CN215927786U

CN215927786U - Crankshaft, compressor and refrigeration and heating equipment

Info

Publication number: CN215927786U
Application number: CN202122482991.XU
Authority: CN
Inventors: 何武鹏
Original assignee: Guangdong Midea Environmental Technologies Co Ltd
Current assignee: Guangdong Midea Environmental Technologies Co Ltd
Priority date: 2021-10-14
Filing date: 2021-10-14
Publication date: 2022-03-01
Anticipated expiration: 2031-10-14

Abstract

The utility model belongs to the technical field of compressors, and particularly relates to a crankshaft, a compressor and refrigeration and heating equipment. Wherein, the bent axle has the bearing cooperation section that supplies the bearing adaptation to cup joint, the inside main oil groove that is equipped with of bent axle, bearing cooperation section is equipped with the oil outlet with main oil groove intercommunication, the both ends of bearing cooperation section are formed with first round platform portion and second round platform portion respectively, the lateral wall of first round platform portion is from the lateral wall of bearing cooperation section to the axis slope of bent axle, the lateral wall of second round platform portion is from the lateral wall of bearing cooperation section to the axis slope of bent axle, the oil outlet is located between two round platform portions. When the crankshaft rotates and inclines, the side surfaces of the two circular truncated cone parts are in surface contact with the inner ring of the bearing, the surface contact increases the action area of extrusion stress, the extrusion stress can be effectively dispersed, and the abrasion of the crankshaft and the bearing caused by the fact that the stress is concentrated at certain positions for a long time is avoided; meanwhile, the surface contact is more beneficial to the formation of a lubricating oil film, and the lubricating effect at the contact position of the crankshaft and the bearing is better.

Description

Crankshaft, compressor and refrigeration and heating equipment

Technical Field

The utility model belongs to the technical field of compressors, and particularly relates to a crankshaft, a compressor and refrigeration and heating equipment.

Background

In the related art, for a compressor, a certain radial gap is generally required to be provided between a crankshaft and a bearing sleeved on the crankshaft to ensure that a lubricating oil film can be formed between the crankshaft and the bearing and ensure the degree of lubrication between the crankshaft and the bearing during operation. Therefore, due to the gap between the crankshaft and the bearing, the crankshaft rotates and inclines when being acted by radial force, so that the crankshaft presses the bearing at the position where the radial force is the largest, the crankshaft and the bearing form point contact, the largest concentrated stress is generated at the contact point, the crankshaft and the bearing form hard pressing at the contact point, and the bearing and the local load of the crankshaft are excessively concentrated, so that the crankshaft and the bearing are abraded. Particularly, for the variable frequency compressor, when the compressor runs at a high rotating speed, under the influence of the supply amount of lubricating oil, an oil film is more difficult to form at the part extruded by the crankshaft and the bearing, and the abrasion is abnormal and serious under a high-frequency working condition, so that the service life of the crankshaft and the bearing of the variable frequency compressor is shortened, and the maintenance frequency of the compressor is increased.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model mainly aims to provide a crankshaft, a compressor and refrigeration and heating equipment, and aims to solve the technical problem that in the prior art, the crankshaft and a bearing are abraded due to the fact that effective lubrication cannot be achieved between the crankshaft and the bearing due to the fact that the crankshaft of the compressor is inclined and the bearing is extruded.

The technical scheme adopted by the utility model is as follows: the utility model provides a crankshaft, bearing cooperation section that supplies the bearing adaptation to cup joint has, the inside of bent axle is equipped with main oil groove, bearing cooperation section is equipped with the oil outlet that communicates mutually with main oil groove, the both ends of bearing cooperation section are formed with first round platform portion and second round platform portion respectively, an extending direction along the bent axle axis, the lateral wall from the bearing cooperation section of first round platform portion inclines to the axis of bent axle, another extending direction along the bent axle axis, the lateral wall from the bearing cooperation section of second round platform portion inclines to the axis of bent axle, the oil outlet is located between first round platform portion and the second round platform portion.

In some embodiments, the first circular truncated cone portion has a length of 5mm to 10mm in an axial direction of the crankshaft.

In some embodiments, the second circular table portion has a length of 5mm to 10mm in an axial direction of the crankshaft.

In some embodiments, the angle θ between the side of the first dome portion and the axis of the crankshaft₁The maximum inclination angle alpha when the crankshaft rotates satisfies the following conditions: tan theta₁A, tan α, a ranging from 0.8 to 1.2;

wherein tan α ═ Φ₁-Φ₂) L, where phi₁Is the inner diameter of a bearing sleeved on the matching section of the bearing₂Is the outer diameter of the bearing mating section and L is the axial length of the bearing.

In some embodiments, the angle θ between the side of the second dome portion and the axis of the crankshaft₂The maximum inclination angle alpha when the crankshaft rotates satisfies the following conditions: tan theta₂B · tan α, with B ranging from 0.8 to 1.2;

In some embodiments, a side surface of the first circular truncated cone portion is inclined toward an axis of the crankshaft by a width of 0.01mm to 0.03mm in a radial direction of the crankshaft.

In some embodiments, a side surface of the second circular truncated cone portion is inclined toward an axis of the crankshaft by a width of 0.01mm to 0.03mm in a radial direction of the crankshaft.

In some embodiments, the side wall of the bearing fitting section is provided with a side oil groove extending in the axial direction of the crankshaft, and the oil outlet hole is provided in the side oil groove and communicates the main oil groove and the side oil groove.

In some embodiments, the crankshaft includes a secondary shaft section, a primary shaft section, and an eccentric section, each forming a bearing mating section.

One or more technical solutions in the crankshaft provided by the embodiment of the present invention have at least one of the following technical effects: the utility model provides a bent axle sets up first round platform portion and second round platform portion through the both ends at bearing cooperation section, the extending direction of the side of first round platform portion along bent axle axis one end inclines towards the axis of bent axle, the extending direction of the side of second round platform portion along the bent axle axis other end inclines towards the axis of bent axle, when the bearing cup joints in the bearing cooperation section of bent axle, the side of first round platform portion and the side of second round platform portion are the inclined plane of relative bearing inner race slope. Therefore, when the crankshaft rotates to incline, the side surfaces of the first circular table part and the second circular table part are in surface contact with the bearing inner ring, and compared with point contact, the surface contact increases the action area of extrusion stress, so that the extrusion stress can be dispersed, and the crankshaft and the bearing are prevented from being abraded due to the fact that the stress is concentrated at certain positions for a long time; meanwhile, the surface contact is more favorable for forming a lubricating oil film, and the lubricating effect at the contact position of the crankshaft and the bearing is better, so that the abrasion can be further reduced, and the service lives of the crankshaft and the bearing are effectively prolonged.

The other technical scheme of the utility model is as follows: a compressor is provided, comprising the crankshaft.

One or more technical solutions in the compressor provided by the embodiment of the present invention have at least one of the following technical effects: the utility model provides a compressor, through using foretell bent axle, the bent axle and the bearing wearing and tearing that lead to by the bent axle slope reduce, bent axle and bearing life extension, the compressor overhauls the frequency and reduces, moves more reliable and more stable.

The utility model also adopts the technical scheme that: a refrigerating and heating device is provided, which comprises the compressor.

One or more technical solutions in the refrigeration and heating equipment provided by the embodiment of the present invention at least have one of the following technical effects: the application discloses refrigeration and heating equipment, through using foretell compressor, because the operating stability and the reliability of compressor improve, the compressor overhauls the frequency and reduces for the holistic maintenance frequency of equipment reduces, and life extension, thereby the user's of satisfying actual use demand that can be better, user use experience can promote.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.

FIG. 1 is a cut-away view of a crankshaft provided in accordance with an embodiment of the present invention;

FIG. 2 is a cut-away view of a compressor using the crankshaft shown in FIG. 1;

FIG. 3 is a schematic illustration of a portion of the crankshaft of FIG. 1;

FIG. 4 is an enlarged schematic view at A in FIG. 3;

FIG. 5 is an enlarged schematic view at B in FIG. 3;

fig. 6 is a schematic view illustrating a state in which the rotation of the crankshaft is inclined during the operation of the compressor shown in fig. 2.

In the figures, the various figures are mainly marked:

10. a crankshaft; 11. a bearing mating section; 111. a first circular table portion; 112. a second circular table portion; 12. a main oil sump; 13. an oil outlet hole; 14. a main shaft section; 15. a secondary shaft section; 16. an eccentric section; 17. an oil suction pipe; 18. a side oil groove;

21. a main frame bearing; 22. a sub-frame bearing; 23. a movable disc bearing;

30. a housing; 31. an oil sump;

40. a main frame;

50. a sub-chassis;

60. a compression assembly; 61. a movable scroll; 62. a fixed scroll;

70. an electric motor.

Detailed Description

In order to make the technical problems, technical solutions and advantageous effects to be solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to fig. 1 to 6 and the embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the utility model and are not intended to limit the utility model.

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.

It will be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like, as used herein, refer to an orientation or positional relationship indicated in the drawings, which is solely for the purpose of facilitating the description and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and is therefore not to be construed as limiting the utility model.

Furthermore, 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. The features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.

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 utility model. The appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," or the like in various places in the specification are not necessarily all referring to the same embodiment, but rather "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.

In the related art, as shown in fig. 2, a conventional compressor generally includes a casing 30, a motor 70, a main frame 40, a sub-frame 50, a compression assembly 60, a crankshaft 10, an oil pump (not shown), and the like, where an oil sump 31 storing lubricating oil is disposed at a bottom of the casing 30, the compression assembly 60 mainly includes a movable scroll 61 and a fixed scroll 62, the crankshaft 10 includes a main shaft portion, a sub-shaft portion, and an eccentric portion, the main shaft portion is connected to the main frame 40 and supported by the main frame 40, the sub-bearing is connected to the sub-frame 50 and supported by the sub-frame 50, the eccentric portion is connected to the movable scroll 61, and the motor 70 drives the crankshaft 10 to rotate so as to drive the movable scroll 61 to rotate under a limit of an oldham ring (not shown). A lubricating oil supply system (oil supply system for short) is generally disposed inside the crankshaft 10, the oil pump is installed at the bottom of the crankshaft 10, an oil outlet of the oil pump is communicated with the oil supply system inside the crankshaft 10, when the compressor is in operation, the crankshaft 10 rotates, and at this time, the lubricating oil at the bottom of the shell 30 can be delivered through the oil supply system and guided to each friction pair of the compressor for lubrication by utilizing the centrifugal force generated when the crankshaft 10 rotates and the pumping pressure of the oil pump.

When the compressor is in use, during the rotation of the crankshaft 10, the crankshaft 10 is subjected to a radial force, generally, in order to avoid abnormal friction between the crankshaft 10 and the supporting portions of the main frame 40, the auxiliary frame 50 and the orbiting scroll 61, sliding bearings are generally required to be arranged on the inner walls of the supporting portions of the main frame 40, the auxiliary frame 50 and the orbiting scroll 61, and a bearing is arranged to be in clearance fit with the crankshaft 10, so that lubricating oil can enter to form a lubricating oil film between the bearing and the crankshaft 10. In this manner, it is generally necessary to provide a certain radial gap between the crankshaft 10 and the bearing fitted to the crankshaft 10 to ensure that a lubricating oil film can be formed between the crankshaft 10 and the bearing and to ensure the degree of lubrication between the crankshaft 10 and the bearing during operation.

However, in actual use, due to the gap between the crankshaft 10 and the bearing, when the crankshaft 10 rotates and is acted by a radial force, the crankshaft 10 tilts when being acted by the radial force, so that the crankshaft 10 presses the bearing at a position where the radial force is the largest, the crankshaft 10 and the bearing form a point contact, and the largest concentrated stress is generated at the contact point, so that the crankshaft 10 and the bearing form a hard pressing at the contact point, and the local load of the bearing and the crankshaft 10 is too concentrated, so that the crankshaft 10 and the bearing are worn. Particularly for the frequency conversion compressor, when the compressor runs at a high rotating speed, under the influence of the supply amount of lubricating oil, an oil film is more difficult to form at the part extruded by the crankshaft 10 and the bearing, and the abrasion is abnormal and serious under a high-frequency working condition, so that the service life of the crankshaft 10 and the bearing of the frequency conversion compressor is shortened, and the maintenance frequency of the compressor is increased.

Based on the above, the present invention provides a compressor, which optimizes the design of the crankshaft 10 of the compressor, and arranges the bearing fitting section 11 at the position of the crankshaft 10 for the bearing to be sleeved, thereby improving the extrusion contact state between the crankshaft 10 and the bearing when the crankshaft is inclined, dispersing the stress acting on the crankshaft 10 and the bearing in the inclined state, and effectively reducing the abrasion of the crankshaft 10 and the bearing. The crankshaft 10 of the present invention will be described in detail with reference to specific embodiments.

Referring to fig. 1 and 2, in which fig. 1 is a sectional view of a crankshaft according to an embodiment of the present invention, fig. 2 is a sectional view of a compressor using the crankshaft shown in fig. 1, and a partial structure is a perspective structure in order to show a flow path of a lubricating oil.

Specifically, as shown in fig. 1 and fig. 2, the embodiment of the present invention provides a crankshaft 10, the crankshaft 10 has a bearing fitting section 11 for bearing fitting, specifically, for the crankshaft 10 used with a compressor, the crankshaft 10 needs to be connected with a main frame 40, an auxiliary frame 50 and a movable scroll 61 of the compressor, that is, when the crankshaft 10 is actually assembled with the compressor, the bearings matched therewith generally include a main frame bearing 21, an auxiliary frame bearing 22 and a movable scroll bearing 23, and correspondingly, the crankshaft 10 generally includes a main shaft section 14 (as shown by a dotted line L in fig. 1)₁To L₂Position in between), the secondary shaft section 15 (shown as dashed line L in fig. 1)₅To L₆Position in between) and an eccentric section 16 (shown as dashed line L in fig. 1)₃To L₄Position in between), wherein the host computerThe frame bearing 21 is disposed on the main frame 40 of the compressor and sleeved on the main shaft section 14 of the crankshaft 10, the auxiliary frame bearing 22 is disposed on the auxiliary frame 50 of the compressor and sleeved on the auxiliary shaft section 15 of the crankshaft 10, and the movable disc bearing 23 is disposed on the movable scroll 61 of the compressor and sleeved on the eccentric section 16 of the crankshaft 10, so as to ensure that the crankshaft 10 can stably support the main frame 40 and the auxiliary frame 50 to drive the movable scroll 61 to rotate, thereby compressing the refrigerant.

Since the crankshaft 10 is worn at all positions contacting the bearings due to the inclination of the crankshaft 10, in the present embodiment, the main shaft section 14, the auxiliary shaft section 15, and the eccentric section 16 of the crankshaft 10 respectively form the bearing fitting sections 11, and the main frame bearing 21, the auxiliary frame bearing 22, and the movable plate bearing 23 are respectively sleeved on the corresponding bearing fitting sections 11. As follows, the bearing fitting section 11 will be described in detail by taking the bearing fitting section 11 formed in the main shaft section 14 as an example.

Referring to fig. 1 to 5, fig. 3 is a partial structural schematic view of the crankshaft 10 shown in fig. 1, fig. 4 is an enlarged schematic view of a portion a in fig. 3, and fig. 5 is an enlarged schematic view of a portion B in fig. 3.

In the present embodiment, as shown in fig. 1, 2 and 3, a main oil groove 12 is provided inside the crankshaft 10, the main oil groove 12 penetrates the crankshaft 10 along the axial direction of the crankshaft 10 and communicates with an oil sump 31 at the bottom of the shell 30 of the compressor, for example, an oil suction pipe 17 is provided at the bottom end of the crankshaft 10 near the oil sump 31, and the main oil groove 12 communicates with the oil sump 31 through the oil suction pipe 17. The bearing fitting section 11 is provided with an oil outlet 13, the oil outlet 13 is communicated with the main oil groove 12 to lead out the lubricating oil in the main oil groove 12, for example, when the main frame bearing 21 is sleeved on the bearing fitting section 11 (i.e. the main shaft section 14) of the crankshaft 10, the led-out lubricating oil enters a gap between the main frame bearing 21 and the bearing fitting section 11, and forms a lubricating oil film to lubricate the main frame bearing 21 and the main shaft section 14 of the crankshaft 10. In an exemplary embodiment, as shown in fig. 1, 2 and 3, the oil outlet hole 13 may penetrate the main oil groove 12 in a radial direction of the crankshaft 10.

In the present embodiment, as shown in fig. 3, 4 and 5, a first circular truncated cone portion 111 and a second circular truncated cone portion 112 are respectively formed at both ends of the bearing fitting section 11, the oil outlet hole 13 is provided between the first circular truncated cone portion 111 and the second circular truncated cone portion 112 so as to lead out the lubricating oil in the main oil tank 12 to between the first circular truncated cone portion 111 and the second circular truncated cone portion 112, and the lubricating oil flows to the side of the first circular truncated cone portion 111 and the side of the second circular truncated cone portion 112 under the action of gravity and centrifugal force, thereby forming effective lubrication.

Specifically, a side oil groove 18 may be provided at a side wall of the bearing fitting section 11, the side oil groove 18 extending in an axial direction of the crankshaft 10, the oil outlet hole 13 being provided in the side oil groove 18, the oil outlet hole 13 communicating the main oil groove 12 and the side oil groove 18, and the side oil groove 18 extending from a bottom surface of the first circular table portion 111 to a bottom surface of the second circular table portion 112, so that the lubricating oil flowing out of the oil outlet hole 13 can flow to a side surface of the first circular table portion 111 and a side surface of the second circular table portion 112 through the side oil groove 18. The side oil grooves 18 may be straight oil grooves parallel to the axis of the crankshaft 10 (as shown by the dotted line R in fig. 1 and 2) or inclined with respect to the axis of the crankshaft 10, or may be spiral oil grooves.

Further, along an extension direction of the axis of the crankshaft 10 (as indicated by an arrow F in FIG. 3)₁The direction shown), the side surface of the first boss portion 111 is inclined from the side wall of the bearing fitting section 11 toward the axis of the crankshaft 10 as shown in fig. 4, in another extending direction of the axis of the crankshaft 10 (arrow F in fig. 3)₂The direction shown), the side of the second boss portion 112 is inclined from the side wall of the bearing fitting section 11 toward the axis of the crankshaft 10, as shown in fig. 5.

When the bearing is sleeved on the bearing fitting section 11 of the crankshaft 10, for example, when the main frame bearing 21 is sleeved on the main shaft section 14 of the crankshaft 10, as shown in fig. 2, the side surface of the first circular platform portion 111 and the side surface of the second circular platform portion 112 are both inclined surfaces inclined with respect to the inner ring of the main frame bearing 21 and along an extending direction of the axis of the crankshaft 10 (as shown by an arrow F in fig. 3)₁The direction shown), the distance between the side surface of the first circular truncated cone portion 111 and the bearing inner race is gradually increased, and the other extension direction (the arrow F in fig. 3) of the axis of the crankshaft 10 is taken₂In the illustrated direction), the interval between the side surface of the second circular truncated cone portion 112 and the inner ring of the bearing is gradually increased, and when the crankshaft 10 is rotated to be inclined, the side surface of the first circular truncated cone portion 111 and the side surface of the second circular truncated cone portion 112 are brought into surface contact with the inner ring of the main frame bearing 21 from the outsideAnd the compression stress generated by compressing the bearing when the crankshaft 10 is tilted can be effectively dispersed.

According to the crankshaft 10 provided by the embodiment of the utility model, the first circular truncated cone part 111 and the second circular truncated cone part 112 are arranged at the two ends of the bearing matching section 11, when the crankshaft 10 rotates and inclines, the side surfaces of the first circular truncated cone part 111 and the second circular truncated cone part 112 are in surface contact with the inner ring of the bearing, compared with point contact, the surface contact increases the action area of extrusion stress, so that the extrusion stress can be dispersed, and the crankshaft 10 and the bearing are prevented from being abraded due to the fact that the stress is concentrated at certain positions for a long time; meanwhile, the surface contact is more favorable for forming a lubricating oil film, and the lubricating effect at the contact position of the crankshaft 10 and the bearing is better, so that the abrasion can be further reduced, and the service lives of the crankshaft 10 and the bearing are effectively prolonged.

In another embodiment of the present invention, as shown in fig. 1, 3 and 4, the length of the first circular truncated cone portion 111 (i.e., l in fig. 4) in the axial direction of the crankshaft 10₁The dimension shown) is 5mm to 10mm to ensure that the contact area with the inner race of the bearing is sufficient to effectively disperse the generated compressive stress when the crankshaft 10 is tilted.

Specifically, since the axial length of the bearing suitable for the compressor is generally about 10cm at the maximum, when the axial length of the bearing is 10cm, the length l of the first boss portion 111 is set to correspond thereto₁10mm, and when a bearing having a reduced axial length is used, the length of the first boss portion 111 is set to be correspondingly reduced, thereby ensuring a reliable coupling between the bearing and the bearing fitting section 11 of the crankshaft 10 while ensuring a surface contact area.

In some embodiments, the length l of the first circular truncated cone portion 111₁May be any value such as 5mm, 6mm, 7mm, 8mm, 9mm, or 10 mm.

Further, in the present embodiment, as shown in fig. 1, 3 and 5, similarly to the above-described first round table portion 111, the length of the second round table portion 112 (as l in fig. 5) in the axial direction of the crankshaft 10₂The dimension shown) is 5mm to 10mm to ensure that the contact area with the inner race of the bearing is sufficient to effectively disperse the generated compressive stress when the crankshaft 10 is tilted.

Specifically, since the axial length of the bearing suitable for the compressor is generally about 10cm at the maximum, when the axial length of the bearing is 10cm, the length l of the second boss portion 112 is set to correspond thereto₂10mm, and when a bearing having a reduced axial length is used, the length of the second boss portion 112 is set to be correspondingly reduced, thereby ensuring a reliable coupling between the bearing and the bearing fitting section 11 of the crankshaft 10 while ensuring a surface contact area.

In some embodiments, the length l of the second circular table portion 112₂May be any value such as 5mm, 6mm, 7mm, 8mm, 9mm, or 10 mm.

In another embodiment of the present invention, as shown in fig. 3, 4 and 6, fig. 6 is a schematic view illustrating a state where the crankshaft 10 is rotated to be inclined during the operation of the compressor shown in fig. 2. In the present embodiment, the angle θ between the side surface of the first round table portion 111 and the axis of the crankshaft 10₁And the maximum inclination angle alpha when the crankshaft 10 rotates (as shown in fig. 6, the inclination angle alpha is the included angle between the axis R' of the crankshaft 10 and the vertical axis R of the compressor when the crankshaft 10 is inclined, namely the axis when the crankshaft 10 is not inclined) satisfies the following conditions: tan theta₁A, tan α, a ranging from 0.8 to 1.2; wherein tan α ═ Φ₁-Φ₂) L, where phi₁For adapting the inner diameter, phi, of a bearing journalled to the bearing fitting section 11₂Is the outer diameter of the bearing fitting section 11 and L is the axial length of the bearing adapted to be sleeved to the bearing fitting section 11.

It is understood that, in the present embodiment, the included angle between the side surface of the first circular truncated cone portion 111 and the axis of the crankshaft 10 refers to the included angle between the generatrix of the first circular truncated cone portion 111 and the axis of the crankshaft 10. Thus, the angle θ between the side surface of the first boss portion 111 and the axis of the crankshaft 10 is set₁The maximum inclination angle α with respect to the rotation of the crankshaft 10 satisfies the above relationship, and when the crankshaft 10 is inclined at the maximum angle, the side surface of the first circular truncated cone portion 111 is in parallel contact with the inner ring side wall of the bearing, and at this time, the contact area between the two is maximized, so that the compressive stress can be dispersed to the maximum extent, and the wear of the crankshaft 10 and the bearing due to the stress can be reduced.

In a particular embodiment of the present invention,an angle θ between the side surface of the first circular truncated cone portion 111 and the axis of the crankshaft 10₁The tangent of (b) may be 0.8 times, 0.85 times, 0.9 times, 0.95 times, 1.0 times, 1.1 times, 1.2 times, or the like of the tangent of the maximum inclination angle α at the time of rotation of the crankshaft 10.

Further, in the present embodiment, as shown in fig. 3, 5, and 6, similarly to the arrangement form of the first round table portion 111, the angle θ between the side surface of the second round table portion 112 and the axis of the crankshaft 10 is set₂The maximum inclination angle α with respect to the rotation of the crankshaft 10 satisfies: tan theta₂B · tan α, B ranging from 0.8 to 1.2; wherein tan α ═ Φ₁-Φ₂) L, where phi₁For adapting the inner diameter, phi, of a bearing journalled to the bearing fitting section 11₂Is the outer diameter of the bearing fitting section 11 and L is the axial length of the bearing adapted to be sleeved to the bearing fitting section 11. It is to be understood that, in the present embodiment, the included angle between the side surface of the second circular truncated cone portion 112 and the axis of the crankshaft 10 refers to the included angle between the generatrix of the second circular truncated cone portion 112 and the axis of the crankshaft 10.

Thus, the angle θ between the side surface of the second round base portion 112 and the axis of the crankshaft 10 is set₂The maximum inclination angle α with respect to the rotation of the crankshaft 10 satisfies the above relationship, and when the crankshaft 10 is inclined at the maximum angle, the side surface of the second circular truncated cone portion 112 is in parallel contact with the inner ring side wall of the bearing, and at this time, the contact area between the two is maximized, so that the compressive stress can be dispersed to the maximum extent, and the wear of the crankshaft 10 and the bearing due to the stress can be reduced.

In the embodiment, the angle θ between the side surface of the second circular truncated cone portion 112 and the axis of the crankshaft 10₂The tangent of (b) may be 0.8 times, 0.85 times, 0.9 times, 0.95 times, 1.0 times, 1.1 times, 1.2 times, or the like of the tangent of the maximum inclination angle α at the time of rotation of the crankshaft 10.

In another embodiment of the present invention, as shown in fig. 3, 4 and 6, the side surface of the first circular truncated cone portion 111 has a width (W in fig. 4) inclined toward the axis of the crankshaft 10 in the radial direction of the crankshaft 10₁The size shown) is 0.01mm to 0.03 mm. The value selected within the above-mentioned vertical range is appropriate in combination with the axial extension l of the first circular truncated cone portion 111₁Ensure thatAn angle theta between the side surface of the first circular truncated cone portion 111 and the axis of the crankshaft 10 is secured₁Satisfies the maximum inclination angle alpha with the crankshaft 10 rotating

tanθ₁＝(0.8～1.2)·tanα。

In the specific embodiment, the extension length l in the axial direction according to the first circular table portion 111₁On the premise that the above formula is satisfied, the width W of the side surface of the first circular truncated cone portion 111 inclined toward the axis of the crankshaft 10₁May be 0.01mm, 0.012mm, 0.015mm, 0.018mm, 0.02mm, 0.025mm, 0.028mm, 0.03mm or the like.

Further, in the present embodiment, as shown in fig. 3, 5 and 6, similarly to the arrangement form of the first round table portion 111, the width of the side face of the second round table portion 112 inclined toward the axis of the crankshaft 10 in the radial direction of the crankshaft 10 is (as W in fig. 5)₂The size shown) is 0.01mm to 0.03 mm. The value selected within the above-mentioned vertical range is appropriate in combination with the axial extension l of the second circular table portion 112₂An angle theta between the side surface of the second circular truncated cone portion 112 and the axis of the crankshaft 10 is ensured₂Satisfies tan theta with the maximum inclination angle alpha when the crankshaft 10 rotates₂＝(0.8～1.2)·tanα。

In the specific embodiment, the extension length l in the axial direction according to the second circular table portion 112₂On the premise that the above formula is satisfied, the width W of the side surface of the second circular truncated cone portion 112 inclined toward the axis of the crankshaft 10₂May be 0.01mm, 0.012mm, 0.015mm, 0.018mm, 0.02mm, 0.025mm, 0.028mm, 0.03mm or the like.

In the crankshaft 10 according to each of the above embodiments of the present invention, the first circular truncated cone portion 111 and the second circular truncated cone portion 112 are disposed at both ends of the bearing fitting section 11, when the crankshaft 10 rotates and tilts, the side surfaces of the first circular truncated cone portion 111 and the second circular truncated cone portion 112 form surface contact with the inner ring of the bearing, and compared with point contact, the surface contact increases the action area of the extrusion stress, so that the extrusion stress can be dispersed, and abrasion of the crankshaft 10 and the bearing due to the stress concentrated at some positions for a long time can be avoided; meanwhile, the surface contact is more favorable for forming a lubricating oil film, and the lubricating effect at the contact position of the crankshaft 10 and the bearing is better, so that the abrasion can be further reduced, and the service lives of the crankshaft 10 and the bearing are effectively prolonged.

Another embodiment of the present invention also provides a compressor, as shown in fig. 2, including the crankshaft 10 described above.

According to the compressor provided by the embodiment of the utility model, by using the crankshaft 10, the abrasion of the crankshaft 10 and the bearing caused by the inclination of the crankshaft 10 is reduced, the service lives of the crankshaft 10 and the bearing are prolonged, the maintenance frequency of the compressor is reduced, and the operation is more stable and reliable.

In addition, the compressor also has other technical effects of the crankshaft 10 provided by the above embodiments, and details are not repeated here.

Another embodiment of the present invention further provides a refrigerating and heating apparatus (not shown) including the compressor described above. It is to be understood that the cooling and heating device may be a device having only a cooling function, may be a device having only a heating function, and may also be a device having both a cooling function and a heating function, for example, in a specific embodiment, the cooling and heating device may be a refrigerator or an air conditioner, etc.

According to the refrigeration equipment provided by the embodiment of the utility model, due to the adoption of the compressor in each embodiment, the operation stability and reliability of the compressor are improved, the maintenance frequency of the compressor is reduced, the maintenance frequency of the whole equipment is reduced, the service life is prolonged, the actual use requirements of users can be better met, and the use experience of the users is improved.

In addition, the refrigerating and heating device also has other technical effects of the compressor provided by the above embodiments, and details are not repeated here.

In a specific embodiment, the refrigeration device may be a refrigerator, an air conditioner, or the like.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.

Claims

1. The utility model provides a bent axle, has the bearing cooperation section that supplies the bearing adaptation to cup joint, the inside of bent axle is equipped with main oil groove, bearing cooperation section be equipped with the oil outlet that main oil groove communicates mutually, a serial communication port, the both ends of bearing cooperation section are formed with first round platform portion and second round platform portion respectively, follow the extending direction of bent axle axis, the side of first round platform portion certainly the lateral wall of bearing cooperation section to the axis slope of bent axle follows another extending direction of bent axle axis, the side of second round platform portion certainly the lateral wall of bearing cooperation section to the axis slope of bent axle, the oil outlet is located first round platform portion with between the second round platform portion.

2. A crankshaft according to claim 1, wherein the first truncated cone portion has a length of 5mm to 10mm in an axial direction of the crankshaft.

3. A crankshaft according to claim 1, wherein the second truncated cone portion has a length of 5mm to 10mm in an axial direction of the crankshaft.

4. A crankshaft according to claim 1, wherein an angle θ between a side surface of the first dome portion and an axis of the crankshaft₁And the maximum inclination angle alpha when the crankshaft rotates satisfies the following conditions: tan theta₁The range of A is 0.8-1.2;

wherein tan α ═ Φ₁-Φ₂) L, where phi₁Is the inner diameter, phi, of a bearing sleeved on the bearing matching section₂The outer diameter of the bearing fitting section is defined as L, and the axial length of the bearing is defined as L.

5. A crankshaft according to claim 1, wherein the angle θ between the side of the second dome and the axis of the crankshaft₂And the maximum inclination angle alpha when the crankshaft rotates satisfies the following conditions: tan theta₂B · tan α, said B being in the range of 0.8 to 1.2;

6. A crankshaft according to claim 1, wherein a side surface of the first truncated cone portion is inclined toward an axis of the crankshaft by a width of 0.01mm to 0.03mm in a radial direction of the crankshaft.

7. A crankshaft according to claim 1, wherein a side surface of the second truncated cone portion is inclined toward an axis of the crankshaft by a width of 0.01mm to 0.03mm in a radial direction of the crankshaft.

8. The crankshaft of claim 1, wherein the side wall of the bearing engaging section is provided with a side oil groove extending in the axial direction of the crankshaft, and the oil outlet hole is formed in the side oil groove and communicates the main oil groove and the side oil groove.

9. A crankshaft according to any one of claims 1 to 7, comprising an auxiliary shaft section, a main shaft section and an eccentric section, the auxiliary shaft section, the main shaft section and the eccentric section forming the bearing engagement section, respectively.

10. A compressor comprising the crankshaft of any one of claims 1 to 9.

11. A refrigerating and heating apparatus comprising the compressor of claim 10.