阅读说明：本技术 曲轴及变频压缩机 (Crankshaft and variable frequency compressor ) 是由 黎林 孙祥 张淼 于 2018-08-29 设计创作，主要内容包括：本发明涉及压缩机领域,公开了一种曲轴及变频压缩机,曲轴包括依次相连的主轴、曲柄臂和副轴,副轴相对主轴的中心线偏心设置,主轴内设置有沿轴向方向延伸的主轴油道,主轴油道的中心线与主轴的中心线重合,主轴的外壁上设置有沿轴向方向螺旋延伸的凹槽以及将凹槽的两端分别与主轴油道连通的第一通油孔和第二通油孔,第一通油孔相对第二通油孔远离曲柄臂设置,主轴从远离曲柄臂的端部开始沿轴向方向依次包括用于安装油泵部件的第一轴段以及位于第一轴段和第一通油孔之间的第二轴段,第二轴段的内壁上设置有与第一通油孔连通且沿轴向方向延伸的凹陷部。本发明的曲轴及变频压缩机,在保证曲轴强度的前提下可最大限度减小主轴壁厚来增大上油量。(The invention relates to the field of compressors and discloses a crankshaft and a variable frequency compressor, wherein the crankshaft comprises main shafts which are connected in sequence, crank arm and countershaft, the countershaft sets up along the central line off-centre of main shaft, be provided with the main shaft oil duct that extends along axial direction in the main shaft, the central line of main shaft oil duct and the coincidence of the central line of main shaft, be provided with on the outer wall of main shaft along the recess of axial direction spiral extension and with the first oil through hole and the second oil through hole of the both ends of recess respectively with main shaft oil duct intercommunication, the crank arm setting is kept away from to the second oil through hole to first oil through hole, the main shaft begins to include the first axle section that is used for installing oil pump part and is located the second axle section between first axle section and the first oil through hole along axial direction in proper order from the tip of keeping away from the crank arm, be provided with on the inner wall of second axle. The crankshaft and the variable frequency compressor can reduce the wall thickness of the main shaft to the maximum extent to increase the oil feeding amount on the premise of ensuring the strength of the crankshaft.)

1. The utility model provides a crankshaft, its characterized in that, the crankshaft includes consecutive main shaft (1), crank arm (2) and countershaft (3), countershaft (3) is relative the central line eccentric settings of main shaft (1), be provided with main shaft oil duct (11) that extend along axial direction in main shaft (1), the central line of main shaft oil duct (11) with the central line coincidence of main shaft (1), be provided with on the outer wall of main shaft (1) along axial direction spiral extension's recess (12) and with the both ends of recess (12) respectively with first logical oilhole (13) and second logical oilhole (14) of main shaft oil duct (11) intercommunication, first logical oilhole (13) are relative second logical oilhole (14) are kept away from crank arm (2) set up, main shaft (1) from keeping away from the tip of crank arm (2) begin along axial direction includes first axial segment (Z1) and be located the oil pump part of installation in proper order and be located A second shaft section (Z2) between the first shaft section (Z1) and the first oil through hole (13), wherein a concave part (15) communicated with the first oil through hole (13) and extending along the axial direction is arranged on the inner wall of the second shaft section (Z2).

2. A crankshaft according to claim 1, characterized in that the cross section of the second shaft section (Z2) is circular, and the cross section of the recess (15) is an arc structure with the depth in the radial direction gradually decreasing from the center to both sides in the circumferential direction.

3. A crankshaft according to claim 1, characterized in that the cross section of the second shaft section (Z2) is circular and the cross section of the recess (15) is an arc-shaped groove structure with constant depth in the radial direction.

4. A crankshaft according to claim 3, wherein the central angle of the arcuate slot structure is in the range of 15 ° to 90 °.

5. A crankshaft according to any one of claims 1-4, characterized in that the minimum wall thickness (T) of the main shaft (1) at the recess (15) has a value in the range of 0.8-0.95 mm.

6. A crankshaft according to any one of claims 1-4, characterized in that the length of the first shaft section (Z1) in the axial direction has a value in the range of 3-6 mm.

7. A crankshaft according to any one of claims 1-4, characterized in that the crank arm (2) is provided with a passage communicating with the second oil passage hole (14), in that the countershaft (3) is provided with a countershaft oil channel (31) communicating with the passage, and in that the countershaft oil channel (31) extends to the end of the countershaft (3) remote from the crank arm (2) to form a third oil passage hole.

8. A crankshaft according to claim 7, characterized in that the outer wall of the secondary shaft (3) is provided with an opening (32) communicating with the secondary shaft oil channel (31).

9. Inverter compressor, characterized in that it comprises an oil pump part (20) and a crankshaft (10) according to any one of claims 1-8, the oil pump part (20) being mounted on the first shaft section (Z1).

10. The inverter compressor according to claim 9, characterized in that the oil pump member (20) is housed inside the first shaft section (Z1).

Technical Field

The invention relates to the field of compressors, in particular to a crankshaft and a variable frequency compressor.

Background

The typical totally-enclosed refrigeration compressor generally comprises an upper shell, a lower shell, a crank shaft, an oil pump, a connecting rod, a piston pin, a valve bank, a motor, refrigerating machine oil and the like, wherein the refrigerating machine oil is stored at the bottom of the shell of the compressor, the crank shaft comprises a main shaft, a crank arm and an auxiliary shaft, an oil inlet channel is generally formed in the crank shaft, the refrigerating machine oil at the bottom of the shell can be conveyed along the oil inlet channel and guided to each friction pair of the compressor for lubrication by utilizing the centrifugal force generated when the crank shaft operates and matching with the oil pump, so that the friction loss generated when the parts operate is reduced, and meanwhile, the refrigerating machine oil also has a certain cooling effect, so that the. Wherein, the formula of the pump oil head of the oil pump is as follows:

h is the lift of the oil pump, R is the maximum distance between the inner wall of the main shaft and the rotation axis of the crankshaft (namely the maximum radius of the oil inlet channel in the main shaft), R is the minimum distance between an oil inlet at the bottom of the oil pump and the rotation axis of the crankshaft, and omega is the running angular speed of the crankshaft. If the crankshaft can lubricate and lubricate each moving part, the lift height H must be larger than the height difference H between the oil level M and the first oil through hole on the main shaft (as shown in fig. 4), and the larger the difference between the two is, the better the oil pumping effect is.

The inverter compressor is a compressor capable of continuously changing output energy by continuously adjusting the rotation speed within a certain range through a control mode or means in the case of a compressor with a constant rotation speed. The refrigerating capacity can be adjusted by changing the running speed according to the working requirement, and the lower the rotating speed is, the lower the power consumption is, so the variable frequency compressor has the advantages of high efficiency and energy saving. In order to ensure good refrigeration effect and reduce abrasion among various moving parts, the rotating speed of the inverter compressor is generally controlled to be about 1200 to 6000 rpm. According to the formula of the pumping oil lift, the pumping oil lift is in positive correlation with the angular velocity omega, so that the pumping oil capacity is poor when the frequency conversion compressor rotates at a low speed, the problem of poor lubrication caused by insufficient oil supply exists, and the normal work of the compressor is influenced. In order to ensure the oil feeding amount, the wall thickness of the main shaft can be reduced to increase the maximum radius R, and the first scheme is as follows: the radius of an oil inlet channel (main shaft oil duct) in the main shaft is integrally increased, so that the wall thickness of the main shaft is integrally reduced, the strength of the main shaft cannot meet the normal working requirement, for example, an oil pump part is arranged at the end part of the main shaft, which is far away from a crank arm, and has a certain requirement on the wall thickness of the main shaft; the second scheme is as follows: the main shaft oil duct is eccentrically arranged (namely, the main shaft oil duct radially moves for a certain distance towards the first oil through hole), so that the thinner side of the wall thickness of the main shaft is thicker, and the lower integral strength of the main shaft can be caused.

Therefore, there is a need to design a crankshaft that can increase the amount of oil supplied by minimizing the thickness of the main shaft wall while ensuring the strength of the crankshaft.

Disclosure of Invention

The invention aims to solve the problem that the wall thickness cannot be reduced to the maximum extent to increase the oil feeding amount on the premise of ensuring the strength of a main shaft in the prior art, and provides a crankshaft which can reduce the wall thickness of the main shaft to the maximum extent to increase the oil feeding amount on the premise of ensuring the strength of the crankshaft.

Another object of the present invention is to provide an inverter compressor comprising the above crankshaft.

In order to achieve the above object, an aspect of the present invention provides a crankshaft, including a main shaft, a crank arm, and an auxiliary shaft, which are sequentially connected to each other, wherein the auxiliary shaft is eccentrically disposed with respect to a center line of the main shaft, a main shaft oil gallery extending in an axial direction is disposed in the main shaft, a center line of the main shaft oil gallery coincides with a center line of the main shaft, a groove spirally extending in the axial direction and a first oil passage hole and a second oil passage hole that communicate both ends of the groove with the main shaft oil gallery, respectively, are disposed on an outer wall of the main shaft, the first oil passage hole is disposed away from the crank arm with respect to the second oil passage hole, the main shaft sequentially includes a first shaft section for mounting an oil pump component and a second shaft section located between the first shaft section and the first oil passage hole from an end portion away from the crank arm in the axial, and a concave part which is communicated with the first oil through hole and extends along the axial direction is arranged on the inner wall of the second shaft section.

In the technical scheme, because the central line of the main shaft oil duct coincides with the central line of the main shaft, the wall thickness of the main shaft is generally consistent, the overall strength of the main shaft is higher in a mode of eccentric arrangement relative to the main shaft oil duct, and the local part of the depressed part is arranged on the inner wall of the second shaft section of the main shaft, the influence on the overall strength of the main shaft is small, the strength of the first shaft section for installing the oil pump part is not influenced, the oil pump part can be reliably installed to prevent oil leakage, meanwhile, the radius of the main shaft oil duct at the first oil through hole is increased by the depressed part, the oil pumping lift at the position is higher, the oil feeding amount can be obviously increased, the oil feeding amount of the crankshaft can still meet the requirement of normal lubrication when the compressor runs at low speed, and. Therefore, the crankshaft in the application can reduce the wall thickness of the main shaft to the maximum extent to increase the oil feeding amount on the premise of ensuring the strength of the crankshaft, has a good lubricating effect, is beneficial to improving the working performance of a compressor using the crankshaft, and is simple in structure, convenient to process and low in cost.

Preferably, the cross section of the second shaft section is circular ring-shaped, and the cross section of the recessed portion is an arc-shaped structure with the depth in the radial direction gradually decreasing from the center to two sides along the circumferential direction.

Preferably, the cross section of the second shaft section is circular ring-shaped, and the cross section of the recess is an arc-shaped groove structure with constant depth along the radial direction.

Preferably, the central angle of the arc-shaped groove structure ranges from 15 degrees to 90 degrees.

Preferably, the minimum wall thickness of the main shaft at the recess is in the range of 0.8mm-0.95 mm.

Preferably, the length of the first shaft section along the axial direction has a value in the range of 3mm to 6 mm.

Preferably, a passage communicating with the second oil passage hole is provided in the crank arm, a counter shaft oil passage communicating with the passage is provided in the counter shaft, and the counter shaft oil passage extends to an end portion of the counter shaft away from the crank arm to form a third oil passage hole.

Preferably, an opening communicated with the auxiliary shaft oil passage is formed in the outer wall of the auxiliary shaft.

The invention provides an inverter compressor, which comprises the oil pump component and the crankshaft, wherein the oil pump component is arranged on the first shaft section.

Preferably, the oil pump part is sleeved inside the first shaft section.

Additional features and advantages of the invention will be set forth in the detailed description which follows.

Drawings

FIG. 1 is a schematic structural view of a crankshaft of a preferred embodiment of the present invention;

FIG. 2 is a partial cross-sectional view of a crankshaft of a preferred embodiment of the present invention;

FIG. 3 is a sectional view A-A of FIG. 2;

fig. 4 is a partial sectional view of the inverter compressor according to the preferred embodiment of the present invention.

Description of the reference numerals

1 main shaft 11 main shaft oil duct

12 groove 13 first oil through hole

14 second oil through hole 15 depression

2 crank arm 3 auxiliary shaft

31 countershaft oil gallery 32 opening

Z1 first shaft segment Z2 second shaft segment

10 crankshaft 20 oil pump parts

30 rack C oil pool

Difference of height of M oil liquid level H

Maximum distance R, minimum wall thickness

Detailed Description

The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the invention, are intended for purposes of illustration and explanation only and are not intended to limit the scope of the invention.

In the present invention, the use of directional terms such as "upper, lower, left, right" generally means upper, lower, left, right as viewed with reference to the accompanying drawings, unless otherwise specified; "inner and outer" refer to the inner and outer relative to the profile of each component itself.

The invention provides a crankshaft, which comprises a main shaft 1, a crank arm 2 and a secondary shaft 3 which are connected in sequence, wherein the secondary shaft 3 is arranged eccentrically relative to the central line of the main shaft 1, a main shaft oil passage 11 which extends along the axial direction is arranged in the main shaft 1, the central line of the main shaft oil passage 11 is coincident with the central line of the main shaft 1, a groove 12 which extends spirally along the axial direction and a first oil through hole 13 and a second oil through hole 14 which respectively communicate the two ends of the groove 12 with the main shaft oil passage 11 are arranged on the outer wall of the main shaft 1, the first oil through hole 13 is arranged far away from the crank arm 2 relative to the second oil through hole 14, the main shaft 1 sequentially comprises a first shaft section Z1 for mounting an oil pump component and a second shaft section Z2 which is arranged between the first shaft section Z1 and the first oil through hole 13 along the axial direction from the end far away from the crank arm 2, a recessed portion 15 communicating with the first oil passage hole 13 and extending in the axial direction is provided on an inner wall of the second shaft section Z2.

It should be noted that, preferably, the recessed portion 15 may extend from the first oil passing hole 13 to a connection position of the second shaft section Z2 and the first shaft section Z1, and of course, the recessed portion 15 may also have a distance from the connection position, and in addition, the recessed portion 15 may also extend continuously from the connection position to the first shaft section Z1 without affecting the installation of the oil pump component, that is, the recessed portion 15 may also be provided at the upper end of the first shaft section Z1 connected to the second shaft section Z2, and the recessed portion 15 is not generally provided at the lower end of the first shaft section Z1 for reliably installing the oil pump component.

In the above technical solution, as shown in fig. 1 and 2, since the center line of the main shaft oil gallery 11 coincides with the center line of the main shaft 1, the wall thickness of the main shaft 1 can be substantially the same, the overall strength of the main shaft 1 is high in a manner of being eccentrically arranged with respect to the main shaft oil gallery 11 under the condition that the outer diameter of the main shaft 1 is the same and the diameter of the main shaft oil gallery 11 is the same, and the recess portion 15 communicated with the first oil through hole 13 is partially arranged on the inner wall of the second shaft section Z2 of the main shaft 1, so that the influence on the overall strength of the main shaft 1 is small, the strength of the first shaft section Z1 on which the oil pump part is mounted is not affected, the oil pump part can be reliably mounted to prevent oil leakage, and meanwhile, the radius of the main shaft oil gallery 11 at the first oil through hole 13 is increased by the recess portion 15, the pumping lift at this position can be high, the oil feeding, the range of the rotational speed of the compressor using the crankshaft can be expanded. Therefore, the bent axle in this application can furthest reduce main shaft wall thickness and increase the oil mass under the prerequisite of guaranteeing bent axle intensity, and lubricated effect is better, helps improving the working property of the compressor that uses this bent axle, and bent axle simple structure simultaneously, processing is convenient, and the cost is lower.

The shape of the recess 15 can be designed according to the strength requirement of the crankshaft and the degree of oil feeding increase, and the shape of the recess 15 can be, but is not limited to, the following two embodiments:

first embodiment

As shown in fig. 3, the cross section of the second shaft section Z2 is circular, and the cross section of the recess 15 is an arc structure in which the depth in the radial direction gradually decreases from the center (of the cross section) to both sides (of the cross section) in the circumferential direction. Here, the "radial direction" refers to the radial direction of the main shaft 1, and the "circumferential direction" refers to the circumferential direction of the main shaft 1. Further preferably, the cross section of the recess 15 may be an arc-shaped structure formed on the inner wall of the main shaft 1 by an inner circle in a circular ring shape after the inner circle is moved toward the first oil passage hole 13 by a set distance in the radial direction. And, the deepest middle position of the arc-shaped structure may be aligned with the first oil passing hole 13 to maximize the pumping head at the first oil passing hole 13.

Second embodiment

The cross section of the second shaft section Z2 is circular, and the cross section of the recess 15 is an arc-shaped groove structure with constant length along the radial direction. Specifically, the cross section of the recess 15 may be an arc-shaped groove structure formed on the inner wall of the main shaft 1 by a circle which takes the center of an inner circle of a circular ring shape as a center and takes the radius of the inner circle and a set distance as radii.

In addition, in order to increase the oil feeding amount without greatly affecting the strength of the main shaft 1, preferably, the central angle of the arc-shaped groove structure ranges from 15 degrees to 90 degrees.

In the above two embodiments, since the minimum wall thickness of the spindle 1 needs to meet the strength requirement required for normal operation, the minimum wall thickness T of the spindle 1 at the recess 15 preferably ranges from 0.8mm to 0.95 mm. At this time, the "set distance" is the difference between the wall thickness of the spindle 1 when the recess 15 is not machined and the minimum wall thickness T.

In order to enable the oil pump component to be reliably mounted on the main shaft 1, the length of the first shaft section Z1 in the axial direction preferably ranges from 3mm to 6 mm.

In addition, it is preferable that a passage communicating with the second oil passage hole 14 is provided on the crank arm 2, a counter oil passage 31 communicating with the passage is provided in the counter shaft 3, and the counter oil passage 31 extends to an end portion of the counter shaft 3 remote from the crank arm 2 to form a third oil passage hole. Specifically, as shown in fig. 4, when the compressor using the crankshaft of the present invention pumps oil, the oil pump part 20 generates a centrifugal force in the oil sump C, so that the oil enters the oil pump part 20 through the oil inlet of the oil pump part 20 submerged in the oil sump C, uniformly rises along the circumference of the housing of the oil pump part 20, enters the main shaft oil gallery 11, and enters the recess 15 on the inner wall of the main shaft oil gallery 11 after reaching the main shaft oil gallery 11, as shown in fig. 1, the maximum radius R increases due to the reduction of the wall thickness of the main shaft 1 at the recess 15, as shown in fig. 3, and the oil pumping head formula according to the centrifugal pump is obtained

It can be seen that the oil pumping capacity of the crankshaft is improved, and the oil flowing out of the first oil passing hole 13 enters the groove 12 and spirally rises along the groove 12 to pass through the second oil passing holeThe two-way oil hole 14 then enters the auxiliary shaft oil passage 31 through the passage of the crank arm 2, and then flows out of the third oil hole, and finally reaches each running part in the compressor for lubrication, so that each part can run normally.

Since the position of the oil line thrown out from the third oil passing hole is too high to lubricate the piston when the compressor is operated at a high speed, it is preferable that an opening 32 communicating with the counter oil passage 31 is provided on the outer wall of the counter shaft 3. The oil thus thrown from the opening 32 lubricates the piston.

In a second aspect, the present invention provides an inverter compressor, as shown in fig. 4, comprising an oil pump unit 20 mounted on the first shaft segment Z1 and the crankshaft 10 described above. The variable frequency compressor also comprises a shell, a rack 30 and a rotor, wherein the rack 30 and the rotor are installed in the shell, the crankshaft 10 is installed on the rack 30, the rotor is sleeved on the crankshaft 10, the refrigerating machine oil is located at the bottom of the shell, and the oil liquid level of the refrigerating machine oil is M.

As shown in fig. 4, the oil pump member 20 is preferably fitted inside the first shaft segment Z1. The lower end of the main shaft 1 can be flush with the rotor or even retracted into the rotor, and compared with the scheme that the lower end of the main shaft 1 extends out of the rotor for a distance to reserve the position of the external riveting oil pump component 20, the oiling height can be shortened.

The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited thereto. Within the scope of the technical idea of the invention, numerous simple modifications can be made to the technical solution of the invention, including combinations of the individual specific technical features in any suitable way. The invention is not described in detail in order to avoid unnecessary repetition. These simple modifications and combinations should be considered as the disclosure of the present invention, and all fall within the scope of the present invention.