Ring for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a ring for a compressor and the compressor, the ring comprises a first end face and a second end face which are oppositely arranged, a first inner chamfer is formed on the first end face, a second inner chamfer is formed on the second end face, the first inner chamfer comprises a first inclined plane, and the second inner chamfer comprises a second inclined plane. The first end face is provided with a first inclined face, the edge, intersecting with the first end face, of the first inclined face is a first curved edge, the edge, intersecting with the inner circumferential face of the ring, of the first inclined face is a second curved edge, the first curved edge and the second curved edge are both closed curves, and in different radial directions, the radial distances between the first curved edge and the second curved edge are not equal. The utility model has the following technical effects: not only can the oil lubrication be satisfied and the reliability be ensured, but also the performance influence caused by leakage can be reduced as much as possible.

Description

Technical Field

[0001] The utility model belongs to the technical field of compressors, and particularly relates to a ring for a compressor and a compressor. Background Art

[0002] Usually, a compressor is composed of components such as a pump assembly, a motor assembly, a casing assembly, and a filter bottle. The pump assembly at least includes an upper support, a cylinder body, a lower support, a ring, a shaft, blades and other components to form a compression chamber, which is used to realize the cycle process of sucking in low-temperature and low-pressure refrigerant, compressing it into high-temperature and high-pressure refrigerant, and then discharging it.

[0003] When the various components of the pump assembly are operating, the outer periphery of the ring and the inner periphery of the cylinder are divided into a compression chamber and an exhaust chamber by blades. The upper and lower end faces of the ring contact the end faces of the upper and lower supports to form a sealed chamber. The ring rotates eccentrically with the crankshaft, and the end faces of the ring rub against the end faces of the upper and lower supports. The inner chamfer of the ring can be used to store oil. During the movement of the ring, the stored oil lubricates the upper and lower end faces of the ring to prevent abnormal wear on the end faces of the upper and lower supports. Generally, the larger the inner chamfer, the better the lubrication effect.

[0004] In winter low-temperature heating heat pumps, a compressor with an air-supply and enthalpy-increasing structure is used. One of the structures is to supply air into the cylinder compression chamber through a middle partition or support, and to seal the air-supply hole through the end face of the ring.

[0005] In order to achieve better air supply effect, the size and position of the air supply hole generally need to be specifically designed. However, in the existing technology, there are two types of rings used in the industry, such as Figure 1 and Figure 2 As shown, one is that the inner chamfers of the two end faces of the ring are of the same size and uniform, giving priority to ensuring the sealing effect and achieving energy efficiency requirements, but the lubricity of the oil is insufficient, and the risk of long-term reliability problems is high; Figure 3 and Figure 4 As shown, one is that the inner chamfers of the two end faces of the ring are inconsistent in size, but both are uniform. The end face close to the air supply hole uses a smaller inner chamfer, and the other end face uses a larger inner chamfer, ensuring that the performance is not affected. However, it cannot completely avoid reliability problems caused by insufficient oil supply due to the small chamfer. Utility Model Content

[0006] In order to address the deficiencies of the prior art, the present invention provides a ring for a compressor and a compressor, which achieves the purpose of satisfying the lubricity of oil, ensuring reliability, and minimizing the performance impact caused by leakage.

[0007] The technical objectives to be achieved by this utility model are achieved through the following technical solutions:

[0008] The present utility model provides a ring for a compressor. The ring includes a first end face and a second end face which are oppositely arranged;

[0009] A first inner chamfer is formed on the first end face, and a second inner chamfer is formed on the second end face;

[0010] The first inner chamfer includes a first inclined surface. The edge where the first inclined surface intersects with the first end face is a first curved edge, and the edge where the first inclined surface intersects with the inner peripheral surface of the ring is a second curved edge. Both the first curved edge and the second curved edge are closed curves;

[0011] In different radial directions, the radial distance between the first curved edge and the second curved edge is not equal.

[0012] In some implementation manners, in the same radial direction, the radial distance between the first curved edge and the second curved edge located on the opposite sides of the axis of the ring is not equal, so that the local part of the first inner chamfer is enlarged to meet oil lubrication and ensure reliability.

[0013] In some implementation manners, the projections of the first curved edge and the second curved edge on the first end face form a non-circular ring shape, so that the first inner chamfer is a non-uniform chamfer with a variable size design.

[0014] In some implementation manners, the projection of the first curved edge on the first end face forms an ellipse, and the projection of the second curved edge on the first end face forms a circle.

[0015] In some implementation manners, the projections of the first curved edge and the second curved edge on the first end face form a circular ring shape, so that the first inner chamfer is a non-uniform chamfer with a variable size design.

[0016] In some implementation manners, the second inner chamfer includes a second inclined surface, and the projection of the second inclined surface on the second end face forms a circular ring shape or a non-circular ring shape.

[0017] This application also provides a compressor, including a cylinder block, a crankshaft, a support and the ring according to any one of the above;

[0018] The crankshaft passes through the cylinder block and the support. The ring is located between the crankshaft and the cylinder block, and the first end face of the ring is connected to the support. An air supplement hole is provided on the support.

[0019] In some implementation manners, the air supplement hole is a circular hole. The leakage length in the radial direction between the first inner chamfer and the air supplement hole is L, and L = r + e + d / 2 + Ci - S;

[0020] Wherein, r is the radius of the air supply hole, e is the eccentricity of the crankshaft, d is the inner diameter of the ring, Ci is the radial distance between the first curved edge and the second curved edge when the center of the ring is closest to the center of the air supply hole, and S is the distance between the center of the air supply hole and the center of the cylinder body.

[0021] In some implementations, 0≤L≤3 mm.

[0022] In some implementations, assuming that the displacement of the cylinder is V, 1000*L / V≤120 mm / cc.

[0023] In summary, the present invention has at least the following advantages:

[0024] 1. The utility model provides a ring for a compressor, in which a first inner chamfer is formed on a first end face of the ring, and the first inner chamfer is a non-uniform chamfer with a variable size, so as to allow the first inner chamfer of the ring to be connected with the air supply hole, thereby achieving oil lubrication and ensuring reliability while minimizing the performance impact caused by leakage.

[0025] 2. The utility model provides a compressor that can ensure the performance and operational reliability of the compressor after applying a first inner chamfer with a non-uniform chamfer whose size varies. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 and Figure 2 It is a structural schematic diagram of two end faces of a ring in the background technology;

[0027] Figure 3 and Figure 4 It is a schematic structural diagram of two end faces of another type of ring in the background art;

[0028] Figure 5 This is a schematic structural diagram of the ring provided in Example 1 of the present utility model;

[0029] Figure 6 This is a schematic projection diagram of the ring provided in Example 1 of the present utility model;

[0030] Figure 7 This is a cross-sectional view of the ring provided in Example 1 of the present utility model;

[0031] Figure 8 This is a schematic structural diagram of the ring provided in Example 2 of the present utility model;

[0032] Figure 9 This is a schematic projection diagram of the ring provided in Example 2 of the present utility model;

[0033] Figure 10This is a cross-sectional view of the ring provided in Embodiment 2 of the present utility model;

[0034] Figure 11 This is a schematic structural diagram of the compressor provided in Embodiment 3 of the present utility model;

[0035] Figure 12 This is a top view of the compressor provided in Embodiment 3 of the present utility model;

[0036] Figure 13 This is a cross-sectional view of the ring provided in Embodiment 3 of the present utility model;

[0037] 100, ring; 110, first end face; 111, first inner chamfer; 111a, first inclined surface; 111b, first curved edge; 111c, second curved edge; 120, second end face; 121, second inner chamfer; 121a, second inclined surface;

[0038] 200, cylinder block;

[0039] 300, crankshaft;

[0040] 400, support; 410, air supply hole. Detailed implementation manners

[0041] To make the purposes, technical solutions and advantages of the embodiments of the present utility model clearer, the technical solutions in the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present utility model. The described embodiments are some, but not all, of the embodiments of the present utility model.

[0042] Therefore, the following detailed description of the embodiments of the present utility model provided in the drawings is not intended to limit the scope of the claimed present utility model, but merely represents selected embodiments of the present utility model. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts fall within the scope of protection of the present utility model.

[0043] Embodiment 1:

[0044] Please refer to Figures 5 - 7 , a ring for a compressor, the ring 100 includes a first end face 110 and a second end face 120 which are oppositely arranged.

[0045] Combined with the understanding of the background art, it is known that the outer circumference of the ring and the inner circumference of the cylinder block are separated into a compression chamber and an exhaust chamber by a vane. The first end face 110 and the second end face 120 of the ring are respectively in contact with the end faces of the upper support and the lower support to form a sealing chamber. As the ring rotates eccentrically with the crankshaft, the end faces of the ring move frictionally with the end faces of the upper support and the lower support. The inner chamfers of the ring can be used to store oil. During the movement of the ring, the stored oil lubricates the upper and lower end faces of the ring to prevent abnormal wear with the end faces of the upper support and the lower support.

[0046] In this embodiment, a first inner chamfer 111 is formed on the first end face 110 of the ring, and a second inner chamfer 121 is formed on the second end face 120. In application, the first inner chamfer 111 corresponds to the side of the air compensation hole. The size of the first inner chamfer 111 affects the oil lubrication, operation reliability and stability. Therefore, in combination with the sealing requirements of the compressor with an air compensation and enthalpy-increasing structure during the movement of the ring, the first inner chamfer 111 is designed as a non-uniform chamfer so that its size is variable.

[0047] Specifically, the first inner chamfer 111 is located between the first end face 110 and the inner circumferential surface of the ring 100. The first inner chamfer 111 includes a first inclined surface 111a. The side of the first inclined surface 111a that intersects with the first end face 110 is a first curved edge 111b, and the side of the first inclined surface 111a that intersects with the inner circumferential surface of the ring 100 is a second curved edge 111c. Combining the understanding of the structure of the ring, it can be known that the first inclined surface 111a is an annular closed surface, and the first curved edge 111b and the second curved edge 111c are closed curves.

[0048] In different radial directions, the radial distance between the first curved edge 111b and the second curved edge 111c is not equal.

[0049] The radial direction refers to the straight line direction along the diameter or radius, or the straight line direction perpendicular to the axis. It is known that the center line of the ring is its axis. In this embodiment, the different radial directions defined herein, that is, the different straight line directions perpendicular to the axis, the radial distance between the first curved edge 111b and the second curved edge 111c is not equal.

[0050] It can be learned from the background art that the sizes of the inner chamfers of the two end faces of the traditional ring are the same or the sizes of the inner chamfers of the two end faces of the ring are different, but the inner chamfers of the two end faces of the ring are all of uniform size. Therefore, in different radial directions, the radial distance between the first curved edge 111b and the second curved edge 111c of the inner chamfers of the two end faces always remains the same. In this way, when the sealing effect can be ensured, there will be a problem of insufficient oil lubricity.

[0051] In this embodiment, in different radial directions, the radial distance between the first curved edge 111b and the second curved edge 111c is different. That is to say, the first inclined surface 111a is an irregular inclined surface, and the shapes of the first curved edge 111b and the second curved edge 111c are different, so that the first inner chamfer 111 presents a non-uniform chamfer, and its size has variability. During the eccentric rotation of the ring 100, when different positions of the first inner chamfer 111 correspond to the air compensation holes, the leakage influence can be minimized, and there is a local enlarged structure design, which increases the oil storage capacity, improves the oil lubrication effect, and ensures reliability.

[0052] Furthermore, in the same radial direction, the radial distance between the first curved edge 111b and the second curved edge 111c, which are located on the opposite sides of the axis of the ring, is not equal, so that the local part of the first inner chamfer 111 is enlarged, meeting the requirements of oil lubrication and ensuring reliability.

[0053] In a compressor with an air compensation and enthalpy-increasing structure, when each component of the pump assembly operates, the outer circumference of the ring and the inner circumference of the cylinder block are divided into a compression chamber and an exhaust chamber by the blades. Driven by the crankshaft, the ring rotates eccentrically in the cylinder block. Since the size and position of the air compensation holes are fixed, during the eccentric rotation of the ring, different positions of the first inner chamfer 111 on the first end face 110 of the ring respectively correspond to the air compensation holes. Combining with the eccentric rotation of the ring, in the design of the size of the first inner chamfer 111, in the same radial direction, the radial distance between the first curved edge 111b and the second curved edge 111c, which are located on the opposite sides of the axis of the ring, is not equal.

[0054] In some embodiments, the projections of the first curved edge 111b and the second curved edge 111c on the first end face 110 form a non-circular ring shape, realizing the design that the first inner chamfer 111 is a non-uniform chamfer and its size has variability.

[0055] For example, referring to Figure 6 , the projection of the first curved edge 111b on the first end face 110 forms an ellipse, and the projection of the second curved edge 111c on the first end face 110 forms a circle.

[0056] It should be noted that in this example, the projection of the first curved edge 111b is not limited to an ellipse, nor is the projection of the second curved edge 111c limited to a circle. It can be an irregular closed shape and can be adjusted according to actual needs.

[0057] In the ring provided in this embodiment for a compressor, there is no case where the radial distance between the first curved edge 111b and the second curved edge 111c is equal in different radial directions or in the same radial direction. Thus, it can be ensured that during the eccentric rotation of the ring, when different positions on the first inner chamfer 111 correspond to the air supply holes, leakage can be minimized as much as possible, and at the same time, oil lubrication can be ensured to improve reliability.

[0058] Embodiment 2:

[0059] The difference between this embodiment and Embodiment 1 is that in this embodiment, further structural optimization is made to the ring for the compressor of the present invention. Please refer to Figures 8 - 10 .

[0060] Refer to Figure 8 and Figure 9 , the projections of the first curved edge 111b and the second curved edge 111c on the first end face 110 form a circular ring shape, realizing that the first inner chamfer 111 is a non-uniform chamfer with a variable size design.

[0061] That is, the projection of the first curved edge 111b on the first end face 110 forms a first circle, and the projection of the second curved edge 111c on the second end face 120 forms a second circle. The first circle and the second circle are concentric, so as a whole, it presents a circular ring shape.

[0062] It should be noted that in this example, the projections of the first curved edge 111b and the second curved edge 111c are not limited to a circular ring shape, and can also be an irregular ring shape, which can be adjusted according to actual needs.

[0063] Refer to Figure 10 , in some embodiments, the second inner chamfer 121 includes a second inclined surface 121a, and the projection of the second inclined surface 121a on the second end face 120 forms a circular ring shape or a non-circular ring shape.

[0064] The first end face 110 and the second end face 120 of the ring are respectively used to contact the end faces of the upper support and the lower support to form a sealing cavity. For example, if the first end face 110 corresponds to the upper support provided with air supply holes, then the second end face 120 corresponds to the lower support. The design of the second inner chamfer 121 on the second end face 120 does not need to consider the size and position of the air supply holes, and only needs to combine the eccentric rotation effect of the ring and the structural design of the first inner chamfer 111 to ensure the oil supply amount and reliability.

[0065] It should be noted that the structural design of the second inner chamfer 121 can be the same as or different from the structural design of the first inner chamfer 111, which can be adjusted according to actual needs.

[0066] Embodiment 3:

[0067] Based on the above embodiments, the present embodiment provides a compressor. Please refer to Figures 11 - 13 .

[0068] A compressor includes a cylinder block 200, a crankshaft 300, a support 400, and the ring 100 in any of the above embodiments.

[0069] The crankshaft 300 passes through the cylinder block 200 and the support 400. The ring 100 is located between the crankshaft 300 and the cylinder block 200. The first end face 110 of the ring 100 is connected to the support 400, and a gas compensation hole 410 is formed in the support 400.

[0070] The crankshaft 300 is used to drive the ring 100 to perform eccentric rotation in the cylinder block 200. The support 400 is used to support the crankshaft 300 and connect with the first end face 110 to form a closed accommodation space. The closed accommodation space is divided into a suction chamber and a compression chamber under the action of a blade. The gas compensation hole enters the compression chamber through the support.

[0071] In the ring used in a traditional compressor with a gas injection and enthalpy increase structure, the inner chamfer on the end face corresponding to the gas compensation hole has uniformity and is relatively small. During the eccentric rotation of the ring, it is necessary to prevent the first inner chamfer 111 from communicating with the gas compensation hole, which results in insufficient oil supply and affects the reliability of the compressor. However, for the ring applied in this embodiment, a first inner chamfer 111 is formed on the first end face 110 of the ring. The first inner chamfer 111 is a non-uniform chamfer, and its size has variability to allow the first inner chamfer 111 of the ring to communicate with the gas compensation hole, so as to meet the requirements of oil lubrication, ensure reliability, and minimize the performance impact caused by leakage as much as possible.

[0072] In some embodiments, the gas compensation hole is a circular hole. The leakage length along the radial direction between the first inner chamfer 111 and the gas compensation hole is L, and L = r + e + d / 2 + Ci - S.

[0073] Wherein, r is the radius of the gas compensation hole, e is the eccentricity of the crankshaft, d is the inner diameter of the ring, Ci is the radial distance between the first curved edge 111b and the second curved edge 111c when the center of the ring is closest to the center of the gas compensation hole, and S is the distance between the center of the gas compensation hole and the center of the cylinder block.

[0074] In a compressor with a gas injection and enthalpy increase structure, the ring has self-rotation and revolution around the center of the inner diameter of the cylinder block. When the distance between the center of the inner diameter of the ring and the center of the gas compensation hole is the closest, during each revolution period, when there is leakage between the first inner chamfer 111 of the ring and the gas compensation hole, due to the self-rotation of the ring, the leakage length is different; the leakage length is related to the radial distance Ci between the first curved edge 111b and the second curved edge 111c of the ring at this position. When Ci is large, the leakage is large; when Ci is small, the leakage is small, and the performance of the gas injection condition during operation is better.

[0075] In some embodiments, 0 ≤ L ≤ 3 mm.

[0076] It can be known that when the leakage length L is smaller, correspondingly, the radial distance Ci is smaller, then the leakage is small, and the performance of the air supplementing condition during operation is better. In one example, in combination with the design requirements, the leakage length L is limited to 2 mm.

[0077] In some embodiments, let the displacement of the cylinder block be V, where 1000 * L / V ≤ 120 mm / cc. Limiting the relationship between the displacement of the cylinder block and the leakage length within this range can better ensure the operating performance of the compressor and improve the reliability.

[0078] A compressor provided in this embodiment can ensure the performance and operating reliability of the compressor after applying a first inner chamfer with non-uniform chamfers and variable sizes.

[0079] In the present utility model, unless otherwise clearly defined and limited, terms such as "installation", "connection", "connection", "fixation" and other terms should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, and can be the communication inside two components or the interaction relationship between two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0080] In the description of the present utility model, it should be noted that the orientation or positional relationship indicated by terms such as "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product of this utility model is usually placed during use. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or component referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present utility model. In addition, terms such as "first", "second", "third", etc. are only used for distinguishing descriptions and cannot be understood as indicating or implying relative importance.

[0081] In addition, terms such as "horizontal", "vertical", "hanging" do not mean that the components are required to be absolutely horizontal or hanging, but can be slightly inclined. For example, "horizontal" only means that its direction is more horizontal relative to "vertical", and does not mean that the structure must be completely horizontal, but can be slightly inclined.

[0082] In the present utility model, unless otherwise clearly specified or limited, the first feature being above or below the second feature may include the direct contact of the first and second features, or may include the contact of the first and second features not directly but through additional features therebetween. Moreover, the first feature being above, over and on the second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the horizontal height of the first feature is higher than that of the second feature. The first feature being below, under and beneath the second feature includes the first feature being directly below and obliquely below the second feature, or merely indicating that the horizontal height of the first feature is lower than that of the second feature.

[0083] Although the description of the present utility model is made in combination with the above specific embodiments, it is obvious that those skilled in the art can make many substitutions, modifications and changes according to the above content. Therefore, all such substitutions, improvements and changes are included within the spirit and scope of the appended claims.

Claims

1. A ring for a compressor, characterized in that, The ring (100) includes a first end face (110) and a second end face (120) which are oppositely arranged; A first inner chamfer (111) is formed on the first end face (110), and a second inner chamfer (121) is formed on the second end face (120); The first inner chamfer (111) includes a first inclined surface (111a). The side of the first inclined surface (111a) intersecting with the first end face (110) is a first curved edge (111b), and the side of the first inclined surface (111a) intersecting with the inner circumferential surface of the ring (100) is a second curved edge (111c). Both the first curved edge (111b) and the second curved edge (111c) are closed curves; In different radial directions, the radial distance between the first curved edge (111b) and the second curved edge (111c) is not equal.

2. The ring for a compressor according to claim 1, wherein In the same radial direction, the radial distances between the first curved edge (111b) and the second curved edge (111c) located on the opposite sides of the axis of the ring (100) are not equal.

3. The ring for a compressor according to claim 1 or 2, characterized in that, The projections of the first curved edge (111b) and the second curved edge (111c) on the first end face (110) form a non-circular ring shape.

4. The ring for a compressor according to claim 3, characterized in that, The projection of the first curved edge (111b) on the first end face (110) forms an ellipse, and the projection of the second curved edge (111c) on the first end face (110) forms a circle.

5. The ring for a compressor according to claim 1 or 2, characterized in that, The projections of the first curved edge (111b) and the second curved edge (111c) on the first end face (110) form a circular ring shape.

6. The ring for a compressor according to claim 1, characterized in that, The second inner chamfer (121) includes a second inclined surface (121a). The projection of the second inclined surface (121a) on the second end face (120) forms a circular ring shape or a non-circular ring shape.

7. A compressor, characterized in that, It includes a cylinder block (200), a crankshaft (300), a support (400), and the ring (100) according to any one of claims 1-6; The crankshaft (300) passes through the cylinder block (200) and the support (400). The ring is located between the crankshaft (300) and the cylinder block (200), and the first end face (110) of the ring is connected to the support (400). An air supplement hole (410) is provided on the support (400).

8. The compressor according to claim 7, characterized in that, The air supplement hole (410) is a circular hole. The leakage length in the radial direction between the first inner chamfer (111) and the air supplement hole (410) is L, and L = r + e + d / 2 + Ci - S; Wherein, r is the radius of the air supplement hole (410), e is the eccentricity of the crankshaft (300), d is the inner diameter of the ring (100), Ci is the radial distance between the first curved edge (111b) and the second curved edge (111c) when the centers of the ring (100) and the air supplement hole (410) are the closest, and S is the distance between the center of the air supplement hole (410) and the center of the cylinder block (200).

9. The compressor according to claim 8, characterized in that, The value of L is 0 ≤ L ≤ 3 mm.

10. The compressor according to claim 8, wherein, Let the displacement of the cylinder block (200) be V, and the value of V is 1000 * L / V ≤ 120 mm / cc.

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