Oil separator and heat pump system

Abstract

An oil separator and a heat pump system can reduce the area where an oil-gas mixture flows slowly or does not flow between a gas inlet pipe and the top wall of the oil separator, and can improve the oil-gas separation efficiency of the oil separator. The oil separator comprises a tank body, an oil return pipe, an air inlet pipe, a spiral guide plate and an exhaust pipe, and one end of the oil return pipe is connected with the tank body from one end of the tank body through a tank body oil return opening. One end of the exhaust pipe is inserted from the other end, opposite to the end, of the tank body through the upper exhaust port and extends into the tank body, one end of the air inlet pipe is inserted from the side wall of the tank body through the air inlet and extends into the tank body, and the spiral guide plate is installed in the tank body; a plurality of layers of spiral blades continuously and spirally extend to the oil return port of the tank body around the axis of the tank body to form the spiral guide plate, and in the axial direction of the tank body, an air inlet port, extending into the tank body, of the air inlet pipe is located below the spiral blade on the uppermost layer of the spiral guide plate.

Description

Technical Field

[0001] This utility model relates to the field of oil separation technology, and more specifically to an oil separator for separating lubricating oil from gaseous refrigerant, and a heat pump system having the oil separator. Background Technology

[0002] The compressor of a heat pump system requires lubricating oil for operation, but when the refrigerant is discharged from the compressor, the lubricating oil is discharged along with the refrigerant.

[0003] If lubricating oil circulates together with refrigerant in a heat pump system, it will increase the thermal resistance of the pipes in the heat pump system, reduce the heat transfer effect, and thus reduce the working efficiency of the heat pump system. On the other hand, if the lubricating oil is not returned to the compressor in time, the compressor will be in a state of lubricating oil shortage, which will shorten the service life of the compressor.

[0004] Chinese utility model publication CN221122598U discloses an oil separator.

[0005] like Figure 6 As shown, the oil separator includes: a tank 10, one end of which has a first connecting hole 11; an oil return pipe 20, one end of which is inserted into the first connecting hole 11 and connected to the tank 10 through the first connecting hole 11; an air inlet pipe 30, one end of which passes through the side wall of the tank 10 and extends into the tank 10; and a spiral guide plate 40, installed inside the tank 10 and spirally extending around the axis of the tank 10 toward the first connecting hole 11; wherein, along the axial direction of the tank 10, the spiral guide plate 40 is located between the end of the air inlet pipe 30 extending into the tank 10 and the first connecting hole 11. Using this existing oil separator, by setting the spiral guide plate 40, the refrigerant, after entering the tank 10, can flow along the spiral direction of the spiral guide plate 40, thereby improving the oil-gas separation effect.

[0006] However, in the existing design, since the spiral guide plate 40 is located between the end of the intake pipe 30 that extends into the tank 10 and the first connecting hole 11, that is, the intake pipe 30 is located above the uppermost spiral blade of the spiral guide plate 40 (located above the uppermost spiral blade of the spiral guide plate 40), when the flow velocity of the intake fluid (a mixture of gaseous refrigerant and lubricating oil, hereinafter referred to as "oil-gas mixture") flowing in through the intake pipe 30 is low, a slow-flowing or even non-flowing area is easily formed in the region between the intake pipe 30 and the top wall of the oil separator. This causes the lubricating oil in the oil-gas mixture to drip onto the spiral guide plate 40 and become difficult to return to the compressor, thereby reducing the oil-gas separation efficiency of the oil separator.

[0007] Therefore, there is an urgent need to find a new type of oil separator and heat pump system that can reduce the area of ​​slow or no flow between the air inlet pipe and the top wall of the oil separator, and improve the oil-gas separation efficiency of the oil separator. Utility Model Content

[0008] This invention addresses the problems of the prior art by providing an oil separator that reduces the area of ​​slow or no flow between the air inlet pipe and the top wall of the oil separator, and improves the oil-gas separation efficiency of the oil separator.

[0009] Another objective of this invention is to provide a heat pump system including the aforementioned oil separator.

[0010] To achieve the above objectives, this utility model provides an oil separator, including a tank, an oil return pipe, an air inlet pipe, a spiral guide plate, and an exhaust pipe. One end of the oil return pipe is connected to the tank via an oil return port from one end of the tank. One end of the exhaust pipe is inserted into the tank via an upper exhaust port from the opposite end of the tank. One end of the air inlet pipe is inserted into the tank via an air inlet from the side wall of the tank. The spiral guide plate is installed in the tank and is formed by multiple spiral blades that continuously extend spirally around the axis of the tank towards the oil return port. The characteristic feature is that, axially, the air inlet port of the air inlet pipe extending into the tank is located below the uppermost spiral blade of the spiral guide plate.

[0011] As described above, by setting a spiral guide plate, the refrigerant can flow along the spiral direction of the guide plate after entering the tank, which improves the oil-gas separation effect. In particular, in the axial direction of the tank, by placing the inlet port of the inlet pipe into the tank below the uppermost spiral blade of the spiral guide plate, the area between the inlet pipe and the top wall of the tank in the oil separator that forms a slow-flowing or non-flowing area is greatly reduced. This allows the oil-gas mixture entering from the inlet pipe to be guided by the upper and lower spiral blades, and to perform centrifugal rotation along the spiral channel formed by the spiral blades, thereby improving the oil-gas separation efficiency.

[0012] Preferably, the blade surface of the spiral blade of the spiral guide plate is inclined such that the portion of the blade surface closer to the axis of the tank is higher and the portion closer to the outer circumference of the tank is lower. Therefore, even if the flow rate of the oil-gas mixture flowing in through the intake pipe is low (at a low flow rate), the lubricating oil drips onto the spiral blade and has difficulty dripping down along the spiral guide plate. The blade surface of the spiral blade, which is inclined such that the portion closer to the axis of the tank is higher and the portion closer to the outer circumference of the tank is lower, can accelerate the sliding of the lubricating oil to the outer circumference, causing the lubricating oil to drip down along the inner wall of the tank, thereby improving the oil-gas separation efficiency.

[0013] More preferably, when the angle between the surface of the spiral blade and the horizontal plane is set to α, the value of α satisfies the relationship 0°<α≤45°. This avoids excessive sliding of the oil-gas mixture to the outer periphery when the flow velocity of the oil-gas mixture flowing in through the inlet pipe is high (at normal flow rate), and accelerates the sliding of the lubricating oil to the outer periphery when the flow velocity of the oil-gas mixture flowing in through the inlet pipe is low (at low flow rate), causing the lubricating oil to drip downwards along the inner wall of the tank, thereby ensuring that the oil separator always has a high oil-gas separation efficiency.

[0014] Furthermore, preferably, the intake port of the intake pipe extending into the tank is located between two layers of spiral blades along the axial direction of the tank, and is positioned closer to the upper spiral blade. This allows the intake pipe to extend further into the tank without touching the lower spiral blade (the second spiral blade). Additionally, the deeper the intake pipe extends into the tank, the closer it gets to the exhaust pipe or the inner wall of the tank, making it easier for the oil-gas mixture entering from the intake pipe to collide with the outer wall of the exhaust pipe or the inner wall of the tank, thereby improving oil-gas separation efficiency.

[0015] In one embodiment of this invention, the air inlet port of the air inlet pipe extending into the tank is entirely or at least partially located within the projection area of ​​the spiral guide plate, which is positioned above one end of the air inlet pipe along the axial direction of the tank. Thus, the oil-gas mixture entering from the air inlet pipe is guided by the spiral blades located above the air inlet pipe (i.e., the first spiral blade), preventing it from entering the slow-flowing or stagnant area near the top wall of the tank in the oil separator, thereby effectively improving the oil-gas separation efficiency of the oil separator.

[0016] In addition, preferably, the air intake port of the air intake pipe extending into the tank is entirely or at least partially located in the projection area of ​​the spiral guide plate, which is located below one end of the air intake pipe in the axial direction of the tank.

[0017] This ensures that the oil-gas mixture entering from the intake pipe is guided by the lower section of spiral blades (i.e., the second spiral blades), allowing the oil-gas mixture to flow along the spiral guide plate after entering the tank, avoiding turbulence and ensuring oil-gas separation efficiency.

[0018] In another embodiment of this invention, along the radial direction of the tank body, the outer diameter of the spiral guide plate is d, and the inner diameter of the tank body is D, satisfying 0.5D≤d≤D. Since a larger outer diameter of the spiral guide plate ensures a larger radial dimension, a larger outer diameter spiral guide plate is beneficial for guiding the refrigerant, ensuring sufficient spiral motion of the oil-gas mixture for centrifugal separation. Furthermore, when the outer diameter d of the spiral guide plate is equal to the inner diameter D of the tank body, the outer wall of the spiral guide plate abuts against the inner wall of the tank body, at which point the size of the spiral guide plate is at its maximum.

[0019] In another embodiment of this utility model, the central axis of the air intake pipe extending into the tank body is perpendicular to and intersects with the central axis of the exhaust pipe, or they are perpendicular to each other in opposite planes.

[0020] When the central axis of the intake pipe is perpendicular to and intersects the central axis of the exhaust pipe,

[0021] Preferably, the intake port of the intake pipe is directly opposite the outer wall of the exhaust pipe, which makes it easier for the oil-gas mixture entering from the intake pipe to directly collide with the exhaust pipe, thereby improving the oil-gas separation efficiency.

[0022] Furthermore, when the central axis of the intake pipe and the central axis of the exhaust pipe are perpendicular to each other in opposite planes, it is preferable that the end of the intake pipe extending into the tank body has a guide surface, and the guide surface is inclined along the direction of rotation of the spiral guide plate. This facilitates the refrigerant entering the guiding area of ​​the spiral guide plate along the inclined direction of the guide surface. Further preferably, the angle β between the guide surface of the intake pipe and the half-section of the exhaust pipe that passes through and is perpendicular to the central axis of the intake pipe is 0° < β ≤ 60°. This allows the oil-gas mixture entering from the intake pipe to more easily undergo centrifugal motion along the inner wall of the tank, ensuring efficient oil-gas separation.

[0023] In another embodiment of this utility model, the axial distance between the exhaust port of the exhaust pipe inside the tank body and the oil return port of the tank body is H, and the axial distance between the oil return port of the tank body and the upper exhaust port is L, satisfying the relationship 1 / 4×L≤H≤2 / 3×L. If the exhaust port is too far from the oil return port of the tank body, that is, if H>2 / 3×L, then either the axial stroke of the spiral guide plate along the tank body will be too short, resulting in insufficient oil-gas separation, or the volume of the oil separator will be unnecessarily large. On the other hand, if the exhaust port is too close to the oil return port of the tank body, that is, if H<1 / 4×L, then the port of the exhaust pipe inside the tank body will be too close to the oil surface at the bottom, making it easy for oil droplets to be mistakenly carried back into the exhaust pipe by the airflow, thus reducing the oil-gas separation efficiency.

[0024] Furthermore, it is conceivable that a baffle plate be installed at the exhaust port inside the tank body of the exhaust pipe. Since oil droplets will flow down the spiral blades on the outer wall of the exhaust port inside the tank body, the baffle plate can prevent these oil droplets from being mistakenly carried back to the exhaust pipe by the airflow.

[0025] To achieve another objective, this utility model provides a heat pump system, characterized in that,

[0026] This includes any of the aforementioned oil separators. Therefore, this oil separator can efficiently and reliably separate the refrigerant flowing from the compressor from the lubricating oil carried away from the compressor, avoiding many adverse effects caused by the lubricating oil circulating together with the refrigerant in the heat pump system. For example, it can increase the thermal resistance of the pipes in the heat pump system, reducing heat transfer efficiency and thus lowering the system's operating efficiency. Furthermore, it can cause the compressor to be in a state of lubricant shortage due to the lubricating oil not returning in time, shortening the compressor's lifespan. Attached Figure Description

[0027] Figure 1 This is a perspective perspective view illustrating the overall structure of the oil separator of this utility model.

[0028] Figure 2 This is a cross-sectional view schematically showing the internal structure and layout of the oil separator of this utility model.

[0029] Figures 3A to 3D These are schematic diagrams illustrating the positional relationship between the intake pipe and the exhaust pipe in the oil separators of the embodiments and modifications of this utility model. Figure 2 A sectional view along the AA direction.

[0030] Figure 4 This is a schematic diagram illustrating the dimensional relationship between the spiral guide plate and the tank body in the oil separator of this utility model. Figure 2 A cross-sectional view along the BB direction.

[0031] Figure 5 This is a schematic diagram of a heat pump system with an oil separator.

[0032] Figure 6 This is a cross-sectional view illustrating the internal structure and layout of an existing oil separator.

[0033] (Symbol Explanation)

[0034] 100 compressor;

[0035] 200 oil separator;

[0036] 210 Tank body;

[0037] 211 Tank return port;

[0038] 212 Upper exhaust port;

[0039] 213 Air intake;

[0040] 220 return oil pipe;

[0041] 230 intake pipe;

[0042] 230ax (intake manifold) center axis;

[0043] 231 Guiding surface;

[0044] 240 spiral guide vane;

[0045] 240a Helical starting end;

[0046] 240b spiral termination end;

[0047] 241 Helical blade;

[0048] 241a First helical blade;

[0049] 241b Second helical blade;

[0050] 241c blade surface;

[0051] 250 exhaust pipe;

[0052] The central axis of 250ax (exhaust pipe);

[0053] 250b (exhaust pipe) half-section;

[0054] 260 deflector;

[0055] α: The angle between the blade surface of the helical blade and the horizontal plane;

[0056] β is the angle between the guide surface of the intake manifold and the half-section of the exhaust manifold.

[0057] D. Inner diameter of the tank;

[0058] d. Outer diameter of the spiral guide plate;

[0059] H is the axial distance between the exhaust port and the tank return port;

[0060] L is the axial distance between the oil return port and the upper exhaust port of the tank. Detailed Implementation

[0061] Below, refer to Figures 1 to 4 The oil separator 200 of this utility model will be described in detail, wherein, Figure 1 This is a perspective perspective view schematically showing the overall structure of the oil separator 200 of this utility model. Figure 2 This is a cross-sectional view schematically showing the internal structure and layout of the oil separator 200 of this utility model. Figures 3A to 3D These are schematic diagrams illustrating the positional relationship between the intake pipe 230 and the exhaust pipe 250 in the oil separator 200 of the embodiments and modifications of this utility model. Figure 2 A cross-sectional view along the AA direction. Figure 4 This is a schematic diagram illustrating the dimensional relationship between the spiral guide plate 240 and the tank 210 in the oil separator 200 of this utility model. Figure 2 A cross-sectional view along the BB direction.

[0062] In this utility model, such as Figure 1 , Figure 2 As shown, the oil separator 200 includes a tank 210, an oil return pipe 220, an air inlet pipe 230, a spiral guide plate 240, and an exhaust pipe 250.

[0063] One end of the tank body 210 (i.e., the bottom of the tank body) has a tank return port 211. One end of the return pipe 220 is inserted into the tank body 210 from one end of the tank body 210 through the tank return port 211 and connected to the tank body 210. The other end of the tank body 210 opposite to one end (i.e., the bottom of the tank body) (i.e., the top of the tank body) has an upper exhaust port 212. One end of the exhaust pipe 250 is inserted into the tank body 210 from the other end of the tank body 210 through the upper exhaust port 212 and extends into the tank body 210, and is connected to the tank body 210. In addition, an air inlet 213 is provided on the side wall of the tank body 210. One end of the air inlet pipe 230 is inserted into the side wall (side of the tank body) of the tank body 210 through the air inlet 213, passes through and extends into the tank body 210.

[0064] The spiral guide plate 240 is installed inside the tank body 210 and has a spiral starting end 240a and a spiral ending end 240b. Starting from the spiral starting end 240a, the spiral guide plate 240 spirals around the axis of the tank body 210 for 360°, which is called one layer of spiral blades. Therefore, the spiral guide plate 240 is composed of multiple layers. Figure 1 , Figure 2 The spiral blades 241 (shown as two layers) are formed by continuously spiraling around the axis of the tank body 210 towards the oil return port 211 of the tank body.

[0065] like Figure 1 , Figure 2 As shown, in the axial direction of the tank 210, the air intake port of the air intake pipe 230 extending into the tank 210 is located below the uppermost spiral blade 241 of the spiral guide plate 240.

[0066] exist Figure 1 , Figure 2 In the illustrated embodiment, the uppermost spiral blade 241 (first spiral blade 241a) of the spiral guide plate 240 spirally winds around the axis of the tank body 210 from 0° to 360°, starting from the spiral starting end 240a. The second spiral blade 241 (second spiral blade 241b) above the spiral guide plate 240 spirals around the axis of the tank body 210 a further 360°, starting from the first spiral blade 241a, that is, the portion spiraling around the axis of the tank body 210 from 360° to 720°, starting from the spiral starting end 240a. This pattern continues as the spiral guide plate 240 has more layers of spiral blades 241.

[0067] like Figure 2As shown more clearly, the blade surface 241c of the continuous multi-layer (two-layer) spiral blades 241 of the spiral guide plate 240 is inclined such that the portion of the blade surface closer to the axis of the tank 210 is higher and the portion closer to the outer circumference of the tank 210 is lower. Therefore, even if the flow rate of the oil-gas mixture flowing in through the intake pipe 230 is low (at a low flow rate), and the lubricating oil drips onto the spiral blades 241 and has difficulty dripping down along the spiral guide plate 240, the blade surface 241c of the spiral blades 241, which is inclined such that the portion of the blade surface closer to the axis of the tank 210 is higher and the portion closer to the outer circumference of the tank 210 is lower, can accelerate the sliding of the lubricating oil to the outer circumference, causing the lubricating oil to drip down along the inner wall of the tank 210, thereby improving the oil-gas separation efficiency.

[0068] When the angle between the blade surface 241c of the spiral blade 241 and the horizontal plane is set to α, ideally, the value of α satisfies the relationship 0°<α≤45°. Thus, on the one hand, it can prevent the oil-gas mixture flowing into the inlet pipe 230 from sliding excessively to the outer periphery when the flow velocity of the oil-gas mixture is high (at normal flow velocity), and on the other hand, it can accelerate the sliding of the lubricating oil to the outer periphery when the flow velocity of the oil-gas mixture flowing into the inlet pipe 230 is low (at low flow velocity), causing the lubricating oil to drip down along the inner wall of the tank 210, thereby ensuring that the oil separator always has a high oil-gas separation efficiency.

[0069] Furthermore, when the blade surface 241c of the helical blade 241 is inclined, it is more preferable that, as Figure 1 , Figure 2 As shown, the intake port of the intake pipe 230, which extends into the tank 210, is located between two layers of spiral blades 241, namely the first spiral blade 241a and the second spiral blade 241b, along the axial direction of the tank 210. It is positioned closer to the upper first spiral blade 241a, allowing the intake pipe 230 to extend further into the tank 210 without touching the lower second spiral blade 241b. Furthermore, the deeper the intake pipe 230 extends into the tank 210, the closer it gets to the exhaust pipe 250 or the inner wall of the tank 210. This makes it easier for the oil-gas mixture entering through the intake pipe 230 to collide with the outer wall of the exhaust pipe 250 or the inner wall of the tank 210, thereby improving oil-gas separation efficiency.

[0070] In addition, such as Figure 1 , Figure 2As shown, the air inlet of the intake pipe 230 extending into the tank 210 is entirely or at least partially located within the projection area of ​​the spiral guide plate 240, where the spiral blade 241 (i.e., the first spiral blade 241a) is projected downwards from one end of the intake pipe 230 in the axial direction (of the tank 210). Therefore, the oil-gas mixture entering from the intake pipe 230 is guided by the section of spiral blades (i.e., the first spiral blade 241a) located above the intake pipe 230, preventing it from entering the slow-flowing or stagnant area near the top wall of the tank 210 in the oil separator 200, thereby effectively improving the oil-gas separation efficiency of the oil separator 200. Furthermore, as... Figure 1 , Figure 2 As shown, the air inlet of the air inlet pipe 230 extending into the tank 210 is entirely or at least partially located in the projection area of ​​the spiral guide plate 240, which is located below one end of the air inlet pipe 230 in the axial direction (of the tank 210) of the spiral blade 241 (i.e., the second spiral blade 241b). This ensures that the oil-gas mixture entering from the air inlet pipe 230 is guided by the lower section of the spiral blade (i.e., the second spiral blade 241b), so that the oil-gas mixture can flow along the spiral of the spiral guide plate 240 after entering the tank 210, avoiding turbulence and ensuring oil-gas separation efficiency.

[0071] In addition, such as Figure 2 As shown, when the axial distance between the exhaust port of the exhaust pipe 250 inside the tank 210 and the oil return port 211 (within the tank 210) is H, and the axial distance between the oil return port 211 and the upper exhaust port 212 (within the tank 210) is L, L and H satisfy the relationship 1 / 4×L≤H≤2 / 3×L. If the exhaust port is too far from the oil return port 211, i.e., if H>2 / 3L, then either the axial stroke of the spiral guide plate 240 along the tank 210 will be too short, resulting in insufficient oil-gas separation, or the volume of the oil separator 200 will be unnecessarily large. On the other hand, if the exhaust port is too close to the oil return port 211, i.e., if H<1 / 4×L, then the port of the exhaust pipe 250 inside the tank 210 will be too close to the bottom oil surface, making it easy for oil droplets to be mistakenly carried back into the exhaust pipe 250 by the airflow, thus reducing the oil-gas separation efficiency.

[0072] In addition, Figure 1 , Figure 2In the illustrated embodiment, the spiral guide plate 240 spirals 720° (360° × 2, i.e., an integer number of spiral turns) from the spiral start end 240a to the spiral end 240b. However, the spiral guide plate 240 of this invention may not necessarily spiral around the axis of the tank 210 at an angle γ starting from the spiral start end. It may also not be an integer multiple of 360° (i.e., an integer number of spiral turns). For example, it may spiral around the axis of the tank 210 starting from the spiral start end 240a at an angle of 900° (i.e., 2.5 spiral turns), or it may spiral around the axis of the tank 210 starting from the spiral start end 240a at an angle of 1170° (i.e., 3.25 spiral turns). This invention does not impose any particular limitation on this.

[0073] In addition, such as Figure 2 As shown, the central axis of the intake pipe 230 extending into the tank 210 is perpendicular to the central axis of the exhaust pipe 250. In this case, it can be as follows: Figure 3A The perpendicular and intersecting lines shown can also be... Figure 3B The two planes shown are perpendicular to each other. For example... Figure 3A As shown, when the central axis 230ax of the intake pipe 230 and the central axis 250ax of the exhaust pipe 250 are perpendicular to each other and intersect, the intake port (flat opening) of the intake pipe 230 faces the outer wall of the exhaust pipe 250, making it easier for the oil-gas mixture entering from the intake pipe 230 to directly collide with the exhaust pipe 250, thus improving the oil-gas separation efficiency. Additionally, as... Figure 3B As shown, when the central axis 230ax of the intake pipe 230 and the central axis 250ax of the exhaust pipe 250 are perpendicular to each other, the orientation of the intake port can be set in a way that makes it easier for the oil-gas mixture entering through the intake pipe 230 to collide with the inner wall of the tank 210. In this case, it is conceivable to have a guide surface 231 (oblique opening) at one end of the intake pipe 230 that extends into the tank 210, and the guide surface 231 is inclined along the spiral direction of the spiral guide plate 240, so that the refrigerant can enter the guiding area of ​​the spiral guide plate 240 along the inclined direction of the guide surface 231. Preferably, the angle β between the guide surface 231 of the intake pipe 230 and the half-section 250b of the exhaust pipe 250, which passes through the central axis 250ax of the exhaust pipe 250 and is perpendicular to the central axis 230ax of the intake pipe 230, is 0° < β ≤ 60°. This allows the oil-gas mixture entering from the intake pipe 230 to more easily undergo centrifugal motion along the inner wall of the tank 210, ensuring efficient oil-gas separation. However, this invention is not limited to this; when the central axis 230ax of the intake pipe 230 and the central axis 250ax of the exhaust pipe 250 are perpendicular to each other and intersect, it can also be done as follows: Figure 3C As shown, the intake port of the intake pipe 230 is formed as Figure 3B Similarly, when the central axis 230ax of the intake pipe 230 and the central axis 250ax of the exhaust pipe 250 are perpendicular to each other, the angled opening can also be... Figure 3D As shown, one end of the air intake pipe 230 that extends into the tank 210 (the air intake port) is formed as Figure 3A Such a flat opening. In addition, compared to the flat opening of the air intake port of the air intake pipe 230, the angled opening of the air intake port of the air intake pipe 230 makes it easier to achieve the centrifugal effect of air intake.

[0074] In addition, such as Figure 4 As shown, along the radial direction of the tank 210, the outer diameter of the spiral guide plate 240 is d, and the inner diameter of the tank 210 is D, satisfying 0.5D≤d≤D. Thus, the larger the outer diameter of the spiral guide plate 240, the larger its size in the radial direction of the tank 210, which is beneficial for guiding the refrigerant and ensuring sufficient spiral motion of the oil-gas mixture for centrifugal separation. When the outer diameter d of the spiral guide plate 240 is equal to the inner diameter D of the tank 210, the outer wall of the spiral guide plate 240 abuts against the inner wall of the tank 210, at which point the size of the spiral guide plate 240 is at its maximum.

[0075] In addition, Figure 2 In the illustrated embodiment, the exhaust pipe 250 may further be provided with a baffle 260 at the exhaust port inside the tank 210. Since oil droplets flowing down the spiral blades 241 will appear on the outer wall of the exhaust port inside the tank 210, the baffle can prevent these oil droplets from being mistakenly carried back to the exhaust pipe 250 by the airflow. The baffle can be formed, for example, as a truncated hollow cone, with the small-diameter end of its truncated portion connected to the exhaust port of the exhaust pipe 250. However, the shape of the baffle is not limited to this. It can be any other suitable shape as long as it helps to prevent the oil droplets flowing down the outer wall of the exhaust port from being mistakenly carried back to the exhaust pipe 250 by the airflow.

[0076] Furthermore, this utility model also includes... Figure 5 As shown, a heat pump system 1 is provided, including the oil separator 200 as described above. The oil separator 200 is located downstream of the compressor 100, more specifically at the outlet end of the compressor 100. The oil separator 200 is used to separate the lubricating oil from the refrigerant in an oil-gas mixture state that is discharged from the compressor 100 and enters the tank 210 through the intake pipe 230. The separated lubricating oil is returned to the compressor 100 through the oil return pipe 220, and the separated gaseous refrigerant is sent to the downstream outdoor heat exchanger (also known as the "outdoor heat exchanger") through the exhaust pipe 250, thereby realizing the circulation of refrigerant in the heat pump system 1.

[0077] Compared to existing technologies, this invention, by setting a spiral guide plate 240, allows the refrigerant to flow along the spiral direction of the spiral guide plate 240 after entering the tank 210, thus improving the oil-gas separation effect. In particular, by positioning the air inlet port of the air inlet pipe 230 extending into the tank 210 below the uppermost spiral blade 241 of the spiral guide plate 240 in the axial direction of the tank 210, the area between the air inlet pipe 230 and the top wall of the tank 210 is greatly reduced to a region with slow or no flow. This allows the oil-gas mixture entering from the air inlet pipe 230 to be guided by both the upper and lower spiral blades 241, and to perform centrifugal rotation along the spiral channel formed by the spiral blades 241, thereby improving the oil-gas separation efficiency.

[0078] Other advantages and modifications will readily occur to those skilled in the art. Therefore, in its broader sense, this invention is not limited to the specific details and representative embodiments shown and described herein. Thus, modifications can be made without departing from the spirit or scope of the overall inventive concept as defined by the appended claims and their equivalents.

[0079] For example, in this utility model, such as Figure 2 As shown, the example illustrates how one end of the return oil pipe 220 is inserted into the tank 210 through the tank return oil port 211 and connected to the tank 210. However, this utility model is not limited to this. As long as one end of the return oil pipe 220 is connected to the tank 210, it is acceptable. Alternatively, one end of the return oil pipe 220 can be sleeved on the outside of the tank return oil port 211, or one end of the return oil pipe 220 can be connected to the tank return oil port 211 by welding, riveting, or any other suitable method.

Claims

1. An oil separator, comprising a tank, an oil return pipe, an air inlet pipe, a spiral guide plate, and an exhaust pipe. One end of the return oil pipe is connected to the tank body from one end via the tank body's return oil port. One end of the exhaust pipe is inserted into the tank body from the opposite end of the tank body via the upper exhaust port and extends into the tank body. One end of the air intake pipe is inserted into the tank body through the air intake port from the side wall of the tank body and extends into the tank body. The spiral guide plate is installed inside the tank and is formed by multiple layers of spiral blades extending continuously spirally around the axis of the tank towards the oil return port of the tank. Its features are, In the axial direction of the tank, the air inlet port of the air inlet pipe extending into the tank is located below the uppermost spiral blade of the spiral guide plate.

2. The oil separator as described in claim 1, characterized in that, The blade surface of the spiral guide plate is inclined such that the portion of the blade surface closer to the axis of the tank is higher and the portion closer to the outer periphery of the tank is lower.

3. The oil separator as described in claim 2, characterized in that, When the angle between the blade surface of the helical blade and the horizontal plane is set as α, the value of α satisfies the relationship 0°<α≤45°.

4. The oil separator as described in claim 2, characterized in that, The air intake port of the air intake pipe, which extends into the tank, is located between two layers of spiral blades in the axial direction of the tank, and is positioned closer to the upper spiral blade.

5. The oil separator as described in any one of claims 1 to 4, characterized in that, The air intake port of the air intake pipe extending into the tank is entirely or at least partially located within the projection area of ​​the spiral guide plate, which is located above one end of the air intake pipe in the axial direction of the tank.

6. The oil separator according to any one of claims 1 to 4, characterized in that, The air intake port of the air intake pipe extending into the tank is entirely or at least partially located within the projection area of ​​the spiral guide plate, which is located below one end of the air intake pipe in the axial direction of the tank.

7. The oil separator according to any one of claims 1 to 4, characterized in that, Along the radial direction of the tank, the outer diameter of the spiral guide plate is d, and the inner diameter of the tank is D, satisfying 0.5D≤d≤D.

8. The oil separator as described in any one of claims 1 to 4, characterized in that, The central axis of the intake pipe extending into the tank body is perpendicular to and intersects with the central axis of the exhaust pipe, or they are perpendicular to each other in opposite planes.

9. The oil separator as described in claim 8, characterized in that, The air intake port of the air intake pipe is directly opposite the outer wall of the exhaust pipe.

10. The oil separator as described in claim 8, characterized in that, The end of the air intake pipe that extends into the tank has a guide surface, and the guide surface is inclined along the rotation direction of the spiral guide plate.

11. The oil separator as claimed in claim 10, characterized in that, The angle β between the guide surface of the intake pipe and the half-section of the exhaust pipe that passes through the central axis of the exhaust pipe and is perpendicular to the central axis of the intake pipe is 0°<β≤60°.

12. The oil separator according to any one of claims 1 to 4, characterized in that, The axial distance between the exhaust port of the exhaust pipe inside the tank and the oil return port of the tank is H, and the axial distance between the oil return port of the tank and the upper exhaust port is L. The two satisfy the relationship 1 / 4×L≤H≤2 / 3×L.

13. The oil separator according to any one of claims 1 to 4, characterized in that, The exhaust pipe is further equipped with a baffle at the exhaust port inside the tank.

14. A heat pump system, characterized in that, The oil separator includes any one of claims 1 to 13.

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