Oil separator and air conditioning system

Abstract

The utility model provides an oil separator and an air conditioning system, and relates to the technical field of air conditioners. The oil separator comprises a filtering structure, and the filtering structure is located between the air inlet pipe and the air outlet pipe in the axial direction of the barrel; the filter structure comprises a filter screen and at least two filter plates, the two filter plates are arranged at intervals in the axial direction of the barrel body, a mounting cavity is defined between any two adjacent filter plates and the inner barrel wall of the barrel body or between any two adjacent filter plates, and the mounting cavity is filled with the filter screen; a plurality of filtering holes which are distributed at intervals are formed in each filtering plate, and the filtering holes are formed in the thickness direction of the filtering plate in a penetrating manner. In the process that a refrigerant flows from the gas inlet pipe to the gas outlet pipe, the refrigerant needs to pass through the filtering structure, a filtering plate in the filtering structure is connected with the inner cylinder wall of the cylinder body to achieve fixed installation, the filtering plate and a filtering net can filter refrigerant gas so as to promote further separation of the refrigerant gas and oil drops, and the oil-gas separation effect is improved; refrigeration oil is promoted to flow out from the oil return opening.

Description

Technical Field

[0001] The present application relates to the technical field of air conditioning, and in particular to an oil separator and an air conditioning system. Background Art

[0002] The oil discharge rate of the variable frequency compressor is relatively high when it is running at high frequency. In order to prevent the compressor from being worn due to lack of oil and to prevent a large amount of refrigerant oil from entering the heat exchanger and affecting the heat exchange effect, an oil separator is generally installed on the compressor exhaust pipe to separate the refrigerant oil from the gaseous refrigerant through centrifugal motion and return the refrigerant oil to the compressor. However, the existing oil separator has a poor effect in separating oil, resulting in low oil return efficiency. Utility Model Content

[0003] Based on this, it is necessary to provide an oil separator to improve the separation effect and promote oil return.

[0004] 8. The diaphragm of claim 7, wherein the filter element has a plurality of diaphragm holes, each of which has a plurality of diaphragm holes disposed on the filter element. The plurality of diaphragm holes have respective openings, each of which has a plurality of diaphragm holes disposed on the filter element.

[0005] It is understandable that the air inlet pipe can input the refrigerant gas into the cylinder, and the refrigerant gas performs centrifugal motion in the cylinder to separate from the oil droplets. In the process of the refrigerant flowing from the air inlet pipe to the air outlet pipe, it needs to pass through the filtering structure. The filter plate in the filtering structure is connected to the cylinder wall in the cylinder to achieve fixed installation. The filter plate and the filter net can filter the refrigerant gas respectively to promote the further separation of the refrigerant gas and the oil droplets, improve the oil-gas separation effect, and promote the refrigerant oil to flow out from the oil return port.

[0006] In one of the embodiments, along the axial direction of the cylinder, the filter holes of any two adjacent filter plates are staggered.

[0007] It is understandable that, with such an arrangement, two adjacent filter plates have different blocking effects on the refrigerant, the refrigerant gas can bypass the blocking surface and pass through the filter holes, and the oil droplets of the refrigerant oil can be blocked by the filter plate, thereby enhancing the filtering effect.

[0008] In one embodiment, the filter screen is woven from a plurality of stainless steel wires, and the diameter of each of the stainless steel wires is no greater than 3 mm.

[0009] It can be understood that by limiting the diameter of the stainless steel wire to be smaller, the obstruction to the refrigerant gas is reduced, thereby promoting the circulation of the refrigerant gas.

[0010] In one embodiment, the air inlet pipe includes a straight section and a bent section, the straight section is connected to the bent section, the straight section is passed through the air inlet, the bent section is arranged at an angle to the straight section, the bent section is located in the cylinder, and within the cylinder, the pipe opening of the bent section is located facing the inner cylinder wall of the cylinder.

[0011] It can be understood that the bending section is arranged so that the refrigerant gas can collide with the inner wall of the cylinder immediately after flowing out from the air inlet pipe, thereby promoting the centrifugal movement.

[0012] In one of the embodiments, in the cylinder, the pipe opening of the bending section is arranged to be inclined relative to the radial direction of the bending section.

[0013] It can be understood that the inclined pipe opening has a larger cross-sectional area so that more refrigerant gas can flow into the cylinder per unit time.

[0014] The present application also provides an air conditioning system, which includes the above-mentioned oil separator and a compressor, wherein the outlet of the compressor is connected to the intake pipe of the oil separator, and the oil return port of the compressor is connected to the oil return pipe of the oil separator.

[0015] It can be understood that by using the above-mentioned oil separator, the refrigerant gas after centrifugation can be filtered again in multiple layers, which has a good filtering effect, promotes the separation of oil droplets in the refrigerant gas, improves the oil return efficiency, and makes the compressor run smoothly.

[0016] In one of the embodiments, when the horsepower of the compressor is P=P1, the height of the cylinder takes the value h, and the inner diameter of the cylinder takes the value d; for every increase or decrease in the horsepower of the compressor by △P, the height of the cylinder increases or decreases by 8% h△P, and the inner diameter of the cylinder increases or decreases by 8% d△P, wherein △P is an integer.

[0017] It can be understood that the inner diameter and height of the cylinder are adaptively adjusted according to the horsepower of the compressor, so that the refrigerant gas output by compressors of different horsepower can perform effective centrifugal motion in the cylinder.

[0018] In one embodiment, the horsepower P of the compressor is between 5 and 30; and / or the pore size of the filter plate is between 2 mm and 4 mm.

[0019] It is understood that the compressor horsepower range is limited to show the applicable range of the oil separator. At the same time, by limiting the pore size of the filter plate, the filtering effect of oil droplets is ensured and the refrigerant gas can flow smoothly.

[0020] In one embodiment, when the horse number P of the compressor is in the range of 5≤P<10, the aperture of the filter hole is 2mm; when the horse number P of the compressor is in the range of 10≤P<25, the aperture of the filter hole is 3mm; when the horse number P of the compressor is ≥25, the aperture of the filter hole is 4mm.

[0021] It is understandable that the diameter of the filter holes is selected according to the compressor rating to meet the requirements of filtering oil droplets and circulating refrigerant gas.

[0022] In one of the embodiments, when the horsepower of the compressor is P=P2, the thickness of the filter along the axial direction of the cylinder takes a value of t, and when the horsepower of the compressor increases or decreases by △P, the thickness of the filter along the axial direction of the cylinder increases or decreases by 2△P accordingly, wherein △P is an integer.

[0023] It is understandable that the thickness of the filter mesh is selected appropriately according to the rating of the compressor to meet the requirements of filtering oil droplets and circulating refrigerant gas. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the conventional technology, the drawings required for use in the embodiments or the conventional technology descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0025] Figure 1 A longitudinal cross-sectional view of the oil separator provided for this application;

[0026] Figure 2 A transverse cross-sectional view of the oil separator provided for this application;

[0027] Figure 3 A perspective view of the oil separator provided for this application;

[0028] Figure 4 This is a schematic diagram of the structure of the filter plate in the oil separator provided in this application.

[0029] Figure numerals: 100, oil separator; 10, cylinder; 101, air outlet; 102, air inlet; 103, oil return port; 104, installation cavity; 20, filter structure; 21, filter plate; 211, filter hole; 22, filter net; 30, air inlet pipe; 31, straight section; 32, bent section; 40, air outlet pipe; 50, oil return pipe. DETAILED DESCRIPTION

[0030] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0031] It should be noted that when a component is referred to as being "fixed to" or "disposed on" another component, it may be directly on the other component or there may also be a central component. When a component is considered to be "connected to" another component, it may be directly connected to the other component or there may be a central component at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in the specification of this application are for illustrative purposes only and do not represent the only implementation method.

[0032] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0033] In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may mean that the first feature is directly in contact with the second feature, or the first feature and the second feature are indirectly in contact through an intermediate medium. Moreover, a first feature being “above”, “above” or “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being “below”, “below” or “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0034] Unless otherwise defined, all technical and scientific terms used in the specification of this application have the same meaning as those commonly understood by those skilled in the art to which this application belongs. The terms used in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and / or" used in the specification of this application includes any and all combinations of one or more related listed items.

[0035] See also Figures 1 to 4 The present application provides an oil separator 100, which includes a cylinder 10, an air outlet pipe 40, an air inlet pipe 30 and a filtering structure 20; the cylinder 10 is provided with an air outlet 101, an air inlet 102 and an oil return port 103 arranged at intervals along its axial direction, and the air inlet 102 is located between the air outlet 101 and the oil return port 103; the air inlet 102 is connected to the air inlet pipe 30, and the pipe opening at one end of the air inlet pipe 30 is located in the inner cavity of the cylinder 10 and is eccentrically arranged close to the inner cylinder wall of the cylinder 10, and the air outlet 101 is connected to the air outlet pipe 40; along the cylinder 10 axially, the filter structure 20 is located between the air inlet pipe 30 and the air outlet pipe 40; the filter structure 20 includes a filter screen 22 and at least two filter plates 21, the two filter plates 21 are arranged at intervals along the axial direction of the cylinder 10, and an installation cavity 104 is formed between any two adjacent filter plates 21 and the inner cylinder wall of the cylinder 10 or between any two adjacent filter plates 21, and the installation cavity 104 is filled with the filter screen 22; each filter plate 21 is constructed with a plurality of filter holes 211 arranged at intervals, and the filter holes 211 are arranged through the filter plate 21 in the thickness direction.

[0036] In this way, the high-temperature and high-pressure refrigerant gas output by the compressor is input into the cylinder 10 of the oil separator 100 from the air inlet pipe 30, and the refrigerant gas entrains the oil droplets of the refrigeration oil. In the cylinder 10, the refrigerant gas can collide with the inner wall of the cylinder 10 to perform centrifugal motion, thereby separating the oil droplets of the refrigeration oil from the refrigerant gas. The refrigerant gas after centrifugation flows upward, and the oil droplets after centrifugation adhere to the inner cylinder wall and gradually converge to the oil return port 103 under the action of gravity. In a specific embodiment, the oil separator 100 also includes an oil return pipe 50, which is installed at the oil return port 103 to transport the separated refrigeration oil back to the compressor.

[0037] Furthermore, the refrigerant gas can be separated from the oil droplets for a second time after being filtered by the filter structure 20. Specifically, the filter plate 21 can have a certain blocking effect on the refrigerant gas. The refrigerant gas collides with the surface of the filter plate 21, and some oil droplets can be blocked. The refrigerant gas needs to bypass the surface blocked by the filter plate 21 and flow out from the filter hole 211 of the filter plate 21. The flow direction and flow rate of the refrigerant gas change, and the refrigerant gas is disturbed, thereby separating the heavier oil droplets from the refrigerant gas. In addition, the filter net 22 can also filter, further promoting the separation of oil droplets from the refrigerant gas. The filter net 22 cooperates with the filter plate 21 to form a multi-layer filtering effect, thereby improving the oil return efficiency.

[0038] In some embodiments, along the axial direction of the cylinder 10, the filter holes 211 of any two adjacent filter plates 21 are aligned one by one, and each filter plate 21 has a similar disturbance effect on the refrigerant gas, so that the refrigerant gas can be disturbed again after each passing through the filter screen 22 in the installation cavity 104, so as to improve the oil-gas separation effect and promote the smooth circulation of the refrigerant gas. Only one filter plate 21 needs to be processed, which is beneficial to improving production efficiency.

[0039] In a further embodiment, along the axial direction of the cylinder 10, the filter holes 211 of any two adjacent filter plates 21 are arranged in a staggered manner. In this way, the positions of the two adjacent filter plates 21 blocking the refrigerant gas are different, and have different blocking effects. Specifically, the refrigerant gas first collides with the filter plate 21 close to the air inlet 102, which can block some oil droplets. The refrigerant gas passes through the filter holes 211 of the filter plate 21. Then, the refrigerant gas is filtered by the filter screen 22 and collides with the surface of another filter plate 21. The other filter plate 21 can block the residual oil droplets again, thereby improving the oil-gas separation effect.

[0040] like Figure 2 As shown, in some embodiments, the air inlet pipe 30 includes a straight section 31 and a bent section 32, the straight section 31 is connected to the bent section 32, the straight section 31 is arranged through the air inlet 102, the bent section 32 is arranged at an angle to the straight section 31, the bent section 32 is located inside the cylinder 10, and inside the cylinder 10, the pipe mouth of the bent section 32 is located facing the inner cylinder wall of the cylinder 10, so that the output refrigerant gas can directly collide with the inner cylinder wall to obtain kinetic energy, so that the flow rate and flow direction of the refrigerant are changed, and the refrigerant gas is promoted to throw out the oil droplets during the flow.

[0041] like Figure 2As shown, in a further embodiment, inside the cylinder 10, the pipe mouth of the bending section 32 is inclined relative to the radial direction of the bending section 32, and the cross-section of the pipe mouth of the air inlet pipe 30 is larger, so that more refrigerant gas flows into the cylinder 10 in the air inlet pipe 30 per unit time, thereby increasing the intensity of the collision between the refrigerant gas and the cylinder 10 and promoting the centrifugal effect of the refrigerant gas in the cylinder 10.

[0042] The present application also provides an air conditioning system, which includes the above-mentioned oil separator 100 and a compressor, wherein the inlet of the compressor is connected to the air inlet pipe 30 of the oil separator 100, and the oil return port 103 of the compressor is connected to the oil return pipe 50 of the oil separator 100. In this way, the separation effect of the oil droplets and the refrigerant gas of the oil separator 100 is improved, the oil return efficiency is improved, and the obstruction of the refrigeration oil to the heat exchange of the refrigerant is reduced, so as to improve the heat exchange efficiency of the refrigerant in the air conditioning system and promote the stable operation of the compressor.

[0043] In an optional embodiment, when the horse number of the compressor P=P1, the height of the cylinder 10 takes the value h, and the inner diameter of the cylinder 10 takes the value d. At this time, the refrigerant gas can achieve the best separation effect by centrifugal motion in the cylinder 10. Therefore, on this basis, for every increase or decrease of the horse number of the compressor △P, the height of the cylinder 10 increases or decreases by 8%h△P, and the inner diameter of the cylinder 10 increases or decreases by 8%d△P, where △P is an integer. In this way, the height and inner diameter of the cylinder 10 are adjusted according to the horse number of the compressor to ensure that a better separation effect can be achieved when using compressors with different horse numbers. The larger the horse number of the compressor, the more the flow rate of the refrigerant output is, and the greater the demand for the separation effect is. Among them, the height of the cylinder 10 affects the time of centrifugal motion. The higher the height of the cylinder 10, the longer the time of centrifugal motion. Of course, the height of the cylinder 10 cannot be too large to meet the simplicity of assembly and the restriction on the size of the space occupied by the cylinder 10. Furthermore, on the basis of a certain height of the cylinder 10, the inner diameter of the cylinder 10 can affect the size of the space in the cylinder 10. The refrigerant gas output from the air inlet pipe 30 enters the cylinder 10 with a larger space, which can reduce the flow rate of the refrigerant gas. Since the mass of the oil droplets is large, they can be separated from the refrigerant gas during the change of the refrigerant gas flow rate.

[0044] In a specific embodiment, the P of the compressor is between 5 and 30 horsepower, and illustratively, P=5, 20 or 30.

[0045] In a further specific embodiment, when the horsepower of the compressor is P=12, the height of the cylinder 10 is 250mm, and the inner diameter of the cylinder 10 is 101.6mm. Therefore, on this basis, △P=1, for every increase of the horsepower of the compressor, the height of the cylinder 10 increases by 20mm, and the inner diameter of the cylinder 10 increases by 8.128mm; for every decrease of the horsepower of the compressor, the height of the cylinder 10 decreases by 20mm, and the inner diameter of the cylinder 10 decreases by 8.128mm. For example, when P=11, the height of the cylinder 10 is 230mm, and the inner diameter of the cylinder 10 is 93.472mm; when P=13, the height of the cylinder 10 is 270mm, and the inner diameter of the cylinder 10 is 109.728mm.

[0046] In an optional embodiment, the pore size of the filter plate 21 is between 2 mm and 4 mm. If the pore size of the filter hole 211 is large, the filtering effect of the filter plate 21 is poor. If the pore size of the filter plate 21 is small, it may cause difficulty in the circulation of the refrigerant gas. Therefore, by limiting the pore size of the filter plate 21, the filtering effect of oil droplets and the smooth circulation of the refrigerant gas are ensured. Exemplarily, the pore size of the filter plate 21 is 2 mm, 3 mm or 4 mm.

[0047] In a further embodiment, when the compressor horse number P is in the range of 5≤P<10, the aperture of the filter hole 211 is 2mm; when the compressor horse number P is in the range of 10≤P<25, the aperture of the filter hole 211 is 3mm; when the compressor horse number P≥25, the aperture of the filter hole 211 is 4mm. In this way, since the larger the compressor horse number is, the more the flow rate of the refrigerant gas is, the corresponding aperture of the filter hole 211 is also increased, so as to meet the circulation requirements of refrigerant gas with different flow rates.

[0048] In a further embodiment, when the compressor horse number P=P2, the thickness of the filter 22 along the axial direction of the cylinder 10 takes the value t, and the thickness of the filter 22 along the axial direction of the cylinder 10 increases or decreases by 2△P for each increase or decrease in the compressor horse number △P, where △P is an integer. In this way, since the larger the compressor horse number, the greater the flow rate of the refrigerant gas, the thickness of the filter 22 is also increased accordingly to ensure the filtering effect of refrigerant gas with different flow rates. When the compressor horse number is small, the thickness of the filter 22 is also small, which is conducive to saving costs and promoting the circulation of refrigerant gas.

[0049] In a specific embodiment, when the horsepower of the compressor is P=12, the thickness of the filter screen 22 along the axial direction of the cylinder 10 is 20 mm, and ΔP=1. For every increase in the horsepower of the compressor, the thickness of the filter screen 22 along the axial direction of the cylinder 10 increases by 2 mm, and for every decrease in the horsepower of the compressor, the thickness of the filter screen 22 along the axial direction of the cylinder 10 decreases by 2 mm. For example, when P=11, the thickness of the filter screen 22 is 18 mm; when P=13, the thickness of the filter screen 22 is 22 mm.

[0050] In a specific embodiment, the filter screen 22 is woven from a plurality of stainless steel wires, each of which has a diameter of no more than 3 mm, so as to form relatively fine holes, promote the filtering effect, and at the same time, avoid the stainless steel wires from causing a large obstruction to the refrigerant gas, thereby promoting the circulation of the refrigerant gas. For example, the diameter of the stainless steel wire is 1 mm, 2 mm or 3 mm.

[0051] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0052] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the scope of patent protection of the present application shall be subject to the attached claims.

Claims

1. An oil separator, comprising a cylinder, an air inlet pipe, an air outlet pipe and an oil return pipe, wherein the cylinder is provided with an air outlet, an air inlet and an oil return port arranged at intervals along its axial direction, wherein the air inlet is located between the air outlet and the oil return port; the air inlet is connected with the air inlet pipe, the pipe opening at one end of the air inlet pipe is located in the inner cavity of the cylinder and is eccentrically arranged close to the inner cylinder wall of the cylinder, the air outlet is connected with the air outlet pipe, and the oil return port is connected with the oil return pipe, characterized in that: The oil separator also includes: A filter structure (20), along the axial direction of the cylinder (10), the filter structure (20) is located between the air inlet pipe (30) and the air outlet pipe (40); the filter structure (20) comprises a filter screen (22) and at least two filter plates (21), the two filter plates (21) are arranged at intervals along the axial direction of the cylinder (10), an installation cavity (104) is formed between any two adjacent filter plates (21) and the inner cylinder wall of the cylinder (10) or between any two adjacent filter plates (21), and the installation cavity (104) is filled with the filter screen (22); each filter plate (21) is constructed with a plurality of filter holes (211) arranged at intervals, and the filter holes (211) are arranged to penetrate along the thickness direction of the filter plate (21).

2. The oil separator according to claim 1, characterized in that: Along the axial direction of the cylinder (10), the filter holes (211) of any two adjacent filter plates (21) are arranged in a staggered manner.

3. The oil separator according to claim 1, characterized in that: The filter screen (22) is woven from a plurality of stainless steel wires, and the diameter of each of the stainless steel wires is no greater than 3 mm.

4. The oil separator according to any one of claims 1 to 3, characterized in that: The air inlet pipe (30) comprises a straight section (31) and a bent section (32); the straight section (31) is connected to the bent section (32); the straight section (31) is arranged through the air inlet (102); the bent section (32) is arranged at an angle to the straight section (31); the bent section (32) is located inside the cylinder (10); inside the cylinder (10), the pipe opening of the bent section (32) is located facing the inner cylinder wall of the cylinder (10).

5. The oil separator according to claim 4, characterized in that: In the cylinder (10), the pipe opening of the bending section (32) is arranged to be inclined relative to the radial direction of the bending section (32).

6. An air conditioning system, characterized in that: include: The oil separator according to any one of claims 1 to 5; A compressor, wherein the outlet of the compressor is communicated with the air inlet pipe (30) of the oil separator, and the oil return port of the compressor is communicated with the oil return pipe (50) of the oil separator.

7. The air conditioning system according to claim 6, characterized in that: When the horsepower of the compressor is P=P1, the height of the cylinder (10) takes the value h, and the inner diameter of the cylinder (10) takes the value d; Every time the horsepower of the compressor increases or decreases by ΔP, the height of the cylinder (10) correspondingly increases or decreases by 8% hΔP, and the inner diameter of the cylinder (10) correspondingly increases or decreases by 8% dΔP, wherein ΔP is an integer.

8. The air conditioning system according to claim 6, characterized in that: The horsepower P of the compressor is between 5 and 30; and / or the pore size of the filter plate (21) is between 2 mm and 4 mm.

9. The air conditioning system according to claim 8, characterized in that: When the horsepower P of the compressor is in the range of 5≤P<10, the diameter of the filter hole (211) is 2 mm; when the horsepower P of the compressor is in the range of 10≤P<25, the diameter of the filter hole (211) is 3 mm; when the horsepower P of the compressor is ≥25, the diameter of the filter hole (211) is 4 mm.

10. The air conditioning system according to claim 6, characterized in that: When the horsepower of the compressor is P=P2, the thickness of the filter (22) along the axial direction of the cylinder (10) takes a value of t, and when the horsepower of the compressor increases or decreases by a horsepower value △P, the thickness of the filter (22) along the axial direction of the cylinder (10) correspondingly increases or decreases by 2△P, where △P is an integer.

Images