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 has compression cavity inside;The piston is located in the compression cavity;The lateral wall of the compression cavity is sequentially provided with vane slot and spring hole along the radial direction of the cylinder, the slot wall of the vane slot intake side is provided with the high-pressure oil groove and the oil guide groove that are connected, the oil guide groove is used to communicate with the spring hole, and for providing oil liquid to the high-pressure oil groove.The cylinder structure is designed with high-pressure oil groove and oil guide groove on the intake side of vane slot, the structure can introduce high-pressure force on the intake side of vane slot, improve the unbalanced force state of vane, reduce the friction between vane and cylinder, which can effectively avoid the situation that 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] Rotary compressors are a common type of refrigeration compressor widely used in household appliances such as air conditioners. A rotary compressor typically includes a sealed housing, a motor, a compressor shaft, a cylinder structure, and an exhaust system. The device primarily uses a motor to drive the compressor shaft to rotate, which in turn drives a piston in the cylinder to compress and output high-temperature, high-pressure gas. The cylinder has an intake port and an exhaust port. The cylinder structure is used to draw in gas through the intake port, compress the gas through the piston, and then output the high-temperature, high-pressure gas through the exhaust port.

[0003] During actual compressor operation, the blades tilt to a certain extent as the piston rotates within the compression chamber. This tilt angle is particularly pronounced when it approaches 180°, resulting in significantly larger asymmetrical forces on both sides of the blades. In the area near the cylinder wall and at the tail of the blade slots, there is a risk of dry friction between the blades and the cylinder wall. This greatly increases the frictional force on the blades, making them highly susceptible to separation from the piston and affecting the compressor's normal operation.

[0004] Therefore, for those skilled in the art, how to design a cylinder structure that reduces the friction between the blades 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 a high-pressure oil groove and an oil inlet groove on the air inlet side of the blade groove. This structure can introduce high pressure force on the air inlet side of the blade groove, improve the unbalanced force state of the blade, reduce the friction between the blade and the cylinder, and effectively avoid the situation where the blade separates from the piston due to excessive friction.

[0006] To achieve the above objectives, this utility model provides a cylinder structure, which includes a cylinder, a cylinder wall, and a piston, wherein the cylinder has a compression chamber; and the piston is located within the compression chamber.

[0007] The side wall of the compression chamber is provided with a blade groove and a spring hole in sequence along the radial direction of the cylinder. The groove wall on the air inlet side of the blade groove is provided with a high-pressure oil groove and an oil priming groove that are connected to each other. The oil priming groove is used to communicate with the spring hole and to supply oil to the high-pressure oil groove.

[0008] Optionally, the high-pressure oil groove extends through the blade groove along the axial direction of the cylinder.

[0009] Optionally, the oil inlet groove extends radially along the cylinder.

[0010] Optionally, the central axis of the oil inlet groove coincides with the central axis of the spring hole.

[0011] Optionally, the cross-sectional shape of the high-pressure oil tank is square, circular, or elliptical.

[0012] Optionally, the cross-sectional shape of the oil inlet groove is square, circular, or elliptical.

[0013] Optionally, the dimension of the high-pressure oil sump 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 high-pressure oil 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 cross-sectional area of ​​the oil inlet groove is greater than or equal to half the cross-sectional area of ​​the high-pressure oil groove, and less than or equal to half the cross-sectional area of ​​the spring hole.

[0016] 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 blades divide the compression chamber into an intake chamber and an exhaust chamber, and the high-pressure oil groove and the oil inlet groove are both disposed on the side of the blade groove corresponding to the intake chamber.

[0017] This utility model provides a cylinder structure and a compressor. The cylinder structure includes a cylinder, a cylinder wall, and a piston, with a compression chamber inside the cylinder. The piston is located inside the compression chamber. A vane groove and a spring hole are sequentially arranged along the radial direction of the cylinder on the side wall of the compression chamber. A high-pressure oil groove and an oil inlet groove are connected on the groove wall on the air inlet side of the vane groove. The oil inlet groove communicates with the spring hole and supplies oil to the high-pressure oil groove.

[0018] The cylinder structure features a high-pressure oil groove on the intake side of the vane slot, which can provide high-pressure force. Simultaneously, considering that supplying oil to the high-pressure oil groove through a gap cannot meet the high-pressure requirements, an oil inlet groove connected to the high-pressure oil groove is also designed on the intake side of the vane slot. This oil inlet groove can achieve direct connection between the high-pressure oil groove and the external high-pressure area through a spring hole.

[0019] 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 blade slots, improving the unbalanced force state of the blades, buffering and reducing the normal pressure between the cylinder and the blades, thereby reducing friction between the blades and the cylinder. This effectively prevents the blades from detaching from the piston due to excessive friction. Simultaneously, introducing high-pressure oil into the high-pressure oil grooves improves the lubrication between the intake-side blades and the blade slots, further preventing blade detachment from the piston. Attached Figure Description

[0020] Figure 1 This is a top view of the compressor pump body in a preferred embodiment of the present invention;

[0021] Figure 2 for Figure 1 An enlarged view of part a;

[0022] Figure 3 for Figure 1 A schematic diagram of the axial cross-sectional structure of line AA in the middle;

[0023] Figure 4 for Figure 3 Enlarged view of part b in the middle.

[0024] The reference numerals in the attached figures are explained as follows:

[0025] Cylinder 1; Cylinder wall 2; Compression chamber 3; Vane groove 4; Spring hole 5; High-pressure oil groove 6; Oil priming groove 7. Detailed Implementation

[0026] 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.

[0027] 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.

[0028] In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0029] 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.

[0030] 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 blades 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.

[0031] 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.

[0032] 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.

[0033] 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 located at both axial ends of the cylinder 1, and the cylinder 1 has a compression chamber 3. The piston is mounted on the eccentric part of the compressor shaft and is located in the compression chamber 3.

[0034] Furthermore, a vane groove 4 and a spring hole 5 are sequentially arranged along the radial direction of the cylinder 1 on the side wall of the compression chamber 3. A vane is installed in the vane groove 4, and a spring is installed in the spring hole 5. One end of the vane abuts against the spring, and the other end always abuts against the outer wall of the piston under the action of the spring. A high-pressure oil groove 6 and an oil inlet groove 7 are connected on the groove wall on the air inlet side of the vane groove 4. The oil inlet groove 7 is used to communicate with the spring hole 5 and to supply oil to the high-pressure oil groove 6.

[0035] More specifically, the blades can reciprocate within the blade groove 4 under the push of the piston. The blades are connected to the piston, and during their movement, they can abut against the inner wall of the blade groove 4. Together, the piston and the blades divide the cylinder 1 into an intake chamber and an exhaust chamber.

[0036] 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 high-pressure oil groove 6 and the oil priming groove 7 are both provided on the side of the blade groove 4 corresponding to the intake chamber, that is, the high-pressure oil groove 6 and the oil priming groove 7 are provided on the intake side of the blade groove 4. The intake side of the blade groove 4 refers to the side where the intake chamber of the cylinder 1 is located.

[0037] This application provides a cylinder structure and a compressor. The cylinder structure has a high-pressure oil groove 6 on the air inlet side of the blade groove 4, which can provide high pressure force. At the same time, considering that the high pressure requirement cannot be met by supplying oil to the high-pressure oil groove through the gap, an oil guide groove 7 connected to the high-pressure oil groove 6 is also designed on the air inlet side of the blade groove 4. The oil guide groove 7 can achieve direct connection between the high-pressure oil groove 6 and the external high-pressure area through the spring hole 5.

[0038] 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 blade groove 4, which can improve the unbalanced force state of the blades, buffer and reduce the normal pressure between cylinder 1 and the blades, thereby reducing the friction between the blades and cylinder 1. This can effectively prevent the blades from detaching from the piston due to excessive friction. Simultaneously, introducing high-pressure oil into the high-pressure oil groove 6 can better improve the lubrication state between the intake-side blades and the blade groove 4, further preventing the blades from detaching from the piston.

[0039] More specifically, by connecting the two ends of the oil inlet groove 7 to the high-pressure oil groove 6 and the spring hole 5 respectively, the structure of the cylinder 1 can be simplified, and the inflow of high-pressure oil can be increased, thereby providing a sufficient volume of high-pressure oil to the high-pressure oil groove 6 through the spring hole 5 and the oil inlet groove 7.

[0040] 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.

[0041] Preferably, the high-pressure oil groove 6 extends through the blade groove 4 along the axial direction of the cylinder 1, so that high pressure force can be provided on the cross-section of the blade, further reducing the friction between the blade and the inner wall of the cylinder.

[0042] 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 high-pressure oil groove 6 through the spring hole 5 and the oil inlet groove 7, thereby reducing the pressure drop generated when the high-pressure oil flows through the oil inlet groove 7.

[0043] In other alternative embodiments, the oil inlet groove 7 may also be set at a certain angle relative to the high pressure oil groove 6 and the spring hole 5. This application does not limit the extension direction of the oil inlet groove 7.

[0044] In a further preferred embodiment, the central axis of the oil inlet groove 7 coincides with the central axis of the spring hole 5. At this time, the end of the oil inlet groove 7 is located in the middle position of the high pressure oil groove 6, and the oil inlet groove 7 can simultaneously provide high pressure oil to the upper and lower parts of the high pressure oil groove 6.

[0045] This application does not limit the shape of the high-pressure oil tank 6 and the oil inlet tank 7. The cross-sectional shape of the high-pressure oil tank 6 can be square or circular, or it can also be semi-circular or elliptical, or other shapes. Similarly, the cross-sectional shape of the oil inlet tank 7 can be square or circular, or it can also be semi-circular or elliptical, or other shapes.

[0046] Furthermore, the height of the high-pressure oil 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 high-pressure oil groove 6 runs through the cylinder 1 along its axis.

[0047] Reference Figure 3 As shown, in the preferred embodiment, the radial dimension W1 of the high-pressure oil groove 6 along the cylinder 1 (i.e., the width W1 of the high-pressure oil 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 blades receive a sufficiently large high-pressure force, reducing the friction between the blades and the cylinder wall; on the other hand, it also prevents the high-pressure oil groove 6 from being too large, which could affect the strength of the cylinder.

[0048] Reference Figure 3 As shown, in the preferred embodiment, the distance L1 between the high-pressure oil 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, that is, 1 / 3 compressor eccentricity ≤ L1 ≤ compressor eccentricity. At this time, the high-pressure oil can act on the required position of the blade (e.g., the tail area of ​​the blade), further reducing the friction between the blade and the inner wall of the cylinder, which can effectively prevent the blade from separating from the piston.

[0049] More preferably, the cross-sectional area of ​​the oil inlet groove 7 is greater than or equal to half the cross-sectional area of ​​the high-pressure oil groove 6, and less than or equal to half the cross-sectional area of ​​the spring hole 5, i.e., 1 / 2S 高压油槽 ≤S引油油槽 ≤1 / 2S 弹簧孔 This configuration not only ensures a smaller pressure drop in the high-pressure oil within the oil inlet sump 7, but also prevents the cross-sectional area of ​​the oil inlet sump 7 from being too large, which could affect the strength of the cylinder 1 itself, thereby ensuring the stable operation of the compressor.

[0050] 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.

[0051]

[0052] Table 1 Comparison of Optimization Effects

[0053] As shown in Table 1, opening high-pressure oil groove 6 and oil inlet groove 7 on the intake side of the cylinder can significantly reduce the contact force between the intake side vanes and the cylinder, without significantly increasing the contact force between the exhaust side vanes and the cylinder. Therefore, slotting on the intake side of cylinder 1 can reduce the friction between the vanes and the cylinder on the intake side, preventing the vanes and piston from separating during operation.

[0054] In summary, this utility model provides a cylinder structure and compressor. The cylinder structure has a high-pressure oil groove 6 on the intake side of the blade groove 4, which can provide high-pressure force. At the same time, considering that supplying oil to the high-pressure oil groove 6 through the gap cannot meet the high-pressure requirements, an oil guide groove 7 connected to the high-pressure oil groove 6 is also designed on the intake side of the blade groove 4. The oil guide groove 7 can achieve direct connection between the high-pressure oil groove 6 and the external high-pressure area through the spring hole 5.

[0055] 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 blade groove 4, which can improve the unbalanced force state of the blades, buffer and reduce the normal pressure between cylinder 1 and the blades, thereby reducing the friction between the blades and cylinder 1. This can effectively prevent the blades from detaching from the piston due to excessive friction. Simultaneously, introducing high-pressure oil into the high-pressure oil groove 6 can better improve the lubrication state between the intake-side blades and the blade groove 4, further preventing the blades from detaching from the piston.

[0056] 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, and the cylinder has a compression chamber; the piston is located in the compression chamber. The side wall of the compression chamber is provided with a blade groove and a spring hole in sequence along the radial direction of the cylinder. The groove wall on the air inlet side of the blade groove is provided with a high-pressure oil groove and an oil priming groove that are connected to each other. The oil priming groove is used to communicate with the spring hole and to supply oil to the high-pressure oil groove.

2. The cylinder structure as described in claim 1, characterized in that, The high-pressure oil groove extends through the blade groove along the axial direction of the cylinder.

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

4. The cylinder structure as described in claim 3, characterized in that, The central axis of the oil inlet groove coincides with the central axis of the spring hole.

5. The cylinder structure as described in claim 1, characterized in that, The cross-sectional shape of the high-pressure oil tank is square, circular, or elliptical.

6. The cylinder structure as described in claim 1, characterized in that, The cross-sectional shape of the oil inlet groove is square, circular, or elliptical.

7. The cylinder structure as described in any one of claims 1 to 6, characterized in that, The radial dimension of the high-pressure oil sump along 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 6, characterized in that, In the radial direction of the cylinder, the distance between the high-pressure oil 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 6, characterized in that, The cross-sectional area of ​​the oil inlet groove is greater than or equal to half the cross-sectional area of ​​the high-pressure oil groove, and less than or equal to half the cross-sectional area of ​​the spring hole.

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

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