Cylinder structure and compressor

Abstract

The utility model provides a kind of cylinder structure and compressor, the cylinder structure includes cylinder, cylinder wall and piston, the cylinder wall is fixed in the end of the cylinder;The cylinder has compression cavity;The piston is located in the compression cavity;The lateral wall of the compression cavity is sequentially provided with sliding vane slot and spring hole along the radial direction of the cylinder;The groove wall of the sliding vane slot intake side is provided with the oil supply groove and the oil guide groove that are connected, the oil guide groove is used to communicate with the high-pressure device outside, and oil can be provided to the oil supply groove.The cylinder structure is designed with oil supply groove and oil guide groove on the intake side of sliding vane slot, the structure can introduce high-pressure force on the intake side of sliding vane slot, improve the unbalanced force state of sliding vane, reduce the friction between sliding vane and cylinder, and effectively avoid the situation that sliding vane and piston are separated due to excessive friction.

Description

Technical Field

[0001] This utility model relates to the field of compressors, and in particular to a cylinder structure and a compressor. Background Technology

[0002] During actual operation of the compressor, the vane will tilt to a certain extent as the piston rotates in the compression chamber. In particular, when the tilt angle of the vane is close to 180°, the asymmetrical force on both sides of the connection between the vane and the piston is significantly larger.

[0003] In the area near the cylinder inner wall and at the tail of the vane groove, there is a risk of dry friction between the vane and the cylinder inner wall. This will greatly increase the friction force on the vane, which can easily cause the vane to separate from the piston and affect the normal operation of the compressor.

[0004] Therefore, for those skilled in the art, how to design a cylinder structure that reduces the friction between the sliding vane and the outer wall of the cylinder is a technical problem that urgently needs to be solved. Utility Model Content

[0005] To address the technical problems existing in the prior art, the purpose of this utility model is to provide a cylinder structure and a compressor. The cylinder structure is designed with an oil supply groove and an oil inlet groove on the air inlet side of the vane groove. This structure can introduce high pressure force on the air inlet side of the vane groove, improve the unbalanced force state of the vane, reduce the friction between the vane and the cylinder, and effectively prevent the vane from separating from the piston due to excessive friction.

[0006] To achieve the above objectives, this utility model provides a cylinder structure, characterized in that the cylinder structure includes a cylinder, a cylinder wall, and a piston, the cylinder wall being fixed to the end of the cylinder; the cylinder having a compression chamber; and the piston being located within the compression chamber.

[0007] The sidewall of the compression chamber is provided with a vane groove and a spring hole in sequence along its own radial direction; the groove wall on the air inlet side of the vane groove is provided with a connected oil supply groove and an oil priming groove, the oil priming groove is used to communicate with an external high-pressure device and can supply oil to the oil supply groove.

[0008] Optionally, there are two oil inlet tanks, which are located at opposite ends of the oil supply tank.

[0009] Optionally, the oil supply groove extends through the vane groove along the axial direction of the cylinder.

[0010] Optionally, the oil inlet groove extends radially along the cylinder.

[0011] Optionally, the end of the vane groove has a through hole extending along the axial direction of the cylinder, the through hole being located outside the cylinder wall; one end of the oil inlet groove is connected to the oil supply groove, and the other end of the oil inlet groove is connected to the through hole.

[0012] Optionally, the cross-sectional shape of the oil supply tank is square, circular, or elliptical, and / or the cross-sectional shape of the oil intake tank is square, circular, or elliptical.

[0013] Optionally, the dimension of the oil supply groove along the radial direction of the cylinder is greater than or equal to half of the compressor eccentricity and less than or equal to the compressor eccentricity.

[0014] Optionally, in the radial direction of the cylinder, the distance between the oil supply groove and the inner wall of the compression chamber is greater than or equal to one-third of the compressor eccentricity and less than or equal to the compressor eccentricity.

[0015] Optionally, the oil inlet tank has at least one of the following features:

[0016] Along the axial direction of the cylinder, the maximum height of the oil inlet groove is greater than one-tenth of the cylinder height;

[0017] The minimum radial distance between the end of the oil inlet groove away from the oil supply groove and the edge of the cylinder wall is greater than 1 mm;

[0018] The height of the cylinder wall in its own axial direction is greater than 0.5 mm.

[0019] To achieve the above objectives, this utility model also provides a compressor, including the cylinder structure described in any one of the claims, wherein the piston and the vane divide the compression chamber into an intake chamber and an exhaust chamber, and the oil supply groove and the oil inlet groove are both disposed on the side of the vane groove corresponding to the intake chamber.

[0020] This utility model provides a cylinder structure and a compressor. The cylinder structure includes a cylinder, a cylinder wall, and a piston, with the cylinder wall fixed to the end of the cylinder. The cylinder has a compression chamber, and the piston is located inside the compression chamber. A vane groove and a spring hole are sequentially arranged radially on the side wall of the compression chamber. A connected oil supply groove and an oil inlet groove are provided on the groove wall on the air inlet side of the vane groove. The oil inlet groove is used to communicate with the outside and can supply oil to the oil supply groove.

[0021] The cylinder structure has an oil supply groove on the air intake side of the vane groove that can provide high pressure. At the same time, considering that the high pressure requirements cannot be met by supplying oil to the oil supply groove through the gap, an oil guide groove connected to the oil supply groove is also designed on the air intake side of the vane groove. The oil guide groove can realize the direct connection between the oil supply groove and the external high pressure area.

[0022] Since the overall structure of the cylinder changes only slightly, this design does not significantly affect the cylinder's strength. Furthermore, this structure introduces high-pressure force on the intake side of the vane slot, improving the unbalanced force state of the vane, buffering and reducing the normal pressure between the cylinder and the vane, thereby reducing friction between the vane and the cylinder. This effectively prevents the vane from detaching from the piston due to excessive friction. Simultaneously, introducing high-pressure oil into the oil supply slot improves the lubrication between the intake-side vane and the vane slot, further preventing vane detachment from the piston and ensuring smooth compressor operation. Attached Figure Description

[0023] Figure 1 This is a top view of the cylinder structure in a preferred embodiment of the present invention;

[0024] Figure 2 for Figure 1 An enlarged view of part a;

[0025] Figure 3 for Figure 1 A schematic diagram of the axial cross-sectional structure of line AA in the middle;

[0026] Figure 4 for Figure 3 Enlarged view of part b in the middle.

[0027] The reference numerals in the attached figures are explained as follows:

[0028] Cylinder 1; Cylinder wall 2; Compression chamber 3; Sliding vane groove 4; Spring hole 5; Oil supply groove 6; Oil inlet groove 7; Through hole 8. Detailed Implementation

[0029] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. The advantages and features of the present invention will become clearer from the following description. It should be noted that the drawings are all in a very simplified form and use non-precise proportions, and are only used to facilitate and clarify the illustration of the embodiments of the present invention.

[0030] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0031] In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0032] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "fixation," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between the components; they can refer to a direct connection or a connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0033] In the following description, a rotary compressor is used as an example to illustrate that the cylinder structure of this invention can reduce the friction between the cylinder and the sliding vane during movement, ensuring the efficient and stable operation of the compressor. However, those skilled in the art should understand that this cylinder structure can also be applied to other types of compressors.

[0034] The cylinder structure and compressor proposed in this utility model will be described in detail below with reference to the accompanying drawings and preferred embodiments.

[0035] Figure 1 This is a top view of the compressor pump body in a preferred embodiment of the present invention. Figure 2 for Figure 1 Enlarged view of part a. Figure 3 for Figure 1 A schematic diagram of the axial cross-section of line AA. Figure 4 for Figure 3 Enlarged view of part b in the middle.

[0036] like Figures 1-4 As shown, this utility model provides a cylinder structure, which includes a cylinder 1, a cylinder wall 2, and a piston (not shown). The cylinder wall 2 is fixed to the end of the cylinder 1, and a compression chamber 3 is provided inside the cylinder 1. The piston 3 is mounted on the eccentric part of the compressor shaft and is located inside the compression chamber 3.

[0037] Furthermore, a sliding vane groove 4 and a spring hole 5 are sequentially arranged radially on the side wall of the compression chamber 3. A sliding vane is installed in the sliding vane groove 4, and a spring is installed in the spring hole 5. One end of the sliding vane abuts against the spring, and the other end abuts against the outer wall of the piston through the spring. A connected oil supply groove 6 and an oil inlet groove 7 are provided on the groove wall on the air inlet side of the sliding vane groove 4. The oil inlet groove 7 is used to communicate with an external high-pressure device and can supply oil to the oil supply groove 6.

[0038] More specifically, the vane can reciprocate within the vane groove 4 under the push of the piston. The vane is connected to the piston, and during its movement, the vane can abut against the inner wall of the vane groove 4. The piston and the vane together divide the cylinder 1 into an intake chamber and an exhaust chamber.

[0039] This utility model also provides a compressor, which includes the cylinder structure described in any one of the claims. In the cylinder structure, the cylinder 1 is provided with an intake port communicating with the intake chamber and an exhaust port (not shown) communicating with the exhaust chamber. The intake port and exhaust port are used to draw in and output gas, respectively. A piston is used to compress the gas and output the compressed gas from the exhaust port. The oil supply groove 6 and the oil priming groove 7 are both located on the side of the vane groove 4 corresponding to the intake chamber; that is, the oil supply groove 6 and the oil priming groove 7 are both located on the intake side of the vane groove 4. The intake side of the vane groove 4 refers to the side corresponding to the intake chamber of the cylinder 1.

[0040] This application provides a cylinder structure and a compressor. The cylinder structure has an oil supply groove 6 on the air inlet side of the vane groove 4 that can provide high pressure force. At the same time, considering that the high pressure requirement cannot be met by supplying oil to the oil supply groove through the gap, an oil guide groove 7 connected to the oil supply groove 6 is also designed on the air inlet side of the vane groove 4. The oil guide groove 7 can realize the direct connection between the oil supply groove 6 and the external high pressure area.

[0041] Since the overall structure of cylinder 1 changes only slightly, this design will not significantly affect the strength of cylinder 1. Furthermore, this structure can introduce high-pressure force on the intake side of the vane groove 4, which can improve the unbalanced force state of the vane, buffer and reduce the normal pressure between cylinder 1 and the vane, thereby reducing the friction between the vane and cylinder 1. This can effectively prevent the vane from separating from the piston due to excessive friction. Simultaneously, introducing high-pressure oil into the oil supply groove 6 can better improve the lubrication state between the intake-side vane and the vane groove 4, further preventing the vane from separating from the piston.

[0042] This application does not limit the number of oil inlet grooves 7. Those skilled in the art can set the number, shape and position of oil inlet grooves 7 on cylinder 1 according to the specific type of compressor, the internal structure of the compressor, the environmental conditions in which the compressor is actually used and other factors.

[0043] In a preferred embodiment, there are two oil inlet grooves 7, located at opposite ends of the oil supply groove 6. This arrangement not only facilitates the machining of the oil inlet grooves 7 and simplifies the structure of the cylinder 1, but also allows for the simultaneous supply of high-pressure oil to both ends of the oil supply groove 6. This increases the inflow of high-pressure oil, thereby increasing the high-pressure force on the end of the vane and reducing the friction between the vane and the cylinder wall.

[0044] Preferably, the oil supply groove 6 extends through the vane groove 4 along the axial direction of the cylinder 1, so that high pressure force can be provided on the entire cross section of the vane, further reducing the friction between the vane and the inner wall of the cylinder.

[0045] In a preferred embodiment, the oil inlet groove 7 extends radially along the cylinder 1, which shortens the length of the oil inlet groove 7 and allows the high-pressure oil to flow directly into the oil supply groove 6 through the oil inlet groove 7, thereby reducing the pressure drop generated when the high-pressure oil flows through the oil inlet groove 7.

[0046] In other alternative embodiments, the oil inlet trough 7 may also be set at a certain angle relative to the oil supply trough 6. This application does not limit the extension direction of the oil inlet trough 7.

[0047] This application does not limit the shape of the oil supply tank 6 and the oil inlet tank 7. The cross-sectional shape of the oil supply tank 6 can be square, circular, or elliptical, or other shapes as required. Similarly, the cross-sectional shape of the oil inlet tank 7 can be square, circular, or elliptical, or other shapes as required.

[0048] Furthermore, the height of the oil supply groove 6 along its own axis is the same as the height of the cylinder 1 along its own axis, that is to say, the oil supply groove 6 is connected along the axis of the cylinder 1.

[0049] Reference Figure 3 As shown, in the preferred embodiment, the radial dimension W1 of the oil supply groove 6 along the cylinder 1 (i.e., the width W1 of the oil supply groove 6) is greater than or equal to half of the compressor eccentricity and less than or equal to the compressor eccentricity, i.e., 1 / 2 compressor eccentricity ≤ W1 ≤ compressor eccentricity. This setting ensures, on the one hand, that the size of the oil supply groove 6 can guarantee that the sliding vane can receive a sufficiently large high-pressure force; on the other hand, it avoids the oil supply groove 6 being too large, which would significantly reduce the strength of the cylinder.

[0050] Reference Figure 3 As shown, in the preferred embodiment, the distance L1 between the oil supply groove 6 and the inner wall of the compression chamber 3 in the radial direction of the cylinder 1 is greater than or equal to one-third of the compressor eccentricity and less than or equal to the compressor eccentricity, i.e., 1 / 3 compressor eccentricity ≤ L1 ≤ compressor eccentricity, so that the high-pressure oil can act on the required position of the vane (e.g., the tail area of ​​the vane), further reducing the friction between the vane and the inner wall of the cylinder, which can effectively prevent the vane from separating from the piston.

[0051] More preferably, the oil inlet tank 7 has at least one of the following features:

[0052] Along the axial direction of cylinder 1, the maximum height H1 of the oil inlet groove 7 is greater than or equal to one-tenth of the height H2 of cylinder 1, i.e., H1≥1 / 10H2, to ensure that the high-pressure oil has a sufficient inflow.

[0053] Reference Figure 3 and Figure 4 As shown, the minimum radial distance L4 between the end of the oil inlet groove 7 furthest from the oil supply groove 6 and the edge of the cylinder wall 2 is greater than or equal to 1 mm, i.e., L4 ≥ 1 mm. In other words, the difference between the distance L3 between the end of the oil inlet groove 7 and the end of the oil supply groove 6 and the distance L2 between the meshing area of ​​the cylinder wall 2 and the cylinder 1 and the end of the oil supply groove 6 is greater than or equal to 1 mm, i.e., L3 - L2 ≥ 1 mm, so that the oil inlet groove 7 has a certain length in its own extension direction.

[0054] In addition, the height H3 of the cylinder wall 2 in its own axial direction is preferably greater than 0.5mm, that is, H3>0.5mm, to ensure that the oil sump 7 has a certain height, so as to accommodate a sufficient volume of high-pressure oil and ensure the stable operation of the compressor.

[0055] Table 1 shows the cylinder structure with slots on the intake side (refer to...). Figure 1 and Figure 3 Comparison table of optimization effects of cylinder structures with and without slotted intake sides during the simulation verification stage.

[0056]

[0057] Table 1 Comparison of Optimization Effects

[0058] As shown in Table 1, opening the oil supply groove 6 and the oil inlet groove 7 on the intake side of the cylinder can significantly reduce the contact force between the intake-side vane and the cylinder 1, without significantly increasing the contact force between the exhaust-side vane and the cylinder 1. Therefore, slotting on the intake side of the cylinder 1 can reduce the friction between the vane and the cylinder on the intake side, thereby preventing the vane and piston from separating during operation.

[0059] In summary, this utility model provides a cylinder structure and a compressor. The cylinder structure has an oil supply groove 6 on the air inlet side of the vane groove 4 that can provide high pressure. At the same time, considering that the high pressure requirement cannot be met by supplying oil to the oil supply groove 6 through the gap, an oil guide groove 7 connected to the oil supply groove 6 is also designed on the air inlet side of the vane groove 4. The oil guide groove 7 can realize the direct connection between the oil supply groove 6 and the external high pressure area.

[0060] Since the overall structure of cylinder 1 changes only slightly, this design will not significantly affect the strength of cylinder 1. Furthermore, this structure can introduce high-pressure force on the intake side of the vane groove 4, which can improve the unbalanced force state of the vane, buffer and reduce the normal pressure between cylinder 1 and the vane, thereby reducing the friction between the vane and cylinder 1. This can effectively prevent the vane from separating from the piston due to excessive friction. Simultaneously, introducing high-pressure oil into the oil supply groove 6 can better improve the lubrication state between the intake-side vane and the vane groove 4, further preventing the vane from separating from the piston and ensuring stable compressor operation.

[0061] The above description is only a description of the preferred embodiment of the present utility model and is not intended to limit the scope of the present utility model in any way. Any changes or modifications made by those skilled in the art based on the above disclosure shall fall within the protection scope of the present utility model.

Claims

1. A cylinder structure, characterized in that, The cylinder structure includes a cylinder, a cylinder wall, and a piston, with the cylinder wall fixed to the end of the cylinder; the cylinder has a compression chamber; and the piston is located within the compression chamber. The sidewall of the compression chamber is provided with a vane groove and a spring hole in sequence along its own radial direction; the groove wall on the air inlet side of the vane groove is provided with a connected oil supply groove and an oil priming groove, the oil priming groove is used to communicate with an external high-pressure device and can supply oil to the oil supply groove.

2. The cylinder structure as described in claim 1, characterized in that, There are two oil inlet tanks, which are located at opposite ends of the oil supply tank.

3. The cylinder structure as described in claim 1, characterized in that, The oil supply groove extends through the vane groove along the axial direction of the cylinder.

4. The cylinder structure as described in claim 2, characterized in that, The oil inlet groove extends radially along the cylinder.

5. The cylinder structure as described in claim 4, characterized in that, The end of the vane groove has a through hole extending along the axial direction of the cylinder, and the through hole is located outside the cylinder wall; one end of the oil inlet groove is connected to the oil supply groove, and the other end of the oil inlet groove is connected to the through hole.

6. The cylinder structure as described in any one of claims 1 to 5, characterized in that, The cross-sectional shape of the oil supply tank is square, circular, or elliptical, and / or the cross-sectional shape of the oil intake tank is square, circular, or elliptical.

7. The cylinder structure as described in any one of claims 1 to 5, characterized in that, The dimension of the oil supply groove along the radial direction of the cylinder is greater than or equal to half of the compressor eccentricity and less than or equal to the compressor eccentricity.

8. The cylinder structure as described in any one of claims 1 to 5, characterized in that, In the radial direction of the cylinder, the distance between the oil supply groove and the inner wall of the compression chamber is greater than or equal to one-third of the compressor eccentricity and less than or equal to the compressor eccentricity.

9. The cylinder structure as described in any one of claims 1 to 5, characterized in that, The oil inlet tank has at least one of the following characteristics: Along the axial direction of the cylinder, the maximum height of the oil inlet groove is greater than or equal to one-tenth of the cylinder height; The minimum radial distance between the end of the oil inlet groove away from the oil supply groove and the edge of the cylinder wall is greater than or equal to 1 mm; The height of the cylinder wall in its own axial direction is greater than 0.5 mm.

10. A compressor, characterized in that, The cylinder structure includes any one of claims 1 to 9, wherein the piston and the slide plate divide the compression chamber into an intake chamber and an exhaust chamber, and the oil supply groove and the oil inlet groove are both disposed on the side of the slide plate groove corresponding to the intake chamber.

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