Compressor pump body structure and rotor compressor

Abstract

The utility model relates to a compressor pump body structure and a rotor compressor, the compressor pump body structure comprises an air cylinder, a crankshaft and a sliding block, the air cylinder is internally provided with a compression chamber penetrating through the two ends of the air cylinder, the crankshaft is coaxially arranged in the compression chamber, the peripheral wall of the crankshaft is sleeved with a piston, the piston is eccentrically arranged on the crankshaft, and the piston is located in the compression chamber; the outer side wall, with the largest distance from the axis of the crankshaft, of the piston abuts against the inner circumferential wall of the compression cavity, the outer side wall, with the smallest distance from the axis of the crankshaft, of the piston is concaved inwards in the radial direction to form a sliding groove, the sliding block is arranged in the sliding groove in a sliding mode, a spring is arranged between the inner side wall of the sliding groove and the sliding block, and the side face, away from the crankshaft, of the sliding block is an arc face. The arc surface abuts against the inner circumferential wall of the compression cavity. According to the compressor pump body structure, the sliding groove for the sliding block to stretch out and draw back is formed in the piston, the sintering phenomenon caused by jumping of the sliding block can be effectively prevented, abrasion of the sliding block is effectively reduced, and the service life of a compressor is prolonged.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a compressor pump body structure and a rotor compressor. Background Art

[0002] The working principle of a rotary compressor is that when the motor is energized, its stator coil generates an electromagnetic field. The rotor cuts through the magnetic lines of force, generating power that drives the pump's crankshaft to rotate. The crankshaft then rotates the piston inside the cylinder, acting on the slider, thereby continuously changing the volume of the intake and exhaust chambers inside the cylinder. This way, the cylinder draws in low-temperature, low-pressure gaseous refrigerant, compresses it into high-temperature, high-pressure gaseous refrigerant, and then discharges it out of the pump, repeating the cycle.

[0003] During the production process, the complex machining of the slider grooves on the cylinders leads to certain errors in the clearance between the sliders and the installation margin. As a result, during operation of the compressor, the sliders are prone to jumping up and down under the influence of the high-speed piston, which can cause the sliders to sinter. Slider sintering can easily reduce the cylinder's compression efficiency, thereby shortening the compressor's service life. Utility Model Content

[0004] Based on this, the purpose of the present invention is to overcome the shortcomings of the existing technology and provide a compressor pump body structure and a rotor compressor. According to the compressor pump body structure and the rotor compressor of the embodiment of the present invention, by providing a sliding groove on the piston for the extension and retraction of the slider, sintering caused by the jumping of the slider can be effectively prevented, thereby effectively reducing the wear of the slider and increasing the service life of the compressor.

[0005] In order to achieve the above-mentioned purpose, the first aspect of the embodiment of the present invention provides a compressor pump body structure, including a cylinder, a crankshaft, and a slider. The interior of the cylinder is provided with a compression chamber at both ends thereof. The crankshaft is coaxially arranged in the compression chamber. The outer peripheral wall of the crankshaft is sleeved with a piston. The piston is eccentrically arranged on the crankshaft, and the piston is located in the compression chamber; the outer side wall of the piston with the largest axial distance from the crankshaft abuts against the inner peripheral wall of the compression chamber, and the outer side wall of the piston with the smallest axial distance from the crankshaft is radially concave inward to form a slide groove, and the slider is slidably arranged in the slide groove, and a spring is arranged between the inner side wall of the slide groove and the slider, and the side of the slider away from the crankshaft is a circular arc surface, which abuts against the inner peripheral wall of the compression chamber.

[0006] The piston is pressed against the piston rod and the piston is pressed against the piston groove, and the piston is pressed against the piston rod, thereby preventing the piston from sliding.

[0007] As an embodiment, one end of the spring is fixedly arranged on the inner side wall of the sliding groove, and the other end of the spring is fixedly arranged on the side wall of the sliding block facing the crankshaft.

[0008] As an embodiment, the radial length of the sliding groove is 10 mm, the length of the spring is 9.6 mm, and the radial length of the slider is 11.5 mm.

[0009] As an embodiment, an eccentric joint is sleeved on the outer peripheral wall of the crankshaft, and the eccentric joint is eccentrically arranged between the crankshaft; the radial cross-section of the piston is a circular ring structure, and the piston is sleeved on the outer peripheral wall of the eccentric joint.

[0010] As an embodiment, a first nail groove is recessed radially inward on the outer wall where the eccentric joint is at the largest distance from the axis of the crankshaft, and a second nail groove is recessed radially outward on the inner wall of the piston at a position corresponding to the first nail groove, and the first nail groove and the second nail groove are fixed by a pin connection.

[0011] As an embodiment, the groove depth of the first nail groove is 3 mm, the groove depth of the second nail groove is 3 mm, and the length of the pin is 6 mm.

[0012] As an embodiment, the upper end face of the cylinder is connected to an upper bearing, and the lower end face of the cylinder is connected to a lower bearing or a middle partition. The upper bearing is provided with an upper through hole along the axial direction for the crankshaft to pass through and which is in clearance with the crankshaft. The lower bearing or the middle partition is provided with a lower through hole along the axial direction for the crankshaft to pass through and which is in clearance with the crankshaft. It can be understood that in these embodiments, the upper bearing on the upper end face of the cylinder and the lower bearing or the middle partition on the lower end face of the cylinder respectively cover the upper and lower openings of the compression chamber, and are respectively provided with only an upper through hole and a lower through hole for the crankshaft to pass through, and can also serve as a limiting structure for the upper and lower end faces of the piston and the slider, thereby limiting the displacement of the slider in the axial direction, effectively preventing the slider from jumping up and down during the sliding of the slide groove.

[0013] As an embodiment, the two axial end surfaces of the piston and the two axial end surfaces of the slider are flush with the two axial end surfaces of the cylinder respectively.

[0014] As an embodiment, an air intake passage communicating with the compression chamber is formed through the outer wall of the cylinder radially inward, and one of the end faces of the cylinder is recessed to form an exhaust notch communicating with the compression chamber.

[0015] A second aspect of the present invention provides a rotary compressor comprising the compressor pump structure of any of the aforementioned embodiments. The rotary compressor of the present invention effectively prevents sintering caused by slider movement by providing a slide groove on the piston for slider extension and retraction, thereby effectively reducing slider wear and extending the compressor's service life.

[0016] In order to better understand and implement the present invention, the present invention is described in detail below with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is one of the structural diagrams of the compressor pump body structure of an embodiment of the utility model;

[0018] Figure 2 This is the second structural diagram of the compressor pump body structure of an embodiment of the present utility model;

[0019] Figure 3 This is the third structural diagram of the compressor pump body structure of an embodiment of the present utility model;

[0020] Figure 4 for Figure 2 The cross-sectional diagram along the AA direction is shown;

[0021] Figure 5 A schematic structural diagram of a crankshaft of a compressor pump structure according to an embodiment of the present invention;

[0022] Figure 6 This is a structural diagram of the cylinder of the compressor pump body structure of an embodiment of the utility model;

[0023] Figure 7 This is an exploded schematic diagram of the piston and slider of the compressor pump body structure of an embodiment of the present utility model.

[0024] Description of reference numerals:

[0025] 10. Cylinder; 11. Compression chamber; 12. Intake channel; 13. Exhaust notch; 20. Crankshaft; 21. Eccentric joint; 22. First nail groove; 30. Piston; 31. Slide groove; 32. Second nail groove; 33. Pin; 40. Slider; 50. Spring. DETAILED DESCRIPTION

[0026] To further illustrate various embodiments, this utility model is provided with accompanying drawings. These drawings form part of the disclosure of this utility model and are primarily used to illustrate the embodiments and, in conjunction with the relevant description in the specification, to explain the operating principles of the embodiments. By referring to these drawings, those skilled in the art will be able to understand other possible implementations and the advantages of this utility model.

[0027] In related technologies, the complex machining of the slider grooves on the cylinders leads to certain errors in factors such as the clearance between the sliders and the installation margin. As a result, during compressor operation, the sliders are prone to bouncing up and down under the influence of the high-speed piston, leading to the undesirable phenomenon of slider sintering. Slider sintering can easily reduce the compression efficiency of the cylinder and, in turn, shorten the service life of the compressor.

[0028] In view of this, an embodiment of the present invention provides a compressor pump body structure and a compressor. According to the compressor pump body structure and the rotor compressor of the embodiment of the present invention, by providing a sliding groove on the piston for the extension and retraction of the slider, sintering caused by the jumping of the slider can be effectively prevented, thereby effectively reducing the wear of the slider and improving the service life of the compressor.

[0029] See also Figures 1 to 7; A first aspect of an embodiment of the present invention provides a compressor pump body structure, including a cylinder 10, a crankshaft 20, and a slider 40. The interior of the cylinder 10 is provided with a compression chamber 11 at both ends thereof, the crankshaft 20 is coaxially arranged in the compression chamber 11, and a piston 30 is sleeved on the outer peripheral wall of the crankshaft 20. The piston 30 is eccentrically arranged on the crankshaft 20, and the piston 30 is located in the compression chamber 11; the outer side wall of the piston 30 with the largest axial distance from the crankshaft 20 abuts against the inner peripheral wall of the compression chamber 11, and the outer side wall of the piston 30 with the smallest axial distance from the crankshaft 20 is radially inwardly recessed to form a slide groove 31, the slider 40 is slidably arranged in the slide groove 31, a spring 50 is provided between the inner side wall of the slide groove 31 and the slider 40, and the side of the slider 40 away from the crankshaft 20 is a circular arc surface, which abuts against the inner peripheral wall of the compression chamber 11.

[0030] It can be understood that the outermost side of the piston 30 abuts the inner circumferential wall of the compression chamber 11, and the length direction of the slider 40 is in the same radial direction as the outermost side of the piston 30. In other words, the outermost side of the piston 30 and the outer side of the slider 40 abut against both sides of the compression chamber 11, so that the piston 30 and the slider 40 can continuously change the volume of the intake and exhaust chambers during the circumferential rotation driven by the crankshaft 20, thereby achieving the effect of compressing the gas.

[0031] In addition, an upper bearing is connected to the upper end surface of the cylinder 10, and a lower bearing or a middle partition is connected to the lower end surface of the cylinder 10. The upper bearing is provided with an upper through-hole extending in the axial direction for the crankshaft 20 to pass through and having a clearance fit with the crankshaft 20. The lower bearing or the middle partition is provided with a lower through-hole extending in the axial direction for the crankshaft 20 to pass through and having a clearance fit with the crankshaft 20. In other words, the upper bearing on the upper end surface of the cylinder 10 and the lower bearing or the middle partition on the lower end surface of the cylinder 10 respectively cover the upper and lower openings of the compression chamber 11 and are provided with only an upper through-hole and a lower through-hole for the crankshaft 20 to pass through, respectively. They also serve as limiting structures for the upper and lower end surfaces of the piston 30 and the slider 40, thereby limiting the displacement of the slider 40 in the axial direction and effectively preventing the slider 40 from bouncing up and down during the sliding process in the slide groove 31. It can be understood that the compressor pump body structure of the present invention can be divided into a single-cylinder pump body structure or a double-cylinder pump body structure according to the number of cylinders 10. When the number of cylinders 10 is one, the lower end face of the cylinder 10 is connected to a lower bearing; when the number of cylinders 10 is two, the lower end face of the cylinder 10 is connected to a middle partition, and a cylinder 10, a piston 30, and a slider 40 are symmetrically arranged at the upper and lower ends of the middle partition relative to the axis of the crankshaft 20. That is to say, when the number of cylinders 10 is two, the compressor pump body structure has two compression structures for compressing gaseous refrigerant, and these two compression structures are symmetrically arranged relative to the axis of the crankshaft 20.

[0032] Therefore, according to the compressor pump body structure of the embodiment of the present invention, the design of providing the slide groove 31 on the cylinder 10 is cancelled, and instead the slide groove 31 for the slider 40 to complain is provided on the piston 30, and the slider 40 is radially telescopically provided in the slide groove 31, and the slider 40 is connected to the inner side of the slide groove 31 through the spring 50, and the outer side wall of the piston 30 with the largest distance from the axis of the crankshaft 20 abuts against the inner circumferential wall of the compression chamber 11 of the cylinder 10, and the arc surface of the outer side of the slider 40 abuts against the inner circumferential wall of the compression chamber 11; in this way, when the crankshaft 20 drives the piston 3 When the piston 30 and the slider 40 rotate circumferentially, the outermost side of the piston 30 always abuts against the compression chamber 11. Due to the eccentric setting of the piston 30, the slider 40 slides radially in the slide groove 31 of the piston 30 during the circumferential rotation, thereby achieving the effect of compressing the gas. Moreover, under the limiting action of the limiting components on the upper and lower end surfaces of the cylinder 10, the slider 40 can only slide in the radial direction and will not jump up and down. This effectively prevents sintering caused by the jumping of the slider 40, thereby reducing the wear of the slider 40 and increasing the service life of the compressor.

[0033] In some embodiments of the present invention, one end of the spring 50 is fixedly mounted on the inner sidewall of the chute 31, and the other end of the spring 50 is fixedly mounted on the sidewall of the slider 40 facing the crankshaft 20. In these embodiments, the two axial end surfaces of the piston 30 and the two axial end surfaces of the slider 40 are flush with the two axial end surfaces of the cylinder 10. Furthermore, an intake passage 12 is formed radially inwardly through the outer sidewall of the cylinder 10, connecting to the compression chamber 11. One end surface of the cylinder 10 is recessed to form an exhaust notch 13, connecting to the compression chamber 11.

[0034] In some embodiments of the present invention, an eccentric joint 21 is sleeved on the outer circumferential wall of the crankshaft 20, and the eccentric joint 21 is eccentrically disposed with respect to the crankshaft 20. The radial cross-section of the piston 30 is an annular structure, and the piston 30 is sleeved on the outer circumferential wall of the eccentric joint 21. Furthermore, in these embodiments, a first nail groove 22 is radially inwardly recessed on the outer side wall where the distance between the eccentric joint 21 and the axis of the crankshaft 20 is greatest. A second nail groove 32 is radially outwardly recessed on the inner side wall of the piston 30 at a position corresponding to the first nail groove 22. The first nail groove 22 and the second nail groove 32 are connected and fixed by a pin 33. It can be understood that in these embodiments, by eccentrically setting the eccentric joint 21 on the crankshaft 20 and designing the piston 30 as a circular ring structure, the piston 30 and the eccentric joint 21 can be easily combined, and the two are limitedly connected by the pin 33 to prevent the piston 30 from being displaced relative to the axial direction of the crankshaft 20, ensuring that the piston 30 can only rotate in the circumferential direction.

[0035] The following combination Figures 1 to 7 A specific embodiment of the compressor pump body structure according to the present invention is described in detail. It is worth noting that this embodiment is merely an exemplary description and cannot be construed as a limitation to the present invention.

[0036] The compressor pump body structure of this embodiment is a single-cylinder 10 pump body structure, which includes a cylinder 10, a crankshaft 20, a slider 40, an upper bearing, and a lower bearing. The interior of the cylinder 10 is provided with a compression chamber 11 at both ends thereof. The crankshaft 20 is coaxially arranged in the compression chamber 11. The outer peripheral wall of the crankshaft 20 is sleeved with a piston 30. The piston 30 is eccentrically arranged on the crankshaft 20, and the piston 30 is located in the compression chamber 11; the outer side wall of the piston 30 with the largest distance from the axis of the crankshaft 20 abuts against the inner peripheral wall of the compression chamber 11, and the piston 30 with the smallest distance from the axis of the crankshaft 20 The small outer wall is radially recessed inward to form a slide groove 31, and the slider 40 is slidably arranged in the slide groove 31. A spring 50 is arranged between the inner wall of the slide groove 31 and the slider 40. The side of the slider 40 away from the crankshaft 20 is an arc surface, and the arc surface abuts against the inner circumferential wall of the compression chamber 11; the upper bearing and the lower bearing are respectively penetrated by an upper through hole and a lower through hole for the crankshaft 20 to pass through. The upper bearing and the lower bearing are respectively arranged on the upper and lower end faces of the cylinder 10, and are used to cover the upper and lower openings of the compression chamber 11, so as to limit the upper and lower ends of the piston 30 and the slider 40.

[0037] Specifically, in this embodiment, one end of the spring 50 is fixedly mounted on the inner sidewall of the chute 31, and the other end of the spring 50 is fixedly mounted on the sidewall of the slider 40 facing the crankshaft 20. The two axial end surfaces of the piston 30 and the two axial end surfaces of the slider 40 are flush with the two axial end surfaces of the cylinder 10. Furthermore, an intake passage 12 is formed radially inwardly through the outer sidewall of the cylinder 10, connecting to the compression chamber 11. The upper end surface of the cylinder 10 is recessed to form an exhaust notch 13, connecting to the compression chamber 11.

[0038] In this embodiment, the radial length of the sliding groove 31 is 10 mm, the length of the spring 50 is 9.6 mm, and the radial length of the slider 40 is 11.5 mm.

[0039] In addition, in this embodiment, an eccentric joint 21 is sleeved on the outer circumferential wall of the crankshaft 20, and the eccentric joint 21 is eccentrically arranged with respect to the crankshaft 20. The radial cross-section of the piston 30 is an annular structure, and the piston 30 is sleeved on the outer circumferential wall of the eccentric joint 21. Furthermore, in these embodiments, a first nail groove 22 is recessed radially inward on the outer side wall where the distance between the eccentric joint 21 and the axis of the crankshaft 20 is greatest, and a second nail groove 32 is recessed radially outward on the inner side wall of the piston 30 at a position corresponding to the first nail groove 22. The first nail groove 22 and the second nail groove 32 are connected and fixed by a pin 33. The groove depth of the first nail groove 22 is 3 mm, the groove depth of the second nail groove 32 is 3 mm, and the length of the pin 33 is 6 mm.

[0040] The following combination Figures 1 to 7 A specific embodiment of the compressor pump body structure according to the present invention is described in detail. It is worth noting that this embodiment is merely an exemplary description and cannot be construed as a limitation to the present invention.

[0041] The compressor pump body structure of this embodiment is a dual-cylinder 10 pump body structure, which includes a cylinder 10, a crankshaft 20, a slider 40, an upper bearing, a middle diaphragm, and a lower bearing. There are two cylinders 10, located on the upper and lower end surfaces of the middle diaphragm, respectively. The upper bearing is provided on the upper cylinder 10, and the lower bearing is provided on the lower cylinder 10, thereby forming a pump body structure with two compression chambers 11. For ease of explanation, the upper cylinder 10 is used as an example below:

[0042] The interior of the cylinder 10 is provided with a compression chamber 11 at both ends thereof, the crankshaft 20 is coaxially arranged in the compression chamber 11, and the outer peripheral wall of the crankshaft 20 is sleeved with a piston 30, the piston 30 is eccentrically arranged on the crankshaft 20, and the piston 30 is located in the compression chamber 11; the outer side wall of the piston 30 at the largest axial distance from the crankshaft 20 abuts against the inner peripheral wall of the compression chamber 11, and the outer side wall of the piston 30 at the smallest axial distance from the crankshaft 20 is radially recessed inward to form a slide groove 31, the slider 40 is slidably arranged in the slide groove 31, and a spring 50 is provided between the inner side wall of the slide groove 31 and the slider 40, and the side of the slider 40 away from the crankshaft 20 is a circular arc surface, which abuts against the inner peripheral wall of the compression chamber 11.

[0043] Specifically, in this embodiment, one end of the spring 50 is fixedly mounted on the inner sidewall of the chute 31, and the other end of the spring 50 is fixedly mounted on the sidewall of the slider 40 facing the crankshaft 20. The two axial end surfaces of the piston 30 and the two axial end surfaces of the slider 40 are flush with the two axial end surfaces of the cylinder 10. Furthermore, an intake passage 12 is formed radially inwardly through the outer sidewall of the cylinder 10, connecting to the compression chamber 11. The upper end surface of the cylinder 10 is recessed to form an exhaust notch 13, connecting to the compression chamber 11.

[0044] In this embodiment, the radial length of the sliding groove 31 is 10 mm, the length of the spring 50 is 9.6 mm, and the radial length of the slider 40 is 11.5 mm.

[0045] In addition, in this embodiment, an eccentric joint 21 is sleeved on the outer circumferential wall of the crankshaft 20, and the eccentric joint 21 is eccentrically arranged with respect to the crankshaft 20. The radial cross-section of the piston 30 is an annular structure, and the piston 30 is sleeved on the outer circumferential wall of the eccentric joint 21. Furthermore, in these embodiments, a first nail groove 22 is recessed radially inward on the outer side wall where the distance between the eccentric joint 21 and the axis of the crankshaft 20 is greatest, and a second nail groove 32 is recessed radially outward on the inner side wall of the piston 30 at a position corresponding to the first nail groove 22. The first nail groove 22 and the second nail groove 32 are connected and fixed by a pin 33. The groove depth of the first nail groove 22 is 3 mm, the groove depth of the second nail groove 32 is 3 mm, and the length of the pin 33 is 6 mm.

[0046] It is worth mentioning that the crankshaft 20 of this embodiment is symmetrically provided with two eccentric joints 21 in the axial direction compared to the axis, so as to facilitate the installation and fixation of the two pistons 30. The structure of the lower cylinder 10, piston 30, and slider 40 is basically the same as the structure of the upper cylinder 10, piston 30, and slider 40. It is just that the installation method of the piston 30 and slider 40 is symmetrically arranged compared to the axis. Therefore, the lower cylinder 10 will not be elaborated.

[0047] A second aspect of the present invention provides a rotary compressor comprising the compressor pump structure of any of the aforementioned embodiments. The rotary compressor of this embodiment of the present invention effectively prevents sintering caused by the bouncing of the slider 40 by providing a slide groove 31 on the piston 30 for the slider 40 to extend and retract, thereby effectively reducing wear of the slider 40 and extending the compressor's service life.

[0048] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "left", "right", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, they cannot be understood as limiting the present invention.

[0049] The above-described embodiments represent only a few implementations of the present invention. While the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the compressor pump structure and compressor of the present invention. It should be noted that those skilled in the art will be able to make various modifications and improvements without departing from the scope of the present invention, and all such modifications and improvements fall within the scope of protection of the present invention.

Claims

1. A compressor pump body structure, characterized in that: The invention comprises a cylinder, a crankshaft and a slider, wherein the interior of the cylinder is provided with a compression chamber at both ends thereof, the crankshaft is coaxially arranged in the compression chamber, the outer peripheral wall of the crankshaft is sleeved with a piston, the piston is eccentrically arranged on the crankshaft, and the piston is located in the compression chamber; the outer side wall at which the piston has the largest axial distance from the crankshaft abuts against the inner peripheral wall of the compression chamber, and the outer side wall at which the piston has the smallest axial distance from the crankshaft is radially recessed inward to form a groove, and the slider is slidably arranged in the groove, a spring is arranged between the inner side wall of the groove and the slider, and the side of the slider away from the crankshaft is an arc surface, which abuts against the inner peripheral wall of the compression chamber.

2. The compressor pump body structure according to claim 1, characterized in that: One end of the spring is fixedly arranged on the inner side wall of the sliding groove, and the other end of the spring is fixedly arranged on the side wall of the sliding block facing the crankshaft.

3. The compressor pump body structure according to claim 2, characterized in that: The radial length of the sliding groove is 10 mm, the length of the spring is 9.6 mm, and the radial length of the slider is 11.5 mm.

4. The compressor pump body structure according to claim 1, characterized in that: An eccentric joint is sleeved on the outer peripheral wall of the crankshaft, and the eccentric joint is eccentrically arranged between the crankshaft; the radial cross section of the piston is a circular ring structure, and the piston is sleeved on the outer peripheral wall of the eccentric joint.

5. The compressor pump body structure according to claim 4, characterized in that: A first nail groove is recessed radially inward on the outer side wall where the eccentric joint is at the largest distance from the axis of the crankshaft, and a second nail groove is recessed radially outward at a position on the inner side wall of the piston corresponding to the first nail groove. The first nail groove and the second nail groove are fixed by a pin connection.

6. The compressor pump body structure according to claim 5, characterized in that: The groove depth of the first nail groove is 3 mm, the groove depth of the second nail groove is 3 mm, and the length of the pin is 6 mm.

7. The compressor pump body structure according to claim 1, characterized in that: The upper end surface of the cylinder is connected to an upper bearing, and the lower end surface of the cylinder is connected to a lower bearing or a middle partition. The upper bearing is penetrated along the axial direction with an upper through hole for the crankshaft to pass through and with a clearance fit with the crankshaft. The lower bearing or the middle partition is penetrated along the axial direction with a lower through hole for the crankshaft to pass through and with a clearance fit with the crankshaft.

8. The compressor pump body structure according to claim 1, characterized in that: The two axial end surfaces of the piston and the two axial end surfaces of the slider are flush with the two axial end surfaces of the cylinder respectively.

9. The compressor pump body structure according to claim 1, characterized in that: An air inlet passage communicating with the compression chamber is formed through the outer wall of the cylinder radially inwardly, and one of the end surfaces of the cylinder is recessed to form an exhaust notch communicating with the compression chamber.

10. A rotary compressor, characterized in that: The compressor pump body structure comprises the compressor pump body structure according to any one of claims 1 to 9.

Images