The sealing structure of the compressor and the compressor

Abstract

This invention provides a sealing structure for a compressor and the compressor itself. The sealing structure includes a cylinder, a piston, a crankshaft, and a cylinder head. The cylinder head has an exhaust port. The crankshaft includes an eccentric portion. The piston is fitted onto the eccentric portion and located inside the cylinder. The eccentric portion has at least one protrusion on the side near the exhaust port. The pistons cooperate to seal the exhaust port. The thickness t of the piston is related to its inner and outer diameters, allowable contact pressure, and the operating pressure difference of the compressor. This invention rationally designs the relationship between the piston thickness and its inner and outer diameters to match pistons of appropriate thickness to compressors of different sizes, achieving good overall performance without increasing compressor costs.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, specifically to a compressor sealing structure and a compressor. Background Technology

[0002] In a rolling rotor compressor, the minimum sealing distance between the piston and the exhaust port directly affects the clearance volume and exhaust resistance. Moving the exhaust port outwards ensures the minimum sealing distance, but it increases the size of the cylinder's DV port (beveled opening), increasing the clearance volume and exhaust resistance. To reduce clearance volume and exhaust resistance, the exhaust port needs to be moved inwards towards the cylinder center, but this results in insufficient sealing distance between the piston end face and the exhaust port. Conventional solutions typically increase the piston thickness (t≥5mm) to ensure the sealing distance, but this leads to:

[0003] (1) Increased cost of piston materials;

[0004] (2) Increased piston inertia affects the compressor's start-stop performance;

[0005] (3) The increased counterweight affects the reliability of the compressor. Utility Model Content

[0006] In view of the problems in the prior art, the purpose of this utility model is to provide a sealing structure and compressor for a compressor, so as to match the appropriate piston thickness for compressors of different sizes, and improve the overall performance of the compressor without increasing the cost of the compressor.

[0007] This utility model provides a sealing structure for a compressor. The sealing structure includes a cylinder, a piston, a crankshaft, and a cylinder head. The cylinder head has an exhaust port. The crankshaft includes an eccentric portion. The piston is sleeved on the eccentric portion and located inside the cylinder. The eccentric portion has at least one protrusion on the side near the exhaust port. The piston cooperates with the cylinder head to achieve [the desired effect].

[0008] The vent hole is sealed;

[0009] The thickness t of the piston satisfies: in,

[0010] D0 is the outer diameter of the piston;

[0011] Di is the inner diameter of the piston;

[0012] p contact The allowable contact pressure of the piston;

[0013] The maximum working pressure differential inside the compressor pump body, as described in P.

[0014] In some embodiments, the piston thickness t satisfies: 2.5mm ≤ t ≤ 5mm.

[0015] In some embodiments, the inner radius of the cylinder is Rc, the radius of the exhaust port is r, the distance between the center of the exhaust port and the center of the cylinder head is L, the radial width of the protrusion is m, and the wall thickness of the piston is t, wherein m and t satisfy: t + m > R c +rL.

[0016] In some embodiments, the gap between the end face of the protrusion near the exhaust port and the end face of the cylinder head near the exhaust port is C, where C ranges from 0.01mm to 0.02mm.

[0017] In some embodiments, the protrusion is provided with an anti-wear layer on the side near the vent.

[0018] In some embodiments, the thickness of the wear-resistant layer is 10 μm to 20 μm.

[0019] In some embodiments, the protrusion is arc-shaped or trapezoidal.

[0020] In some embodiments, the difference between the coefficient of thermal expansion of the piston and the coefficient of thermal expansion of the crankshaft is less than or equal to 10%.

[0021] In some embodiments, the cylinder head includes an upper cylinder head and a lower cylinder head, the eccentric portion located on one side of the upper cylinder head is a first end face, the eccentric portion located on one side of the lower cylinder head is a second end face, and the protrusion is provided on one side of the first end face and / or on one side of the second end face.

[0022] This utility model embodiment also provides a compressor, including the sealing structure of the compressor as described above.

[0023] The sealing structure and compressor provided by this utility model have the following advantages:

[0024] This invention provides pistons of appropriate thickness for compressors of different sizes by rationally designing the relationship between piston thickness, piston inner and outer diameters, piston allowable pressure, and the working pressure difference of the compressor. This improves the overall performance of the compressor without increasing piston cost. Attached Figure Description

[0025] Other features, objects, and advantages of this invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings.

[0026] Figure 1 This is a schematic diagram of the sealing structure of a compressor provided in an embodiment of the present invention;

[0027] Figure 2 A schematic diagram of a crankshaft provided in an embodiment of the present invention is shown;

[0028] Figure 3 A schematic diagram of a crankshaft sleeved with a piston is shown according to an embodiment of the present invention;

[0029] Figure label:

[0030] 10 cylinders

[0031] 20 Pistons

[0032] 30 crankshaft

[0033] 31 Long shaft section

[0034] 32. Eccentric part

[0035] 33 Short shaft section

[0036] 34. Protrusion

[0037] 41 Exhaust port Detailed Implementation

[0038] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that the present invention will be comprehensive and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted.

[0039] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics represented in connection with that embodiment or example, which are included in at least one embodiment or example of this application. Furthermore, the specific features, structures, materials, or characteristics represented may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate different embodiments or examples represented in this application, as well as features of different embodiments or examples.

[0040] Furthermore, the terms "first" and "second" are used for illustrative purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the representation of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0041] It should be further understood that the terms "comprising" or "including" indicate the presence of a feature, step, operation, element, component, item, kind, and / or group, but do not exclude the presence, occurrence, or addition of one or more other features, steps, operations, elements, components, items, kinds, and / or groups. The terms "or" and "and / or" as used herein are interpreted as inclusive, or mean any one or any combination thereof. Therefore, "A, B, or C" or "A, B, and / or C" means "any one of the following: A; B; C; A and B; A and C; B and C; A, B, and C." Exceptions to this definition only arise when a combination of elements, functions, steps, or operations is inherently mutually exclusive in some way.

[0042] To address the problems in the prior art, this utility model provides a sealing structure for a compressor. The sealing structure includes a cylinder, a piston, a crankshaft, and a cylinder head. The cylinder head has an exhaust port. The crankshaft includes an eccentric portion. The piston is sleeved on the eccentric portion and located inside the cylinder. The eccentric portion has at least one protrusion on the side near the exhaust port. The piston cooperates with the piston to seal the exhaust port. The thickness t of the piston satisfies:

[0043]

[0044] Wherein, D0 is the outer diameter of the piston;

[0045] Di is the inner diameter of the piston;

[0046] p contact The allowable contact pressure of the piston;

[0047] The maximum working pressure differential inside the compressor pump body, as described in P.

[0048] By rationally designing the relationship between piston thickness and piston inner and outer diameters, piston allowable pressure, and compressor working pressure difference, pistons of appropriate thickness can be provided for compressors of different sizes, thereby improving the overall performance of the compressor without increasing piston costs.

[0049] The sealing structure of the compressor provided in the embodiments of this utility model will be explained in detail below with reference to the accompanying drawings.

[0050] Figure 1 A schematic diagram of the sealing structure of a compressor provided in an embodiment of the present invention is shown; Figure 2 A schematic diagram of a crankshaft provided in an embodiment of the present invention is shown; Figure 3 A schematic diagram of a crankshaft sleeved with a piston according to an embodiment of the present invention is shown. Figures 1 to 3As shown, the sealing structure includes a cylinder 10, a piston 20, a crankshaft 30, and a cylinder head. The cylinder head has an exhaust port 41. The crankshaft 30 includes an eccentric portion 32 (the crankshaft 30 also includes a long shaft portion 31 and a short shaft portion 32). The piston 20 is fitted onto the eccentric portion 32 and located inside the cylinder 10. The eccentric portion 32 has a protrusion 34 on the side near the exhaust port 41. The protrusion 34 cooperates with the piston 20 to seal the exhaust port 41. The sealing of the exhaust port 41 here is to prevent the exhaust port 41 from connecting the inner cavity and outer cavity of the piston 20, thereby causing gas leakage. That is to say, when the piston 20 passes through the exhaust port 41, the end face of the piston 20 must completely cover the exhaust port 41 when it cooperates with the protrusion 34 of the eccentric portion 32; otherwise, the inner cavity and outer cavity (high and low pressure chambers) of the piston 20 will connect, resulting in internal leakage. It should be noted that the area formed by the piston 20 and the eccentric part 32 is the inner cavity of the piston 20, and the area formed by the piston 20 and the cylinder 10 is the outer cavity of the piston 20.

[0051] The end face seal of piston 20 requires contact pressure to counteract the force generated by the gas pressure. The area where the gas pressure acts is the projected area of ​​the rotor end face, πD0. 2 / 4, the sealing contact area is annular area Where D0 is the outer diameter of the piston, D i is the inner diameter of the piston.

[0052] When the contact pressure meets At that time, the relationship between the piston thickness t and the given information is obtained. Among them, P contact The allowable contact pressure of piston 20, when it exceeds P contact When the value is reached, the piston will deform; △P is the maximum working pressure difference inside the compressor pump body, which is the pressure difference between the suction pressure and the discharge pressure of the compressor pump body.

[0053] The above formula rationally designs the relationship between piston thickness and piston inner and outer diameters, piston allowable pressure, and compressor working pressure difference, providing pistons of reasonable thickness for compressors of different sizes. This can improve the overall performance of the compressor without increasing piston cost.

[0054] In some embodiments, the thickness t of the piston 20 satisfies: 2.5mm ≤ t ≤ 5mm. For example, t can be 3mm, 3.5mm, 4mm, and 4.5mm, but is not limited thereto.

[0055] In some embodiments, such as Figure 1 and Figure 2As shown, the inner radius of cylinder 10 is Rc, the radius of exhaust port 41 is r, the distance between the center of exhaust port 41 and the center of cylinder head is L, and the crankshaft 30 is provided with a protrusion 34 on the side near exhaust port 41. The radial width of protrusion 34 is m, the wall thickness of piston 20 is t, and the width of protrusion 34 is m, satisfying: t + m > Rc. c +rL. By designing a protrusion 34 with a suitable radial width and a piston thickness t with a suitable thickness, the piston 20 and the protrusion 34 work together to seal the exhaust port 41, reduce compressor leakage, and improve compressor performance.

[0056] Furthermore, such as Figure 3 As shown, in some embodiments, the gap between the end face of the protrusion 34 near the exhaust port 41 and the end face of the cylinder head near the exhaust port 41 is C, where C ranges from 0.01 mm to 0.02 mm. By limiting the gap between the end face of the protrusion and the end face of the cylinder head, it is ensured that the protrusion 34 and the piston 20 can completely seal the exhaust port 41 in the axial direction of the compressor, preventing communication between the inner and outer cavities of the piston 20.

[0057] Furthermore, in some embodiments, an anti-wear layer is provided on the side of the protrusion 34 near the exhaust port 41. By providing an anti-wear layer on the side of the protrusion 34 near the exhaust port 41, the wear resistance of the protrusion 34 is improved, the wear of the protrusion 34 is reduced, and the frictional wear between the piston end face and the cylinder head mating surface is effectively reduced. Furthermore, in some embodiments, the material of the anti-wear layer is CrN; the thickness of the anti-wear layer is 10μm to 20μm; and the hardness of the anti-wear layer is greater than or equal to 2000HV.

[0058] Furthermore, in some embodiments, the protrusion 34 is arc-shaped or trapezoidal. For example, as shown... Figure 1 As shown, the protrusion 34 is arc-shaped. However, the shape of the protrusion 34 is not limited to this and can be set according to actual needs.

[0059] Furthermore, in some embodiments, the difference between the thermal expansion coefficient of the piston 20 and the thermal expansion coefficient of the crankshaft 30 is less than or equal to 10%. Controlling the difference in thermal expansion coefficients between the crankshaft 30 and the piston 20 within a certain range can prevent changes in the gap C between the end face of the protrusion 34 and the end face of the piston 20 during high-temperature deformation, thus avoiding excessive wear between the protrusion 34 and the cylinder head.

[0060] In some embodiments, the cylinder head includes an upper cylinder head and a lower cylinder head. The eccentric portion 32 is located on one side of the upper cylinder head as a first end face, and the eccentric portion 32 is located on one side of the lower cylinder head as a second end face. The protrusion 34 is disposed on one side of the first end face and / or on one side of the second end face. Depending on whether the compressor is an upper-discharge (upper cylinder head exhaust), lower-discharge (lower cylinder head exhaust), or dual-discharge (both upper and lower cylinder heads exhaust), the position and number of the protrusion 34 on the end face of the eccentric portion 32 are reasonably set.

[0061] This utility model embodiment also provides a compressor, including the sealing structure of the compressor as described above. The compressor including the sealing structure described above achieves all the technical effects of the sealing structure described above, which will not be elaborated further here.

[0062] To further explore the technical effects of the compressor obtained according to the embodiments of this utility model, a performance comparison was made between existing compressors and the compressor provided by the embodiments of this utility model. Table 1 shows the performance comparison results between existing compressors and the compressor provided by the embodiments of this utility model.

[0063] Table 1. Performance Comparison Between Existing Compressors and Compressors Provided in the Embodiments of this Utility Model

[0064]

[0065] According to Table 1, the piston thickness of the compressor in the prior art is 4.5mm, while the piston thickness provided in this embodiment is 3.2mm. Therefore, compared with the compressor in the prior art, the piston thickness of the compressor in this embodiment is reduced by about 30%, resulting in less piston material and lower piston cost. Furthermore, the clearance volume of the compressor in this embodiment is 0.09cc, which is 25% less than that of the compressor in the prior art, thereby improving the volumetric efficiency of the compressor, increasing the discharge capacity, and reducing energy consumption. Furthermore, the required balance weight of the compressor in this embodiment is 20g, which is 29% less than that of the compressor in the prior art. Reducing the balance weight can reduce starting and braking energy consumption and optimize the stability of the compressor. Furthermore, the inertial force of the compressor in this embodiment is 83N at 6000rpm, which is 50% less than that of the compressor in this embodiment. This reduction in compressor inertial force can increase the reliability of the compressor. Therefore, compared with the compressors in the prior art, the compressor piston in this embodiment has lower cost, smaller clearance volume, smaller counterweight, and smaller inertial force, resulting in better overall performance.

[0066] The sealing structure and compressor provided by this utility model have the following advantages:

[0067] This invention provides pistons of appropriate thickness for compressors of different sizes by rationally designing the relationship between piston thickness, piston inner and outer diameters, piston allowable pressure, and the working pressure difference of the compressor. This improves the overall performance of the compressor without increasing piston cost.

[0068] The above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of the present invention. It should not be construed that the specific implementation of the present invention is limited to these descriptions. For those skilled in the art, various simple deductions or substitutions can be made without departing from the concept of the present invention, and all such modifications and substitutions should be considered within the protection scope of the present invention.

Claims

1. A sealing structure for a compressor, characterized in that, The sealing structure includes a cylinder, a piston, a crankshaft, and a cylinder head. The cylinder head has an exhaust port. The crankshaft includes an eccentric portion. The piston is fitted onto the eccentric portion and located inside the cylinder. The eccentric portion has at least one protrusion on the side near the exhaust port. The piston cooperates with the piston to seal the exhaust port. The thickness t of the piston satisfies: in, D0 is the outer diameter of the piston; Di is the inner diameter of the piston; p contact The allowable contact pressure of the piston; The maximum working pressure differential inside the pump body of the compressor described in P.

2. The sealing structure of the compressor according to claim 1, characterized in that, The thickness t of the piston satisfies: 2.5mm≤t≤5mm.

3. The sealing structure of the compressor according to claim 1 or 2, characterized in that, The cylinder has an inner radius of Rc, the exhaust port has a radius of r, the distance between the center of the exhaust port and the center of the cylinder head is L, the protrusion has a radial width of m, and the piston has a wall thickness of t. The values ​​of m and t satisfy: t + m > Rc. c +rL.

4. The sealing structure of the compressor according to claim 1, characterized in that, The gap between the end face of the protrusion near the exhaust port and the end face of the cylinder head near the exhaust port is C, and the range of C is 0.01mm to 0.02mm.

5. The sealing structure of the compressor according to claim 1, characterized in that, The protrusion is provided with an anti-wear layer on the side near the vent.

6. The sealing structure of the compressor according to claim 5, characterized in that, The thickness of the wear-resistant layer is 10μm to 20μm.

7. The sealing structure of the compressor according to claim 1, characterized in that, The protrusion is in the shape of an arc or a trapezoid.

8. The sealing structure of the compressor according to claim 1, characterized in that, The difference between the coefficient of thermal expansion of the piston and the coefficient of thermal expansion of the crankshaft is less than or equal to 10%.

9. The sealing structure of the compressor according to claim 1, characterized in that, The cylinder head includes an upper cylinder head and a lower cylinder head. The eccentric portion is located on one side of the upper cylinder head and is called the first end face. The eccentric portion is located on one side of the lower cylinder head and is called the second end face. The protrusion is located on one side of the first end face and / or on one side of the second end face.

10. A compressor, characterized in that, Includes the sealing structure of the compressor as described in any one of claims 1 to 9.

Images