A crankshaft, compressor and air conditioner

Abstract

The application provides a crankshaft, a compressor and an air conditioner, the crankshaft comprises a long shaft, an eccentric part and a short shaft, the short shaft is provided with a first central oil hole, the first central oil hole extends from the inside of the short shaft to the inside of the eccentric part, the inside of the eccentric part is also provided with a second central oil hole, one end of the second central oil hole communicates with one end of the first central oil hole, and the other end of the second central oil hole extends to the position where the eccentric part and the long shaft are connected; the aperture of the first central oil hole is d1, the aperture of the second central oil hole is d2, and d1>d2. According to the application, the deflection deformation of the crankshaft of the compressor under the high-frequency operation condition is reduced, the local contact stress of the upper flange and the crankshaft friction pair is optimized, and the risk of the failure of the small high-speed compressor under the high-frequency heavy operation condition is reduced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, specifically to a crankshaft, a compressor, and an air conditioner. Background Technology

[0002] A conventional rotary compressor mainly consists of a pump body assembly 1, a motor assembly 2, a distributor assembly 3, and a housing 4. The housing is primarily composed of the pump body assembly and the motor assembly. The pump body assembly mainly includes components such as an upper flange, cylinder, crankshaft, rollers, and lower flange. These components work together to form a sealed intake and exhaust chamber. The motor assembly includes a stator assembly and a rotor assembly. The rotary compressor uses the motor to drive the crankshaft of the pump body. Under the rotational drive of the crankshaft, the volume of the compressor's intake and exhaust chambers continuously changes, thus realizing the periodic intake, compression, and exhaust process of the compressor. The crankshaft, as the core component of the compressor pump body, mainly serves to support, bear pressure, and supply oil. An oil passage structure is installed on the crankshaft to pump the lubricating oil from the oil sump at the bottom of the compressor to the contact surfaces of the various moving parts of the pump body, thereby achieving lubrication of the various moving friction pairs of the pump body.

[0003] In recent years, driven by the demand for cost reduction and lean manufacturing in air conditioning systems, miniaturized and high-speed design has gradually become a trend in the compressor field. However, the design of miniaturized and high-speed compressors requires optimization and improvement in various aspects, such as crankshaft strength and pump structure, to simultaneously address cost, performance, and noise and vibration. Regarding compressor energy efficiency, a small crankshaft diameter design is beneficial for establishing a performance advantage, but an excessively small crankshaft diameter can lead to poor strength and low reliability. In terms of compressor reliability, under high-frequency operation, the centrifugal force generated by the rotor assembly at the upper end of the crankshaft increases exponentially, leading to increased crankshaft deflection. Especially under high-frequency heavy operating conditions, this can easily cause excessive local contact stress between the flange and crankshaft friction pair, resulting in crankshaft wear failure and severely affecting the reliability of the compressor bearings and the entire unit. On the other hand, under high-frequency heavy operating conditions, a large amount of lubricating oil mixes with the high-speed flowing gas and is discharged from the compressor into the air conditioning system, resulting in a persistently high oil discharge rate during high-frequency operation. This reduces compressor performance and increases the reliability risk of internal oil shortage. Regarding compressor noise and vibration, frictional noise caused by crankshaft bearing pressure and electromagnetic noise caused by crankshaft deflection will increase dramatically.

[0004] Because the rotational centrifugal force caused by the rotor assembly at the upper end of the crankshaft long shaft of existing small high-speed compressors increases exponentially under high-frequency operation, the crankshaft deflection deformation increases. Especially under high-frequency heavy working conditions, it is very easy to cause excessive local contact stress between the flange and crankshaft friction pair, which in turn causes crankshaft wear failure, thus seriously affecting the reliability of compressor bearings and the whole machine. Therefore, this invention studies and designs a crankshaft, compressor and air conditioner. Summary of the Invention

[0005] Therefore, the technical problem to be solved by the present invention is to overcome the defect in the prior art where the crankshaft long axis deflection deformation increases under high frequency operation, resulting in excessive local contact stress between the flange and crankshaft friction pair, leading to crankshaft wear failure. Thus, the present invention provides a crankshaft, a compressor, and an air conditioner.

[0006] To address the aforementioned problems, the present invention provides a crankshaft comprising a long shaft, an eccentric portion, and a short shaft. The eccentric portion is connected between the long shaft and the short shaft. A first central oil hole is formed at the axial end of the short shaft facing the eccentric portion. The first central oil hole extends from the interior of the short shaft to the interior of the eccentric portion. A second central oil hole is also formed inside the eccentric portion. One end of the second central oil hole communicates with one end of the first central oil hole, and the other end of the second central oil hole extends to the position where the eccentric portion meets the long shaft.

[0007] The diameter of the first central oil hole is d1, and the diameter of the second central oil hole is d2, with d1 > d2.

[0008] In some implementations...

[0009] A first side oil hole is provided on the short shaft, a second side oil hole is provided on the eccentric portion, and a third side oil hole is provided on the long shaft. One end of the first side oil hole is connected to the first central oil hole and the other end extends to the outer peripheral wall of the short shaft. One end of the second side oil hole is connected to the first central oil hole and the other end extends to the outer peripheral wall of the eccentric portion. One end of the third side oil hole is connected to the second central oil hole and the other end extends to the outer peripheral wall of the long shaft.

[0010] In some implementations...

[0011] The shaft segment on the short shaft and connected to the eccentric portion is configured as a short shaft journal, and the first side oil hole is opened on the short shaft journal.

[0012] The shaft segment on the long shaft that connects to the eccentric portion is designated as a long shaft journal, and the third side oil hole is located on the long shaft journal.

[0013] The end of the second central oil hole that is away from the first central oil hole is a closed end, and the closed end is located at the journal of the long shaft.

[0014] In some implementations...

[0015] The axial end face of the eccentric part that connects with the short shaft is the first shaft end, and the axial end face of the eccentric part that connects with the long shaft is the second shaft end. The position where the first central oil hole connects with the second central oil hole is located between the first shaft end and the second shaft end, and is spaced at a first preset distance greater than 0 from the first shaft end and a second preset distance greater than 0 from the second shaft end.

[0016] In some implementations...

[0017] The position where the first central oil hole and the second central oil hole meet is the meeting end; the position where the second side oil hole meets the first central oil hole is located at the meeting end or at a third preset distance greater than 0 from the meeting end; and / or the first side oil hole, the second side oil hole and the third side oil hole all extend in the radial direction.

[0018] In some implementations...

[0019] The diameter of the first central oil hole is d1, the diameter of the second central oil hole is d2, the diameter of the long shaft is D2, and d2 < 0.8d1, d2 / D2 ≤ 0.45.

[0020] In some implementations...

[0021] The short shaft includes a first shaft segment and a second shaft segment. The first shaft segment is far away from the eccentric part relative to the second shaft segment and is a non-fitting segment that does not mate with the lower flange. The second shaft segment is close to the eccentric part relative to the first shaft segment and is a fitting segment that mates with the lower flange. The shaft diameter of the first shaft segment is D0, and the shaft diameter of the second shaft segment is D1, with D0 < D1.

[0022] In some implementations...

[0023] When D0, D1, d1, d2 and D2 are included simultaneously, D0 < D1 - 0.3 mm, d2 < 0.65d1, and d2 / D2 ≤ 0.32.

[0024] The present invention also provides a compressor, which includes a pump body assembly and a housing. The pump body assembly is disposed inside the housing. The pump body assembly includes the aforementioned crankshaft, and also includes an upper flange, a lower flange, and rollers. The upper flange is engaged with the long shaft, the rollers are engaged with the eccentric portion, and the lower flange is engaged with the short shaft.

[0025] In some implementations...

[0026] The effective volume of the pump assembly is V, the maximum operating frequency of the compressor is f, and the inner diameter of the compressor housing is Dk. The parameters f, V, and Dk satisfy: 121 ≤ f * V / Dk ≤ 367, f ≥ 120 Hz, where V is in cm. 3 The unit of Dk is cm.

[0027] In some implementations...

[0028] The bottom of the housing has an oil sump, when the short shaft includes a first shaft section and a second shaft section:

[0029] The vertical distance between the lower end face of the first shaft segment of the crankshaft and the bottom of the oil sump is set as h1, the axial length of the first shaft segment is L1, the axial length of the second shaft segment is L2, and the axial height of the lower flange is h2. The parameters h1, h2, L1, and L2 satisfy: h2≤L2, 3mm≤h1≤35mm, and 8mm≤L1≤15mm.

[0030] In some implementations...

[0031] An oil guide component is provided in the first central oil hole of the crankshaft. The oil guide component is interference-fitted with the first central oil hole. The assembly depth of the oil guide component extends at least axially to the position of the second side oil hole of the eccentric part.

[0032] Alternatively, a first oil guide component is installed in the first central oil hole of the crankshaft, and a second oil guide component is installed in the second central oil hole. The first oil guide component is interference-fitted with the first central oil hole, and the second oil guide component is interference-fitted with the second central oil hole.

[0033] Alternatively, the crankshaft may have an oil guiding component in the first and second central oil holes. The oil guiding component is a segmented structure, including a first oil guiding section and a second oil guiding section. The first oil guiding section cooperates with the first central oil hole, and the second oil guiding section cooperates with the second central oil hole.

[0034] The present invention also provides an air conditioner that includes the aforementioned compressor.

[0035] The crankshaft, compressor, and air conditioner provided by this invention have the following beneficial effects:

[0036] 1. This invention configures the central oil hole inside the crankshaft as a structure including first and second central oil holes, with the diameter of the first central oil hole being larger than that of the second central oil hole. The first central oil hole extends to the eccentric portion, and the second central oil hole extends from the position where the first central oil hole connects to the position where the long shaft connects. This ensures lubrication between the lower flange and the short shaft via the first side oil hole, between the roller and the eccentric portion via the second side oil hole, and between the upper flange and the long shaft via the third side oil hole. Furthermore, it effectively reduces the volume of the central oil holes at the upper end of the eccentric portion and on the long shaft, and even eliminates the need for a central oil hole at the upper end of the third side oil hole. This is particularly beneficial for small shaft structures, enabling high-frequency heavy-duty operation. The optimization of the structural strength of the long shaft and its root, which suffers from severe structural strength deterioration, balances the design points of both crankshaft diameter and crankshaft strength in high-efficiency compressors. While ensuring compressor energy efficiency and oil supply, it effectively improves the structural strength of the long shaft of the small-diameter compressor crankshaft, thereby reducing crankshaft deflection under high-frequency operating conditions. It also optimizes the local contact stress between the upper flange and the crankshaft friction pair, greatly reducing the risk of crankshaft wear failure caused by insufficient crankshaft strength in small high-frequency heavy-duty compressors. This improves the reliability of compressor bearings and the entire machine, and solves the problem of excessive local contact stress between the flange and crankshaft friction pair due to increased crankshaft deflection, which leads to crankshaft wear failure.

[0037] 2. The present invention further comprises a short shaft including a first shaft segment and a second shaft segment. The first shaft segment is far from the eccentric portion relative to the second shaft segment and is a non-fitting segment that does not mate with the lower flange. The second shaft segment is close to the eccentric portion relative to the first shaft segment and is a fitting segment that mates with the lower flange. The shaft diameter of the first shaft segment is D0, and the shaft diameter of the second shaft segment is D1, with D0 < D1. This enables the lower end face of the short shaft (i.e., the inlet of the crankshaft center oil hole) to extend out of the lower flange and shortens the distance from the oil hole inlet to the bottom of the compressor oil sump. This ensures that when the compressor is operating under high-frequency heavy working conditions and the oil level in the oil sump is too low, the inlet of the crankshaft center oil hole does not detach from the oil sump surface, avoiding abnormal oil supply. This effectively solves the reliability problem of insufficient oil supply to the compressor pump body friction pair and causing wear of parts when the oil level in the oil sump is very low during high-frequency operation of the compressor. When the crankshaft of the present invention is rotating, there is liquid-solid contact friction between the non-fitting section of its short shaft and the lubricating oil in the oil sump. Therefore, the present invention designs the shaft diameter of the non-fitting section to be a smaller value than that of the journal of the fitting section, which can further reduce the liquid-solid contact friction resistance loss.

[0038] 3. Furthermore, this invention provides a preferred limit value for the relationship between the central oil hole and the shaft diameter (preferably D0 < D1 - 0.3 mm, d2 < 0.65d1, d2 / D2 ≤ 0.32). Its main function is to optimize and reduce crankshaft deflection and increase oil pumping capacity under high-frequency operating conditions. While ensuring the compressor's oil supply and friction pair lubrication requirements, it optimizes the oil pumping capacity of small, high-speed compressors under high-frequency heavy operating conditions, thereby achieving a high-frequency, low-oil-discharge rate. This improves the compressor's heating (cooling) capacity while effectively reducing the reliability risk of internal oil shortage during high-frequency operation. Attached Figure Description

[0039] Figure 1-1 This is an internal cross-sectional view of a conventional rotary compressor in the prior art;

[0040] Figure 1-2 yes Figure 1-1 A close-up view of the pump body;

[0041] Figure 2 This is a partially enlarged structural view of the pump body portion of the rotary compressor according to the preferred embodiment of the present invention;

[0042] Figure 2-2 yes Figure 2 A partial enlarged sectional view of the crankshaft section;

[0043] Figure 3-1 This is a partially enlarged structural view of the pump body portion of the rotary compressor of the alternative embodiment 1 of the present invention;

[0044] Figure 3-2 This is a partially enlarged structural view of the pump body portion of the rotary compressor in alternative embodiment 2 of the present invention;

[0045] Figure 3-3 yes Figure 3-2 Enlarged view of the oil guiding component.

[0046] The reference numerals in the attached figures are as follows:

[0047] 1. Pump body assembly; 11. Upper flange; 12. Cylinder; 13. Crankshaft; 131. Short shaft; 1311. First shaft section; 1312. Second shaft section; 132. Eccentric part; 133. Long shaft; 134. Central oil hole; 1341. First central oil hole; 1342. Second central oil hole; 135. Side oil hole; 1351. First side oil hole; 1352. Second side oil hole; 1353. Third side oil hole; 14. Roller; 15. Lower flange; 2. Motor assembly; 21. Rotor assembly; 22. Stator assembly; 3. Distributor assembly; 4. Housing; 5. Oil sump; 8. Oil guiding component; 81. First oil guiding component; 82. Second oil guiding component; 801. First oil guiding section; 802. Second oil guiding section. Detailed Implementation

[0048] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0049] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0050] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0051] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not 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 on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0052] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0053] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0054] Figure 1 is a background diagram of the structure of this invention.

[0055] like Figure 1-1 The diagram shows the overall assembly structure of a conventional rotary compressor (using a single-cylinder compressor as an example). A conventional rotary compressor mainly consists of a pump body assembly 1, a motor assembly 2, a distributor assembly 3, and a housing 4. The housing 4 is primarily composed of the pump body assembly 1 and the motor assembly 2. The pump body assembly 1 mainly includes components such as an upper flange 11, a cylinder 12, a crankshaft 13, rollers 14, and a lower flange 15. These components work together to form a sealed intake and exhaust chamber. The motor assembly 2 includes a rotor assembly 21 and a stator assembly 22. The rotary compressor drives the crankshaft 13 in the pump body assembly 1 through the motor assembly 2. The rotation of the crankshaft 13 causes the volume of the compressor's intake and exhaust chambers to continuously change, thus realizing the periodic intake, compression, and exhaust process of the compressor.

[0056] like Figure 1-2 The diagram shown is a partial enlarged view of the pump body assembly of a conventional rotary compressor. The crankshaft 13, as the core component of the compressor pump body assembly 1, mainly serves to support, bear pressure, and supply oil. The crankshaft 13 is equipped with an oil passage structure to pump the lubricating oil from the oil sump 5 at the bottom of the compressor to the contact surfaces of the various moving parts of the pump body (as indicated by the solid arrows in Figure 1-2), thereby achieving lubrication of the various moving friction pairs of the pump body.

[0057] In recent years, driven by the demand for cost reduction and lean development in air conditioning systems, miniaturized and high-speed design has gradually become a trend in the compressor field. However, the design of miniaturized and high-speed compressors requires optimization and improvement in various aspects, such as crankshaft strength and pump structure, to simultaneously address cost, performance, and noise and vibration. Regarding compressor energy efficiency, a small crankshaft diameter design is beneficial for establishing a performance advantage, but an excessively small crankshaft diameter can lead to poor strength and low reliability. In terms of compressor reliability, under high-frequency operation, the centrifugal force generated by the rotor assembly 21 at the upper end of the crankshaft long shaft increases exponentially, leading to increased crankshaft deflection. Especially under high-frequency heavy operating conditions, this can easily cause excessive local contact stress between the flange and crankshaft friction pair, resulting in crankshaft wear failure and severely affecting the reliability of the compressor bearings and the entire unit. On the other hand, under high-frequency heavy operating conditions, a large amount of lubricating oil mixes with the high-speed flowing gas and is discharged from the compressor into the air conditioning system, resulting in a high oil discharge rate during high-frequency operation. This reduces compressor performance and increases the reliability risk of internal oil shortage. Regarding compressor noise and vibration, frictional noise caused by crankshaft bearing pressure and electromagnetic noise caused by crankshaft deflection will increase dramatically.

[0058] This invention addresses the aforementioned technical problems of small, high-capacity gas compressors by proposing an innovative pump body assembly structure to achieve the beneficial effects of balancing energy efficiency, reliability, noise and vibration, oil supply, and oil discharge rate in small, high-speed compressors.

[0059] like Figures 2 to 3-3 As shown, the present invention provides a crankshaft, which includes a long shaft 133, an eccentric portion 132, and a short shaft 131. The eccentric portion 132 is connected between the long shaft 133 and the short shaft 131. A first central oil hole 1341 is formed at the axial end of the short shaft 131 toward the eccentric portion 132. The first central oil hole 1341 extends from the interior of the short shaft 131 to the interior of the eccentric portion 132. A second central oil hole 1342 is also formed inside the eccentric portion 132. One end of the second central oil hole 1342 communicates with one end of the first central oil hole 1341, and the other end of the second central oil hole 1342 extends to the position where the eccentric portion 132 meets the long shaft 133.

[0060] The diameter of the first central oil hole 1341 is d1, and the diameter of the second central oil hole 1342 is d2, with d1 > d2.

[0061] This invention addresses the issue of crankshaft lubrication by configuring the internal center oil hole as a structure comprising first and second center oil holes, with the diameter of the first center oil hole being larger than that of the second center oil hole. The first center oil hole extends to the eccentric portion, while the second center oil hole extends from the point where it connects to the first center oil hole to the point where it connects to the long shaft. This ensures lubrication between the lower flange and the short shaft via the first side oil hole, between the roller and the eccentric portion via the second side oil hole, and between the upper flange and the long shaft via the third side oil hole. Furthermore, it effectively reduces the volume required for the center oil holes at the upper end of the eccentric portion and on the long shaft, and even eliminates the need for a center oil hole at the upper end of the third side oil hole. This is particularly beneficial for small shaft structures, enabling lubrication under high-frequency, heavy-duty operating conditions. The optimization of the structural strength of the long shaft and its root, which suffered from severe structural strength deterioration, balances the design points of both crankshaft diameter and crankshaft strength in high-efficiency compressors. While ensuring compressor energy efficiency and oil supply, it effectively improves the structural strength of the long shaft of the small-diameter compressor crankshaft, thereby reducing crankshaft deflection under high-frequency operating conditions. It also optimizes the local contact stress between the upper flange and the crankshaft friction pair, greatly reducing the risk of crankshaft wear failure caused by insufficient crankshaft strength in small high-frequency heavy-duty compressors. This improves the reliability of compressor bearings and the entire machine, and solves the problem of excessive local contact stress between the flange and crankshaft friction pair due to increased crankshaft deflection, which leads to crankshaft wear failure.

[0062] In some implementations...

[0063] A first side oil hole 1351 is provided on the short shaft 131, a second side oil hole 1352 is provided on the eccentric portion 132, and a third side oil hole 1353 is provided on the long shaft 133. One end of the first side oil hole 1351 is connected to the first central oil hole 1341, and the other end extends to the outer peripheral wall of the short shaft 131. One end of the second side oil hole 1352 is connected to the first central oil hole 1341, and the other end extends to the outer peripheral wall of the eccentric portion 132. One end of the third side oil hole 1353 is connected to the second central oil hole 1342, and the other end extends to the outer peripheral wall of the long shaft 133.

[0064] This invention, by setting three side oil holes at different positions, can ensure lubrication between the lower flange and the short shaft through the first side oil hole, between the roller and the eccentric part through the second side oil hole, and between the upper flange and the long shaft through the third side oil hole. At the same time, it can reduce the length of the opening of the center oil hole of the long shaft or even eliminate it. This can improve the structural strength of the long shaft of the crankshaft of the small-diameter compressor, thereby reducing the crankshaft deflection deformation of the compressor under high-frequency operating conditions, optimizing the local contact stress of the friction pair between the upper flange and the crankshaft, and reducing the risk of crankshaft wear failure caused by insufficient crankshaft strength when the small high-speed compressor is operating under high-frequency heavy conditions.

[0065] In some implementations...

[0066] The shaft segment on the short shaft 131 that is connected to the eccentric portion 132 is configured as a short shaft journal, and the first side oil hole 1351 is opened on the short shaft journal.

[0067] The shaft segment on the long shaft 133 that connects to the eccentric portion 132 is configured as a long shaft journal, and the third side oil hole 1353 is formed on the long shaft journal.

[0068] The end of the second central oil hole 1342 that is away from the first central oil hole 1341 is a closed end, and the closed end is located at the journal of the long shaft 133.

[0069] This is a preferred structural form of the first side oil hole, the third side oil hole, and the second central oil hole of the present invention. The first side oil hole is preferably located on the short shaft journal where the short shaft connects to the eccentric part. Since the short shaft journal is located at the uppermost end of the short shaft, the oil flowing out from the first side oil hole can effectively lubricate the part between the short shaft and the lower flange. The third side oil hole is located on the long shaft journal and can supply oil between the long shaft and the upper flange. The oil can be delivered to the position that needs lubrication through the upper oil groove and other structures on the upper flange. Furthermore, the present invention also sets the oil supply end of the second central oil hole as a closed end, that is, a blind hole. This closed end only acts to supply oil to the third side oil hole. Since the long shaft journal is located at the lowermost end of the long shaft, the opening of the internal hole structure of the long shaft can be minimized to the greatest extent, while ensuring effective oil supply. Therefore, it can further reduce the deflection deformation of the long shaft under high-frequency operating conditions, reduce the contact stress between the flange and the long shaft, and further avoid crankshaft wear failure.

[0070] In some implementations...

[0071] The axial end face of the eccentric portion 132 that connects with the short shaft 131 is the first shaft end, and the axial end face of the eccentric portion 132 that connects with the long shaft 133 is the second shaft end. The position where the first central oil hole 1341 connects with the second central oil hole 1342 is located between the first shaft end and the second shaft end, and is spaced at a first preset distance greater than 0 from the first shaft end and a second preset distance greater than 0 from the second shaft end.

[0072] The present invention further improves upon the present invention by setting the position where the second central oil hole connects to the first central oil hole between the two shaft ends of the eccentric part. This ensures that the connection position between the second central oil hole and the third side oil hole is as high as possible, guaranteeing the oil output of the third side oil hole to ensure lubrication between the eccentric part and the roller. At the same time, it also ensures that the first central oil hole (large diameter oil hole) is as short as possible to reduce the impact on the crankshaft structural strength. Oil is transferred through the second central oil hole (small diameter oil hole), which improves the crankshaft structural strength, further avoids deflection deformation under high-frequency operating conditions, further reduces stress, and reduces the risk of crankshaft wear failure.

[0073] In some implementations...

[0074] The position where the first central oil hole 1341 and the second central oil hole 1342 meet is the meeting end. The position where the second side oil hole 1352 meets the first central oil hole 1341 is located at the meeting end or at a third preset distance greater than 0 from the meeting end; and / or the first side oil hole 1351, the second side oil hole 1352 and the third side oil hole 1353 all extend in the radial direction.

[0075] This is the preferred positional relationship between the second side oil hole and the first and second central oil holes of the present invention. Preferably, the second side oil hole is located at the junction of the first and second central oil holes, which can further increase the position of the second side oil hole and further increase the lubrication area between the eccentric part and the roller, thereby improving the lubrication performance of this part. Preferably, all three side oil holes extend in the radial direction, which can effectively ensure that the oil in the first and second central oil holes is guided and delivered to the lower flange and the short shaft, the eccentric part and the roller, and the upper flange and the long shaft, respectively, so as to lubricate the above-mentioned positions respectively.

[0076] In some implementations...

[0077] The diameter of the first central oil hole 1341 is d1, the diameter of the second central oil hole 1342 is d2, the diameter of the long shaft 133 is D2, and d2 < 0.8d1, d2 / D2 ≤ 0.45.

[0078] The pump body assembly 1 of this invention includes main components such as an upper flange 11, a cylinder 12, a crankshaft 13, rollers 14, and a lower flange 15. The crankshaft 13 includes a short shaft 131, an eccentric portion 132, and a long shaft 133, which respectively mate with the lower flange 15, the rollers 14, and the upper flange 11. The short shaft 131 consists of a first shaft section 1311 and a second shaft section 1312. The first shaft section 1311 is located away from the crankshaft eccentric portion 132 and is a non-matement section with the lower flange 15. The second shaft section 1312 is located close to the crankshaft eccentric portion 132 and is a matement section with the lower flange 15. The crankshaft 13 is provided with a central oil hole 134 and a side oil hole 135. The side oil holes 135 are composed of a first side oil hole 1351, a second side oil hole 1352, and a third side oil hole 1353 respectively located at the root of the short shaft 131 (near the eccentric portion 132), the middle of the eccentric portion 132, and the root of the long shaft 133. The crankshaft center oil hole 134 has a segmented structure, consisting of a first center oil hole 1341 and a second center oil hole 1342. The first center oil hole 1341 penetrates the lower end face of the crankshaft short shaft 131 and extends axially to above the second side oil hole 1352 of the crankshaft eccentric portion 132. The first center oil hole 1341 has an oil guiding component 8, which is interference-fitted with the first center oil hole 1341. Its assembly depth extends axially to at least the position of the second side oil hole of the crankshaft eccentric portion. The second center oil hole 1342 is a blind hole extending axially to the third side oil hole 1353 at the root of the long shaft 133. The outer diameters of the first shaft segment 1311, the second shaft segment 1312, and the long shaft 133 of the crankshaft short shaft 131 are set to D0, D1, and D2, respectively, and the inner diameters of the first central oil hole 1341 and the second central oil hole 1342 are set to d1 and d2, respectively. The parameters D0, D1, D2, d1, and d2 satisfy the following conditions: D0 < D1, d2 < 0.8d1, d2 / D2 ≤ 0.45. Preferably, D0 < D1 - 0.3mm, d2 < 0.65d1, and d2 / D2 ≤ 0.32. Therefore, this design balances the design considerations of both crankshaft diameter and crankshaft strength in high-efficiency compressors. While ensuring compressor energy efficiency, it effectively improves the structural strength of the long crankshaft of small-diameter compressors, thereby reducing crankshaft deflection under high-frequency operating conditions. It also optimizes the local contact stress between the upper flange and crankshaft friction pair, significantly reducing the risk of crankshaft wear failure due to insufficient crankshaft strength during high-frequency, heavy-duty operation of small, high-speed compressors, thus improving the reliability of compressor bearings and the entire unit. On the other hand, through the segmented blind hole structure of the central oil hole and the optimized design of the central oil hole size, while ensuring the compressor's oil supply and friction pair lubrication requirements, it optimizes the oil pumping volume of small, high-speed compressors under high-frequency, heavy-duty conditions. This achieves a high-frequency, low-oil-discharge rate, improving the compressor's heating (cooling) capacity while effectively reducing the reliability risk of internal oil shortage during high-frequency operation.

[0079] In some implementations...

[0080] The short shaft 131 includes a first shaft segment 1311 and a second shaft segment 1312. The first shaft segment 1311 is away from the eccentric portion 132 relative to the second shaft segment 1312 and is a non-fitting segment that does not mate with the lower flange. The second shaft segment 1312 is close to the eccentric portion 132 relative to the first shaft segment 1311 and is a fitting segment that mates with the lower flange. The shaft diameter of the first shaft segment 1311 is D0, and the shaft diameter of the second shaft segment 1312 is D1, with D0 < D1.

[0081] The present invention further includes a short shaft comprising a first shaft segment and a second shaft segment. The first shaft segment is located away from the eccentric portion relative to the second shaft segment and is a non-fitting segment that does not mate with the lower flange. The second shaft segment is located closer to the eccentric portion relative to the first shaft segment and is a fitting segment that mates with the lower flange. The shaft diameter of the first shaft segment is D0, and the shaft diameter of the second shaft segment is D1, with D0 < D1. This allows the lower end face of the short shaft (i.e., the inlet of the crankshaft center oil hole) to extend beyond the lower flange and shortens the distance from the oil hole inlet to the bottom of the compressor oil sump. This ensures that when the compressor is operating under high-frequency heavy working conditions and the oil level in the oil sump is too low, the inlet of the crankshaft center oil hole does not detach from the oil sump surface, avoiding abnormal oil supply. This effectively solves the reliability problem of insufficient oil supply to the compressor pump body friction pair and causing wear of parts when the oil level in the oil sump is very low during high-frequency operation of the compressor. When the crankshaft of the present invention is rotating, there is liquid-solid contact friction between the non-fitting section of its short shaft and the lubricating oil in the oil sump. Therefore, the present invention designs the shaft diameter of the non-fitting section to be a smaller value than that of the journal of the fitting section, which can further reduce the liquid-solid contact friction resistance loss.

[0082] In some implementations...

[0083] When D0, D1, d1, d2, and D2 are included simultaneously, D0 < D1 - 0.3 mm, d2 < 0.65d1, and d2 / D2 ≤ 0.32. This invention further provides a preferred limit value for the relationship between the central oil hole and the shaft diameter (preferably D0 < D1 - 0.3 mm, d2 < 0.65d1, and d2 / D2 ≤ 0.32). Its main function is to optimize and reduce crankshaft deflection and increase oil pumping capacity under high-frequency operating conditions. While ensuring the compressor's oil supply and friction pair lubrication requirements, it optimizes the oil pumping capacity of small, high-speed compressors under high-frequency, heavy-duty conditions, thereby achieving a high-frequency, low-oil-discharge rate, improving the compressor's heating (cooling) capacity, and effectively reducing the reliability risk of internal oil shortage during high-frequency operation.

[0084] The present invention also provides a compressor, which includes a pump body assembly and a housing. The pump body assembly is disposed inside the housing. The pump body assembly includes the aforementioned crankshaft, and also includes an upper flange 11, a lower flange 15 and rollers 14. The upper flange is engaged with the long shaft 133, the rollers 14 are engaged with the eccentric portion 132, and the lower flange 15 is engaged with the short shaft 131.

[0085] This invention addresses the aforementioned technical problems of small, high-capacity gas compressors by proposing an innovative pump body assembly structure to achieve the beneficial effects of balancing energy efficiency, reliability, noise and vibration, oil supply, and oil discharge rate in small, high-speed compressors.

[0086] This invention solves the following technical problems:

[0087] 1. To improve the energy efficiency of the compressor, the pump body crankshaft adopts a small shaft diameter design. This invention solves the problem of reduced crankshaft strength and low reliability caused by the small shaft diameter by using a small shaft diameter crankshaft structure with a first central oil hole and a second central oil hole, as well as the correlation between the two central oil holes and the shaft diameter.

[0088] 2. In high-frequency operation, the centrifugal force caused by the rotor assembly at the upper end of the crankshaft of a small high-speed compressor increases exponentially, leading to increased crankshaft deflection. This invention effectively solves the problem of excessive local contact stress between the flange and crankshaft friction pair, especially under high-frequency heavy operating conditions, by using the positions of the two central oil holes and their correlation with the shaft diameter. This leads to crankshaft wear failure and seriously affects the reliability of the compressor bearings and the entire machine.

[0089] 3. The present invention also utilizes a segmented short shaft structure to enable the lower end face of the short shaft (i.e., the inlet of the crankshaft center oil hole) to extend out of the lower flange, thereby shortening the distance from the oil hole inlet to the bottom of the compressor oil sump. This effectively solves the problem that in small, high-speed compressors operating under high-frequency and heavy-duty conditions, a large amount of lubricating oil mixes with the high-speed flowing gas and is subsequently discharged from the compressor to the air conditioning system, resulting in a persistently high oil discharge rate during high-frequency operation of the compressor, which reduces compressor performance and increases the reliability risk of internal oil shortage.

[0090] 4. The present invention, through the arrangement of the first and second central oil holes, can solve the problem of rapidly increasing frictional noise caused by crankshaft bearing pressure and electromagnetic noise caused by crankshaft deflection in small high-speed compressors.

[0091] Beneficial effects:

[0092] 1. This invention balances the small diameter design of the compressor crankshaft with crankshaft strength, thereby improving compressor performance and reliability;

[0093] 2. This invention optimizes the structural strength of the long shaft of the crankshaft, reduces its deflection deformation, reduces the local contact stress between the flange and the crankshaft friction pair, and reduces the reliability risk of crankshaft wear failure under high-frequency operation;

[0094] 3. This invention optimizes the crankshaft oil circuit supply structure, reduces the amount of oil pumped during high-frequency operation of the compressor, thereby reducing the compressor oil discharge rate and reducing the reliability risk of high-frequency internal oil shortage in the compressor;

[0095] 4. This invention improves the sound quality and listening experience of small, high-speed compressors by optimizing the strength of the crankshaft structure, reducing frictional and electromagnetic noise caused by crankshaft pressure and deflection.

[0096] In some implementations...

[0097] The effective volume of the pump assembly is V, the maximum operating frequency of the compressor is f, and the inner diameter of the compressor casing is Dk. The parameters f, V, and Dk satisfy: 121 ≤ f*V / Dk ≤ 367, f ≥ 120Hz; preferably, 152 ≤ f*V / Dk ≤ 310, 140Hz ≤ f ≤ 180Hz. The unit of V is cm. 3 The unit of Dk is cm.

[0098] Furthermore, this invention proposes a rolling rotor compressor using the above-described pump body assembly. Let the effective volume of the pump body assembly 1 be V, the maximum operating frequency of the compressor be f, and the inner diameter of the compressor casing be Dk. The parameters f, V, and Dk satisfy: 121 ≤ f*V / Dk ≤ 367, f ≥ 120Hz; preferably, 152 ≤ f*V / Dk ≤ 310, 140Hz ≤ f ≤ 180Hz. Here, the units of V and Dk are cm. 3 cm. Thus, it is possible to effectively optimize the gas delivery volume and the internal volume of the compressor housing of a small, high-speed compressor, thereby reducing the aerodynamic noise of the small, high-speed compressor.

[0099] In some implementations...

[0100] The bottom of the housing 4 has an oil sump 5. When the short shaft 131 includes a first shaft segment 1311 and a second shaft segment 1312:

[0101] The vertical distance between the lower end face of the first shaft segment 1311 of the crankshaft and the bottom of the oil sump 5 is defined as h1. The axial length of the first shaft segment 1311 is L1, the axial length of the second shaft segment 1312 is L2, and the axial height of the lower flange 15 is h2. The parameters h1, h2, L1, and L2 satisfy: h2 ≤ L2, 3mm ≤ h1 ≤ 35mm, and 8mm ≤ L1 ≤ 15mm. Preferably, the parameters h1, h2, L1, and L2 satisfy: h2 < L2 - 1.5mm, 5mm ≤ h1 ≤ 25mm, and 10mm ≤ L1 ≤ 13mm.

[0102] By using the above-mentioned dimensional design, this invention can optimize the oil pumping effect of the crankshaft center oil hole while ensuring the effective fit length between the crankshaft short shaft and the lower flange. This avoids situations where the distance between the oil pump inlet and the bottom of the oil sump is too small, resulting in insufficient oil pumping smoothness and increased oil pumping resistance, or where the distance between the pump inlet and the bottom of the oil sump is too large, causing the compressor to be unable to pump oil normally when the oil level in the oil sump is low.

[0103] For the solution of this invention, theoretical simulation of crankshaft structural strength and verification of compressor oil circulation rate, noise and vibration were carried out on a specific model. The results show that under high-frequency 160Hz heating conditions, compared with conventional compressors, the crankshaft deflection and contact stress of the present invention are significantly reduced, the performance is slightly optimized, and the oil circulation rate, noise and vibration are significantly reduced.

[0104] Table 1

[0105]

[0106] Preferred implementation, such as Figure 2 and 2-2 In some implementation methods,

[0107] An oil guide component 8 is provided in the first central oil hole 1341 of the crankshaft. The oil guide component 8 is interference-fitted with the first central oil hole 1341. The assembly depth of the oil guide component 8 extends at least axially to the position of the second side oil hole 1352 of the eccentric portion 132.

[0108] The compressor and its pump assembly have a crankshaft with a first central oil hole having an oil guide component. The oil guide component is interference-fitted with the first central oil hole, and the assembly depth extends at least axially to the position of the second side oil hole of the eccentric part of the crankshaft.

[0109] It can ensure that the oil guide plate is assembled to extend at least to the upper end face of the neck of the long shaft flange, thus ensuring effective oil supply to the upper and lower flanges and the eccentric part.

[0110] Alternative Example 1:

[0111] like Figure 3-1As shown, alternatively, in the compressor and pump body assembly of the present invention, the first central oil hole 1341 and the second central oil hole 1342 of the crankshaft 13 are respectively equipped with a first oil guide component 81 and a second oil guide component 82, the first oil guide component 81 is interference-fitted with the first central oil hole 1341, and the second oil guide component 82 is interference-fitted with the second central oil hole 1342.

[0112] That is, the crankshaft of the present invention has a first oil guide component 81 installed in the first central oil hole 1341 and a second oil guide component 82 installed in the second central oil hole 1342. The first oil guide component 81 is interference-fitted with the first central oil hole 1341, and the second oil guide component 82 is interference-fitted with the second central oil hole 1342. This ensures that the installation depth of the oil guide component extends at least to the upper end face of the long shaft flange neck, ensuring effective oil supply to the upper and lower flanges and the eccentric portion.

[0113] Alternative Example 2:

[0114] like Figure 3-2 As shown, alternatively, in the compressor and pump assembly of this embodiment of the invention, the crankshaft central oil hole 134 (including a first central oil hole 1341 and a second central oil hole 1342) is equipped with an oil guiding component 8. The oil guiding component 8 has a segmented structure, consisting of a first oil guiding section 801 and a second oil guiding section 802. The first oil guiding section 801 mates with the first central oil hole 1341, and the second oil guiding section 802 mates with the second central oil hole 1342.

[0115] That is, the crankshaft has an oil guiding component 8 in the first central oil hole 1341 and the second central oil hole 1342. The oil guiding component 8 has a segmented structure, including a first oil guiding section 801 and a second oil guiding section 802. The first oil guiding section 801 cooperates with the first central oil hole 1341, and the second oil guiding section 802 cooperates with the second central oil hole 1342.

[0116] Alternative embodiment 2 of the present invention further protects the assembly depth of its oil guiding component, further ensuring that the assembly depth of the oil guiding plate extends at least to the upper end face of the neck of the long shaft flange, thus ensuring effective oil supply to the upper and lower flanges and the eccentric portion.

[0117] This invention also protects an air conditioner with a compressor having the structural features described in this invention. This invention provides an air conditioner with a compressor and pump assembly having the aforementioned structural features, wherein the compressor can be a single-cylinder, double-cylinder, or multi-cylinder rotary compressor, etc.

[0118] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A crankshaft, characterized in that: The device includes a long shaft (133), an eccentric portion (132), and a short shaft (131). The eccentric portion (132) is connected between the long shaft (133) and the short shaft (131). The axial end of the short shaft (131) is provided with a first central oil hole (1341) facing the eccentric portion (132). The first central oil hole (1341) extends from the interior of the short shaft (131) to the interior of the eccentric portion (132). The interior of the eccentric portion (132) is also provided with a second central oil hole (1342). One end of the second central oil hole (1342) is connected to one end of the first central oil hole (1341), and the other end of the second central oil hole (1342) extends to the position where the eccentric portion (132) and the long shaft (133) meet. The diameter of the first central oil hole (1341) is d1, and the diameter of the second central oil hole (1342) is d2, with d1 > d2.

2. The crankshaft according to claim 1, characterized in that: A first side oil hole (1351) is provided on the short shaft (131), a second side oil hole (1352) is provided on the eccentric part (132), and a third side oil hole (1353) is provided on the long shaft (133). One end of the first side oil hole (1351) is connected to the first central oil hole (1341), and the other end extends to the outer peripheral wall of the short shaft (131). One end of the second side oil hole (1352) is connected to the first central oil hole (1341), and the other end extends to the outer peripheral wall of the eccentric part (132). One end of the third side oil hole (1353) is connected to the second central oil hole (1342), and the other end extends to the outer peripheral wall of the long shaft (133).

3. The crankshaft according to claim 2, characterized in that: The shaft segment on the short shaft (131) and connected to the eccentric portion (132) is configured as a short shaft journal, and the first side oil hole (1351) is opened on the short shaft journal. The shaft segment on the long shaft (133) that connects to the eccentric portion (132) is configured as a long shaft journal, and the third side oil hole (1353) is formed on the long shaft journal. The end of the second central oil hole (1342) away from the first central oil hole (1341) is a closed end, and the closed end is located at the journal of the long shaft (133).

4. The crankshaft according to claim 1, characterized in that: The axial end face of the eccentric part (132) that connects with the short shaft (131) is the first shaft end, and the axial end face of the eccentric part (132) that connects with the long shaft (133) is the second shaft end. The position where the first central oil hole (1341) and the second central oil hole (1342) connect is located between the first shaft end and the second shaft end. The position where they connect is spaced from the first shaft end by a first preset distance, which is greater than 0. The position where they connect is spaced from the second shaft end by a second preset distance, which is greater than 0.

5. The crankshaft according to claim 2, characterized in that: The position where the first central oil hole (1341) and the second central oil hole (1342) meet is the connecting end. The position where the second side oil hole (1352) meets the first central oil hole (1341) is located at the connecting end or at a third preset distance from the connecting end, the third preset distance being greater than 0; and / or the first side oil hole (1351), the second side oil hole (1352) and the third side oil hole (1353) all extend in the radial direction.

6. The crankshaft according to any one of claims 1-5, characterized in that: The diameter of the first central oil hole (1341) is d1, the diameter of the second central oil hole (1342) is d2, the diameter of the long shaft (133) is D2, and d2 < 0.8d1, d2 / D2 ≤ 0.

45.

7. The crankshaft according to any one of claims 1-5, characterized in that: The short shaft (131) includes a first shaft segment (1311) and a second shaft segment (1312). The first shaft segment (1311) is away from the eccentric part (132) relative to the second shaft segment (1312) and is a non-fitting segment that does not mate with the lower flange. The second shaft segment (1312) is close to the eccentric part (132) relative to the first shaft segment (1311) and is a fitting segment that mates with the lower flange. The shaft diameter of the first shaft segment (1311) is D0, and the shaft diameter of the second shaft segment (1312) is D1, with D0 < D1.

8. The crankshaft according to claim 7, characterized in that: When both D0 and D are included 1、 When d1, d2 and D2 are, D0 < D1 - 0.3 mm, d2 < 0.65d1, and d2 / D2 ≤ 0.

32.

9. A compressor, characterized in that: The pump body assembly (1) includes a pump body assembly (1) and a housing (4). The pump body assembly (1) is disposed inside the housing (4). The pump body assembly (1) includes a crankshaft (13) according to any one of claims 1-8, and also includes an upper flange (11), a lower flange (15) and rollers (14). The upper flange (11) is engaged with the long shaft (133), the rollers (14) are engaged with the eccentric portion (132), and the lower flange (15) is engaged with the short shaft (131).

10. The compressor according to claim 9, characterized in that: The effective volume of the pump assembly is V, the maximum operating frequency of the compressor is f, and the inner diameter of the compressor housing is Dk. The parameters f, V, and Dk satisfy: 121≤f*V / Dk≤367, f≥120Hz, where V is in cm³ and Dk is in cm.

11. The compressor according to claim 9, characterized in that: The bottom of the housing (4) has an oil sump (5), when the short shaft (131) includes a first shaft segment (1311) and a second shaft segment (1312): The vertical distance between the lower end face of the first shaft segment (1311) of the crankshaft and the bottom of the oil sump (5) is set as h1, the axial length of the first shaft segment (1311) is L1, the axial length of the second shaft segment (1312) is L2, and the axial height of the lower flange (15) is h2. The parameters h1, h2, L1, and L2 satisfy: h2≤L2, 3mm≤h1≤35mm, and 8mm≤L1≤15mm.

12. The compressor according to claim 9, characterized in that: An oil guide component (8) is provided in the first central oil hole (1341) of the crankshaft. The oil guide component (8) is interference-fitted with the first central oil hole (1341). A second side oil hole (1352) is provided on the eccentric part (132). The assembly depth of the oil guide component (8) extends at least axially to the position of the second side oil hole (1352) of the eccentric part (132). Alternatively, a first oil guide component (81) is assembled in the first central oil hole (1341) of the crankshaft, and a second oil guide component (82) is assembled in the second central oil hole (1342). The first oil guide component (81) is interference-fitted with the first central oil hole (1341), and the second oil guide component (82) is interference-fitted with the second central oil hole (1342). Alternatively, the crankshaft may have an oil guiding component (8) in the first central oil hole (1341) and the second central oil hole (1342). The oil guiding component (8) is a segmented structure, including a first oil guiding section (801) and a second oil guiding section (802). The first oil guiding section (801) cooperates with the first central oil hole (1341), and the second oil guiding section (802) cooperates with the second central oil hole (1342).

13. An air conditioner, characterized in that: The compressor included in any one of claims 9-12.

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