WO2023020033A1

WO2023020033A1 - Cylinder and compressor

Info

Publication number: WO2023020033A1
Application number: PCT/CN2022/092116
Authority: WO
Inventors: 彭慧明; 赵旭敏; 韩鑫; 刘达炜
Original assignee: 珠海格力节能环保制冷技术研究中心有限公司; 珠海凌达压缩机有限公司
Priority date: 2021-08-20
Filing date: 2022-05-11
Publication date: 2023-02-23
Also published as: CN113464434A

Abstract

A cylinder and a compressor. The cylinder comprises a cylinder body (1), an exhaust port (2), and a sliding sheet groove (3). The exhaust port (2) and the sliding sheet groove (3) are both arranged on the cylinder body (1). The exhaust port (2) comprises a first notch (21) and a second notch (22); the first notch (21) is arranged distant from the sliding sheet groove relative to the second notch (22); the second notch (22) is arranged close to the sliding sheet groove (3) relative to the first notch (21); the second notch (22) has one end communicated with the sliding sheet groove (3) and the other end communicated with the first notch (21); and the second notch (22) is located between the first notch (21) and the sliding sheet groove (3). The first notch (21) is used for exhausting air, and the second notch (22) is for chamfering processing of a special structure, thereby effectively eliminating flanges and burrs while reducing the clearance volume.

Description

Cylinders and Compressors

Cross References to Related Applications

This application claims the priority of the Chinese patent application with the application number 202110963098.0 and the application name "A Cylinder and Compressor" submitted to the China Patent Office on August 20, 2021, which is hereby incorporated by reference in its entirety.

technical field

The present disclosure relates to the technical field of compressors, in particular to a cylinder and a compressor.

Background technique

At present, the cylinder of the rotary compressor includes the structure of the suction hole, the exhaust port, the sliding vane groove, etc., and the exhaust port should be set as close as possible to the sliding vane groove to reduce the clearance volume of the compressor, thereby reducing the clearance volume Impact on compressor energy efficiency. In order to make the exhaust port as close as possible to the sliding vane groove, after the parts are processed into fine parts, flanging, burrs, or even broken edges will occur, which will affect the stability of the compressor performance, and there are great hidden dangers in quality, which may lead to high compressor power. Even stuck.

Due to the large clearance volume of the compressor cylinder in the related art and the burr flanging at the exhaust port cannot be solved at the same time and other technical problems, this application researches and designs a cylinder and a compressor.

Contents of the invention

Therefore, the technical problem to be solved in the present application is to overcome the defects that the relatively large clearance volume of the compressor cylinder and the burr flanging at the exhaust port cannot be solved simultaneously in the related art, so as to provide a cylinder and a compressor.

In order to solve the above problems, the present disclosure provides a cylinder, which includes: a cylinder body, an exhaust port and a sliding vane groove, the exhaust port and the sliding vane groove are both arranged on the cylinder body, and the exhaust gas The mouth includes a first notch and a second notch, the first notch is arranged away from the slide groove relative to the second notch, and the second notch is arranged close to the slide groove relative to the first notch, And one end of the second notch communicates with the slide slot, and the other end communicates with the first notch, and the second notch is located between the first notch and the slide slot.

In some embodiments, the volume of the first gap is V _large , the volume of the second gap is V _small , and V _small <V _large .

In some embodiments, the first notch can be used for venting.

In some embodiments, _Vsmall < _0.25Vmajor .

In some embodiments, the shape of the surface of the first notch is the same as that of a part of the side surface of the first cylinder; the shape of the surface of the second notch is the same as that of a part of the side surface of the second cylinder or sphere. same shape.

In some embodiments, the diameter of the first cylinder is D1, the diameter of the second cylinder or the sphere is D2, and D1=D2.

In some embodiments, the cylinder body includes a cylinder end surface, the second notch intersects with the first notch and the cylinder end surface at a first point, and the shortest distance between the first point and the slide groove is The distance is L _P1 , and L _P1 ≥0.2mm.

In some embodiments, the cylinder body includes an inner circle of the cylinder, the second notch intersects with the first notch and the inner circle of the cylinder at a second point, and a chamfer is provided at the slide slot , the chamfer intersects the inner circle of the cylinder at the fourth side, the side where the slider groove intersects with the second notch is the first surface, and the distance between the fourth side and the first surface is The distance between the second _point and the first surface is L P2 , and the distance between the second point and the first surface is L _P2 ; satisfying L _P2 -L _{chamfer≥0.2mm} .

In some embodiments, L _P1 -L _chamfer > 0.4 mm.

In some embodiments, in the longitudinal section of the cylinder, the included angle between the central axis of the first cylinder and the axis of the cylinder is _greater than α, and in the longitudinal section of the cylinder, the central axis of the second cylinder and the axis of the cylinder The included angle of the cylinder axis is α _small , satisfying 0°≤α _large -α _small≤15 °.

In some embodiments, the cylinder body includes a cylinder end surface, the second notch intersects with the cylinder end surface to form a first side, the slider groove intersects with the cylinder end surface to form a second side, and the first An intersection angle β is formed between the side and the second side, satisfying β≧60°.

In some embodiments, the cylinder body includes a cylinder inner circle, the second notch intersects with the cylinder inner circle to form a third side, and the chamfer intersects with the cylinder inner circle to form a fourth side, the An intersection angle θ is formed between the third side and the fourth side, which satisfies θ≧60°.

In some embodiments, in any cross-section parallel to the cylinder end face, a line between the center of the second notch and the center of the cylinder body forms a line between the center axis of the sliding vane groove. The included angle γ satisfies 3°≤γ≤10°.

The present disclosure also provides a compressor, which includes the cylinder described in any one of the preceding items.

A cylinder and a compressor provided by the present disclosure have the following beneficial effects:

In the present disclosure, two notches are provided on the cylinder body, and one end of the second notch communicates with the first notch, and the other end communicates with the sliding vane groove, so that the first notch can be used for exhausting, and the second notch effectively forms an inverted structure of a special structure. Corner treatment, which eliminates flanging burrs. This solution can reduce the clearance volume, and the production process is good. It has a significant effect on improving the production off-line rate, improving the energy efficiency of the compressor, and reducing after-sales hidden dangers. Edges and burrs, avoid excessive concentrated stress caused by flanging and burrs, ensure the performance of the produced cylinders and compressors is qualified, and improve the product qualification rate.

Description of drawings

Fig. 1 is the top structural view of the cylinder of an embodiment of the present application;

Fig. 1 a is the partial enlarged view of part A in Fig. 1;

Fig. 2 is the three-dimensional structure diagram of the cylinder of the embodiment of the present application;

Figure 2a is a partial enlarged view of part B of Figure 2;

Fig. 3 is the schematic diagram that adopts cylindrical structure milling cutter to carry out notch machining;

Fig. 4 is a schematic diagram of notch processing by a milling cutter with a spherical head structure;

Fig. 5 is a three-dimensional structure diagram of a cylinder according to another embodiment of the present application;

Figure 5a is a partially enlarged view of part C of Figure 5;

Fig. 5b is a partial enlarged view of part C of Fig. 5 illustrating the imaginary intersecting surface of the first notch and the second notch;

Fig. 6 is the cylinder top view of an embodiment of the present application;

Figure 6a is a D-D sectional view of Figure 6 illustrating the angle between the first notch and the cylinder end face of the present application;

Fig. 6b is a sectional view of E-E of Fig. 6 illustrating the angle between the second notch and the cylinder end face of the present application;

Fig. 7 is a perspective view of the cylinder illustrating the intersection angle between the second notch of the present application and the slide groove and the angle between the chamfer;

Figure 7a is a partially enlarged view of part F of Figure 7;

Fig. 8 is a plan view illustrating the angle between the center of the second notch and the central axis of the slide groove of the present application.

The reference signs are indicated as:

1. Cylinder body; 11. Cylinder end face; 12. Cylinder inner circle; 13. Cylinder axis; 2. Exhaust port; 21. First notch; 22. Second notch; 3. Slide groove; 31. First surface ; 41, the first cylinder; 42, the sphere; 5, the chamfer; 6, the suction hole.

Detailed ways

As shown in Figures 1-8, the present application provides a cylinder, which includes a cylinder body 1, an exhaust port 2 and a sliding vane groove 3, and the exhaust port 2 and the sliding vane groove 3 are both arranged on the cylinder On the main body 1, the exhaust port 2 includes a first notch 21 and a second notch 22, the first notch 21 is set away from the slide slot 3 relative to the second notch 22, and the second notch 22 Relative to the first notch 21, it is arranged close to the slide groove 3, and one end of the second notch 22 communicates with the slide groove 3, and the other end communicates with the first notch 21, and the second notch 22 is located between the first notch 21 and the slide groove 3 . In this application, two notches are provided on the cylinder body, and one end of the second notch 22 communicates with the first notch 21, and the other end communicates with the slide slot, so that the first notch 21 can be used for exhaust, and the second notch 22 is effectively formed The chamfering treatment of the special structure eliminates the flanging burr. This solution can reduce the clearance volume, and the production process is good. It has a significant effect on improving the production off-line rate, improving the energy efficiency of the compressor, and reducing after-sales hidden dangers. As far as the structure is concerned, the first notch used for exhaust in the present disclosure is effectively close to the slide groove, and the chamfer structure (second notch) is processed between the first notch and the slide groove, which can reduce the The clearance volume also effectively eliminates flanging and burrs, thereby reducing the excessive concentrated stress caused by flanging and burrs, ensuring the performance of the produced cylinders and compressors is qualified, and improving the qualified rate of products. The problems of flanging and burr are completely solved, and the clearance volume is reduced.

The two notches define the first notch 21 away from the slide groove, and the second notch 22 near the notch of the slide groove, wherein the first notch 21 is the exhaust passage of the cylinder, and the size of the first notch 21 is the key The parameters cannot be changed arbitrarily. The general design principle is that when ensuring smooth exhaust, it is necessary to make the gap as small as possible to reduce the clearance volume. The second notch 22 is to remove the flanging and burrs generated during the processing of the sliding sheet, so it also needs to be as small as possible, so as to avoid too much increase in the clearance volume. Because part of the high-pressure gas will remain in the chamber corresponding to the clearance volume, it cannot be discharged from the cylinder and flow back to the suction and compression chamber, thereby affecting the energy efficiency of the compressor.

In some embodiments, the volume of the first notch 21 is V _large , the volume of the second notch 22 is V _small , and V _small < V _large ; and/or, the first notch 21 can be used to discharge gas.

Since the first notch is mainly used to exhaust the cylinder, and the second notch is used for effective special chamfering or rounding to eliminate burrs or flanging, its volume should be as small as possible to reduce the clearance volume . Regarding the definition of V _small and V _large , it can be understood that: V _large is the cavity part surrounded by the cylinder end surface, the first notch curved surface, the inner circular surface of the cylinder, and the virtual intersecting surface S of the first notch and the second notch. Volume; where the virtual intersection surface S of the first notch and the second notch is a curved surface formed by scanning the intersection curve of the first notch and the second notch along the central axis of the inner circle of the cylinder, as shown in Figure 5b. Similarly, V _{is defined} as the volume of the cavity surrounded by the cylinder end surface, the second notch surface, the cylinder inner circular surface, the side of the slide slot near the exhaust port, and the intersecting surfaces of the first notch and the second notch .

In some embodiments, _Vsmall < _0.25Vmajor . When satisfying that V _is _small ≤ 0.25 V, it can ensure that no flanging and burrs are generated, and at the same time, it has little impact on the energy efficiency of the compressor.

As shown in Table 1 below, when different sizes are set for the second gap of the compressor, the statistics of the energy efficiency of the compressor in mass production and the production of unqualified products:

Table 1

The _smaller V/V _is , the smaller the burrs are, the more unqualified products will be, and _the _smaller V/V is, the larger the clearance volume of the compressor will be, which will reduce the energy efficiency of the compressor. Therefore, it is preferred that _0.05≤V /V _Larger than or equal to 0.06 is the best, which can not only achieve the highest energy efficiency, but also reduce burrs, increase the number of qualified cylinders and improve the qualified rate; in actual use, the second gap is designed to be as small as possible.

In some embodiments, as shown in FIG. 3 , the first notch 21 is obtained by cutting through the intersection of the first cylinder 41 and the cylinder body 1 . As shown in FIG. 4 , the second notch 22 is obtained by intersecting the cylinder body 1 with a second cylinder (not shown) or sphere 42 . This is a forming method of forming the first notch and the second notch in the present disclosure. The first notch is milled out by the first cylindrical milling cutter, and the second notch can be milled by the second cylindrical or spherical milling cutter or milling cutter head. Mill it out.

The two notches are machined twice with a milling cutter, so the shape of the two notches is the shape obtained by the intersection of two cylinders and the cylinder respectively. This processing method has low cost and high processing efficiency.

Among the two notches, one is obtained by cutting off the intersection of the cylinder and the cylinder, and the other is obtained by cutting off the intersection of the sphere and the cylinder.

FIG. 4 is a schematic diagram of processing the second notch. The second notch is processed by a milling cutter with a spherical head, so the shape of the second notch is the shape obtained by the intersection of the sphere and the cylinder respectively. When the head is processed with a spherical milling cutter, the direction of the cutter and the cylinder can be vertical, so there is no need to tilt the cylinder. This processing method further reduces the cost.

The two gaps, one of which is obtained by crossing the cylinder and the cylinder, and the other is obtained by intersecting the cylinder along a certain trajectory. When the spherical milling cutter cannot guarantee that the processed cylinder is completely free of burrs, some parts can be processed by the spherical milling cutter on a CNC milling machine or machining center. (Whether there is a burr is not determined by the shape of the cutter head, but by the shape of the exhaust port after processing.)

In some embodiments, the diameter of the first cylinder 41 is D1, the diameter of the second cylinder or the sphere 42 is D2, and D1=D2.

When D1=D2, the equipment does not need to switch tools for processing, the tool feed rate is different, and the size of the notch can be formed differently, so the production efficiency is guaranteed during the design, and the man-hour cost is reduced.

In some embodiments, as shown in FIG. 5 and FIG. 5a, the cylinder body 1 includes a cylinder end surface 11, and the second notch 22 intersects the first notch 21 and the cylinder end surface 11 at a first point. P1, the shortest distance between the first point P1 and the sliding vane groove 3 is L _P1 , and L _P1 ≥ 0.2 mm.

The design of the second notch 22 should be as small as possible to ensure that the parts do not produce sharp edges and burrs, but if it is too small, there is a risk of burrs due to errors in equipment processing. When L _P1 ≥ 0.2mm, flanging and burrs will occur when machining the slide groove.

In one embodiment, L _P1 ≥0.4 mm. In view of the processing accuracy of existing semi-finishing parts and precision parts, when L _P1 <0.2mm, unqualified compressor products are more likely to appear. In one embodiment, when L _P1 ≧0.4 mm, there is no defective product in the mass production process. In fact, the larger the distance, the better the deburring effect, but the larger the volume of the second notch, the larger the clearance volume, and the worse the energy efficiency of the compressor.

In some embodiments, as shown in FIG. 5 and FIG. 5a, the cylinder body 1 includes a cylinder inner circle 12, and the second notch 22, the first notch 21 and the cylinder inner circle 12 jointly intersect at the second Two o'clock P2. The sliding vane groove 3 is also provided with a chamfer 5, the chamfering 5 intersects the inner circle 12 of the cylinder at the fourth side S4, and the side where the sliding vane groove 3 intersects with the second notch 22 is The first surface 31, and the distance between the fourth side S4 and the first surface 31 is L _chamfering , the distance between the second point P2 and the first surface 31 is L _P2 ; satisfying L _P2 -L _chamfer ≥ 0.2mm.

The above-mentioned second notch close to the slider groove, the first notch and the inner circle of the cylinder intersect at the second point P2, the distance between the fourth side S4 and the first surface 31 is L _chamfering , the second point P2 and the The distance between the first surfaces 31 is L _P2 and satisfies L _P2 -L _chamfering ≥ 0.2 mm. When L _P2 -L _chamfer ≥ 0.2mm, there will be no flanging and burrs when processing the chamfering of the slide groove (because the chamfering cannot touch a large gap, and burrs will occur if it does, the above formula can be used when there is a chamfer reduce or eliminate burrs in the case of corners).

In one embodiment, L _P2 -L _chamfer ≥ 0.4 mm. In view of the processing accuracy of the existing semi-finishing parts and fine parts, when the L _P2 -L _chamfer < 0.2mm, it is relatively easy to produce unqualified compressor products, when the L _P2 -L _chamfer ≥ 0.4mm, mass production There were no defective products in the process.

In some embodiments, when the first cylinder 41 processes the first notch 21, the angle between the central axis of the first cylinder 41 and the cylinder axis 13 in the longitudinal section of the cylinder is α _big . When the second cylinder is processing the second notch 22, the included angle between the central axis of the second cylinder and the cylinder axis 13 in the longitudinal section of the cylinder is α _small ; satisfying 0°≤α _large - α _small ≤ 15°.

The two gaps are obtained by the intersection and cutting of two cylinders and the cylinder respectively, and the diameters of the two cylinders are the same; and the second gap close to the slide groove, the angle between the cylinder and the axis of the cylinder is α is _small , far away from the slide The angle between the first notch of the slot, the cylinder, and the axis of the cylinder is _α , which satisfies 0°≦α≦ _−α _≦≦ 15°. Generally, due to the existence of the chamfer of the slide groove, it is necessary to ensure that L _P2 is larger than L _P1 , so it will be ensured by a smaller value of _α . When 0° _≤αlarge - _αsmall≤15 °, the design Can better reduce or prevent burrs. As shown in Figure 6-6b.

In some embodiments, the cylinder body 1 includes a cylinder end surface 11, the second notch 22 intersects with the cylinder end surface 11 to form a first side S1, and the slider groove 3 intersects with the cylinder end surface 11 to form a second edge S1. For the two sides S2, the first side S1 and the second side S2 form an intersection angle β, and β≥60°. If the angle of intersection is too small, flanging and burrs are likely to occur. Setting the angle of intersection β within this range can further reduce or prevent the occurrence of burrs.

In some embodiments, as shown in Figure 7a, the cylinder body 1 includes a cylinder inner circle 12, the second notch 22 intersects with the cylinder inner circle 12 to form a third side S3, and the chamfer 5 and the The cylinder inner circles 12 intersect to form a fourth side S4, and the third side S3 and the fourth side S4 form an intersection angle θ, and θ≥60°. If the intersection angle is too small, flanging and burrs are likely to occur, and setting the intersection angle θ within the above range can further reduce or prevent the occurrence of burrs.

In some embodiments, in any section parallel to the cylinder end face 11 , the line between the center of the second notch 22 and the center of the cylinder body 1 and the center of the slide slot 3 An included angle γ is formed between the axes, and 3°≤γ≤10°. As shown in FIG. 8 , when the included angle between the second notch and the slide groove is too small, the solid part of the slide groove close to the second notch 22 will be cut off, which will not be allowed. When the included angle is too large, the volume of the notch cut out is too large, resulting in the problem of large clearance volume of the compressor and low energy efficiency. When 3°≤γ≤10° is satisfied, the comprehensive effect is good, which can not only ensure energy efficiency but also not affect the slide groove, and reduce burrs.

In this disclosure, the above-mentioned first notch 21 and second notch 22 are provided on the semi-finishing parts of the cylinder, which include the suction hole 6 and the exhaust port 2, but do not include the slide groove structure. It is characterized in that the exhaust port of the cylinder is at least composed of Consists of two gaps. If the second notch is not processed when the semi-finished parts are supplied, the corresponding effect can also be achieved by deburring the refined parts of the cylinder, but the cost is high and the parts are easy to be damaged.

The above descriptions are only preferred embodiments of the present disclosure, and are not intended to limit the present disclosure. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present disclosure shall be included in the protection of the present disclosure. within range. The above descriptions are only preferred implementations of the present disclosure. It should be pointed out that those skilled in the art can make several improvements and modifications without departing from the technical principles of the present disclosure. These improvements and modifications It should also be regarded as the protection scope of the present disclosure.

Claims

A cylinder, characterized in that: comprising:

The cylinder body (1), the exhaust port (2) and the sliding vane groove (3), the exhaust port (2) and the sliding vane groove (3) are all arranged on the cylinder body (1), so The exhaust port (2) includes a first notch (21) and a second notch (22), and the first notch (21) is set away from the slide groove (3) relative to the second notch (22) , the second notch (22) is arranged closer to the slide groove (3) relative to the first notch (21), and one end of the second notch (22) communicates with the slide groove (3) , and the other end communicates with the first notch (21), and the second notch (22) is located between the first notch (21) and the slide groove (3).
The cylinder according to claim 1, characterized in that:

The volume of the first gap (21) is V large , the volume of the second gap (22) is V small , and V small <V large .
The cylinder according to claim 1, characterized in that: the first notch (21) is used for exhaust gas.
The cylinder according to claim 2, characterized in that: the first notch (21) is used for exhaust gas.
The cylinder according to claim 2, characterized in that:

V small ≤ 0.25V large .
The cylinder according to claim 1, characterized in that:

The shape of the surface of the first notch (21) is the same as that of a part of the side surface of the first cylinder (41); the shape of the surface of the second notch (22) is the same as that of the second cylinder or sphere (42) The shape of a part of the side surface is the same.
The cylinder according to claim 6, characterized in that:

The diameter of the first cylinder (41) is D1, the diameter of the second cylinder or the sphere (42) is D2, and D1=D2.
The cylinder according to any one of claims 1-7, characterized in that:

The cylinder body (1) includes a cylinder end surface (11), the second notch (22), the first notch (21) and the cylinder end surface (11) jointly intersect at a first point (P1), the second The shortest distance between a point (P1) and the slide slot (3) is L P1 , and L P1 ≥ 0.2mm.
The cylinder according to any one of claims 1-7, characterized in that:

The cylinder body (1) includes a cylinder inner circle (12), and the second notch (22), the first notch (21) and the cylinder inner circle (12) jointly intersect at a second point (P2) , the sliding vane groove (3) is also provided with a chamfer (5), the chamfering (5) intersects the cylinder inner circle (12) at the fourth side (S4), the sliding vane groove ( 3) The side intersecting the second notch (22) is the first surface (31), and the distance between the fourth side (S4) and the first surface (31) is L chamfering , the second The distance between the two points (P2) and the first surface (31) is L P2 ; satisfying L P2 -L chamfering ≥ 0.2mm.
The cylinder according to claim 9, characterized in that: L P1 -L chamfer ≥ 0.4mm.
The cylinder according to claim 6, characterized in that:

In the longitudinal section of the cylinder, the included angle between the central axis of the first cylinder (41) and the cylinder axis (13) is α large , and in the longitudinal section of the cylinder, the central axis of the second cylinder and the cylinder axis The included angle of the cylinder axis (13) is α small , satisfying 0°≤α large -α small≤15 °.
The cylinder according to any one of claims 1-11, characterized in that:

The cylinder body (1) includes a cylinder end surface (11), the second notch (22) intersects with the cylinder end surface (11) to form a first side (S1), and the sliding vane groove (3) and the The cylinder end surfaces (11) intersect to form a second side (S2), and an intersection angle β is formed between the first side (S1) and the second side (S2), which satisfies β≥60°.
The cylinder according to claim 9, characterized in that:

The cylinder body (1) includes a cylinder inner circle (12), the second notch (22) intersects with the cylinder inner circle (12) to form a third side (S3), and the third side (S3) and An intersection angle θ is formed between the fourth sides ( S4 ), which satisfies θ≥60°.
The cylinder according to any one of claims 1-13, characterized in that:

The cylinder body (1) includes a cylinder end face (11), and in any section parallel to the cylinder end face (11), the center of the second notch (22) and the center of the cylinder body (1) An angle γ is formed between the connecting line and the central axis of the sliding vane groove (3), which satisfies 3°≤γ≤10°.
A compressor, characterized by comprising the cylinder described in any one of claims 1-14.