An adaptive dynamic balance lubrication crankshaft assembly and compressor

Abstract

This invention provides an adaptive dynamic balance lubrication crankshaft assembly and compressor, relating to the field of compressors. It addresses the problem of poor compressor operation stability caused by poor lubrication performance at the crankshaft tip and mismatched counterweight torque. The solution involves reducing the amount of refrigerant oil thrown into the cylinder, temporary storage and reflux of the refrigerant oil, and adaptive adjustment of the crankshaft assembly's center of gravity. An oil baffle support plate constrains the outward throwing of refrigerant oil at the crankshaft and connecting rod mating points and refluxes it, improving lubrication and reducing operational instability. The support frame, in conjunction with the oil baffle support plate, can adjust the center of gravity to balance the torque of the crankshaft's eccentric portion, thus improving the compressor's operational stability.

Description

Technical Field

[0001] This invention relates to the field of compressors, and more specifically to an adaptive dynamic balance lubrication crankshaft assembly and a compressor. Background Technology

[0002] During operation, the smoothness of fully hermetic reciprocating compressors needs to be considered to reduce vibration and noise. However, due to their structural characteristics, fully hermetic reciprocating compressors always have unbalanced forces. To reduce these unbalanced forces, a balance weight of appropriate size is usually installed in the opposite direction of the crankshaft eccentricity. The balancing torque required by the compressor at high and low speeds is different. If the torque of the counterweight does not change, the vibration will increase when the speed changes, affecting the smoothness of the compressor's operation.

[0003] Furthermore, when compressor lubrication uses crankshaft-based oil slinging, meaning the spiral oil groove on the eccentric part of the crankshaft runs through the top without obstruction, the refrigerant oil is thrown into the cylinder by centrifugal force. Excessive refrigerant oil in the cylinder causes large oil discharge, leading to cylinder load changes and vibrations. This not only results in poor compressor stability but also affects the refrigeration effect of the refrigeration system. With crankshaft-based lubrication, after the compressor stops, the refrigerant oil gradually leaks from the crankshaft eccentric part and the rotating contact point of the connecting rod. During the subsequent start-up of the compressor, the distance between the crankshaft eccentric part and the oil sump is also relatively large. The long distance between the crankshaft and cylinder causes short-term oilless wear, and the cumulative wear of the crankshaft eccentric part will cause the rotational clearance to increase, resulting in running vibration between the crankshaft and cylinder, affecting the operating stability of the compressor and reducing its service life. At present, non-through spiral oil grooves are used to reduce the outward splashing of refrigeration oil to reduce the impact on the cylinder. However, the vibration problem caused by the inability to adapt the counterweight torque due to changes in speed and the problem of short-term oilless wear of the crankshaft eccentric part have not been solved. As a result, the fully hermetically sealed reciprocating compressor still has problems with poor operating stability, large vibration and high noise. Summary of the Invention

[0004] The purpose of this invention is to address the shortcomings of existing technologies by providing an adaptive dynamic balance lubrication crankshaft assembly and compressor. An oil baffle support plate is installed at the top of the crankshaft to block and collect the refrigerant oil flowing upwards after lubrication. After flowing through the oil reservoir, the oil flows back to the rotating positions of the crankshaft and connecting rod through auxiliary oil holes. After shutdown, the refrigerant oil remaining in the oil reservoir can quickly enter the rotating positions for lubrication during the next startup, thereby mitigating the problem of oilless wear. Combined with a variable center of mass support frame to balance the torque of the crankshaft's eccentric part, the crankshaft's running stability is improved, thus ensuring the smooth operation of the compressor.

[0005] The first objective of this invention is to provide an adaptive dynamic balance lubrication crankshaft assembly, which employs the following solution:

[0006] include:

[0007] The crankshaft has a eccentric part at the top with separate spiral oil grooves and auxiliary oil holes. The auxiliary oil holes connect the end face of the eccentric part and the outer circumferential surface.

[0008] An oil baffle support plate is provided with an oil storage tank. The oil inlet of the oil storage tank is connected to a spiral oil groove, and the oil outlet is connected to an auxiliary oil hole.

[0009] The support frame covers the oil baffle support plate and rotates together with the eccentric part. The support frame is provided with a guide groove and an elastic element arranged radially along the crankshaft. The guide groove is slidably fitted with a support column that is eccentric to the crankshaft. The elastic element connects the support column and the support frame. When the support column slides along the guide groove, it changes the position of the center of gravity of the support frame.

[0010] Furthermore, the oil baffle support plate is provided with an oil baffle plate, which covers the top of the crankshaft and connecting rod mating area to block the top and circumferential parts of the crankshaft and connecting rod mating part.

[0011] Furthermore, the oil storage tank is a U-shaped trough with an open top. The open part of the top of the oil storage tank is sealed by a support frame to form a U-shaped channel. The auxiliary oil hole and the spiral oil trough are connected through the U-shaped channel.

[0012] Furthermore, the oil baffle support plate is provided with a support plate located on the side of the oil baffle plate close to the crankshaft axis, and the support plate is provided with a limiting groove radially distributed along the eccentric part of the crankshaft, and the support frame is provided with a limiting protrusion that matches the limiting groove.

[0013] Furthermore, the support frame is provided with a support arm, and a counterweight bar is rotatably connected to the end of the support arm via a pin. The end of the counterweight bar away from the pin passes through a preset sliding hole on the support column. When the support column slides along the guide groove, it drives the counterweight bar to rotate around the pin via the sliding hole, thereby changing the position of the center of gravity of the support frame.

[0014] Furthermore, support arms are provided on both sides of the guide groove, and a first pin and a second pin are provided respectively. The first pin rotates and engages with a first counterweight bar, and the second pin rotates and engages with a second counterweight bar. The first counterweight bar engages with a first sliding hole on the support column, and the second counterweight bar engages with a second sliding hole that is offset from the first sliding hole.

[0015] Furthermore, the support column has a slider with a guide groove at one end and a counterweight at the other end, with a first sliding hole and a second sliding hole arranged at intervals between the slider and the counterweight.

[0016] Furthermore, the direction of rotation of the auxiliary oil hole is opposite to that of the spiral oil groove.

[0017] Furthermore, a protrusion is provided on the end face of the crankshaft eccentric part, and the oil baffle support plate is provided with a mounting hole that matches the protrusion. The fastener passes through the support frame and the oil baffle support plate in sequence and then fits into the crankshaft eccentric part.

[0018] A second object of the present invention is to provide a compressor that utilizes an adaptive dynamic balance lubrication crankshaft assembly as described in the first object.

[0019] Compared with the prior art, the advantages and positive effects of this invention are:

[0020] (1) To address the problem of poor compressor operation stability caused by poor lubrication performance at the top of the crankshaft and unsuitable counterweight torque, the following measures are taken: reducing the amount of refrigerant oil thrown into the cylinder, temporarily storing and returning the refrigerant oil, and adaptively adjusting the center of gravity of the crankshaft assembly. The oil baffle support plate constrains the outward throwing of refrigerant oil at the crankshaft and connecting rod mating position and returns it to improve the lubrication effect and reduce the problem of poor operation stability. The support frame of the oil baffle support plate can adjust the center of gravity to balance the torque of the eccentric part of the crankshaft, thereby improving the operation stability of the compressor.

[0021] (2) The oil baffle support plate is placed above the crankshaft and connecting rod mating position to block the flow path of the refrigeration oil surging up at the crankshaft and connecting rod mating position, and uses the circumferential block to prevent it from being thrown out into the cylinder. Part of the refrigeration oil transported in the spiral oil groove is supplied to the rotating position for lubrication, and the other oil can flow up to the oil reservoir, and return to the crankshaft and connecting rod rotating mating position for secondary lubrication through the oil reservoir and auxiliary oil hole. In addition, when the machine is stopped, the oil reservoir can retain some refrigeration oil to quickly replenish the lubrication position when it is started again.

[0022] (3) The U-shaped oil reservoir can gradually accumulate after the refrigeration oil enters. After accumulating to the position of the oil outlet, it is discharged through the auxiliary oil hole, thus ensuring that the oil reservoir can retain oil when the machine is stopped, so that it can be quickly input into the auxiliary oil hole for lubrication when the machine is started again.

[0023] (4) The support column is connected by an elastic element to adjust the center of gravity of the support frame and adapt to the rotation speed of the crankshaft to achieve adaptive counterweight. For different compressor requirements, the adaptability can be optimized by adjusting the elastic coefficient of the elastic element, the mass of the counterweight block at the top of the support column, and the weight of the first and second counterweight bars. Attached Figure Description

[0024] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0025] Figure 1 This is a schematic diagram of the adaptive dynamic balance lubrication crankshaft assembly in Embodiments 1 and 2 of the present invention.

[0026] Figure 2 This is a cross-sectional schematic diagram of the adaptive dynamic balance lubrication crankshaft assembly in Embodiments 1 and 2 of the present invention.

[0027] Figure 3 This is a schematic diagram of the crankshaft in Embodiments 1 and 2 of the present invention.

[0028] Figure 4 This is a schematic diagram of the crankshaft and oil baffle support plate in Embodiments 1 and 2 of the present invention.

[0029] Figure 5 This is a schematic diagram of the crankshaft, oil baffle support plate, and support frame in Embodiments 1 and 2 of the present invention.

[0030] Figure 6 This is a schematic diagram of the support frame in Embodiments 1 and 2 of the present invention.

[0031] Figure 7 This is a schematic diagram of the support column in Embodiments 1 and 2 of the present invention.

[0032] Among them, 1. crankshaft, 2. oil baffle support plate, 3. support frame, 4. first counterweight bar, 5. support column, 6. elastic element, 7. second counterweight bar, 11. end hole, 12. spiral oil groove, 13. auxiliary oil hole, 14. protrusion, 15. eccentric part, 16. connecting rod, 21. oil inlet hole, 22. oil outlet hole, 23. oil reservoir, 24. limiting groove, 25. oil baffle plate, 26. mounting hole, 31. through hole, 32. first pin, 33. second pin, 34. guide groove, 35. limiting block, 36. cover plate, 41. first pin hole, 42. first mating end, 51. slider, 52. first sliding hole, 53. second sliding hole, 54. counterweight block, 61. first baffle plate, 62. second baffle plate, 71. second pin hole, 72. second mating end. Detailed Implementation

[0033] Example 1

[0034] In a typical embodiment of the present invention, such as Figures 1-7 As shown, an adaptive dynamic balance lubrication crankshaft assembly is presented.

[0035] Compressors, especially fully hermetic reciprocating compressors, require consideration of operational stability to ensure that operating noise and vibration meet standard requirements. The torque imbalance of the counterweight corresponding to the eccentric part 15 of crankshaft 1 causes vibration during operation. Since the required balancing torque differs between high and low speeds, it is difficult to solve the problem of torque balance at different speeds to reduce vibration and noise. Furthermore, the top-slinging lubrication method allows refrigeration oil to enter the cylinder, causing cylinder vibration. The mating position between the eccentric part 15 of crankshaft 1 and the connecting rod 16 experiences short-term oil-free wear during restart after shutdown, affecting the precision of the mating position and leading to cylinder vibration. Ultimately, this results in the compressor's operational stability failing to meet requirements.

[0036] Based on this, this embodiment provides an adaptive dynamic balance lubrication crankshaft assembly. An oil baffle support plate 2 blocks and guides the upward-splashed refrigeration oil, achieving secondary smoothing through oil return while preventing it from being thrown into the cylinder and affecting operational stability. An oil reservoir 23, set up during the guidance process, retains some refrigeration oil after shutdown, allowing it to quickly flow into the mating position of the crankshaft 1 eccentric part 15 and connecting rod 16 during the next startup, reducing oil-free wear. The support frame 3, which forms the guiding channel, has an adjustable center of mass structure, achieving torque balance of the crankshaft 1 eccentric part 15 at different operating speeds, improving the rotational stability of the crankshaft 1, and synergistically enhancing the compressor's operational smoothness.

[0037] The adaptive dynamic balance lubrication crankshaft assembly will now be described in detail with reference to the accompanying drawings.

[0038] See Figure 1 The adaptive dynamic balance lubrication crankshaft assembly mainly includes a crankshaft 1, an oil baffle support plate 2, and a support frame 3. One end of the crankshaft 1 is provided with an eccentric part 15 that cooperates with the cylinder connecting rod 16. The oil baffle support plate 2 is installed on the top surface of the eccentric part 15. The support frame 3 cooperates with the oil baffle support plate 2 and is fixed to the eccentric part 15 together by fasteners.

[0039] like Figure 2 and Figure 5 As shown, the eccentric portion 15 at the top of the crankshaft 1 is provided with a spiral oil groove 12 and an auxiliary oil hole 13. The spiral oil groove 12 is arranged on the outer circumferential surface of the eccentric portion 15, and one end extends through to the top end face of the eccentric portion 15. The spiral oil groove 12 is connected to the spiral oil passages distributed on the crankshaft 1, so that the refrigeration oil can be transported from the bottom through the spiral oil passages to the spiral oil groove 12, and can enter the rotational engagement position of the eccentric portion 15 and the connecting rod 16 at the lateral opening of the spiral oil groove 12 to achieve lubrication of the rotational engagement position. It can also continue to rise along the spiral oil groove 12 to the top end face of the eccentric portion 15 and be thrown out. The auxiliary oil hole 13 is a through hole, one end of which is connected to the top end face of the eccentric portion 15, and the other end is connected to the outer circumferential surface of the eccentric portion 15. Therefore, the refrigeration oil in the auxiliary oil hole 13 can be transported to the rotational engagement position of the eccentric portion 15 and the connecting rod 16 to achieve secondary lubrication of the rotational engagement position.

[0040] The refrigeration oil splashed out from the spiral oil groove 12 is blocked and guided by the oil baffle support plate 2. Figure 3 As shown, an oil reservoir 23 is provided on the oil baffle support plate 2. The oil reservoir 23 is provided with an oil inlet 21 and an oil outlet 22. The oil inlet 21 is connected to the spiral oil groove 12, so that the refrigeration oil thrown out by it enters the oil reservoir 23. The oil outlet 22 is connected to the auxiliary oil hole 13, so that the refrigeration oil stored in the oil reservoir 23 is input into the auxiliary oil hole 13 for output lubrication.

[0041] In this embodiment, as Figure 3 and Figure 4 As shown, the oil baffle support plate 2 is provided with an oil baffle plate 25. The bottom of the oil baffle plate 25 is provided with a groove, and the oil baffle plate 25 is fastened to the top of the mating area between the crankshaft 1 and the connecting rod 16 through the groove, so as to cover the top and circumferential parts of the mating part between the crankshaft 1 and the connecting rod 16.

[0042] The oil baffle 25 is placed above the mating position of the crankshaft 1 and the connecting rod 16. On the one hand, it blocks the flow path of the refrigerant oil that surges up at the mating position of the crankshaft 1 and the connecting rod 16, preventing the refrigerant oil in the non-spiral oil groove 12 area from continuing to flow up. On the other hand, it uses the circumferential inner wall of the groove to achieve circumferential blocking to prevent the refrigerant oil from being thrown out into the cylinder.

[0043] The refrigeration oil transported in the spiral oil groove 12 is partially supplied to lubricate the rotating positions. For the corresponding position of the spiral oil groove 12, the oil baffle 25 has an oil storage inlet 21. Other refrigeration oil that has not entered the rotating position can flow upward through the oil storage inlet 21 to the oil storage tank 23. It then flows back to the rotating engagement position of the crankshaft 1 and connecting rod 16 for secondary lubrication via the oil storage tank 23 and auxiliary oil hole 13. Furthermore, when the machine is stopped, the oil storage tank 23 can retain some refrigeration oil to quickly replenish the lubrication position when the machine is started again.

[0044] like Figure 5 , Figure 6 As shown, the support frame 3 covers the oil baffle support plate 2 and rotates together with the oil baffle support plate 2 following the rotation of the eccentric part 15. The support frame 3 is provided with a guide groove 34 and an elastic element 6 arranged radially along the crankshaft 1. The guide groove 34 is slidably fitted with a support column 5 that is eccentric to the crankshaft 1. The elastic element 6 connects the support column 5 and the support frame 3. When the support frame 3 rotates with the crankshaft 1, the centrifugal force of the support column 5 and the elastic force of the elastic element 6 work together to make the support column 5 slide along the guide groove 34, thereby changing the overall center of gravity position of the support frame 3. As the counterweight structure of the eccentric part 15, the counterweight torque realized by the support frame 3 changes accordingly after its center of gravity changes, thereby adapting to different crankshaft 1 speeds.

[0045] During the flow of refrigeration oil from the spiral oil groove 12 to the auxiliary oil hole 13, it needs to pass through the oil storage tank 23. The oil storage tank 23 is a U-shaped groove with an open top. The open part of the top of the oil storage tank 23 is blocked by the support frame 3 so that the oil storage tank 23 forms a U-shaped channel. The auxiliary oil hole 13 and the spiral oil groove 12 are connected through the U-shaped channel.

[0046] In this embodiment, the support frame 3 blocks the oil storage tank 23 at the position of the cover plate 36, forming a U-shaped channel for the refrigeration oil to flow smoothly from the oil storage inlet 21 to the oil storage outlet 22, thus achieving the effects of blocking upward splashing and assisting lubrication.

[0047] The U-shaped oil reservoir 23 allows refrigeration oil to gradually accumulate after entering, and then be discharged through the auxiliary oil hole 13 once it reaches the position of the oil outlet 22. Since the oil outlet 22 and the oil inlet 21 are closer to the axis of the eccentric part 15 relative to the blocked end of the U-shaped channel, the refrigeration oil in the spiral oil groove 12 will no longer be replenished to the oil reservoir 23 when the machine is stopped. The blocked end of the U-shaped channel, which is far away from the axis of the eccentric part 15, can retain refrigeration oil when the machine is stopped. Thus, when the machine is started again, the refrigeration oil can be quickly input into the auxiliary oil hole 13 under the action of inertia to achieve lubrication, reducing the loss caused by oilless wear.

[0048] When the compressor restarts after being stopped, the rotational inertia force allows the refrigeration oil stored in the oil reservoir 23 to directly and quickly enter the friction surface of the eccentric part 15 of the crankshaft 1, reducing the risk of oilless friction.

[0049] It should be noted that the rotation direction of the auxiliary oil hole 13 is opposite to that of the spiral oil groove 12. When the compressor starts, the refrigerant oil can lubricate the mating position between the eccentric part 15 and the connecting rod 16 from the top down. Using an auxiliary oil hole 13 with a rotation direction opposite to that of the spiral oil groove 12 helps the refrigerant oil in the temporary storage chamber to drain smoothly. Centrifugal force is used to throw the refrigerant oil into the auxiliary oil hole 13 from top to bottom, promoting a lubricating effect.

[0050] like Figure 2 , Figure 4 As shown, the oil baffle support plate 2 is provided with a support plate located on the side of the oil baffle plate 25 close to the crankshaft 1 axis. The support plate is provided with a limiting groove 24 radially distributed along the eccentric part 15 of the crankshaft 1. The support frame 3 is provided with a limiting protrusion that matches the limiting groove 24. The cooperation between the limiting protrusion and the limiting groove 24 provides auxiliary support for the cantilever part of the support frame 3 and improves the stability of the support frame 3.

[0051] like Figure 6 , Figure 7 As shown, the support frame 3 is provided with a support arm, and the end of the support arm is rotatably connected to a counterweight bar through a pin. The end of the counterweight bar away from the pin is inserted into a preset sliding hole on the support column 5. When the support column 5 slides along the guide groove 34, it drives the counterweight bar to rotate around the pin through the sliding hole, thereby changing the position of the center of gravity of the support frame 3.

[0052] In this embodiment, two support arms are provided, respectively located on opposite sides of the guide groove 34, and counterweights are connected to each support arm. The two support arms are respectively provided with a first pin 32 and a second pin 33. One end of the first counterweight 4 is a first pin hole 41, and the other end is a first mating end 42. The first pin 32 rotatably engages with the first pin hole 41 of the first counterweight 4. One end of the second counterweight 7 is a second pin hole 71, and the other end is a second mating end 72. The second pin 33 rotatably engages with the second pin hole 71 of the second counterweight 7. The first mating end 42 of the first counterweight 4 engages with the first sliding hole 52 on the support column 5, and the second mating end 72 of the second counterweight 7 engages with the second sliding hole 53, which is offset from the first sliding hole 52.

[0053] The first counterweight bar 4 and the second counterweight bar 7 are arc-shaped counterweight structures. When the support column 5 adjusts its position relative to the guide groove 34 as the rotation speed changes, the movement of the first sliding hole 52 will drive the first counterweight bar 4 to rotate, causing the length of the first counterweight bar 4 passing through the first sliding hole 52 to change. Similarly, the second sliding hole 53 will drive the second counterweight bar 7 to rotate, causing the length of the second counterweight bar 7 passing through the first sliding hole 52 to change.

[0054] Specifically, as the support column 5 gradually approaches the axis of the crankshaft 1, it causes the first mating end 42 of the first support bar to rotate towards the axis of the crankshaft 1, and causes the second mating end 72 of the second support bar to rotate towards the axis of the crankshaft 1, thereby bringing the center of mass of the entire support frame 3 closer to the crankshaft axis. Conversely, it causes the center of mass of the entire support frame 3 to move away from the crankshaft axis.

[0055] One end of the elastic element 6 is connected to one end of the guide groove 34 via a first baffle 61, and the other end is connected to the support column 5 via a second baffle 62. A limiting block 35 is provided in the guide groove 34 to constrain the movement range of the support column 5. In this embodiment, the elastic element 6 can be a tension spring, rubber strip, etc.

[0056] like Figure 7 As shown, the support column 5 has a slider 51 with a guide groove 34 at one end and a counterweight 54 at the other end. A first sliding hole 52 and a second sliding hole 53 are arranged at intervals between the slider 51 and the counterweight 54.

[0057] The center of gravity of the support frame 3 is adjusted by using the elastic element 6 to connect the support column 5, and the adaptive counterweight is achieved to match the rotation speed of the crankshaft 1. For different compressor requirements, the adaptability can be optimized by adjusting the elastic coefficient of the elastic element 6, the mass of the counterweight block 54 at the top of the support column 5, and the weight of the first counterweight bar 4 and the second counterweight bar 7.

[0058] The positions of the support column 5, the first counterweight 4, and the second counterweight 7 change with the compressor speed, so that the center of gravity of the entire support frame 3 adapts to the compressor speed. At the same time, it reduces the amount of refrigeration oil entering the cylinder and stores refrigeration oil to facilitate lubrication of the eccentric part 15 of the crankshaft 1 during startup.

[0059] like Figure 1 As shown, a protrusion 14 is provided on the end face of the eccentric part 15 of the crankshaft 1, and an oil baffle support plate 2 is provided with a mounting hole 26 that matches the protrusion 14. At the same time, the support frame 3 is also provided with a through hole for fasteners. The oil baffle support plate 2 is provided with a through hole 31 that is coaxially distributed with the through hole. An end hole 11 is provided on the end face of the eccentric part 15 of the crankshaft 1. The coaxially distributed fasteners pass through the through hole 31 of the support frame 3 and the through hole of the oil baffle support plate 2 in sequence and then fit into the end hole 11 of the eccentric part 15 of the crankshaft 1 to achieve fastening.

[0060] Example 2

[0061] In another typical embodiment of the present invention, such as Figures 1-7 As shown, a compressor is presented.

[0062] Using the adaptive dynamic balance lubrication crankshaft assembly as in Example 1, the eccentric part 15 of the crankshaft 1 rotates with the connecting rod 16, thereby achieving the connection between the crankshaft 1 and the cylinder.

[0063] When the compressor is stationary, the elastic element 6 pulls the support frame 3 to the limit position. At this time, the first counterweight 4, the second counterweight 7 and the support frame 3 are all close to the axis of the crankshaft 1, and the distance between the center of mass of the overall counterweight and the axis of the crankshaft 1 is small.

[0064] As the compressor speed increases, the centrifugal force overcomes the elastic force of the elastic element 6, causing the first counterweight 4, the second counterweight 7, and the support frame 3 to move away from the crankshaft 1 axis, increasing the overall center-of-mass distance of the counterweight. When the speed decreases, the elastic element 6 pulls back the support column 5. This method reduces the rotational torque of the counterweight at low compressor speeds, facilitating adaptation to low speeds, and increases the rotational torque of the counterweight at high speeds, facilitating adaptation to high speeds.

[0065] For different compressor requirements, the adaptability can be optimized by adjusting the elastic coefficient of the elastic element 6 and adjusting the mass of the top counterweight 54, the first counterweight 4 and the second counterweight 7 of the support frame 3.

[0066] The oil baffle support plate 2 is installed on the top of the eccentric part 15 of the crankshaft 1. Since the top protrusion 14 of the eccentric part 15 mates with the mounting hole 26 of the oil baffle support plate 2, after installation, the outlet of the spiral oil groove 12 of the eccentric part 15 faces the oil inlet hole 21, and the auxiliary oil hole 13 of the eccentric part 15 faces the oil outlet hole 22. The cover plate 36 of the support frame 3 is installed on top of the oil baffle support plate 2, thus the oil reservoir 23 forms an oil storage space of a certain volume. When the compressor rotates, the lubricating oil of the eccentric part 15 is thrown out through the spiral oil groove 12. Due to the obstruction of the oil baffle plate 25, the thrown-out refrigeration oil cannot enter the cylinder. At the same time, the refrigeration oil enters the oil reservoir 23 through the oil inlet hole 21. The oil reservoir 23 stores lubricating oil and circulates back to the eccentric part 15 through the auxiliary oil hole 13 for further lubrication. When the compressor stops, the refrigeration oil is stored in the oil reservoir 23. When it is restarted, the lubricating oil in the oil reservoir 23 enters the eccentric part 15 through the auxiliary oil hole 13, which accelerates the lubrication of the eccentric part 15.

[0067] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. An adaptive dynamic balance lubrication crankshaft assembly, characterized in that, include: The crankshaft has a eccentric part at the top with separate spiral oil grooves and auxiliary oil holes. The auxiliary oil holes connect the end face of the eccentric part and the outer circumferential surface. An oil baffle support plate is provided with an oil storage tank. The oil inlet of the oil storage tank is connected to a spiral oil groove, and the oil outlet is connected to an auxiliary oil hole. The support frame covers the oil baffle support plate and rotates together with the oil baffle support plate following the eccentric part. The support frame is provided with a guide groove and an elastic element arranged radially along the crankshaft. The guide groove is slidably fitted with a support column that is eccentric to the crankshaft. The elastic element connects the support column and the support frame. When the support column slides along the guide groove, it changes the position of the center of gravity of the support frame. The support frame is provided with a support arm, and the end of the support arm is rotatably connected to a counterweight bar via a pin. The end of the counterweight bar away from the pin passes through a pre-set sliding hole on the support column. When the support column slides along the guide groove, it drives the counterweight bar to rotate around the pin through the sliding hole, thereby changing the position of the center of gravity of the support frame. Support arms are provided on both sides of the guide groove, and a first pin and a second pin are respectively provided. The first pin rotates to engage with the first counterweight bar, and the second pin rotates to engage with the second counterweight bar. The first counterweight bar engages with the first sliding hole on the support column, and the second counterweight bar engages with the second sliding hole that is offset from the first sliding hole.

2. The adaptive dynamic balance lubrication crankshaft assembly as described in claim 1, characterized in that, The oil baffle support plate is equipped with an oil baffle plate, which covers the top of the crankshaft and connecting rod mating area to shield the top and circumferential parts of the crankshaft and connecting rod mating part.

3. The adaptive dynamic balance lubrication crankshaft assembly as described in claim 2, characterized in that, The oil storage tank is a U-shaped trough with an open top. The open part of the top of the oil storage tank is sealed by a support frame to form a U-shaped channel. The auxiliary oil hole and the spiral oil trough are connected through the U-shaped channel.

4. The adaptive dynamic balance lubrication crankshaft assembly as described in claim 2, characterized in that, The oil baffle support plate is provided with a support plate located on the side of the oil baffle plate close to the crankshaft axis. The support plate is provided with a limiting groove radially distributed along the eccentric part of the crankshaft, and the support frame is provided with a limiting protrusion that matches the limiting groove.

5. The adaptive dynamic balance lubrication crankshaft assembly as described in claim 4, characterized in that, The support column has a slider with a guide groove at one end and a counterweight at the other end. A first sliding hole and a second sliding hole are arranged at intervals between the slider and the counterweight.

6. The adaptive dynamic balance lubrication crankshaft assembly as described in claim 1, characterized in that, The direction of rotation of the auxiliary oil hole is opposite to that of the spiral oil groove.

7. The adaptive dynamic balance lubrication crankshaft assembly as described in claim 1, characterized in that, The crankshaft eccentric part has a protrusion on its end face, and the oil baffle support plate has a mounting hole that matches the protrusion. The fastener passes through the support frame and the oil baffle support plate in sequence and then fits into the crankshaft eccentric part.

8. A compressor utilizing an adaptive dynamic balance lubrication crankshaft assembly as claimed in any one of claims 1-7.

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