Gas-liquid separator and heat pump system

Abstract

The utility model provides a gas-liquid separator and a heat pump system. The gas-liquid separator comprises a pipe body, a refrigerant inlet pipe, a gaseous refrigerant outlet pipe, a plurality of liquid refrigerant outlet holes and rotational flow fan blades. The tube body extends in the vertical direction. The refrigerant inlet pipe penetrates through the bottom face of the pipe body from bottom to top and extends upwards by a certain distance. And the gaseous refrigerant outlet pipe is inserted into the upper end of the pipe body. The multiple liquid refrigerant outlet holes are located in the bottom face of the pipe body and located in the periphery of the refrigerant inlet pipe. The rotational flow fan blades are spiral and are fixedly connected to the interior of the pipe body. The rotational flow fan blades are located on the lower side of the gaseous refrigerant outlet pipe. According to the gas-liquid separator, the gas-liquid separation effect is better, the efficiency is higher, the problem that liquid separation of two-phase refrigerants is difficult is solved, and the liquid separation efficiency of the two-phase refrigerants is improved. And on the other hand, the problems that the overall heat exchange efficiency of two-phase refrigerants is low, and the refrigerants are prone to excessive overheating are solved, and the heat exchange efficiency of the refrigerants is improved. And on the other hand, the problem that refrigerant flowing sound is easily caused when the two-phase refrigerant flows is solved, and the purpose of reducing noise is achieved.

Description

Technical Field

[0001] The utility model relates to the technical field of heat pumps, in particular to a gas-liquid separator and a heat pump system. Background Art

[0002] At present, in heat pump systems, the refrigerant is often in a two-phase state before it flows out of the electronic expansion valve or capillary tube and enters the heat exchanger. This two-phase refrigerant can cause the following defects in the operation of the heat pump system:

[0003] 1. Two-phase refrigerant in the heat pump system is difficult to separate due to gravity and the different back pressures at each branch of the heat exchanger.

[0004] 2. At least a part of the heat absorbed by the two-phase refrigerant in the heat exchanger is absorbed by the gaseous refrigerant. In terms of heat transfer efficiency, the gaseous refrigerant is significantly lower than the liquid refrigerant, resulting in the overall heat exchange efficiency of the two-phase refrigerant being lower than the heat exchange efficiency of the pure liquid refrigerant, and the refrigerant flowing out of the heat exchanger is prone to excessive overheating.

[0005] 3. The two-phase refrigerant flows in the heat exchanger and the inlet branch, which easily causes refrigerant flow noise. Utility Model Content

[0006] In view of the above problems, the utility model is proposed to provide a gas-liquid separator and heat pump system that overcomes the above problems or at least partially solves the above problems. On the one hand, it can solve the problem of difficulty in separating two-phase refrigerant, and achieve the purpose of improving the efficiency of two-phase refrigerant separation. On the other hand, it can solve the problem of low overall heat exchange efficiency of two-phase refrigerant and the problem of excessive overheating of refrigerant, and achieve the purpose of improving the heat exchange efficiency of refrigerant. On the other hand, it can solve the problem of refrigerant flow sound easily caused by the flow of two-phase refrigerant, and achieve the purpose of reducing the generation of refrigerant flow sound.

[0007] Specifically, the utility model provides a gas-liquid separator, comprising:

[0008] The tube body extends in the up-down direction.

[0009] The refrigerant inlet pipe penetrates the bottom surface of the tube body from bottom to top and extends upward for a distance.

[0010] A gaseous refrigerant outlet pipe is inserted at the upper end of the pipe body.

[0011] A plurality of liquid refrigerant outlet holes are provided, and the plurality of liquid refrigerant outlet holes are located on the bottom surface of the tube body and are located at the periphery of the refrigerant inlet tube.

[0012] The swirl blades are spiral-shaped and are directly or indirectly fixedly connected to the inside of the tube body. The swirl blades are located at the lower side of the gaseous refrigerant outlet pipe.

[0013] Optionally, the swirl blade is a second swirl blade, and the upper end of the second swirl blade is fixedly connected to the lower end of the gaseous refrigerant outlet pipe.

[0014] Optionally, the outer diameter of the second swirl blade increases gradually from top to bottom, and the maximum outer diameter of the second swirl blade is smaller than the inner diameter of the tube body.

[0015] Optionally, the bottom of the second swirl blade is located at the lower side of the upper end opening of the refrigerant inlet pipe.

[0016] Optionally, the swirl blade is a first swirl blade. The first swirl blade is spirally wound around the outer circumference of the refrigerant inlet pipe, and the first swirl blade is located at the lower side of the upper end opening of the refrigerant inlet pipe.

[0017] Optionally, the outer edge of the first swirl blade is in contact with the inner wall of the tube body.

[0018] Optionally, the distance between the upper end opening of the refrigerant inlet pipe and the bottom surface of the tube body is greater than or equal to 1 / 2 of the height of the tube body.

[0019] Optionally, a plurality of through holes are formed on the surface of the swirl blade, and the plurality of through holes are evenly distributed along the spiral direction of the swirl blade.

[0020] Optionally, a plurality of the liquid refrigerant outlet holes are evenly spaced along the circumferential direction and arranged on the bottom surface of the tube body.

[0021] A liquid refrigerant outlet pipe is fixedly connected to the outer side of each liquid refrigerant outlet hole.

[0022] Optionally, the total area of ​​the plurality of liquid refrigerant outlet holes is smaller than the area of ​​the upper end opening of the refrigerant inlet pipe.

[0023] The utility model also provides a heat pump system, comprising:

[0024] Heat exchangers, and

[0025] In the gas-liquid separator described above, the gas refrigerant outlet pipe is used to communicate with the outlet branch of the heat exchanger, and the multiple liquid refrigerant outlet holes are used to communicate with the multiple inlet branches of the heat exchanger.

[0026] In the gas-liquid separator of the utility model, the refrigerant inlet pipe is used to transport gas-liquid two-phase refrigerant into the tube body, and the two-phase refrigerant flows upward along the refrigerant inlet pipe into the tube body. Under the action of gravity, a part of the two-phase refrigerant is separated into gas and liquid, and the gas phase refrigerant flows out from the gaseous refrigerant outlet pipe at the upper end of the tube body. The other part of the two-phase refrigerant contacts the swirl blades, is guided by the swirl blades, flows along the spiral direction of the swirl blades, and achieves gas-liquid separation through the centrifugal force. The gaseous refrigerant rises along the spiral of the swirl blades and flows out through the gaseous refrigerant outlet pipe, and the liquid refrigerant flows out from the multiple liquid refrigerant outlet holes on the bottom surface of the tube body.

[0027] Under the dual effects of gravity and centrifugal force, the refrigerant on the bottom of the tube body is a liquid refrigerant close to single-phase. When the liquid refrigerant flows out through multiple liquid refrigerant outlets, the liquid separation is completed, and the difficulty of liquid separation caused by gravity and the different back pressures at each branch of the heat exchanger is avoided.

[0028] Under the action of buoyancy and the flow guidance of the swirl blades, the gaseous refrigerant spirals up through the swirl blades and flows out through the gaseous refrigerant outlet pipe, and forms a negative pressure during the spiral rise process, further accelerating the separation of the gaseous refrigerant from the two-phase refrigerant and accelerating the upward flow out of the gaseous refrigerant outlet pipe. After the gaseous refrigerant is separated and flows out, it does not participate in the evaporation process of the evaporator, and will not absorb heat in the evaporator, nor will it affect the heat exchange efficiency of the evaporator, thus avoiding overheating of the refrigerant flowing out of the evaporator.

[0029] Compared with gas-liquid separation by gravity alone, the two-phase refrigerant in the present application has a more consistent flow direction, less turbulence, and less flow noise when flowing along the spiral direction of the swirl blade. On the other hand, the spiral structure of the swirl blade can have a sound-absorbing effect to a certain extent, which can further reduce the flow noise of the refrigerant.

[0030] Based on the detailed description of the specific embodiments of the present invention in combination with the accompanying drawings below, those skilled in the art will become more aware of the above and other purposes, advantages and features of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Hereinafter, some specific embodiments of the present invention will be described in detail in an exemplary and non-limiting manner with reference to the accompanying drawings. The same reference numerals in the accompanying drawings indicate the same or similar components or parts. It should be understood by those skilled in the art that these drawings are not necessarily drawn to scale. In the accompanying drawings:

[0032] Figure 1 is a schematic cross-sectional view of a gas-liquid separator according to an embodiment of the utility model;

[0033] Figure 2 is a schematic structural diagram of a second cyclone blade of a gas-liquid separator according to an embodiment of the utility model;

[0034] Figure 3 is a schematic cross-sectional view of a gas-liquid separator according to an embodiment of the utility model;

[0035] Figure 4 is a schematic structural diagram of a first cyclone blade of a gas-liquid separator according to an embodiment of the utility model;

[0036] Figure 5 is a schematic top view of the bottom of a gas-liquid separator according to an embodiment of the utility model;

[0037] Figure 6 It is a schematic structural diagram of a heat pump system according to an embodiment of the utility model.

[0038] List of reference numerals: 100, gas-liquid separator; 110, tube body; 120, refrigerant inlet pipe; 130, gaseous refrigerant outlet pipe; 140, liquid refrigerant outlet pipe; 141, liquid refrigerant outlet hole; 150, swirl blade; 160, through hole; 151, second swirl blade; 152, first swirl blade; 200, heat exchanger. DETAILED DESCRIPTION

[0039] Refer to the following Figures 1 to 6 To describe a gas-liquid separator and a heat pump system of an embodiment of the utility model. In the description of this embodiment, it should be understood that the terms "first" and "second" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features, that is, include one or more of the features. In the description of the utility model, the meaning of "multiple" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined. When a feature "includes or contains" one or some of the features it covers, unless otherwise specifically described, this indicates that other features are not excluded and may further include other features.

[0040] Unless otherwise clearly specified and limited, the terms "set", "install", "connect", "connect", "fix", "couple" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral one; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. A person of ordinary skill in the art should be able to understand the specific meanings of the above terms in the present utility model according to the specific circumstances.

[0041] In addition, in the description of this embodiment, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or may include the first and second features not being in direct contact but being in contact through another feature between them. That is, in the description of this embodiment, the first feature being "above", "above", and "above" the second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. The first feature being "below", "below", or "below" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0042] In the description of the present embodiment, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0043] Figure 1 is a schematic cross-sectional view of a gas-liquid separator 100 according to an embodiment of the present utility model, as shown Figure 1 As shown, and refer to Figures 2 to 6 The embodiment of the utility model provides a gas-liquid separator, comprising: a tube body 110, a refrigerant inlet pipe 120, a gaseous refrigerant outlet pipe 130, a plurality of liquid refrigerant outlet holes 141 and a swirl blade 150. The tube body 110 extends in the up-down direction. The refrigerant inlet pipe 120 penetrates the bottom surface of the tube body 110 from bottom to top, and extends upward for a distance. The gaseous refrigerant outlet pipe 130 is inserted at the upper end of the tube body 110. A plurality of liquid refrigerant outlet holes 141 are located on the bottom surface of the tube body 110 and are located on the periphery of the refrigerant inlet pipe 120. The swirl blade 150 is spiral-shaped and is directly or indirectly fixedly connected to the inside of the tube body 110. The swirl blade 150 is located on the lower side of the gaseous refrigerant outlet pipe 130.

[0044] In this embodiment, the refrigerant inlet pipe 120 is used to transport gas-liquid two-phase refrigerant into the tube body 110. The two-phase refrigerant enters the tube body 110. Under the action of gravity, a part of the two-phase refrigerant is separated into gas and liquid, and the gas phase refrigerant flows out from the gaseous refrigerant outlet pipe at the upper end of the tube body. The other part of the two-phase refrigerant contacts the swirl blades 150, is guided by the swirl blades 150, flows in the spiral direction of the swirl blades 150 inside the tube body 110, and achieves gas-liquid separation through the action of centrifugal force.

[0045] Under the influence of gravity, the liquid refrigerant flows downward and the gaseous refrigerant flows upward. The separated liquid refrigerant flows out of the tube body 110 through the multiple liquid refrigerant outlet holes 141 at the lower end of the tube body 110, and the gaseous refrigerant flows out of the tube body 110 through the gaseous refrigerant outlet pipe 130 at the upper end of the tube body 110, thereby realizing the separation of liquid refrigerant and gaseous refrigerant, solving the problem of difficulty in two-phase refrigerant separation, and achieving the purpose of improving the two-phase refrigerant separation efficiency.

[0046] Under the dual effects of gravity and centrifugal force, the refrigerant on the bottom surface of the tube body 110 is a liquid refrigerant close to a single-phase state. When the liquid refrigerant flows out through a plurality of liquid refrigerant outlet holes 141, liquid separation is completed, and the difficulty of liquid separation caused by gravity and the different back pressures at each branch point of the heat exchanger 200 is avoided.

[0047] Under the action of buoyancy and the guiding action of the swirl blades 150, at least part of the gaseous refrigerant spirally rises through the swirl blades 150 and flows out through the gaseous refrigerant outlet pipe 130, and forms a negative pressure in the process of spiral rise, further accelerating the separation of the gaseous refrigerant from the two-phase refrigerant, and accelerating the upward flow out of the gaseous refrigerant outlet pipe 130. After the gaseous refrigerant is separated and flows out, it does not participate in the heat exchange process of the heat exchanger 200, so it will not absorb heat in the heat exchanger 200, nor will it affect the heat exchange efficiency of the heat exchanger 200, thereby avoiding overheating of the refrigerant flowing out of the heat exchanger 200.

[0048] Compared with gas-liquid separation by gravity alone, the two-phase refrigerant in the present application has a more consistent flow direction, less turbulence, and less flow noise when flowing along the spiral direction of the swirl blade 150. On the other hand, the spiral structure of the swirl blade 150 can have a sound-absorbing effect to a certain extent, which can further reduce the flow noise of the refrigerant.

[0049] In some embodiments of the gas-liquid separator of the present invention, the swirl blades 150 are made of porous material to absorb the noise generated when the refrigerant flows.

[0050] In some embodiments of the gas-liquid separator of the present invention, the swirl blades 150 are made of porous material to absorb the noise generated when the refrigerant flows.

[0051] In some embodiments of the gas-liquid separator of the present utility model, Figure 1 As shown, the swirl blade 150 is a second swirl blade 151. The upper end of the second swirl blade 151 is fixedly connected to the lower end of the gas refrigerant outlet pipe 130.

[0052] In this embodiment, inside the tube body 110, the two-phase refrigerant is transported upward by the refrigerant inlet pipe 120, flows upward from the upper end opening of the refrigerant inlet pipe 120, falls on the second swirl blade 151, and then flows downward along the spiral direction of the second swirl blade 151, and the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are separated by centrifugal force. After the gaseous refrigerant and the liquid refrigerant are separated, the liquid refrigerant falls under the influence of gravity, accumulates at the lower part of the tube body 110, and flows out of the tube body 110 from the multiple liquid refrigerant outlet holes 141 at the lower end of the tube body 110. Since the density of the gaseous refrigerant is greater than that of the liquid refrigerant, it accumulates at the upper part of the tube body 110 and flows out of the tube body 110 from the gaseous refrigerant outlet pipe 130 at the upper end of the tube body 110. Under the action of buoyancy and the guiding action of the swirl blades 150 , at least part of the gaseous refrigerant spirals up and flows out through the gaseous refrigerant outlet pipe 130 , and forms a negative pressure during the spiral ascent, further accelerating the separation of the gaseous refrigerant from the two-phase refrigerant and accelerating the upward flow out of the gaseous refrigerant outlet pipe 130 .

[0053] The gas-liquid separator 100 has a simple structure and is easy to manufacture, thereby reducing the production cost of the gas-liquid separator 100. Moreover, the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are separated by the gas-liquid separator 100, thereby reducing the difficulty of separating the liquid refrigerant from the two-phase refrigerant and improving the two-phase refrigerant separation efficiency.

[0054] In some embodiments of the gas-liquid separator of the present invention, the second cyclone blade 151 and the gas refrigerant outlet pipe 130 are an integrally formed structure.

[0055] Alternatively, the second swirl blade 151 may also be connected to the lower end of the gas refrigerant outlet pipe 130 by a fixed connection method such as gluing.

[0056] In some embodiments of the gas-liquid separator of the present utility model, Figure 1 or Figure 2 As shown, the outer diameter of the second swirl blade 151 gradually increases from top to bottom, and the maximum outer diameter of the second swirl blade 151 is smaller than the inner diameter of the tube body 110 .

[0057] In this embodiment, on the one hand, as the refrigerant flows, the amount of refrigerant becomes less as it is closer to the upper end of the second swirl blade 151 due to the influence of gravity. Reducing the outer diameter of the upper end of the second swirl blade 151 can reduce the use of material for the second swirl blade 151, thereby reducing manufacturing costs.

[0058] On the other hand, since the inertia of the gaseous refrigerant in the two-phase refrigerant is smaller than that of the liquid refrigerant, as the refrigerant flows, the amount of gaseous refrigerant closer to the upper end of the second swirl blade 151 becomes smaller, thereby reducing the outer diameter of the upper end of the second swirl blade 151 to facilitate the liquid refrigerant at the upper end of the second swirl blade 151 to flow down, thereby improving the liquid separation efficiency.

[0059] Moreover, there is a gap between the outer edge of the second swirl blade 151 and the inner wall of the tube body 110, so that the liquid refrigerant at the upper end of the second swirl blade 151 can flow down, thereby improving the liquid separation efficiency.

[0060] In some embodiments of the gas-liquid separator of the present utility model, Figure 1 As shown, the bottom of the second swirl blade 151 is located at the lower side of the upper end opening of the refrigerant inlet pipe 120.

[0061] In this embodiment, the first refrigerant swirl blade 150 is spiral-shaped, the bottom portion of the second swirl blade 151 is arranged around the outer periphery of the upper end of the refrigerant inlet pipe 120, and the upper end of the refrigerant inlet pipe 120 is spaced apart from the first refrigerant swirl blade 150. The bottom of the second swirl blade 151 is located at the lower side of the upper end opening of the refrigerant inlet pipe 120, and part of the gaseous refrigerant flows out of the tube body 110 through the gaseous refrigerant outlet pipe 130 at the upper end of the tube body 110 in a spiral, and forms a negative pressure during the spiral rising process, further accelerating the separation of the gaseous refrigerant from the two-phase refrigerant, and accelerating the upward flow of the gaseous refrigerant outlet pipe 130. At the same time, the two-phase refrigerant flowing out of the refrigerant inlet pipe 120 is more fully contacted with the second swirl blade 151, thereby improving the separation efficiency of the liquid refrigerant and the gaseous refrigerant in the two-phase refrigerant. The upper end of the refrigerant inlet pipe 120 is spaced apart from the first refrigerant swirl blade 150 , which does not affect the outflow of the refrigerant from the upper end opening of the refrigerant inlet pipe 120 , thereby avoiding the generation of noise due to blockage of the upper end opening of the refrigerant inlet pipe 120 , and even affecting the normal operation of the gas-liquid separator 100 .

[0062] In some other embodiments of the gas-liquid separator 100 of the present invention, the bottom of the second cyclone blade 151 and the upper opening of the refrigerant inlet pipe 120 are spaced apart in the vertical direction.

[0063] In this embodiment, the second cyclone blade 151 is spaced apart from the refrigerant inlet pipe 120, so that the structure of the gas-liquid separator 100 is easy to manufacture and install, and the production cost of the gas-liquid separator 100 is reduced. At the same time, the faults caused by the friction or even collision between the second cyclone blade 151 and the refrigerant inlet pipe 120 are reduced, and the user experience is improved.

[0064] In some other embodiments of the gas-liquid separator 100 of the present invention, the distance between the bottom of the second cyclone blade 151 and the top surface of the tube body 110 is greater than or equal to 1 / 2 of the height of the tube body 110 .

[0065] In this embodiment, the bottom of the second swirl blade 151 is at a large distance from the top surface of the tube body 110, and the arrangement range of the second swirl blade 151 can be appropriately extended to increase the length of the contact path between the two-phase refrigerant and the second swirl blade 151, so that the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant can be more fully separated, thereby further reducing the dryness of the refrigerant, and even approaching a single-phase (liquid phase) state.

[0066] Preferably, the distance between the bottom of the second swirl blade 151 and the top surface of the tube body 110 is 1 / 2 of the height of the tube body 110 .

[0067] In this embodiment, the total height of the second swirl blade 151 is 1 / 2 of the total height of the tube body 110. While increasing the length of the contact path between the two-phase refrigerant and the second swirl blade 151, so that the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant can be more fully separated, it also avoids the waste of material of the second swirl blade 151 caused by the total length of the second swirl blade 151 being too long and the two-phase refrigerant being unable to reach the upper side of the second swirl blade 151 for liquid separation.

[0068] In some embodiments of the gas-liquid separator of the present utility model, Figure 3 or Figure 4 As shown, the swirl blade 150 is a first swirl blade 152 . The first swirl blade 152 is spirally wound around the outer circumference of the refrigerant inlet pipe 120 , and the first swirl blade 152 is located at the lower side of the upper end opening of the refrigerant inlet pipe 120 .

[0069] In this embodiment, inside the tube body 110, the two-phase refrigerant flows out from the upper end opening of the refrigerant inlet pipe 120, falls on the first swirl blade 152 due to gravity, and under the influence of inertia, the two-phase refrigerant flows downward along the spiral direction of the first swirl blade 152, and the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are separated by centrifugal force. After the gaseous refrigerant and the liquid refrigerant are separated, the liquid refrigerant falls under the influence of gravity, accumulates at the lower part of the tube body 110, and flows out of the tube body 110 from the multiple liquid refrigerant outlet holes 141 at the lower end of the tube body 110. Since the density of the gaseous refrigerant is greater than that of the liquid refrigerant, it accumulates at the upper part of the tube body 110 and flows out of the tube body 110 from the gaseous refrigerant outlet pipe 130 at the upper end of the tube body 110. The refrigerant on the bottom surface of the tube body 110 is a liquid refrigerant close to a single phase. When the liquid refrigerant flows out through the multiple liquid refrigerant outlet holes 141, the liquid separation is completed, and the difficulty of liquid separation caused by gravity and the different back pressures at each branch port of the heat exchanger 200 is avoided.

[0070] The gas-liquid separator 100 has a simple structure and is easy to manufacture and maintain, thereby reducing the production cost of the gas-liquid separator 100. Moreover, the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are separated by the gas-liquid separator 100, which reduces the difficulty of separating the liquid refrigerant from the two-phase refrigerant and improves the two-phase refrigerant separation efficiency.

[0071] In some embodiments of the gas-liquid separator of the present invention, the first cyclone blade 152 and the refrigerant inlet pipe 120 are an integrally formed structure.

[0072] Alternatively, the second swirl blades 151 may also be connected to the outer periphery of the refrigerant inlet pipe 120 by a fixed connection method such as gluing.

[0073] In some embodiments of the gas-liquid separator of the present invention, at least a portion of the outer edge of the first cyclone blade 152 is in contact with the inner wall of the tube body 110 .

[0074] Preferably, in some embodiments of the gas-liquid separator of the present utility model, Figure 3 As shown, the entire outer edge of the first swirl blade 152 is in contact with the inner wall of the tube body 110 .

[0075] In this embodiment, there is no gap between the outer edge of the first swirl blade 152 and the inner wall of the tube body 110, and the refrigerant flowing downward can only flow downward along the spiral direction of the first swirl blade 152, thereby further separating the refrigerant flowing downward, and making the gaseous refrigerant and liquid refrigerant in the two-phase refrigerant more fully separated. Fully separating the liquid refrigerant alleviates the defects of the two-phase refrigerant in the operation of the heat pump system, improves the heat exchange effect of the heat pump system, reduces the refrigerant flow noise, and thus improves the quality of the heat pump system.

[0076] In some embodiments of the gas-liquid separator of the present invention, the distance between the upper end opening of the refrigerant inlet pipe 120 and the bottom surface of the tube body 110 is greater than or equal to 1 / 2 of the height of the tube body 110 .

[0077] In this embodiment, the distance between the upper end opening of the refrigerant inlet pipe 120 and the bottom surface of the tube body 110 is appropriately increased, which can extend the arrangement range of the first swirl blade 152, so as to increase the length of the contact path between the two-phase refrigerant and the first swirl blade 152, so that the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant can be more fully separated, thereby further reducing the refrigerant dryness, and even approaching a single-phase (liquid phase) state.

[0078] Preferably, in some embodiments of the gas-liquid separator of the present utility model, the distance between the upper end opening of the refrigerant inlet pipe 120 and the bottom surface of the tube body 110 is 2 / 3 of the height of the tube body 110 .

[0079] In this embodiment, the total height of the first swirl blade 152 is 2 / 3 of the total height of the tube body 110. While increasing the length of the contact path between the two-phase refrigerant and the first swirl blade 152, so that the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant can be more fully separated, it also avoids the waste of material of the first swirl blade 152 caused by the total length of the first swirl blade 152 being too long and the two-phase refrigerant being unable to reach the lower side of the first swirl blade 152 for liquid separation.

[0080] In some embodiments of the gas-liquid separator of the utility model, the swirl blade 150 includes a second swirl blade 151 and a first swirl blade 152. The upper end of the second swirl blade 151 is fixedly connected to the lower end of the gaseous refrigerant outlet pipe 130. The first swirl blade 152 is spirally wound around the outer circumference of the refrigerant inlet pipe 120, and the first swirl blade 152 is located at the lower side of the upper end opening of the refrigerant inlet pipe 120.

[0081] In this embodiment, inside the tube body 110, the two-phase refrigerant is transported upward by the refrigerant inlet pipe 120 and flows out from the upper end opening of the refrigerant inlet pipe 120, so that the two-phase refrigerant contacts the second swirl blade 151. Affected by inertia, the two-phase refrigerant flows upward along the spiral direction of the second swirl blade 151, and the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are separated by centrifugal force.

[0082] The refrigerant left from the second swirl blade 151 falls to the first swirl blade 152, and the two-phase refrigerant flows downward along the spiral direction of the first swirl blade 152, and the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are further separated by centrifugal force.

[0083] After the gaseous refrigerant and the liquid refrigerant are separated, the liquid refrigerant falls under the influence of gravity, accumulates at the lower part of the tube body 110, and flows out of the tube body 110 from the multiple liquid refrigerant outlet holes 141 at the lower end of the tube body 110. Since the density of the gaseous refrigerant is greater than that of the liquid refrigerant, it accumulates at the upper part of the tube body 110 and flows out of the tube body 110 from the gaseous refrigerant outlet pipe 130 at the upper end of the tube body 110. The refrigerant on the bottom surface of the tube body 110 is a liquid refrigerant close to a single phase. When the liquid refrigerant flows out through the multiple liquid refrigerant outlet holes 141, liquid separation is completed, and the difficulty of liquid separation caused by gravity and the different back pressures of each branch port of the heat exchanger 200 is avoided.

[0084] The gas-liquid separator 100 has a simple structure and is easy to manufacture, thereby reducing the production cost of the gas-liquid separator 100. Moreover, the gaseous refrigerant and the liquid refrigerant in the two-phase refrigerant are fully separated by the second cyclone blades 151 and the first cyclone blades 152 in the gas-liquid separator 100, thereby reducing the difficulty of separating the liquid refrigerant from the two-phase refrigerant and improving the two-phase refrigerant separation efficiency.

[0085] In some embodiments of the gas-liquid separator of the present utility model, Figure 2 or Figure 4 As shown, a plurality of through holes 160 are formed on the surface of the swirl blade 150 .

[0086] In this embodiment, when the refrigerant flows on the surface of the swirl blade 150, the liquid refrigerant can leak to the lower end of the through hole 160 through the through hole 160, thereby improving the efficiency of separating the liquid refrigerant from the two-phase refrigerant. In addition, the through hole 160 has a sound-absorbing effect, reducing the noise generated when the refrigerant flows in the tube body 110.

[0087] Preferably, in some embodiments of the gas-liquid separator of the present invention, the plurality of through holes 160 are evenly distributed along the spiral direction of the swirl blade 150 .

[0088] In this embodiment, the through holes 160 evenly distributed on the swirl blades 150 are in more sufficient contact with the refrigerant, and the manufacturing method is simple, thereby reducing the production cost.

[0089] Alternatively, as many through holes 160 as possible are arranged on the swirl blades 150 , and each through hole 160 is arranged at intervals.

[0090] In this embodiment, the number of through holes 160 is large, so that the through holes 160 on the swirl blades 150 are in more complete contact with the refrigerant, thereby increasing the falling speed of the liquid refrigerant and further increasing the liquid separation efficiency of the gas-liquid separator 100 .

[0091] In some embodiments of the gas-liquid separator of the present invention, a plurality of liquid refrigerant outlet holes 141 are evenly spaced and arranged along the circumferential direction on the bottom surface of the tube body 110. A liquid refrigerant outlet pipe 140 is fixedly connected to the outer side of each liquid refrigerant outlet hole 141.

[0092] In this embodiment, the liquid refrigerant outlet pipe 140 is connected to the heat exchanger 200 to transport the liquid refrigerant to the heat exchanger 200 for heat exchange. The liquid refrigerant outlet pipe 140 is fixedly connected to the outside of the liquid refrigerant outlet hole 141, and the liquid refrigerant outlet pipe 140 will not interfere with the liquid refrigerant in the tube body 110 entering the liquid refrigerant outlet pipe 140 through the liquid refrigerant outlet hole 141.

[0093] In some embodiments of the gas-liquid separator of the present utility model, Figure 5 As shown, a plurality of liquid refrigerant outlet holes 141 are symmetrically and spaced apart along the front-to-back direction and the left-to-right direction on the bottom surface of the tube body 110 .

[0094] Furthermore, the number of the liquid refrigerant outlet holes 141 is consistent with the number of the inlet branches of the heat exchanger 200 .

[0095] Preferably, there are 8 liquid refrigerant outlet holes 141 .

[0096] Furthermore, in some embodiments of the gas-liquid separator of the present invention, the apertures of each through hole 160 are the same. Each branch adjusts different refrigerant flow rates by adjusting the external capillary force.

[0097] Alternatively, the apertures of the plurality of through holes 160 are different, so that the resistance of the liquid refrigerant passing through the apertures is different, thereby making the refrigerant flow rates of each branch different to meet different needs.

[0098] In some embodiments of the gas-liquid separator of the present invention, the total area of ​​the plurality of liquid refrigerant outlet holes 141 is smaller than the area of ​​the upper opening of the refrigerant inlet pipe 120 .

[0099] In this embodiment, the flow rate of the two-phase refrigerant entering the tube body 110 from the upper end opening of the refrigerant inlet tube 120 and the flow rate of the refrigerant flowing out of the tube body 110 from the liquid refrigerant outlet hole 141 are controlled by the liquid refrigerant outlet hole 141 and the cross-sectional area of ​​the refrigerant inlet tube 120, so that the amount of the two-phase refrigerant entering the tube body 110 from the upper end opening of the refrigerant inlet tube 120 is greater than the amount of the refrigerant flowing out of the tube body 110 from the liquid refrigerant outlet hole 141, that is, the amount of the separated liquid refrigerant is greater than or equal to the amount of the liquid refrigerant flowing out of the tube body 110 from the liquid refrigerant outlet hole 141. It is avoided that the amount of the two-phase refrigerant entering the tube body 110 is too small, resulting in too small an amount of the liquid refrigerant separated in the tube body 110, thereby causing a large amount of gaseous refrigerant to flow out of the liquid refrigerant outlet hole 141.

[0100] Alternatively, the flow rate of the two-phase refrigerant entering the tube body 110 from the upper end opening of the refrigerant inlet pipe 120 and the flow rate of the refrigerant flowing out of the tube body 110 from the liquid refrigerant outlet hole 141 may also be controlled by adjusting the pressure.

[0101] In some embodiments of the gas-liquid separator of the present invention, the tube body 110 is in the shape of a hollow shell.

[0102] Further, in some embodiments of the gas-liquid separator of the present utility model, Figure 1 or Figure 3 As shown, both ends of the tube body 110 are tapered, and the tapered opening faces the center of the tube body 110 .

[0103] In this embodiment, both ends of the tube body 110 are designed to be tapered, which can guide the flow of gaseous refrigerant and liquid refrigerant.

[0104] Alternatively, the tube body 110 may also be a cylinder. Both ends of the tube body 110 are flat surfaces.

[0105] In this embodiment, the liquid refrigerant outlet hole 141 is located at the bottom of the tube body 110 , thereby preventing a portion of the liquid refrigerant from being unable to flow out of the liquid refrigerant outlet pipe 140 .

[0106] The present utility model also provides a heat pump system. In some embodiments of the heat pump system of the present utility model, such as Figure 6 As shown, the heat pump system includes: a heat exchanger 200, and a gas-liquid separator 100 of any of the above-mentioned embodiments, the gas refrigerant outlet pipe 130 is used to communicate with the outlet branch of the heat exchanger 200, and the multiple liquid refrigerant outlet holes 141 are used to communicate with the multiple inlet branches of the heat exchanger 200.

[0107] In this embodiment, the refrigerant inlet pipe 120 of the gas-liquid separator 100 in the heat pump system is used to transport the gas-liquid two-phase refrigerant into the tube body 110. The two-phase refrigerant enters the tube body 110. Under the action of gravity, a part of the two-phase refrigerant is separated into gas and liquid, and the gas phase refrigerant flows out from the gaseous refrigerant outlet pipe at the upper end of the tube body. The other part of the two-phase refrigerant contacts the swirl blades 150, is guided by the swirl blades 150, flows in the spiral direction of the swirl blades 150 inside the tube body 110, and achieves gas-liquid separation through the action of centrifugal force.

[0108] Under the influence of gravity, the liquid refrigerant flows downward and the gaseous refrigerant flows upward. The separated liquid refrigerant flows out of the tube body 110 through the multiple liquid refrigerant outlet holes 141 at the lower end of the tube body 110, and the gaseous refrigerant flows out of the tube body 110 through the gaseous refrigerant outlet pipe 130 at the upper end of the tube body 110, thereby realizing the separation of liquid refrigerant and gaseous refrigerant, solving the problem of difficulty in two-phase refrigerant separation, and achieving the purpose of improving the two-phase refrigerant separation efficiency.

[0109] Under the dual effects of gravity and centrifugal force, the refrigerant on the bottom surface of the tube body 110 is a liquid refrigerant close to a single-phase state. When the liquid refrigerant flows out through a plurality of liquid refrigerant outlet holes 141, liquid separation is completed, and the difficulty of liquid separation caused by gravity and the different back pressures at each branch point of the heat exchanger 200 is avoided.

[0110] Under the action of buoyancy and the guiding action of the swirl blades 150, at least part of the gaseous refrigerant spirals up through the swirl blades 150 and flows out through the gaseous refrigerant outlet pipe 130, and forms a negative pressure during the spiral ascent, further accelerating the separation of the gaseous refrigerant from the two-phase refrigerant and accelerating the upward flow out of the gaseous refrigerant outlet pipe 130.

[0111] After the gaseous refrigerant is separated and flows out, it does not participate in the heat exchange process of the heat exchanger 200, will not absorb heat in the heat exchanger 200, and will not affect the heat exchange efficiency of the heat exchanger 200, thereby avoiding overheating of the refrigerant flowing out of the heat exchanger 200.

[0112] Compared with gas-liquid separation by gravity alone, the two-phase refrigerant in the present application has a more consistent flow direction, less turbulence, and less flow noise when flowing along the spiral direction of the swirl blade 150. On the other hand, the spiral structure of the swirl blade 150 can have a sound-absorbing effect to a certain extent, which can further reduce the flow noise of the refrigerant.

[0113] At this point, those skilled in the art should recognize that, although multiple exemplary embodiments of the present invention have been shown and described in detail herein, many other variations or modifications that conform to the principles of the present invention can still be directly determined or derived from the contents disclosed in the present invention without departing from the spirit and scope of the present invention. Therefore, the scope of the present invention should be understood and recognized as covering all such other variations or modifications.

Claims

1. A gas-liquid separator, characterized in that: include: A tube body extending in an up-down direction; A refrigerant inlet pipe, the refrigerant inlet pipe penetrates the bottom surface of the tube body from bottom to top and extends upward for a distance; A gaseous refrigerant outlet pipe, wherein the gaseous refrigerant outlet pipe is inserted at the upper end of the tube body; A plurality of liquid refrigerant outlet holes, wherein the plurality of liquid refrigerant outlet holes are located on the bottom surface of the tube body and are located on the periphery of the refrigerant inlet tube; The swirl blades are spiral-shaped and are directly or indirectly fixedly connected to the inside of the tube body; the swirl blades are located at the lower side of the gaseous refrigerant outlet pipe.

2. The gas-liquid separator according to claim 1, characterized in that: The swirl blade is a first swirl blade; the first swirl blade is spirally wound around the outer circumference of the refrigerant inlet pipe, and the first swirl blade is located at the lower side of the upper end opening of the refrigerant inlet pipe.

3. The gas-liquid separator according to claim 2, characterized in that: The outer edge of the first swirl blade contacts the inner wall of the tube body.

4. The gas-liquid separator according to claim 2, characterized in that: The distance between the upper end opening of the refrigerant inlet pipe and the bottom surface of the tube body is greater than or equal to 1 / 2 of the height of the tube body.

5. The gas-liquid separator according to claim 1, characterized in that: The swirl blade is a second swirl blade; the upper end of the second swirl blade is fixedly connected to the lower end of the gaseous refrigerant outlet pipe.

6. The gas-liquid separator according to claim 5, characterized in that: From top to bottom, the outer diameter of the second swirl blade gradually increases; and the maximum outer diameter of the second swirl blade is smaller than the inner diameter of the tube body.

7. The gas-liquid separator according to claim 5, characterized in that: The bottom of the second swirl blade is located at the lower side of the upper end opening of the refrigerant inlet pipe.

8. The gas-liquid separator according to claim 1, characterized in that: A plurality of through holes are formed on the surface of the swirl blade, and the plurality of through holes are evenly distributed along the spiral direction of the swirl blade.

9. The gas-liquid separator according to claim 1, characterized in that: A plurality of the liquid refrigerant outlet holes are evenly spaced and arranged on the bottom surface of the tube body along the circumferential direction; A liquid refrigerant outlet pipe is fixedly connected to the outer side of each of the liquid refrigerant outlet holes; and / or The total area of ​​the plurality of liquid refrigerant outlet holes is smaller than the area of ​​the upper end opening of the refrigerant inlet pipe.

10. A heat pump system, characterized in that: include: Heat exchangers, and In the gas-liquid separator described in any one of claims 1 to 9 above, the gas refrigerant outlet pipe is used to communicate with the outlet branch of the heat exchanger, and the multiple liquid refrigerant outlet holes are used to communicate with the multiple inlet branches of the heat exchanger.

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