WO2025086365A1 - Pump body assembly and rolling piston compressor - Google Patents

Abstract

A pump body assembly, comprising a cylinder (1). The cylinder (1) comprises a cylinder body (11) and a first cavity (12) surrounded and defined by the cylinder body (11). The cylinder body (11) is provided with a notched portion (111). An end of the notched portion (111) extends to an inner wall of the cylinder body (11), and another end of the notched portion (111) extends to an exhaust side (112) of the cylinder (1). The maximum distance between an edge of the notched portion (111) and the inner wall of the cylinder body (11) is b, and the thickness of the cylinder body (11) is B, where 0 < b/B ≤ 0.2. The cylinder body (11) is provided with the notched portion (111) to reduce the clearance volume and improve volumetric efficiency. Additionally, by limiting the dimensions of the notched portion (111), the overall clearance volume range of the cylinder (1) is controlled, avoiding solely pursuing an increase in displacement while also addressing noise control, thereby enhancing overall performance.

Description

Pump assembly and rolling rotor compressor

This application claims priority to the Chinese patent application filed with the China Patent Office on October 23, 2023, with application number 202322842440.9 and the Chinese patent application filed with the China Patent Office on October 23, 2023, with application number 202311375911.8. The entire contents of the above applications are incorporated by reference into this application.

Technical Field

The present application relates to the technical field of compressors, for example, to a pump body assembly and a rolling rotor compressor.

Background Art

A compressor is a driven fluid machine that lifts low-pressure gas into high-pressure gas. Compressors include reciprocating and rotary types. Among them, the rotary type is commonly used with rolling rotor compressors. Rolling rotor compressors have many advantages such as simple structure, excellent performance, and low cost. They work by using the rotational force of the motor to compress low-pressure gas into high-pressure gas and discharge it. The rotary compressor is mainly composed of a housing, a motor, a crankshaft, a piston, a cylinder, and blades. The piston is located in the cylinder. When the crankshaft rotates around the center of rotation, the piston rotates closely against the inner surface of the cylinder. As a result, a crescent-shaped space can be formed between the outer surface of the piston and the inner surface of the cylinder.

It is a trend to make small series compressors with large displacement to replace large series compressors. However, the cylinder exhaust side incisions of the rolling rotor compressors in the related art all adopt arc-shaped incisions as shown in Figure 7, so that the compression volume between the cylinder exhaust side and the exhaust port is not well utilized, making it difficult to increase the effective volume of the rolling rotor compressor, resulting in low volumetric efficiency and small displacement. In addition, the rolling rotor compressor will cause noise due to exhaust pulsation during exhaust, thereby increasing power consumption.

Summary of the invention

The present application provides a pump body assembly that reduces the clearance volume, improves volumetric efficiency, and reduces noise.

A pump body assembly includes a cylinder, wherein the cylinder includes a cylinder body and a first cavity formed by the cylinder body, the cylinder body is provided with a cutout portion, and one end of the cutout portion extends to the inner wall of the cylinder body, and the other end of the cutout portion extends to the exhaust side of the cylinder, the maximum distance between the edge of the cutout portion and the inner wall of the cylinder body is b, and the thickness of the cylinder body is B, wherein 0＜b/B≤0.2.

Optionally, the length of the cutout portion is L, wherein 0＜b/L≤0.37.

Optionally, a central angle β of two side edges of the cutout portion along the length direction satisfies 0°≤β≤23°.

Optionally, an angle θ between a tangent line of an edge of the cutout portion radially away from an inner side of the cylinder body and a horizontal plane satisfies 0＜θ≤45°.

Optionally, the depth of the cutout portion intersecting the inner wall of the cylinder body is h, and the depth of the cylinder body is H, wherein h≤b, and h≤H.

Optionally, the cutting surface line of the incision portion is formed by a straight line, or the cutting surface line of the incision portion is formed by a plurality of straight lines, or the cutting surface line of the incision portion is formed by a curve, or the cutting surface line of the incision portion is formed by a straight line and a curve.

Optionally, the pump body assembly also includes a cylinder head, which is connected to the exhaust side of the cylinder body, and the cylinder head is provided with an exhaust hole, which passes through the cylinder head, and the axial direction of the exhaust hole is perpendicular to the exhaust side, at least part of the exhaust hole is connected to the first cavity, and the cutout portion is connected to the exhaust hole.

Optionally, the diameter of the exhaust hole is D, and the maximum distance between any two points of the cutout portion is L, wherein 0＜L≤D.

Optionally, the cross-sectional shape of the exhaust hole is circular or D-shaped.

The present application also provides a rolling rotor compressor, comprising the above-mentioned pump body assembly.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is a structural schematic diagram of a cylinder provided in Example 1 of the present application;

FIG2A is a second structural schematic diagram of a cylinder provided in Example 1 of the present application;

FIG2B is a third structural schematic diagram of the cylinder provided in Example 1 of the present application;

FIG3 is a partial cross-sectional view of a cylinder provided in Embodiment 1 of the present application;

FIG4 is a schematic diagram of the assembly of a cylinder and a cylinder head provided in Embodiment 1 of the present application;

FIG5 is a second schematic diagram of the assembly of the cylinder and the cylinder head provided in the first embodiment of the present application;

FIG6 is a comparison diagram of noise peaks at different operating frequencies between a rolling rotor compressor provided in Example 2 of the present application and a rolling rotor compressor in the related art;

FIG. 7 is a schematic diagram of the structure of a cylinder in the related art.

In the figure:

1. Cylinder; 11. Cylinder body; 111. Cutout portion; 112. Exhaust side; 12. First cavity; 2. Cylinder head; 21. Exhaust hole.

DETAILED DESCRIPTION

The present application is described below in conjunction with the accompanying drawings and embodiments. It is to be understood that the specific embodiments described herein are only used to explain the present application, rather than to limit the present application. In addition, for ease of description, only parts related to the present application, rather than all structures, are shown in the accompanying drawings.

In the description of this application, unless otherwise clearly specified and limited, the terms "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may include the first feature being in direct contact with the second feature, or may include the first feature being in contact with the second feature through another feature between them instead of being in direct contact. Moreover, a first feature being “above”, “above”, and “above” a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being “below”, “below”, and “below” a second feature includes the first feature being directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

In the description of this embodiment, the terms "upper", "lower", "left", "right" and other directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description and simplified operation, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation of the present application. In addition, the terms "first" and "second" are only used to distinguish in the description and have no special meaning.

Embodiment 1

As shown in Fig. 1 to Fig. 5, the present embodiment provides a pump body assembly, which includes a cylinder 1, and the cylinder 1 includes a cylinder body 11 and a first cavity 12 formed by the cylinder body 11, that is, as shown in Fig. 1 and Fig. 2A, the cylinder body 11 is annular, and the inner wall of the cylinder body 11 is formed to form the first cavity 12. The cylinder 1 provided in the present embodiment is also provided with at least one air intake hole, and the air intake hole is connected to the first cavity 12. When the rolling rotor compressor is working, the gas enters the first cavity 12 through the air intake hole and is compressed, and the compressed high-pressure gas is discharged through the exhaust side 112 of the cylinder 1.

The cylinder body 11 is provided with a cutout portion 111, one end of the cutout portion 111 extends to the inner wall of the cylinder body 11, and the other end of the cutout portion 111 extends to the exhaust side 112 of the cylinder 1, that is, the cutout portion 111 is connected to the first cavity 12 and intersects with the exhaust side 112 of the cylinder 1. The high-pressure gas in the first cavity 12 is discharged through the cutout portion 111 and the exhaust side 112 of the cylinder 1, thereby widening the discharge channel of the high-pressure gas and making reasonable use of the cylinder 1. The compression volume between the exhaust side 112 and the exhaust port reduces the clearance volume and improves the volumetric efficiency.

As shown in FIG3 , the present application can effectively improve the volumetric efficiency while reducing noise by controlling the ratio b/B of the radial length of the cutout 111 to the thickness of the cylinder 11; b is the maximum distance between the edge of the cutout 111 and the inner wall of the cylinder 11, and B is the thickness of the cylinder 11. This embodiment defines the size parameters of the cutout 111, for example, the maximum distance between the edge of the cutout 111 and the inner wall of the cylinder 11 is set to b, and the thickness of the cylinder 11 is set to B. This embodiment defines 0＜b/B≤0.2. The ratio of the radial dimension of the cutout 111 (the maximum distance between the edge of the cutout 111 and the inner wall of the cylinder 11) to the thickness of the cylinder 11 is much smaller than the corresponding ratio of the exhaust cutout in the related art, which can effectively reduce the overall clearance volume of the cylinder 1, improve the volumetric efficiency, and reduce noise at the same time.

As shown in Fig. 2B, the length of the cutout 111 is set to L in the embodiment of the present application. To ensure the exhaust capacity, b and L satisfy: 0＜b/L≤0.37. The angle between the central axis of the blade slot and the cutout 111 is α, and α satisfies 4°≤α≤23°.

Optionally, the central angle β of the two side edges of the cut-out portion 111 along the length direction satisfies 0°≤β≤23°. By designing the aspect ratio of the cut-out portion 111, the clearance volume can be reduced and the noise peak during the operation of the compressor can be effectively reduced, especially the noise peak when the operating frequency is 1250 Hz.

The embodiment of the present application sets the depth of the intersection of the cutout portion 111 and the inner wall of the cylinder body 11 to h, and the depth of the cylinder body 11 to H. The present embodiment limits h≤b, and h≤H, and keeps the depth of the cutout portion 111 within this range, thereby controlling the overall clearance volume range of the cylinder 1, and providing the high-pressure gas with sufficient guiding depth, which is beneficial to the smooth discharge of the high-pressure gas in the cylinder 1 and improves the reliability of the compressor.

As shown in FIG3 , the angle between the tangent line of the edge of the cutout 111 away from the inner side of the cylinder body 11 in the radial direction and the horizontal plane is θ, and 0＜θ≤45°, which limits the size of the cutout 111 and controls the overall clearance volume range of the cylinder 1.

Optionally, the cutout portion 111 in this embodiment is formed by cutting. Exemplarily, the cutting surface line of the cutout portion 111 is a straight line, and the cross-sectional shape of any part of the cutout portion 111 is the same right triangle, or the cutting surface line of the cutout portion 111 is a plurality of straight lines, that is, the cross-sectional shape of any part of the cutout portion 111 is a right triangle, and the shapes are not exactly the same, or the cutting surface line of the cutout portion 111 is a curve, such as a smooth curve or an irregular curve, or the cutting surface line of the cutout portion 111 is a combination of a straight line and a curve, which is not specifically limited in this embodiment. In this embodiment, the cutout portion 111 is chamfered, such as a triangular chamfer, and satisfies 0＜θ≤45°. The cutting surface line is usually used to represent the cross-sectional view of a part. It is a contour line used to represent the shape and size of the cross section or cross section of a part, which is convenient for actual processing and production operations.

As shown in FIG. 4 and FIG. 5 , the pump assembly provided in this embodiment further includes a cylinder head 2, which is connected to the cylinder body 11, and one side of the cylinder head 2 is attached to the exhaust side 112 of the cylinder body 11. The cylinder head 2 is provided with an exhaust hole 21. The exhaust hole 21 penetrates the cylinder head 2, and at least part of the exhaust hole 21 can be connected to the first cavity 12. The cutout portion 111 is connected to the exhaust hole 21, that is, the high-pressure gas can be discharged through the exhaust hole 21. The axial direction of the exhaust hole 21 is perpendicular to the exhaust side 112, which is conducive to the smooth discharge of the high-pressure gas in the cylinder 1.

Since the first cavity 12 is circular, the cross-sectional shape of the exhaust hole 21 is adaptively set to be circular or D-shaped to match the cutout portion 111 opened on the cylinder body 11 .

Optionally, the diameter of the exhaust hole 21 is set to D. In this embodiment, 0＜L≤D is defined, and the size of the cutout portion 111 is limited to control the overall clearance volume range of the cylinder 1.

Optionally, the cylinder head 2 is provided with a second cavity, which is cylindrical, and the center line of the second cavity coincides with the center line of the cylinder head 2. The second cavity is directly opposite to the first cavity 12, so that the bearing and the rotor can be installed through the second cavity, so that the rotor can rotate eccentrically in the first cavity 12 in close contact with the inner wall of the cylinder body 11, thereby forming a crescent-shaped space between the inner wall of the cylinder body 11.

In summary, the pump body assembly disclosed in this embodiment has at least the following advantages: by setting the cut-out portion 111 in the cylinder body 11, the clearance volume is reduced and the volumetric efficiency is improved; at the same time, by limiting the size of the cut-out portion 111, the overall clearance volume range of the cylinder 1 is controlled, and the pursuit of increasing the displacement is not blindly pursued, while taking into account the control of noise and improving the overall performance.

Embodiment 2

The present embodiment provides a rolling rotor compressor, including the above-mentioned pump body assembly, wherein the detailed structural features of the pump body assembly can be referred to the description of the above-mentioned embodiment and will not be repeated here. The rolling rotor compressor provided by the present embodiment has a small clearance volume, high volumetric efficiency, and low operating noise.

As shown in FIG6 , in this embodiment, H=20 mm, h=b=0.5 mm, L=6.15 mm, θ=45°, B=13 mm, and β=23° are set. The clearance volume of the rolling rotor compressor provided in this embodiment is reduced by 35% compared to the clearance volume of the rolling rotor compressor shown in FIG7 , and the noise peak in the 1250 Hz frequency band is reduced by about 4 dB.

The present application provides a pump body assembly, which includes a cylinder, wherein the cylinder includes a cylinder body and a first cavity formed by the cylinder body, the cylinder body is provided with a cutout portion, and one end of the cutout portion extends to the inner wall of the cylinder body, and the other end of the cutout portion extends to the exhaust side of the cylinder, the maximum distance between the edge of the cutout portion and the inner wall of the cylinder body is b, and the thickness of the cylinder body is B, wherein 0＜b/B≤0.2. The cutout portion is connected to the first cavity and intersects with the exhaust side of the cylinder, and the high-pressure gas in the first cavity is discharged after passing through the cutout portion and the exhaust side of the cylinder, thereby widening the discharge channel of the high-pressure gas, rationally utilizing the compression volume between the exhaust side of the cylinder and the exhaust port, reducing the clearance volume, and improving the volumetric efficiency. At the same time, by setting the ratio of b to B, the noise generated during operation is effectively reduced; the rolling rotor compressor provided by the present application includes the above-mentioned pump body assembly, and since the pump body assembly reduces the clearance volume and improves the volumetric efficiency, at the same time The size of the cutout portion is limited, so the displacement of the rolling rotor compressor is large and the operating noise is effectively reduced.

Claims (10)

A pump body assembly comprises a cylinder (1), wherein the cylinder (1) comprises a cylinder body (11) and a first cavity (12) formed by the cylinder body (11), the cylinder body (11) is provided with a cutout portion (111), and one end of the cutout portion (111) extends to the inner wall of the cylinder body (11), and the other end of the cutout portion (111) extends to the exhaust side (112) of the cylinder (1), the maximum distance between the edge of the cutout portion (111) and the inner wall of the cylinder body (11) is b, and the thickness of the cylinder body (11) is B, wherein 0＜b/B≤0.2. The pump body assembly according to claim 1, wherein the length of the cutout portion (111) is L, wherein 0＜b/L≤0.37. The pump body assembly according to claim 1, wherein a central angle β of two side edges of the cutout portion (111) along the length direction satisfies 0°≤β≤23°. The pump body assembly according to claim 1, wherein an angle θ between a tangent line of an edge of the cutout portion (111) radially away from an inner portion of the cylinder body (11) and a horizontal plane satisfies 0＜θ≤45°. The pump assembly according to claim 1, wherein the depth of the cutout portion (111) intersecting the inner wall of the cylinder body (11) is h, and the depth of the cylinder body (11) is H, wherein h≤b, and h≤H. The pump body assembly according to any one of claims 1 to 5, wherein the cutting plane line of the cutout portion (111) is formed by a straight line, or the cutting plane line of the cutout portion (111) is formed by a plurality of straight lines, or the cutting plane line of the cutout portion (111) is formed by a curve, or the cutting plane line of the cutout portion (111) is formed by a straight line and a curve. The pump body assembly according to claim 6 further includes a cylinder head (2), the cylinder head (2) is connected to the exhaust side (112) of the cylinder body (11), the cylinder head (2) is provided with an exhaust hole (21), the exhaust hole (21) passes through the cylinder head (2), and the axial direction of the exhaust hole (21) is perpendicular to the exhaust side (112), at least a part of the exhaust hole (21) is connected to the first cavity (12), and the cutout portion (111) is connected to the exhaust hole (21). The pump body assembly according to claim 7, wherein the diameter of the exhaust hole (21) is D, and the maximum distance between any two points of the cutout portion (111) is L, wherein 0＜L≤D. The pump body assembly according to claim 7, wherein the cross-sectional shape of the exhaust hole (21) is circular or D-shaped. A rolling rotor compressor, comprising the pump body assembly according to any one of claims 1-9.