CN113790614A

CN113790614A - Tank type heat exchanger and heat pump system

Info

Publication number: CN113790614A
Application number: CN202111232668.5A
Authority: CN
Inventors: 马剑; 李丰; 张铁钢; 颜利波
Original assignee: GD Midea Heating and Ventilating Equipment Co Ltd; Hefei Midea Heating and Ventilating Equipment Co Ltd
Current assignee: GD Midea Heating and Ventilating Equipment Co Ltd; Hefei Midea Heating and Ventilating Equipment Co Ltd
Priority date: 2021-10-22
Filing date: 2021-10-22
Publication date: 2021-12-14

Abstract

The application relates to a tank heat exchanger and a heat pump system, and relates to the field of heat exchange devices. The tank type heat exchanger comprises an outer cylinder; the inner cylinder is arranged inside the outer cylinder; the partition plate is arranged in the outer barrel so as to divide the space between the outer barrel and the inner barrel into a first chamber and a second chamber, and the second chamber is positioned above the first chamber; the heat exchange tube is arranged in the first cavity and spirally wound outside the inner cylinder; the liquid inlet pipe is used for providing liquid refrigerant to the second chamber; the gas outlet pipe is used for sucking the gaseous refrigerant from the first chamber; the partition plate is provided with a spraying hole, and the spraying hole is used for spraying the liquid refrigerant of the second cavity to the heat exchange tube. In the pot-type heat exchanger of this application, liquid refrigerant sprays to the heat exchange tube, has improved the utilization ratio in the main pipe district of heat exchange tube, has improved heat exchange efficiency. All liquid refrigerants enter the first cavity in a spraying mode, the liquid refrigerants are fully contacted with the heat exchange pipe, and the heat exchange effect is good.

Description

Tank type heat exchanger and heat pump system

Technical Field

The application relates to the field of heat exchangers, in particular to a tank type heat exchanger and a heat pump system.

Background

The heat pump system is a common heat exchange system and has a wide application range. In a heat pump system, a condenser and an evaporator are main heat exchange elements, and heat is absorbed or released through the phase change process of a refrigerant.

Compared with the traditional shell and tube heat exchanger, the tank type heat exchanger has the advantages of small volume and compact structure. The tank type heat exchanger in the prior art has low heat exchange efficiency when being used as an evaporator.

Disclosure of Invention

An object of the embodiment of the application is to provide a tank heat exchanger and a heat pump system, the tank heat exchanger can be used as an evaporator in the heat pump system, and has high heat exchange efficiency.

In a first aspect, the present application provides a can heat exchanger comprising an outer drum; the inner cylinder is arranged inside the outer cylinder; the partition plate is arranged in the outer barrel so as to divide the space between the outer barrel and the inner barrel into a first chamber and a second chamber, and the second chamber is positioned above the first chamber; the heat exchange tube is arranged in the first cavity and spirally wound outside the inner cylinder; the liquid inlet pipe is used for providing liquid refrigerant to the second chamber; the gas outlet pipe is used for sucking the gaseous refrigerant from the first chamber; the partition plate is provided with a spraying hole, and the spraying hole is used for spraying the liquid refrigerant of the second cavity to the heat exchange tube.

In above-mentioned technical scheme, when the pot-type heat exchanger of this application is used as the evaporimeter, the feed liquor pipe provides liquid refrigerant to in the second cavity, liquid refrigerant sprays to the heat exchange tube from the top of heat exchange tube through the hole that sprays that sets up in the baffle, thereby adhere to the part by liquid refrigerant submergence not of heat exchange tube, and form the liquid film, the liquid film is cooled down to the medium in the heat exchange tube through the phase transition heat absorption process when evaporating for gaseous refrigerant, the dry tube district of heat exchange tube (not by liquid refrigerant adnexed part) has been reduced, the heat transfer area has been increased, and the heat exchange efficiency when pot-type heat exchanger is used as the evaporimeter has been improved. All liquid refrigerants enter the first cavity in a spraying mode, so that the liquid refrigerants are fully contacted with a main pipe area of the heat exchange pipe, and the heat exchange effect is good.

As an optional technical scheme of this application embodiment, spray the hole and be provided with a plurality ofly, a plurality ofly spray the hole and distribute and be located the top of heat exchange tube along the circumference of baffle.

In the technical scheme, the plurality of spraying holes are formed in the circumferential direction of the partition plate, so that the liquid refrigerant can be uniformly sprayed to the heat exchange tube.

As an optional technical scheme of this application embodiment, among a plurality of spray holes, the area of keeping away from the spray hole of feed liquor pipe is greater than the area of the spray hole of being close to the feed liquor pipe.

In the technical scheme, the farther the distance from the liquid inlet pipe is, the larger the area of the spraying holes is, the closer the distance from the liquid inlet pipe is, the smaller the area of the spraying holes is, and the more average the flow of the liquid refrigerant of each spraying hole is ensured.

As an optional technical scheme of the embodiment of the application, in the plurality of spraying holes, the concentration degree of the spraying holes far away from the liquid inlet pipe is greater than that of the spraying holes close to the liquid inlet pipe.

In the technical scheme, the farther the distance from the liquid inlet pipe is, the more dense the spraying holes are, and the closer the distance from the liquid inlet pipe is, the more sparse the spraying holes are, so that the flow of the liquid refrigerant in each spraying hole is ensured to be relatively average.

As an optional technical scheme of the embodiment of the application, one end of the air outlet pipe extends into the first chamber, and the projection of the air outlet pipe on the partition plate is not overlapped with the spraying hole.

In the technical scheme, because the projection of the air outlet pipe on the partition plate is not overlapped with the spraying holes, the spraying holes can not directly spray the liquid refrigerant on the air outlet pipe in the spraying process, and the air outlet pipe can not directly discharge the liquid refrigerant which does not exchange heat with the heat exchange pipe, so that the liquid refrigerant can fully exchange heat with the heat exchange pipe, and the heat exchange efficiency of the tank-type heat exchanger is improved.

As an optional technical scheme of the embodiment of the application, the tank heat exchanger further comprises a baffle plate, wherein the baffle plate is connected to the inner wall of the outer cylinder and covers one end of the air outlet pipe so as to prevent the liquid refrigerant sprayed from the spraying holes from being discharged through the air outlet pipe.

In the technical scheme, the baffle is arranged at the air outlet pipe, so that the liquid refrigerant can not be directly sprayed on the air outlet pipe in the spraying process of the spraying hole, the liquid refrigerant which does not exchange heat with the heat exchange pipe can not be directly discharged from the air outlet pipe, the liquid refrigerant can fully exchange heat with the heat exchange pipe, and the heat exchange efficiency of the tank-type heat exchanger is improved.

As an optional technical scheme of the embodiment of the application, the first chamber and the second chamber are not communicated with the inner space of the inner cylinder.

In the technical scheme, the first cavity and the second cavity are not communicated with the inner space of the inner cylinder, so that the liquid refrigerant cannot enter the inner space of the inner cylinder, and the liquid refrigerant is accumulated in the first cavity and fully contacted with the heat exchange tube, thereby improving the heat exchange efficiency.

As an optional technical scheme of the embodiment of the application, the upper end of the inner cylinder is closed by a partition plate.

In the technical scheme, the partition plate separates the first chamber and the second chamber on the one hand, and seals the upper end of the inner cylinder on the other hand, so that two functions are realized by the same partition plate, the number of parts is reduced, and the tank type heat exchanger is simple and compact in structure.

As an optional technical scheme of the embodiment of the application, the outer barrel comprises an outer barrel bottom wall, and the lower end of the inner barrel is closed by the outer barrel bottom wall.

In the scheme, the lower end of the inner cylinder is sealed through the bottom wall of the outer cylinder, so that the number of parts is reduced, and the structure of the tank type heat exchanger is simple and compact.

As an optional technical scheme of the embodiment of the application, the inner cylinder comprises an inner cylinder bottom wall, the outer cylinder comprises an outer cylinder bottom wall, and a gap is formed between the inner cylinder bottom wall and the outer cylinder bottom wall.

In the scheme, the lower end of the inner cylinder is sealed by the bottom wall of the inner cylinder, so that the sealing property between the inner cylinder and the outer cylinder is improved. Simultaneously, have the clearance between inner tube diapire and the urceolus diapire, increased the volume of first cavity for can coil more heat exchange tubes in the first cavity, further increased tank heat exchanger's heat exchange efficiency.

As an optional technical scheme of the embodiment of the application, the partition plate is sleeved on the inner cylinder.

In the technical scheme, the partition plate is sleeved on the inner cylinder to form the annular second chamber, and the cross sectional area of the annular second chamber is smaller, so that the liquid refrigerant can rapidly flow to the spraying holes far away from the liquid inlet pipe, and the whole spraying holes are covered.

As an optional technical scheme of the embodiment of the application, the outer cylinder comprises an outer cylinder top wall and an outer cylinder bottom wall, the upper end of the inner cylinder is sealed by the outer cylinder top wall, and the lower end of the inner cylinder is sealed by the outer cylinder bottom wall.

In the technical scheme, the upper end and the lower end of the inner cylinder are respectively sealed by the top wall and the bottom wall of the outer cylinder, so that the number of parts is reduced, and the structure of the tank type heat exchanger is compact.

As an optional technical scheme of the embodiment of the application, the upper end and the lower end of the inner cylinder are both open and are communicated with the outside.

In the technical scheme, the upper end and the lower end of the inner barrel are directly communicated with the external environment, air in the external environment can circulate from the inner barrel, partial heat is taken away, and the heat exchange efficiency of the tank type heat exchanger is further improved.

As an optional technical scheme of this application embodiment, the one end and the first cavity intercommunication of outlet duct, the other end and the inner space intercommunication of inner tube of outlet duct, pot-type heat exchanger still include the muffler, and the muffler sets up in the inner tube, and muffler and inner tube form vapour and liquid separator.

In the technical scheme, the gas-liquid separator is formed by the gas return pipe and the inner barrel, so that the structure and space of the tank type heat exchanger are reasonably utilized to integrate the gas-liquid separation function. When the tank type heat exchanger is used as an evaporator in the heat pump system, an additional gas-liquid separator is not needed, the number of components of the heat pump system is reduced, and the structure of the heat pump system is simplified.

As an optional technical scheme of this application embodiment, the lower extreme of inner tube is equipped with first oil return hole, and the muffler is equipped with the second oil return hole, and first oil return hole and second oil return hole are arranged in introducing the muffler with the lubricating oil in the liquid refrigerant in the first chamber.

In the technical scheme, lubricating oil in the liquid refrigerant enters the air return pipe through the first oil return hole and the second oil return hole and is sucked to the compressor together with the gaseous refrigerant, and the structure and the space of the tank type heat exchanger are reasonably utilized to integrate an oil return function.

In a second aspect, embodiments of the present application further provide a heat pump system, which includes a compressor; a condenser; an expansion valve; the above-described tank heat exchanger; the outlet of the compressor is communicated with the inlet of the condenser, the outlet of the condenser is communicated with the liquid inlet pipe of the tank type heat exchanger through the expansion valve, and the air outlet pipe of the tank type heat exchanger is communicated with the inlet of the compressor.

The heat pump system has the advantages that the heat pump system is high in heat exchange efficiency due to the fact that the tank type heat exchanger is arranged.

As an optional technical scheme of the embodiment of the application, the heat pump system further comprises a gas-liquid separator, and an air outlet pipe of the tank type heat exchanger is communicated with an inlet of the compressor through the gas-liquid separator.

In the technical scheme, the gas-liquid separator is used for separating the gaseous refrigerant from the liquid refrigerant so as to prevent the liquid refrigerant from entering the compressor and generating liquid impact, and prolong the service life of the compressor.

In a third aspect, embodiments of the present application further provide a heat pump system, which includes a compressor; a condenser; an expansion valve; the above-described tank heat exchanger; the outlet of the compressor is communicated with the inlet of the condenser, the outlet of the condenser is communicated with a liquid inlet pipe of the tank type heat exchanger through an expansion valve, and an air return pipe of the tank type heat exchanger is communicated with the inlet of the compressor.

The heat pump system has the advantages that the heat pump system is high in heat exchange efficiency due to the fact that the tank type heat exchanger is arranged. Meanwhile, the tank type heat exchanger is integrated with a gas-liquid separator, and the gas-liquid separator is used for separating gaseous refrigerants and liquid refrigerants so as to prevent the liquid refrigerants from entering the compressor and generating liquid impact, and prolong the service life of the compressor.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained from the drawings without inventive effort.

FIG. 1 is a schematic structural diagram of a tank heat exchanger provided in an embodiment of the present application;

FIG. 2 is a schematic view of an inner cylinder and a bottom wall of an outer cylinder having a gap according to an embodiment of the present application;

fig. 3 is a schematic view illustrating a partition plate sleeved on an inner cylinder according to an embodiment of the present disclosure;

FIG. 4 is a schematic view of the inner barrel in communication with the external environment according to an embodiment of the present disclosure;

FIG. 5 is a schematic diagram of an increase in the area of spray holes provided in an embodiment of the present application;

FIG. 6 is a schematic view of an increased density of spray holes provided in accordance with an embodiment of the present application;

fig. 7 is a schematic view of a long spray hole according to an embodiment of the present disclosure;

fig. 8 is a schematic view illustrating oblique spray holes provided in an embodiment of the present application;

FIG. 9 is a schematic illustration of an inner barrel integrated gas-liquid separator as provided in an embodiment of the present application;

fig. 10 is a system diagram of a heat pump system according to a second embodiment of the present application;

fig. 11 is a system schematic diagram of a heat pump system according to a third embodiment of the present application.

Icon: 10-can heat exchanger; 100-outer cylinder; 110-outer barrel side wall; 120-the top wall of the outer cylinder; 130-the bottom wall of the outer barrel; 200-an inner cylinder; 210-inner barrel sidewall; 220-inner barrel bottom wall; 300-a separator; 310-spraying holes; 320-a first chamber; 330-a second chamber; 400-heat exchange tube; 500-liquid inlet pipe; 600-an air outlet pipe; 700-a baffle; 800-muffler; 810-a first oil return hole; 820-a second oil return hole; 830-a gas phase space; 840-liquid phase space; 1000-heat pump system; 20-a compressor; 30-a condenser; 40-an expansion valve; 50-user terminal; 60-gas-liquid separator.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. It is to be understood that the embodiments described are only a few embodiments of the present application and not all embodiments. The components of the embodiments of the present application, generally described and illustrated in the figures herein, can be arranged and designed in a wide variety of different configurations.

In the description of the present application, it should be noted that the terms "inside", "outside", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings or orientations or positional relationships that the products of the application usually place when using, and are only used for convenience in describing the present application and simplifying the description, but do not indicate or imply that the devices or elements that are referred to must have a specific orientation, be constructed in a specific orientation, and operate, and thus, should not be construed as limiting the present application. Furthermore, the terms "first," "second," and the like are used merely to distinguish one description from another, and are not to be construed as indicating or implying relative importance.

In the description of the present application, it is also to be noted that, unless otherwise explicitly specified or limited, the terms "disposed" and "connected" are to be interpreted broadly, e.g., as being either fixedly connected, detachably connected, or integrally connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood in a specific case by those of ordinary skill in the art.

In a heat pump system, a condenser and an evaporator are main heat exchange elements, and a refrigerant circulates among a compressor, the condenser and the evaporator. The condenser and the evaporator both rely on the phase change process of the refrigerant to absorb or release heat in the working process. The gaseous refrigerant is liquefied in the condenser to release heat, and the liquid refrigerant is gasified in the evaporator to absorb heat.

In a medium-and-small-sized heat pump system used in application scenes such as floor heating and air conditioning for household and household, a tank-type heat exchanger with a compact structure and a small occupied space is mostly used as an evaporator and a condenser in the heat pump system in order to reduce the occupied space of the heat pump system.

In the working process of the tank type heat exchanger, a shell pass passes through a refrigerant, a tube pass passes through media such as water and air, and heat exchange is carried out through the phase change process of the refrigerant. Compared with the traditional shell and tube heat exchanger, the tank type heat exchanger has the advantages of small volume, compact structure, high heat exchange efficiency and the like.

However, when the can-type heat exchanger is used as an evaporator, liquid refrigerant can only fill the space 1/5 in the shell pass, and the rest of the space in the shell pass is filled with gaseous refrigerant, so that only a small part of the tube pass can be immersed in the liquid refrigerant and efficiently exchanges heat with the liquid refrigerant, and most of the rest of the tube pass is located in the space filled with the gaseous refrigerant in the shell pass, and the tube pass of which part is directly contacted with the gaseous refrigerant can be understood as a main tube area which cannot be contacted with the liquid refrigerant and exchanges heat.

Because the dry pipe area can not effectively contact with liquid refrigerant for the medium in the dry pipe area can not change into the phase transition heat absorption process of gaseous refrigerant through liquid refrigerant and carry out the heat transfer, and then has leaded to the heat exchange efficiency when whole pot heat exchanger is as the evaporimeter lower. In the prior art, the tank heat exchanger is mainly used as a condenser in a heat pump system, but is not basically used as an evaporator.

In view of this, the present application provides a tank heat exchanger that can be used as an evaporator in a heat pump system. Specifically, the tank heat exchanger sprays liquid refrigerant through the heat exchange tube (tube side) in the shell side, so that the liquid refrigerant can be attached to the heat exchange tube and form a liquid film, thereby greatly reducing the dry tube area of the heat exchange tube and improving the heat exchange efficiency of the tank heat exchanger as an evaporator.

The tank heat exchanger and the heat pump system of the present application will be described in detail below with reference to the accompanying drawings.

In one aspect, as shown in fig. 1 to 4, the present application provides a tank heat exchanger 10, where the tank heat exchanger 10 includes an outer cylinder 100, an inner cylinder 200, a partition 300, a heat exchange pipe 400, a liquid inlet pipe 500, and a gas outlet pipe 600.

Specifically, as shown in fig. 1, the inner tube 200 is disposed inside the outer tube 100, the partition plate 300 is also disposed inside the outer tube 100 and divides a space between the outer tube 100 and the inner tube 200 into a first chamber 320 and a second chamber 330, the second chamber 330 is located above the first chamber 320, and the heat exchange tube 400 is disposed in the first chamber 320 and spirally wound outside the inner tube 200. The liquid inlet pipe 500 is disposed in the tub 100 to provide liquid refrigerant to the second chamber 330, and the gas outlet pipe 600 is disposed in the tub 100 to draw gaseous refrigerant from the first chamber 320. The partition plate 300 is provided with spray holes 310, and the spray holes 310 are used for spraying the liquid refrigerant in the second chamber 330 to the heat exchange tube 400, so as to form a liquid film on the heat exchange tube 400 and reduce a main tube area of the heat exchange tube 400.

It should be noted that the space between the outer cylinder 100 and the inner cylinder 200 is the shell side of the tank heat exchanger 10, that is, the first chamber 320 and the second chamber 330 jointly form the shell side of the tank heat exchanger 10, and the heat exchange tube 400 is the tube side of the tank heat exchanger 10.

As shown in fig. 1 to 4, the X direction in the drawings is a height direction of the tank heat exchanger 10, and alternatively, the height direction of the tank heat exchanger 10 may be a vertical direction.

As shown in fig. 1, the outer cylinder 100 is enclosed by an outer cylinder side wall 110 extending in the X direction, and an outer cylinder top wall 120 and an outer cylinder bottom wall 130 oppositely arranged at both ends of the outer cylinder side wall 110 in the X direction, and the outer cylinder top wall 120 is located above the outer cylinder bottom wall 130. The liquid inlet pipe 500 and the gas outlet pipe 600 are disposed on the outer tub 100, and the rest of the outer tub 100 except the liquid inlet pipe 500 and the gas outlet pipe 600 is closed to prevent the refrigerant inside the outer tub 100 from leaking. Specifically, the outer cylinder sidewall 110 may be a column, such as a cylinder, a prism, or the like, or the outer cylinder sidewall 110 may also be a barrel, where the barrel means that the diameter of the middle of the outer cylinder sidewall 110 is larger than the diameters of the two ends of the outer cylinder sidewall 110 along the X direction.

Accordingly, as shown in FIG. 1, the inner barrel 200 includes an inner barrel sidewall 210, and the inner barrel sidewall 210 can extend along the X direction (as shown in FIG. 1) or along a direction perpendicular to the X direction (not shown). Specifically, the inner cylinder sidewall 210 can be a cylindrical shape, such as a cylinder, a prism, etc., or the outer cylinder sidewall 110 can also be a barrel shape.

The inner cylinder 200 is disposed inside the outer cylinder 100, that is, the inner cylinder sidewall 210 is disposed inside the outer cylinder 100, and when the inner cylinder sidewall 210 extends along the X direction, the central axis of the inner cylinder sidewall 210 may coincide with the central axis of the outer cylinder 100, or the central axis of the inner cylinder sidewall 210 may be parallel to the central axis of the outer cylinder 100, that is, the inner cylinder sidewall 210 and the outer cylinder 100 are disposed eccentrically.

Taking the inner cylinder sidewall 210 extending along the X direction as an example, as shown in fig. 1, one end of the bottom of the inner cylinder sidewall 210 can be connected to the outer cylinder bottom wall 130, in this case, the outer cylinder bottom wall 130 is the bottom wall of the inner cylinder 200, and the bottom of the inner cylinder sidewall 210 is closed by the outer cylinder bottom wall 130. As shown in fig. 2, the inner cylinder 200 may further include an inner cylinder bottom wall 220, the inner cylinder bottom wall 220 is disposed at the bottom of the inner cylinder side wall 210 to close the bottom of the inner cylinder side wall 210, and at this time, a certain gap may be left between the inner cylinder bottom wall 220 and the outer cylinder bottom wall 130 along the X direction, or may be attached to each other.

Also taking the inner cylinder sidewall 210 extending along the X direction as an example, as shown in fig. 2, one end of the top of the inner cylinder sidewall 210 may be further connected to a partition 300, in which case, the partition 300 is the top wall of the inner cylinder 200, and the top of the inner cylinder sidewall 210 is closed by the partition 300. As shown in fig. 3, one end of the top of the inner cylinder sidewall 210 can be connected to the outer cylinder top wall 120, in this case, the outer cylinder top wall 120 is the top wall of the inner cylinder 200, and the top of the inner cylinder sidewall 210 is closed by the outer cylinder top wall 120.

Further, both ends of the inner cylinder sidewall 210, i.e. the top and the bottom of the inner cylinder sidewall 210, may not be closed, and it can be understood that both ends of the inner cylinder sidewall 210 are directly communicated with the external environment. For example, as shown in fig. 4, one end of the bottom of the inner cylinder sidewall 210 is connected to the outer cylinder bottom wall 130, the outer cylinder bottom wall 130 is ring-shaped, and the bottom of the inner cylinder 200 is directly communicated with the external environment, or two ends of the inner cylinder sidewall 210 are respectively connected to the outer cylinder top wall 120 and the outer cylinder bottom wall 130, the outer cylinder top wall 120 and the outer cylinder bottom wall 130 are both ring-shaped, the inner cylinder sidewall 210 passes through the partition plate 300, that is, the partition plate 300 is sleeved on the inner cylinder sidewall 210, and two ends of the inner cylinder 200 are both directly communicated with the external environment, at this time, the inner cylinder 200 passes through the outer cylinder 100, and in the view along the X direction, the tank heat exchanger 10 is ring-shaped.

It is noted that the inner space of the inner cylinder 200 and the space between the outer cylinder 100 and the inner cylinder 200 are not communicated regardless of the connection relationship between the inner cylinder 200 and the outer cylinder 100.

The outer cylinder 100 and the inner cylinder 200 may be made of metal, such as cast iron, steel, aluminum, copper, or alloy, and the outer cylinder 100 and the inner cylinder 200 may be made of ABS (Acrylonitrile Butadiene Styrene) engineering plastic, nylon, or the like. When the outer cylinder 100 and the inner cylinder 200 are made of iron or steel, the outer cylinder 100 and the inner cylinder 200 may be connected by welding.

As shown in fig. 1 to 4, the partition 300 is disposed inside the outer tub 100, and the partition 300 does not extend into the inner space of the inner tub 200, i.e., the partition 300 is used to divide the space between the outer tub 100 and the inner tub 200 into the first chamber 320 and the second chamber 330, and the first chamber 320 and the second chamber 330 are in a mutually isolated relationship with the inner space of the inner tub 200, i.e., the first chamber 320 and the second chamber 330 are not communicated with the inner space of the inner tub 200.

The second chamber 330 is located above the first chamber 320, that is, the second chamber 330 is located above the first chamber 320 along a vertical direction, that is, along a direction of action of gravity, so as to ensure that the liquid refrigerant in the second chamber 330 can naturally fall into the first chamber 320 through the spraying holes 310 under the action of gravity. For example, the second chamber 330 may be located above the first chamber 320 in the X direction.

Further, as shown in fig. 1 to 4, the partition 300 is provided at a position of the tub 100 adjacent to the tub top wall 120. Since the first chamber 320 is mainly used for heat exchange and the second chamber 330 is mainly used for uniformly spraying the liquid refrigerant to the first chamber 320, the volume of the first chamber 320 should be set to be larger, and the volume of the second chamber 330 may be set to be smaller. Correspondingly, the first chamber 320 may have a larger size and the second chamber 330 may have a smaller size along the X-direction, i.e. the partition 300 is disposed at a position of the tub 100 close to the tub top wall 120.

Similarly, the material of the partition 300 may be metal, such as cast iron, steel, aluminum, copper, or alloy, and the material of the outer cylinder 100 and the inner cylinder 200 may be ABS engineering plastic, nylon, or the like. When the material of the partition 300 is iron or steel, the partition 300 may be connected to the outer cylinder 100 and the inner cylinder 200 by welding.

As shown in fig. 1 to 4, the heat exchange tube 400 is spirally wound outside the inner tube 200, that is, the heat exchange tube 400 is spirally wound around the inner tube 200, and a certain gap is left between the heat exchange tube 400 and the inner tube 200, that is, the heat exchange tube 400 is not in contact with the inner tube 200. Specifically, the heat exchange tube 400 may be spirally wound around the inner tube 200 along the outer contour of the inner tube 200. For example, when the inner cylinder sidewall 210 of the inner cylinder 200 is cylindrical, the heat exchange tube 400 is spirally wound around the inner cylinder 200 along a circular track, that is, the extending track of the heat exchange tube 400 is a cylindrical spiral line, that is, the central line track of the heat exchange tube 400 is a cylindrical spiral line; when the inner sidewall 210 of the inner cylinder 200 is prism-shaped, the heat exchange tube 400 is spirally wound around the inner cylinder 200 along the cross-sectional shape of the inner sidewall 210 perpendicular to the X direction, at this time, the heat exchange tube 400 may be formed by sequentially connecting multiple sections of straight tubes, the arrangement direction of each section of straight tube is parallel to the extension direction of the corresponding inner sidewall 210, and the adjacent two sections of straight tubes may be transited by using a bent tube.

Further, when the inner cylinder sidewall 210 of the inner cylinder 200 is prism-shaped, the central line track of the heat exchange tube 400 may be a cylindrical spiral line, and the central line track of the heat exchange tube 400 may also be a conical spiral line. When the heat exchange tube 400 extends in a conical spiral line, the distances between the heat exchange tube 400 and the inner tube 200 at different positions in the X direction are different. This kind of arrangement, the projection of the heat exchange tube 400 of different positions along the X direction on baffle 300 is incomplete overlapping, also is that the heat exchange tube 400 that is located the top along the X direction can not shelter from the heat exchange tube 400 that is located the below, and after the liquid refrigerant got into first cavity 320 from second cavity 330, can be more for even spray to whole heat exchange tube 400, reduced effectively that the liquid refrigerant can spray to the heat exchange tube 400 that is located the top along the X direction, and can't spray to the heat exchange tube 400 that is located the below along the X direction the possibility.

In order to improve the heat exchange efficiency between the medium inside the heat exchange tube 400 and the liquid film of the liquid refrigerant formed on the outer surface of the heat exchange tube 400, the heat exchange tube 400 should be made of a material with a high thermal conductivity coefficient, such as copper, aluminum, etc.

It should be noted that, in order to improve the heat exchange efficiency, the flowing direction of the medium in the heat exchange tube 400 (tube side) should be opposite to the flowing direction of the refrigerant in the first chamber 320 and the second chamber 330 (shell side), and in this application, the refrigerant flows from top to bottom along the X direction, so that the medium in the heat exchange tube 400 flows from bottom to top, that is, along the X direction, the inlet of the heat exchange tube 400 is located below, and the outlet of the heat exchange tube 400 is located above.

As shown in fig. 1 to 4, both the liquid inlet pipe 500 and the gas outlet pipe 600 may be connected to the outer tub 100. The end of the liquid inlet pipe 500 connected to the tub 100 may extend into the second chamber 330, or may only communicate with the second chamber 330 and not extend into the second chamber 330, that is, the liquid inlet pipe 500 is disposed at a portion of the tub 100 corresponding to the second chamber 330 and extends in a direction away from the second chamber 330. Similarly, one end of the outlet pipe 600 connected to the outer tub 100 may extend into the first chamber 320, or may only communicate with the first chamber 320 and does not extend into the first chamber 320, that is, the outlet pipe 600 is disposed on a portion of the outer tub 100 corresponding to the first chamber 320 and extends in a direction away from the first chamber 320.

Further, the liquid inlet pipe 500 is connected to the tub 100, and may be connected to the tub top wall 120 of the tub 100 or may be connected to the tub side wall 110 of the tub 100.

The utility model provides a when pot-type heat exchanger 10 is as the evaporimeter, feed liquor pipe 500 provides liquid refrigerant in to second cavity 330, liquid refrigerant sprays to heat exchange tube 400 from the top of heat exchange tube 400 through the hole 310 that sprays that sets up in baffle 300, thereby adhere to the main pipe district of heat exchange tube 400 (the part by liquid refrigerant submergence not), and form the liquid film, the medium in the heat exchange tube 400 is cooled down to the phase transition heat absorption process when the liquid film is gaseous refrigerant through the evaporation, thereby the utilization ratio in the area in the main pipe of heat exchange tube 400 has been improved, the heat transfer area has been increased, and the heat exchange efficiency when pot-type heat exchanger 10 is as the evaporimeter has been improved. All liquid refrigerants enter the first cavity 320 in a spraying mode, so that the liquid refrigerants are fully contacted with the main pipe area of the heat exchange pipe 400, and the heat exchange effect is good.

For convenience of understanding, other embodiments of the present application will be described below by taking the X direction as the height direction of the can type heat exchanger 10 and taking the outer cylinder 100 and the inner cylinder 200 as cylindrical shapes as examples.

In some embodiments of the present application, one end of the outlet pipe 600 extends into the first chamber 320, and a projection of a portion of the outlet pipe 600 extending into the first chamber 320 on the partition 300 does not overlap the shower holes 310 in the X direction.

One end that outlet duct 600 stretched into first cavity 320 has the opening that is used for sucking gaseous refrigerant, near opening can form the negative pressure region, in order to can suck gaseous refrigerant, along the X direction, if offer spray hole 310 with the position that the opening corresponds on baffle 300, will have partial liquid refrigerant and follow spray hole 310 and get into behind the first cavity 320, directly spray near the opening that outlet duct 600 stretched into first cavity 320 to directly be sucked and get into in outlet duct 600, lead to liquid refrigerant not to contact with heat exchange tube 400 and carry out the heat transfer and discharge from outlet duct 600 promptly, the availability factor that has reduced liquid refrigerant has just reduced the heat exchange efficiency of can heat exchanger 10. Meanwhile, when a large amount of liquid refrigerant directly returns to the compressor 20 from the air outlet pipe 600, the liquid refrigerant may cause a liquid impact problem to the compressor 20, affect the normal working cycle of the compressor 20, and easily cause the compressor 20 to break down, and shorten the service life of the compressor 20. Therefore, the opening of the outlet pipe 600 extending into the first chamber 320 in the X direction is not provided with the shower holes 310 near the position of the projection of the partition plate 300, so as to prevent the outlet pipe 600 from directly sucking and discharging the liquid refrigerant that is not heat-exchanged.

It should be noted that in some embodiments of the present application, the outlet pipe 600 does not extend into the first chamber 320, but is disposed on the outer cylinder 100 and extends in a direction away from the first chamber 320, and the opening of the outlet pipe 600 for sucking the gaseous refrigerant is located on the side wall 110 of the outer cylinder 100. At this time, in order to prevent the outlet pipe 600 from sucking the liquid refrigerant, the shower holes 310 may not be provided at positions of the partition plate 300 corresponding to the outlet pipe 600 in the X direction.

This kind of mode of arrangement, because the projection of outlet duct 600 on baffle 300 does not overlap with spraying hole 310, spray hole 310 and can not directly spray liquid refrigerant on outlet duct 600 at the in-process that sprays, outlet duct 600 can not directly discharge the liquid refrigerant that does not carry out the heat transfer with heat exchange tube 400 to make liquid refrigerant can carry out abundant heat transfer with heat exchange tube 400, improve the heat exchange efficiency of pot-type heat exchanger 10.

As shown in fig. 1 to 4, in some embodiments of the present application, the can type heat exchanger 10 further includes a baffle 700, the baffle 700 being connected to an inner wall of the outer tub 100 and covering an end of the outlet pipe 600 for preventing the liquid refrigerant sprayed from the spray holes 310 from being discharged through the outlet pipe 600. The baffle 700 is disposed on the inner wall of the outer cylinder sidewall 110 and at the position where the outlet pipe 600 is disposed, so as to effectively prevent the liquid refrigerant from being discharged from the outlet pipe 600.

Specifically, as shown in fig. 1 to 4, an opening is formed below the baffle 700 along the X direction, so that the outlet pipe 600 is still communicated with the first chamber 320, the outlet pipe 600 can suck the gaseous refrigerant in the first chamber 320, and the baffle 700 is tightly connected with the outer cylinder sidewall 110 above the baffle 700, that is, there is no gap between the baffle 700 and the outer cylinder sidewall 110, so as to prevent the liquid refrigerant from being discharged from the outlet pipe 600.

Further, when the baffle 700 is provided in the can type heat exchanger 10, the spray holes 310 may be formed at any position on the partition plate 300 regardless of whether the outlet pipe 600 extends into the first chamber 320. Since the baffle 700 shields the outlet pipe 600, even if the spraying holes 310 are opened at a position corresponding to the outlet pipe 600, the liquid refrigerant entering the first chamber 320 through the spraying holes 310 can only be sprayed to the heat exchange pipe 400 and the baffle 700, and the liquid refrigerant sprayed to the baffle 700 is not directly sucked and discharged by the outlet pipe 600 after being shielded by the baffle 700. It can be understood that, when the baffle 700 is arranged, the baffle 700 can shield the air outlet pipe 600, the position of the partition board 300 provided with the spraying holes 310 is not required to be limited too much, the uniformity of spraying the liquid refrigerant to the heat exchange pipe 400 through the spraying holes 310 is ensured, the heat exchange pipe 400 corresponding to the position of the air outlet pipe 600 is also ensured to be sprayed by the liquid refrigerant with sufficient flow, and the dry pipe area of the heat exchange pipe 400 corresponding to the position of the air outlet pipe 600 can be reduced.

The baffle 700 is disposed on the inner wall of the outer tub 100, and the outlet pipe 600 is shielded by the baffle 700, thereby effectively preventing the liquid refrigerant that has not been heat-exchanged from being directly sucked and discharged by the outlet pipe 600. Meanwhile, when the baffle 700 is arranged, the position of the partition plate 300 provided with the spraying holes 310 is not required to be limited, the uniformity of spraying the liquid refrigerant to the heat exchange tube 400 is improved, the probability of occurrence of a dry tube area in the heat exchange tube 400 corresponding to the position of the air outlet tube 600 is reduced, and the heat exchange efficiency of the tank-type heat exchanger 10 is improved.

In some embodiments of the present application, both the first chamber 320 and the second chamber 330 do not communicate with the interior space of the inner barrel 200. That is, both ends of the inner cylinder sidewall 210 are closed along the X direction, and the inner cylinder 200 has a closed inner space.

The upper end of the inner cylinder sidewall 210 may also be connected with a partition 300 to close the upper end of the inner cylinder sidewall 210 by the partition 300, or the upper end of the inner cylinder sidewall 210 may be connected with the outer cylinder top wall 120 to close the upper end of the inner cylinder sidewall 210 by the outer cylinder top wall 120.

The first chamber 320 and the second chamber 330 are not communicated with the inner space of the inner cylinder 200, namely, the liquid refrigerant cannot enter the inner space of the inner cylinder 200 and only can enter the first chamber 320 and the second chamber 330, the liquid refrigerant can be gathered in the first chamber 320 and exchanges heat with the heat exchange tube 400, the space required for spraying the liquid refrigerant is reduced, the efficiency of spraying the liquid refrigerant is improved, and the heat exchange efficiency of the tank type heat exchanger 10 is further improved.

As shown in fig. 1 and 2, when the upper end of the inner cylinder 200 is closed by the partition 300, the inner cylinder sidewall 210 does not pass through the partition 300, and the second chamber 330 is between the upper end of the inner cylinder sidewall 210 and the outer cylinder top wall 120, and at this time, the projection of the first chamber 320 on the partition 300 is located inside the projection of the second chamber 330 on the partition 300 along the X direction. In this arrangement, the liquid inlet pipe 500 can be disposed in the middle of the top wall 120 of the outer tub, i.e., the central axis of the liquid inlet pipe 500 can coincide with the central axis of the outer tub 100 and the central axis of the partition 300. When the liquid refrigerant is provided through the liquid inlet pipe 500 located in the middle of the top wall 120 of the outer cylinder, the liquid refrigerant can be uniformly diffused from the middle of the second chamber 330 to the periphery of the second chamber 330, and it is further ensured that the liquid refrigerant can be uniformly sprayed to the heat exchange tube 400 from the second chamber 330.

It should be noted that, when the upper end of the inner cylinder sidewall 210 is sealed by the partition 300, the portion of the partition 300 corresponding to the inner space of the inner cylinder 200 should not be provided with the spraying holes 310, so that the inner space of the inner cylinder 200 is not communicated with the second chamber 330, and the liquid refrigerant cannot enter the inner space of the inner cylinder 200 from the second chamber 330.

According to the arrangement mode, the partition plate 300 separates the first chamber 320 and the second chamber 330, and seals the upper end of the inner barrel 200, so that the same partition plate realizes two functions, the number of parts is reduced, and the structure of the tank type heat exchanger 10 is simple and compact.

Further, as shown in fig. 1, in some embodiments of the present application, the tub 100 includes a tub bottom wall 130, and the lower end of the inner tub 200 is closed by the tub bottom wall 130. It is understood that the lower end of the inner cylinder side wall 210 may be connected to the outer cylinder bottom wall 130 in the X direction to close the lower end of the inner cylinder side wall 210 by the outer cylinder bottom wall 130.

This kind of mode of setting seals the lower extreme of inner tube 200 through urceolus diapire 130, need not to add extra spare part, has reduced the quantity of spare part for the simple structure of pot heat exchanger 10 is compact.

In other embodiments of the present application, as shown in fig. 2, the inner cartridge 200 comprises an inner cartridge bottom wall 220, the outer cartridge 100 comprises an outer cartridge bottom wall 130, and a gap is provided between the inner cartridge bottom wall 220 and the outer cartridge bottom wall 130. It will be appreciated that the lower end of the inner barrel side wall 210 can also be provided with an inner barrel bottom wall 220 to close off the lower end of the inner barrel side wall 210.

In this arrangement, the lower end of the inner cylinder 200 is provided with an independent component for sealing, thereby improving the sealing property between the inner cylinder 200 and the outer cylinder 100. Meanwhile, a certain gap is formed between the inner barrel bottom wall 220 and the outer barrel bottom wall 130, the volume of the first chamber 320 is increased, more heat exchange tubes 400 can be coiled in the first chamber 320, and the heat exchange efficiency of the tank type heat exchanger 10 is further increased.

Of course, in other embodiments of the present application, the inner cylinder bottom wall 220 and the outer cylinder bottom wall 130 can also be attached.

As shown in fig. 3, when the upper end of the inner cylinder 200 is closed by the top wall 120 of the outer cylinder, the partition 300 is sleeved on the inner cylinder 200, that is, the inner cylinder 200 passes through the partition 300, that is, the inner cylinder sidewall 210 passes through the partition 300, at this time, both the first chamber 320 and the second chamber 330 surround the inner cylinder 200, and along the X direction, the projection of the first chamber 320 on the partition 300 coincides with the projection of the second chamber 330 on the partition 300.

When the partition 300 is disposed on the inner tube 200, the second chamber 330 surrounds the inner tube 200, and a projection of the second chamber 330 on the partition 300 and a projection of the inner space of the inner tube 200 on the partition 300 do not have an overlapping region along the X direction. At this time, the liquid inlet pipe 500 cannot be disposed at the middle portion of the top wall 120 of the outer tub, but needs to be disposed at a portion of the top wall 120 of the outer tub corresponding to the second chamber 330, that is, the central axis of the liquid inlet pipe 500 does not coincide with the central axis of the partition 300, but the liquid inlet pipe 500 is disposed eccentrically with respect to the second chamber 330 and the partition 300.

According to the arrangement mode, the first cavity 320 and the second cavity 330 correspond to each other along the X direction, so that liquid refrigerants in the second cavity 330 can be conveniently sprayed to the heat exchange tubes 400 in the first cavity 320 through the spraying holes 310, and the heat exchange efficiency of the tank type heat exchanger 10 is ensured. It can be understood that the partition plate 300 is sleeved on the inner cylinder 200 to form the annular second chamber 330, and the cross-sectional area of the annular second chamber 330 is smaller, so that the liquid refrigerant can rapidly flow to the spraying holes 310 far away from the liquid inlet pipe 500, and all the spraying holes 310 are covered.

Further, as shown in fig. 3, in some embodiments of the present application, the tub 100 includes a tub top wall 120 and a tub bottom wall 130, an upper end of the inner tub 200 is closed by the tub top wall 120, and a lower end of the inner tub 200 is closed by the tub bottom wall 130. It can be understood that the inner cylinder side wall 210 passes through the partition 300, and the outer cylinder top wall 120 closes the upper end of the inner cylinder side wall 210, and the outer cylinder bottom wall 130 closes the lower end of the inner cylinder side wall 210.

According to the arrangement mode, the upper end and the lower end of the inner cylinder 200 are respectively sealed through the outer cylinder top wall 120 and the outer cylinder bottom wall 130, additional parts do not need to be added, the number of the parts is reduced, and the tank type heat exchanger 10 is compact in structure.

In other embodiments of the present application, as shown in FIG. 4, both the upper and lower ends of the inner cartridge 200 are open and in communication with the outside, i.e., the upper and lower ends of the inner cartridge sidewall 210 are not closed, it being understood that both ends of the inner cartridge 200 are in direct communication with the outside environment. At this time, two ends of the inner cylinder sidewall 210 are respectively connected with the outer cylinder top wall 120 and the outer cylinder bottom wall 130, the outer cylinder top wall 120 and the outer cylinder bottom wall 130 are both annular, the inner cylinder sidewall 210 passes through the partition plate 300, that is, the partition plate 300 is sleeved on the inner cylinder sidewall 210, and two ends of the inner cylinder 200 are both directly communicated with the external environment. At this time, the inner cylinder 200 penetrates the outer cylinder 100, the can type heat exchanger 10 is ring-shaped, and air in the external environment can pass through the inner cylinder 200, that is, air in the external environment can circulate through the inner cylinder 200.

This kind of mode of setting, the upper end and the lower extreme of inner tube 200 are direct and external environment intercommunication, and the air among the external environment can pass from inner tube 200, takes away partial heat, has further improved the heat exchange efficiency of can-type heat exchanger 10.

As shown in fig. 5 and 6, in some embodiments of the present application, a plurality of spray holes 310 are provided, the plurality of spray holes 310 are distributed along the circumferential direction of the partition 300 and are located above the heat exchange tube 400, and all the spray holes 310 are connected to and communicated with the first chamber 320 (shown in fig. 1) and the second chamber 330 (shown in fig. 1), that is, each spray hole 310 can spray the liquid refrigerant in the second chamber 330 to the heat exchange tube 400 (shown in fig. 1).

Specifically, as shown in fig. 5, in some embodiments of the present application, the plurality of spray holes 310 may be spaced around the central axis of the baffle plate 300, i.e., spaced along the circumferential direction of the baffle plate 300, i.e., the plurality of spray holes 310 are distributed in an annular array with the center of the baffle plate 300 as the center. The plurality of spray holes 310 may be distributed at equal intervals, or the plurality of spray holes 310 may be distributed at unequal intervals. In other embodiments of the present application, the plurality of spray holes 310 may also be distributed in the separator plate 300 in a rectangular array, or alternatively, may be distributed at intervals along a spline curve in the separator plate 300.

Further, the plurality of spray holes 310 are distributed at intervals around the central axis of the partition 300, the plurality of spray holes 310 may all be located on the same circumference with the center of the partition 300 as the center, or the plurality of spray holes 310 may be located on a plurality of circumferences with the center of the partition 300 as the center, and some of the plurality of spray holes 310 may be located on the same circumference, for example, as shown in fig. 5 and 6, that is, the plurality of spray holes 310 are located on a plurality of circumferences with the center of the partition 300 as the center.

The arrangement of the plurality of spraying holes 310 can ensure that the liquid refrigerant is uniformly sprayed to the heat exchange tube 400.

Further, as shown in fig. 5, in some embodiments of the present application, an area of the spray holes 310 far from the liquid inlet pipe 500 is larger than an area of the spray holes 310 near the liquid inlet pipe 500 among the plurality of spray holes 310.

The area of the spray holes 310 refers to the area of the flow cross section of the spray holes 310, and the flow cross section can be understood as a cross section perpendicular to the flow velocity direction of the fluid. Under the condition of the same flow velocity, the larger the area of the overflowing section is, the larger the flow of the fluid passing through the overflowing section in unit time is correspondingly.

After the liquid refrigerant enters the second chamber 330 through the liquid inlet pipe 500, the liquid refrigerant is more in the area of the second chamber 330 close to the liquid inlet pipe 500, and less in the area far from the liquid inlet pipe 500. At this time, if the areas of the plurality of spraying holes 310 are consistent, the spraying holes 310 close to the liquid inlet pipe 500 can spray more liquid refrigerants to the heat exchange pipe 400, and the spraying holes 310 far away from the liquid inlet pipe 500 cannot spray enough liquid refrigerants to the heat exchange pipe 400, even the liquid refrigerants cannot be sprayed to a part of the heat exchange pipe 400 far away from the liquid inlet pipe 500, the part of the heat exchange pipe 400 is still a dry pipe area and cannot form a liquid film on the surface of the heat exchange pipe 400, and the heat exchange efficiency of the tank heat exchanger 10 as an evaporator is still low. Therefore, the area of the spraying holes 310 far away from the liquid inlet pipe 500 is set to be larger than the area of the spraying holes 310 close to the liquid inlet pipe 500, so as to ensure that the flow of the liquid refrigerant sprayed into the first chamber 320 from the spraying holes 310 at different positions of the partition plate 300 is relatively average, the liquid refrigerant can be sprayed to all the heat exchange tubes 400, all the heat exchange tubes 400 can effectively form a liquid film on the surface, so that the medium in the heat exchange tubes 400 is effectively cooled through the phase change heat absorption process when the liquid refrigerant is converted into the gaseous refrigerant, and the heat exchange efficiency of the tank heat exchanger 10 as an evaporator is improved.

Similarly, as shown in fig. 6, in other embodiments of the present application, the spray holes 310 far from the liquid inlet pipe 500 are more densely packed than the spray holes 310 near the liquid inlet pipe 500 among the plurality of spray holes 310.

The density of the spray holes 310 is the number of the spray holes 310 formed in a unit area of the separator 300. As shown in fig. 6, taking the areas of the plurality of spray holes 310 as an example, the density of the spray holes 310 far from the liquid inlet pipe 500 is greater than the density of the spray holes 310 near the liquid inlet pipe 500, that is, the number of the spray holes 310 per unit area is greater at the position far from the liquid inlet pipe 500 on the partition plate 300 than at the position near the liquid inlet pipe 500 on the partition plate 300. In this arrangement, it can be understood that the number of the spraying holes 310 formed in the unit area of the partition 300 is changed, so that the area of the flow cross section of the partition 300 is changed, and finally, the flow rate of the liquid refrigerant sprayed to the heat exchange tube 400 through the spraying holes 310 at different positions of the partition 300 is uniform.

After the liquid refrigerant enters the second chamber 330 through the liquid inlet pipe 500, the liquid refrigerant is more in the area of the second chamber 330 close to the liquid inlet pipe 500, and less in the area far from the liquid inlet pipe 500. At this time, if the density of the spraying holes 310 at different positions on the partition 300 is consistent, the spraying holes 310 close to the liquid inlet pipe 500 can spray more liquid refrigerants to the heat exchange pipe 400, and the spraying holes 310 far away from the liquid inlet pipe 500 cannot spray enough liquid refrigerants to the heat exchange pipe 400, even the liquid refrigerants cannot be sprayed to a part of the heat exchange pipe 400 far away from the liquid inlet pipe 500, the part of the heat exchange pipe 400 still serves as a dry pipe region and cannot form a liquid film on the surface of the heat exchange pipe 400, and the heat exchange efficiency of the tank heat exchanger 10 as an evaporator is still low. Therefore, the density of the spraying holes 310 far away from the liquid inlet pipe 500 is set to be greater than the density of the spraying holes 310 close to the liquid inlet pipe 500, so as to ensure that the flow of the liquid refrigerant sprayed into the first chamber 320 from the spraying holes 310 at different positions of the partition plate 300 is relatively average, the liquid refrigerant can be sprayed to all the heat exchange tubes 400, all the heat exchange tubes 400 can effectively form a liquid film on the surface, so that the medium in the heat exchange tubes 400 is effectively cooled through the phase change heat absorption process when the liquid refrigerant is converted into the gaseous refrigerant, and the heat exchange efficiency of the tank heat exchanger 10 as an evaporator is improved.

It should be noted that, the opening manner of the spraying holes 310 on the partition board 300 only needs to be satisfied, at the position of the partition board 300 far away from the liquid inlet pipe 500, the area of the overflowing section of the spraying holes 310 in the unit area is larger than that of the spraying holes 310 in the unit area, and at the position of the partition board 300 near the liquid inlet pipe 500, the area of the overflowing section of the spraying holes 310 in the unit area is only needed, that is, the opening manner of the spraying holes 310 on the partition board 300 only needs to be satisfied that the liquid refrigerant entering the first chamber 320 from the second chamber 330 is relatively uniform, and the heat dissipation pipes located at different positions are all sprayed by the liquid refrigerant. For example, according to the actual requirement, while the area of the spray holes 310 far from the liquid inlet pipe 500 is increased, the density of the spray holes 310 far from the liquid inlet pipe 500 may be increased within a certain range.

According to the position of the spraying holes 310 from the liquid inlet pipe 500, the area of the spraying holes 310 and the density of the spraying holes 310 are adjusted adaptively, so that the effect that the flow of the liquid refrigerant sprayed to the heat exchange pipe 400 through the spraying holes 310 at any positions of the partition plate 300 is uniform is achieved, the liquid refrigerant can be uniformly sprayed to all the heat exchange pipes 400, and the heat exchange efficiency of the tank type heat exchanger 10 is further guaranteed.

In addition, the area of the spraying holes 310 and the density of the spraying holes 310 may also be determined according to the actual spraying situation and the demand of the heat pipe 400 for the liquid refrigerant flow at different positions. For example, in some embodiments of the present application, the middle portion of the heat exchange tube 400 has a large demand for liquid refrigerant along the radial direction of the inner tube 200 or the outer tube 100, and both sides of the heat exchange tube 400, i.e., the side of the heat exchange tube 400 close to the inner tube 200 and the side of the heat exchange tube 400 close to the outer tube 100, have a small demand for liquid refrigerant, which can also be understood as that, along the X direction, the projection of the heat exchange tube 400 on the partition 300 covers a large demand for liquid refrigerant, and the projection of the heat exchange tube 400 on the partition 300 does not cover a small demand for liquid refrigerant. At this time, the arrangement manner and the arrangement position of the spraying holes 310 on the partition 300, that is, the area and the density of the spraying holes 310, should be determined according to the liquid refrigerant demand of the heat exchange tube 400. For example, in the X direction, in the area covered by the projection of the heat exchange tube 400 of the partition 300, that is, in the area where the projection of the heat exchange tube 400 overlaps with the spray holes 310, the area of the spray holes 310 and the density of the spray holes 310 may be appropriately increased, and in other positions of the partition 300, the area of the spray holes 310 and the density of the spray holes 310 may be appropriately decreased, accordingly, in the corresponding positions of the heat exchange tube 400, the area of the flow cross section of the spray holes 310 per unit area is large, the flow rate of the sprayed liquid refrigerant is also large, and in other positions of the partition 300, the area of the flow cross section of the spray holes 310 per unit area is small, and the flow rate of the sprayed liquid refrigerant is also small.

The shape of the spray holes 310 may be circular, elliptical, polygonal, or may be any shape formed by enclosing a closed spline curve, the shape of the spray holes 310 is not limited in this application, and it is only required to ensure that the spray holes 310 can spray the liquid refrigerant in the second chamber 330 to the heat exchange tube 400 more smoothly.

Further, as shown in fig. 7, the spray holes 310 may also be elongated, and in this case, a plurality of spray holes 310 may be spaced along the circumferential direction of the partition 300. The long spray holes 310 mean that the spray holes 310 have a large size in the radial direction of the inner cylinder 200 or the outer cylinder 100, and the spray holes 310 have a small size in the circumferential direction of the partition 300. When the spray holes 310 are elongated, the size of the spray holes 310 in the circumferential direction of the partition 300 may vary in the radial direction, for example, as shown in fig. 7, the size of the spray holes 310 in the circumferential direction may increase first and then decrease in the radial direction; also for example, in the radial direction, the size of the shower holes 310 in the circumferential direction may also be increased all the time. At this time, the spray holes 310 may be oval, fusiform, spindle-shaped, drop-shaped, etc.

As shown in fig. 8, in some embodiments of the present application, the spray holes 310 may penetrate the partition 300 in the X direction, i.e., central axes of the spray holes 310 are disposed in the X direction, and central axes of the plurality of spray holes 310 are parallel to each other. In this arrangement, when the liquid refrigerant enters the first chamber 320 from the second chamber 330 through the spraying holes 310, the liquid refrigerant is sprayed to the heat exchange tube 400 along the X direction. In other embodiments of the present application, as shown in fig. 8, the spray holes 310 may also extend through the baffle 300 at an angle to the X-direction, i.e., the central axis of the spray holes 310 is at an angle to the X-direction.

Further, as shown in fig. 8, when the plurality of spray holes 310 are located at a plurality of circumferences centering on the center of the barrier 300, angles of angles between central axes of the spray holes 310 located at different circumferences and the X direction may be different. For example, in the X direction, when the projection of the spray hole 310 and the projection of the heat exchange tube 400 on the partition 300 overlap, the central axis of the spray pipe may be arranged in the X direction, and at this time, when the liquid refrigerant in the second chamber 330 enters the first chamber 320 through the spray hole 310, the liquid refrigerant can be accurately sprayed to the heat exchange tube 400. Similarly, along the X direction, when the spray holes 310 and the projection of the heat exchange tube 400 on the partition 300 are not overlapped, that is, the spray holes 310 are located between the projection of the heat exchange tube 400 on the partition 300 and the outer cylinder 100, or the spray holes 310 are located between the projection of the heat exchange tube 400 on the partition 300 and the inner cylinder 200, the central axis of the spray holes 310 may be set toward the heat exchange tube 400, at this time, the spray holes 310 penetrate through the partition 300 in the direction toward the heat exchange tube 400, and when the liquid refrigerant in the second chamber 330 enters the first chamber 320 through the spray holes 310, the liquid refrigerant can be sprayed to the heat exchange tube 400 more accurately. This kind of setting mode has reduced the probability that liquid refrigerant can't spray to heat exchange tube 400, has reduced heat exchange tube 400 and has had the possibility in dry tube district, has further improved heat exchange tube 400's heat exchange efficiency, has also improved the heat exchange efficiency of can-type heat exchanger 10.

As shown in fig. 9, in some embodiments of the present application, one end of the outlet pipe 600 communicates with the first chamber 320, and the other end of the outlet pipe 600 communicates with the inner space of the inner tube 200, that is, the outlet pipe 600 can suck and discharge the gaseous refrigerant in the first chamber 320 to the inner space of the inner tube 200. At this time, the can-type heat exchanger 10 may further include a gas return pipe 800, the gas return pipe 800 is disposed in the inner tube 200, the gas return pipe 800 and the inner tube 200 form a gas-liquid separator 60, and separation of a gaseous refrigerant and a liquid refrigerant is achieved in an inner space of the inner tube 200.

Specifically, as shown in FIG. 9, the inner space of the inner barrel 200 can be divided into a lower liquid phase space 840 and an upper vapor phase space 830. The liquid phase space 840 may be understood as a space filled with a liquid refrigerant in the inner tube 200, and correspondingly, the gas phase space 830 may be understood as a space filled with a gas refrigerant in the inner tube 200. The other end of the outlet pipe 600 is communicated with the inner space of the inner cylinder 200, that is, the other end of the outlet pipe 600 is communicated with the gas phase space 830 of the inner cylinder 200, and can suck and discharge the gaseous refrigerant in the first chamber 320 to the gas phase space 830 of the inner cylinder 200. One end of the muffler 800 is disposed in the gas phase space 830 of the inner tube 200, and the other end of the muffler 800 is connected to the compressor 20, provides a negative pressure through the compressor 20, and pumps the gaseous refrigerant to the compressor 20.

When the gaseous refrigerant flows in the outlet pipe 600, a small amount of gaseous refrigerant is converted into liquid refrigerant, namely, a small amount of liquid refrigerant exists in the gaseous refrigerant entering the inner cylinder 200 from the outlet pipe 600, the liquid refrigerant enters the liquid phase space 840 at the lower part of the inner cylinder 200 under the action of gravity, and the gaseous refrigerant discharged from the outlet pipe 600 directly enters the gaseous space of the inner cylinder 200, so that the separation of the gaseous refrigerant and the liquid refrigerant is realized.

This kind of setting mode utilizes the inner space of inner tube 200 to set up vapour and liquid separator 60, realizes the separation of gaseous state refrigerant and liquid refrigerant, rational utilization the structure and the space of pot heat exchanger 10 for the compact structure of pot heat exchanger 10. Meanwhile, when the tank heat exchanger 10 is used as an evaporator in the heat pump system 1000, the gas-liquid separator 60 does not need to be additionally arranged, so that the number of components of the heat pump system 1000 is reduced, and the structure of the heat pump system 1000 is simplified.

In some embodiments of the present application, the lower end of the inner tube 200 is provided with a first oil return hole 810, the air return pipe 800 is provided with a second oil return hole 820, and the first oil return hole 810 and the second oil return hole 820 are used for introducing the lubricating oil in the liquid refrigerant in the first chamber 320 into the air return pipe 800 and pumping the lubricating oil and the gaseous refrigerant to the compressor 20 through the air return pipe 800.

Specifically, as shown in fig. 9, a first oil return hole 810 is formed at a lower end of the inner cylinder 200, and the first oil return hole 810 is used for communicating the liquid phase space 840 of the inner cylinder 200 with the first chamber 320. Since not all the liquid refrigerant sprayed to the first chamber 320 can adhere to the surface of the heat exchange tube 400 to form a liquid film, the liquid refrigerant with a certain height is accumulated below the first chamber 320, the first oil return hole 810 is disposed at the lower end of the inner cylinder sidewall 210 of the inner cylinder 200, and the distance from the first oil return hole 810 to the outer cylinder bottom wall 130 along the X direction is determined according to the height of the liquid refrigerant and the lubricating oil accumulated in the first chamber 320, that is, according to the liquid level height of the liquid accumulated in the first chamber 320. Accordingly, the muffler 800 located in the inner space of the inner cylinder 200 is in a J shape, a portion of the muffler 800 is located in the gas phase space 830, another portion of the muffler 800 is located in the liquid phase space 840, the end of the muffler 800 extending into the inner cylinder 200 has an opening located in the gas phase space 830 to enable the gaseous refrigerant to be pumped from the gas phase space 830 to the compressor 20, and since the muffler 800 pumps the gaseous refrigerant to the compressor 20, the pressure in the inner space of the inner cylinder 200 is lower than that in the first chamber 320, and there is a pressure difference between the inner space of the inner cylinder 200 and the first chamber 320, the lubricating oil and the liquid refrigerant in the first chamber 320 will be sucked into the inner cylinder 200 through the first oil return hole 810. Meanwhile, the second oil return hole 820 is disposed on the air return pipe 800 located in the liquid phase space 840 corresponding to the first oil return hole 810, so that the lubricating oil can be introduced into the air return pipe 800 from the liquid refrigerant located in the liquid phase space 840 and pumped to the compressor 20.

It should be noted that the specific positions and heights of the first oil return hole 810 and the second oil return hole 820 need to be determined according to the density relationship between the liquid refrigerant and the lubricating oil, and the enrichment degree of the lubricating oil in the liquid refrigerant. For example, in some embodiments of the present disclosure, the density of the lubricating oil is lower than that of the liquid-phase refrigerant, and the lubricating oil is mainly concentrated at the position 3/4 of the liquid level of the liquid-phase refrigerant, and at this time, both the first oil return hole 810 and the second oil return hole 820 may be disposed at the positions 2/3 to 4/5 of the liquid-phase refrigerant, so as to be able to pump more lubricating oil from the liquid stored in the first chamber 320 and the liquid-phase space 840. Correspondingly, in other embodiments of the present disclosure, when the density of the lubricating oil is greater than the density of the liquid-state refrigerant, the first oil return hole 810 and the second oil return hole 820 may be disposed according to a position where the lubricating oil in the liquid stored in the first chamber 320 and the liquid-phase space 840 is mainly concentrated in the liquid-state refrigerant. It can be understood that, regardless of the density relationship between the liquid-phase refrigerant and the lubricating oil, the first oil return hole 810 and the second oil return hole 820 may be provided according to a position where the lubricating oil is mainly concentrated in the liquid-phase refrigerant in the liquid stored in the first chamber 320 and the liquid-phase space 840.

According to the arrangement mode, when the gas-liquid separator 60 is formed by the gas return pipe 800 and the inner cylinder 200, the gas return pipe 800 can not only suck the gaseous refrigerant to the compressor 20, but also can simultaneously suck the lubricating oil in the liquid refrigerant and the gaseous refrigerant to the compressor 20, and further reasonably utilizes the structural arrangement form and space of the tank type heat exchanger 10. Meanwhile, when the tank heat exchanger 10 is used as an evaporator in the heat pump system 1000, the return pipe 800 simultaneously pumps the gaseous refrigerant and the lubricant oil to the compressor 20, thereby further improving the structural compactness of the heat pump system 1000.

On the other hand, as shown in fig. 10, the present application provides a heat pump system 1000, the heat pump system 1000 including a compressor 20, a condenser 30, an expansion valve 40, and the above-described can heat exchanger 10 (the gas-liquid separator 60 is not provided in the inner tube 200 of the can heat exchanger 10). In which the tank heat exchanger 10 serves as an evaporator of the heat pump system 1000.

Specifically, as shown in fig. 10, an outlet of the compressor 20 is communicated with an inlet of the condenser 30, an outlet of the condenser 30 is communicated with an inlet pipe 500 of the tank heat exchanger 10 through the expansion valve 40, and an outlet pipe 600 of the tank heat exchanger 10 is communicated with an inlet of the compressor 20.

Wherein, when the gas-liquid separator 60 is not disposed in the inner cylinder 200 of the tank heat exchanger 10, the heat exchange process of the tank heat exchanger 10 as an evaporator is as follows:

1. the liquid refrigerant enters the second chamber 330 through the liquid inlet pipe 500;

2. the liquid refrigerant in the second chamber 330 is sprayed to the heat exchange tube 400 through the spraying holes 310;

3. the liquid refrigerant is attached to the heat exchange tube 400 and forms a liquid film, and the liquid refrigerant exchanges heat with the medium in the heat exchange tube 400 and is evaporated into a gaseous refrigerant;

4. the gaseous refrigerant in the first chamber 320 is sucked and discharged through the outlet pipe 600.

Further, as shown in fig. 10, the heat pump system 1000 further includes a gas-liquid separator 60, in which case, the outlet pipe 600 of the tank heat exchanger 10 is connected to the inlet of the compressor 20 through the gas-liquid separator 60. The gas-liquid separator 60 is used for separating the gas refrigerant and the liquid refrigerant pumped in the air outlet pipe 600, so as to prevent a large amount of liquid refrigerant from being sucked into the compressor 20, and the liquid impact problem is generated on the compressor 20, thereby reducing the influence of the liquid impact problem on the service condition of the compressor 20 and the influence on the service life of the compressor 20.

In yet another aspect, as shown in fig. 11, the present application provides a heat pump system 1000, the heat pump system 1000 including a compressor 20, a condenser 30, an expansion valve 40, and the above-described can heat exchanger 10 (a gas-liquid separator 60 is disposed in an inner tube 200 of the can heat exchanger 10). In which the tank heat exchanger 10 serves as an evaporator of the heat pump system 1000.

Specifically, as shown in fig. 11, an outlet of the compressor 20 communicates with an inlet of the condenser 30, an outlet of the condenser 30 communicates with the liquid inlet pipe 500 of the tank heat exchanger 10 through the expansion valve 40, and a gas return pipe 800 of the tank heat exchanger 10 communicates with an inlet of the compressor 20.

Wherein, when the gas-liquid separator 60 is arranged in the inner cylinder 200 of the tank heat exchanger 10, the heat exchange process of the tank heat exchanger 10 as an evaporator is as follows:

3. the liquid refrigerant is attached to the heat exchange tube 400 and forms a liquid film, the liquid refrigerant exchanges heat with a medium in the heat exchange tube 400 and is evaporated into a gaseous refrigerant, and part of the liquid refrigerant and the lubricating oil are accumulated at the lower end of the first chamber 320;

4. the gaseous refrigerant in the first chamber 320 is sucked through the outlet pipe 600 and discharged to the inner cylinder 200, and the lubricating oil and the liquid refrigerant accumulated in the first chamber 320 are sucked to the inner cylinder 200 through the first oil return hole 810;

5. the liquid refrigerant and the lubricating oil are gathered in the liquid phase space 840 of the inner cylinder 200, the lubricating oil is introduced into the muffler 800 through the second oil return hole 820, and the gaseous refrigerant and the lubricating oil are sucked and discharged through the muffler 800.

This kind of setting mode utilizes the inner space of inner tube 200 to set up vapour and liquid separator 60, realizes the separation of gaseous state refrigerant and liquid refrigerant, has rationally utilized the structure and the space of pot-type heat exchanger 10. When the tank heat exchanger 10 is used as an evaporator in the heat pump system 1000, the gas-liquid separator 60 does not need to be additionally arranged, and the structural compactness of the heat pump system 1000 is improved.

Meanwhile, the inner cylinder 200 of the can-type heat exchanger 10 is provided with the first oil return hole 810 and the air return pipe 800 is provided with the second oil return hole 820, the air return pipe 800 and the inner cylinder 200 form the gas-liquid separator 60, and meanwhile, the air return pipe 800 can not only suck the gaseous refrigerant to the compressor 20, but also can simultaneously suck the lubricating oil in the liquid refrigerant and the gaseous refrigerant to the compressor 20, so that the structural arrangement form and the space of the can-type heat exchanger 10 are further reasonably utilized. When the tank heat exchanger 10 is used as an evaporator in the heat pump system 1000, the return pipe 800 simultaneously pumps the gaseous refrigerant and the lubricant oil to the compressor 20, thereby further improving the structural compactness of the heat pump system 1000.

It should be noted that, in the heat pump system 1000 of this application, the tank heat exchanger 10 is used as an evaporator, a low-temperature low-pressure gaseous refrigerant is compressed by the compressor 20, and is converted into a high-temperature high-pressure gaseous refrigerant, which flows to the condenser 30 from an outlet of the compressor 20, and is phase-changed to release heat in the condenser 30, and is converted into a medium-temperature high-pressure liquid refrigerant, and then the medium-temperature high-pressure liquid refrigerant enters the expansion valve 40, and is converted into low-temperature low-pressure wet steam, and the low-temperature low-pressure wet steam enters the tank heat exchanger 10, and is phase-changed to absorb heat in the tank heat exchanger 10, and is converted into a low-temperature low-pressure gaseous refrigerant, and cools a medium to be heat exchanged, and the medium to be heat exchanged flows to the user terminal 50 after being cooled, and the low-temperature low-pressure gaseous refrigerant returns to the compressor 20 again, and completes circulation.

In some embodiments of this application, treat that the medium of heat transfer is water, and user end 50 can be for holding with water, through the water pump with water pump income pot heat exchanger 10, water supplies the user to use after the cooling, perhaps, user end still can be air conditioner, water gets into air conditioner after the cooling, with indoor air heat transfer in order to provide air conditioning.

It should be noted that the features of the embodiments in the present application may be combined with each other without conflict.

The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A tank heat exchanger (10), comprising:

an outer tub (100);

an inner cylinder (200), wherein the inner cylinder (200) is arranged inside the outer cylinder (100);

a partition plate (300), the partition plate (300) being disposed inside the outer tub (100) to divide a space between the outer tub (100) and the inner tub (200) into a first chamber (320) and a second chamber (330), the second chamber (330) being located above the first chamber (320);

a heat exchange tube (400), the heat exchange tube (400) being disposed in the first chamber (320) and spirally wound outside the inner tube (200);

the liquid inlet pipe (500) is used for providing liquid refrigerant to the second chamber (330);

an outlet pipe (600), the outlet pipe (600) being used for sucking the gaseous refrigerant from the first chamber (320);

the partition plate (300) is provided with spraying holes (310), and the spraying holes (310) are used for spraying the liquid refrigerant of the second chamber (330) to the heat exchange tube (400).

2. The can type heat exchanger (10) according to claim 1, wherein the spray holes (310) are provided in plurality, and the plurality of spray holes (310) are distributed along a circumference of the partition (300) and located above the heat exchange pipe (400).

3. The tank heat exchanger (10) according to claim 2, wherein an area of the spray holes (310) far from the liquid inlet pipe (500) among the plurality of spray holes (310) is larger than an area of the spray holes (310) near the liquid inlet pipe (500).

4. The tank heat exchanger (10) according to claim 2, wherein the spray holes (310) far from the liquid inlet pipe (500) among the plurality of spray holes (310) are more densely packed than the spray holes (310) near the liquid inlet pipe (500).

5. The tank heat exchanger (10) according to claim 1, wherein one end of the outlet pipe (600) protrudes into the first chamber (320), and a projection of the outlet pipe (600) on the baffle plate (300) does not overlap with the shower holes (310).

6. The can type heat exchanger (10) according to claim 1, wherein the can type heat exchanger (10) further comprises a baffle (700), the baffle (700) is connected to an inner wall of the outer tub (100) and covers one end of the outlet pipe (600) to prevent the liquid refrigerant sprayed from the spray holes (310) from being discharged through the outlet pipe (600).

7. The tank heat exchanger (10) of claim 1 wherein the first chamber (320) and the second chamber (330) are each not in communication with the interior space of the inner barrel (200).

8. The can heat exchanger (10) according to claim 1, wherein the upper end of the inner drum (200) is closed by the partition (300).

9. The tank heat exchanger (10) according to claim 8, wherein the outer drum (100) comprises an outer drum bottom wall (130), the lower end of the inner drum (200) being closed by the outer drum bottom wall (130).

10. The can heat exchanger (10) of claim 8 wherein the inner drum (200) includes an inner drum bottom wall (220) and the outer drum (100) includes an outer drum bottom wall (130), the inner drum bottom wall (220) and the outer drum bottom wall (130) having a gap therebetween.

11. The tank heat exchanger (10) of claim 1 wherein the baffle (300) is sleeved to the inner barrel (200).

12. The can heat exchanger (10) of claim 11 wherein the outer drum (100) includes an outer drum top wall (120) and an outer drum bottom wall (130), the upper end of the inner drum (200) being closed by the outer drum top wall (120) and the lower end of the inner drum (200) being closed by the outer drum bottom wall (130).

13. The tank heat exchanger (10) of claim 11 wherein the inner cylinder (200) is open at both its upper and lower ends and communicates with the ambient.

14. The can type heat exchanger (10) according to claim 1, wherein one end of the outlet pipe (600) communicates with the first chamber (320), the other end of the outlet pipe (600) communicates with the inner space of the inner tube (200), the can type heat exchanger (10) further comprising a gas return pipe (800), the gas return pipe (800) being disposed inside the inner tube (200), the gas return pipe (800) forming a gas-liquid separator (60) with the inner tube (200).

15. The can type heat exchanger (10) according to claim 14, wherein a first oil return hole (810) is formed at a lower end of the inner tube (200), and a second oil return hole (820) is formed at the air return pipe (800), and the first oil return hole (810) and the second oil return hole (820) are used for introducing lubricating oil in the liquid refrigerant in the first chamber (320) into the air return pipe (800).

16. A heat pump system (1000), comprising:

a compressor (20);

a condenser (30);

an expansion valve (40);

the tank heat exchanger (10) as claimed in any of claims 1 to 13;

wherein the outlet of the compressor (20) is communicated with the inlet of the condenser (30), the outlet of the condenser (30) is communicated with the liquid inlet pipe (500) of the tank type heat exchanger (10) through the expansion valve (40), and the gas outlet pipe (600) of the tank type heat exchanger (10) is communicated with the inlet of the compressor (20).

17. The heat pump system (1000) of claim 16, wherein the heat pump system (1000) further comprises a gas-liquid separator (60), and the gas outlet pipe (600) of the tank heat exchanger (10) is in communication with the inlet of the compressor (20) through the gas-liquid separator (60).

18. A heat pump system (1000), comprising:

a compressor (20);

a condenser (30);

an expansion valve (40);

the tank heat exchanger (10) as claimed in any of claims 14 to 15;

wherein the outlet of the compressor (20) is communicated with the inlet of the condenser (30), the outlet of the condenser (30) is communicated with the liquid inlet pipe (500) of the tank type heat exchanger (10) through the expansion valve (40), and the air return pipe (800) of the tank type heat exchanger (10) is communicated with the inlet of the compressor (20).