Crankshaft assembly, variable-frequency compressor and refrigeration equipment

Abstract

The present invention belongs to the technical field of compressors, and more specifically, it relates to a crankshaft assembly, a variable frequency compressor and a refrigeration device. The crankshaft assembly includes a crankshaft and a connecting rod. The crankshaft includes a main shaft, a balancing block and an eccentric shaft. The eccentric shaft is installed at one end of the main shaft. The main shaft is provided with a main shaft oil groove. The eccentric shaft is provided with an oil pumping channel connected to the main shaft oil groove. The outlet of the oil pumping channel passes through the end of the eccentric shaft. The connecting rod includes a connecting rod connecting end sleeved on the eccentric shaft. The outer side wall of the eccentric shaft is provided with an oil drain hole connected to the oil pumping channel. The connecting rod connecting end is provided with a connecting rod oil groove connected to the gap between the eccentric shaft and the balancing block. When the eccentric shaft rotates, the oil drain hole can be connected to or staggered with the connecting rod oil groove. When the two are connected, the lubricating oil can flow out through the oil drain hole, the connecting rod oil groove, and the gap between the connecting rod connecting end and the balancing block, and cannot enter the cylinder hole, thereby reducing the lubricating oil pumped to the cylinder hole during the entire operation cycle and avoiding excessive oil pumping under high-speed operation conditions.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and more specifically, relates to a crankshaft assembly, a variable-frequency compressor, and a refrigeration device. Background Art

[0002] A variable-frequency compressor is a compressor whose rotational speed can be continuously adjusted within a certain range by a certain control method or means, so that the output energy can be continuously changed. Compared with a fixed-speed compressor, a variable-frequency compressor can operate smoothly under low-speed and low-energy-consumption conditions, and has the advantages of high working efficiency, smooth operation, and low energy consumption. It is widely used in electrical appliances such as refrigerators and air conditioners.

[0003] Generally, a compressor needs to be provided with a lubricating oil supply system. The lubricating oil supply system is used to guide the lubricating oil to flow into or out of the crankshaft, so as to lubricate each friction pair of the compressor and ensure the flexible operation of moving parts such as the crankshaft. For a variable-frequency compressor, its lubricating oil supply system needs to meet the lubricating oil supply under both low-frequency and high-frequency operating states. In recent years, the development of compressors has tended to be low-frequency. In order to ensure that the compressor can supply a sufficient amount of lubricating oil at low speeds, the lubricating oil supply system often needs to have a strong oil pumping capacity, such as using an oil pump with a larger oil pumping lift. However, for such variable-frequency compressors, due to the strong oil supply capacity of their lubricating oil supply systems, when the compressor operates at high frequency and high speed, the lubricating oil supply system will pump too much oil. In this way, the lubricating oil of the compressor is over-supplied in the high-frequency state, and the oil discharge volume of the compressor increases, which will cause the input efficiency of the compressor (the ratio of the theoretical input power required by the compressor to the actual input power is called the input efficiency) to increase, so that the lubricating oil supply system has a discontinuous oil pumping situation, affecting the lubrication effect. Summary of the Invention

[0004] The main purpose of the embodiments of the present invention is to provide a crankshaft assembly, a variable-frequency compressor, and a refrigeration device, so as to solve the technical problem that the lubricating oil supply system of the existing variable-frequency compressor is prone to over-pump oil under high-frequency working conditions, which increases the input efficiency of the compressor, resulting in discontinuous oil pumping of the lubricating oil supply system and affecting the lubrication effect.

[0005] In order to achieve the aforementioned purpose of the present invention, a lubricating oil supply system needs to be set up based on the compressor. At the same time, since the variable frequency compressor has two operating conditions, high frequency and low frequency, in order to meet the sufficient supply of lubricating oil under low frequency conditions, the pumping capacity of the lubricating oil supply system needs to be improved. Under high frequency conditions, in order to avoid excessive pumping of oil, the high frequency oil supply of the lubricating oil supply system must be reduced to ensure that the pumping amount of the compressor is always kept within a relatively moderate range when the compressor is running at high frequency. Based on this, the inventor studied the amount of lubricating oil under high frequency conditions, designed various lubricating oil supply systems that can stably supply oil under high frequency conditions, and tested each system separately, and provided the following technical solutions based on the test results.

[0006] The technical solution adopted by the present invention is: to provide a crankshaft assembly, including a crankshaft and a connecting rod, the crankshaft including a main shaft, a balancing block and an eccentric shaft, the eccentric shaft is eccentrically installed on one end of the main shaft through the balancing block, the main shaft is provided with a main shaft oil groove, the eccentric shaft is provided with an oil pumping channel extending to the main shaft and connected with the main shaft oil groove, the outlet of the oil pumping channel extends to the end of the eccentric shaft away from the main shaft, the connecting rod includes a connecting rod connecting end sleeved on the eccentric shaft, the outer side wall of the eccentric shaft is provided with an oil drain hole connected with the oil pumping channel, the inner side wall of the connecting rod connecting end is provided with a connecting rod oil groove, there is a gap between the connecting rod connecting end and the balancing block, the connecting rod oil groove is connected with the gap, when the eccentric shaft rotates relative to the connecting rod connecting end, the oil drain hole can be rotated to be connected with the connecting rod oil groove or staggered.

[0007] In some embodiments, the oil drain hole is arranged at the lower end of the eccentric shaft toward the balance block and is located on the side of the eccentric shaft away from the center line of the main shaft, and the connecting rod oil groove is arranged at the lower end of the connecting rod connecting end toward the balance block.

[0008] In some embodiments, the connecting rod also includes a connecting rod driving end arranged opposite to the connecting rod connecting end, and a rod body connected at both ends to the connecting rod connecting end and the connecting rod driving end respectively, and the connecting rod oil groove is arranged on the side of the connecting rod connecting end away from the connecting rod driving end.

[0009] In some embodiments, the connecting rod oil groove is a notch arranged on the inner wall of the connecting rod connecting end toward the bottom of the balancing block, and along the circumference of the inner wall of the connecting rod connecting end, the ratio of the length of the connecting rod oil groove to the circumference of the inner wall of the connecting rod connecting end is 1:2 to 4:5.

[0010] In some embodiments, along the circumference of the inner wall of the connecting rod connecting end, the ratio of the length of the connecting rod oil groove to the circumference of the inner wall of the connecting rod connecting end is 3:4, and the angle between the line connecting one end point of the connecting rod oil groove along the length direction and the center of the bottom of the connecting rod connecting end and the rod body is 0°~90°, and the angle between the line connecting the other end point of the connecting rod oil groove along the length direction and the center of the bottom of the connecting rod connecting end and the rod body is 0°~90°.

[0011] In some embodiments, the oil drain hole is a strip hole arranged along the circumference of the outer side wall of the eccentric shaft, and the ratio of the length of the oil drain hole to the circumference of the outer side wall of the eccentric shaft is 1:10 to 1:8.

[0012] In some embodiments, the width of the oil leakage hole is 0.5 mm to 1.5 mm.

[0013] In some embodiments, a receiving groove is provided on the top of the balancing block toward the eccentric shaft, the receiving groove is connected to the connecting rod oil groove, and at least one oil leakage hole is opened on the balancing block, which passes through the top and bottom of the balancing block, and the oil leakage hole is connected to the receiving groove.

[0014] In some embodiments, the accommodating groove is an arc groove or an annular groove arranged around the eccentric shaft, and two oil leakage holes are arranged on the balancing block, and the two oil leakage holes are respectively located on both sides of the eccentric shaft.

[0015] In some embodiments, an eccentric oil groove is also provided on the outer wall of the eccentric shaft, one end of the eccentric oil groove is connected to the oil drain hole, and the other end of the eccentric oil groove spirally extends to the upper end of the eccentric shaft away from the balance block and does not exceed the connecting end of the connecting rod; the spiral direction of the eccentric oil groove is opposite to the rotation direction of the eccentric shaft.

[0016] The above one or more technical solutions in the crankshaft assembly provided by the embodiment of the present invention have at least one of the following technical effects: Compared with the prior art, the crankshaft assembly of the present invention is provided with an oil drain hole on the eccentric shaft and a connecting rod oil groove at the connecting rod connecting end of the connecting rod, wherein the oil drain hole is connected to the pump oil channel of the eccentric shaft, and the connecting rod oil groove is connected to the gap between the eccentric shaft and the balance block, and when the eccentric shaft rotates, the oil drain hole can be rotated to be connected to or staggered with the connecting rod oil groove. During the rotation of the eccentric shaft, the lubricating oil entering the pump oil channel can flow out through the oil drain hole, wherein, when the eccentric shaft rotates to the point where the oil drain hole is staggered with the connecting rod oil groove, the lubricating oil flowing out of the oil drain hole is blocked by the inner side wall of the connecting rod connecting end and cannot be thrown out in large quantities, and at this time only a very small part of the lubricating oil enters the gap between the inner side wall of the connecting rod connecting end and the outer side wall of the eccentric shaft to lubricate the connecting rod connecting end and the eccentric shaft. When the eccentric shaft rotates until the oil drain hole is connected to the connecting rod oil groove, the lubricating oil flowing out of the oil drain hole further flows into the connecting rod oil groove and flows out from the gap between the connecting rod connection end and the balance block. At this time, the lubricating oil flowing out of the oil drain hole cannot flow to the cylinder hole of the cylinder. In this way, the lubricating oil pumped to the cylinder hole during the entire operation cycle of the crankshaft can be reduced, thereby avoiding excessive oil pumping under high-speed operation conditions of the crankshaft, thereby ensuring that the variable frequency compressor using the crankshaft assembly of the present invention reduces the oil discharge amount on the basis of ensuring the lubrication of the cylinder hole, and realizes continuous and stable oil supply under high-frequency conditions.

[0017] Another technical solution of the present invention is to provide a variable frequency compressor, comprising the above-mentioned crankshaft.

[0018] The beneficial effect of the variable frequency compressor provided by the embodiment of the present invention is that compared with the prior art, the variable frequency compressor of the present invention, by using the above-mentioned crankshaft assembly, enables the compressor to achieve continuous and stable oil supply under high-frequency and low-frequency conditions, the cylinder hole can be effectively lubricated, and under high-frequency conditions, there will be no excessive pumping of oil, thereby making the operation of the compressor more stable and efficient.

[0019] Another technical solution of the present invention is to provide a refrigeration device, comprising the above-mentioned variable frequency compressor.

[0020] The beneficial effect of the refrigeration equipment provided by the embodiment of the present invention is that compared with the prior art, the refrigeration equipment of the present invention, due to the use of the above-mentioned variable frequency compressor, can operate smoothly under low-frequency and high-frequency conditions, the operating stability of the refrigeration equipment is improved, the refrigeration effect is improved, the operating energy consumption is lower, and the service life is extended. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0022] Figure 1 A schematic diagram of the structure when the oil drain hole of the crankshaft assembly provided by one embodiment of the present invention is connected to the connecting rod oil groove;

[0023] Figure 2 for Figure 1 The enlarged schematic diagram of point A in the middle;

[0024] Figure 3 for Figure 1 The structural schematic diagram of the crankshaft assembly when the oil drain hole and the connecting rod oil groove are staggered;

[0025] Figure 4 for Figure 3 The enlarged schematic diagram of point B in the middle;

[0026] Figure 5 for Figure 1 A schematic structural diagram of a crankshaft of a crankshaft assembly shown;

[0027] Figure 6 for Figure 1 A schematic structural diagram of a connecting rod of a crankshaft assembly shown;

[0028] Figure 7 for Figure 6 A top view of a partial structure of the connecting rod shown;

[0029] Figure 8 is Figure 1 a top view of the crankshaft assembly shown;

[0030] Figure 9 is Figure 1 a schematic structural view of the balance weight of the crankshaft of the crankshaft assembly shown.

[0031] In the figure, the main reference signs of each drawing are as follows:

[0032] 10. Crankshaft; 11. Main shaft; 111. Main shaft oil groove; 112. First oil hole; 113. Second oil hole; 12. Eccentric shaft; 121. Oil pumping channel; 122. Oil drain hole; 123. Eccentric oil groove; 13. Balance weight; 131. Accommodating groove; 132. Oil leakage hole; 20. Connecting rod; 21. Connecting rod connection end; 211. Connecting rod oil groove; 22. Connecting rod driving end; 23. Rod body; 231. Connecting rod oil passage; 30. Piston; 40. Cylinder hole; 50. Crankcase; 60. Bearing. Detailed implementation manners

[0033] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention clearer and more understandable, the following further describes the present invention in detail with reference to the accompanying Figures 1 to 9 drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0034] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.

[0035] The orientation or positional relationship indicated by the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the purpose of simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0036] The terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features. The features defined with "first" and "second" may explicitly or implicitly include one or more of such features, and the meaning of "a plurality" is two or more.

[0037] References to "an embodiment", "some embodiments" or "embodiments" described in the specification of the present invention mean that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the present invention. Statements such as "in one embodiment", "in some embodiments", "in other some embodiments", "in still other embodiments", etc., which appear in different places in this specification, do not necessarily refer to the same embodiment, but mean "one or more but not all embodiments", unless otherwise specifically emphasized. In one or more embodiments, specific features, structures, or characteristics may be combined in any suitable manner.

[0038] Generally, a commonly used compressor usually includes a housing, a crankcase, a crankshaft, an oil pump, a connecting rod, a cylinder, a piston, a driving motor, etc. An oil sump storing lubricating oil is provided at the bottom of the housing. The crankshaft includes a main shaft drivingly connected to the driving motor, a balance weight (also called a crank) connected to one end of the main shaft, and an eccentric shaft eccentrically connected to one end of the main shaft through the balance weight. Generally, a lubricating oil supply system (abbreviated as an oil supply system) is provided inside the crankshaft. The oil pump is installed at the bottom of the other end of the main shaft away from the eccentric shaft, and the oil pumping outlet of the oil pump is communicated with the oil supply system inside the crankshaft. The cylinder is arranged in the crankcase, the piston is arranged at the cylinder bore of the cylinder, the crankshaft is installed in the crankcase, and the connecting rod connects the eccentric shaft of the crankshaft and the piston. When the compressor operates, the driving motor rotates the crankshaft, and the crankshaft drives the piston to perform a reciprocating linear motion in the cylinder bore through the connecting rod, thereby compressing the refrigerant in the cylinder. At the same time, the lubricating oil at the bottom of the housing can be transported through the lubricating oil supply system and led to each friction pair of the compressor for lubrication, thereby reducing the frictional loss during the operation between the components inside the compressor. At the same time, the lubricating oil also has a certain cooling effect. Therefore, the oil supply amount of the crankshaft has an important influence on the normal operation of the compressor.

[0039] For a variable-frequency compressor, it can continuously adjust the output driving energy by changing the operating speed according to the working needs. The lower the speed, the smaller the power consumption. Therefore, the variable-frequency compressor has the advantages of high efficiency and energy saving. In the related art, based on the development of the low-frequency of the compressor, the existing lubricating oil supply system of the variable-frequency compressor generally has a strong oil pumping ability, such as using an oil pump with a larger oil pumping lift, etc., to ensure that a sufficient amount of lubricating oil can be supplied under low-frequency working conditions; and when the compressor operates at high frequency and high speed, due to the strong oil supply ability of the lubricating oil supply system, the lubricating oil supply system pumps too much oil under the high-speed operating conditions, resulting in an increase in the oil discharge amount of the compressor in the high-frequency state and an increase in the input efficiency of the compressor, thus causing the lubricating oil supply system to have a situation of discontinuous oil pumping, affecting the lubrication effect, and the operating conditions of the variable-frequency compressor at high speed are poor.

[0040] Based on the requirements of the compressor, a lubricating oil supply system needs to be set up. At the same time, since the variable-frequency compressor has two operating conditions: high frequency and low frequency, in order to meet the sufficient supply of lubricating oil under low-frequency conditions, it is necessary to improve the oil pumping capacity of the lubricating oil supply system. And under high-frequency conditions, in order to avoid excessive oil pumping, it is necessary to reduce the high-frequency oil supply volume of the lubricating oil supply system to ensure that the oil pumping volume of the compressor always remains within a relatively moderate range during high-speed operation. Based on this, the embodiments of the present invention optimize the crankshaft assembly of the variable-frequency compressor, improve the oil supply volume of the lubricating oil supply system at high rotational speeds, and provide a lubricating oil supply system that can stably and continuously supply oil under low-frequency and high-frequency conditions. The following will specifically describe the crankshaft assembly of the present invention with reference to specific embodiments.

[0041] Please refer to Figures 1 to 6 as shown below. Among them, Figure 1 and Figure 3 are respectively the structural schematic diagrams of the crankshaft assembly provided by an embodiment of the present invention in two rotational states. Some structures in the figure are perspective structures to show the flow path of the lubricating oil. Figure 1 The middle oil drain hole 122 is communicated with the connecting rod oil groove 211. Figure 3 The middle oil drain hole 122 is offset from the connecting rod oil groove 211. Figure 2 is Figure 1 the enlarged schematic diagram at position A in Figure 4 is Figure 3 the enlarged schematic diagram at position B in Figure 5 is the structural schematic diagram of the crankshaft 10 of the crankshaft assembly provided by this embodiment. Figure 6 is the structural schematic diagram of the connecting rod 20 of the crankshaft assembly provided by this embodiment. The dotted arrow in the figure indicates the rotation direction of the eccentric shaft 12.

[0042] Specifically, as shown in Figure 1 , Figure 3 and Figure 5 , this embodiment provides a crankshaft assembly. The crankshaft assembly includes a crankshaft 10. The crankshaft 10 includes a main shaft 11, an eccentric shaft 12, and a balance weight 13. The main shaft 11 is drivingly connected to an external driving component. The eccentric shaft 12 is installed at one end of the main shaft 11 through the balance weight 13 and is eccentrically arranged relative to the center line of the main shaft 11 (such as Figure 3 the center line R shown). The main shaft 11 is provided with an oil suction inner cavity (not shown) communicated with the outlet of an oil pump (not shown). The outer side wall of the main shaft 11 is provided with a main shaft oil groove 111. The eccentric shaft 12 is internally provided with an oil pumping channel 121. The oil pumping channel 121 extends into the main shaft 11 and is communicated with the main shaft oil groove 111.

[0043] Specifically, as shown in Figure 5As shown, a first oil hole 112 and a second oil hole 113 are provided on the main shaft 11. The main shaft oil groove 111 is connected with the oil suction cavity through the first oil hole 112, and is connected with the oil pump channel 121 through the second oil hole 113. The oil pump channel 121 extends from one end of the main shaft 11 to the end of the eccentric shaft 12 away from the balance block 13, and forms an outlet of the oil pump channel 121.

[0044] In this way, when the crankshaft 10 rotates, the oil pump pumps lubricating oil into the oil suction chamber. The lubricating oil entering the oil suction chamber enters the main shaft oil groove 111 through the first oil hole 112, moves along the main shaft oil groove 111 and flows into the oil pumping channel 121 through the second oil hole 113. The lubricating oil entering the oil pumping channel 121 then moves upward along the channel wall of the oil pumping channel 121 under the action of centrifugal force until it is thrown out from the outlet of the oil pumping channel 121, so that the lubricating oil reaches the various moving parts inside the compressor for lubrication, ensuring that the various moving parts of the compressor using the crankshaft assembly of this embodiment can operate normally and cooling down the various components.

[0045] like Figures 1 to 4 as well as Figure 6 As shown, the crankshaft assembly of this embodiment also includes a connecting rod 20, which includes a connecting rod connecting end 21 sleeved on the eccentric shaft 12, and the outer wall of the eccentric shaft 12 is provided with an oil drain hole 122 connected to the pump oil channel 121, and the inner wall of the connecting rod connecting end 21 is provided with a connecting rod oil groove 211, and there is a gap between the connecting rod connecting end 21 and the balance block 13, and the connecting rod oil groove 211 is connected to the gap, and when the eccentric shaft 12 rotates relative to the connecting rod connecting end 21, the oil drain hole 122 can rotate to be connected with or offset from the connecting rod oil groove 211.

[0046] Specifically, in this embodiment, the size of the connecting rod oil groove 211 is larger than the size of the oil drain hole 122. Along the radial direction of the eccentric shaft 12, the height of the upper edge of the orifice of the oil drain hole 122 is lower than or equal to the height of the upper edge of the notch of the connecting rod oil groove 211, so as to ensure that when the eccentric shaft 12 rotates, the oil drain hole 122 can rotate to be completely located in the connecting rod oil groove 211, thereby communicating with the connecting rod oil groove 211. Figure 1 and Figure 2 The oil drain hole 122 can also be rotated to be completely located outside the connecting rod oil groove 211, thereby staggering the connecting rod oil groove 211, such as Figure 3 and Figure 4 shown.

[0047] Based on this, during the rotation of the eccentric shaft 12, the lubricating oil entering the oil pump channel 121 can flow out through the oil drain hole 122. When the eccentric shaft 12 rotates until the oil drain hole 122 is connected to the connecting rod oil groove 211, the lubricating oil flowing out from the oil drain hole 122 further flows into the connecting rod oil groove 211, and flows out from the gap between the connecting rod connecting end 21 and the balance block 13. At this time, the lubricating oil flowing out from the oil drain hole 122 cannot flow to the cylinder hole 40 of the cylinder, thereby reducing the lubricating oil pumped to the cylinder hole 40 during the entire operating cycle of the crankshaft 10, thereby avoiding excessive oil pumping of the crankshaft 10 under high-speed operating conditions, thereby ensuring that the variable frequency compressor using the crankshaft assembly of the present invention reduces the oil discharge amount on the basis of ensuring the lubrication of the cylinder hole 40, thereby achieving continuous and stable oil supply under high-frequency conditions. When the eccentric shaft 12 rotates until the oil drain hole 122 is misaligned with the connecting rod oil groove 211, the lubricating oil flowing out of the oil drain hole 122 is blocked by the inner wall of the connecting rod connecting end 21 and cannot be thrown out in large quantities. At this time, only a very small portion of the lubricating oil enters the gap between the connecting rod connecting end 21 and the eccentric shaft 12 to lubricate the connecting rod connecting end 21 and the eccentric shaft 12. In this way, by providing the oil drain hole 122 and the connecting rod oil groove 211, the lubrication between the connecting rod connecting end 21 and the eccentric shaft 12 can be increased.

[0048] In addition, when the eccentric shaft 12 rotates until the oil drain hole 122 is connected to the connecting rod oil groove 211, the lubricating oil flowing out from the gap between the connecting rod connecting end 21 and the balance block 13 cannot be thrown toward the housing and other components, thereby reducing the amount of oil mist formed by the impact of lubricating oil droplets on the housing and other components, thereby reducing the amount of lubricating oil carried in the refrigerant and reducing the oil discharge amount of the compressor using the crankshaft assembly of this embodiment. In another embodiment of the present invention, please refer to Figure 2 , Figure 5 and Figure 6, the oil drain hole 122 is provided at the lower end of the eccentric shaft 12 facing the balance weight 13 and is located on the side of the eccentric shaft 12 away from the center line of the main shaft 11 (specifically, since the eccentric shaft 12 is eccentrically arranged relative to the main shaft 11, among the two opposite side parts of the eccentric shaft 12, one side part is close to the center line of the main shaft 11, and the other side part is far from the center line of the main shaft). The connecting rod oil groove 211 is provided at the lower end of the connecting rod connection end 21 facing the balance weight 13. During the rotation of the eccentric shaft 12, the position on the eccentric shaft 12 farther from the center line of the main shaft 11 is subjected to greater centrifugal force. Thus, by setting the oil drain hole 122 at the position of the eccentric shaft 12 away from the center line of the main shaft 11, the amount of lubricating oil flowing out from the oil drain hole 122 can be increased. By setting the oil drain hole 122 at the lower part of the eccentric shaft 12 and the connecting rod oil groove 211 at the lower part of the connecting rod connection end 21, the lubricating oil can flow to the gap between the connecting rod connection end 21 and the balance weight 13 at a shorter distance, avoiding congestion of the lubricating oil in the oil drain hole 122 and the connecting rod oil groove 211, which may cause the lubricating oil to still not flow out continuously when the oil drain hole 122 is communicated with the connecting rod oil groove 211.

[0049] In another embodiment of the present invention, as Figure 1 , Figure 2 and Figure 5 shown, an eccentric oil groove 123 is further provided on the outer side wall of the eccentric shaft 12. One end of the eccentric oil groove 123 is communicated with the oil drain hole 122, and the other end of the eccentric oil groove 123 spirally extends to the upper end of the eccentric shaft 12 away from the balance weight 13. The lubricating oil flowing out from the oil drain hole 122 can flow into the eccentric oil groove 123, thereby increasing the amount of lubricating oil entering the gap between the eccentric shaft 12 and the connecting rod connection end 21 and better lubricating the eccentric shaft 12 and the connecting rod connection end 21 as the eccentric shaft 12 rotates. In addition, the spiral extension of the eccentric oil groove 123 to the upper end of the eccentric shaft 12 does not exceed the connecting rod connection end 21, that is, the lubricating oil is restricted by the connecting rod connection end 21 within the gap between the eccentric shaft 12 and the connecting rod connection end 21 and cannot flow out through the eccentric oil groove 123.

[0050] In this embodiment, as Figure 1 , Figure 2 and Figure 5 shown, the spiral direction of the eccentric oil groove 123 is opposite to the rotation direction of the eccentric shaft 12. For example, as Figure 5 shown, when the eccentric shaft 12 rotates clockwise, the eccentric oil groove 123 is spirally arranged counterclockwise. In this way, when the lubricating oil enters the eccentric oil groove 123, it is ensured that the lubricating oil can spiral upward along the eccentric oil groove 123 under the action of the viscous force of the inner side wall of the connecting rod connection end 21 and the frictional force between the inner side wall of the connecting rod connection end 21 and the outer side wall of the eccentric shaft 12, so as to fully lubricate the eccentric shaft 12 and the connecting rod connection end 21.

[0051] In another embodiment of the present invention, as Figure 6 shown, the connecting rod 20 further includes a connecting rod driving end 22 disposed opposite to the connecting rod connecting end 21 and connected to the piston 30, and a rod body 23 with two ends respectively connected to the connecting rod connecting end 21 and the connecting rod driving end 22. A connecting rod oil passage 231 is provided in the rod body 23. The two ends of the connecting rod oil passage 231 respectively penetrate the inner side walls of the connecting rod connecting end 21 and the connecting rod driving end 22. During the rotation of the eccentric shaft 12, the eccentric oil groove 123 can rotate to communicate with the first end of the connecting rod oil passage 231. Thus, the lubricating oil flowing out from the oil drain hole 122 can enter the connecting rod oil passage 231 through the eccentric oil groove 123 and flow to the inner side wall of the connecting rod driving end 22, thereby lubricating the connecting rod driving end 22 and the piston pin 30 sleeved therein.

[0052] In another embodiment of the present invention, as Figure 5 shown, the oil drain hole 122 is a strip-shaped hole circumferentially provided along the outer side wall of the eccentric shaft 12. Since the lubricating oil is affected by the centrifugal force of the eccentric shaft 12 and its own gravity when flowing out from the oil drain hole 122, the outflow of the lubricating oil is concentrated at the bottom of the oil drain hole 122 facing the balance weight 13. Thus, setting the oil drain hole 122 as a long strip-shaped hole helps to increase the amount of lubricating oil flowing out through the oil drain hole 122, so that the entire orifice of the oil drain hole 122 can be used for oil outflow.

[0053] In addition, the ratio of the length of the oil drain hole 122 to the circumference of the outer side wall of the eccentric shaft 12 is set to be 1:10 to 1:8, that is, the length dimension of the oil drain hole 122 is reasonably set to ensure the amount of lubricating oil discharged. In a specific embodiment, the length of the oil drain hole 122 can be 0.1, 0.11, 0.115, 0.118, 0.12, 0.122, or 0.125 times the circumference of the outer side wall of the eccentric shaft 12, etc. In specific design, it can be set according to the size of the eccentric shaft 12 and the amount of lubricating oil that needs to be discharged through the oil drain hole 122, and no unique limitation is made here.

[0054] In this embodiment, as Figure 5 shown, along the axial direction of the eccentric shaft 12, the width of the oil drain hole 122 is 0.5 mm to 1.5 mm, that is, the width of the oil drain hole 122 is reasonably set to ensure the smooth outflow of the lubricating oil. In a specific embodiment, the width of the oil drain hole 122 can be 0.5 mm, 0.6 mm, 0.8 mm, 1.0 mm, 1.2 mm, or 1.5 mm, etc. In specific design, it can be set according to the size of the eccentric shaft 12, the length of the oil drain hole 122, and the amount of lubricating oil that needs to be discharged through the oil drain hole 122, and no unique limitation is made here.

[0055] In another embodiment of the present invention, as Figure 6As shown, the connecting rod oil groove 211 is provided on the side of the connecting rod connecting end 21 away from the connecting rod driving end 22, that is, the oil drain hole 122 communicates with the connecting rod oil groove 211 on the side away from the connecting rod driving end 22, and is offset from the connecting rod oil groove 211 on the side facing the connecting rod driving end 22, as Figure 1 and Figure 3 shown. Thus, since the oil drain hole 122 is provided on the side of the eccentric shaft 12 away from the center line of the main shaft 11, when the oil drain hole 122 communicates with the connecting rod oil groove 211, the side of the eccentric shaft 12 away from the center line of the main shaft 11 faces away from the connecting rod driving end 22, that is, away from the cylinder bore 40 of the cylinder, as Figure 1 and Figure 2 shown. At this time, most or even all of the lubricating oil is discharged through the oil drain hole 122 and the connecting rod oil groove 211, and only a small amount or even almost no lubricating oil can be thrown from the outlet of the oil pumping channel 121 towards the cylinder bore 40. On the contrary, when the oil drain hole 122 is offset from the connecting rod oil groove 211, the side of the eccentric shaft 12 away from the center line of the main shaft 11 moves towards the connecting rod driving end 22, that is, towards the cylinder bore 40 of the cylinder, as Figure 3 and Figure 4 shown. At this time, most or even all of the lubricating oil is thrown out through the outlet of the oil pumping channel 121 and is thrown towards the cylinder bore 40 under the action of centrifugal force, so as to ensure that when the oil drain hole 122 is offset from the connecting rod oil groove 211, a sufficient amount of lubricating oil can be thrown out from the outlet of the oil pumping channel 121 and enter the cylinder bore 40 to lubricate the cylinder bore 40.

[0056] In this embodiment, as Figure 1 and Figure 6As shown, the connecting rod oil groove 211 is a notch arranged at the bottom of the connecting rod connecting end 21 toward the balancing block 13, that is, the connecting rod oil groove 211 is actually a notch recessed at the bottom of the inner wall of the connecting rod connecting end 21, and along the circumference of the inner wall of the connecting rod connecting end 21, the ratio of the length of the connecting rod oil groove 211 to the circumference of the inner wall of the connecting rod connecting end 21 is 1:2 to 4:5, that is, the connecting rod oil groove 211 is set at a position of 1 / 2 to 4 / 5 of the inner wall of the connecting rod connecting end 21, so that during the rotation of the eccentric shaft 12, the oil drain hole 122 is connected to the connecting rod oil groove 211 for 1 / 2 to 4 / 5 of the time, and is staggered with the connecting rod oil groove 211 for the rest of the time. In this way, within one rotation cycle of the eccentric shaft 12, by setting the length of the connecting rod oil groove 211, the length of the connection time between the oil drain hole 122 and the connecting rod oil groove 211 can be controlled, thereby controlling the amount of lubricating oil leaking through the oil drain hole 122, thereby controlling the amount of lubricating oil flowing out of the outlet of the pump oil channel 121 and thrown to the cylinder hole 40 within a suitable range, avoiding excessive oil supply or insufficient oil supply. In actual production, the length of the connecting rod oil groove 211 can be designed according to the amount of lubricating oil required by the compressor under high-frequency and low-frequency working conditions, thereby ensuring that the compressor is fully supplied with oil under various working conditions. In some specific embodiments, the length of the connecting rod oil groove 211 can be 0.5, 0.55, 0.6, 0.65, 0.7, 0.75 or 0.8 times the circumference of the inner wall of the connecting rod connecting end 21, etc.

[0057] In this embodiment, by designing the sizes of the oil drain hole 122 and the connecting rod oil groove 211, as long as the size of the oil drain hole 122 is set large enough and the connection time between the connecting rod oil groove 211 and the oil drain hole 122 is set long enough, two extreme states of lubricating oil supply can be achieved. One state is that, in the stage where the oil drain hole 122 is staggered with the connecting rod oil groove 211, the lubricating oil is blocked by the inner wall of the connecting section of the connecting rod 20 and cannot flow out smoothly from the oil drain hole 122. At this time, the lubricating oil entering the oil pump channel 121 is continuously and completely thrown toward the cylinder hole 40 through the outlet of the oil pump channel 121 under the action of centrifugal force to lubricate the cylinder hole 40; the other state is that in the stage where the oil drain hole 122 is connected with the connecting rod oil groove 211, the lubricating oil entering the oil pump channel 121 can continuously and completely flow out through the oil drain hole 122. At this time, no lubricating oil can move to the outlet of the oil pump channel 121 to be thrown out, that is, no lubricating oil enters the cylinder hole 40. At this time, the lubrication of the cylinder hole 40 is achieved by the lubricating oil entering the cylinder hole 40 in the previous state.

[0058] For example, in a specific embodiment, see Figure 7 and Figure 8 , the sizes of the connecting rod oil groove 211 and the oil drain hole 122 in the specific embodiment are described. Figure 7FIG. 2 is a top view of a local structure of a connecting rod 20 of a crankshaft assembly of this embodiment. Figure 8 1 is a top view of the crankshaft assembly of this embodiment.

[0059] In this specific embodiment, the ratio of the length of the connecting rod oil groove 211 to the circumference of the inner wall of the connecting rod connecting end 21 is 3:4. In addition, the connecting rod oil groove 211 is connected to the connecting rod connecting end 21 by a line (e.g., the center of one end of the connecting rod oil groove 211 in the length direction) and the bottom center of the connecting rod connecting end 21. Figure 5 Center Line L 1 As shown) and the rod body 23 (specifically as shown Figure 7 Center Line L 2 The angle α of the center line of the rod body 23 shown in FIG. 1 The angle between the connecting rod oil groove 211 and the connecting rod connecting end 21 is 0° to 90°, and the connecting rod oil groove 211 is connected to the connecting rod connecting end 211 along the length direction (the center position of the other end of the connecting rod oil groove 211 along the length direction) and the connecting rod connecting end 21 bottom center (such as Figure 7 Center Line L 3 The angle α between the rod body 23 is shown in FIG. 2 The angle is 0° to 90°. That is, the line connecting one end of the connecting rod oil groove 211 along the length direction and the center of the bottom of the connecting rod connecting end 21 (such as Figure 7 Center Line L 1 ), and the line connecting the other end of the connecting rod oil groove 211 along the length direction and the bottom center of the connecting rod connecting end 21 (as shown in Figure 7 Center Line L 3 The included angle β between the connecting rod connecting end 21 and the connecting rod connecting end 21 is 90°, and the portion of the connecting rod connecting end 21 where the connecting rod oil groove 211 is not provided occupies 1 / 4 of the circumference of the inner side wall of the connecting rod connecting end 21.

[0060] Thus, when the eccentric shaft 12 rotates until the oil drain hole 122 is offset from the connecting rod oil groove 211, that is, the oil drain hole 122 moves to the range of 0° to 90° on both sides of the rod body 23 (such as Figure 7 When the lubricating oil is within the range shown in the middle angle β, all the lubricating oil is thrown out to the cylinder hole 40 through the outlet of the pump oil channel 121. This area corresponds to the oil outlet area of ​​the pump oil channel 121. Figure 8 The two dotted lines L 4 and L 5 When the eccentric shaft 12 rotates until the oil drain hole 122 is connected to the connecting rod oil groove 211, all the lubricating oil is drained out through the oil drain hole 122 and the connecting rod oil groove 211. At this time, no lubricating oil is thrown out from the outlet of the pump oil channel 121, that is, the pump oil channel 121 does not discharge oil within this range. This area corresponds to the oil-free area of ​​the pump oil channel 121. Figure 8 The area except area W. It should be noted that, in this embodiment, theoretically, Figure 8 The angle value of the oil outlet area W should be Figure 7The value of the included angle β is equal. However, when the lubricating oil is thrown out from the outlet of the oil pumping passage 121, the lubricating oil will move towards the rod body 23 under the action of the centrifugal force of the eccentric shaft 12, so that the angular value of the oil outlet area W where the lubricating oil is actually discharged is slightly smaller than the theoretical included angle β.

[0061] In a specific embodiment, the above-mentioned included angle α 1 can be 0°, 30°, 44°, 60°, 75°, 80° or 90°, etc. The above-mentioned included angle α 2 can be 0°, 30°, 45°, 60°, 75°, 80° or 90°, etc. The design of the above-mentioned included angle can be selected according to the rotation direction of the eccentric shaft 12 and the rotation speed. For example, when the eccentric shaft 12 rotates clockwise, the lubricating oil thrown out from the outlet of the oil pumping passage 121 will be affected by the centrifugal force in the clockwise direction, and the faster the rotation speed of the eccentric shaft 12, the greater the centrifugal force when the lubricating oil is thrown out, and the more likely it is to move towards the rod body 23 after being thrown out. In this way, when the rotation speed of the eccentric shaft 12 is relatively fast, the part of the connecting rod connection end 21 without the connecting rod oil groove can be located entirely above the right of the rod body 23, that is, even if the above-mentioned included angle α 1 is 90°, the included angle α 2 is 0°, as shown in Figure 7 (b); conversely, when the eccentric shaft 12 rotates counterclockwise, the lubricating oil thrown out from the outlet of the oil pumping passage 121 is affected by the centrifugal force in the counterclockwise direction. When the rotation speed of the eccentric shaft 12 is relatively fast, the part of the connecting rod connection end 21 without the connecting rod oil groove can be located entirely below the left of the rod body 23, that is, even if the above-mentioned included angle α 1 is 0°, the included angle α 2 is 90°, as shown in Figure 7 (c); and as the rotation speed of the eccentric shaft 12 decreases, the centrifugal force received by the lubricating oil after being thrown out decreases. At this time, the angular values of α 1 and α 2 can be adjusted to ensure that the lubricating oil can still be thrown towards the cylinder bore 40 at a lower rotation speed, as shown in Figure 7 (a).

[0062] In another embodiment of the present invention, please refer to Figure 1 、 Figure 5 and Figure 9 , wherein, Figure 9 is a schematic structural view of the balance weight 13 of the crankshaft 10 of the crankshaft assembly of this embodiment.

[0063] In this embodiment, a receiving groove 131 is further provided at the top of the balance weight 13 facing the eccentric shaft 12. The receiving groove 131 communicates with the connecting rod oil groove 211, that is, the receiving groove 131 is located directly below the connecting rod oil groove 211. At least one oil leakage hole 132 is also formed in the balance weight 13. The oil leakage hole 132 penetrates through the top and bottom of the balance weight 13 and communicates with the receiving groove 131. In this way, after the lubricating oil flowing out from the oil discharge hole 122 enters the connecting rod oil groove 211, it can further fall into the receiving groove 131 and flow out through the oil leakage hole 132 to contact the bearing 60 sleeved outside the main shaft 11, thereby lubricating the bearing 60. In this way, the receiving groove 131 and the oil leakage hole 132 are provided on the balance weight 13 to guide a part of the lubricating oil entering the connecting rod oil groove 211 to flow to contact the bearing 60, thereby lubricating the bearing 60, so that the compressor using the crankshaft assembly of this embodiment can increase the lubrication of the bearing 60 while ensuring the lubrication of the cylinder bore 40, reduce the friction and noise at the bearing 60, and improve the rotational smoothness of the main shaft 11.

[0064] In this embodiment, as Figure 5 and Figure 9 shown, the receiving groove 131 is an arc-shaped groove or an annular groove provided around the eccentric shaft 12. Two oil leakage holes 132 are provided on the balance weight 13, and the two oil leakage holes 132 are respectively located on both sides of the eccentric shaft 12. That is, the lubricating oil entering the receiving groove 131 can flow out to the bearing 60 through the two oil leakage holes 132, thereby realizing multi-point lubrication of the bearing 60, and the lubrication effect of the bearing 60 is better.

[0065] In this embodiment, as Figure 5 and Figure 9 shown, the oil leakage hole 132 is a strip-shaped hole. One long side of the strip-shaped hole is connected to the side of the receiving groove 131. The lubricating oil flows in from the long side of the oil leakage hole 132. And, along the radial direction of the eccentric shaft 12, the width of the oil leakage hole 132 is 0.5 mm to 1.5 mm, ensuring that an appropriate amount of lubricating oil is provided to lubricate the bearing 60. In a specific embodiment, the width of the oil leakage hole 132 can be 0.5 mm, 0.8 mm, 1.0 mm, 1.2 mm or 1.5 mm, etc. When designing, it can be set according to the amount of lubricating oil required by the bearing 60, and it is not uniquely limited here.

[0066] It can be understood that in some other embodiments, the oil leakage hole 132 can also be a round hole. At this time, the oil leakage hole 132 is provided at the bottom of the receiving groove 131, so that the lubricating oil entering the receiving groove 131 directly flows out from the bottom of the groove through the oil leakage hole 132. At this time, the diameter of the oil leakage hole 132 can be set to 0.5 mm to 1.5 mm, specifically, it can be 0.5 mm, 0.8 mm, 1.0 mm, 1.2 mm or 1.5 mm, etc.

[0067] The crankshaft assembly of each of the above embodiments of the present invention can reduce the lubricating oil pumped to the cylinder bore 40 during the entire operating cycle of the crankshaft 10, thereby avoiding excessive oil pumping of the crankshaft 10 under high-speed operating conditions. Thus, it is ensured that the variable-frequency compressor using the crankshaft assembly of each embodiment can reduce the oil discharge amount while ensuring the lubrication of the cylinder bore 40, achieve continuous and stable oil supply under high-frequency conditions, and ensure that the variable-frequency compressor can operate efficiently and reliably under both high-frequency and low-frequency conditions. The variable-frequency operation of the variable-frequency compressor is more stable and more energy-saving.

[0068] Another embodiment of the present invention further provides a variable-frequency compressor, including the above-mentioned crankshaft assembly.

[0069] The variable-frequency compressor provided by the embodiment of the present invention can achieve continuous and stable oil supply under both high-frequency and low-frequency conditions by using the crankshaft assemblies of the above embodiments. The cylinder bore can be effectively lubricated, and under high-frequency conditions, there will also be no excessive oil pumping situation. Thus, the operation of the compressor is more stable and efficient.

[0070] It can be understood that the variable-frequency compressor also has other technical effects of the crankshaft assemblies provided by the above embodiments, which will not be elaborated here.

[0071] Another embodiment of the present invention further provides a refrigeration device, including the above-mentioned variable-frequency compressor.

[0072] The refrigeration device provided by the embodiment of the present invention can operate smoothly under both low-frequency and high-frequency conditions due to the use of the variable-frequency compressors of the above embodiments. The operation stability of the refrigeration device is improved, the refrigeration effect is improved, the operation energy consumption is lower, and the service life is extended.

[0073] It can be understood that the refrigeration device also has other technical effects of the variable-frequency compressors provided by the above embodiments, which will not be elaborated here.

[0074] In a specific embodiment, the above-mentioned refrigeration device can be a refrigerator, an air conditioner, etc.

[0075] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A crankshaft assembly, comprising a crankshaft and a connecting rod, wherein the crankshaft comprises a main shaft, a balancing block and an eccentric shaft, wherein the eccentric shaft is eccentrically mounted on one end of the main shaft through the balancing block, wherein the main shaft is provided with a main shaft oil groove, wherein the eccentric shaft is provided with an oil pump passage extending to the main shaft and communicating with the main shaft oil groove, wherein an outlet of the oil pump passage extends to an end of the eccentric shaft away from the main shaft, wherein the connecting rod comprises a connecting rod connecting end sleeved on the eccentric shaft, Features: The outer side wall of the eccentric shaft is provided with an oil drain hole connected to the pump oil channel, the inner side wall of the connecting rod connecting end is provided with a connecting rod oil groove, there is a gap between the connecting rod connecting end and the balancing block, and the connecting rod oil groove is connected to the gap; when the eccentric shaft rotates relative to the connecting rod connecting end, the oil drain hole can rotate to be connected to or staggered with the connecting rod oil groove; When the oil drain hole is rotated to be connected with the connecting rod oil groove, the lubricating oil flowing out of the oil drain hole can flow out from the gap; when the oil drain hole is rotated to be offset from the connecting rod oil groove, the inner side wall of the connecting rod connecting end prevents the lubricating oil from flowing out of the oil drain hole.

2. The crankshaft assembly according to claim 1, Features: The oil drain hole is arranged at the lower end of the eccentric shaft toward the balancing block and is located at the side of the eccentric shaft away from the center line of the main shaft. The connecting rod oil groove is arranged at the lower end of the connecting rod connecting end toward the balancing block.

3. The crankshaft assembly according to claim 2, Features: The connecting rod also includes a connecting rod driving end arranged opposite to the connecting rod connecting end, and a rod body connected to the connecting rod connecting end and the connecting rod driving end at both ends respectively, and the connecting rod oil groove is arranged on the side of the connecting rod connecting end away from the connecting rod driving end.

4. The crankshaft assembly according to claim 3, Features: The connecting rod oil groove is a notch arranged on the inner wall of the connecting rod connecting end toward the bottom of the balancing block, and along the circumference of the inner wall of the connecting rod connecting end, the ratio of the length of the connecting rod oil groove to the circumference of the inner wall of the connecting rod connecting end is 1:2 to 4:

5.

5. The crankshaft assembly according to claim 4, Features: Along the circumference of the inner wall of the connecting rod connecting end, the ratio of the length of the connecting rod oil groove to the circumference of the inner wall of the connecting rod connecting end is 3:4, and the angle between the line connecting one end point of the connecting rod oil groove along the length direction and the center of the bottom of the connecting rod connecting end and the rod body is 0°~90°, and the angle between the line connecting the other end point of the connecting rod oil groove along the length direction and the center of the bottom of the connecting rod connecting end and the rod body is 0°~90°.

6. The crankshaft assembly according to any one of claims 1 to 5, Features: The oil leakage hole is a strip hole arranged along the circumference of the outer side wall of the eccentric shaft, and the ratio of the length of the oil leakage hole to the circumference of the outer side wall of the eccentric shaft is 1:10 to 1:

8.

7. The crankshaft assembly according to claim 6, Features: The width of the oil drain hole is 0.5 mm to 1.5 mm.

8. The crankshaft assembly according to any one of claims 1 to 5, Features: The balancing block is also provided with a receiving groove on the top facing the eccentric shaft, the receiving groove is connected with the connecting rod oil groove, and the balancing block is also provided with at least one oil leakage hole penetrating the top and bottom of the balancing block, the oil leakage hole is connected with the receiving groove.

9. The crankshaft assembly according to claim 8, Features: The accommodating groove is an arc groove or an annular groove arranged around the eccentric shaft. Two oil leakage holes are arranged on the balancing block, and the two oil leakage holes are respectively located on both sides of the eccentric shaft.

10. The crankshaft assembly according to any one of claims 2 to 5, Features: An eccentric oil groove is also provided on the outer side wall of the eccentric shaft, one end of the eccentric oil groove is connected to the oil drain hole, and the other end of the eccentric oil groove spirally extends to the upper end of the eccentric shaft away from the balancing block and does not exceed the connecting end of the connecting rod; the spiral direction of the eccentric oil groove is opposite to the rotation direction of the eccentric shaft.

11. A variable frequency compressor, Features: A crankshaft assembly comprising any one of claims 1 to 10.

12. A refrigeration device, Features: Including the variable frequency compressor as claimed in claim 11.

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