Crankshaft structure and rolling piston compressor

Abstract

The application provides a crankshaft structure and a rolling rotor compressor. The crankshaft structure comprises a shaft body and a roller. A first matching part is arranged on the outer peripheral wall of the shaft body. The roller comprises a ring body and a transmission part. A preset shaft around the ring body is parallel to the central axis of the shaft body. The first end of the transmission part is connected with the inner wall of the ring body. The second end of the transmission part is provided with a second matching part. When the first matching part is a groove, the second matching part is a protruding part, and the protruding part is located in the groove. When the second matching part is a groove, the first matching part is a part of the shaft segment of the shaft body, and the first matching part is located in the groove. The first matching part has a first matching side surface, and the second matching part has a second matching side surface. When the shaft body rotates, the first matching side surface and the second matching side surface abut, so that the shaft body drives the transmission part to rotate. The crankshaft structure solves the problem that the deflection of the crankshaft is large due to the arrangement of the balance block in the prior art.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressor, in particular to a crankshaft structure and a rolling rotor compressor. BACKGROUND

[0002] In order to reduce material cost, reduce the space occupied by the compressor, and ensure the refrigerating capacity of the compressor, the current compressor develops towards high speed and miniaturization. However, the reduction of the diameter of the crankshaft of the compressor means the reduction of the rigidity, and the increase of the speed will cause the crankshaft to be affected by a larger centrifugal force. Therefore, one problem faced by the miniaturized and high-speed compressor is that the deflection of the crankshaft is large, and the stress, vibration and noise thereof will be affected. The large deflection of the crankshaft is a common problem in the direction of miniaturization and high speed of the compressor. SUMMARY

[0003] The main purpose of the present application is to provide a crankshaft structure and a rolling rotor compressor to solve the problem of large deflection of the crankshaft caused by the balance block in the prior art.

[0004] In order to achieve the above-mentioned purpose, according to one aspect of the present application, a crankshaft structure is provided, which comprises: a shaft body, a first matching part is arranged on the outer peripheral wall of the shaft body; a roller, the roller comprises a ring body and a transmission part, the ring body is arranged around a predetermined axis, the predetermined axis is parallel to the central axis of the shaft body; along the radial direction of the ring body, the transmission part has oppositely arranged first and second ends; the first end of the transmission part is connected with the inner wall of the ring body; the second end of the transmission part is provided with a second matching part; wherein one of the first matching part and the second matching part is a groove; when the first matching part is the groove, the second matching part is a protruding part, and the protruding part is located in the groove; when the second matching part is the groove, the first matching part is a part of the shaft segment of the shaft body, and the first matching part is located in the groove; the first matching part has a first matching side surface, and the second matching part has a second matching side surface, so that when the shaft body rotates, the first matching side surface and the second matching side surface abut, and the shaft body drives the transmission part to rotate.

[0005] Further, the groove has two oppositely arranged specified groove side walls, one of the two specified groove side walls forms the first matching side surface or the second matching side surface; when the second matching part is the protruding part, the protruding part has two oppositely arranged specified outer side walls, one of the two specified outer side walls forms the second matching side surface; when the first matching part is the part of the shaft segment of the shaft body, the outer peripheral wall surface of the part of the shaft segment of the shaft body forms the first matching side surface.

[0006] Further, when the second matching part is the groove, the shaft body comprises a predetermined shaft segment, the predetermined shaft segment is the first matching part; at least part of the outer peripheral wall of the predetermined shaft segment is recessed to form a recess; the predetermined shaft segment is located in the groove.

[0007] Further, the outer peripheral wall of the preset shaft section comprises two oppositely arranged first side surfaces, one of the two first side surfaces forms a first matching side surface; the groove has two oppositely arranged specified groove side walls, one of the two specified groove side walls forms a second matching side surface.

[0008] Further, the shaft body has a central through hole; when the shaft body is provided with one first matching part, the roller is one; when the shaft body is provided with a plurality of first matching parts arranged along the axial direction of the shaft body, the plurality of rollers are arranged in one-to-one correspondence with the plurality of first matching parts; at least part of the plurality of first matching parts is distributed along the circumferential direction of the shaft body; when the shaft body has an eccentric mass, at least one balance oil hole is arranged on the outer peripheral wall of the shaft body, the balance oil hole is in communication with the central through hole of the shaft body, so as to reduce the eccentric mass of the shaft body or make the shaft body not have the eccentric mass.

[0009] Further, the shaft body is provided with a balance hole group, the balance hole group comprises one or a plurality of balance oil holes distributed along the axial direction of the shaft body; when the first matching part is a groove or a recess formed therein, each first matching part is arranged in correspondence with a balance hole group.

[0010] Further, when the first matching part is a groove, along the radial direction of the shaft body, each first matching part and the corresponding balance hole group are respectively located on opposite sides of the shaft body.

[0011] Further, when the shaft body is provided with a plurality of first matching parts which are grooves or recesses formed therein, among the plurality of first matching parts which are grooves or recesses formed therein, along the radial direction of the shaft body, any two adjacent first matching parts are respectively located on opposite sides of the shaft body.

[0012] Further, from the first end to the second end of the transmission member, the cross section of the transmission member gradually decreases; wherein the cross section of the transmission member is parallel to the preset axis, and the cross section of the transmission member is perpendicular to the distribution direction of the first end and the second end of the transmission member.

[0013] Further, the transmission member has two oppositely arranged inclined side surfaces, the distribution direction of the two inclined side surfaces of the transmission member is perpendicular to the distribution direction of the first end and the second end of the transmission member, and the distribution direction of the two inclined side surfaces of the transmission member is perpendicular to the axial direction of the shaft body; from the first end to the second end of the transmission member, each inclined side surface of the transmission member gradually approaches the other inclined side surface.

[0014] Further, when the second matching part is a protruding part, the transmission member and the protruding part are an integral structure; or the crank structure further comprises a connecting key, the second end of the transmission member is provided with a connecting groove, a part of the connecting key is clamped in the connecting groove, and another part of the connecting key is located outside the connecting groove to form the protruding part.

[0015] Further, the transmission member and the ring body are integrally formed; or, the inner wall of the ring body is provided with an annular groove arranged around the preset axis, and the first end of the transmission member is slidably arranged in the annular groove, so that the transmission member drives the ring body to rotate when the shaft body drives the transmission member to rotate, and the transmission member and the ring body can relatively rotate.

[0016] Further, the inner wall of the ring body has a preset position; the preset position is a position along the circumferential direction of the ring body, and the vertical distance between the inner wall of the ring body and the second end of the transmission member is the smallest; the vertical distance between the preset position and the outer peripheral wall of the shaft body is H1; when the first matching part is a groove, the groove depth of the first matching part is H2, and the groove depth direction of the first matching part is perpendicular to the axial direction of the shaft body; and H1>H2.

[0017] Further, the roller is arranged to be rotatable in the cylinder cavity of the cylinder, and the central axis of the cylinder cavity coincides with the central axis of the shaft body; the minimum vertical distance between the outer peripheral wall of the ring body and the cavity wall of the cylinder cavity is H3; the inner wall of the ring body has a preset position; the preset position is a position along the circumferential direction of the ring body, and the vertical distance between the inner wall of the ring body and the second end of the transmission member is the smallest; the vertical distance between the preset position and the outer peripheral wall of the shaft body is H1; and H1>H3.

[0018] According to another aspect of the present application, a rolling rotor type compressor is provided, which comprises a cylinder and the above-mentioned crankshaft structure.

[0019] In the crankshaft structure provided by the present application, the crankshaft structure comprises a shaft body and a roller; the shaft body is arranged to be rotatable around a central axis thereof; the outer peripheral wall of the shaft body is provided with a first matching part; the roller comprises a ring body and a transmission member, the ring body is arranged around a preset axis, and the preset axis is parallel to the central axis of the shaft body; along the radial direction of the ring body, the transmission member has oppositely arranged first and second ends; the first end of the transmission member is connected to the inner wall of the ring body; and the second end of the transmission member is provided with a second matching part. One of the first matching part and the second matching part is a groove.

[0020] The first matching part and the second matching part have a first arrangement form: the first matching part is a groove, and the second matching part is a protruding part which is located in the groove. It should be noted that when the protruding part is located in the groove, the protruding part is not tightly clamped in the groove, but is only placed in the groove.

[0021] The first matching part and the second matching part have a second arrangement form: the second matching part is a groove, and the first matching part is a part of the shaft segment of the shaft body in the axial direction thereof, and the first matching part is located in the groove, i.e. the shaft body is located in the groove. It should be noted that when the first matching part is located in the groove, the shaft body is not tightly clamped in the groove, but is only placed in the groove.

[0022] The first matching part has a first matching side surface, and the second matching part has a second matching side surface; when the shaft body rotates around the central axis thereof, and when the first matching side surface and the second matching side surface abut, under the abutting matching of the first matching side surface and the second matching side surface, the shaft body will generate a pushing force on the transmission member, so as to push the transmission member to rotate, and the transmission member and the ring body rotate around the central axis of the shaft body.

[0023] If the transmission member and the shaft body are fixed by welding, the transmission member will make the shaft body have a large eccentric mass, and thus a balance block needs to be arranged to balance the eccentric mass of the shaft body. In the present application, the transmission member and the shaft body have no actual connection relationship, but the first matching side surface and the second matching side surface abut to push the shaft body to rotate the transmission member; that is, the transmission member of the present application will not cause the eccentric mass problem of the shaft body, thereby greatly reducing the mass of the balance block, and even not needing to arrange the balance block, so as to reduce or avoid the problem that the large mass of the balance block leads to a large deflection of the shaft body, that is, the influence of the centrifugal force of the balance block on the deflection of the shaft body is eliminated, so that the shaft body is no longer limited in speed due to the large deflection, and thus the high speed of the compressor can be realized without the arrangement of the balance block, thereby solving the problem that the large deflection of the crankshaft is caused by the arrangement of the balance block in the prior art. BRIEF DESCRIPTION OF DRAWINGS

[0024] The drawings accompanying the specification of the present application form a part thereof, serve to provide further understanding of the present application, and together with the description of the exemplary embodiments of the present application and the explanation thereof, to explain the present application. In the drawings:

[0025] Figure 1 A structural schematic view of a crankshaft structure according to the present application is shown; wherein the first matching part and the second matching part adopt the first setting form thereof, and the transmission member and the protruding part adopt the first setting form thereof;

[0026] Figure 2 A structural schematic view of a crankshaft structure according to the present application is shown; wherein the first matching part and the second matching part adopt the first setting form thereof, and the transmission member and the protruding part adopt the second setting form thereof;

[0027] Figure 3 A structural schematic view of a shaft body of a crankshaft structure according to the present application is shown; wherein the first matching part is a groove;

[0028] Figure 4 A transverse sectional view of the shaft body of the crankshaft structure in Figure 3 is shown;

[0029] Figure 5 A structural schematic view of a roller of a crankshaft structure according to the present application is shown; wherein the second matching part is a protruding part;

[0030] Figure 6 a top view of the roller of the crankshaft structure in Figure 5

[0031] Figure 7 a structural schematic view of the roller of the crankshaft structure in Figure 5

[0032] Figure 8 a structural schematic view of the shaft body of the crankshaft structure according to the present application; wherein the first matching part is a preset shaft section, and a recess is formed at the preset shaft section;

[0033] Figure 9 a transverse sectional view of the shaft body of the crankshaft structure in Figure 8

[0034] Figure 10 a structural schematic view of the roller of the crankshaft structure according to the present application; wherein the second matching part is a groove;

[0035] Figure 11 a top view of the roller of the crankshaft structure in Figure 10

[0036] Figure 12 a structural schematic view of the roller of the crankshaft structure in Figure 10

[0037] Figure 13 a structural schematic view of the roller of the crankshaft structure in Figure 11

[0038] Figure 14 a structural schematic view of the ring body of the roller of the crankshaft structure according to the present application; wherein an annular groove is arranged on the ring body;

[0039] Figure 15 a structural schematic view of the roller of the crankshaft structure according to the present application; wherein a connecting groove is arranged on the transmission part;

[0040] Figure 16 a longitudinal sectional view of the rolling rotor compressor according to the present application; wherein the first matching part and the second matching part adopt the first setting form thereof, and the transmission part and the protruding part adopt the first setting form thereof;

[0041] Figure 17 a longitudinal sectional view of the rolling rotor compressor according to the present application; wherein the first matching part and the second matching part adopt the first setting form thereof, and the transmission part and the protruding part adopt the second setting form thereof;

[0042] Figure 18 ​​​​​​Fig. 1 shows a structure schematic diagram of a rolling rotor compressor according to the present application;

[0043] Figure 19 Fig. 2 shows a longitudinal sectional view of a shaft body of a crankshaft structure according to the present application; wherein the first fitting part is a groove, and each balance hole group includes two balance oil holes;

[0044] Figure 20 Fig. 3 shows a longitudinal sectional view of a shaft body of a crankshaft structure according to the present application; wherein the first fitting part is a groove, and each balance hole group includes one balance oil hole;

[0045] Figure 21 Fig. 4 shows a longitudinal sectional view of a crankshaft structure according to the present application; wherein the first fitting part and the second fitting part adopt their first setting form, and the transmission member and the protrusion adopt their second setting form.

[0046] Wherein, the above-mentioned drawings include the following reference signs:

[0047] 10, shaft body; 11, first fitting part; 112, first groove; 113, first groove side wall; 114, second groove side wall; 12, balance oil hole; 13, center through hole; 14, preset shaft section; 141, recess; 142, first side face; 1421, first one side face; 1422, first two side face; 143, second side face; 1431, second one side face; 1432, second two side face;

[0048] 20, roller; 21, ring body; 211, annular groove; 22, transmission member; 221, inclined side face; 222, connecting groove; 223, second fitting part; 2232, second groove; 22321, third groove side wall; 22322, fourth groove side wall;

[0049] 30, connecting key;

[0050] 40, cylinder; 41, cylinder cavity; 411, suction cavity; 412, compression cavity; 42, sliding vane groove; 43, cylinder inner wall;

[0051] 50, sliding vane; 51, sliding vane head; 52, sliding vane tail;

[0052] 61, groove; 611, specified groove side wall; 62, protrusion; 621, specified outer side wall; 622, first outer side wall; 623, second outer side wall. DETAILED DESCRIPTION

[0053] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0054] It should be noted that the following detailed description is exemplary in nature and is intended to provide further description of the application. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

[0055] It is to be understood that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, components, and / or groups thereof, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0056] The present application provides a crankshaft structure, please refer to Figures 1 to 21 The crankshaft structure comprises a shaft body 10 and a roller 20; the shaft body 10 is rotatably arranged around a central axis; a first matching part 11 is arranged on the outer peripheral wall of the shaft body 10; the roller 20 comprises a ring body 21 and a transmission part 22, the ring body 21 is arranged around a preset axis, the preset axis is parallel to the central axis of the shaft body 10; along the radial direction of the ring body 21, the transmission part 22 has oppositely arranged first and second ends; the first end of the transmission part 22 is connected with the inner wall of the ring body 21; the second end of the transmission part 22 is provided with a second matching part 223. One of the first matching part 11 and the second matching part 223 is a groove 61.

[0057] In the present embodiment, the first kind of arrangement form of the first matching part 11 and the second matching part 223 is that, as shown in Figures 3 to 7 , the first matching part 11 is a groove 61, and the second matching part 223 is a protruding part 62, the protruding part 62 is located in the groove 61. It should be noted that when the protruding part 62 is located in the groove 61, the protruding part 62 is not clamped in the groove 61, but is only placed in the groove 61.

[0058] In the present embodiment, the second kind of arrangement form of the first matching part 11 and the second matching part 223 is that, as shown in Figures 8 to 13 , the second matching part 223 is a groove 61, and the first matching part 11 is a part of the shaft section of the shaft body 10 in the axial direction of the shaft body 10, the first matching part 11 is located in the groove 61, that is, the shaft body 10 is located in the groove 61. It should be noted that when the first matching part 11 is located in the groove 61, the shaft body 10 is not clamped in the groove 61, but is only placed in the groove 61.

[0059] The first matching part 11 has a first matching side, and the second matching part 223 has a second matching side; when the shaft body 10 rotates around the central axis thereof, and when the first matching side and the second matching side abut, under the abutting matching of the first matching side and the second matching side, the shaft body 10 will generate a pushing force on the transmission member 22, so as to push the transmission member 22 to rotate, the transmission member 22 drives the ring body 21 to rotate, and the transmission member 22 and the ring body 21 rotate around the central axis of the shaft body 10.

[0060] In the crankshaft structure of the present application, the abutting matching of the first matching part 11 and the second matching part 223 enables the shaft body 10 to transmit torque to the ring body 21 through the transmission member 22, and further enables the shaft body 10 to drive the roller 20 to rotate around the central axis of the shaft body 10 through the transmission member 22.

[0061] If the transmission member and the shaft body are welded and fixed, the transmission member will make the shaft body have a large eccentric mass, and thus a balance block needs to be arranged to balance the eccentric mass of the shaft body. However, in the present application, the transmission member 22 and the shaft body 10 have no actual connection relationship, but the shaft body 10 pushes the transmission member 22 to rotate through the abutting matching of the first matching side and the second matching side; that is, the transmission member 22 of the present application will not cause the eccentric mass problem of the shaft body 10, and thus the mass of the balance block is greatly reduced, and even the balance block does not need to be arranged, thereby reducing or avoiding the problem that the deflection of the shaft body 10 is large due to the arrangement of the balance block with a large mass, that is, the influence of the centrifugal force of the balance block on the deflection of the shaft body is eliminated, so that the shaft body 10 is no longer limited in speed due to the large deflection, and thus the arrangement of the balance block does not need to limit the high speed of the compressor, thereby solving the problem that the deflection of the crankshaft is large due to the arrangement of the balance block in the prior art.

[0062] It should be noted that, since the transmission member 22 and the shaft body 10 have no actual connection relationship, and the transmission member 22 and the shaft body 10 are only abutted and matched through the first matching side and the second matching side, except for the contact area of the first matching side and the second matching side, the transmission member 22 and the shaft body 10 are not in contact, and thus the centrifugal force of the ring body 21 when rotating is acting on the cavity wall of the cylinder cavity 41 of the cylinder 40, rather than on the shaft body 10, and therefore the balance block can be cancelled under the condition that the shaft body 10 has no eccentric mass through reasonable design, thereby eliminating the influence of the centrifugal force of the balance block on the deflection of the crankshaft, so that the high speed of the compressor is no longer limited.

[0063] It should be noted that, this way of transmitting torque through the abutting matching of the first matching side and the second matching side can reduce the radial pressure of the roller 20 when the shaft body 10 rotates.

[0064] It should be noted that, the shaft body 10 having no eccentric mass means that the shaft body 10 will not generate eccentric force when rotating around the central axis thereof.

[0065] It should be noted that the deflection is the linear displacement of the axis of the rod in the direction perpendicular to the axis.

[0066] It should be noted that when the first matching side is a plane, the first matching side is parallel to the central axis of the shaft body 10. When the first matching side is not a plane, for example, the first matching side is a bent surface or a curved surface, the first matching side is arranged around the central axis of the shaft body 10. When the second matching side is a plane and when the first matching part 11 and the second matching part 223 are matched, the second matching side is parallel to the central axis of the shaft body 10. When the second matching side is not a plane and when the first matching part 11 and the second matching part 223 are matched, the second matching side is arranged around the central axis of the shaft body 10; for example, when the second matching side is not a plane, the second matching side can be a bent surface or a curved surface. Wherein, the matching of the first matching part 11 and the second matching part 223 means that the protruding part 62 is located in the groove 61, or the shaft body 10 is located in the groove 61.

[0067] For the convenience of description, when the first matching part 11 and the second matching part 223 are in the first setting form, the groove 61 on the shaft body 10 is a first groove 112; when the first matching part 11 and the second matching part 223 are in the second setting form, the groove 61 on the transmission part 22 is a second groove 2232.

[0068] In the embodiment, the groove 61 has two oppositely arranged specified groove side walls 611, one of the two specified groove side walls 611 forms the first matching side or the second matching side; when the first matching part 11 and the second matching part 223 are matched, the distribution direction of the two specified groove side walls 611 is perpendicular to the axial direction of the shaft body 10.

[0069] In the embodiment, as shown in Figures 3 to 7 When the first matching part 11 and the second matching part 223 are in the first setting form, one of the two specified groove side walls 611 of the first groove 112 forms the first matching side; the protruding part 62 has two oppositely arranged specified outer side walls 621; one of the two specified outer side walls 621 forms the second matching side. When the first matching part 11 and the second matching part 223 are matched, the distribution direction of the two specified outer side walls 621 is perpendicular to the axial direction of the shaft body 10; the distribution direction of the two specified outer side walls 621 is perpendicular to the protruding direction of the protruding part 62, and the protruding direction of the protruding part 62 is the same as or parallel to the distribution direction of the first end and the second end of the transmission part 22.

[0070] In the implementation, the two designated groove sidewalls 611 of the first groove 112 are respectively the first groove sidewall 113 and the second groove sidewall 114; the two designated outer sidewalls 621 of the protruding part 62 are respectively the first outer sidewall 622 and the second outer sidewall 623. When the protruding part 62 is located in the first groove 112, the first outer sidewall 622 is arranged towards the first groove sidewall 113, and the second outer sidewall 623 is arranged towards the second groove sidewall 114; before the shaft body 10 rotates, there is a gap between the first outer sidewall 622 and the first groove sidewall 113, and / or there is a gap between the second outer sidewall 623 and the second groove sidewall 114; if the shaft body 10 rotates counterclockwise (from the perspective of the figure), when the first outer sidewall 622 and the first groove sidewall 113 abut, the shaft body 10 will push the transmission part 22 to rotate, at this time, the first groove sidewall 113 is the first matching side, and the first outer sidewall 622 is the second matching side; if the shaft body 10 rotates clockwise (from the perspective of the figure), when the second outer sidewall 623 and the second groove sidewall 114 abut, the shaft body 10 will push the transmission part 22 to rotate, at this time, the second groove sidewall 114 is the first matching side, and the second outer sidewall 623 is the second matching side. Figure 3 The perspective of the figure) Figure 3 The perspective of the figure)

[0071] In the embodiment, as shown in the figure Figures 8 to 13 , when the first matching part 11 and the second matching part 223 are in the second setting form, one of the two designated groove sidewalls 611 of the second groove 2232 forms the second matching side; the outer peripheral wall surface of the part shaft segment of the shaft body 10 forming the first matching part 11 forms the first matching side.

[0072] In the embodiment, as shown in the figure Figures 8 to 13 , when the first matching part 11 and the second matching part 223 are in the second setting form, the shaft body 10 includes a preset shaft segment 14, the preset shaft segment 14 is the first matching part 11; at least part of the outer peripheral wall of the preset shaft segment 14 is recessed to form a recessed part 141; the preset shaft segment 14 is located in the groove 61.

[0073] Specifically, the outer peripheral wall of the preset shaft segment 14 includes two oppositely arranged first sides 142, one of the two first sides 142 forms the first matching side; the distribution direction of the two first sides 142 is perpendicular to the axial direction of the shaft body 10.

[0074] In the implementation process, the two first side surfaces 142 are respectively a first one side surface 1421 and a first two side surface 1422, and the two specified groove side walls 611 of the second groove 2232 are respectively a third groove side wall 22321 and a fourth groove side wall 22322; when the preset shaft section 14 is located in the second groove 2232, the first one side surface 1421 is arranged towards the third groove side wall 22321, and the first two side surface 1422 is arranged towards the fourth groove side wall 22322; before the shaft body 10 rotates, there is a gap between the first one side surface 1421 and the third groove side wall 22321, and / or there is a gap between the first two side surface 1422 and the fourth groove side wall 22322; if the shaft body 10 rotates counterclockwise (viewed from the perspective), when the first two side surface 1422 and the fourth groove side wall 22322 abut, the shaft body 10 will push the transmission member 22 to rotate, at this time, the first two side surface 1422 is the first matching side surface, and the fourth groove side wall 22322 is the second matching side surface; if the shaft body 10 rotates clockwise (viewed from the perspective), when the first one side surface 1421 and the third groove side wall 22321 abut, the shaft body 10 will push the transmission member 22 to rotate, at this time, the first one side surface 1421 is the first matching side surface, and the third groove side wall 22321 is the second matching side surface. Figure 8 Figure 8

[0075] In the embodiment, the shaft body 10 has a center through hole 13; along the axial direction of the shaft body 10, the center through hole 13 penetrates the shaft body 10; the center line of the center through hole 13 coincides with the center axis of the shaft body 10.

[0076] When the shaft body 10 is provided with one first matching part 11, the roller 20 is one. When the shaft body 10 is provided with a plurality of first matching parts 11 arranged at intervals along the axial direction of the shaft body 10, the roller 20 is a plurality of rollers 20, and the plurality of rollers 20 are arranged in one-to-one correspondence with the plurality of first matching parts 11, that is, the second matching part 223 of the transmission member 22 of the plurality of rollers 20 is matched with the plurality of first matching parts 11 in one-to-one correspondence, and the second matching part 223 of the transmission member 22 of each roller 20 is matched with the corresponding first matching part 11, so that when the shaft body 10 rotates, the shaft body 10 can push each transmission member 22 to rotate. At least part of the plurality of first matching parts 11 is distributed along the circumferential direction of the shaft body 10.

[0077] When the shaft body 10 has eccentric mass, at least one balance oil hole 12 is arranged on the outer peripheral wall of the shaft body 10, and the balance oil hole 12 is communicated with the center through hole 13 of the shaft body 10, so as to reduce the eccentric mass of the shaft body 10 or make the shaft body 10 not have eccentric mass.

[0078] ​​Specifically, when all the first matching portions 11 on the shaft body 10 are in the second setting form, and no recessed portion 141 is formed at the first matching portion 11 on the shaft body 10, the shaft body 10 will not have eccentric mass, and thus the balancing oil hole 12 is not needed to balance the eccentric mass of the shaft body 10.

[0079] Specifically, when one first matching portion 11 is arranged on the shaft body 10, and the first matching portion 11 is a groove 61 or a recessed portion 141 is formed at the first matching portion 11, the balancing oil hole 12 is needed to balance the eccentric mass of the shaft body 10, i.e., at least one balancing oil hole 12 is arranged on the outer peripheral wall of the shaft body 10.

[0080] Specifically, when multiple first matching portions 11 are arranged on the shaft body 10 and the shaft body 10 has eccentric mass, at least part of the multiple first matching portions 11 is a groove 61 or a recessed portion 141 is formed at the first matching portion 11, and the balancing oil hole 12 is needed to balance the eccentric mass of the shaft body 10, i.e., at least one balancing oil hole 12 is arranged on the outer peripheral wall of the shaft body 10.

[0081] It can be seen that the shaft body 10 of the present application can balance the eccentric mass caused by the arrangement of the recessed portion 141 or the groove 61 through the balancing oil hole 12, so as to reduce the eccentric mass of the shaft body 10 or make the shaft body 10 not have eccentric mass.

[0082] It should be noted that when the eccentric mass of the shaft body 10 is extremely small and within an acceptable range, the balancing block or other balancing structure can no longer be arranged. Since the high-speed compression machine will cause the centrifugal force of the shaft body 10 to be large, and thus the deflection of the shaft body 10 is increased, the arrangement of the balancing block or other balancing structure can be removed in the assembly relationship and space, so as to remove the limitation on the high-speed compression machine.

[0083] Specifically, the lubricating oil in the central through hole 13 can flow out through the balancing oil hole 12, so as to supply oil for the roller 20 and the shaft body 10, and ensure lubrication.

[0084] In the present embodiment, the balancing hole group is arranged on the shaft body 10, and the balancing hole group includes one balancing oil hole 12 or multiple balancing oil holes 12 distributed along the axial direction of the shaft body 10. For all the first matching portions 11 which are grooves 61 or have recessed portions 141 formed thereat, each first matching portion 11 is arranged in correspondence with one balancing hole group.

[0085] Specifically, when one first matching portion 11 which is a groove 61 or has a recessed portion 141 formed thereat is arranged on the shaft body 10, one balancing hole group is arranged on the shaft body 10.

[0086] Specifically, when the shaft body 10 is provided with a plurality of first matching portions 11 which are the grooves 61 or have the recesses 141 formed at the grooves 61, the shaft body 10 is provided with a plurality of balance hole groups, and the plurality of first matching portions 11 which are the grooves 61 or have the recesses 141 formed at the grooves 61 are provided in one-to-one correspondence with the plurality of balance hole groups.

[0087] In the present embodiment, for all the first matching portions 11 which are the grooves 61, along the radial direction of the shaft body 10, each first matching portion 11 and the corresponding balance hole group are respectively located on opposite sides of the shaft body 10.

[0088] Specifically, when the shaft body 10 is provided with one first matching portion 11 which is the groove 61, the shaft body 10 is provided with one balance hole group; along the radial direction of the shaft body 10, the first matching portion 11 and the balance hole group are respectively located on opposite sides of the shaft body 10.

[0089] Specifically, when the shaft body 10 is provided with a plurality of first matching portions 11 which are the grooves 61, the shaft body 10 is provided with a plurality of balance hole groups; the plurality of first matching portions 11 which are the grooves 61 are provided in one-to-one correspondence with the plurality of balance hole groups; along the radial direction of the shaft body 10, each first matching portion 11 which is the groove 61 and the corresponding balance hole group are respectively located on opposite sides of the shaft body 10.

[0090] Figure 20 Each balance hole group in the shaft body 10 includes one balance oil hole 12. Figure 19 Each balance hole group in the shaft body 10 includes two balance oil holes 12. Figure 19 The first matching portion 11 in the shaft body 10 is the groove 61. Figure 20 The first matching portion 11 in the shaft body 10 is the groove 61.

[0091] Optionally, as shown in Figure 19 The first matching portion 11 in the shaft body 10 is the groove 61. Figure 20 The first matching portion 11 in the shaft body 10 is the groove 61.

[0092] Further, in the axial direction of the shaft body 10, Figure 19 The two balance oil holes 12 of each balance hole group in the shaft body 10 are symmetrically arranged relative to the corresponding first matching portion 11.

[0093] The first matching portion 11 in the shaft body 10 is the groove 61. Figure 9As shown, the first matching part 11 is provided with a recess 141, and the balance hole group corresponding to the first matching part 11 includes a balance oil hole 12; the preset shaft section 14 includes two oppositely arranged second sides 143, which are respectively a first second side 1431 and a second second side 1432; the distribution direction of the two second sides 143 is perpendicular to the axial direction of the shaft body 10, and the distribution direction of the two second sides 143 is perpendicular to the distribution direction of the two first sides 142. The balance oil hole 12 is arranged on the second second side 1432; the recess 141 includes the two first sides 142 and the first second side 1431, and the second second side 1432 is not recessed.

[0094] In the embodiment, when the shaft body 10 is provided with the plurality of first matching parts 11 which are the recesses 61 or the recesses 141 formed at the recesses 61, in the plurality of first matching parts 11 which are the recesses 61 or the recesses 141 formed at the recesses 61, any two adjacent first matching parts 11 are located on opposite sides of the shaft body 10 along the radial direction of the shaft body 10.

[0095] In the embodiment, the cross section of the transmission member 22 gradually decreases from the first end to the second end of the transmission member 22; wherein the cross section of the transmission member 22 is parallel to the preset axis, and the cross section of the transmission member 22 is perpendicular to the distribution direction of the first end and the second end of the transmission member 22.

[0096] Specifically, the transmission member 22 has two oppositely arranged inclined sides 221, the distribution direction of the two inclined sides 221 of the transmission member 22 is perpendicular to the distribution direction of the first end and the second end of the transmission member 22, and the distribution direction of the two inclined sides 221 of the transmission member 22 is perpendicular to the axial direction of the shaft body 10; from the first end to the second end of the transmission member 22, each inclined side 221 of the transmission member 22 gradually approaches the other inclined side 221.

[0097] In the embodiment, when the second matching part 223 is the protrusion 62, the first arrangement form of the transmission member 22 and the protrusion 62 is that the transmission member 22 and the protrusion 62 are integrally formed.

[0098] In the embodiment, when the second matching part 223 is the protrusion 62, the second arrangement form of the transmission member 22 and the protrusion 62 is that Figure 15 and Figure 21 As shown, the crankshaft structure further includes a connecting key 30; the second end of the transmission member 22 is provided with a connecting groove 222, a part of the connecting key 30 is clamped in the connecting groove 222, so that the transmission member 22 and the connecting key 30 are relatively fixed; another part of the connecting key 30 is located outside the connecting groove 222 to form the protrusion 62. That is, the shaft body 10 transmits torque to the transmission member 22 through the connecting key 30. Figure 21 In the embodiment, the left part of the connecting key 30 shown by the dashed line forms the protrusion 62.

[0099] In the first arrangement of the transmission member 22 and the ring body 21, the transmission member 22 and the ring body 21 are integrally formed; at this time, the ring body 21 and the cylinder cavity 41 of the cylinder 40 are in sliding friction.

[0100] In the second arrangement of the transmission member 22 and the ring body 21, as shown in Figure 14 , the inner wall of the ring body 21 is provided with an annular groove 211 arranged around the preset axis, and the first end of the transmission member 22 is slidably arranged in the annular groove 211, so that when the shaft body 10 drives the transmission member 22 to rotate, the transmission member 22 drives the ring body 21 to rotate, and the transmission member 22 and the ring body 21 can relatively rotate. That is, at this time, the roller 20 is a split structure.

[0101] It should be noted that in the process of the transmission member 22 driving the ring body 21 to rotate around the central axis of the shaft body 10, the gas compressed by the ring body 21 will generate a reverse force on the ring body 21 in the opposite direction of the rotation direction of the ring body 21; if the ring body 21 and the transmission member 22 are relatively fixed, the same position on the ring body 21 contacts the cylinder cavity 41 of the cylinder 40, and the reverse force of the gas on the ring body 21 will form a friction force between the ring body 21 and the cylinder cavity 41 of the cylinder 40, and the friction force between the ring body 21 and the cylinder cavity 41 of the cylinder 40 will repeatedly rub the same position of the ring body 21 contacting the cylinder cavity 41. If the ring body 21 and the transmission member 22 can relatively rotate, the reverse force of the gas on the ring body 21 will cause a certain relative rotation between the ring body 21 and the transmission member 22 around the preset axis, so that the position of the ring body 21 contacting the cylinder cavity 41 will change, and then the friction force between the ring body 21 and the cylinder cavity 41 will not repeatedly rub the same contact position of the ring body 21 with the cylinder cavity 41; that is, the ring body 21 not only rotates with the transmission member 22 around the central axis of the shaft body 10, but also relatively rotates with the transmission member 22 in the opposite direction around the preset axis, and the rotation degree of the ring body 21 around the preset axis relative to the transmission member 22 is necessarily less than the rotation degree of the ring body 21 around the central axis of the shaft body 10 with the transmission member 22. At this time, the ring body 21 and the cylinder cavity 41 of the cylinder 40 are in rolling friction, and the split structure of the roller 20 can appropriately reduce the friction force between the ring body 21 and the cylinder cavity 41 of the cylinder 40.

[0102] In the embodiment, as shown in Figure 16 and Figure 17 , the inner wall of the ring body 21 has a preset position; the preset position is the position between the inner wall of the ring body 21 and the second end of the transmission member 22 with the smallest vertical distance along the circumferential direction of the ring body 21; the vertical distance between the preset position and the outer peripheral wall of the shaft body 10 is H1; when the first fitting part 11 is the groove 61, the groove depth of the first fitting part 11 is H2, and the groove depth direction of the first fitting part 11 is perpendicular to the axial direction of the shaft body 10; wherein H1>H2.

[0103] In the implementation, when the transmission member 22 and the protrusion 62 adopt the first arrangement form, a proper H1 is reserved to move the roller 20 along the radial direction of the shaft body 10 after the roller 20 is sleeved on the shaft body 10, so as to place the protrusion 62 in the first groove 112; therefore, H1 > H2 is to enable the roller 20 and the shaft body 10 to be normally and smoothly assembled.

[0104] In the embodiment, the roller 20 is rotatably arranged in the cylinder cavity 41 of the cylinder 40, the central axis of the cylinder cavity 41 is coincident with the central axis of the shaft body 10; the minimum vertical distance between the outer peripheral wall of the ring body 21 and the cavity wall of the cylinder cavity 41 is H3; wherein, H1 > H3.

[0105] It should be noted that theoretically, H3 should be 0; however, in the actual manufacturing process, it is impossible to make H3 be absolutely 0; therefore, H3 is an assembly gap, and H3 is usually in microns. For example, H3 is tens of microns or twenties of microns.

[0106] In the implementation, when the transmission member 22 and the protrusion 62 adopt the second arrangement form, the relative assembly between the roller 20 and the shaft body 10 is convenient, H1 can be designed to be smaller, and the assembly between the roller 20 and the shaft body 10 can also be realized. However, it is still necessary to ensure that H1 is greater than H3, so as to ensure that the centrifugal force of the roller 20 does not act on the shaft body 10 when the roller 20 rotates, but acts on the cylinder cavity 41, so that the centrifugal force of the roller 20 does not affect the deflection of the shaft body 10.

[0107] Specifically, when the roller 20 is a plurality of rollers, the cylinder 40 is a plurality of cylinders, and the plurality of rollers 20 and the plurality of cylinders 40 are arranged in one-to-one correspondence. Each roller 20 is rotatably arranged in the cylinder cavity 41 of the corresponding cylinder 40. The central axes of the cylinder cavities 41 of the plurality of cylinders 40 are all coincident with the central axis of the shaft body 10.

[0108] The application also provides a rolling rotor type compressor, which comprises the cylinder 40 and the crankshaft structure.

[0109] Specifically, as shown in the figure, Figure 18 The rolling rotor type compressor further comprises a sliding vane 50, and the inner wall surface of the cylinder cavity 41 of the cylinder 40 is provided with a sliding vane groove 42; the sliding vane 50 is slidably arranged in the sliding vane groove 42; in the process of rotating the ring body 21 by the shaft body 10, the sliding vane 50 keeps in contact with the outer peripheral wall of the ring body 21, and the farthest position on the outer peripheral wall of the ring body 21 keeps in contact with the inner wall of the cylinder cavity 41, so as to divide the cylinder cavity 41 into an intake cavity 411 and a compression cavity 412 by the sliding vane 50 and the ring body 21; and through the rotation of the ring body 21, the intake cavity 411 inhales air, and the gas in the compression cavity 412 is compressed.

[0110] The farthest position on the outer peripheral wall of the ring body 21 refers to a position where the vertical distance between the outer peripheral wall of the ring body 21 and the cavity wall of the cylinder cavity 41 is the smallest along the circumference of the ring body 21, that is, the vertical distance between the farthest position on the outer peripheral wall of the ring body 21 and the cavity wall of the cylinder cavity 41 is H3.

[0111] Figure 18 The inner wall 43 of the cylinder in the above-mentioned cylinder cavity 41 is the cavity wall.

[0112] Specifically, the sliding piece 50 includes a sliding piece head 51; the sliding piece head 51 is in contact with the outer peripheral wall of the ring body 21.

[0113] Specifically, the sliding piece 50 includes a sliding piece tail 52, and a spring is arranged between the sliding piece tail 52 and the groove wall of the sliding piece groove 42, so that the sliding piece head 51 is in contact with the outer peripheral wall of the ring body 21.

[0114] From the above description, it can be seen that the above-mentioned embodiments of the present application achieve the following technical effects:

[0115] In the crankshaft structure provided by the present application, the crankshaft structure includes a shaft body 10 and a roller 20; the shaft body 10 is rotatably arranged around a central axis; a first matching part 11 is arranged on the outer peripheral wall of the shaft body 10; the roller 20 includes a ring body 21 and a transmission part 22, the ring body 21 is arranged around a predetermined axis, and the predetermined axis is parallel to the central axis of the shaft body 10; along the radial direction of the ring body 21, the transmission part 22 has oppositely arranged first and second ends; the first end of the transmission part 22 is connected with the inner wall of the ring body 21; and the second end of the transmission part 22 is provided with a second matching part 223. One of the first matching part 11 and the second matching part 223 is a groove 61.

[0116] The first matching part 11 is a groove 61, and the second matching part 223 is a protruding part 62, and the protruding part 62 is located in the groove 61. It should be noted that when the protruding part 62 is located in the groove 61, the protruding part 62 is not clamped in the groove 61, but is only placed in the groove 61.

[0117] The second matching part 223 is a groove 61, and the first matching part 11 is a part of the shaft segment of the shaft body 10 in the axial direction of the shaft body 10, and the first matching part 11 is located in the groove 61, that is, the shaft body 10 is located in the groove 61. It should be noted that when the first matching part 11 is located in the groove 61, the shaft body 10 is not clamped in the groove 61, but is only placed in the groove 61.

[0118] The first matching part 11 has a first matching side surface, and the second matching part 223 has a second matching side surface; when the shaft body 10 rotates around the central axis thereof, and when the first matching side surface and the second matching side surface abut, under the abutting matching action of the first matching side surface and the second matching side surface, the shaft body 10 will generate a pushing force on the transmission member 22, so as to push the transmission member 22 to rotate, the transmission member 22 drives the ring body 21 to rotate, and the transmission member 22 and the ring body 21 rotate around the central axis of the shaft body 10.

[0119] If the transmission member and the shaft body are welded and fixed, the transmission member will make the shaft body have a large eccentric mass, and then a balance block needs to be arranged to balance the eccentric mass of the shaft body. However, in the present application, the transmission member 22 and the shaft body 10 have no actual connection relationship, but the first matching side surface and the second matching side surface abut and match to push the shaft body 10 to rotate the transmission member 22; that is, the transmission member 22 of the present application will not cause the eccentric mass problem of the shaft body 10, thereby greatly reducing the mass of the balance block, and even not needing to arrange the balance block, thereby reducing or avoiding the problem that the deflection of the shaft body 10 is large due to the arrangement of the balance block with a large mass, that is, eliminating the influence of the centrifugal force of the balance block on the deflection of the shaft body, so that the shaft body 10 is no longer limited in speed due to the large deflection, and then the high speed of the compressor can be realized without the arrangement of the balance block, thereby solving the problem that the deflection of the crankshaft is large due to the arrangement of the balance block in the prior art.

[0120] It should be noted that the terms "first", "second", and the like in the specification and claims of the present application and the above-described drawings are used to distinguish similar objects, and do not necessarily have to be used to describe a specific order or sequence. It should be understood that the data used in this way can be interchanged under appropriate circumstances, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion, for example, a process, method, system, product or device including a series of steps or units does not have to be limited to those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0121] For purposes of the description hereinafter, the terms "upper", "lower", "right", "left", "rear", "front", "vertical", "horizontal", and derivatives thereof shall relate to the application as oriented in the drawing figures. However, it is to be understood that the application can assume various alternative orientations and, accordingly, such terms are not to be taken as limitations of the present application. Additionally, terms such as "first", "second", "third", etc. are used herein for purposes of description and do not necessarily have an ordinal meaning unless specifically stated.

[0122] The above description is embodied in the form of preferred embodiments only and is not intended to limit the present application. The present application can be variously changed and substituted without departing from the spirit and principles of the present application. Any and all modifications, variations or equivalent arrangements which do not depart from the spirit and principles of the present application should be considered to be within the scope of the present application.

Claims

1. A crankshaft structure characterized by comprising: The utility model relates to a kind of shafts, including: Shaft body (10), first fitting part (11) is provided on the outer peripheral wall of the shaft body (10); Roller (20), the roller (20) includes ring body (21) and transmission part (22), the ring body (21) is arranged around preset axis, the preset axis is parallel with the central axis of the shaft body (10);Transmission part (22) has oppositely arranged first end and second end along the radial direction of the ring body (21);The first end of the transmission part (22) is connected with the inner wall of the ring body (21);Second end of the transmission part (22) is provided with second fitting part (223); Wherein, one of the first fitting part (11) and the second fitting part (223) is groove (61);When the first fitting part (11) is the groove (61), the second fitting part (223) is convex part (62), and the convex part (62) is located in the groove (61);When the second fitting part (223) is the groove (61), the first fitting part (11) is part of shaft section of the shaft body (10), and the first fitting part (11) is located in the groove (61); The first fitting part (11) has first fitting side, and the second fitting part (223) has second fitting side, so that the first fitting side and the second fitting side abut when the shaft body (10) rotates, and then the shaft body (10) drives the transmission part (22) to rotate; The inner wall of the ring body (21) has preset position;The preset position is the position between the inner wall of the ring body (21) and the second end of the transmission part (22) with minimum vertical spacing along the circumferential direction of the ring body (21);The vertical spacing between the preset position and the outer peripheral wall of the shaft body (10) is H1;When the first fitting part (11) is the groove (61), the groove depth of the first fitting part (11) is H2, and the groove depth direction of the first fitting part (11) is perpendicular to the axial direction of the shaft body (10);Wherein, H1>H2.

2. The crankshaft structure according to claim 1, characterized by The groove (61) has oppositely arranged two specified groove side walls (611), one of the two specified groove side walls (611) forms the first fitting side or the second fitting side; When the second fitting part (223) is the convex part (62), the convex part (62) has oppositely arranged two specified outer side walls (621), one of the two specified outer side walls (621) forms the second fitting side; When the first fitting part (11) is part of shaft section of the shaft body (10), the outer peripheral wall surface of the part of shaft section of the shaft body (10) forms the first fitting side.

3. The crankshaft structure according to claim 1, characterized by When the second matching part (223) is the groove (61), the shaft body (10) comprises a preset shaft section (14), the preset shaft section (14) is the first matching part (11); at least part of the outer peripheral wall of the preset shaft section (14) is concave to form a recess (141); the preset shaft section (14) is located in the groove (61).

4. The crankshaft structure according to claim 3, characterized by The outer peripheral wall of the preset shaft section (14) comprises two oppositely arranged first side faces (142), one of the two first side faces (142) forms the first matching side face; the groove (61) has two oppositely arranged specified groove side walls (611), one of the two specified groove side walls (611) forms the second matching side face.

5. The crankshaft structure according to any one of claims 1 to 4, characterized by, The shaft body (10) has a central through hole (13); When the shaft body (10) is provided with one first matching part (11), the roller (20) is one; when the shaft body (10) is provided with a plurality of first matching parts (11) arranged along the axial direction of the shaft body (10), the roller (20) is a plurality of rollers (20), and the plurality of rollers (20) are arranged in one-to-one correspondence with the plurality of first matching parts (11); at least part of the plurality of first matching parts (11) is distributed along the circumferential direction of the shaft body (10); When the shaft body (10) has eccentric mass, at least one balance oil hole (12) is arranged on the outer peripheral wall of the shaft body (10), the balance oil hole (12) is communicated with the central through hole (13) of the shaft body (10), so as to reduce the eccentric mass of the shaft body (10) or make the shaft body (10) not have eccentric mass.

6. The crankshaft structure according to claim 5, characterized by The shaft body (10) is provided with a balance hole group, the balance hole group comprises one or a plurality of balance oil holes (12) distributed along the axial direction of the shaft body (10); when the first matching part (11) is the groove (61) or the recess (141) is formed at the first matching part (11), each first matching part (11) is arranged in correspondence with one balance hole group.

7. The crankshaft structure according to claim 6, characterized by When the first matching part (11) is the groove (61), along the radial direction of the shaft body (10), each first matching part (11) and the corresponding balance hole group are respectively located on opposite sides of the shaft body (10).

8. The crankshaft structure according to claim 6, characterized by When the shaft body (10) is provided with a plurality of first matching parts (11) which are the grooves (61) or have the recesses (141) formed therein, along the radial direction of the shaft body (10), any two adjacent first matching parts (11) are respectively located on opposite sides of the shaft body (10).

9. The crankshaft structure according to claim 1, characterized by From the direction from the first end to the second end of the transmission member (22), the cross section of the transmission member (22) gradually decreases; wherein the cross section of the transmission member (22) is parallel to the preset axis, and the cross section of the transmission member (22) is perpendicular to the distribution direction of the first end and the second end of the transmission member (22).

10. The crankshaft structure according to claim 1 or 9, characterized by The transmission member (22) has two opposite inclined sides (221), the distribution direction of the two inclined sides (221) of the transmission member (22) is perpendicular to the distribution direction of the first end and the second end of the transmission member (22), and the distribution direction of the two inclined sides (221) of the transmission member (22) is perpendicular to the axial direction of the shaft body (10); from the direction of the first end to the second end of the transmission member (22), each inclined side (221) of the transmission member (22) gradually approaches the other inclined side (221).

11. The crankshaft structure according to claim 1, characterized by When the second matching part (223) is the protruding part (62), The transmission member (22) and the protruding part (62) are an integral structure; or The connecting key (30) is provided with a part clamped in the connecting groove (222) and another part outside the connecting groove (222) to form the protruding part (62).

12. The crankshaft structure according to claim 1, wherein The transmission member (22) and the ring body (21) are an integral structure; or The inner wall of the ring body (21) is provided with an annular groove (211) arranged around the preset axis, and the first end of the transmission member (22) is slidably arranged in the annular groove (211), so that when the shaft body (10) drives the transmission member (22) to rotate, the transmission member (22) drives the ring body (21) to rotate, and the transmission member (22) and the ring body (21) can rotate relative to each other.

13. The crankshaft structure according to claim 1, characterized by The roller (20) is arranged rotatably in the cylinder cavity (41) of the cylinder (40), the central axis of the cylinder cavity (41) coincides with the central axis of the shaft body (10), the minimum vertical distance between the outer peripheral wall of the ring body (21) and the cavity wall of the cylinder cavity (41) is H3, and H1>H3.

14. A rolling piston compressor characterized by, The crankshaft structure according to any one of claims 1 to 13. The crankshaft structure according to any one of claims 1 to 13.

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