CN117823516A - Crankshaft, compressor and refrigerating and heating equipment - Google Patents

Abstract

The application provides a crankshaft, a compressor and refrigerating and heating equipment. The crankshaft comprises a crank, a main shaft and an eccentric shaft, wherein a first oil groove is formed in the outer peripheral surface of the main shaft, an oil supply channel is formed in the eccentric shaft, the oil supply channel extends to the outer peripheral surface of the main shaft to be communicated with the first oil groove, and the axis of the oil supply channel is inclined to the axis of the eccentric shaft. According to the crankshaft, the oil supply channel is arranged in the eccentric shaft and extends to the outer peripheral surface of the main shaft obliquely to the axis of the eccentric shaft so as to be communicated with the first oil groove, so that the structural strength of the eccentric shaft can be ensured, lubricating oil pumped by the first oil groove can conveniently directly enter the oil supply channel to improve the oil supply capacity, and further the lubricating effect is improved; the main shaft is not required to be provided with an oil hole which is used for communicating the oil supply channel and the first oil groove, so that the processing technology is simplified, and the structural strength of the main shaft is increased; and furthermore, the spindle diameter of the crankshaft can be set smaller on the premise of ensuring the structural strength requirement of the spindle, so that the friction power loss is reduced.

Description

Crankshaft, compressor and refrigerating and heating equipment

Technical Field

The application belongs to the technical field of compressors, and particularly relates to a crankshaft, a compressor and refrigerating and heating equipment.

Background

Under the large background of global carbon peak and carbon neutralization, the reciprocating compressor is used as a core energy consumption unit of a refrigerating system, and the reduction of energy consumption loss and the improvement of reliability are hot spots for technical research of the reciprocating compressor. The crankshaft is used as a main transmission component in the compressor, the structural strength of the crankshaft is the basis of normal transmission, and the oiling capacity, the friction power loss performance and the wear resistance of the crankshaft have very important influence on the overall energy consumption coefficient and the reliability of a compressor system. In the related art, reducing the diameter of the crankshaft can reduce frictional power loss to a great extent, but deteriorate the oil application ability and increase the wear risk.

Disclosure of Invention

An aim of the embodiment of the application is to provide a crankshaft, a compressor and refrigerating and heating equipment, and solve the problems that in the prior art, under the premise of guaranteeing the structural strength of the crankshaft, when the diameter of the crankshaft is reduced, oiling capacity is deteriorated and abrasion risk is increased.

In order to achieve the above purpose, the technical scheme adopted in the embodiment of the application is as follows: the utility model provides a bent axle, including the crank, connect in the main shaft of crank one side with connect in the eccentric shaft of crank opposite side, be equipped with the first oil groove that is used for pumping lubricating oil on the outer peripheral face of main shaft, oil supply channel has been seted up to the inside of eccentric shaft, oil supply channel's one end runs through the eccentric shaft, oil supply channel's the other end extends to the outer peripheral face of main shaft, just oil supply channel with first oil groove intercommunication, oil supply channel's axis slope is in the axis of eccentric shaft.

In an alternative embodiment, the plane of the axis of the main shaft and the axis of the eccentric shaft is a zero plane, and the axis of the oil supply channel is inclined to the zero plane.

In an alternative embodiment, a first intersection point is formed at the intersection of the axis of the oil supply channel and the peripheral surface of the main shaft, the direction from the axis of the main shaft to the axis of the eccentric shaft is a zero position direction, the included angle between the perpendicular line from the first intersection point to the axis of the main shaft and the zero position direction is a, and the included angle between the perpendicular line and the zero position direction is-160 degrees-a-160 degrees.

In an alternative embodiment, a thrust surface is arranged on one side, close to the main shaft, of the crank, and the distance from the first intersection point to the thrust surface is h1, and h1 is more than or equal to 0 and less than or equal to 10mm.

In an alternative embodiment, the oil supply channel has an inner diameter d1, and 0 < d 1.ltoreq.9 mm.

In an alternative embodiment, an auxiliary oil hole is formed in the peripheral side face of the eccentric shaft, the auxiliary oil hole is communicated with the oil supply channel, the inner diameter of the auxiliary oil hole is d2, and d2 is more than 0 and less than or equal to 8mm.

In an alternative embodiment, a third intersection point is formed at the intersection of the axis of the auxiliary oil hole and the outer peripheral surface of the eccentric shaft, the direction from the axis of the main shaft to the axis of the eccentric shaft is a zero position direction, the included angle between the perpendicular line from the third intersection point to the axis of the eccentric shaft and the zero position direction is b, and the included angle is-90 degrees-t-90 degrees.

In an alternative embodiment, a second oil groove is formed in the peripheral side face of the eccentric shaft, the second oil groove is communicated with the auxiliary oil hole, and the second oil groove extends from the auxiliary oil hole towards one end, away from the crank, of the eccentric shaft.

In an alternative embodiment, an oil suction hole is formed in one end, away from the crank, of the main shaft, and an oil outlet hole for communicating the oil suction hole with the first oil groove is formed in the outer circumferential surface of the main shaft.

In an alternative embodiment, the inner diameter of the oil outlet hole is D1, and 0 < D1 is less than or equal to 10mm.

In an alternative embodiment, the included angle between the axis of the oil suction hole and the axis of the main shaft is b, and b is more than or equal to 0 and less than or equal to 15 degrees.

In an alternative embodiment, a second intersection point is formed at the intersection of the axis of the oil suction hole and the end face of the main shaft far away from the end of the crank, and the distance between the second intersection point and the circle center of the end face of the main shaft far away from the end of the crank is h2, and h2 is more than or equal to 0 and less than or equal to 6mm.

It is another object of an embodiment of the present application to provide a compressor, including casing, motor and crankcase, be equipped with compression pump group on the crankcase, the motor with the crankcase install in the casing, still include the bent axle of any embodiment above, the bent axle install in on the crankcase, the motor with the main shaft links to each other, compression pump group with the eccentric shaft links to each other.

It is still another object of an embodiment of the present application to provide a refrigeration and heating apparatus including a compressor as described in the above embodiment.

The beneficial effect of bent axle that this application embodiment provided lies in: compared with the prior art, the crankshaft provided by the embodiment of the application has the advantages that the oil supply channel is arranged in the eccentric shaft and extends to the outer peripheral surface of the main shaft obliquely to the axis of the eccentric shaft so as to be communicated with the first oil groove, so that lubricating oil pumped by the first oil groove can conveniently directly enter the oil supply channel to improve the oil supply capacity, and further the lubricating effect is improved; the oil hole which is used for communicating the oil supply channel and the first oil groove is not required to be arranged on the main shaft independently, so that the processing technology can be simplified, and the structural strength of the main shaft can be increased when the diameter of the main shaft is fixed; the oil supply channel extends obliquely to the axis of the eccentric shaft, and the structural strength of the eccentric shaft can be ensured when the diameter of the eccentric shaft is fixed; correspondingly, under the premise of guaranteeing the structural strength requirement of the main shaft, the main shaft diameter of the crankshaft can be set smaller, the working reliability of the crankshaft is improved, the friction power loss is reduced, the efficiency of a compressor applying the crankshaft is improved, and the vibration noise is reduced.

The beneficial effect of the compressor that this application embodiment provided lies in: compared with the prior art, the compressor provided by the embodiment of the application uses the crankshaft of the embodiment, has small friction loss, and can improve the running stability and reliability of the compressor and the running performance of the compressor.

The beneficial effect of refrigeration and heating equipment that this application embodiment provided lies in: compared with the prior art, the refrigerating and heating equipment has the advantages that the compressor is used, the operation is more stable, the noise is smaller, and the service life is long.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings that are required for the description of the embodiments or exemplary techniques will be briefly described below, and it is apparent that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to these drawings without inventive effort for a person of ordinary skill in the art.

Fig. 1 is a schematic structural view of a compressor according to an embodiment of the present application;

FIG. 2 is a schematic diagram of a crankshaft according to an embodiment of the present disclosure;

FIG. 3 is a schematic elevational view of the crankshaft of FIG. 2;

FIG. 4 is a schematic top view of the crankshaft of FIG. 3;

FIG. 5 is a schematic cross-sectional view taken along line A-A of FIG. 3;

fig. 6 is an enlarged schematic view of a part of the structure of the crankshaft in fig. 2.

Wherein, each reference numeral in the figure mainly marks:

a 100-compressor;

10-a crankshaft; 101-zero plane; 102-zero direction;

11-a main shaft; 1101-circle center; 111-a first oil groove; 1110-a first intersection point; 112-oil suction holes; 1121-a second intersection point; 113-an oil outlet hole; 114-an exhaust hole; 115-ring groove;

12-an eccentric shaft; 121-an oil supply channel; 122-an auxiliary oil hole; 123-a second oil groove;

13-crank; 131-ring table; 132-thrust surface;

21-a housing; 22-motor; 23-crankcase; 24-compressing the pump set; 241-cylinder; 242-piston; 243-a connecting rod; 25-thrust bearing.

Detailed Description

In order to make the technical problems, technical schemes and beneficial effects to be solved by the present application more clear, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the present application.

It will be understood that when an element is referred to as being "mounted" or "disposed" on another element, it can be directly on the other element or be 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 be indirectly connected to the other element.

In the description of the present application, the meaning of "a plurality" is two or more, unless explicitly defined otherwise. The meaning of "a number" is one or more than one unless specifically defined otherwise. The terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. The terms "center," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship based on that shown in the drawings, merely to facilitate description of the present application and to simplify the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be configured and operated in a particular orientation, and therefore should not be construed as limiting the present application.

In the description of the present application, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.

Reference in the specification to "one embodiment," "some embodiments," or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," and the like in the specification are not necessarily all referring to the same embodiment, but mean "one or more but not all embodiments" unless expressly specified otherwise. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.

The crankshaft is a component for driving a piston to operate in the reciprocating compressor, a main shaft of the crankshaft is arranged on a crank case of the compressor, the main shaft of the crankshaft is driven to rotate by a motor, and the eccentric shaft is driven to rotate by the crank, so that the eccentric shaft drives a connecting rod and the piston to reciprocate. When the crankshaft rotates, the crankshaft and the crankcase relatively move to form a friction pair. In order to reduce friction loss and ensure operational reliability, it is necessary to lubricate the friction pair. The design of the oil path on the crankshaft directly determines the performance, noise and stability of the operation of the compressor. Therefore, how to optimize the oil path of the crankshaft, so that the lubricating oil can effectively enter each friction pair, is important to improve the friction lubrication condition, reduce the abrasion, reduce the friction loss, improve the performance and reduce the vibration noise. At present, an oil suction cavity is generally arranged at the lower end of a main shaft, a main oil groove is arranged on the peripheral side surface of the main shaft, which is close to a crank, an upper oil hole and a lower oil hole are respectively arranged at two ends of the main oil groove, the lower oil hole is communicated with the oil suction cavity, an oil passage is arranged in an eccentric shaft to be communicated with the upper oil hole, an auxiliary oil hole communicated with the oil passage and an auxiliary oil groove communicated with the auxiliary oil hole are arranged on the eccentric shaft, and a lubricating oil pumping oil way on a crankshaft is formed to supply lubricating oil so as to lubricate each friction pair. The structure is characterized in that more oil holes are arranged on the crankshaft, the process is complex, the structural strength of the crankshaft can be influenced, particularly when the diameter of a main shaft of the crankshaft is smaller, the structural strength of the crankshaft is difficult to meet the structural requirement of transmission, and when the structural strength of the crankshaft is ensured, the sizes of the oil holes and the oil grooves are required to be reduced greatly, so that the oiling capacity of the crankshaft is reduced, the friction loss is increased, the performance of a compressor is influenced, larger vibration noise is generated, the risk of abrasion of the crankshaft is even increased, and the service life of the compressor is influenced.

Based on the principle, the embodiment of the application provides a crankshaft of a compressor, and the main shaft diameter of the crankshaft is reduced on the premise of ensuring the structural strength of the crankshaft so as to optimize an oil way on the crankshaft and ensure the oiling capacity of the crankshaft.

Referring to fig. 1, the compressor 100 includes a casing 21, a motor 22, a crank case 23, and a crankshaft 10, wherein a compression pump set 24 is provided on the crank case 23, the motor 22 is installed in the casing 21, the crank case 23 is installed in the casing 21, and the motor 22, the crank case 23, and the compression pump set 24 are supported and protected by the casing 21. The crankshaft 10 is mounted on a crankcase 23, and the crankshaft 10 connects the motor 22 with the compression pump set 24, so that the motor 22 drives the crankshaft 10 to rotate to drive the compression pump set 24 to operate, thereby achieving gas compression.

Referring to fig. 2 and 3, the crankshaft 10 includes a main shaft 11, a crank 13 and an eccentric shaft 12, wherein the main shaft 11 and the eccentric shaft 12 are respectively mounted on two sides of the crank 13, and the eccentric shaft 12 is connected with the main shaft 11 through the crank 13 so as to drive the eccentric shaft 12 to rotate when the main shaft 11 rotates.

The first oil groove 111 is provided on the outer circumferential surface of the main shaft 11, and when the crankshaft 10 rotates, the first oil groove 111 may function to pump lubricating oil, and when the main shaft 11 rotates on the crankcase 23 of the compressor 100, the first oil groove 111 may also supply lubricating oil into a friction pair formed between the main shaft 11 and the crankcase 23 to reduce friction loss, so that the main shaft 11 may flexibly and smoothly rotate on the crankcase 23.

The eccentric shaft 12 is internally provided with an oil supply channel 121, an axis 1210 of the oil supply channel 121 is inclined to an axis 120 of the eccentric shaft 12, one end of the oil supply channel 121 penetrates through the eccentric shaft 12, the other end of the oil supply channel 121 extends to the outer circumferential surface of the main shaft 11, and the oil supply channel 121 is communicated with the first oil groove 111, so that the resistance of lubricating oil entering the oil supply channel 121 can be reduced, the lubricating oil pumped in the first oil groove 111 can smoothly enter the oil supply channel 121, and the oiling capacity and the lubricating effect can be improved. And the outer peripheral surface extending to the main shaft 11 through the oil supply channel 121 is communicated with the first oil groove 111, and an oil hole is not required to be arranged to be communicated with the first oil groove 111 and the oil supply channel 121, so that the process can be reduced, and the structural strength of the main shaft 11 can be enhanced due to the reduction of the oil hole, so that when the structural strength of the main shaft 11 is fixed, the diameter of the main shaft 11 can be set smaller, further the friction power loss is reduced, the performance of the compressor 100 is improved, and the vibration noise during operation is reduced. In addition, since the axis 1210 of the oil supply channel 121 in the eccentric shaft 12 is inclined with the axis 120 of the eccentric shaft 12, the structural strength of the eccentric shaft 12 can be increased compared with the structure that the oil supply channel 121 is arranged along the axial direction of the eccentric shaft 12, and further, when the structural strength of the eccentric shaft 12 is constant, the diameter of the eccentric shaft 12 can be made smaller, so that the friction function loss is reduced, the performance of the compressor 100 is improved, and the vibration noise during operation is reduced.

Referring to fig. 1 and 2, when the crankshaft 10 is applied to a compressor 100, a main shaft 11 of the crankshaft 10 is connected with a motor 22, an eccentric shaft 12 is connected with a compression pump set 24, the main shaft 11 is driven to rotate by the motor 22, and the eccentric shaft 12 is driven to rotate by a crank 13, so as to drive the compression pump set 24 to work.

Compared with the prior art, in the crankshaft 10 provided by the embodiment of the present application, the oil supply channel 121 is provided in the eccentric shaft 12, and the oil supply channel 121 extends to the outer peripheral surface of the main shaft 11 obliquely to the axis 120 of the eccentric shaft 12 so as to be communicated with the first oil groove 111, so that lubricating oil pumped by the first oil groove 111 is convenient to directly enter the oil supply channel 121 to promote the oil application capability, and further promote the lubricating effect; and the oil hole for communicating the oil supply passage 121 with the first oil groove 111 is not required to be separately provided on the main shaft 11, so that not only the processing process can be simplified, but also the structural strength of the main shaft 11 can be increased when the diameter of the main shaft 11 is fixed; the oil supply channel 121 extends obliquely to the axis 120 of the eccentric shaft 12, so that the structural strength of the eccentric shaft 12 can be ensured when the diameter of the eccentric shaft 12 is fixed; accordingly, under the premise of ensuring the structural strength requirement of the main shaft 11, the shaft diameter of the main shaft 11 of the crankshaft 10 can be set smaller, the working reliability of the crankshaft 10 is improved, the friction power loss is reduced, the efficiency of the compressor 100 applying the crankshaft 10 is improved, and the vibration noise is reduced.

Compared with the prior art, the compressor 100 provided by the embodiment of the application uses the crankshaft 10 of the embodiment, has small friction loss, can improve the running stability and reliability of the compressor 100, and improves the running performance of the compressor 100.

In one embodiment, the compression pump set 24 further comprises a cylinder 241, a connecting rod 243 and a piston 242, the cylinder 241 is disposed on the crankcase 23, one end of the connecting rod 243 is connected to the eccentric shaft 12, the other end of the connecting rod 243 is connected to the piston 242, and the piston 242 is slidably disposed in the cylinder 241, so that when the crankshaft 10 rotates, the eccentric shaft 12 drives the connecting rod 243 to reciprocate to drive the piston 242 to reciprocate in the cylinder 241, thereby compressing gas, so that the compressor 100 forms a reciprocating piston compressor.

In one embodiment, referring to fig. 1 to 3, a thrust surface 132 is provided on one side of the crank 13, the thrust surface 132 being located on the side of the crank 13 adjacent to the main shaft 11, that is, the side of the crank 13 facing the main shaft 11 is provided with the thrust surface 132, so that the thrust surface 132 can locate the position of the crank 13 when the crankshaft 10 is mounted on the crankcase 23. The side of the crank 13 is provided with a thrust surface 132, the thrust surface 132 being located on the side of the crank 13 close to the main shaft 11, that is to say the side of the crank 13 facing the main shaft 11 is provided with a thrust surface 132.

In one embodiment, referring to fig. 1 to 3, the compressor 100 further includes a thrust bearing 25, the thrust surface 132 may position the thrust bearing 25, the thrust bearing 25 is sleeved on the main shaft 11, one end of the thrust bearing 25 is connected to the crankcase 23, and the other end of the thrust bearing 25 is attached to the thrust surface 132. The thrust bearing 25 is provided so that the crankshaft 10 can rotate smoothly and flexibly in the crankcase 23.

Referring to fig. 3 and 4, the axis 110 of the main shaft 11 is parallel to the axis 120 of the eccentric shaft 12, the axis 110 of the main shaft 11 and the axis 120 of the eccentric shaft 12 may define a plane, and the axis 110 of the main shaft 11 and the axis 120 of the eccentric shaft 12 are located on the plane, which is defined as a zero plane 101, that is, the plane on which the axis 110 of the main shaft 11 and the axis 120 of the eccentric shaft 12 are located is the zero plane 101.

In one embodiment, referring to fig. 3 and 4, the axis 1210 of the oil supply passage 121 is inclined to the zero-position surface 101. That is, the axis 1210 of the oil supply channel 121 is inclined to the plane of the axis 110 of the main shaft 11 and the axis 120 of the eccentric shaft 12, which not only improves the structural strength of the main shaft 11 and the eccentric shaft 12, but also improves the oil supply capability of the oil supply channel 121, thereby providing lubrication effect at the eccentric shaft 12.

Referring to fig. 3 and 4, since the oil supply passage 121 extends to the outer circumferential surface of the main shaft 11 to communicate with the first oil groove 111, the axis 1210 of the oil supply passage 121 is connected to the outer circumferential surface of the main shaft 11, and the intersection of the axis 1210 of the oil supply passage 121 and the outer circumferential surface of the main shaft 11 is defined as a first intersection 1110, that is, the intersection of the axis 1210 of the oil supply passage 121 and the outer circumferential surface of the main shaft 11 forms the first intersection 1110.

Referring to fig. 3 to 5, the axis 110 of the main shaft 11 is parallel to the axis 120 of the eccentric shaft 12, and the direction from the axis 110 of the main shaft 11 to the axis 120 of the eccentric shaft 12 is defined as the zero position direction 102, the zero position direction 102 is perpendicular to the axis 110 of the main shaft 11 and also perpendicular to the axis 120 of the eccentric shaft 12.

In one embodiment, referring to fig. 3, 4 and 5, the perpendicular 1111 of the first intersection 1110 to the axis 110 of the main shaft 11 forms an angle a with the zero direction 102, and-160 ° -a-160 °, such as-160 °, -140 °, -120 °, -100 °, -90 °, -80 °, -60 °, -40 °, -20 °, 0 °, 20 °, 40 °, 60 °, 80 °, 90 °, 100 °, 120 °, 140 °, 160 °, etc., the position of the first intersection 1110 may determine the position of the oil supply channel 121, and may also allow the lubricating oil in the first oil sump 111 to enter the oil supply channel 121 more smoothly, providing oil supply capability.

In one embodiment, referring to fig. 1 to 3, the distance from the first intersection point 1110 to the thrust surface 132 is h1, and 0.ltoreq.h1.ltoreq.10mm, for example, h1 may be 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, etc., and this position may enable the oil supply channel 121 to be close to one end of the main shaft 11, may be closer to the main shaft 11, shorten the length of the oil supply channel 121 in the main shaft 11, and ensure the structural strength of the main shaft 11. In addition, the oil supply channel 121 can make the lubricating oil pumped by the first oil groove 111 pass through the oil supply channel 121 and reach the thrust surface 132, so that the thrust bearing 25 can be flexibly and stably rotated on the main shaft 11 during use, and the compressor 100 using the crankshaft 10 can be more stably and reliably operated with less vibration operation sound.

In one embodiment, referring to fig. 1 to 3, a ring table 131 is disposed on one surface of the crank 13, the ring table 131 is disposed on one surface of the crank 13 near the main shaft 11, the ring table 131 is disposed around the main shaft 11, the thrust surface 132 is a surface of the ring table 131 away from the eccentric shaft 12, and the positioning of the ring table 131 can facilitate determining the position of the thrust surface 132, improving the manufacturing accuracy, and facilitating the installation of the thrust bearing 25.

In one embodiment, referring to fig. 1 to 3, the spindle 11 is provided with a ring groove 115, the ring groove 115 is disposed around the spindle 11, the ring groove 115 is located on the spindle 11 near the thrust surface 132, and the thrust surface 132 may be a side wall of the ring groove 115, i.e., the thrust surface 132 may be a side wall of the ring groove 115 near the crank 13. The oil supply channel 121 passes through the annular groove 115, so that the oil supply channel 121 is communicated with the annular groove 115, and the annular groove 115 is arranged, so that on one hand, during manufacturing, the annular groove 115 can be a tool withdrawal groove to facilitate machining of the thrust surface 132, improve machining precision, and on the other hand, the annular groove 115 can store a certain amount of lubricating oil so as to supply lubricating oil to the thrust bearing 25, and ensure the lubricating effect of the thrust bearing 25.

In one embodiment, referring to fig. 3 and 4, the inner diameter d1 of the oil supply channel 121 is d1, and 0 < d1 is less than or equal to 9mm, for example, d1 may be 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, etc., and the inner diameter d1 of the oil supply channel 121 is set to be less than or equal to 9mm to ensure good oiling ability of the oil supply channel 121, ensure lubrication effect of the eccentric shaft 12, and ensure structural strength of the eccentric shaft 12 and the main shaft 11. When the inner diameter d1 of the oil supply passage 121 is excessively large, for example, more than 9mm, structural strength of the eccentric shaft 12 and the main shaft 11 is affected, resulting in difficulty in satisfying the transmission requirement of the structural strength of the main shaft 11.

In one embodiment, the inner diameter of the oil supply passage 121 is the same throughout the length of the oil supply passage 121 to facilitate machining. It will be appreciated that the oil supply passage 121 may be provided with a variable inner diameter, such as in the direction from the main shaft 11 to the eccentric shaft 12, with the inner diameter of the oil supply passage 121 being gradually reduced so that the lubricating oil may enter the oil supply passage 121 more sequentially. Of course, the inner diameter of the oil supply passage 121 is gradually increased from the main shaft 11 to the eccentric shaft 12 so that the lubricating oil in the oil supply passage 121 can more sequentially enter the friction pair on the eccentric shaft 12. In addition, the inner diameter of the oil supply passage 121 may be increased and then decreased in the direction from the main shaft 11 to the eccentric shaft 12. Of course, the inner diameter of the oil supply passage 121 may be decreased first and then increased in the direction from the main shaft 11 to the eccentric shaft 12, etc.

In an embodiment, referring to fig. 3 and 4, an auxiliary oil hole 122 is formed on a circumferential side surface of the eccentric shaft 12, the auxiliary oil hole 122 is communicated with the oil supply channel 121, and the auxiliary oil hole 122 is provided, so that oil feeding capability can be improved, and further lubrication effect of a part of the eccentric shaft 12 is improved.

In one embodiment, the inner diameter d2 of the auxiliary oil hole 122 is d2, and 0 < d2 is less than or equal to 8mm, for example, d2 may be 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, etc., and the inner diameter d2 of the auxiliary oil hole 122 is set to be less than or equal to 8mm, so as to ensure good oiling ability of the auxiliary oil hole 122, ensure lubrication effect of the eccentric shaft 12, and ensure structural strength of the eccentric shaft 12. However, when the inner diameter d2 of the auxiliary oil hole 122 is too large, for example, greater than 8mm, the structural strength of the eccentric shaft 12 is affected, so that the structural strength of the eccentric shaft 12 is difficult to meet the transmission requirement.

In one embodiment, referring to fig. 3 to 5, the intersection of the axis 1220 of the auxiliary oil hole 122 with the outer circumferential surface of the eccentric shaft 12 is defined as a third intersection 1221, that is, the intersection of the axis 1220 of the auxiliary oil hole 122 with the outer circumferential surface of the eccentric shaft 12 forms a third intersection 1221, the angle between the perpendicular 1222 of the axis 120 of the third intersection 1221 to the eccentric shaft 12 and the zero direction 102 is t, and-90 t is 90, such as t may be-90, -80, -70, -60, -50, -40, -30, -20, -10, 0, 10, 20, 30, 40, 50, 60, 70, 80, 90, etc., and such a position of the third intersection 1221 may be determined that the auxiliary oil hole 122 is located on the side of the eccentric shaft 12 close to the main shaft 11, while in use, the side of the eccentric shaft 12 close to the main shaft 11 is relatively less stressed, such that the auxiliary oil hole 122 is located in a less stressed region of the eccentric shaft 12 to ensure good structural strength of the eccentric shaft 12. In one embodiment, referring to fig. 3 and 4, a second oil groove 123 is provided on the circumferential side surface of the eccentric shaft 12, the second oil groove 123 is communicated with the auxiliary oil hole 122, the second oil groove 123 is provided by extending the auxiliary oil hole 122 toward one end of the eccentric shaft 12 far away from the crank 13, and the second oil groove 123 is provided, and the lubricating oil in the auxiliary oil hole 122 can enter the second oil groove 123 to supply the lubricating oil to the friction pair on the eccentric shaft 12, so as to improve the lubricating effect.

In one embodiment, referring to fig. 3 and 4, the second oil groove 123 may be a chute inclined in a length direction to the axial direction of the eccentric shaft 12, so as to increase the coverage area of the second oil groove 123, and further improve the oil supply lubrication effect of the second oil groove 123. It will be appreciated that the second oil groove 123 may also be provided as a straight groove parallel to the axial direction of the eccentric shaft 12.

In one embodiment, the second oil groove 123 may be further configured as a spiral groove, and the spiral direction of the second oil groove 123 is opposite to the rotation direction of the crankshaft 10, so as to improve the oil pumping capability of the second oil groove 123, and further improve the oil applying capability and lubrication effect of the crankshaft 10.

In an embodiment, referring to fig. 3 and 4, when the second oil groove 123 is a chute, the inclination direction of the second oil groove 123 is opposite to the rotation direction of the crankshaft 10, so that the oil pumping capability of the second oil groove 123 can be improved, and further the oil pumping capability and lubrication effect of the crankshaft 10 can be improved.

In one embodiment, referring to fig. 3 and 4, the first oil groove 111 is a spiral groove having a rotation direction opposite to that of the main shaft 11 so that lubricating oil can be pumped through the spiral groove when the crankshaft 10 rotates, thereby improving oil supply capability.

In one embodiment, the first oil groove 111 is a straight groove, and the length direction of the second oil groove 123 is along the axial direction of the main shaft 11, so as to facilitate machining.

In one embodiment, referring to fig. 3, 4 and 6, an oil suction hole 112 is formed at an end of the main shaft 11 away from the crank 13, and an oil outlet hole 113 is formed on an outer circumferential surface of the main shaft 11, which communicates the oil suction hole 112 with the first oil groove 111. Thus, when the crankshaft 10 rotates, the oil suction hole 112 can suck the lubricating oil, and the lubricating oil in the oil suction hole 112 is sucked from the oil outlet hole 113 to the first oil groove 111, that is, the lubricating oil can be sucked through the oil suction hole 112 and then enters the first oil groove 111 through the oil outlet hole 113, so that pumping supply of the lubricating oil is realized.

In one embodiment, referring to fig. 3, 4 and 6, the oil outlet 113 has an inner diameter D1, and 0 < D1 is less than or equal to 10mm, for example, D1 may be 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, etc. to ensure that lubrication can smoothly enter the first oil groove 111 from the oil outlet 113, and the structural strength of the main shaft 11 is not greatly affected, so that the main shaft 11 can meet the transmission requirement. When the inner diameter D1 of the oil outlet hole 113 is set too large, for example, greater than 10mm, the structural strength of the main shaft 11 may be difficult to satisfy the transmission requirement.

In one embodiment, referring to fig. 3, 4 and 6, the included angle between the axis 1120 of the oil suction hole 112 and the axis 110 of the main shaft 11 is b, and b is 0 ° or less and 15 °, for example, b may be 0 °, 1 °, 2 °, 3 °, 4 °, 5 °, 6 °, 7 °, 8 °, 9 °, 10 °, 11 °, 12 °, 13 °, 14 °, 15 °, etc. to ensure good oil suction capability of the oil suction hole 112 and may well ensure structural strength of the main shaft 11. However, when the included angle b between the axis 1120 of the oil suction hole 112 and the axis 110 of the main shaft 11 is too large, for example, greater than 15 °, the diameter of the main shaft 11 needs to be increased, or the thickness of the sidewall on one side of the main shaft 11 may be too small, which makes it difficult for the structural strength of the main shaft 11 to meet the transmission requirement.

Referring to fig. 3, 4 and 6, the intersection of the axis 1120 of the oil suction hole 112 with the end surface of the main shaft 11 at the end far from the crank 13 is defined as a second intersection 1121, that is, the intersection of the axis 1120 of the oil suction hole 112 with the end surface of the main shaft 11 at the end far from the crank 13 forms the second intersection 1121.

In one embodiment, the distance from the second intersection point 1121 to the center 1101 of the end surface of the main shaft 11 far from the crank 13 is h2, and 0.ltoreq.h2.ltoreq.6mm, for example, h2 may be 0, 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, etc., and this position may ensure that the thickness of the side wall of the oil suction hole 112 is not too small, so as to ensure good structural strength of the main shaft 11. When the distance h2 from the second intersection 1121 to the center 1101 of the end surface of the main shaft 11 away from the crank 13 is too large, for example, greater than 6mm, the thickness of the side wall on the side of the main shaft 11 is too small, resulting in difficulty in satisfying the transmission requirement for the structural strength of the main shaft 11.

In one embodiment, the inner diameter D2 of the oil suction hole 112 is D2, and 0 < D2 is less than or equal to 9mm, for example, D2 may be 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, etc., and the inner diameter D2 of the oil suction hole 112 is set to be less than or equal to 9mm to ensure good oil suction capability of the oil suction hole 112, and also to ensure structural strength of the main shaft 11. However, when the inner diameter D2 of the oil suction hole 112 is too large, for example, greater than 9mm, the thickness of the sidewall of the oil suction hole 112 is too small, which affects the structural strength of the main shaft 11, so that the structural strength of the main shaft 11 is difficult to meet the transmission requirement.

In one embodiment, the crankshaft 10 may be made of gray cast iron, ductile iron, or the like to ensure good structural strength of the crankshaft 10.

In one embodiment, the main shaft 11 is provided with an exhaust hole 114, and the exhaust hole 114 is communicated with the oil suction hole 112, so that the oil suction hole 112 can be used for conveniently exhausting gas in the oil suction hole 112 when sucking the lubricating oil, and the capability of the oil suction hole 112 for sucking the lubricating oil is improved.

Referring to fig. 1 and 3, in the crankshaft 10 of the embodiment of the present application, the oil supply channel 121 in the eccentric shaft 12 extends to the outer peripheral surface of the main shaft 11 to be communicated with the first oil groove 111, so that not only can lubricating oil in the first oil groove 111 enter the oil supply channel 121, and the oil supply effect is improved, but also the processing technology can be simplified, and good structural strength of the crankshaft 10 can be ensured, friction loss of the crankshaft 10 is reduced, rotational vibration and noise of the crankshaft 10 are reduced, and performance and service life of the compressor 100 using the crankshaft 10 are improved.

The embodiment of the application also provides a refrigerating and heating device, which comprises the compressor in any embodiment. The refrigerating and heating equipment uses the compressor, is more stable in operation, smaller in noise and long in service life, and has the technical effects of the compressor of the embodiment, and the compressor is not repeated herein.

The refrigerating and heating equipment can be refrigerating equipment, such as a refrigerator and an air conditioner, heating equipment, and cooling and heating equipment.

The foregoing description of the preferred embodiments is merely exemplary in nature and is in no way intended to limit the invention, since it is intended to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention.

Claims (14)

1. The utility model provides a bent axle, includes the crank, connect in main shaft of crank one side with connect in the eccentric shaft of crank opposite side, be equipped with the first oil groove that is used for pumping lubricating oil on the outer peripheral face of main shaft, its characterized in that: an oil supply channel is formed in the eccentric shaft, one end of the oil supply channel penetrates through the eccentric shaft, the other end of the oil supply channel extends to the outer peripheral surface of the main shaft, the oil supply channel is communicated with the first oil groove, and the axis of the oil supply channel is inclined to the axis of the eccentric shaft.

2. The crankshaft as claimed in claim 1, wherein: the axial line of the main shaft and the plane where the axial line of the eccentric shaft is located are zero-position surfaces, and the axial line of the oil supply channel is inclined to the zero-position surfaces.

3. The crankshaft as claimed in claim 1, wherein: the intersection of the axis of the oil supply channel and the outer peripheral surface of the main shaft forms a first intersection point, the direction from the axis of the main shaft to the axis of the eccentric shaft is a zero position direction, the included angle between the perpendicular line from the first intersection point to the axis of the main shaft and the zero position direction is a, and the included angle between the perpendicular line and the zero position direction is-160 degrees more than or equal to 160 degrees.

4. A crankshaft as claimed in claim 3, wherein: the side of the crank, which is close to the main shaft, is provided with a thrust surface, and the distance from the first intersection point to the thrust surface is h1, and h1 is more than or equal to 0 and less than or equal to 10mm.

5. The crankshaft as claimed in any one of claims 1 to 4, wherein: the inner diameter of the oil supply channel is d1, and d1 is more than 0 and less than or equal to 9mm.

6. The crankshaft as claimed in any one of claims 1 to 4, wherein: an auxiliary oil hole is formed in the circumferential side face of the eccentric shaft, the auxiliary oil hole is communicated with the oil supply channel, the inner diameter of the auxiliary oil hole is d2, and d2 is more than 0 and less than or equal to 8mm.

7. The crankshaft as claimed in claim 6, wherein: the intersection of the axis of the auxiliary oil hole and the outer peripheral surface of the eccentric shaft forms a third intersection point, the direction from the axis of the main shaft to the axis of the eccentric shaft is a zero position direction, the included angle between the perpendicular line from the third intersection point to the axis of the eccentric shaft and the zero position direction is t, and the included angle is-90 degrees more than or equal to 90 degrees.

8. The crankshaft as claimed in claim 6, wherein: the eccentric shaft is characterized in that a second oil groove is formed in the circumferential side face of the eccentric shaft and communicated with the auxiliary oil hole, and the second oil groove extends towards one end, away from the crank, of the eccentric shaft through the auxiliary oil hole.

9. The crankshaft as claimed in any one of claims 1 to 4, wherein: the main shaft is far away from the one end of crank is equipped with the oil suction hole, set up on the outer peripheral face of main shaft intercommunication the oil suction hole with the oil outlet of first oil groove.

10. The crankshaft as claimed in claim 9, wherein: the inner diameter of the oil outlet hole is D1, and D1 is more than 0 and less than or equal to 10mm.

11. The crankshaft as claimed in claim 9, wherein: the included angle between the axis of the oil suction hole and the axis of the main shaft is b, and b is more than or equal to 0 degree and less than or equal to 15 degrees.

12. The crankshaft as claimed in claim 9, wherein: the axis of the oil suction hole and the intersection of the end surface of the main shaft far away from one end of the crank form a second intersection point, and the distance from the second intersection point to the circle center of the end surface of the main shaft far away from one end of the crank is h2, and h2 is more than or equal to 0 and less than or equal to 6mm.

13. The utility model provides a compressor, includes casing, motor and crankcase, be equipped with compression pump group on the crankcase, the motor with the crankcase install in the casing, its characterized in that: a crankshaft as claimed in any one of claims 1 to 12, wherein the crankshaft is mounted to the crankcase, the motor is connected to the main shaft, and the compression pump unit is connected to the eccentric shaft.

14. A refrigeration and heating apparatus, characterized in that: comprising a compressor according to claim 13.