Cylinder and rotor compressor

Abstract

This utility model provides a cylinder, including a cylinder barrel, on which a spring hole and an intake hole are formed. The cylinder barrel has a height T. The intake hole has a first tangent on its outer edge near the spring hole, and a second tangent on its outer edge near the intake hole. The first tangent and the second tangent are parallel, and the distance between the first tangent and the second tangent is the wall thickness X between the holes. The characteristic feature is that when the wall thickness X between the holes remains constant, the centerline of the intake hole and the centerline of the spring hole have a height difference H in the direction of the cylinder barrel height, and the height difference H satisfies 0 < H ≤ 0.32T. A rotary compressor is also provided. By adopting the technical solution of this utility model, while ensuring that the cylinder has a wall thickness X between the holes to maintain its strength, the intake hole angle α and the intake end angle b can be reduced, increasing the compressor's cooling capacity Y, thereby improving the compressor's performance.

Description

Technical Field

[0001] This application relates to the field of compressors, and more particularly to a rotary compressor. Background Technology

[0002] Rotary compressors are widely used in refrigeration, air conditioning and other fields. A rotary compressor typically includes a housing, motor, pump body assembly, upper cover, lower cover, distributor assembly, etc. The pump body assembly includes: upper bearing, lower bearing, cylinder, crankshaft, piston, vane, spring, upper silencer, lower silencer, etc.

[0003] The piston is located inside the cylinder. When the crankshaft rotates around the center of rotation, the piston rotates close to the inner surface of the cylinder. As a result, a crescent-shaped space is formed between the outer surface of the piston and the inner surface of the cylinder. The linearly reciprocating sliding vane divides this space into two independent parts: one part is the intake chamber and the other part is the compression chamber. The sliding vane is pressed against the outer surface of the piston by a spring.

[0004] The cylinder has an intake port and a spring hole. The centerlines of the intake port and the spring hole are aligned with the cylinder center, which is the crankshaft. The centerlines of the intake port and the spring hole are usually at the same height along the cylinder's height, meaning they are on the same horizontal plane. The two holes maintain a certain angle. One side of the intake port angle 'a' is the centerline of the spring hole, and the other side is the centerline of the intake port. The intake port angle 'a' is the angle between the centerlines of the spring hole and the intake port. One side of the intake termination angle 'b' is the centerline of the spring hole, and the other side is the line connecting the edge of the intake port furthest from the spring hole to the cylinder centerline. The intake termination angle 'b' is the angle between the centerline of the spring hole and the connecting line. The shortest distance between the outer edges of the intake port and the spring hole is the distance between the holes. The wall thickness X can be increased by reducing the intake port angle α, which reduces the intake end angle b of the cylinder, thereby increasing the intake volume, improving the cylinder volumetric efficiency, and increasing the compressor's cooling capacity Y, thus improving compressor efficiency. However, reducing the intake port angle α also reduces the wall thickness X between the ports, reducing the structural strength of the cylinder, which may lead to damage to the inner wall of the cylinder and direct failure of the compressor. Conversely, if the intake port angle α is increased, the wall thickness X between the ports will also increase. Although the structural strength of the cylinder will be improved, it will lead to an increase in the intake end angle b, thereby reducing the intake volume, decreasing the cylinder volumetric efficiency, decreasing the compressor's cooling capacity Y, and reducing compressor performance. Therefore, how to effectively improve the compressor performance while ensuring the wall thickness X between the ports is the key problem that this utility model needs to solve. Summary of the Invention

[0005] To overcome at least one of the aforementioned defects and problems in the prior art, the present invention provides a cylinder.

[0006] According to a specific embodiment of the present invention, a cylinder is provided, including a cylinder barrel, on which a spring hole and an intake hole are formed. The cylinder barrel has a height of T. The intake hole has a first tangent on its outer edge near the spring hole, and the spring hole has a second tangent on its outer edge near the intake hole. The first tangent and the second tangent are parallel, and the distance between the first tangent and the second tangent is the wall thickness X between the holes. The characteristic feature is that when the wall thickness X between the holes remains constant, the centerline of the intake hole and the centerline of the spring hole have a height difference H in the cylinder barrel height direction, and the height difference H satisfies 0 < H ≤ 0.32T.

[0007] In a preferred embodiment, the cylinder has a first surface and a second surface opposite to each other, the first surface and the second surface being parallel to each other, and the distance between the first surface and the second surface being the cylinder height T.

[0008] In a preferred embodiment, both the spring hole and the intake hole are cylindrical, the centerline of the spring hole and the centerline of the intake hole are parallel to the first surface and both pass through the centerline of the cylinder, and the cylinder is connected to the center of the crankshaft.

[0009] In a preferred embodiment, the cylinder has an intake port angle and an intake termination angle. One side of the intake port angle is the centerline of the spring hole, and the other side is the centerline of the intake port. The degree measure of the intake port angle is the angle between the projection of the centerline of the spring hole and the centerline of the intake port onto the first surface or the second surface. One side of the intake termination angle is the centerline of the spring hole, and the other side is the line connecting the edge of the intake port away from the spring hole to the centerline of the cylinder. The degree measure of the intake termination angle is the angle between the projection of the centerline of the spring hole and the connecting line onto the first surface or the second surface. The intake termination angle increases and decreases as the intake port angle increases, and the degree of increase or decrease remains consistent.

[0010] In a preferred embodiment, when X is 1 mm and H is 0.05 T, the suction orifice angle decreases by 0.1 degrees; when X is 1 mm and H is 0.1 T, the suction orifice angle decreases by 0.2 degrees; when X is 1 mm and H is 0.15 T, the suction orifice angle decreases by 0.5 degrees; when X is 1 mm and H is 0.2 T, the suction orifice angle decreases by 0.7 degrees; when X is 1 mm and H is 0.25 T, the suction orifice angle decreases by 1.4 degrees; and when X is 1 mm and H is 0.32 T, the suction orifice angle decreases by 2.2 degrees. To overcome at least one aspect of the aforementioned defects and problems in the prior art, the present invention provides a rotary compressor comprising a cylinder as described above.

[0011] In summary, the technical solution of this utility model can reduce the suction port angle a and the suction end angle b while ensuring that the cylinder has a wall thickness X between the holes that can maintain its strength, thereby increasing the compressor's cooling capacity Y and improving the compressor's performance. Attached Figure Description

[0012] Figure 1 This is a front view of the cylinder in Embodiment 1 of this application; Figure 2 This is a bottom view of the cylinder in Embodiment 1 of this application; Figure 3 This is a bottom view of the cylinder in Embodiment 2 of this application; Figure 4 This is a bottom view of the cylinder in Embodiment 3 of this application; Figure 5 This is a bottom view of the cylinder of Comparative Example 1 of this application.

[0013] Explanation of reference numerals in the attached drawings: 1. Cylinder; 11. Cylinder barrel; 111. First surface; 112. Second surface; 12. Intake port; 13. Spring hole; 2. Crankshaft; T. Cylinder barrel height; T / 2. Position of 1 / 2 cylinder barrel height; a. Intake port angle; b. Intake end angle; X. Wall thickness between holes; H. Height difference; L1. First tangent; L2. Second tangent. Detailed Implementation

[0014] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0015] Example 1: Refer to Appendix Figure 1 ~Appendix Figure 2 .

[0016] Embodiment 1 provides a cylinder 1, which includes a cylinder barrel 11. The cylinder barrel 11 has a first surface 111 and a second surface 112 that are opposite each other. The first surface 111 and the second surface 112 are parallel to each other, and the vertical distance between the first surface 111 and the second surface 112 is the cylinder barrel height T.

[0017] The cylinder 11 has an intake hole 12 and a spring hole 13 on its wall. Both the intake hole 12 and the spring hole 13 are cylindrical. The center lines of the intake hole 12 and the spring hole 13 are parallel to the first surface 111 and pass through the center line of the cylinder 11. The cylinder 1 has a crankshaft 2 at its center.

[0018] There is a certain angle between the intake port 12 and the spring port 13. One side of the intake port angle α is the center line of the spring port 13, and the other side is the center line of the intake port 12. The intake port angle α is the angle between the projections of the center line of the spring port 13 and the center line of the intake port 12 in the horizontal direction, that is, the angle between the projections on the first surface 111 or the second surface 112. One side of the intake end angle b is the center line of the spring port 13, and the other side is the line connecting the edge of the intake port 12 away from the spring port 13 and the center line of the cylinder 11. The intake end angle b is the angle between the projections of the center line of the spring port 13 and the center line of the cylinder 11 in the horizontal direction, that is, the angle between the projections on the first surface 111 or the second surface 112. The intake end angle b will increase or decrease as the intake port angle α increases, and the degree of increase or decrease remains consistent.

[0019] Cylinder 1 has a wall thickness X between holes. The wall thickness X between holes is the straight-line distance at the narrowest point between the intake hole 12 and the spring hole 13. It is the perpendicular distance between the tangents on the opposite sides of the intake hole 12 and the spring hole 13. Specifically, the intake hole 12 has a first tangent L1 on the outer edge near the spring hole 13, and the spring hole 13 has a second tangent L2 on the outer edge near the intake hole 12. L1 and L2 are parallel, and the perpendicular distance between L1 and L2 is the wall thickness X between holes.

[0020] When cylinder 1 has a wall thickness X between the holes that can maintain its strength and X remains constant, the height difference H between the center lines of the two holes in the height direction of cylinder 11, and the height difference H satisfies 0 < H ≤ 0.32T, will cause the suction port 12 to move closer to the spring port 13 or the spring port 13 to move closer to the suction port 12. Since the suction port angle α is the angle between the projections of the center line of spring port 13 and the center line of suction port 12 in the horizontal direction, the suction port angle α will decrease, and the suction end angle b will also decrease accordingly. Thus, while ensuring that cylinder 1 has a wall thickness X between the holes that can maintain its strength, the cooling capacity Y of the compressor is increased, thereby improving the performance of the compressor.

[0021] In this embodiment, the centerline of the spring hole 13 is at the T / 2 cylinder height position, while the centerline of the intake hole 12 is between the T / 2 cylinder height position and the first surface 111 of the cylinder 11.

[0022] Example 2: Refer to Appendix Figure 3 .

[0023] Another embodiment of this utility model, such as Figure 3As shown, a cylinder 1 is provided. This embodiment is basically the same as Embodiment 1, except that the center line of the intake port 12 and the center line of the spring hole 13 are positioned differently along the height of the cylinder 11. Specifically, in this embodiment, the center line of the intake port 12 is at a height of T / 2 of the cylinder 11, while the center line of the spring hole 13 is between the T / 2 cylinder 11 height and the first surface 111 of the cylinder 11. The technical effects and problems solved by this embodiment are the same as those of Embodiment 1, and it overcomes the defects of the prior art and achieves the purpose of this invention.

[0024] Example 3: Refer to Appendix Figure 4 .

[0025] Another embodiment of this utility model, such as Figure 3 As shown, a cylinder 1 is provided. This embodiment is basically the same as Embodiments 1 and 2, except that the center line of the intake port 12 and the center line of the spring port 13 are not at the T / 2 cylinder height position. Instead, the center line of the spring port 13 is between the T / 2 cylinder height position and the first surface 111 of the cylinder 11, and the center line of the intake port 12 is between the T / 2 cylinder height position and the second surface 112 of the cylinder 11. The technical effects and problems solved by this embodiment are the same as those of Embodiments 1 and 2, and it also overcomes the defects of the prior art and achieves the invention purpose of this utility model.

[0026] Example 4: Example 4 provides a rotary compressor, which includes a cylinder 1 as described in any of Examples 1 to 3.

[0027] Comparative Example 1: Refer to Appendix Figure 5 .

[0028] Comparative Example 1 provides a conventionally configured intake port 12 and spring port 13, where the centerline of the intake port 12 and the centerline of the spring port 13 are both at the height of cylinder T / 2, that is, the height difference H between the centerlines of the two ports in the height direction of cylinder 11 is 0.

[0029] The parameters and related performance of Comparative Example 1 are as follows: Table 1:

[0030] The compressor's cooling capacity Y can be obtained through compressor performance testing under the same 60Hz operating conditions.

[0031] As shown in the table above, when the height difference H between the centerline of the suction port 12 and the centerline of the spring port 13 in the height direction of the cylinder 11 is 0, as the suction port angle a increases, the wall thickness X between the ports also increases, the cooling capacity Y of the compressor decreases, thereby reducing the performance of the compressor.

[0032] The parameters and related performance of the compressor when the wall thickness between holes X=1mm in Examples 1-4 are as follows: Table 2:

[0033] The compressor's cooling capacity Y can be obtained through compressor performance testing under the same 60Hz operating conditions.

[0034] As shown in the table above, when the wall thickness X between the holes is constant, the greater the height difference H between the center line of the suction hole 12 and the center line of the spring hole 13 in the height direction of the cylinder 11, the smaller the suction hole angle α, and the higher the cooling capacity Y of the compressor. This improves the performance of the compressor while ensuring the strength of the wall thickness X between the holes.

[0035] Tables 1 and 2 above are independent tables, only showing the relationship between their respective data changes.

[0036] The above are all preferred embodiments of this utility model, and are not intended to limit the scope of protection of this utility model. Therefore, all equivalent changes made to the structure, shape and principle of this utility model should be covered within the scope of protection of this utility model.

Claims

1. A cylinder, comprising a cylinder barrel, wherein a spring hole and an intake hole are formed on the cylinder barrel wall, the cylinder barrel having a height T, the intake hole having a first tangent on its outer edge near the spring hole, the spring hole having a second tangent on its outer edge near the intake hole, the first tangent and the second tangent being parallel, and the distance between the first tangent and the second tangent being the wall thickness X between the holes, characterized in that: When the wall thickness X between the holes remains constant, the centerline of the intake hole and the centerline of the spring hole have a height difference H in the cylinder height direction, and the height difference H satisfies 0 < H ≤ 0.32T.

2. A cylinder according to claim 1, characterized in that: The cylinder has a first surface and a second surface opposite to each other, the first surface and the second surface being parallel to each other, and the distance between the first surface and the second surface being the cylinder height T.

3. A cylinder according to claim 2, characterized in that: Both the spring hole and the intake hole are cylindrical. The center lines of the spring hole and the intake hole are parallel to the first surface and pass through the center line of the cylinder. The cylinder is connected to the center of the crankshaft.

4. A cylinder according to claim 3, characterized in that: The cylinder has an intake port angle and an intake termination angle. One side of the intake port angle is the centerline of the spring hole, and the other side is the centerline of the intake port. The degree measure of the intake port angle is the angle between the projection of the centerline of the spring hole and the centerline of the intake port onto the first surface or the second surface. One side of the intake termination angle is the centerline of the spring hole, and the other side is the line connecting the edge of the intake port away from the spring hole to the centerline of the cylinder. The degree measure of the intake termination angle is the angle between the projection of the centerline of the spring hole and the connecting line onto the first surface or the second surface. The intake termination angle increases and decreases as the intake port angle increases, and the degree of increase or decrease remains consistent.

5. A cylinder according to claim 4, characterized in that: When X is 1 mm and H is 0.05 T, the suction orifice angle decreases by 0.1 degrees; when X is 1 mm and H is 0.1 T, the suction orifice angle decreases by 0.2 degrees; when X is 1 mm and H is 0.15 T, the suction orifice angle decreases by 0.5 degrees; when X is 1 mm and H is 0.2 T, the suction orifice angle decreases by 0.7 degrees; when X is 1 mm and H is 0.25 T, the suction orifice angle decreases by 1.4 degrees; and when X is 1 mm and H is 0.32 T, the suction orifice angle decreases by 2.2 degrees.

6. A rotary compressor, characterized in that: Includes the cylinder as described in any one of claims 1-5.

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