An oil control mechanism, crankshaft, compressor and refrigeration equipment

Abstract

This application provides an oil control mechanism, a crankshaft, a compressor, and a refrigeration device, belonging to the field of compressor technology. The oil control mechanism, by setting a valve block and elastic element in the oil pumping channel inside the crankshaft, achieves precise adaptive control of the lubricating oil flow path, thereby simultaneously resolving the lubrication contradiction of reciprocating compressors under both low-speed start-up and high-frequency operation conditions.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more specifically, to an oil control mechanism, crankshaft, compressor, and refrigeration equipment. Background Technology

[0002] Compressors (such as fully enclosed reciprocating refrigeration compressors used in refrigerators) typically use centrifugal or spiral pump oil to deliver lubricating oil from the oil sump at the bottom of the housing to the top of the crankshaft to lubricate the bearings and moving parts.

[0003] Existing oil pumping systems generally include a crankshaft and an oil suction pipe. After the motor is powered on, the rotor drives the crankshaft to rotate, and the lubricating oil is drawn in from the lower end of the oil suction pipe under the action of centrifugal force, spirals up along the inside of the crankshaft to the top oil outlet, and then lubricates the various friction parts.

[0004] However, the above-mentioned oil pumping system has the following technical problems in actual operation: First, insufficient lubrication during low-speed startup. When the compressor stops, the lubricating oil inside the crankshaft flows back to the oil sump under gravity. During restart, especially at low speeds (such as below 1600 r / min), due to the small centrifugal force, the oil rises slowly, and the oil pressure inside the crankshaft has not yet been established in time, resulting in poor lubrication of the bearings and easily causing wear on components such as pistons, connecting rods, and piston pins.

[0005] Second, excessive oil discharge during high-frequency operation. When the compressor operates at high frequencies (such as 3600 r / min to 5000 r / min), the centrifugal force increases significantly, and the oil pumping volume increases accordingly. Excessive lubricating oil is discharged to the outside of the compressor along with the refrigerant, causing the oil level in the oil sump inside the casing to drop, affecting the efficiency of subsequent oiling, and even leading to wear of parts due to lack of oil.

[0006] In existing technologies, the oil pumping channels inside the crankshaft are usually simple straight-through structures, which cannot automatically adjust the oil pumping volume according to changes in rotational speed, making it difficult to simultaneously meet the needs of rapid oil supply during low-speed starts and the needs of oil control during high-frequency operation. Summary of the Invention

[0007] This application provides an oil control mechanism, a crankshaft, a compressor, and a refrigeration device. The oil control mechanism achieves precise adaptive control of the lubricating oil flow path by setting a valve block and an elastic element in the oil pump channel inside the crankshaft, thereby simultaneously solving the lubrication contradiction of the reciprocating compressor under both low-speed start-up and high-frequency operation conditions. Specifically, when the compressor stops or runs at low speed, the elastic element remains in a closed state under its own elastic force, preventing the lubricating oil in the upper oil chamber from flowing back downwards. This allows the oil to remain in the upper oil chamber, forming a reserve oil reservoir. This ensures that oil can be supplied to the friction pair immediately at the beginning of the next startup, significantly shortening the oil supply response time under low-speed conditions and effectively avoiding component wear caused by lubrication lag. When the compressor speed increases and the upward pumping force generated by the lower oil chamber increases, the elastic element can deform accordingly to open the oil passage, allowing lubricating oil to be smoothly replenished from the lower oil chamber to the upper oil chamber, meeting the lubrication requirements during stable operation. When the compressor is in a high-frequency operating state and the pumping force further increases, the elastic element's deformation opening is adaptively limited under the combined action of its own elastic restoring force and the gravity of the oil in the upper oil chamber. This automatically inhibits excessive lubricating oil from entering the upper oil chamber, reducing the loss of lubricating oil with the refrigerant discharge, maintaining the stability of the oil level in the oil sump, and ensuring subsequent oil supply efficiency. The entire control process relies solely on the mechanical response of the elastic element to the pumping oil force, requiring no additional external control devices or complex sensing and adjustment systems. It features a simple and reliable structure, rapid response, and real-time adaptive adjustment based on the compressor's actual operating conditions, significantly improving the compressor's lubrication reliability and operational stability over a wide speed range. Specifically: The first aspect of this application provides an oil control mechanism for installation in an oil pump passage inside a crankshaft. The oil control mechanism includes: A valve block, used to divide the pump oil passage into an upper oil chamber and a lower oil chamber, has an oil passage connecting the upper and lower oil chambers; and An elastic element is located on the side of the valve block near the upper oil chamber and covers the upper passage opening of the oil passage. The elastic element is configured to be able to elastically deform under the upward pumping force of the lower oil chamber to open the oil passage, and elastically reset to close the oil passage when the upward pumping force weakens, thereby preventing the oil in the upper oil chamber from falling back into the lower oil chamber.

[0008] In the above technical solution, the valve block has an upper valve surface, a lower valve surface, and an outer peripheral surface between the upper valve surface and the lower valve surface. The outer peripheral surface is used to seal with the channel wall of the pump oil passage, and the oil passage passes through the upper valve surface and the lower valve surface. The central region of the elastic element is connected to the central region of the upper valve face, and the outer peripheral region of the elastic element covers the upper channel opening of the oil passage located on one side of the upper valve face. It can elastically deform upward under the upward pumping force to open the upper channel opening.

[0009] In the above technical solution, the elastic element is preferably an elastic valve plate.

[0010] In the above technical solution, the central region of the elastic valve plate has a mounting part, and the mounting part is provided with a central hole. The central hole is used for the locking element to fix the elastic valve plate to the central region of the upper valve surface. The outer peripheral area of ​​the elastic valve plate has an annular valve body portion, the upper passage opening of the oil passage is configured as annular, and the upper passage opening can be covered by the valve body portion. There are multiple circumferentially distributed hollow sections between the mounting section and the valve body section, and a connecting rib is formed between two circumferentially adjacent hollow sections, which connects the mounting section and the valve body section.

[0011] In the above technical solution, the radial width of the upper channel opening is w1, and the radial width of the valve body is w2; Where 0.2mm≤w2-w1≤0.5mm.

[0012] In the above technical solution, the stiffness of the elastic valve plate is K, where 0.1 N / mm ≤ K ≤ 0.25 N / mm.

[0013] In the above technical solution, the valve block includes a valve core and a valve sleeve, and an oil passage is formed between the valve core and the valve sleeve. The oil passage includes a lower passage section and an upper passage section along its axial direction. The lower channel section includes multiple arc-shaped grooves that are separated by multiple connecting parts in the circumferential direction. The connecting parts are connected between the outer circumference of the valve core and the inner circumference of the valve sleeve. The upper channel section is an annular channel section.

[0014] In the above technical solution, the axial depth of the lower channel section is H1, and the axial depth of the upper channel section is H2, where H2 = (0.8~2) × H1.

[0015] In the above technical solution, the axial height of the valve core is lower than the axial height of the valve sleeve; The upper valve face of the valve core is flush with the upper valve face of the valve sleeve, and the lower valve face of the valve core is located above the lower valve face of the valve sleeve, so that a buffer cavity is formed between the lower valve face of the valve core and the lower valve face of the valve sleeve.

[0016] The second aspect of this application provides a crankshaft, which includes the oil control mechanism described above. The crankshaft has an oil pumping channel with an oil inlet at the bottom. The oil control mechanism is disposed in the oil pumping channel and divides the oil pumping channel into an upper oil chamber and a lower oil chamber.

[0017] In the above technical solution, the axial depth of the upper oil cavity is h1, and the axial depth of the lower oil cavity is h2, where h1≥1 / 3*h2.

[0018] In the above technical solution, the crankshaft includes a main shaft and an oil pump. The main shaft has an oil pump chamber with an opening at the bottom. The oil pump is installed at the lower opening of the oil pump chamber and defines an oil pumping channel between the oil pump chamber and the oil pump chamber. The bottom of the oil pump has an oil inlet.

[0019] In the above technical solution, the outer wall of the spindle is provided with a spiral oil groove that spirals upwards, wherein the spiral oil groove is connected to the upper oil cavity through an oil port opened in the spindle.

[0020] In the above technical solution, the oil port includes an upwardly extending upper oil port and a horizontally extending oil outlet; The bottom of the upper oil port is connected to the upper oil cavity, the top is connected to the oil outlet, and the outside of the oil outlet is connected to the spiral oil groove.

[0021] A third aspect of this application provides a compressor that includes the crankshaft described above.

[0022] In the above technical solution, the compressor is a variable frequency reciprocating compressor.

[0023] A fourth aspect of this application provides a refrigeration device, which includes the compressor described above.

[0024] By adopting the above technical solution, the present invention has the following beneficial effects compared with the prior art: The oil control mechanism in this embodiment achieves precise adaptive control of the lubricating oil flow path by setting a valve block and an elastic element in the oil pumping channel inside the crankshaft, thereby simultaneously solving the lubrication contradiction of the reciprocating compressor under both low-speed start-up and high-frequency operation conditions. Specifically, when the compressor stops or runs at low speed, the elastic element remains in a closed state under its own elastic force, preventing the lubricating oil in the upper oil chamber from flowing back downwards. This allows the oil to remain in the upper oil chamber, forming a reserve oil reservoir. This ensures that oil can be supplied to the friction pair immediately at the beginning of the next startup, significantly shortening the oil supply response time under low-speed conditions and effectively avoiding component wear caused by lubrication lag. When the compressor speed increases and the upward pumping force generated by the lower oil chamber increases, the elastic element can deform accordingly to open the oil passage, allowing lubricating oil to be smoothly replenished from the lower oil chamber to the upper oil chamber, meeting the lubrication requirements during stable operation. When the compressor is in a high-frequency operating state and the pumping force further increases, the elastic element's deformation opening is adaptively limited under the combined action of its own elastic restoring force and the gravity of the oil in the upper oil chamber. This automatically inhibits excessive lubricating oil from entering the upper oil chamber, reducing the loss of lubricating oil with the refrigerant discharge, maintaining the stability of the oil level in the oil sump, and ensuring subsequent oil supply efficiency. The entire control process can be achieved solely through the mechanical response of the elastic element to the pumping oil force, without the need for additional external control devices or complex sensing and adjustment systems. It has a simple and reliable structure, rapid response, and can adaptively adjust in real time according to the actual operating status of the compressor, significantly improving the lubrication reliability and operational stability of the compressor over a wide speed range. Attached Figure Description

[0025] Figure 1 This is an exploded structural diagram of the oil control mechanism in the embodiments of this application; Figure 2 This is a top view of the elastic valve plate with four connecting ribs in an embodiment of this application. Figure 3 This is a top view of the elastic valve plate with two connecting ribs in an embodiment of this application. Figure 4 This is a top view of the valve block with three connecting parts in an embodiment of this application. Figure 5 for Figure 4 A schematic diagram of the cross-sectional structure of the AA plane; Figure 6 This is a top view of the valve block with two connecting parts in an embodiment of this application. Figure 7 This is a top view of the valve block with four connecting parts in an embodiment of this application. Figure 8 This is a schematic diagram of the main structure of the crankshaft in an embodiment of this application; Figure 9 This is a cross-sectional view of the crankshaft in an embodiment of this application; Figure 10 This is a schematic diagram of the structure of the oil control mechanism assembled in the compressor in this application embodiment; Figure 11 This is a schematic diagram of the oil control mechanism of the compressor when it stops after operation in an embodiment of this application; Figure 12 This is a schematic diagram of the oil circuit structure of the compressor in the initial stage of low-frequency secondary start-up in the embodiments of this application; Figure 13 for Figure 12 Enlarged structural diagram at point A; Figure 14 This is a schematic diagram of the oil circuit structure of the compressor in this embodiment after a second start-up to a stable state; Figure 15 for Figure 14 A magnified structural diagram at point B in the middle.

[0026] in: 10-Valve block; 10a-Valve core; 10b-Valve sleeve; 101-Oil passage; 1011-Lower passage section; 1012-Upper passage section; 102-Connecting part; 103-Rivet hole; 20-Elastic valve plate; 201-Mounting part; 2011-Center hole; 202-Valve body; 203-Connecting rib; 204-Hollowed-out part; 30 - Locking element; 40 - Main spindle; 401 - Spiral oil groove; 402 - Upper oil port; 403 - Oil outlet; 404 - Pump oil chamber; 4041 - Upper oil chamber; 4042 - Lower oil chamber; 50 - Crankshaft; 501 - Inclined oil groove; 60-Piston; 70-link; 80-Cylinder seat; 90 - Oil pump; 901 - Oil inlet. Detailed Implementation

[0027] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0028] Throughout the specification and claims, the following terms will have at least the meaning explicitly associated herein, unless the context otherwise requires. The meanings defined below are not intended to limit the terms, but are merely illustrative examples. In the description of this invention, the phrase "in one embodiment" does not necessarily refer to the same embodiment, although it may refer to the same embodiment. Similarly, the phrase "in some embodiments," as used herein, does not necessarily refer to the same embodiment when used multiple times, although it may refer to the same embodiment. As used herein, the term "or" is an inclusive "or" operator and is equivalent to the term "and / or," unless the context clearly specifies otherwise. The term "based on" is not exclusive and allows for reliance on additional factors not described, unless the context clearly specifies otherwise. The word "exemplary" herein means "used as an example, instance, or illustration." Any embodiment described herein as "exemplary" is not necessarily to be construed as superior to or better than other embodiments. The scope of this invention is limited only by the scope of the appended claims, and any examples set forth in this specification are not intended to be limiting, but merely illustrate some of the many possible embodiments of the claimed invention. The various embodiments provided in this invention should not be construed as limiting the scope of protection of this invention.

[0029] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and 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. Therefore, they should not be construed as limitations on this invention.

[0030] Furthermore, the terms "first" and "second" are used for descriptive 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 one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0031] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0032] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0033] Example like Figures 1-15 As shown, the first aspect of this application provides an oil control mechanism for installation in the oil pump passage inside the crankshaft. The oil control mechanism includes: Valve block 10, used to divide the pump oil passage into an upper oil chamber 4041 and a lower oil chamber 4042, valve block 10 having an oil passage 101 connecting the upper oil chamber 4041 and the lower oil chamber 4042; and An elastic element is provided on the side of the valve block 10 near the upper oil chamber 4041 and covers the upper channel opening of the oil passage 101. The elastic element is configured to be able to elastically deform under the upward pumping force of the lower oil chamber 4042 to open the oil passage 101, and elastically reset to close the oil passage 101 when the upward pumping force weakens, thereby preventing the oil in the upper oil chamber 4041 from falling back into the lower oil chamber 4042.

[0034] The oil control mechanism in this embodiment achieves precise adaptive control of the lubricating oil flow path by setting a valve block 10 and an elastic element in the oil pumping channel inside the crankshaft. This simultaneously solves the lubrication contradiction of the reciprocating compressor under both low-speed start-up and high-frequency operation conditions. Specifically, when the compressor stops or runs at low speed, the elastic element remains in a closed state under its own elastic force, preventing the lubricating oil in the upper oil chamber 4041 from flowing back downwards. This allows the oil to remain in the upper oil chamber 4041 to form a reserve oil reservoir, enabling immediate oil supply to the friction pair at the initial stage of the next start-up. This significantly shortens the oil supply response time under low-speed conditions and effectively avoids component wear caused by lubrication lag. When the compressor speed increases and the upward pumping force generated by the lower oil chamber 4042 increases, the elastic element can correspondingly undergo elastic deformation. The elastic element opens the oil passage 101, allowing lubricating oil to smoothly flow from the lower oil chamber 4042 to the upper oil chamber 4041, meeting the lubrication requirements during stable operation. When the compressor operates at high frequency and the pumping force increases further, the elastic element, under the combined action of its own elastic restoring force and the gravity of the oil in the upper oil chamber 4041, adaptively limits its deformation opening. This automatically inhibits excessive lubricating oil from entering the upper oil chamber 4041, reducing lubricating oil loss with the refrigerant, maintaining a stable oil level in the oil sump, and ensuring efficient subsequent oiling. The entire control process relies solely on the mechanical response of the elastic element to the pumping force, requiring no additional external control devices or complex sensing and adjustment systems. It features a simple and reliable structure, rapid response, and real-time adaptive adjustment based on the compressor's actual operating state, significantly improving the compressor's lubrication reliability and operational stability over a wide speed range.

[0035] Furthermore, in some possible embodiments, the valve block 10 has an upper valve surface, a lower valve surface, and an outer peripheral surface between the upper valve surface and the lower valve surface. The outer peripheral surface is used to seal with the channel wall of the oil pump passage. The oil passage 101 passes through the upper valve surface and the lower valve surface. Preferably, the outer peripheral surface of the valve block 10 and the channel wall of the oil pump passage are sealed together by an interference fit. The central region of the elastic element is connected to the central region of the upper valve surface, and the outer peripheral region of the elastic element covers the upper channel opening of the oil passage 101 located on one side of the upper valve surface. It can elastically deform upward under the upward pumping force to open the upper channel opening.

[0036] In this embodiment, the sealing fit between the outer peripheral surface of the valve block 10 and the channel wall of the oil pumping channel effectively blocks the non-oil passage 101 between the upper oil chamber 4041 and the lower oil chamber 4042, preventing undesirable flow of oil from the periphery of the valve block 10 and ensuring the reliability of the dual-chamber separation. At the same time, the middle region of the elastic element is fixed to the central region of the valve block 10, and its outer peripheral region covers the upper channel opening of the valve block 10 to form a cantilever-like structure. This allows the outer peripheral region of the elastic element to undergo upward elastic deformation under the direct action of the upward oil pumping force, thereby accurately opening the upper channel opening.

[0037] This structure, with a fixed center and deformable outer periphery, offers a more sensitive mechanical response compared to the reverse configuration of a fixed outer periphery and a raised center. Due to the smaller mass and longer deformation stroke of the outer periphery, it can achieve an effective opening under lower pumping forces, improving the oil supply response speed during low-speed startup. Furthermore, the fixed center configuration simplifies the installation structure and the arrangement of the locking element 30, making assembly more convenient and reliable. Of course, those skilled in the art will understand that setting the elastic element to a fixed outer periphery with a center that can be lifted by pressure can also achieve the basic function of adaptive opening and closing based on pumping forces. However, the fixed center and deformable outer periphery configuration offers superior technical advantages in terms of response sensitivity and structural simplification, and is therefore presented as the preferred solution.

[0038] Furthermore, the aforementioned elastic element is preferably an elastic valve plate 20.

[0039] Of course, in some embodiments not shown, the elastic element described above can also be an elastic component such as a rubber sheet or rubber pad. However, it is preferable to use an elastic valve plate as the elastic element, which can better utilize the unique rigid-elastic composite characteristics of the valve plate to achieve a better adaptive check pumping effect.

[0040] Specifically, the elastic valve plate, being a rigid-elastic composite structure, differs fundamentally from conventional elastic components such as flexible diaphragms and rubber gaskets. It relies on its own rigidity to provide a stable sealing surface and reset reference, ensuring that the oil in the upper oil chamber does not flow back after the compressor stops. Simultaneously, it achieves oil pressure response through its elastic region. With the center fixed, the outer periphery can be lifted upwards in a unified, synchronous, and controllable manner under pump oil pressure, without wrinkling, skewing, or adhesion failure. Its matching rigidity and elasticity also automatically limit the opening at high speeds, preventing excessive pumping of oil and truly achieving an adaptive check-back pumping effect of "low-speed oil storage, rapid start-up oil supply, and high-speed precise flow restriction."

[0041] Furthermore, in some possible embodiments, the central region of the elastic valve plate 20 has a mounting portion 201, the mounting portion 201 is provided with a central hole 2011, the central hole 2011 is used for the locking member 30 to fix the elastic valve plate 20 to the central region of the upper valve surface. Preferably, the center of the upper valve surface of the valve block 10 is provided with a rivet hole 103, and the locking member 30 is preferably a valve rivet that can cooperate with the rivet hole 103 to lock, so that the central region of the elastic valve plate 20 can be firmly fixed to the central region of the upper end face of the valve block 10. Furthermore, the outer peripheral area of ​​the elastic valve plate 20 has an annular valve body portion 202, the upper channel opening of the oil passage 101 is configured as annular, and the upper channel opening can be covered by the valve body portion 202. That is, the upper valve surface of the valve block 10 is provided with an annular channel for controlling the rise of lubricating oil. The elastic valve plate 20 is fixed to the upper valve surface of the valve block 10 by means of valve rivet riveting. The edge valve body portion 202 of the elastic valve plate 20 cooperates with the annular channel opening of the upper valve surface of the valve block 10 to control the pumping oil volume. There are multiple circumferentially distributed hollow portions 204 between the mounting portion 201 and the valve body portion 202, and a connecting rib 203 is formed between two circumferentially adjacent hollow portions 204, and the connecting rib 203 connects the mounting portion 201 and the valve body portion 202.

[0042] In this embodiment, the central region of the elastic valve plate 20 is a mounting portion 201 with a central hole 2011, providing a clear fixing position for the locking member 30. This ensures a reliable connection between the valve plate and the central region of the valve block 10, guaranteeing the positional stability of the valve plate during repeated elastic deformation and preventing displacement or detachment due to insecure fixing. Simultaneously, the outer periphery is an annular valve body portion 202, with the upper channel opening of the oil passage 101 correspondingly configured as an annular structure, forming a complete annular covering fit. This ensures the effectiveness of the sealing closure and the uniformity of oil flow during opening. More importantly, multiple circumferentially distributed hollow portions 204 are provided between the mounting portion 201 and the valve body portion 202, and connecting ribs 20 are formed between adjacent hollow portions 204 to connect them. 3. This structure provides necessary space for the elastic deformation of the valve body 202 through the hollow part 204, allowing the annular valve body 202 to smoothly lift upward and open the channel under the upward pumping force. At the same time, the elastic restoring force of the connecting ribs 203 ensures that the valve body 202 can close the channel in time when the pumping force weakens. The circumferential distribution of multiple connecting ribs 203 also makes the deformation of the annular valve body 202 more uniform and symmetrical, avoiding local stress concentration and skew deformation, improving the fatigue life of the valve plate and the reliability of long-term operation. Thus, the structure and function of the elastic valve plate 20 are integrated and optimized as a whole, and it forms a precise match with the annular oil passage 101, improving the working stability and response consistency of the oil control mechanism.

[0043] It should be noted that in the embodiments of this application, the number of connecting ribs 203 on the elastic valve plate 20 can be two, three, four, etc., and the number is not limited. However, regardless of how many connecting ribs 203 are provided, preferably, the multiple connecting ribs 203 are evenly distributed circumferentially along the center line of the elastic valve plate 20.

[0044] Furthermore, in some possible implementations, the radial width of the upper channel opening is w1, and the radial width of the valve body portion 202 is w2. Where 0.2mm≤w2-w1≤0.5mm.

[0045] In this embodiment, the difference between the radial width w1 of the upper channel opening and the radial width w2 of the valve body 202 ensures that the valve body 202 forms an appropriate radial overlap allowance when covering the upper channel opening. This design ensures that the valve body 202 can completely cover the channel opening to achieve a reliable seal and prevent undesirable leakage of oil from the edge gaps. It also provides a suitable radial clearance space for the elastic deformation of the valve body 202, avoiding mechanical interference or jamming between the valve body 202 and the edge of the channel opening due to manufacturing errors or thermal expansion. At the same time, the optimized setting of this difference range can ensure that the valve body 202 obtains an appropriate effective flow area when opening, while ensuring sealing performance. This balances sealing reliability and flow efficiency, further improving the working stability and adaptability of the oil control mechanism under different working conditions.

[0046] Furthermore, in some possible implementations, the stiffness of the resilient valve plate 20 is K, where 0.1 N / mm ≤ K ≤ 0.25 N / mm.

[0047] In this embodiment, by designing the stiffness range of the elastic valve plate 20 to be between 0.1 N / mm and 0.25 N / mm, the technical drawbacks caused by excessively low or high stiffness are effectively avoided, and the mechanical properties of the valve plate are precisely matched with the variable frequency operation requirements of the compressor.

[0048] Specifically, when the stiffness is below the lower limit of this range, the elastic restoring force of the valve plate is insufficient. When the compressor is running at high frequency and the lower oil chamber 4042 generates a large pumping force, the valve plate is prone to excessive deformation or even complete flipping. This results in the upper channel opening being too large and the amount of oil entering the upper oil chamber 4041 being out of control, failing to effectively suppress excessive pumping. At the same time, the excessively low stiffness also makes it difficult for the valve plate to tightly close the channel after the machine stops, reducing the oil storage capacity of the upper oil chamber 4041. When the stiffness is above the upper limit of this range, the opening resistance of the valve plate is too large. When the compressor starts at low speed and the pumping force is small, the valve plate is difficult to deform effectively to open the channel. The oil in the lower oil chamber 4042 cannot be replenished to the upper oil chamber 4041 in time, resulting in insufficient oil supply capacity under low-speed conditions. Furthermore, excessively high stiffness will also make the valve plate sluggish in response to changes in pumping force, losing its adaptive adjustment sensitivity. By setting the stiffness within the aforementioned range, the valve plate can have sufficient sensitivity to smoothly open the channel and ensure initial oil supply under low-speed conditions, while having moderate resistance to deformation under high-frequency conditions to limit the opening and control the pump oil volume. At the same time, it can reliably reset and close after shutdown to maintain oil storage. Thus, it achieves overall adaptive optimization for operating conditions over a wide speed range, significantly improving the comprehensive working performance and reliability of the oil control mechanism.

[0049] Furthermore, in some possible embodiments, the valve block 10 includes a valve core 10a and a valve sleeve 10b, with an oil passage 101 formed between the valve core 10a and the valve sleeve 10b, and the oil passage 101 includes a lower passage section 1011 and an upper passage section 1012 along its axial direction. The lower channel section 1011 includes multiple arc-shaped grooves separated by multiple connecting portions 102 in the circumferential direction. The connecting portions 102 are connected between the outer periphery of the valve core 10a and the inner periphery of the valve sleeve 10b. The upper channel section 1012 is an annular channel section.

[0050] It should be noted that the upper channel segment 1012 mentioned in the embodiments of this application can be called an annular channel segment as long as it is continuously connected along the circumference of the valve block 10.

[0051] In this embodiment, the valve block 10 is configured as a structure including a valve core 10a and a valve sleeve 10b, with an oil passage 101 formed between them. This oil passage 101 can be axially segmented into a lower passage segment 1011 and an upper passage segment 1012. The lower passage segment 1011 is designed as multiple arc-shaped groove segments separated circumferentially by multiple connecting parts 102. The connecting parts 102 ensure the structural strength and stability between the valve core 10a and the valve sleeve 10b. For positional stability, the arc-shaped groove provides multiple circumferentially distributed upward flow channels for the oil in the lower oil chamber 4042, allowing the oil to enter the upper channel section 1012 evenly from all circumferential positions, avoiding the flow deviation and eddy current phenomena caused by unilateral oil inlet; and designing the upper channel section 1012 as an annular channel section ensures a precise match with the annular valve body 202 of the elastic valve plate 20, ensuring the integrity of the seal of the valve body 202 and the uniformity of oil flow when opened.

[0052] Whether the nested structure is integrally molded or assembled separately, it can effectively construct complex internal flow channels. While ensuring the overall structural strength of the valve block 10, it optimizes the oil flow path and makes it work in synergy with the elastic valve plate 20, further improving the structural reliability and operational stability of the oil control mechanism.

[0053] It should be noted that the connecting part 102 between the valve core 10a and the valve sleeve 10b can be provided in two, three, four, etc., and the number of such parts is not limited. However, regardless of the number of connecting parts 102 provided, preferably, the multiple connecting parts 102 are evenly distributed circumferentially along the center line of the valve block 10.

[0054] Furthermore, in some possible implementations, the axial depth of the lower channel segment 1011 is H1, and the axial depth of the upper channel segment 1012 is H2, where H2 = (0.8~2) × H1.

[0055] In this embodiment, the proportional relationship between the axial depth H1 of the lower channel section 1011 and the axial depth H2 of the upper channel section 1012, combined with the difference in radial width between the upper channel section 1012 and the valve body 202, achieves coordinated optimization of the geometric parameters of the oil passage 101 and the working characteristics of the elastic valve plate 20.

[0056] Specifically, when the ratio of H2 to H1 is below the lower limit of this range, the volume of the upper channel section 1012 is too small, resulting in insufficient oil storage in the upper oil chamber 4041 when the machine stops, making it difficult to meet the lubrication requirements at the initial stage of low-frequency start-up and weakening the technical effect of rapid oiling. When the ratio is above the upper limit of this range, the upper channel section 1012 is too deep, which not only increases the opening stroke and elastic deformation required by the valve body 202, leading to increased opening resistance and decreased response sensitivity, but also wastes axial space and results in a non-compact structure. Setting H2 in the range of (0.8~2)×H1 ensures that the upper channel section 1012 has sufficient axial depth to form an effective oil storage space, while avoiding excessive requirements on the opening stroke of the valve body 202, ensuring the adaptive performance of the elastic valve plate 20, which can open smoothly at low frequencies and effectively limit flow at high frequencies.

[0057] Furthermore, in some possible implementations, the axial height of the valve core 10a is lower than the axial height of the valve sleeve 10b; The upper valve surface of valve core 10a is flush with the upper valve surface of valve sleeve 10b, and the lower valve surface of valve core 10a is located above the lower valve surface of valve sleeve 10b, so that a buffer cavity is formed between the lower valve surface of valve core 10a and the lower valve surface of valve sleeve 10b.

[0058] In this embodiment, the design of the buffer chamber can, on the one hand, serve as a storage space for lubricating oil, and on the other hand, store some of the refrigerant gas that evaporates from the lubricating oil, thereby playing a certain buffering role.

[0059] Furthermore, a second aspect of the present application provides a crankshaft that includes the aforementioned oil control mechanism. The crankshaft has an oil pumping channel with an oil inlet 901 at its bottom end. The oil control mechanism is disposed in the oil pumping channel and divides the oil pumping channel into an upper oil chamber 4041 and a lower oil chamber 4042.

[0060] In this embodiment, the crankshaft has an oil pumping channel with an oil inlet 901 at its bottom, and the aforementioned oil control mechanism is integrated into this channel. This achieves an integrated structural design between the oil control mechanism and the crankshaft body, allowing the oil control mechanism to directly utilize the centrifugal force generated by the crankshaft's rotation as the oil pumping power source. This eliminates the need for an independent drive device or external control components, simplifying the overall structural layout and assembly process of the compressor. Simultaneously, the oil control mechanism divides the oil pumping channel into an upper oil chamber 4041 and a lower oil chamber 4042, ensuring that the lower oil... The cavity 4042 is directly connected to the bottom oil inlet 901 to receive lubricating oil from the oil sump, while the upper oil cavity 4041 is connected to the oil outlet structure at the top of the crankshaft to supply oil to the friction pair. This cavity-based oil control method built into the crankshaft not only makes full use of the internal space of the crankshaft, but also enables the oil control mechanism to rotate synchronously with the crankshaft and directly respond to changes in speed to adaptively adjust the pump oil volume. As a result, the overall structure of the compressor lubrication system is compact, the response is real-time, and the control is adaptive, which significantly improves the operational reliability and energy efficiency of the variable frequency reciprocating compressor.

[0061] Furthermore, in some possible implementations, the axial depth of the upper oil cavity 4041 is h1, and the axial depth of the lower oil cavity 4042 is h2, where h1 ≥ 1 / 3 * h2.

[0062] In this embodiment, the optimized configuration of the oil storage space distribution inside the crankshaft is achieved by limiting the proportional relationship between the axial depth h1 of the upper oil chamber 4041 and the axial depth h2 of the lower oil chamber 4042. Specifically, when h1 < 1 / 3 * h2, the volume of the upper oil chamber 4041 is too small, resulting in insufficient reserve oil after shutdown. This means that sufficient initial lubrication cannot be provided at the beginning of the next compressor start-up, weakening the technical effect of rapid oiling. At the same time, the excessively small upper space also limits the effective deformation stroke of the elastic element, affecting its adaptive adjustment performance.

[0063] Furthermore, in some possible embodiments, the crankshaft includes a main shaft 40 and an oil pump 90. Preferably, the oil pump 90 is a centrifugal pump. The main shaft 40 has an oil pump chamber 404 with an opening at the bottom. The oil pump 90 is installed at the lower opening of the oil pump chamber 404 and defines an oil pumping channel between the oil pump chamber 404 and the oil pump 90. The bottom of the oil pump 90 has an oil inlet 901 with a diameter between 2.5 mm and 5 mm.

[0064] The crankshaft in this embodiment includes a main shaft 40 and an oil pump 90. The oil pumping chamber 404, which is open at the bottom of the main shaft 40, cooperates with the oil pump 90 installed at its lower end to define the oil pumping channel. This avoids the high-difficulty process requirements of directly machining deep and long blind holes or complex internal flow channels on the solid main shaft 40, significantly reducing the manufacturing difficulty and cost of the crankshaft. At the same time, this split assembly method allows the oil control mechanism to be conveniently pre-installed in the oil pump 90 or the oil pumping chamber 404, and then the oil pump 90 and the main shaft 40 can be assembled to complete the overall assembly, simplifying the installation process and positioning accuracy control of the oil control mechanism. In addition, the oil inlet 901 is directly set at the bottom of the oil pump 90, so that it is located at the lowest end of the crankshaft and can be directly close to the oil surface of the oil sump. This facilitates the smooth entry of lubricating oil into the oil pumping channel under the action of centrifugal force, reduces the oil suction resistance, and thus achieves overall optimization of the crankshaft structure and improvement of assembly convenience, while ensuring the oil suction efficiency of the oil pumping channel.

[0065] Furthermore, in some possible embodiments, the outer wall of the spindle 40 is provided with a spiral oil groove 401 that spirals upward, wherein the spiral oil groove 401 is connected to the upper oil cavity 4041 through an oil port opened in the spindle 40.

[0066] In this embodiment, the outer wall of the main shaft 40 is provided with a spiral oil groove 401 that rises in a spiral manner. The spiral oil groove 401 is connected to the upper oil cavity 4041 through an oil port opened inside the main shaft 40, realizing the continuous delivery of lubricating oil in the upper oil cavity 4041 to the friction pair at the top of the crankshaft. The spiral rising structure of the spiral oil groove 401 allows the lubricating oil to rise continuously with the rotation of the main shaft 40 by means of centrifugal force and spiral guidance, forming a stable oil film supply path, avoiding the problem of oil backflow under gravity in traditional straight groove or channel oil supply methods. At the same time, the spiral oil groove The direct connection between 401 and the upper oil chamber 4041 allows the oil adjusted by the oil control mechanism to enter the spiral rising channel immediately, reducing intermediate transition links and oil retention, and improving the oil supply response speed and continuity. In addition, the distribution pattern of the spiral oil groove 401 along the outer wall of the main shaft 40 can also provide uniform circumferential lubrication to the friction pairs such as the main shaft 40 and bearings, improving the uneven wear phenomenon caused by uneven local lubrication. Thus, the lubricating oil is smoothly discharged from the inside of the crankshaft to the outside and efficiently distributed to the friction pairs, further improving the lubrication reliability and operational stability of the crankshaft.

[0067] Furthermore, in some possible embodiments, the oil port includes an upwardly extending upper oil port 402 and a horizontally extending outlet 403. The bottom of the upper oil port 402 is connected to the upper oil cavity 4041, and the top is connected to the oil outlet 403. The outer side of the oil outlet 403 is connected to the spiral oil groove 401.

[0068] In this embodiment, the oil port is designed as a combination of an upwardly extending upper oil port 402 and a horizontally extending oil outlet 403, which optimizes the oil flow path between the upper oil cavity 4041 and the spiral oil groove 401. The upwardly extending upper oil port 402 allows the lubricating oil in the upper oil cavity 4041 to flow smoothly upward along the inclined direction under centrifugal force, reducing the flow resistance and energy loss of the oil during the turning process, and avoiding oil stagnation and air bubble mixing caused by vertical rise or sharp turning. The horizontally extending oil outlet 403, on the other hand, allows the upwardly extending upper oil port 402 to flow smoothly upward along the inclined direction under centrifugal force, reducing the flow resistance and energy loss of the oil during the turning process, and avoiding oil stagnation and air bubble mixing caused by vertical rise or sharp turning. The lubricating oil is smoothly guided to the spiral oil groove 401 on the outer wall of the main shaft 40, allowing the oil to enter the spiral rising channel at a suitable angle and speed, ensuring the stability and continuity of the oil flow. At the same time, this segmented oil port design creates a step-by-step connection between the upper oil chamber 4041, the inclined upper oil port 402, the horizontal oil outlet 403, and the spiral oil groove 401. Each flow channel performs its own function and is interconnected, achieving efficient and stable delivery of lubricating oil from the inside of the crankshaft to the external friction pair, further improving the flow efficiency and reliability of the oil supply system.

[0069] As can be seen from the above, in this embodiment of the application, the oil control mechanism composed of valve block 10, elastic valve plate 20 and valve rivet is located in the middle area of ​​crankshaft center pump oil chamber 404. The oil control mechanism divides the internal oil storage space of the crankshaft into two parts: upper oil chamber 4041 and lower oil chamber 4042, with space heights of h1 and h2 respectively. The relationship between the two satisfies h1≥1 / 3*h2, and the minimum size of h2 is not less than 20mm and the maximum is not more than 100mm.

[0070] When the compressor is working, the crankshaft and centrifugal pump rotate under the drive of the motor rotor. The lubricating oil at the bottom of the compressor housing enters the lower oil chamber 4042 inside the crankshaft through the oil inlet 901 of the centrifugal pump. Under the action of centrifugal force, the lubricating oil rises along the inner wall of the crankshaft, forming a parabolic hollow isobaric oil surface. When the speed increases to a certain level, the lubricating oil on the wall reaches the height of the elastic valve plate 20 of the oil control mechanism, and pushes open the elastic valve plate 20 to enter the upper oil chamber 4041 inside the crankshaft. Then, it reaches the top of the crankshaft through the oil port and the spiral oil groove 401 on the outer wall, lubricating the various friction pairs composed of the connecting rod 70, piston 60, crankshaft and cylinder seat 80. The flow path of the lubricating oil in the crankshaft is as follows: centrifugal pump oil inlet 901 → lower oil chamber 4042 → elastic valve plate 20 → upper oil chamber 4041 → crankshaft oil port discharge.

[0071] It should be noted that the crankshaft also includes an upper crank 50, on which an inclined oil groove 501 is provided, and a spiral oil groove 401 is provided on the main shaft 40. The upper oil cavity 4041 inside the crankshaft has an upwardly inclined upper oil port 402 and a horizontally oriented oil outlet 403, which are connected to each other. The oil outlet 403 is integrated with the spiral oil groove 401 on the outer wall of the crankshaft.

[0072] Furthermore, a third aspect of this application provides a compressor that includes the crankshaft described above.

[0073] Preferably, the compressor described above is a variable frequency reciprocating compressor.

[0074] When the compressor in this embodiment is equipped with the aforementioned crankshaft, after the compressor stops running, due to the action of the elastic valve plate 20 in the oil control mechanism, the lubricating oil located in the upper oil chamber 4041 of the crankshaft cannot return to the bottom oil sump of the housing, thus forming an oil storage chamber 4041. When the compressor starts in the next cycle, the presence of the oil stored in the upper oil chamber 4041 reduces the compressor's upward resistance and greatly improves the compressor's oil pumping capacity during low-frequency startup.

[0075] It should be noted that the lubricating oil stored in the upper oil chamber 4041 in this embodiment can reduce the upward resistance of the lubricating oil during low-frequency operation of the compressor because: the oil pumping height is lowered. Previously, the oil pumping height from the oil sump was 50mm, but now, due to the oil storage pump 90 at the top, the oil height is reduced to 10mm. Under the same centrifugal force, the pumping speed increases, thereby reducing the upward resistance of the lubricating oil during low-frequency operation of the compressor.

[0076] Furthermore, during the initial stage of low-frequency secondary start-up, the compressor forms an upper oil chamber 4041 and a lower oil chamber 4042 within the crankshaft. In the initial startup phase, due to the low crankshaft speed, the lubricating oil level in the lower oil chamber 4042, close to the inner wall edge, is low, and the elastic valve 20 of the oil control mechanism is closed. The lubricating oil remaining in the upper oil chamber 4041, with its lower level below the oil outlet 403, plays a primary role in lubricating the crankshaft.

[0077] Furthermore, when the compressor starts up again and the speed stabilizes, the lubricating oil that is close to the inner wall of the lower oil chamber 4042 rises to the position of the upper annular channel opening of the valve block 10. It can then use the lift force to open the elastic valve plate 20 and enter the upper oil chamber 4041 to replenish the lubricating oil inside the upper oil chamber 4041, ensuring that sufficient lubricating oil flows into the oil outlet of the crankshaft and forming a stable oil supply.

[0078] Furthermore, when the compressor is running at high speed, as more lubricating oil enters the upper oil chamber 4041 of the crankshaft, the elastic valve plate 20 is opened while being subjected to the downward gravity of the lubricating oil inside the upper oil chamber 4041. As a result, the opening angle of the elastic valve plate 20 becomes smaller, and the amount of oil entering the upper oil chamber 4041 under high-speed operation is relatively reduced, but it is still sufficient to meet the lubricating oil requirements of the bearing. This greatly reduces the amount of oil discharged by the compressor under high-frequency operation.

[0079] Furthermore, a fourth aspect of this application provides a refrigeration device that includes the compressor described above.

[0080] In the above embodiments of this application, the descriptions of each embodiment have their own emphasis. Parts not described in detail in a certain embodiment can be referred to in the relevant descriptions of other embodiments. The steps illustrated in the related flowcharts can be executed in a computer system such as a set of computer-executable instructions. Furthermore, although a logical order is shown in the flowcharts, in some cases, the steps shown or described may be performed in a different order than that shown here. In other words, the order of steps described in the foregoing embodiments is merely an example. Reasonable adjustments to the order of steps based on the content of the embodiments of this application are also within the protection scope of the embodiments of this application.

[0081] The sequence numbers or order of description of the embodiments in this application are for descriptive purposes only and do not represent the superiority or inferiority of the embodiments.

[0082] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0083] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. An oil control mechanism, characterized in that, The oil control mechanism, used for installation in the oil pump passage inside the crankshaft, includes: A valve block (10) for dividing the pump oil passage into an upper oil chamber (4041) and a lower oil chamber (4042), the valve block (10) having an oil passage (101) connecting the upper oil chamber (4041) and the lower oil chamber (4042); and An elastic element is provided on the side of the valve block (10) near the upper oil chamber (4041) and covers the upper channel opening of the oil passage (101); The elastic element is configured to be able to elastically deform under the upward pumping force of the lower oil chamber (4042) to open the oil passage (101), and elastically reset to close the oil passage (101) when the upward pumping force weakens, thereby preventing the oil in the upper oil chamber (4041) from falling back into the lower oil chamber (4042).

2. The oil control mechanism according to claim 1, characterized in that, The valve block (10) has an upper valve surface, a lower valve surface, and an outer peripheral surface between the upper valve surface and the lower valve surface. The outer peripheral surface is used to seal with the channel wall of the oil pump channel. The oil passage (101) passes through the upper valve surface and the lower valve surface. The central region of the elastic element is connected to the central region of the upper valve surface, and the outer peripheral region of the elastic element covers the upper channel opening of the oil passage (101) located on one side of the upper valve surface, and can be elastically deformed upward under the upward pumping force to open the upper channel opening.

3. The oil control mechanism according to claim 2, characterized in that, The elastic element is an elastic valve plate (20).

4. The oil control mechanism according to claim 3, characterized in that, The central region of the elastic valve plate (20) has a mounting portion (201), the mounting portion (201) is provided with a central hole (2011), the central hole (2011) is used for the locking member (30) to fix the elastic valve plate (20) to the central region of the upper valve surface; The outer peripheral region of the elastic valve plate (20) has an annular valve body portion (202), the upper channel opening of the oil passage (101) is configured as annular, and the upper channel opening can be covered by the valve body portion (202). The mounting part (201) and the valve body part (202) have a plurality of circumferentially distributed hollow parts (204), and a connecting rib (203) is formed between two circumferentially adjacent hollow parts (204), and the connecting rib (203) connects the mounting part (201) and the valve body part (202).

5. The oil control mechanism according to claim 4, characterized in that, The radial width of the upper channel opening is w1, and the radial width of the valve body (202) is w2; Where 0.2mm≤w2-w1≤0.5mm.

6. The oil control mechanism according to claim 3, characterized in that, The stiffness of the elastic valve plate (20) is K, where 0.1 N / mm ≤ K ≤ 0.25 N / mm.

7. The oil control mechanism according to any one of claims 4-6, characterized in that, The valve block (10) includes a valve core (10a) and a valve sleeve (10b), and the oil passage (101) is formed between the valve core (10a) and the valve sleeve (10b). The oil passage (101) includes a lower passage section (1011) and an upper passage section (1012) along its axial direction. The lower channel section (1011) includes multiple arc-shaped grooves separated in the circumferential direction by multiple connecting parts (102), the connecting parts (102) being connected between the outer periphery of the valve core (10a) and the inner periphery of the valve sleeve (10b), and the upper channel section (1012) being an annular channel section.

8. The oil control mechanism according to claim 7, characterized in that, The axial depth of the lower channel segment (1011) is H1, and the axial depth of the upper channel segment (1012) is H2, where H2 = (0.8~2) × H1.

9. The oil control mechanism according to claim 7, characterized in that, The axial height of the valve core (10a) is lower than the axial height of the valve sleeve (10b); The upper valve surface of the valve core (10a) is flush with the upper valve surface of the valve sleeve (10b), and the lower valve surface of the valve core (10a) is located above the lower valve surface of the valve sleeve (10b), so that a buffer cavity is formed between the lower valve surface of the valve core (10a) and the lower valve surface of the valve sleeve (10b).

10. A crankshaft, characterized in that, The crankshaft includes an oil control mechanism according to any one of claims 1-9, wherein the crankshaft has an oil pumping channel with an oil inlet (901) at the bottom end, the oil control mechanism is disposed in the oil pumping channel and divides the oil pumping channel into an upper oil chamber (4041) and a lower oil chamber (4042).

11. The crankshaft according to claim 10, characterized in that, The axial depth of the upper oil cavity (4041) is h1, and the axial depth of the lower oil cavity (4042) is h2, where h1≥1 / 3*h2.

12. The crankshaft according to claim 10, characterized in that, The crankshaft includes a main shaft (40) and an oil pump (90). The main shaft (40) has an oil pump chamber (404) with an opening at the bottom. The oil pump (90) is installed at the lower opening of the oil pump chamber (404) and defines the oil pumping channel between the oil pump chamber (404) and the oil pump (90). The bottom of the oil pump (90) has an oil inlet (901).

13. The crankshaft according to claim 12, characterized in that, The outer wall of the main shaft (40) is provided with a spiral oil groove (401) that spirals upward, wherein the spiral oil groove (401) is connected to the upper oil cavity (4041) through an oil port opened in the main shaft (40).

14. The crankshaft according to claim 13, characterized in that, The oil port includes an upwardly extending upper oil port (402) and a horizontally extending outlet (403). The bottom of the upper oil port (402) is connected to the upper oil cavity (4041), the top is connected to the oil outlet (403), and the outer side of the oil outlet (403) is connected to the spiral oil groove (401).

15. A compressor, characterized in that, The crankshaft includes any one of claims 10-14.

16. The compressor according to claim 15, characterized in that, The compressor is a variable frequency reciprocating compressor.

17. A refrigeration device, characterized in that, Includes the compressor described in claim 15 or 16.

Images