CN215486452U - Crankshaft assembly for compressor and compressor with crankshaft assembly - Google Patents
Crankshaft assembly for compressor and compressor with crankshaft assembly Download PDFInfo
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- CN215486452U CN215486452U CN202120480994.7U CN202120480994U CN215486452U CN 215486452 U CN215486452 U CN 215486452U CN 202120480994 U CN202120480994 U CN 202120480994U CN 215486452 U CN215486452 U CN 215486452U
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Abstract
The utility model provides a crankshaft assembly for a compressor and the compressor with the same, wherein the crankshaft assembly comprises a crankshaft and a movable disc, the top of the crankshaft is provided with an eccentric shaft, and the excircle of the eccentric shaft is connected with the movable disc through a movable disc bearing; the top of the eccentric shaft is provided with a groove, and the bottom of the movable disc is provided with a bulge; when the eccentric shaft drives the movable disc to rotate, the force of the eccentric shaft acting on the movable disc comprises the force of the excircle of the eccentric shaft acting on the movable disc bearing and the force of the groove acting on the bulge; applying the crankshaft assembly to a compressor, the moving disk having a centrifugal force and a tangential force of the gas acting on the moving disk; the power that the excircle of eccentric shaft acted on movable disk bearing is balanced with the tangential force of gaseous effect on movable disk, and the recess acts on bellied power and the centrifugal force balance of movable disk, and then the frictional force action point is invariable and the atress size is unchangeable between eccentric shaft and the movable disk, has prolonged the life-span of eccentric shaft, has reduced the leakage of movable disk and quiet dish fit clearance department, has increased the motor life-span.
Description
Technical Field
The utility model relates to the technical field of compressors, in particular to a crankshaft assembly for a compressor and the compressor with the crankshaft assembly.
Background
At present, in a compressor, a matching mode of a crankshaft and a movable disc is that an eccentric shaft of the crankshaft is matched with a movable disc bearing with a gap, and then the movable disc does pure revolution motion around a circle center under the action of the eccentric shaft of the crankshaft. Due to the continuity of air suction and air exhaust, the rotation speed of the scroll compressor is far higher than that of the rotor compressor; when the compressor rotates at a high speed, the frequency of alternating load on parts of the turbine compressor in the same time is greatly higher than that of a rotor compressor; in order to increase the reliability of the parts and reduce the energy consumption, the friction loss of the autorotation preventing mechanism and the alternating load applied to the parts need to be reduced. In the prior art, although the crankshaft and the cross slip ring jointly drive the moving disc to realize autorotation prevention, a higher alternating load is generated on a shafting; the crankshaft eccentric shaft of the compressor is easy to generate fatigue wear, and the whole compressor is scrapped.
Disclosure of Invention
In view of the above, the utility model provides a crankshaft assembly for a compressor and a compressor with the same, so as to solve the problems that in the prior art, an eccentric shaft is subjected to fatigue wear due to periodic load, and a gap between a movable disc and a static disc is continuously changed to cause leakage.
The utility model provides a crankshaft assembly for a compressor, wherein the crankshaft assembly comprises a crankshaft and a movable disc, an eccentric shaft is formed at the top of the crankshaft, and the excircle of the eccentric shaft is connected with the movable disc through a movable disc bearing; and a bulge and a groove are arranged between the top of the eccentric shaft and the bottom of the movable disc, and the force applied to the movable disc is balanced through the interaction of the bulge and the groove, so that the action point of the friction force between the eccentric shaft and the movable disc is constant and the force applied to the eccentric shaft does not change along with the rotation of the eccentric shaft.
Further optionally, a protrusion is formed on one side of the movable disc close to the eccentric shaft, and a groove is correspondingly formed on one side of the eccentric shaft close to the movable disc; the grooves and the protrusions form the interaction when the crankshaft rotates.
Further optionally, the center line of the protrusion is collinear with the center line of the eccentric shaft; the center line of the groove is deviated from the center line of the eccentric shaft.
Further optionally, a centerline of the groove is collinear with a centerline of the crankshaft; in the rotation process of the crankshaft, the force of the eccentric shaft acting on the movable disc comprises the force of the excircle of the eccentric shaft acting on the movable disc bearing and the force of the groove acting on the bulge, and the force of the excircle of the eccentric shaft acting on the movable disc bearing is vertical to the force of the groove acting on the bulge.
Further optionally, when the crankshaft drives the movable disc to rotate, the force of the outer circle of the eccentric shaft acting on the movable disc bearing is collinear with the linear velocity direction of the movable disc; the force of the groove acting on the protrusion is vertical to the linear velocity direction of the movable disc.
Further optionally, the force of the outer circle of the eccentric shaft acting on the movable disc bearing is balanced with the tangential force of the gas acting on the movable disc, the force of the groove acting on the protrusion is balanced with the centrifugal force of the movable disc, and the acting point of the friction force between the eccentric shaft and the movable disc is constant.
Further optionally, when the crankshaft rotates clockwise and the force of the outer circle of the eccentric shaft acting on the movable disc bearing is vertically upward, the force of the groove acting on the protrusion is horizontally rightward; the centrifugal force of the movable disc is horizontally leftward, and the tangential force of the gas acting on the movable disc is vertically downward.
Further optionally, a rolling bearing or a wear-resistant material is further arranged at the matching position of the protrusion and the groove.
Further optionally, the protrusion height is greater than the axial distance between the eccentric shaft and the movable disc.
The utility model also provides a crankshaft, wherein an eccentric shaft is formed at the top of the crankshaft, and the eccentric shaft is provided with an outer contour and an inner groove; the eccentric shaft is matched with the movable disc through the inner groove and the protrusion; at least a part of the outer contour is contacted with the movable disc bearing, and at least a part of the inner groove is contacted with the protrusion; the eccentric shaft acts on the movable disc through the outer contour and the inner groove;
the force of the eccentric shaft acting on the movable disc comprises a force of the outer contour of the eccentric shaft acting on the movable disc bearing and a force of the inner groove acting on the bulge, and the force of the outer contour of the eccentric shaft acting on the movable disc bearing is perpendicular to the force of the inner groove acting on the bulge.
The utility model also provides a compressor, which is provided with the crankshaft assembly shaft for the compressor.
The utility model provides a crankshaft assembly for a compressor, which comprises a crankshaft and a movable disc, wherein the top of the crankshaft is provided with an eccentric shaft, and the excircle of the eccentric shaft is connected with the movable disc through a movable disc bearing; the top of the eccentric shaft is provided with a groove, and the bottom of the movable disc is provided with a bulge; the center of the bulge corresponds to the center of the eccentric shaft, and the center of the groove corresponds to the center of the crankshaft; the force of the eccentric shaft acting on the movable disc comprises the force of the excircle of the eccentric shaft acting on the movable disc bearing and the force of the groove acting on the bulge; be applied to the compressor with above-mentioned bent axle subassembly, when bent axle drive movable disk rotated, the power that the excircle of eccentric shaft acted on movable disk bearing was balanced with the tangential force of gaseous effect on the movable disk, the recess acts on bellied power and the centrifugal force balance of movable disk, and then frictional force action point is invariable between eccentric shaft and the movable disk, the load that the bent axle received has been reduced, and the load no longer changes along with the rotation of eccentric shaft, the life-span of eccentric shaft has been prolonged, the unsteady that eccentric shaft and movable disk bearing clearance arouse has been eliminated, the leakage of sound dish fit clearance department has been reduced, the motor life-span has been increased.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. It should be apparent that the drawings in the following description are merely exemplary, and that other embodiments can be derived from the drawings provided by those of ordinary skill in the art without inventive effort.
The structures, ratios, sizes, and the like shown in the present specification are only used for matching with the contents disclosed in the specification, so as to be understood and read by those skilled in the art, and are not used to limit the conditions that the present invention can be implemented, so that the present invention has no technical significance, and any structural modifications, changes in the ratio relationship, or adjustments of the sizes, without affecting the effects and the achievable by the present invention, should still fall within the range that the technical contents disclosed in the present invention can cover.
FIGS. 1a and 1b are schematic structural views of an embodiment of a crankshaft assembly for a compressor according to the present invention;
FIGS. 2a and 2b are schematic structural diagrams illustrating an embodiment of a stress situation of a crankshaft assembly for a compressor according to the present invention;
FIG. 3 is a schematic structural view of another embodiment of a crankshaft provided in the present invention;
FIG. 4 is a schematic structural diagram of an embodiment of a crankshaft assembly for a compressor according to the present invention, illustrating a stress situation when an eccentric shaft is worn;
in the figure:
1-a crankshaft; 11-an eccentric shaft; 111-grooves; 112-outer contour; 113-an inner groove;
2-a movable disc; 21-a moving disc bearing; 22-a bump;
31-rolling bearing.
Detailed Description
The present invention is described in terms of particular embodiments, other advantages and features of the utility model will become apparent to those skilled in the art from the following disclosure, and it is to be understood that the described embodiments are merely exemplary of the utility model and that it is not intended to limit the utility model to the particular embodiments disclosed. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The terminology used in the embodiments of the utility model is for the purpose of describing particular embodiments only and is not intended to be limiting of the utility model. As used in the examples of the present invention and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms as well, and "a" and "an" generally include at least two, but do not exclude at least one, unless the context clearly dictates otherwise.
It should be understood that the term "and/or" as used herein is merely one type of association that describes an associated object, meaning that three relationships may exist, e.g., a and/or B may mean: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.
It is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a good or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such good or system. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in a commodity or system that includes the element.
The utility model provides a crankshaft assembly for a compressor, which comprises a crankshaft and a movable disc, wherein the top of the crankshaft is provided with an eccentric shaft, and the excircle of the eccentric shaft is connected with the movable disc through a movable disc bearing; the top of the eccentric shaft is provided with a groove, and the bottom of the movable disc is provided with a bulge; the center of the bulge corresponds to the center of the eccentric shaft, and the center of the groove corresponds to the center of the crankshaft; the force of the eccentric shaft acting on the movable disc comprises the force of the excircle of the eccentric shaft acting on the movable disc bearing and the force of the groove acting on the bulge; be applied to the compressor with above-mentioned bent axle subassembly, when bent axle drive movable disk rotated, the power that the excircle of eccentric shaft acted on movable disk bearing was balanced with the tangential force of gaseous effect on the movable disk, the recess acts on bellied power and the centrifugal force balance of movable disk, and then frictional force action point is invariable between eccentric shaft and the movable disk, the load that the bent axle received has been reduced, and the load no longer changes along with the rotation of eccentric shaft, the life-span of eccentric shaft has been prolonged, the unsteady that eccentric shaft and movable disk bearing clearance arouse has been eliminated, the leakage of sound dish fit clearance department has been reduced, the motor life-span has been increased.
Example 1
< crankshaft Assembly >
As shown in fig. 1a, the present embodiment provides a crankshaft assembly for a compressor, wherein the crankshaft assembly includes a crankshaft 1 and a movable plate 2, an eccentric shaft 11 is formed at the top of the crankshaft 1, and the outer circumference of the eccentric shaft 11 is connected with the movable plate 2 through a movable plate bearing 21; be equipped with arch 22 and recess 111 between the top of eccentric shaft 11 and movable disk 2 bottom, through the interact of arch 22 and recess 111, balanced movable disk 2 received power, make the constant and atress size of frictional force action point between eccentric shaft 11 and the movable disk 2 not change along with the rotation of eccentric shaft, reduce the wearing and tearing between eccentric shaft 11 and the movable disk 2.
Preferably, the side of the movable disc 2 close to the eccentric shaft 11 is formed with a projection 22, and correspondingly, the side of the eccentric shaft 11 close to the movable disc 2 is formed with a groove 111; when the crankshaft 1 is rotated, the outer circumference of the eccentric shaft 11 can act on the movable disc bearing 21, and the groove 111 interacts with the projection 22.
Preferably, the center line of the protrusion 22 is on the same straight line with the center line of the eccentric shaft 11; the center line of the groove 111 is offset from the center line of the eccentric shaft 11.
Preferably, the center line of the groove 111 is on the same straight line as the center line of the crankshaft 1; the force of the eccentric shaft 11 acting on the moving disc 2 during the rotation of the crankshaft 1 comprises the force F of the outer circle of the eccentric shaft 11 acting on the moving disc bearing 211And the force F of the groove 111 acting on the projection 222And the force F of the outer circle of the eccentric shaft 11 acting on the movable disc bearing 211The force F acting on the projection 22 with the groove 1112Are perpendicular to each other.
Preferably, when the crankshaft 1 drives the movable disc 2 to rotate, the force F of the external circle of the eccentric shaft 11 acting on the movable disc bearing 211Is collinear with the linear velocity direction of the movable disc 2; force F of the groove 111 acting on the protrusion 222Is vertical to the linear velocity direction of the movable disc 2; when the linear velocity direction of the movable disc 2 changes, the force F of the outer circle of the eccentric shaft 11 acting on the movable disc bearing 211And the force F of the groove 111 acting on the projection 222The direction of (a) changes accordingly.
Preferably, when the crankshaft 1 drives the movable disc 2 to rotate, the tangential force of the gas on the movable disc 2 is opposite to the linear velocity direction of the movable disc 2 due to the pressure of the gas; due to the centrifugal action, the centrifugal force of the movable disc 2 can enable the protrusions 22 to act on the grooves 111, and the centrifugal force of the movable disc 2 is perpendicular to the linear velocity direction of the movable disc 2;
force F of the outer circle of the eccentric shaft 11 acting on the movable disc bearing 211The force F of the grooves 111 acting on the protrusions 22 is balanced by the tangential force of the gas acting on the moving disk 22With the centrifugal force balance of driving disk 2, and then the contact point between eccentric shaft 11 and the driving disk 2 keeps unchangeable, the linear velocity of direction follow-up disk 2 changes, the centrifugal force of driving disk 2 changes with the linear velocity that receives gaseous tangential force direction follow-up disk 2, makes frictional force action point invariant and atress size unchangeable between eccentric shaft 11 and the driving disk 2 to the wearing and tearing between eccentric shaft 11 and the driving disk 2 have been avoided.
Preferably, the height of the protrusions 22 is greater than the axial distance between the eccentric shaft 11 and the moving disk 2, so that when the protrusions 22 are fitted into the grooves 111, the ends of the protrusions 22 are at a distance from the bottoms of the grooves 111.
In some embodiments, as shown in fig. 1b, the engagement of the protrusions 22 with the grooves 111 is provided with a rolling bearing 31 or a wear-resistant material, which further reduces the wear between the eccentric shaft 11 and the moving plate 2.
In the present embodiment, as shown in fig. 2a, when the crankshaft 1 rotates clockwise, the linear velocity of the movable plate 2 is vertically upward, and the force F of the outer circle of the eccentric shaft 11 acting on the movable plate bearing 21 is1Vertically upwards, the force F of the groove 111 acting on the protrusion 222Horizontally to the right; the centrifugal force of the movable disc 2 is horizontally leftwards, and the tangential force of the gas acting on the movable disc 2 is vertically downwards; outer circle of eccentric shaft 11Force F for the moving disc bearing 211Balancing the tangential force of the gas acting on the movable disc 2; force F of the groove 111 acting on the protrusion 222The friction force acting point between the movable disc 2 and the eccentric shaft 11 is constant and the stress is not changed, so that the abrasion between the movable disc 2 and the crankshaft 1 is eliminated.
In the present embodiment, as shown in FIG. 2b, when the crankshaft 1 rotates clockwise, the linear velocity of the movable plate 2 is horizontally rightward, and the force F of the outer circle of the eccentric shaft 11 acting on the movable plate bearing 21 is generated1Horizontal to the right, the force F of the groove 111 acting on the protrusion 222Vertically downwards; the centrifugal force of the movable disc 2 is vertical upwards, and the tangential force of the gas acting on the movable disc 2 is horizontal leftwards; force F of the outer circle of the eccentric shaft 11 acting on the movable disc bearing 211Balancing the tangential force of the gas acting on the movable disc 2; force F of the groove 111 acting on the protrusion 222The action point of the friction force between the movable disc 2 and the eccentric shaft 11 is constant and the force is not changed along with the rotation of the eccentric shaft, thereby eliminating the abrasion between the movable disc 2 and the crankshaft 1.
Example 2
In the utility model, the contact point of the eccentric shaft and the movable disc is kept unchanged, and certain slippage can be generated according to the abrasion degree only when the eccentric shaft is abraded, and in this case, the eccentric shaft of the utility model does not need to be a whole shaft, but can be made into a structure as shown in figure 3. An eccentric shaft 11 is formed at the top of the crankshaft 1, a part of the outer contour 112 of the eccentric shaft 11 is matched with the movable disc bearing 21, in order to ensure the bearing rigidity of radial force, the left side of the outer contour 112 is a section of circular arc, the circular arc is not contacted with the movable disc bearing 21, and the right side of the outer contour is not provided with the circular arc; the eccentric shaft 11 is internally formed with an inner groove 113, a portion of which is in contact with the boss 22; the eccentric shaft 11 acts on the moving disc bearing 21 through the outer contour 112 and on the protrusion 22 through the inner recess 111, and the eccentric shaft 11 in turn acts on the moving disc 2.
In the embodiment, the eccentric shaft 11 at the top of the crankshaft 1 is removed except the periphery of the acting point, only the outer contour 112 contacting with the movable disc bearing 21 and the inner groove 113 contacting with the bulge 22 are reserved, the total mass of the eccentric shaft 11 is reduced, and enough rigidity is ensured in the main stress direction, so that the eccentric mass is reduced; meanwhile, except for the outer contour 112 matched with the movable disc bearing 21 and the inner groove 113 matched with the bulge 22, other surfaces of the eccentric shaft 11 do not need to be subjected to finish machining, and even the non-finished surface of the back can be directly used for correcting the influence of grinding on the cylindricity of the crankshaft, so that the machining cost is reduced.
Preferably, the force of the eccentric shaft 11 on the movable disc 2 comprises the force of the outer contour 112 of the eccentric shaft 11 on the movable disc bearing 21 and the force of the inner groove 113 on the protrusion 22, and the force of the outer contour 112 of the eccentric shaft 11 on the movable disc bearing 21 is perpendicular to the force of the inner groove 113 on the protrusion 22.
Preferably, when the eccentric shaft 11 drives the movable disc 2 to rotate, the force of the outer contour 112 of the eccentric shaft 11 acting on the movable disc bearing 21 is collinear with the linear velocity direction of the movable disc 2; the force of the inner grooves 113 on the protrusions 22 is perpendicular to the linear velocity direction of the movable platen 2.
In this embodiment, when the crankshaft 1 rotates clockwise, the linear velocity of the movable disc 2 is vertically upward, the force of the outer contour 112 of the eccentric shaft 11 acting on the movable disc bearing 21 is vertically upward, and the force of the inner groove 113 acting on the protrusion 22 is horizontally rightward; the centrifugal force of the movable disc 2 is horizontally leftwards, and the tangential force of the gas acting on the movable disc 2 is vertically downwards; the force of the outer contour 112 of the eccentric shaft 11 acting on the movable disc bearing 21 is balanced with the tangential force of the gas acting on the movable disc 2; the force of the inner recess 113 on the projection 22 is balanced by the centrifugal force of the rotor plate 2.
As shown in FIG. 4, the present embodiment provides the stress condition of the eccentric shaft 11 of the crankshaft 1 when it is worn, the relative position of the protrusion 22 of the movable plate 2 and the movable plate bearing 21 is not changed; the outer circle of the eccentric shaft 11 has relatively small size due to abrasion, and the position of the contact point of the eccentric shaft and the movable disc bearing 21 is changed; because of the different abrasion positions of the excircle of the eccentric shaft 11, the force of the eccentric shaft 11 acting on the movable disc bearing 21 is uncertain and can be left or right;
when the left end of the excircle of the eccentric shaft 11 is seriously abraded, the contact point of the excircle of the eccentric shaft 11 and the movable disc bearing 21 moves rightwards; the force of the outer circle of the eccentric shaft 11 acting on the movable disc bearing 21 deflects towards the upper right, and the component force of the force can share a part of the component force of the movable disc 2; the force of the protrusion 22 acting on the groove 111 is leftward, and the component of the force shares a part of the pressure of the eccentric shaft 11 on the movable disc bearing 21; if the component force of the excircle of the eccentric shaft 11 acting on the movable disc bearing 21, the component force of the bulge acting on the groove 111 and the centripetal force required by the movable disc 2 are greater than those of the excircle of the eccentric shaft 11, the eccentric shaft 11 can deform, the direction of the acting force of the eccentric shaft 11 on the movable disc bearing 21 is changed, and the eccentric shaft 11 is in stress balance after being worn again.
In another embodiment, the outer circle of the eccentric shaft 11 is too small due to wear, and in this case, contrary to fig. 4, the protrusion 22 of the movable disk 2 slides to the upper side of the groove 111, so that the force of the groove 111 acting on the protrusion 22 deflects downward and rightward; the force of the movable plate bearing 21 and the protrusion 22 is increased, so that the clearance of the movable plate bearing 21 is larger than the clearance between the protrusion 22 and the groove 111 to avoid wear.
It should be noted that, no matter how, the structure of the utility model is constant in the action point of the friction force between the eccentric shaft and the movable disc bearing under the same working condition and the same abrasion degree; on the contrary, for the matching of the traditional eccentric shaft and the movable disc bearing, the more the eccentric shaft and the movable disc bearing are worn in, the larger the gap between the eccentric shaft and the movable disc bearing is, the larger the relative motion range between the eccentric shaft and the movable disc bearing is, and the larger the leakage becomes.
Exemplary embodiments of the present disclosure are specifically illustrated and described above. It is to be understood that the present disclosure is not limited to the precise arrangements, instrumentalities, or instrumentalities described herein; on the contrary, the disclosure is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
Claims (10)
1. A crankshaft assembly for a compressor, wherein the crankshaft assembly comprises a crankshaft (1) and a movable plate (2), an eccentric shaft (11) is formed at the top of the crankshaft (1), and the outer circle of the eccentric shaft (11) is connected with the movable plate (2) through a movable plate bearing (21); the eccentric shaft friction force balancing device is characterized in that a protrusion (22) and a groove (111) are arranged between the top of the eccentric shaft (11) and the bottom of the movable disc (2), and the force applied on the movable disc (2) is balanced through the interaction of the protrusion (22) and the groove (111), so that the action point of the friction force between the eccentric shaft (11) and the movable disc (2) is constant.
2. The crankshaft assembly for compressors according to claim 1, characterized in that the side of the moving plate (2) close to the eccentric shaft (11) is formed with a projection (22), and correspondingly the side of the eccentric shaft (11) close to the moving plate (2) is formed with a recess (111); the interaction between the groove (111) and the projection (22) is formed when the crankshaft (1) is rotated.
3. The crankshaft assembly for a compressor according to claim 2, characterized in that the centre line of the lobe (22) is collinear with the centre line of the eccentric shaft (11); the center line of the groove (111) is offset from the center line of the eccentric shaft (11).
4. The crankshaft assembly for a compressor according to claim 2, wherein the centerline of the groove (111) is collinear with the centerline of the crankshaft (1); in the rotation process of the crankshaft (1), the force of the eccentric shaft (11) acting on the movable disc (2) comprises the force of the outer circle of the eccentric shaft (11) acting on the movable disc bearing (21) and the force of the groove (111) acting on the protrusion (22), and the force of the outer circle of the eccentric shaft (11) acting on the movable disc bearing (21) is perpendicular to the force of the groove (111) acting on the protrusion (22).
5. The crankshaft assembly for a compressor according to claim 4, characterized in that the force applied by the outer circle of the eccentric shaft (11) on the movable disc bearing (21) is collinear with the linear velocity direction of the movable disc (2) when the crankshaft (1) drives the movable disc (2) to rotate; the force of the groove (111) acting on the protrusion (22) is perpendicular to the linear velocity direction of the movable disc (2).
6. The crankshaft assembly for compressors according to claim 4, characterized in that the force of the outer circle of the eccentric shaft (11) acting on the movable disc bearing (21) is balanced with the tangential force of the gas acting on the movable disc (2), the force of the groove (111) acting on the protuberance (22) is balanced with the centrifugal force of the movable disc (2), and the point of action of the frictional force between the eccentric shaft (11) and the movable disc (2) is constant.
7. The crankshaft assembly for a compressor according to claim 4, characterized in that when the crankshaft (1) rotates clockwise and the force of the outer circle of the eccentric shaft (11) acting on the movable disc bearing (21) is vertically upward, the force of the groove (111) acting on the protuberance (22) is horizontally rightward; the centrifugal force of the movable disc (2) is horizontally leftwards, and the tangential force of the gas acting on the movable disc (2) is vertically downwards.
8. The crankshaft assembly for a compressor according to claim 1, wherein the place where the protrusion (22) is engaged with the groove (111) is further provided with a rolling bearing (31) or a wear-resistant material.
9. The crankshaft assembly for compressors according to claim 1, characterized in that said reliefs (22) have a height greater than the axial distance between the eccentric shaft (11) and the moving disc (2).
10. A compressor having a crankshaft assembly for a compressor as claimed in any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120480994.7U CN215486452U (en) | 2021-03-05 | 2021-03-05 | Crankshaft assembly for compressor and compressor with crankshaft assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120480994.7U CN215486452U (en) | 2021-03-05 | 2021-03-05 | Crankshaft assembly for compressor and compressor with crankshaft assembly |
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| Publication Number | Publication Date |
|---|---|
| CN215486452U true CN215486452U (en) | 2022-01-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202120480994.7U Active CN215486452U (en) | 2021-03-05 | 2021-03-05 | Crankshaft assembly for compressor and compressor with crankshaft assembly |
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| CN (1) | CN215486452U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112922808A (en) * | 2021-03-05 | 2021-06-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft assembly for compressor and compressor with crankshaft assembly |
-
2021
- 2021-03-05 CN CN202120480994.7U patent/CN215486452U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112922808A (en) * | 2021-03-05 | 2021-06-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft assembly for compressor and compressor with crankshaft assembly |
| CN112922808B (en) * | 2021-03-05 | 2023-12-29 | 珠海格力节能环保制冷技术研究中心有限公司 | A compressor that is used for bent axle subassembly of compressor and has it |
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