Sealing structure of compressor and compressor
By adding a protrusion to the eccentric part of the crankshaft of the rolling rotor compressor to cooperate with the piston, and by rationally designing the sealing structure, the problem of insufficient sealing of the exhaust port was solved, the minimum sealing distance under different dimensions was achieved, and the performance and versatility of the compressor were improved.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SHANGHAI HITACHI ELECTRICAL APPLIANCES CO LTD
- Filing Date
- 2025-06-09
- Publication Date
- 2026-05-01
AI Technical Summary
Traditional rolling rotor compressors suffer from problems with excessive clearance volume and sealing issues in their exhaust port design, leading to gas leakage or mechanical interference, and lack a systematic solution.
Design a sealing structure by adding a protrusion to the eccentric part of the crankshaft to cooperate with the piston, satisfying the formula relationship Lr-Rc+t+m>0, and reasonably setting the exhaust port diameter, cylinder inner radius, piston thickness and protrusion radial width to ensure minimum sealing distance and avoid gas leakage.
By ensuring the minimum sealing distance of the exhaust port under different sized sealing structures, compressor performance can be improved, the risk of gas leakage can be reduced, and versatility and efficiency can be enhanced.
Smart Images
Figure CN224187746U_ABST
Abstract
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] Roller compressors are widely used due to their compact structure and smooth operation, but the following problems exist when matching the position of the exhaust port with the cylinder block parameters in traditional designs:
[0003] (1) Excessive clearance volume: The arrangement of the exhaust port on the outer edge leads to an increase in the amount of high-pressure gas residue, resulting in significant loss of intake during expansion.
[0004] (2) Exhaust resistance and sealing contradiction: If the exhaust port is simply moved inward to reduce the clearance volume, it is easy to cause insufficient minimum sealing distance between the piston and the cylinder head exhaust port. The exhaust port connects the piston inner cavity and the piston outer cavity, thereby causing gas leakage or mechanical interference.
[0005] To address the insufficient sealing distance between the piston and the exhaust port caused by its inward shift, a protrusion is added to the eccentric portion of the crankshaft. This protrusion works in conjunction with the piston to seal the exhaust port, thereby expanding the space available for its inward shift. However, currently, there is no systematic solution for the dimensional compatibility of the protrusion with the various compressor components, and no effective theoretical guidance has been provided for installing protrusions on compressors of different sizes. Utility Model Content
[0006] To address the problems in the existing technology, the purpose of this utility model is to provide a sealing structure for a compressor and a compressor in general. The formula relationship of the key dimensions of each component in the sealing structure is reasonably designed. Under the sealing distance of sealing structures of different sizes, the minimum sealing distance of the exhaust port can be guaranteed, avoiding gas leakage caused by insufficient sealing due to the inward movement of the exhaust port, thereby improving the performance of the compressor.
[0007] This utility model embodiment 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 protrusion cooperates with the piston to seal the exhaust port. The sealing structure satisfies: Lr - Rc + t + m > 0; where...
[0008] r is the radius of the vent hole, satisfying:
[0009] L is the distance from the center of the exhaust port to the center of the cylinder head where it is located;
[0010] Rc is the inner radius of the cylinder;
[0011] t is the wall thickness of the piston;
[0012] m is the maximum radial width of the protrusion.
[0013] In some embodiments, the sealing structure satisfies: 0.5mm < Lr - Rc + t + m < 3mm.
[0014] In some embodiments, the inner radius of the cylinder, the radius of the exhaust port, and the distance from the center of the exhaust port to the center of the cylinder head where it is located satisfy: Rc-0.5r≤L≤Rc.
[0015] In some embodiments, the edge of the vent near the protrusion does not extend beyond the edge of the protrusion away from the vent.
[0016] In some embodiments, the minimum distance between the edge of the vent near the protrusion and the edge of the protrusion away from the vent is δ, where δ satisfies: 10μm < δ < 20μm.
[0017] In some embodiments, the protrusion is a symmetrical structure symmetrical about the axis of the protrusion.
[0018] 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.
[0019] In some embodiments, the outer edge of the protrusion in the radial direction of the crankshaft is flush with the outer diameter surface of the eccentric portion.
[0020] In some embodiments, the protrusion is widest at the axis of the protrusion and narrows to both sides along the circumference of the eccentric portion from the axis of the protrusion.
[0021] This utility model embodiment also provides a compressor, including the sealing structure described above.
[0022] The sealing structure and compressor provided by this utility model have the following advantages:
[0023] This invention rationally designs the relationship between the exhaust port diameter and position, the cylinder inner radius, the piston thickness, and the radial width of the protrusion. Under different sized sealing structures, it ensures the minimum sealing distance of the exhaust port, avoiding gas leakage caused by insufficient sealing due to inward displacement of the exhaust port, thus improving compressor performance. When this sealing structure is applied to different scenarios, the relationship between the exhaust port diameter and position, the cylinder inner radius, the piston thickness, and the radial width of the protrusion provides theoretical guidance for the sealing distance of sealing structures of different sizes, ensuring the minimum sealing distance of the exhaust port in different scenarios and improving the versatility of this sealing structure. Attached Figure Description
[0024] 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.
[0025] Figure 1 This is a schematic diagram of the sealing structure of a compressor provided in an embodiment of the present invention;
[0026] Figure 2 This is a front view of the crankshaft of the relevant technology;
[0027] Figure 3 It is a bottom view of the crankshaft of the related technology;
[0028] Figure 4 This is a schematic diagram showing the fit between the cylinder, vanes, and cylinder head exhaust port of the relevant technology.
[0029] Figure label:
[0030] 10 cylinders
[0031] 20 Pistons
[0032] 30 Eccentric part
[0033] 31 Long shaft section
[0034] 32. Eccentric part
[0035] 33 Short shaft section
[0036] 34. Protrusion
[0037] 341 Protrusion axis
[0038] 41 Exhaust port
[0039] 50 blades Detailed Implementation
[0040] 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.
[0041] 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.
[0042] 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.
[0043] 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.
[0044] To address the problems in the prior art, this utility model provides a sealing structure for a compressor. The compressor includes a cylinder, a piston, a crankshaft, and a cylinder head. The cylinder head has an exhaust port. The crankshaft includes an eccentric portion, and 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 protrusion cooperates with the piston to seal the exhaust port. The sealing structure satisfies: Lr - Rc + t + m > 0; where...
[0045] r is the radius of the vent hole;
[0046] L is the distance from the center of the exhaust port to the center of the cylinder head where it is located;
[0047] Rc is the inner radius of the cylinder;
[0048] t is the wall thickness of the piston;
[0049] m is the maximum radial width of the protrusion.
[0050] The above-mentioned reasonable design of the relationship between the exhaust port diameter, position, cylinder inner radius, piston thickness and protrusion provides theoretical guidance for the sealing distance of sealing structures of different sizes, which can ensure the minimum sealing distance of the exhaust port, avoid gas leakage caused by insufficient sealing due to the inward movement of the exhaust port, and improve the performance of the compressor.
[0051] 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.
[0052] 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 front view of a crankshaft related to the technology is shown; Figure 3 A bottom view of a crankshaft, related to the technology, is shown. (See attached image.) Figures 1 to 3 As 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 33). 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 and the end face of the protrusion 34 of the eccentric portion 32 must completely cover the entire exhaust port 41; otherwise, the high and low pressure chambers 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.
[0053] like Figure 1 As shown, the radius of the exhaust port 41 is r; the distance L from the center of the exhaust port 41 to the center of the cylinder head is L. It should be noted that the cylinder head and the cylinder 10 are coaxially arranged, so the axes of the upper cylinder head and the cylinder are on the same straight line. In the bottom view, the centers of the cylinder head and the cylinder 10 coincide; the cylinder diameter of the cylinder 10 is Rc; the wall thickness of the piston 20 is t; and the maximum radial width of the protrusion 34 is m.
[0054] When there is no protrusion 34 on the eccentric part 32, the minimum sealing distance of the exhaust port 41 is related to the diameter of the exhaust port 41, the position of the exhaust port 41, the cylinder diameter of the cylinder 10, and the thickness of the piston 20. When the piston 20 is close to the exhaust port 41 and its center is on the line connecting the exhaust port 41 and the center of the cylinder 10, and the exhaust port 41 does not cross the edge of the inner diameter of the piston 20, that is, the minimum sealing distance of the exhaust port 41 is a positive value. At this time, there will be no leakage problem caused by incomplete sealing of the exhaust port, that is: Lr-Rc+t>0.
[0055] As the exhaust port 41 moves inward, with the piston 20 thickness remaining unchanged, gas leakage will inevitably occur because the end face of the piston 20 cannot cover the exhaust port 41. Therefore, by adding a protrusion 34 to the eccentric portion 32 of the crankshaft 30, the protrusion 34 and the end face of the piston 20 are fitted together to seal the exhaust port 41. As long as the exhaust port 41 does not extend beyond the inner edge of the protrusion 34, leakage from the exhaust port 41 can be prevented, which can be expressed by the formula Lr-Rc+t+m>0.
[0056] Therefore, Lr-Rc+t+m>0 defines the relationship between the diameter and position of the exhaust port 41, the cylinder diameter of the cylinder 10, the thickness of the piston 20, and the maximum radial width of the protrusion 34. This provides theoretical guidance for the sealing distance of sealing structures of different sizes, ensures the minimum sealing distance of the exhaust port, avoids gas leakage caused by insufficient sealing due to the inward movement of the exhaust port, and improves the performance of the compressor.
[0057] Furthermore, in some embodiments, the sealing structure satisfies: 0.5mm < Lr - Rc + t + m < 3mm.
[0058] Because the dimensions of the compressor components may fluctuate during processing, in order to avoid gas leakage caused by the misalignment of the protrusion 34 and the piston 20 due to errors in the cylinder 10, cylinder head, piston 20 and crankshaft 30, it is necessary to increase the lower limit of the sealing distance of the sealing structure to avoid insufficient sealing caused by dimensional fluctuations of other components.
[0059] For the gap oil film seal type at the exhaust port 41, a larger minimum sealing distance is not necessarily better. Experiments have shown that when the minimum sealing distance is above 3mm, the sealing performance of the sealing structure is already good enough, but at the same time, it will cause greater friction loss on the end face of the protrusion 34, which will reduce the efficiency of the compressor. Therefore, by setting an upper and lower limit value for the sealing distance, the sealing effect can be guaranteed while taking into account the optimal friction loss, thereby improving the overall performance of the compressor.
[0060] Furthermore, in some embodiments, the inner radius of the cylinder 10, the radius of the exhaust port 41, and the distance from the center of the exhaust port 41 to the center of the cylinder head where it is located satisfy: Rc-0.5r≤L≤Rc.
[0061] Figure 4 A schematic diagram of the cylinder, vanes, and cylinder head exhaust port of the related technology is shown. When the center of the exhaust port 41 is arranged on the outer edge of the cylinder 10, the clearance volume is too large, which easily leads to significant loss of intake volume during expansion. To reduce the clearance volume, the exhaust port 41 can be moved inward. Figure 4 As shown, when the exhaust port 41 moves inward so that its center is on the edge of the cylinder 10, that is, the distance from the exhaust port 41(1) to the center of the cylinder head is L equal to the inner radius Rc of the cylinder 10, that is, L = Rc; when the exhaust port 41 continues to move inward, that is, when the distance from the exhaust port 41(2) to the center of the cylinder head is less than the inner radius Rc of the cylinder 10, that is, L < Rc, at this time there is an exhaust dead angle between the vane 50, the cylinder 10 and the piston 20, which is not conducive to the efficiency of the exhaust process. Therefore, the exhaust port 41 cannot move inward indefinitely. By limiting the inward position of the exhaust port 41, the setting of the position of the exhaust port 41 can take into account both reducing the clearance volume and improving the exhaust efficiency.
[0062] Furthermore, in some embodiments, the edge of the vent 41 near the protrusion 34 does not extend beyond the edge of the protrusion 34 away from the vent 41. This arrangement allows the vent 41 to be completely sealed by the piston 20 and the protrusion 34, preventing gas leakage.
[0063] Furthermore, in some embodiments, the minimum sealing distance between the edge of the vent 41 near the protrusion 34 and the edge of the protrusion 34 opposite to the vent 41 is δ, where δ satisfies: 10μm < δ < 20μm. By limiting the upper and lower limits of the minimum sealing distance, it is convenient to select a reasonable minimum sealing distance for sealing structures of different sizes, thereby reducing gas leakage.
[0064] Furthermore, in some embodiments, the protrusion 34 is a symmetrical structure about the protrusion axis 341. The axisymmetric protrusion 34 helps to reduce unnecessary tilting of the crankshaft 30 eccentric portion 32 and avoid scratches.
[0065] Furthermore, 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 top-discharge (exhaust from the upper cylinder head), bottom-discharge (exhaust from the lower cylinder head), or double-discharge (exhaust from both the upper and lower cylinder heads), the position and number of the protrusion 34 on the end face of the eccentric portion 32 are reasonably set.
[0066] Furthermore, in some embodiments, the outer edge of the protrusion 34 in the radial direction of the crankshaft 30 is flush with the outer diameter surface of the eccentric portion 32. If the outer edge of the protrusion 34 protrudes beyond the outer diameter surface of the eccentric portion 32, it will cause the protrusion 34 to rub against the inner wall of the cylinder 10 when the compressor is running.
[0067] Furthermore, in some embodiments, the protrusion 34 is widest at the axis of the protrusion 34, and narrows to both sides along the circumference of the eccentric portion 32 from the axis of the protrusion 34.
[0068] This utility model embodiment also provides a compressor, including the sealing structure described above. The sealing structure achieves all the technical effects of the aforementioned sealing structure, and will not be elaborated further here.
[0069] In summary, the sealing structure and compressor provided by this utility model have the following advantages:
[0070] This invention rationally designs the relationship between the exhaust port diameter and position, the cylinder inner radius, the piston thickness, and the radial width of the protrusion. It ensures the minimum sealing distance of the exhaust port for sealing structures of different sizes, preventing gas leakage caused by insufficient sealing due to inward displacement of the exhaust port, thus improving compressor performance. When this sealing structure is applied to different scenarios, the relationship between the exhaust port diameter and position, the cylinder inner radius, the piston thickness, and the radial width of the protrusion provides theoretical guidance for the sealing distance of sealing structures of different sizes, ensuring the minimum sealing distance of the exhaust port in different scenarios and improving the versatility of this sealing structure.
[0071] 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 protrusion cooperates with the piston to seal the exhaust port. The sealing structure satisfies: Lr - Rc + t + m > 0; where... r is the radius of the vent hole; L is the distance from the center of the exhaust port to the center of the cylinder head where it is located; Rc is the inner radius of the cylinder; t is the wall thickness of the piston; m is the maximum radial width of the protrusion.
2. The sealing structure of the compressor according to claim 1, characterized in that, The sealing structure satisfies the following condition: 0.5mm < Lr - Rc + t + m < 3mm.
3. The sealing structure of the compressor according to claim 1, characterized in that, The inner radius of the cylinder, the radius of the exhaust port, and the distance from the center of the exhaust port to the center of the cylinder head satisfy the following condition: Rc-0.5r≤L≤Rc.
4. The sealing structure of the compressor according to claim 1, characterized in that, The edge of the vent near the protrusion does not extend beyond the edge of the protrusion away from the vent.
5. The sealing structure of the compressor according to claim 4, characterized in that, The minimum distance between the edge of the vent near the protrusion and the edge of the protrusion away from the vent is δ, where δ satisfies: 10μm < δ < 20μm.
6. The sealing structure of the compressor according to claim 1, characterized in that, The protrusion is a symmetrical structure about the axis of the protrusion.
7. 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 a first end face. The eccentric portion is located on one side of the lower cylinder head and is a 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.
8. The sealing structure of the compressor according to claim 1, characterized in that, The outer edge of the protrusion in the radial direction of the crankshaft is flush with the outer diameter surface of the eccentric part.
9. The sealing structure of the compressor according to claim 6, characterized in that, The protrusion is widest at its axis and narrows to both sides along the circumference of the eccentric portion from the axis of the protrusion.
10. A compressor, characterized in that, Includes the compressor's sealing structure as described above.