CN217539307U - Crankshaft, compressor and refrigeration equipment - Google Patents
Crankshaft, compressor and refrigeration equipment Download PDFInfo
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- CN217539307U CN217539307U CN202221642440.3U CN202221642440U CN217539307U CN 217539307 U CN217539307 U CN 217539307U CN 202221642440 U CN202221642440 U CN 202221642440U CN 217539307 U CN217539307 U CN 217539307U
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Abstract
The utility model discloses a bent axle, compressor and refrigeration plant, the bent axle includes: the oil-saving device comprises a main shaft, a first oil tank and a second oil tank, wherein a main oil duct is formed in the main shaft, a first oil groove is formed in the outer peripheral wall of the main shaft, and the first oil groove is communicated with the main oil duct through a first oil hole; the auxiliary shaft is fixedly connected with the main shaft, and a second oil groove is formed in the peripheral wall of the auxiliary shaft; the outer shaft is fixedly connected with one end, far away from the main shaft, of the auxiliary shaft, and a third oil groove is formed in the outer peripheral wall of the outer shaft; the secondary shaft is offset relative to the primary shaft and the outer shaft, respectively; the first oil groove, the second oil groove and the third oil groove are spirally arranged along a first direction; the second oil groove is communicated with the main oil gallery through a second oil hole, and the third oil groove is communicated with the main oil gallery through a third oil hole. The utility model discloses a make first oil groove, second oil groove and third oil groove all be spiral setting along first direction, the extension corresponds the length of oil groove, promotes the performance of bent axle.
Description
Technical Field
The utility model relates to a compressor field, in particular to bent axle, compressor and refrigeration plant.
Background
The crankshaft is the most important component in a compressor of a refrigerator. The crankshaft is used for bearing the force transmitted by the connecting rod, converting the force into torque output and driving other driven parts on the compressor to work. The crankshaft is subjected to the combined action of centrifugal force of the rotating mass, gas inertia force of periodic variation and reciprocating inertia force, so that the crankshaft is subjected to the action of bending and twisting load.
The surfaces of the crank shaft connected with other driven parts are friction surfaces, and the friction surfaces of the existing crank shaft are not sufficiently lubricated, so that the use performance of the compressor is influenced.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a bent axle, the insufficient problem of friction surface lubrication of aiming at solving current bent axle.
In order to achieve the above object, the utility model provides a crankshaft, include:
the oil-saving device comprises a main shaft, a first oil tank and a second oil tank, wherein a main oil duct is formed in the main shaft, a first oil groove is formed in the outer peripheral wall of the main shaft, and the first oil groove is communicated with the main oil duct through a first oil hole;
the yielding section is fixedly connected with the main shaft;
the auxiliary shaft is fixedly connected with one end, far away from the main shaft, of the abdicating section, and a second oil groove is formed in the outer peripheral wall of the auxiliary shaft; the secondary shaft is offset relative to the primary shaft; the projection of the relief section in the axial direction falls into the projection of the auxiliary shaft in the axial direction; and
the outer shaft is fixedly connected with one end, far away from the main shaft, of the auxiliary shaft, and a third oil groove is formed in the outer peripheral wall of the outer shaft; the secondary shaft is also offset from the outer shaft;
the first oil groove, the second oil groove and the third oil groove are spirally arranged along a first direction; the second oil groove is communicated with the main oil gallery through a second oil hole, and the third oil groove is communicated with the main oil gallery through a third oil hole; and a fourth oil hole is formed in the peripheral wall of the yielding section and communicated with the main oil duct.
In some examples, the first oil groove has a helix angle α 1 Wherein, alpha is more than or equal to 40 degrees 1 Less than or equal to 50 degrees; and/or the helix angle of the second oil groove is alpha 2 Wherein, alpha is more than or equal to 40 degrees 2 Less than or equal to 50 degrees; and/or the helix angle of the third oil groove is alpha 3 Wherein, alpha is more than or equal to 40 degrees 3 ≤50°。
In some examples, the first oil groove extends along the first direction to a side end face of the main shaft facing the auxiliary shaft; the second oil groove extends to one side end face of the auxiliary shaft facing the outer shaft along the first direction.
In some examples, the third oil groove extends in the first direction to an end face of the outer shaft on a side facing away from the countershaft.
In some examples, the crankshaft further comprises:
one end of the oil distribution passage is communicated with the main oil passage and extends towards the outer shaft direction; the second oil groove is communicated with the oil distribution passage through a second oil hole, and the third oil groove is communicated with the oil distribution passage through a third oil hole.
In some examples, an end of the branch oil passage remote from the main oil passage extends to an end face of one side of the outer shaft remote from the main shaft;
the oil distribution channel comprises:
the first oil dividing passage is communicated with the main oil passage and penetrates through the auxiliary shaft, and the second oil groove is communicated with the first oil dividing passage through the second oil hole; and
and the second oil distribution passage is communicated with the main oil passage and sequentially penetrates through the auxiliary shaft and the outer shaft, and the third oil groove is communicated with the second oil distribution passage through the third oil hole.
In some examples, the axis of the first oil distribution passage and the axis of the main shaft form an included angle β 1 Wherein 0 is not more than beta 1 Not more than 5 degrees; and/or the included angle between the axis of the second oil distribution passage and the axis of the main shaft is beta 2 Wherein 0 is not more than beta 2 ≤5°。
In some examples, the main shaft has a first end and a second end which are oppositely arranged, and the auxiliary shaft is fixedly connected with the second end of the main shaft; the first end of the main shaft is provided with an opening communicated with the main oil gallery, and the main oil gallery is provided with a bottom wall facing the first end of the main shaft; the bottom wall is a conical surface or an arc surface protruding towards the direction of the second end of the main shaft, and the first oil distribution passage and the second oil distribution passage extend to the bottom wall respectively.
In some examples, the oil distribution passage further includes:
one end of the third oil dividing passage is communicated with the main oil passage and extends towards the outer shaft direction; the fourth oil hole is communicated with the third oil-dividing passage.
In some examples, an included angle between the axis of the third oil distribution passage and the axis of the main shaft is β 3 Wherein 0 is not more than beta 3 ≤5°。
The utility model discloses on the basis of above-mentioned bent axle, still provide a compressor, the compressor includes as in any one of the above-mentioned example the bent axle, the bent axle first oil groove the second oil groove and the spiral of third oil groove revolve to with the direction of rotation of bent axle is the same.
The utility model discloses on the basis of above-mentioned compressor, still provide a refrigeration plant, refrigeration plant includes like this example the compressor.
The technical proposal of the utility model adopts the auxiliary shaft and the outer shaft to form a double-support crankshaft, and the first oil groove is communicated with the main oil duct to supply oil to the outer wall surface of the main shaft for lubrication; the second oil groove is communicated with the main oil channel through a second oil channel so as to supply oil to the outer wall surface of the auxiliary shaft for lubrication; the third oil groove and the main oil channel are communicated through a third oil channel so as to supply oil to the outer wall surface of the outer shaft for lubrication, and lubrication surfaces are formed on the outer wall surfaces of the main shaft, the auxiliary shaft and the outer shaft; all be spiral setting along first direction through making first oil groove, second oil groove and third oil groove to the length that the extension corresponds the oil groove, with the lubricated face that the increase corresponds the surface, and then promote the lubricating property of each friction surface of bent axle, and then promote bent axle's performance.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
Fig. 1 is a schematic structural view of an embodiment of a crankshaft of the present invention;
FIG. 2 is a left side view of FIG. 1;
FIG. 3 is a sectional view taken along line 2a-2a of FIG. 2;
FIG. 4 is a top view of FIG. 1;
fig. 5 is a schematic structural view of an embodiment of the fourth oil hole of the present invention.
The reference numbers illustrate:
the objects, features and advantages of the present invention will be further described with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
It should be noted that, if directional indications (such as up, down, left, right, front, and back … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative position relationship between the components, the motion situation, etc. in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indications are changed accordingly.
In addition, if there is a description relating to "first", "second", etc. in the embodiments of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the feature. In addition, the technical solutions in the embodiments may be combined with each other, but it must be based on the realization of those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should not be considered to exist, and is not within the protection scope of the present invention.
Referring to fig. 1, the present invention provides a crankshaft, which can be used in a compressor or other situations where a crankshaft is used. The crankshaft includes a main shaft 10, a sub shaft 30, and an outer shaft 40, which are sequentially disposed. The counter shaft 30 is positioned between the main shaft 10 and the outer shaft 40, the counter shaft 30 is offset from the main shaft 10 and the outer shaft 40, and in a cross section perpendicular to the axial direction of the main shaft 10, the axial center of the counter shaft 30 and the axial center of the main shaft 10 are offset from each other, the axial center of the counter shaft 30 and the axial center of the outer shaft 40 are also offset from each other, and the axial center of the outer shaft 40 may overlap with the axial center of the main shaft 10. The outer peripheral walls of the main shaft 10, the auxiliary shaft 30 and the outer shaft 40 may be connected and fixed with the corresponding driven members, respectively, to achieve synchronous movement of the driven members. In some examples, the primary shaft 10, the secondary shaft 30, and the outer shaft 40 may be integrally formed to facilitate the formation of the crankshaft.
Referring to fig. 1, 2 and 3, in some examples, a main oil gallery 11 is formed in a main shaft 10, the main shaft 10 is provided with an opening communicating with the main oil gallery 11, and the opening of the main shaft 10 is communicated with an oil storage groove of an external part of a crankshaft, so as to form a passage for external lubricating oil to enter the crankshaft. The connecting mode of the crankshaft and the oil storage tank of the external part can refer to the crankshaft of the existing compressor, and the description is omitted. A first oil groove 13 is formed in the outer peripheral wall of the main shaft 10, the first oil groove 13 is spirally arranged along a first direction, and the first oil groove 13 is communicated with the main oil gallery 11 through a first oil hole 14. When the crankshaft rotates, the lubricating oil in the oil reservoir enters the main oil gallery 11, and under the action of centrifugal force, the lubricating oil enters the first oil groove 13 through the first oil hole 14 and flows in the first direction along the first oil groove 13, so that the lubricating oil can lubricate the friction surfaces of the main shaft 10 and a driven member connected with the main shaft 10. Because first oil groove 13 is the heliciform along first direction for the area of the friction surface that first oil groove 13 can cover increases, makes the lubricated face of lubricating oil increase, and then can have better lubricated effect.
The first direction in this and the following examples is a helical direction of the corresponding oil groove, such as a counterclockwise direction, a clockwise direction, or the like.
In some examples, the main shaft 10 has a first end and a second end which are oppositely arranged along the axial direction of the main shaft 10, the main oil gallery 11 extends along the axial direction of the main shaft 10, and the opening of the main shaft 10 is arranged on the end face of the first end of the main shaft 10 and can also be arranged on the side wall of the first end of the main shaft 10. The first oil groove 13 has a front end and a rear end that are oppositely disposed, and in some examples, the rear end of the first oil groove 13 is disposed closer to the second end of the main shaft 10, and the first oil hole 14 communicates with the front end of the first oil groove 13. In some examples, a front end of the first oil groove 13 may be disposed near a middle portion of the main shaft 10, or a front end of the first oil groove 13 may be disposed at a portion from the middle portion to the first end of the main shaft 10, and the first oil hole 14 communicates with the front end of the first oil groove 13. The rear end of the first oil groove 13 is located at a portion from the middle to the second end of the main shaft 10. The lubricating oil in the main oil gallery 11 enters the first oil groove 13 via the first oil hole 14 and flows along the first oil groove 13 to lubricate the frictional surfaces of the outer surface of the main shaft 10. Since the opening of the main shaft 10 extends to the first end of the main shaft 10, when the crankshaft rotates, the lubricating oil enters the main oil gallery 11 from the opening of the main shaft 10 and enters the first oil groove 13 along the first oil hole 14. When the crankshaft operates, because the front end of the first oil groove 13 is arranged in the middle of the main shaft 10 or at a position closer to the first end of the main shaft 10, a path for lubricating oil in the main oil gallery 11 to enter the first oil hole 14 is relatively short, the oil amount entering the first oil hole 14 can be effectively increased, the oil amount of the first oil groove 13 can be further increased, and the lubricating effect of the friction surfaces of the main shaft 10 and a driven member connected with the main shaft 10 is improved. Because first oil groove 13 is the heliciform setting, can further increase first oil groove 13's lubricated route's length, further promote lubricated effect.
Further, in some examples, the rear end of the first oil groove 13 extends to the second end of the main shaft 10, so that the first oil groove 13 can be sufficiently supplied with lubricating oil from the front end to the rear end, the excess lubricating oil in the first oil groove 13 can flow to the second end of the main shaft 10, and the excess lubricating oil is thrown out under the action of centrifugal force, so that the friction surface between the main shaft 10 and the driven member of the main shaft 10 is sufficiently lubricated, and the excess lubricating oil is output.
In some examples, the first oil groove 13 extends in a first direction, and in a cross section parallel to the axial direction of the main shaft 10, the first direction makes an angle of less than 90 ° and greater than 0 ° with the axis of the main shaft 10. In some examples, the helix angle of the first oil groove 13 is α 1 Wherein α is 1 Not more than 50 DEG, and alpha 1 Not less than 40. As shown in fig. 2, a straight line perpendicular to the axial direction of the main shaft 10 is a radial line of the main shaft 10, and the helix angle is an included angle between a helix line where the first oil groove 13 is located and the radial line of the main shaft 10. The helix angle of the first oil groove 13 may be any of 41 °, 42 °, 43 °, 44 °, 46 °, 47 °, 48 °, or 50 °. Because the helix angle of the first oil groove 13 is not more than 50 degrees, the problem that the movement resistance of the lubricating oil is increased due to the overlarge helix angle of the first oil groove 13 can be avoided, and then the first oil groove is avoidedThe rear end portion of 13 has a shortage of oil. Because the helix angle of first oil groove 13 is not less than 40 °, the problem that the service performance of the crankshaft compressor is affected by the overlarge oil amount of first oil groove 13 can be effectively prevented.
Further, in some examples, a rear end of the first oil groove 13 extends to a second end of the main shaft 10. Taking the example where the helix angle of the first oil groove 13 is 44 °, the lubricating oil enters the first oil groove 13 from the main oil gallery 11 of the main shaft 10 via the first oil hole 14, and the flow resistance of the lubricating oil in the first oil groove 13 is relatively smaller; the lubricating oil can fully lubricate the friction surface from the front end to the rear end of the first oil groove 13, flows to the second end of the main shaft 10 along the first oil groove 13, and under the action of centrifugal force, the lubricating oil on the surface of the second end of the main shaft 10 can be thrown out towards the outer side of the main shaft 10, so that redundant lubricating oil can enter the oil storage tank again and enter the circulation again.
In some examples, the first oil groove 13 communicates with the main oil gallery 11 through a first oil hole 14, wherein the first oil hole 14 is a straight hole, and the inner diameter of the first oil hole 14 is constant from the first oil groove 13 to the main oil gallery 11. Since the first oil hole 14 is a straight hole, the amount of oil entering the first oil hole 14 can be effectively controlled, and the reduction of the amount of oil in the first oil groove 13 due to the excessive flow resistance when the lubricating oil enters the first oil hole 14 can be prevented.
In some examples, the countershaft 30 has first and second oppositely disposed ends, the first end of the countershaft 30 being fixedly connected with the main shaft 10 and the second end of the countershaft 30 being fixedly connected with the outer shaft 40. The secondary shaft 30 is offset relative to the primary shaft 10. The outer peripheral wall of the counter shaft 30 is provided with a second oil groove 31, the second oil groove 31 is spirally arranged along the first direction, the second oil groove 31 is communicated with the main oil gallery 11 through a second oil hole 32, and the second oil groove 31 forms a lubricating oil conveying passage for lubricating oil to flow between the counter shaft 30 and a friction surface of a driven member of the counter shaft 30. The second oil groove 31 has a front end and a rear end, and the rear end of the second oil groove 31 is disposed closer to the second end of the countershaft 30. In some examples, the second oil hole 32 communicates with the front end of the second oil groove 31 to allow the lubricating oil to flow from the front end of the second oil groove 31 to the rear end of the second oil groove 31. In some examples, the front end of the second oil groove 31 may be located in the middle of the counter shaft 30, and further, the front end of the second oil groove 31 may be disposed closer to the first end of the counter shaft 30, so that the flow path of the second oil groove 31 on the outer peripheral wall of the counter shaft 30 is extended, and thus the area of the lubricating surface of the lubricating oil on the counter shaft 30 may be increased, the lubricating effect is improved, and further, in combination with the spiral extension of the second oil groove 31, the total length of the second oil groove 31 may be extended, and the lubricating surface is effectively increased. When the front end of the second oil groove 31 is closer to the first end of the counter shaft 30, the path of the lubricating oil when entering the second oil hole 32 from the main oil gallery 11 is relatively shortened, enabling the amount of the lubricating oil entering the second oil groove 31 to be effectively increased.
Further, in some examples, the rear end of the second oil groove 31 extends to the second end of the countershaft 30, so that the second oil groove 31 can be sufficiently supplied with lubricating oil from the front end to the rear end, the excess lubricating oil in the second oil groove 31 can flow to the second end of the countershaft 30, the excess lubricating oil is thrown out under the action of centrifugal force, and the excess lubricating oil is output and recycled while the friction surface between the driven member of the countershaft 30 and the driven member of the countershaft 30 is sufficiently lubricated.
In some examples, the second oil groove 31 is spirally arranged in a first direction, and in a cross section parallel to the axial direction of the counter shaft 30, the first direction makes an angle of less than 90 ° and more than 0 ° with the axial line of the counter shaft 30. In some examples, the helix angle of the second oil groove 31 is α 2 Wherein α is 2 Not more than 50 DEG, and alpha 2 Not less than 40. As shown in fig. 2, a straight line perpendicular to the axial direction of the auxiliary shaft 30 is a radial line of the auxiliary shaft 30, and the helix angle is an angle between a helix line in which the second oil groove 31 is located and the radial line of the auxiliary shaft 30. The helix angle of the second oil groove 31 may be any of 40 °, 42 °, 43 °, 44 °, 46 °, 47 °, 49 °, or 50 °. Because the helix angle of second oil groove 31 does not exceed 50, can avoid the too big problem that causes of lubricating oil removal resistance increase of helix angle of second oil groove 31, and then avoid the rear end position oil mass of second oil groove 31 not enough. Because the helix angle of second oil groove 31 is not less than 40 °, the problem that the service performance of the crankshaft compressor is affected by the overlarge oil amount of second oil groove 31 can be effectively prevented. Further, in some examples, the rear end of the second oil groove 31 extends to the countershaft 30 and the helix angle of the second oil groove 31 is alpha 2 Wherein α is 2 Not more than 50 DEG, and alpha 2 Not less than 40. Taking the example where the helix angle of the second oil groove 31 is 46 °, the lubricating oil enters the second oil groove 31 from the main oil passage 11 via the second oil holes 32, and the flow resistance of the lubricating oil in the second oil groove 31 is relatively smaller; the lubricating oil can sufficiently lubricate the friction surfaces from the front end to the rear end of the second oil groove 31, flows to the second end of the auxiliary shaft 30 along the second oil groove 31, and under the action of centrifugal force, the lubricating oil on the surface of the second end of the auxiliary shaft 30 can be thrown out to the outer side of the auxiliary shaft 30, so that redundant lubricating oil can enter the oil storage groove again and enter the circulation again. In some examples, the helix angles of first oil groove 13 and second oil groove 31 are equal.
In some examples, the second oil groove 31 communicates with the main oil gallery 11 through a second oil hole 32, wherein the second oil hole 32 is a straight hole, and the inner diameter of the second oil hole 32 is constant from the second oil groove 31 to the main oil gallery 11. Since the second oil holes 32 are straight holes, the amount of oil entering the second oil holes 32 can be effectively controlled, and the reduction of the amount of oil in the second oil groove 31 due to the excessive flow resistance when the lubricating oil enters the second oil holes 32 can be prevented. Because the inner diameter of the second oil hole 32 is not changed, the flow area of the lubricating oil flowing in the second oil hole 32 is not changed, and thus the problems of vortex and the like generated in the second oil hole 32 by the lubricating oil can be avoided, and the flow rate of the lubricating oil in the second oil hole 32 can be controlled.
In some examples, an end of the secondary shaft 30 remote from the primary shaft 10 is provided with an outer shaft 40, and the outer shaft 40 may be integrally formed with the secondary shaft 30 and the primary shaft 10. A third oil groove 41 is formed in the outer peripheral wall of the outer shaft 40, and the third oil groove 41 is spirally arranged along the first direction. The outer shaft 40 has first and second oppositely disposed ends, with the first end of the outer shaft 40 being connected to the second end of the countershaft 30. The third oil groove 41 is used for conveying lubricating oil to the friction surfaces between the outer shaft 40 and the driven member of the outer shaft 40, and the third oil groove 41 is spirally arranged, so that the length of the third oil groove 41 can be effectively prolonged, the flow path of the lubricating oil on the friction surfaces between the outer shaft 40 and the driven member of the outer shaft 40 is prolonged, the lubricating surface is increased, and the lubricating effect is improved.
The third oil groove 41 has a front end and a rear end, and the rear end of the third oil groove 41 is disposed closer to the second end of the outer shaft 40. In some examples, the third oil holes 42 communicate with the front end of the third oil groove 41 to enable the lubricating oil to flow from the front end of the third oil groove 41 to the rear end of the third oil groove 41.
In some examples, the front end of the third oil groove 41 is disposed near the middle of the outer shaft 40, and further, the front end of the third oil groove 41 may be disposed near the first end of the outer shaft 40, so that the flow path of the third oil groove 41 on the outer circumferential wall of the outer shaft 40 is extended, and thus the area of the lubricating surface of the lubricating oil on the outer shaft 40 may be increased, the lubricating effect is improved, and further, the third oil groove 41 is spirally extended, so that the total length of the third oil groove 41 can be extended, and the lubricating surface is effectively increased. When the front end of the third oil groove 41 is closer to the first end of the outer shaft 40, the path of the lubricating oil when entering the third oil hole 42 from the main oil gallery 11 is relatively shortened, enabling the amount of lubricating oil entering the third oil groove 41 to be effectively increased.
Further, in some examples, the rear end of the third oil groove 41 extends to the second end of the outer shaft 40, so that the third oil groove 41 can be sufficiently supplied with lubricating oil from the front end to the rear end, the excess lubricating oil in the third oil groove 41 can flow to the second end of the outer shaft 40, the excess lubricating oil is thrown out under the action of centrifugal force, and the excess lubricating oil is output and recycled while the friction surface between the outer shaft 40 and the driven member of the outer shaft 40 is sufficiently lubricated.
In some examples, the third oil groove 41 extends in a first direction that makes an angle of less than 90 ° and greater than 0 ° with the axis of the counter shaft 30 in a cross section parallel to the axial direction of the outer shaft 40. In some examples, the helix angle of the third oil groove 41 is α 3 Wherein α is 3 Not more than 50 DEG, and alpha 3 Not less than 40. As shown in fig. 2, a straight line perpendicular to the axial direction of the auxiliary shaft 30 is a radial line of the auxiliary shaft 30, and the helix angle is an angle between a helix line in which the third oil groove 41 is located and the radial line of the auxiliary shaft 30. The helix angle of the third oil groove 41 may be any of 40 °, 41 °, 42 °, 43 °, 44 °, 45 °, 46 °, 47 °, 48 °, 49 °, or 50 °. Due to the spiral of the third oil groove 41The lead angle does not exceed 50 °, so that the problem of increase in the movement resistance of the lubricating oil due to an excessively large lead angle of the third oil groove 41 can be avoided, and further, the shortage of the oil amount at the rear end part of the third oil groove 41 can be avoided. Because the helix angle of the third oil groove 41 is not less than 40 degrees, the problem that the service performance of the crankshaft compressor is influenced by the overlarge oil amount of the third oil groove 41 can be effectively prevented, the processing area of the outer wall surface of the outer shaft 40 can be further reduced, and the connection performance between the outer shaft 40 and the driven part of the outer shaft 40 is improved.
Further, in some examples, a rear end of the third oil groove 41 extends to a second end of the outer shaft 40, and a helix angle of the third oil groove 41 is α 3 Wherein α is 3 Not more than 50 DEG, and alpha 3 Not less than 40. Taking the example where the helix angle of the third oil groove 41 is 47 °, the lubricating oil enters the third oil groove 41 from the main oil gallery 11 via the third oil holes 42, and the flow resistance of the lubricating oil in the third oil groove 41 is relatively smaller; the lubricating oil can fully lubricate the friction surfaces from the front end to the rear end of the third oil groove 41, flows to the second end of the outer shaft 40 along the third oil groove 41, and under the action of centrifugal force, the lubricating oil on the surface of the second end of the outer shaft 40 can be thrown out to the outer side of the outer shaft 40, so that the redundant lubricating oil can enter the oil storage tank again and enter the circulation again. In some examples, the helix angles of first oil groove 13, second oil groove 31, and third oil groove 41 are equal.
In some examples, the third oil groove 41 communicates with the main oil gallery 11 through a third oil hole 42, wherein the third oil hole 42 is a straight hole, and the inner diameter of the third oil hole 42 is constant from the third oil groove 41 to the main oil gallery 11. Since the third oil hole 42 is a straight hole, the amount of oil entering the third oil hole 42 can be effectively controlled, and the reduction of the amount of oil in the third oil groove 41 due to the excessive flow resistance when lubricating oil enters the third oil hole 42 can be prevented. Because the inner diameter of the third oil hole 42 is not changed, the flow area of the lubricating oil flowing in the third oil hole 42 is not changed, so that the problems of the lubricating oil such as vortex generation in the third oil hole 42 can be avoided, and the flow rate of the lubricating oil in the third oil hole 42 can be controlled.
Further, in some examples, the inner diameters of the first, second, and third oil holes 14, 32, 42 are equal. In some examples, the inner diameters of the first, second, and third oil holes 14, 32, 42 sequentially increase. In some examples, the lengths of the first, second, and third oil holes 14, 32, and 42 increase incrementally.
Referring to fig. 1 and 3, in some examples, the crankshaft further includes an oil distribution passage 50, the oil distribution passage 50 penetrates the auxiliary shaft 30 and the outer shaft 40, and one end of the oil distribution passage 50 communicates with the main oil passage 11 and extends toward the outer shaft 40. The second oil groove 31 communicates with the branch oil passage 50 through the second oil hole 32, so that the lubricating oil in the main oil passage 11 can enter the second oil groove 31 via the branch oil passage 50. The third oil groove 41 communicates with the oil-dividing passage 50 through the third oil hole 42, so that the lubricating oil in the main oil passage 11 can enter the third oil groove 41 via the oil-dividing passage 50.
By providing the branch oil passage 50, a passage extending in the direction toward the outer shaft 40 can be formed so that the lubricating oil in the main oil passage 11 can more easily enter the second oil groove 31 and the third oil groove 41. The main oil gallery 11 is communicated by separately providing the oil distribution gallery 50, so that the inner diameters of the main oil gallery 11 and the oil distribution gallery 50 can be preset according to the requirement of the lubricating oil amount, and the oil amounts of the main oil gallery 11 and the oil distribution gallery 50 can be further controlled. In some examples, the second and third oil holes 32 and 42 may be straight holes disposed in a radial direction of the crankshaft, and the second and third oil holes 32 and 42 communicate with the branch oil passages 50, respectively, so that the holes may be conveniently bored.
Since the outer shaft 40 is disposed at an end of the auxiliary shaft 30 away from the main shaft 10, in some examples, an end of the oil distribution passage 50 away from the main oil passage 11 extends to an end of the outer shaft 40 away from the auxiliary shaft 30, which may help control the amount of oil in the oil distribution passage 50 and prevent the amount of lubricating oil at the position of the outer shaft 40 from being reduced. Because the excessive lubricating oil in the oil distribution passage 50 can flow to the side of the outer shaft 40 away from the auxiliary shaft 30, the excessive lubricating oil is thrown out under the action of centrifugal force during the rotation of the crankshaft and can enter into circulation again.
Referring to fig. 3, in some examples, the main shaft 10 has a first end and a second end opposite to each other, and the auxiliary shaft 30 is fixedly connected to the second end of the main shaft 10; a first end of the main shaft 10 is provided with an opening communicated with the main oil gallery 11, the main oil gallery 11 is provided with a bottom wall 12, the bottom wall 12 is arranged towards the first end of the main shaft 10, and specifically, the bottom wall 12 can be arranged towards the opening; inside the main shaft 10 as shown in fig. 3, the first end of the main shaft 10 forms an opening, which may be provided on the end surface of the first end of the main shaft 10 as shown in fig. 3, or may be provided on a side wall of the first end of the main shaft 10, and the lubricating oil in the oil reservoir enters the main oil gallery 11 through the opening, and the branch oil gallery 50 extends to the bottom wall 12 of the main oil gallery 11. Further, in some examples, the bottom wall 12 is a conical surface or an arc surface protruding toward the second end of the main shaft 10, the lubricating oil enters the main oil gallery 11 from the opening and flows along the main oil gallery 11 toward the bottom wall 12, and when the position of the bottom wall 12 is reached, the lubricating oil enters the branch oil gallery 50 along the conical surface or the arc surface formed by the bottom wall 12, so that the lubricating oil can be prevented from generating eddy currents at the position of the bottom wall 12 of the main oil gallery 11, and the amount of the lubricating oil entering the branch oil gallery 50 can be increased. In order to make the lubricant oil smoothly flow toward the bottom wall 12, in some examples, the main oil gallery 11 is a channel with a circular cross section, the lubricant oil flows along the inner wall surface of the main oil gallery 11 under the action of centrifugal force, and a smooth and continuous guide surface is formed by the circular inner wall surface of the main oil gallery 11, so that the flow direction of the lubricant oil is prevented from changing suddenly during the flow process, the lubricant oil is continuously conveyed, the supply amount of the lubricant oil is stabilized, and the flow resistance of the lubricant oil is reduced.
Further, in some examples, the oil dividing passage 50 includes a first oil dividing passage 51 and a second oil dividing passage 52, wherein one end of the first oil dividing passage 51 communicates with the main oil passage 11 and penetrates the counter shaft 30, and the second oil groove 31 communicates with the first oil dividing passage 51 through the second oil hole 32. One end of the second oil distribution passage 52 communicates with the main oil passage 11, and sequentially passes through the counter shaft 30 and the outer shaft 40, and the third oil groove 41 communicates with the second oil distribution passage 52 through the third oil hole 42. The second oil groove 31 and the third oil groove 41 are respectively communicated with the main oil gallery 11 through the corresponding oil dividing passages 50, and further, passages with different inner diameters can be selected as the second oil dividing passage 52 and the third oil dividing passage 53 as required, so that the oil supply amount of the second oil groove 31 and the third oil groove 41 can meet the preset requirement. Since the outer shaft 40 is disposed away from the main oil gallery 11, when the inner diameters of the third and second oil holes 42 and 32 are equal, the inner diameter of the second branch oil gallery 52 may be increased to increase the amount of lubricating oil entering the second branch oil gallery 52 to maintain the amount of lubricating oil entering the third oil hole 42 at a preset level.
In some examples, the first oil distribution passage 51 and/or the second oil distribution passage 52 are passages having a circular cross-section to reduce the flow resistance of the lubricating oil and maintain a continuous supply of the lubricating oil.
Further, on the basis of the above example, the angle between the axis of the first oil gallery 51 and the axis of the main shaft 10 is β 1 Wherein 0 is not more than beta 1 Not more than 5 degrees, when beta 1 When =0, the axis of the first sub-oil passage 51 is arranged in parallel with the axis of the main oil passage 11 when β 1 When =5 °, the axis of the first sub-oil gallery 51 is inclined at an angle to the axis of the main oil gallery 11.
Further, in some examples, the axis of the second oil distribution passage 52 and the axis of the main shaft 10 form an included angle β 2 Wherein 0 is not more than beta 2 Not more than 5 degrees, when beta 2 =0, the axis of the second branch oil gallery 52 is arranged in parallel with the axis of the main oil gallery 11, when β 2 When the angle is 5 °, the axis of the second branch oil gallery 52 is inclined at a certain angle to the axis of the main oil gallery 11.
By defining beta 1 And beta 2 When the first oil distribution passage 51 and the second oil distribution passage 52 are machined, the first oil distribution passage 51 and the second oil distribution passage 52 can be ensured to be within a certain error range, and the hole drilling machining is facilitated.
Further, in some examples, the outer shaft 40 has a first end connected with the countershaft 30 and a second end far away from the countershaft 30, one ends of the first oil distribution passage 51 and the second oil distribution passage 52 far away from the main oil passage 11 extend to the second end of the outer shaft 40, so that a passage for lubricating oil to flow is formed in the first oil distribution passage 51 and the second oil distribution passage 52, excessive lubricating oil in the first oil distribution passage 51 and the second oil distribution passage 52 can flow to the second end of the outer shaft 40, and the excessive lubricating oil can be thrown out under the action of centrifugal force and enter the circulation again. By making 0 ≦ beta 1 ≤5°，0≤β 2 Be less than or equal to 5, can make things convenient for the processing of first branch oil duct 51 and second branch oil duct 52, when the trompil, make first branch oil duct 51 and second branch oil duct 52 extend to the diapire 12 of main oil gallery 11 from the second end of outer axle 40, reduce the error of trompil processing.
Further, in some examples, the main oil gallery 11 has the bottom wall 12 described in the above examples, and the first and second branch oil galleries 51, 52 extend to the bottom wall 12 of the main oil gallery 11 to enable lubricating oil to enter the first and second branch oil galleries 51, 52 along the bottom wall 12.
Referring to fig. 1 and 4, in some examples, the crankshaft further includes a relief section 20, wherein the relief section 20 is located between the main shaft 10 and a secondary shaft 30, and the secondary shaft 30 is connected to the main shaft 10 through the relief section 20. In some examples, the primary shaft 10, the relief section 20, the secondary shaft 30, and the outer shaft 40 are integrally formed when the crankshaft is manufactured.
Further, in some examples, a projection of the abduction section 20 in the axial direction falls within a projection of the secondary shaft 30 in the axial direction. The abdicating section 20 and the secondary shaft 30 are located within the secondary shaft 30 in a projection of a cross section perpendicular to the axis of the secondary shaft 30.
In some examples, a fourth oil hole 21 is opened in the outer circumferential wall of the relief section 20, and the fourth oil hole 21 communicates with the main oil gallery 11 to supply oil to the relief section 20. Further, in some examples, the fourth oil hole 21 is a straight hole to facilitate control of the amount of oil of the fourth oil hole 21 and to facilitate the tapping process. In some examples, the inner diameter of the fourth oil hole 21 is equal to the inner diameter of the first oil hole. In some examples, the first, fourth, second, and third oil holes have successively increasing inner diameters.
In some examples, the crankshaft is opened with a third oil branch passage 53, the third oil branch passage 53 communicates with the main oil passage 11, and the fourth oil hole 21 communicates with the third oil branch passage 53, so that the lubricating oil of the main oil passage 11 reaches the outer peripheral wall of the relief section 20 via the third oil branch passage 53 and the fourth oil hole 21. When the third oil dividing passage 53 is manufactured, the third oil dividing passage 53 may sequentially penetrate through the relief section 20, the auxiliary shaft 30 and the outer shaft 40 and extend to one side end face of the outer shaft 40 far away from the auxiliary shaft 30, when the oil amount in the third oil dividing passage 53 reaches the preset oil amount, when excessive lubricating oil exists in the third oil dividing passage 53, the excessive lubricating oil may flow to one side of the outer shaft 40 far away from the auxiliary shaft 30 and enter the circulation again after being thrown out under the action of centrifugal force. In some examples, the third oil distribution passage 53 extends to the bottom wall 12 of the main oil passage 11, so that the lubricating oil can flow into the third oil distribution passage 53 along the tapered surface or the arc surface formed by the bottom wall 12, and the flow resistance of the lubricating oil can be reduced.
In some examples, the axis of the third oil distribution passage 53 forms an angle β with the axis of the main shaft 10 3 Wherein 0 is not more than beta 3 Is less than or equal to 5 degrees so as to facilitate the hole opening and simultaneously facilitate the communication between the third oil-dividing passage 53 and the preset position in the main oil passage 11. In some examples, the first oil distribution passage, the second oil distribution passage, and the third oil distribution passage have equal inner diameters. In some examples, the first, fourth, second, and third oil holes have equal inner diameters, and the third, first, and second oil branch passages have successively increasing inner diameters.
In some examples, the present invention further provides a compressor, which includes the crankshaft in any one of the above examples, wherein the spiral direction of the first oil groove 13, the second oil groove 31 and the third oil groove 41 of the crankshaft is the same as the rotation direction of the crankshaft, so that when the crankshaft rotates, under the action of centrifugal force, the lubricating oil can flow along the first oil groove 13, the second oil groove 31 and the third oil groove 41, and further the lubricating oil can be supplied to the main shaft 10, the auxiliary shaft 30 and the outer shaft 40. In some examples, the compressor further includes other functional structures, such as a driven part connected to the crankshaft, a housing, etc., which are referred to in the prior art and will not be described in detail.
In some examples, a threaded hole 60 is formed in an end of the outer shaft 40 remote from the auxiliary shaft 30 for connecting and fixing the crankshaft with other functional components.
In some examples, a locating hole 70 is formed in the end of the outer shaft 40 remote from the auxiliary shaft 30 to facilitate location and installation.
It is worth noting, because the utility model discloses a compressor is based on the example of above-mentioned bent axle, consequently, the utility model discloses the example of compressor includes all technical scheme of the whole examples of above-mentioned bent axle, and the technological effect that reaches is also identical, no longer explains here.
In some examples, the present invention also proposes a refrigeration device comprising a compressor as described in the above examples. The refrigerating equipment can be a refrigerator or other equipment with a refrigerating function. In some examples, the refrigeration device may further include other functional modules, which may refer to the prior art and are not described in detail. It is worth noting, because the utility model discloses an example of refrigeration plant based on above-mentioned bent axle, consequently, the utility model discloses refrigeration plant's example includes all technical scheme of the whole examples of above-mentioned compressor, and the technological effect that reaches is also identical, and is not repeated here.
The above only is the preferred embodiment of the present invention, not limiting the scope of the present invention, all the equivalent structure changes made by the contents of the specification and the drawings under the inventive concept of the present invention, or the direct/indirect application in other related technical fields are included in the patent protection scope of the present invention.
Claims (12)
1. A crankshaft, comprising:
the oil-saving device comprises a main shaft, a first oil tank and a second oil tank, wherein a main oil duct is formed in the main shaft, a first oil groove is formed in the outer peripheral wall of the main shaft, and the first oil groove is communicated with the main oil duct through a first oil hole;
the yielding section is fixedly connected with the main shaft;
the auxiliary shaft is fixedly connected with one end, far away from the main shaft, of the abdicating section, and a second oil groove is formed in the outer peripheral wall of the auxiliary shaft; the secondary shaft is offset relative to the primary shaft; the projection of the position-giving section in the axial direction falls into the projection of the auxiliary shaft in the axial direction; and
the outer shaft is fixedly connected with one end, far away from the main shaft, of the auxiliary shaft, and a third oil groove is formed in the outer peripheral wall of the outer shaft; the secondary shaft is also offset from the outer shaft;
the first oil groove, the second oil groove and the third oil groove are spirally arranged along a first direction; the second oil groove is communicated with the main oil gallery through a second oil hole, and the third oil groove is communicated with the main oil gallery through a third oil hole; and a fourth oil hole is formed in the peripheral wall of the yielding section and communicated with the main oil duct.
2. The crankshaft of claim 1 wherein said first channel has a lead angle α 1 Wherein, alpha is more than or equal to 40 degrees 1 Less than or equal to 50 degrees; and/or the helix angle of the second oil groove is alpha 2 Wherein, alpha is more than or equal to 40 degrees 2 Less than or equal to 50 degrees; and/or the helix angle of the third oil groove is alpha 3 Wherein, alpha is more than or equal to 40 degrees 3 ≤50°。
3. The crankshaft of claim 1 wherein said first oil channel extends in said first direction to a side end face of said main shaft facing said auxiliary shaft; the second oil groove extends to one side end face of the auxiliary shaft facing the outer shaft along the first direction.
4. The crankshaft of claim 1 wherein said third oil groove extends in said first direction to an end surface of said outer shaft on a side facing away from said countershaft.
5. The crankshaft of claim 1, further comprising:
one end of the oil distribution passage is communicated with the main oil passage and extends towards the outer shaft direction; the second oil groove is communicated with the oil distribution passage through a second oil hole, and the third oil groove is communicated with the oil distribution passage through a third oil hole.
6. The crankshaft of claim 5,
one end of the oil distribution passage, which is far away from the main oil passage, extends to the end face of one side of the outer shaft, which is far away from the main shaft;
the oil distribution channel comprises:
the first oil distributing passage is communicated with the main oil distributing passage and penetrates through the auxiliary shaft, and the second oil groove is communicated with the first oil distributing passage through the second oil hole; and
and the second oil distribution passage is communicated with the main oil passage and sequentially penetrates through the auxiliary shaft and the outer shaft, and the third oil groove is communicated with the second oil distribution passage through the third oil hole.
7. The crankshaft of claim 6, wherein the axis of the first oil distribution passage and the axis of the main shaft form an angle β 1 Wherein 0 is not more than beta 1 Not more than 5 degrees; and/or the included angle between the axis of the second oil distribution passage and the axis of the main shaft is beta 2 Wherein 0 is not more than beta 2 ≤5°。
8. The crankshaft of claim 6 wherein said primary shaft has a first end and a second end disposed opposite one another, said secondary shaft fixedly connected to said second end of said primary shaft; the first end of the main shaft is provided with an opening communicated with the main oil duct, and the main oil duct is provided with a bottom wall facing the first end of the main shaft; the bottom wall is a conical surface or an arc surface protruding towards the direction of the second end of the main shaft, and the first oil distribution passage and the second oil distribution passage extend to the bottom wall respectively.
9. The crankshaft of claim 5 or 6, wherein the branch oil gallery further comprises:
one end of the third oil dividing passage is communicated with the main oil passage and extends towards the outer shaft direction; the fourth oil hole is communicated with the third oil-dividing passage.
10. The crankshaft of claim 9, wherein the axis of the third oil distribution channel forms an angle β with the axis of the main shaft 3 Wherein, 0 is less than or equal to beta 3 ≤5°。
11. A compressor comprising a crankshaft according to any one of claims 1 to 10, wherein the first oil groove, the second oil groove, and the third oil groove of the crankshaft have the same spiral direction as the rotation direction of the crankshaft.
12. A refrigeration appliance, characterized in that it comprises a compressor as claimed in claim 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221642440.3U CN217539307U (en) | 2022-06-28 | 2022-06-28 | Crankshaft, compressor and refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221642440.3U CN217539307U (en) | 2022-06-28 | 2022-06-28 | Crankshaft, compressor and refrigeration equipment |
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| Publication Number | Publication Date |
|---|---|
| CN217539307U true CN217539307U (en) | 2022-10-04 |
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|---|---|---|---|
| CN202221642440.3U Active CN217539307U (en) | 2022-06-28 | 2022-06-28 | Crankshaft, compressor and refrigeration equipment |
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| Country | Link |
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| CN (1) | CN217539307U (en) |
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2022
- 2022-06-28 CN CN202221642440.3U patent/CN217539307U/en active Active
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