轴向第二端的边缘与所述凹槽结构的靠近所述罐式换热器的轴向第一端的边缘沿所述罐式换热器的轴向对齐。
  11. 根据前述权利要求中任一项所述的罐式换热器，其中，所述内筒(2)为圆筒或多边形筒。
  12. 根据权利要求11所述的罐式换热器，还包括U形管(7)，所述U形管(7)的管中心线所在的平面沿所述罐式换热器的径向设置，所述U形管(7)的第一端设 置于所述内筒(2)内且连通于所述内筒(2)，所述U形管(7)的第二端用于与气态工质管路连接以导入或导出气态工质。
  13. 根据前述权利要求中任一项所述的罐式换热器，其中，
    所述工质入口包括设置于所述外筒(1)的轴向第一端的用于导入液态工质的进液口(10)，所述工质出口包括与所述内筒(2)连通的用于导出气态工质的气态工质口(70)；和/或
    所述工质入口包括与所述内筒(2)连通的用于导入气态工质的气态工质口(70)，所述工质出口包括设置于所述外筒(1)的轴向第二端的用于导出液态工质的出液口(13)。
  14. 根据前述权利要求中任一项所述的罐式换热器，还包括：
    第二换热管(32)，盘绕于所述外筒(1)内且位于所述遮挡部(5)的远离所述均液盘(4)的一侧；和/或
    第三换热管(9)，盘绕于所述外筒(1)内且位于所述第一换热管(31)的远离所述均液盘(4)的一侧。
  15. 根据前述权利要求中任一项所述的罐式换热器，其中，所述外筒(1)包括筒体(11)、第一端盖(12)和第二端盖(14)，所述筒体(11)沿所述罐式换热器的径向可剖分地设置，所述第一端盖(12)封闭于所述筒体(11)的轴向第一端，所述第二端盖(14)封闭于所述筒体(11)轴向第二端，所述内筒(2)的轴向第一端连接于所述第一端盖(12)。
  16. 一种空调系统，包括根据前述权利要求中任一项所述的罐式换热器。
PCT/CN2023/119689 2022-10-12 2023-09-19 罐式换热器和空调系统 WO2024078274A1 (zh)

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