CN218407730U - Crankshaft, compressor and refrigerating and heating equipment - Google Patents

Abstract

The application provides a bent axle, compressor and refrigeration equipment of heating. The crankshaft comprises a crank, a main shaft and an eccentric shaft, wherein a first oil groove and a second oil groove are formed in the outer peripheral surface of the main shaft, a thrust surface is arranged on the crank, and the second oil groove extends to the thrust surface through the first oil groove. According to the crankshaft, the first oil groove is formed in the outer peripheral surface of the main shaft, so that lubricating oil can be supplied to a friction pair formed between the crankcase and the main shaft when the crankshaft rotates, and friction loss between the crankcase and the main shaft is reduced; set up the second oil groove on the main shaft, the first oil groove of second oil groove one end intercommunication, the second oil groove other end extends to the thrust surface to when being applied to the compressor, can supply lubricating oil to the footstep bearing of compressor, in order to reduce footstep bearing pivoted friction loss, guarantee that footstep bearing is steady, nimble to rotate, reduce bent axle pivoted friction loss and vibration noise, and then promote compressor operation's stationarity and reliability, promote compressor operating characteristics.

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 refrigeration and heating equipment.

Background

With the continuous development of social economy and scientific technology, the living standard of people is improved, and the environmental protection consciousness is also greatly enhanced. As a household appliance essential to daily life, a refrigerator has higher and higher requirements for performance. The compressor is the most central part of refrigerator refrigeration, and the performance quality directly determines the performance of the refrigerator, and how to promote the efficiency of the compressor and reduce the vibration noise of the compressor on the premise of ensuring the reliability is the core problem of the current industry technical research.

The crankshaft is a part for driving the piston to operate in the reciprocating compressor, a main shaft of the crankshaft is arranged on a crankcase of the compressor and drives the main shaft of the crankshaft to rotate through a motor, and an eccentric shaft is driven to rotate through the crankshaft, so that the eccentric shaft drives the connecting rod and the piston to reciprocate. When the crankshaft rotates, the crankshaft and the crankcase move relatively to form a friction pair. In order to reduce friction loss and ensure the reliability of operation, the friction pair needs to be lubricated. The design of the oil circuit 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 and enable lubricating oil to 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. Currently, 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 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 path on a crankshaft is formed to supply lubricating oil to lubricate each friction pair. However, the oil circuit still has the problems of insufficient oil supply and lubrication, so that the friction loss is large when the crankshaft runs, the performance of the compressor is affected, and the vibration noise is large.

SUMMERY OF THE UTILITY MODEL

An object of the embodiment of the application is to provide a bent axle, compressor and refrigeration equipment of heating, solve the problem that the oil circuit has fuel feeding and lubrication deficiency on the bent axle of compressor among the prior art, lead to the bent axle when the operation, frictional loss is great, influences the compressor performance, and vibration noise is great problem.

In order to achieve the above purpose, the embodiment of the present application adopts the following technical solutions: the crank comprises a crank, a main shaft arranged on one side of the crank and an eccentric shaft arranged on the other side of the crank, wherein a first oil groove used for pumping lubricating oil is formed in the peripheral surface of the main shaft, a thrust surface used for positioning a thrust bearing is arranged on one side, close to the main shaft, of the crank, a second oil groove is further formed in the main shaft, one end of the second oil groove is communicated with the first oil groove, and the other end of the second oil groove extends to the thrust surface.

In an alternative embodiment, a ring groove is circumferentially arranged on the main shaft, one side wall of the ring groove is the thrust surface, and the other end of the second oil groove is communicated with the ring groove.

In an alternative embodiment, the absolute value of the difference between the depth of the second oil groove and the depth of the ring groove is less than or equal to 0.5mm.

In an optional embodiment, the main shaft is provided with a first oil hole, the first oil hole is located at one end of the first oil groove close to the crank, and one end of the second oil groove is connected with the first oil hole.

In an alternative embodiment, a width of an end of the second oil groove that is connected to the first oil hole is smaller than or equal to a width of the first oil hole.

In an alternative embodiment, the axial direction of the first oil hole is arranged in the radial direction of the main shaft; in the rotation direction of the spindle: the axis of the first oil hole is coincident with or positioned on the front side of a zero line, the included angle between the axis of the first oil hole and the zero line is a, the a is more than or equal to 0 degrees and less than or equal to 120 degrees, and the zero line is a straight line which points to the axis of the eccentric shaft from the intersection point of the axis of the first oil hole and the axis of the main shaft along the radial direction of the main shaft.

In an alternative embodiment, the minimum width of the second oil groove is greater than or equal to 0.5mm.

In an alternative embodiment, the second oil groove is a straight groove with the length direction extending along the axial direction of the main shaft; or the second oil groove is an inclined groove with the length direction inclined to the axial direction of the main shaft; or the second oil groove is a spiral groove, and the rotation direction of the spiral groove is opposite to the rotation direction of the main shaft.

In an optional embodiment, the width of the second oil groove is set to be equal to the width of the first oil groove in the direction from the thrust surface; or the width of the second oil groove is gradually changed from the first oil groove to the thrust surface.

In an alternative embodiment, the first oil groove is a spiral groove, and the spiral direction of the spiral groove is opposite to the rotation direction of the main shaft; or the first oil groove is a straight groove arranged along the axial direction of the main shaft in the length direction.

In an optional embodiment, the first oil grooves are two spiral grooves with opposite rotation directions, the number of the second oil grooves is two, and the second oil grooves are in one-to-one correspondence communication with the first oil grooves.

Another objective of an embodiment of the present application is to provide a compressor, which includes a crankcase, a thrust bearing, and the crankshaft of any of the above embodiments, wherein the crankcase is sleeved on the main shaft, the thrust bearing is sleeved on the main shaft, one end of the thrust bearing is connected to the crankcase, and the other end of the thrust bearing is attached to the thrust surface.

It is a further object of the embodiments of the present application to provide a refrigerating and heating apparatus including a compressor as in the above embodiments.

The beneficial effect of the 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 first oil groove is formed in the outer peripheral surface of the main shaft, so that lubricating oil can be supplied to a friction pair formed between the crankcase and the main shaft when the crankshaft rotates, and the friction loss between the crankcase and the main shaft is reduced; set up the second oil groove on the main shaft, the first oil groove of second oil groove one end intercommunication, the second oil groove other end extends to the thrust surface to when being applied to the compressor, can supply lubricating oil to the footstep bearing of compressor, in order to reduce footstep bearing pivoted friction loss, guarantee that footstep bearing is steady, nimble to rotate, reduce bent axle pivoted friction loss and vibration noise, and then promote compressor operation's stationarity and reliability, promote compressor operating characteristics.

The beneficial effect of the compressor that this application embodiment provided lies in: compared with the prior art, the compressor of this application embodiment has used the bent axle of above-mentioned embodiment, not only can reduce the friction loss between crankcase and main shaft, can also reduce footstep bearing pivoted friction loss, promotes compressor operation's stationarity and reliability, promotes compressor running performance.

The beneficial effect of the refrigeration equipment that this application embodiment provided lies in: compared with the prior art, this application refrigeration equipment of heating has used above-mentioned compressor, and the operation is more stable, and the noise is littleer, and is longe-lived.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for the embodiments or exemplary technical descriptions will be briefly introduced below, it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art that other drawings may be obtained according to the drawings without creative efforts.

Fig. 1 is a schematic view of a partial structure of a compressor according to an embodiment of the present disclosure;

FIG. 2 is a schematic structural diagram of a first crankshaft provided in an embodiment of the present application;

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

FIG. 4 is a schematic structural diagram of a second crankshaft provided in an embodiment of the present application;

FIG. 5 is a schematic top view of the crankshaft of FIG. 3;

FIG. 6 is a schematic structural diagram of a third crankshaft provided in an embodiment of the present application;

FIG. 7 is a schematic structural diagram of a fourth crankshaft provided in the exemplary embodiment of the present disclosure;

FIG. 8 is a schematic structural diagram of a fifth crankshaft provided in an embodiment of the present application;

FIG. 9 is a schematic structural diagram of a sixth crankshaft provided in an embodiment of the present application;

FIG. 10 is a schematic structural diagram of a seventh crankshaft provided in the embodiments of the present application;

fig. 11 is a schematic structural diagram of an eighth crankshaft provided in an embodiment of the present application.

Wherein, in the figures, the various reference numbers are given by way of example only:

10-a crankshaft; 101-zero bit line; 11-a main shaft; 111-a first oil sump; 1111-a first helical groove; 1112-a second helical groove; 112-first oil hole; 1121-first oil dividing hole; 1122-a second oil dividing hole; 113-a second oil sump; 1131 — first oil subglotting; 1132 — a second oil sub-tank; 114-a ring groove; 115-an oil suction chamber; 116-a second oil hole; 1161-a first sub oil hole; 1162-a second oil sub-hole; 12-an eccentric shaft; 121-oil duct; 13-a crank; 131-ring table; 132-a thrust surface;

21-a crankcase; 211-cylinder block; 22-a thrust bearing; 23-a piston; 24-a connecting rod; 25-wrist pin; 26-spring pin.

Detailed Description

In order to make the technical problems, technical solutions and advantageous effects to be solved by the present application clearer, 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 merely illustrative of and not restrictive on the broad application.

It will be understood that when an element is referred to as being "secured to" 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, "a plurality" means two or more unless specifically limited otherwise. The meaning of "a number" is one or more unless specifically limited otherwise. The terms "first", "second" and "first" 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 defined as "first" or "second" may explicitly or implicitly include one or more of that 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 indicated in the drawings for convenience in describing the application and for simplicity in description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus are not to be considered limiting of the application.

In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or may be connected through the use of two elements or the interaction of two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

Reference throughout this 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 present application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," or the like, in various places throughout this specification are not necessarily all referring to the same embodiment, but rather mean "one or more but not all embodiments" unless specifically stated otherwise. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.

Fig. 3 is a schematic top view of the crankshaft 10 of the present embodiment, which is rotated clockwise, and the main shaft 11 is partially shown in a perspective view to show the position of the main shaft 11. Fig. 5 is a schematic top view of the crankshaft 10 of the present embodiment when rotating counterclockwise, in which the main shaft 11 is partially in perspective view to show the position of the main shaft 11. When the crankshaft 10 rotates, the rotation direction of the crankshaft 10 is the rotation direction of the crankshaft 10 viewed from the direction from the eccentric shaft 12 to the main shaft 11, and the crankshaft 10 rotates clockwise as shown in fig. 3. As shown in fig. 5, the crankshaft 10 rotates counterclockwise.

Referring to FIG. 2, a crankshaft 10 provided herein will now be described. The crankshaft 10 comprises a main shaft 11, a crank 13 and an eccentric shaft 12, wherein the main shaft 11 and the eccentric shaft 12 are respectively installed on two sides of the crank 13, and the crank 13 is used for connecting the eccentric shaft 12 with the main shaft 11 so as to drive the eccentric shaft 12 to rotate when the main shaft 11 rotates.

Referring to fig. 1, a first oil groove 111 is formed on an 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 21 of the compressor, the first oil groove 111 may also supply the lubricating oil to a friction pair formed between the main shaft 11 and the crankcase 21 to reduce wear, so that the main shaft 11 may flexibly and smoothly rotate on the crankcase 21.

One side of the crank 13 is provided with a thrust surface 132, and the thrust surface 132 is located on one side of the crank 13 close 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. The thrust surface 132 is used to position the thrust bearing 22 so that the thrust bearing 22 may be defined by the thrust surface 132 when the thrust bearing 22 is installed.

The main shaft 11 is further provided with a second oil groove 113, one end of the second oil groove 113 is communicated with the first oil groove 111, and the other end of the second oil groove 113 extends to the thrust surface 132, so that when the crankshaft 10 rotates, the first oil groove 111 pumps lubricating oil, when the lubricating oil reaches the joint of the second oil groove 113 and the first oil groove 111, the lubricating oil can reach the thrust surface 132 through the second oil groove 113, so that when the crankshaft 10 rotates, the thrust bearing 22 can be sleeved on the main shaft 11, and one end of the thrust bearing 22 is attached to the thrust surface 132 to limit the position of the thrust bearing 22, so that the thrust bearing 22 can be supplied with the lubricating oil through the second oil groove 113, so that the thrust bearing 22 can flexibly and stably rotate on the main shaft 11, and therefore, a compressor applying the crankshaft 10 can operate more stably and reliably, and vibration operation sound is small.

Compared with the prior art, in the crankshaft 10 of the embodiment of the present application, the first oil groove 111 is provided on the outer circumferential surface of the main shaft 11, so that when the crankshaft 10 rotates, lubricating oil can be supplied to a friction pair formed between the crankcase 21 and the main shaft 11, and the friction loss between the crankcase 21 and the main shaft 11 is reduced; set up second oil groove 113 on main shaft 11, the first oil groove 111 of 113 one ends of second oil groove intercommunication, the 113 other ends of second oil groove extend to thrust surface 132, thereby when being applied to the compressor, can supply lubricating oil to the footstep bearing 22 of compressor, with reduce footstep bearing 22 pivoted friction loss, guarantee that footstep bearing 22 is steady, nimble rotation, reduce bent axle 10 pivoted friction loss and vibration noise, and then promote compressor operation's stationarity and reliability, promote compressor operating performance.

In one embodiment, referring to fig. 2 and 3, a ring platform 131 is disposed on one side of the crank 13, the ring platform 131 is disposed on one side of the crank 13 close to the main shaft 11, the ring platform 131 is disposed around the main shaft 11, the thrust surface 132 is a side of the ring platform 131 away from the eccentric shaft 12, and the disposition of the ring platform 131 can facilitate determining a position of the thrust surface 132, improving manufacturing accuracy, and facilitating installation of the thrust bearing 22.

In an embodiment, referring to fig. 2, an annular groove 114 is formed on the main shaft 11, the annular groove 114 is disposed around the main shaft 11, the annular groove 114 is located on the main shaft 11 near the thrust surface 132, the second oil groove 113 is communicated with the annular groove 114, that is, a first end of the second oil groove 113 away from the first oil groove 111 is communicated with the annular groove 114, the thrust surface 132 may be a side wall of the annular groove 114, that is, the thrust surface 132 may be a side wall of the annular groove 114 on a side of the annular groove 114 close to the crank 13. The ring groove 114 is provided, on one hand, during manufacturing, the ring groove 114 can be a tool withdrawal groove to facilitate processing of the thrust surface 132 and improve processing accuracy, and on the other hand, the ring groove 114 can also store certain lubricating oil to facilitate supplying the lubricating oil to the thrust bearing 22 and ensure the lubricating effect of the thrust bearing 22.

In one embodiment, the absolute value of the difference between the depth of the second oil groove 113 and the depth of the ring groove 114 is less than or equal to 0.5mm, that is, when the depth of the second oil groove 113 is H1 and the depth of the ring groove 114 is H2, then-0.5 mm is less than or equal to H1-H2 is less than or equal to 0.5mm, which can ensure that the second oil groove 113 can supply oil well and is convenient for manufacturing. When the depth of the second oil groove 113 is too large, for example, the difference between the depth of the second oil groove 113 and the depth of the ring groove 114 is greater than 0.5mm, on one hand, the structural strength of the main shaft 11 is reduced, and the processing and manufacturing are inconvenient. When the depth of the second oil groove 113 is too small, for example, the difference between the depth of the second oil groove 113 and the depth of the ring groove 114 is less than-0.5 mm, the oil supply capacity of the second oil groove 113 is reduced, and the effective oil supply amount is reduced.

In one embodiment, the depth of the second oil groove 113 is equal to the depth of the ring groove 114, so that the second oil groove 113 can be directly machined when the ring groove 114 is machined, and the machining is more convenient.

In one embodiment, the main shaft 11 is provided with a first oil hole 112, the first oil hole 112 is located at one end of the first oil groove 111 close to the crank 13, and one end of the second oil groove 113 is connected to the first oil hole 112. The first oil hole 112 is arranged so that the lubricating oil pumped by the second oil groove 113 is conveyed to other positions through the first oil hole 112 to supply oil to other friction pairs, and the lubricating effect is improved. In addition, when the first oil hole 112 is provided, the second oil groove 113 can be conveniently communicated with the first oil groove 111, and if the second oil groove 113 is communicated with the first oil hole 112, the second oil groove 113 can be communicated with the first oil groove 111.

In one embodiment, the width of the end of the second oil groove 113 connected to the first oil hole 112 is smaller than or equal to the width of the first oil hole 112, that is, the width of the end of the second oil groove 113 near the first oil groove 111 is smaller than or equal to the width of the first oil hole 112, which facilitates the transmission of the lubricant pumped by the first oil hole 112 to the position of the thrust surface 132, and improves the oil supply effect.

In one embodiment, the minimum width of the second oil groove 113 is greater than or equal to 0.5mm, that is, the width of the position of the second oil groove 113 with the minimum width is also greater than or equal to 0.5mm, that is, the width of each position of the second oil groove 113 along the length direction of the second oil groove 113 is greater than or equal to 0.5mm, so that the lubricating oil can pass through the second oil groove 113 conveniently to improve the oil supply capability of the second oil groove 113. When the minimum width of the second oil groove 113 is less than 0.5mm, the resistance of the lubricating oil in the second oil groove 113 increases, which is not favorable for delivering the lubricating oil to the thrust surface 132,

in one embodiment, the first oil hole 112 is axially disposed along the radial direction of the main shaft 11 to facilitate the machining of the first oil hole 112.

Referring to fig. 3, for convenience of description, the following are defined: a line extending from the intersection of the axis 1120 of the first oil hole 112 and the axis 110 of the main shaft 11 in the radial direction of the main shaft 11 to the axis 120 of the eccentric shaft 12 is a zero line 101. The front side of the direction of rotation refers to: when the crankshaft 10 rotates, it is located at the front side of the rotation direction of the crankshaft 10, for example, A1, A2, and A3 are arranged in the rotation direction in this order, and then the direction from A1 to A3 through A2 is the rotation direction, A2 is located at the front side of the rotation direction of A1, and A3 is located at the front side of the rotation direction of A2. In one embodiment, in the rotation direction of the spindle 11: the axis 1120 of the first oil hole 112 coincides with the zero line 101 or the axis 1120 of the first oil hole 112 is located at the front side of the zero line 101, and the included angle between the axis 1120 of the first oil hole 112 and the zero line 101 is a, and a is greater than or equal to 0 degrees and less than or equal to 120 degrees, so that the good structural strength of the main shaft 11 can be ensured.

Referring to fig. 3, when the crankshaft 10 rotates, the first oil hole 112 is located at the front side of the zero line 101 along the rotation direction of the crankshaft 10 when the crankshaft 10 rotates clockwise, as shown by the arrow N in fig. 3.

Referring to fig. 4 and 5, when the crankshaft 10 rotates, and the crankshaft 10 rotates counterclockwise as shown by arrow M in fig. 5, the first oil hole 112 is located at the front side of the zero line 101 along the rotation direction of the crankshaft 10, so as to ensure good structural strength of the main shaft 11.

When the crankshaft 10 rotates, the motor drives the main shaft 11 to rotate, so as to drive the eccentric shaft 12 to rotate through the crank 13, and the eccentric shaft 12 drives the load to operate, so that the stress on one end of the main shaft 11, which is close to the eccentric shaft 12, is mainly located at the rear side of the zero line 101 along the rotation direction of the main shaft 11, the axis 1120 of the first oil hole 112 is overlapped with the zero line 101 or the axis 1120 of the first oil hole 112 is located at the front side of the zero line 101, the included angle between the axis 1120 of the first oil hole 112 and the zero line 101 is in the range of 0-120 degrees, the first oil hole 112 can be located in the area of the main shaft 11 with smaller stress, and the good structural strength of the main shaft 11 is ensured.

In one embodiment, referring to fig. 2 and 3, the first oil groove 111 is a spiral groove having a direction opposite to a rotation direction of the main shaft 11, so that the lubricating oil can be pumped through the spiral groove when the crankshaft 10 rotates, thereby improving oil supplying capability.

The spiral direction of the spiral groove is opposite to the rotation direction of the main shaft 11, which means that when the crankshaft 10 rotates clockwise, the spiral direction of the spiral groove is a right-hand spiral, and as viewed in fig. 3, the spiral direction of the spiral groove is a counterclockwise direction.

In one embodiment, referring to fig. 4 and 5, the first oil groove 111 is a spiral groove having a direction opposite to a rotation direction of the main shaft 11 so that the lubricating oil is pumped through the spiral groove when the crankshaft 10 rotates, thereby improving oil supplying capability.

The spiral direction of the spiral groove is opposite to the rotation direction of the main shaft 11, which means that when the crankshaft 10 rotates counterclockwise, the spiral direction of the spiral groove is a left-hand spiral, and as viewed in fig. 5, the spiral direction of the spiral groove is a clockwise direction.

In one embodiment, referring to fig. 2, the second oil groove 113 is a straight groove, and the length direction of the second oil groove 113 is arranged along the axial direction of the main shaft 11 to facilitate processing.

In one embodiment, referring to fig. 2, the width of the second oil groove 113 is set to be equal along the length direction thereof, that is, the width of the second oil groove 113 is set to be equal from the first oil groove 111 to the thrust surface 132, so as to facilitate the processing.

In one embodiment, referring to fig. 6, the second oil groove 113 is a chute, and the length direction of the second oil groove 113 is inclined to the axial direction of the main shaft 11.

In one embodiment, referring to fig. 6, when the second oil groove 113 is a tapered groove and the first oil groove 111 is a spiral groove, the second oil groove 113 inclines from the first oil groove 111 to the thrust surface 132 along the spiral direction of the first oil groove 111, so that when the crankshaft 10 rotates, the lubricating oil can be pumped to the thrust surface 132 through the second oil groove 113, and the oil supply capacity can be improved. In this embodiment, the rotation direction of first oil groove 111 is a right-handed screw, and accordingly, second oil groove 113 is a thrust surface 132 extending obliquely from first oil groove 111 along the rotation direction of the right-handed screw.

In one embodiment, referring to fig. 7, when the second oil groove 113 is a tapered groove and the first oil groove 111 is a spiral groove, the spiral direction of the first oil groove 111 is a left-hand spiral, and correspondingly, the second oil groove 113 extends from the first oil groove 111 along the spiral direction of the left-hand spiral to form the thrust surface 132.

It will be appreciated that the second oil groove 113 may also be provided with a spiral groove, the spiral direction of the spiral groove is opposite to the rotation direction of the main shaft 11, so as to improve the capability of the second oil groove 113 to pump lubricating oil to the thrust surface 132.

It can be understood that, when the first oil groove 111 and the second oil groove 113 are both spiral grooves, the spiral directions of the first oil groove 111 and the second oil groove 113 are the same, so that the lubricating oil pumped by the first oil groove 111 can enter the second oil groove 113 more smoothly and is pumped to the thrust surface 132, thereby improving the oil supply capability.

In an embodiment, referring to fig. 8, the width of the second oil groove 113 is gradually changed from the first oil groove 111 to the thrust surface 132, that is, the width of the second oil groove 113 is gradually changed from the first oil groove 111 to the thrust surface 132, in this embodiment, the width of the second oil groove 113 is gradually increased from the first oil groove 111 to the thrust surface 132, so that the lubricating oil entering the second oil groove 113 can flow to the thrust surface 132 more smoothly, and particularly after the ring groove 114 is disposed, the lubricating oil entering the second oil groove 113 can enter the ring groove 114 conveniently.

In one embodiment, referring to fig. 9, the width of the second oil groove 113 gradually decreases from the first oil groove 111 to the thrust surface 132, so that the lubricating oil pumped by the first oil groove 111 enters the second oil groove 113, and the speed of the lubricating oil in the second oil groove 113 flowing into the ring groove 114 can be increased to better supply the lubricating oil to the thrust bearing 22. It is understood that the direction from the first oil groove 111 to the thrust surface 132: the width of the second oil groove 113 may be set to be smaller and then larger. Of course, the direction from the first oil groove 111 to the thrust surface 132: the width of the second oil groove 113 may be set to be first increased and then decreased

In an embodiment, referring to fig. 10, the number of the first oil grooves 111 is two, the two first oil grooves 111 are both spiral grooves, the spiral directions of the two first oil grooves 111 are opposite, the number of the second oil grooves 113 is two, the second oil grooves 113 correspond to the first oil grooves 111 one by one, and one ends of the second oil grooves 113 are communicated with the corresponding first oil grooves 111. Thus, when the crankshaft 10 rotates in a forward direction (i.e., clockwise rotation) or a reverse direction (i.e., counterclockwise rotation), the first oil groove 111 pumps the lubricating oil and supplies the lubricating oil to the thrust surface 132 through the corresponding second oil groove 113.

As shown in fig. 10, the first oil groove 111 includes a first spiral groove 1111 that is a right-hand spiral and a second spiral groove 1112 that is a left-hand spiral, and the two second oil grooves 113 are divided into a first oil groove 1131 and a second oil groove 1132, one end of the first oil groove 1131 is connected to the first spiral groove 1111, the other end of the first oil groove 1131 is extended to the thrust surface 132, one end of the second oil groove 113 is connected to the second oil groove 1112, and the other end of the second oil groove 1132 is extended to the thrust surface 132, so that when the crankshaft 10 rotates clockwise, the first oil groove 1111 pumps up the lubricant and supplies the lubricant in the direction of the thrust surface 132 through the first oil groove 1131. When the crankshaft 10 rotates counterclockwise, the second spiral groove 1112 pumps the lubricating oil and supplies the oil to the thrust surface 132 through the second sub oil groove 1132. Thereby, the lubricating oil can be supplied both in the forward rotation and in the reverse rotation of the crankshaft 10.

In one embodiment, an oil suction cavity 115 is formed at an end of the main shaft 11 away from the crank 13, the two first oil grooves 111 are respectively connected to the oil suction cavity 115 through the second oil holes 116, for example, the two second oil holes 116 are respectively a first oil hole 1161 and a second oil hole 1162, the first spiral groove 1111 is connected to the oil suction cavity 115 through the first oil hole 1161, and the second spiral groove 1112 is connected to the oil suction cavity 115 through the second oil hole 1162, so that when the crankshaft 10 rotates clockwise, the lubricating oil can be sucked through the oil suction cavity 115 and then enter the first spiral groove 1111 through the first oil hole 1161. When the crankshaft 10 rotates counterclockwise, the lubricating oil can be sucked through the oil suction chamber 115 and then enter the second spiral groove 1112 through the second oil hole 1162.

In one embodiment, two first oil holes 112 are provided and are connected to the two second oil grooves 113, for example, the first oil hole 112 includes a first oil dividing hole 1121 and a second oil dividing hole 1122, the first oil dividing hole 1121 is connected to the first spiral groove 1111, and the second oil dividing hole 1122 is connected to the second spiral groove 1112, so that oil is supplied to the first oil dividing hole 1121 through the first spiral groove 1111 and oil is supplied to the second oil dividing hole 1122 through the second spiral groove 1112.

In one embodiment, the eccentric shaft 12 is provided with an oil passage 121, and the oil passage 121 is connected to the first oil hole 112, so that the lubricating oil of the first oil groove 111 can enter the oil passage 121 through the first oil hole 112 to supply the lubricating oil to the eccentric shaft 12, thereby lubricating the friction pair at the eccentric shaft 12. In this embodiment, two first oil holes 112 are provided, and the oil passage 121 is connected to both the first oil holes, and if the first oil hole 112 includes a first oil dividing hole 1121 and a second oil dividing hole 1122, the oil passage 121 is communicated with both the first oil dividing hole 1121 and the second oil dividing hole 1122, so that when the crankshaft 10 rotates clockwise, the lubricating oil can enter the oil passage 121 through the first oil dividing hole 1121. When the crankshaft 10 rotates counterclockwise, the lubricating oil can enter the oil passage 121 through the second oil dividing hole 1122. It is understood that the oil passages 121 may also be provided in two one-to-one correspondence with the first oil holes 112, respectively communicating with the corresponding first oil holes 112.

In one embodiment, referring to fig. 11, the first oil groove 111 may also be a straight groove, and the length direction of the straight groove is arranged along the axial direction of the main shaft 11. The straight groove is used, the structure is simple, and the manufacture is convenient.

Referring to fig. 1 and 2, in the crankshaft 10 according to the embodiment of the present disclosure, the second oil groove 113 is disposed on the crankshaft 10, so that the lubricating oil pumped by the first oil groove 111 can be supplied to the thrust surface 132 through the second oil groove 113, so as to ensure good lubrication to the thrust bearing 22 installed at the thrust surface 132, thereby improving an oil path on the crankshaft 10, improving a lubricating effect of the crankshaft 10 in operation, better ensuring smooth rotation of the crankshaft 10, reducing vibration and noise of the crankshaft 10 in rotation, reducing friction loss of the crankshaft 10 in rotation, and improving performance and service life of a compressor using the crankshaft 10.

Referring to fig. 1, an embodiment of the present application further provides a compressor, which includes a crankcase 21, a thrust bearing 22, and the crankshaft 10 according to any of the above embodiments, wherein the crankcase 21 is sleeved on the main shaft 11, the thrust bearing 22 is sleeved on the main shaft 11, one end of the thrust bearing 22 is connected to the crankcase 21, and the other end of the thrust bearing 22 is attached to the thrust surface 132. The thrust bearing 22 is provided so that the crankshaft 10 can smoothly and flexibly rotate in the crankcase 21. Moreover, the compressor uses the crankshaft 10 of any embodiment, so that the friction loss between the crankcase 21 and the main shaft 11 can be reduced, the friction loss of the thrust bearing 22 in rotation can be reduced, the running stability and reliability of the compressor are improved, and the running performance of the compressor is improved. The compressor also has the technical effects of the crankshaft 10 of the above embodiment, and the description is omitted here.

In one embodiment, the compressor further comprises a connecting rod 24 and a piston 23, a cylinder block 211 is provided on the crank case 21, one end of the connecting rod 24 is connected to the eccentric shaft 12, the other end of the connecting rod 24 is connected to the piston 23 through a piston pin 25, the piston 23 is slidably disposed in the cylinder block 211, such that when the crank shaft 10 rotates, the eccentric shaft 12 drives the connecting rod 24 to reciprocate, so as to drive the piston 23 to reciprocate in the cylinder block 211, so as to compress gas, thereby forming the compressor into a reciprocating piston compressor.

In one embodiment, spring pins 26 are also provided on the cylinder block 211 to limit the travel of the piston 23 toward the end of the crankshaft 10 by the spring pins 26.

The embodiment of the application also provides a refrigerating and heating device, which comprises the compressor in any one of the embodiments. This refrigeration and heating equipment has used above-mentioned compressor, and the operation is more stable, and the noise is littleer, and the life-span is high to still have the technological effect of the compressor of above-mentioned embodiment, no longer describe herein.

The cooling and heating device in the embodiment of the application can be a device only used for cooling, such as a refrigerator, an air conditioner, a device only used for heating, and a device both used for cooling and heating.

The above description is intended only to serve as an alternative embodiment of the present application, and should not be taken as limiting the present application, and any modifications, equivalents, improvements, etc. made within the spirit and principle of the present application should be included in the scope of the present application.

Claims (13)

1. The utility model provides a crankshaft, includes the crank, locate the main shaft of crank one side and locate the eccentric shaft of crank opposite side, be equipped with the first oil groove that is used for pump sending lubricating oil on the outer peripheral face of main shaft, its characterized in that: the crank is close to one side of main shaft is equipped with the thrust surface that is used for fixing a position footstep bearing, the second oil groove has still been seted up on the main shaft, the one end of second oil groove with first oil groove intercommunication, the other end of second oil groove extends to the thrust surface.

2. The crankshaft of claim 1, wherein: the main shaft is provided with an annular groove in an encircling mode, one side wall of the annular groove is the thrust surface, and the other end of the second oil groove is communicated with the annular groove.

3. The crankshaft of claim 2, wherein: the absolute value of the difference between the depth of the second oil groove and the depth of the ring groove is less than or equal to 0.5mm.

4. The crankshaft of claim 1, wherein: the main shaft is provided with a first oil hole, the first oil hole is located at one end, close to the crank, of the first oil groove, and one end of the second oil groove is connected with the first oil hole.

5. The crankshaft of claim 4, wherein: the width of the end of the second oil groove connected with the first oil hole is less than or equal to the width of the first oil hole.

6. The crankshaft of claim 4 wherein: the axial direction of the first oil hole is arranged along the radial direction of the main shaft; in the rotation direction of the spindle: the axis of the first oil hole is coincident with or positioned on the front side of a zero line, the included angle between the axis of the first oil hole and the zero line is a, a is more than or equal to 0 degree and less than or equal to 120 degrees, and the zero line is a straight line which points to the axis of the eccentric shaft from the intersection point of the axis of the first oil hole and the axis of the main shaft along the radial direction of the main shaft.

7. The crankshaft of any of claims 1-6, wherein: the minimum width of the second oil groove is greater than or equal to 0.5mm.

8. The crankshaft of any one of claims 1 to 6, wherein: the second oil groove is a straight groove which extends along the axial direction of the main shaft in the length direction; or the second oil groove is an inclined groove with the length direction inclined to the axial direction of the main shaft; or the second oil groove is a spiral groove, and the rotation direction of the spiral groove is opposite to the rotation direction of the main shaft.

9. The crankshaft of any one of claims 1 to 6, wherein: the width of the second oil groove is equal to the width of the first oil groove in the direction from the first oil groove to the thrust surface; or the width of the second oil groove is gradually changed from the first oil groove to the thrust surface.

10. The crankshaft of any one of claims 1 to 6, wherein: the first oil groove is a spiral groove, and the rotating direction of the spiral groove is opposite to the rotating direction of the main shaft; or the first oil groove is a straight groove arranged along the axial direction of the main shaft in the length direction.

11. The crankshaft of any one of claims 1 to 6, wherein: the first oil groove is two spiral grooves with opposite rotation directions, the number of the second oil grooves is two, and the second oil grooves are communicated with the first oil grooves in a one-to-one correspondence mode.

12. A compressor comprising a crankcase and a thrust bearing, characterized in that: the crankshaft of any of claims 1-11, wherein the crankcase is sleeved on the main shaft, the thrust bearing is sleeved on the main shaft, one end of the thrust bearing is connected with the crankcase, and the other end of the thrust bearing is attached to the thrust surface.

13. A refrigerating and heating apparatus characterized by: comprising a compressor as claimed in claim 12.

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