Crankshaft for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a crankshaft for a compressor. The crankshaft comprises a shaft body and a rotor; the rotor and the shaft body are coaxially arranged, the rotor is symmetrical relative to the rotation axis of the rotor, the section, perpendicular to the rotation axis of the rotor, of the rotor is of an oval main body outline, and the end, in the short axis direction of the section, of the rotor is provided with a tangent plane so that the end, in the short axis direction of the section, of the section can form a cut edge. The shaft body of the crankshaft rotates to drive the rotor to rotate in the inner cavity of the air cylinder, and compression of refrigerant gas is achieved. A larger compression space can be formed between the rotor and the inner wall surface of the cylinder inner cavity by arranging the tangent plane at the end part of the rotor along the short axis direction of the cross section. And the larger compression space allows the refrigerant gas to be compressed more sufficiently in the compression process, so that the compression efficiency of the compressor can be improved. The utility model further discloses the compressor.

Description

Technical Field

[0001] This application relates to the field of compressor technology, specifically to a crankshaft and compressor for use in compressors. Background Technology

[0002] Currently, rotary compressors achieve compression by setting an eccentric part on the crankshaft, which causes the compressor to vibrate during operation.

[0003] To reduce compressor vibration and noise, a rotary compressor is disclosed in the related technology. The compressor's pump body assembly includes a cylinder, an elliptical piston disposed within the cylinder cavity, a vane disposed within a vane slot in the cylinder, a shaft for driving the elliptical piston to rotate, and main bearings and auxiliary bearings disposed on the upper and lower sides of the cylinder. The centerline of the elliptical piston overlaps with the centerline of the cylinder cavity. Two vane slots are provided, each containing a vane, one end of which contacts the outer circumference of the elliptical piston. When the compressor is running, the end of the vane is in close contact with the outer circumference of the elliptical piston.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In related technologies, although eccentric vibrations caused by an eccentric part can be avoided by setting an elliptical piston with a symmetrical structure, the range of motion of the elliptical piston in the cylinder cavity is limited, resulting in a relatively smaller actual usable compression space, which affects the compression efficiency of the compressor.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Utility Model Content

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides a crankshaft for a compressor and a compressor to improve the compression efficiency of the compressor.

[0009] According to a first aspect of the present invention, a crankshaft for a compressor is provided, the crankshaft including a shaft body and a rotor; the rotor is coaxially arranged with the shaft body, the rotor is symmetrical with respect to the rotor rotation axis, the rotor has an elliptical main outline in a cross section perpendicular to the rotor rotation axis, and the rotor has a cut surface at the end of the cross section along the minor axis direction, so that the end of the cross section along the minor axis direction forms a cut edge.

[0010] Optionally, the cut surface is a planar structure parallel to the major axis of the cross section, and the cut edge is a straight line segment parallel to the major axis of the cross section.

[0011] Optionally, the ratio of the length between the cut edge and the major axis of the cross section is greater than 0 and less than or equal to 1; and / or, the ratio of the length of the major axis of the cross section to the length of the minor axis of the cross section is greater than 1.

[0012] According to a second aspect of the present invention, a compressor is provided, comprising: a cylinder including a cylinder body having a cylinder cavity; a crankshaft for a compressor as described in any of the above-disclosed embodiments, wherein a rotor of the crankshaft is disposed in the cylinder cavity, the end face of the rotor along the long axis of its cross section is in contact with the inner wall surface of the cylinder cavity, and the rotor is capable of rotating in the cylinder cavity to compress refrigerant.

[0013] Optionally, the cylinder body is provided with a first sliding vane groove, a second sliding vane groove, a first intake port, a second intake port, a first exhaust oblique cut, and a second exhaust oblique cut, all communicating with the cylinder cavity. The axes of the first and second sliding vane grooves intersect to divide the cylinder cavity into a first compression chamber and a second compression chamber. The first intake port and the first exhaust oblique cut are connected to the first compression chamber, and the second intake port and the second exhaust oblique cut are connected to the second compression chamber. The cylinder also includes: a first sliding vane, disposed in the first sliding vane groove, and capable of moving towards or away from the cylinder cavity relative to the first sliding vane groove; and a second sliding vane, disposed in the second sliding vane groove, and capable of moving towards or away from the cylinder cavity relative to the second sliding vane groove. During the rotation of the rotor in the cylinder cavity, the first and second sliding vanes are always in contact with the rotor.

[0014] Optionally, the length of the minor axis of the cross section is greater than or equal to the width of the first slider; and / or, the length of the minor axis of the cross section is greater than or equal to the width of the second slider.

[0015] Optionally, the first and second sliding vane slots are symmetrically arranged with respect to the rotor's axis of rotation; and / or, the first and second intake holes are symmetrically arranged with respect to the rotor's axis of rotation; and / or, the first and second exhaust oblique cuts are symmetrically arranged with respect to the rotor's axis of rotation.

[0016] Optionally, the cylinder body is further provided with a first intake oblique cut and a second intake oblique cut, the first intake oblique cut being connected between the first intake port and the first compression chamber, and the second intake oblique cut being connected between the second intake port and the second compression chamber.

[0017] Optionally, the first exhaust oblique cut and the second exhaust oblique cut are located on the upper end face of the cylinder; and / or, the first intake port and the second intake port are located on the side wall of the cylinder.

[0018] Optionally, the compressor further includes: a main bearing, having a first exhaust valve hole and a second exhaust valve hole, wherein the first exhaust valve hole is connected to the first exhaust oblique cut of the cylinder, and the second exhaust valve hole is connected to the second exhaust oblique cut of the cylinder.

[0019] The crankshaft and compressor for a compressor provided in this disclosure can achieve the following technical effects:

[0020] The rotation of the crankshaft drives the rotor to rotate within the cylinder, compressing the refrigerant gas. By creating a cross-section at the end of the rotor along its minor axis, a larger compression space is formed between the rotor and the inner wall of the cylinder. This larger compression space allows the refrigerant gas to be compressed more thoroughly during the compression process, thereby improving the compressor's compression efficiency. Simultaneously, the rotor and crankshaft are coaxial, and the rotor is symmetrical with respect to its axis of rotation. This eliminates the need for an eccentric crankshaft structure, effectively avoiding centrifugal force imbalance caused by mass eccentricity. The rotor's cross-section perpendicular to its axis of rotation has an elliptical profile, allowing it to better adapt to the shape of the cylinder. The combination of the major and minor axes enables differentiated compression volume changes of the refrigerant gas. The elliptical profile also results in more uniform and stable flow of the refrigerant gas within the cylinder, reducing vibration and improving the compressor's compression efficiency.

[0021] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0022] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0023] Figure 1 This is a schematic diagram of the structure of a crankshaft provided in an embodiment of this disclosure;

[0024] Figure 2 This is a schematic diagram of a rotor provided in an embodiment of the present disclosure, wherein the direction pointed to by the arrow is the direction of the minor axis of the cross section;

[0025] Figure 3 This is a schematic diagram of the assembly of a crankshaft and a cylinder provided in an embodiment of this disclosure, wherein the direction pointed to by the arrow is the direction of the major axis of the cross section;

[0026] Figure 4 This is another assembly diagram of a crankshaft and cylinder provided in an embodiment of this disclosure;

[0027] Figure 5This is another assembly diagram of a crankshaft and cylinder provided in an embodiment of this disclosure;

[0028] Figure 6 This is another assembly diagram of a crankshaft and cylinder provided in an embodiment of this disclosure;

[0029] Figure 7 This is a schematic diagram of the structure of a cylinder provided in an embodiment of this disclosure;

[0030] Figure 8 This is a schematic diagram of the structure of a main bearing provided in an embodiment of this disclosure.

[0031] Figure label:

[0032] 10: Crankshaft; 11: Shaft body; 12: Rotor; 121: Section; 122: Long shaft; 123: Short shaft; 124: Cut surface; 125: Cut edge; 126: First end; 127: Second end; 128: Rotor rotation axis;

[0033] 20: Cylinder; 30: Cylinder body; 301: First sliding vane groove; 302: Second sliding vane groove; 303: First intake port; 304: Second intake port; 305: First exhaust oblique cut; 306: Second exhaust oblique cut; 309: Upper end face; 310: Side wall; 40: Cylinder inner cavity; 41: Inner wall surface; 42: First compression chamber; 43: Second compression chamber; 50: First sliding vane; 51: Second sliding vane;

[0034] 60: Main bearing; 61: First exhaust valve hole; 62: Second exhaust valve hole. Detailed Implementation

[0035] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0036] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0037] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0038] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0039] Unless otherwise stated, the term "multiple" means two or more.

[0040] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0041] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0042] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0043] Combination Figure 1-6 As shown, this disclosure provides a crankshaft 10 for a compressor, including a shaft body 11 and a rotor 12.

[0044] The rotor 12 is coaxially arranged with the shaft 11. The rotor 12 is symmetrical with respect to the rotation axis of the rotor 12. The rotor 12 has an elliptical main outline in the cross section 121 perpendicular to the rotation axis of the rotor 12. The rotor 12 has a cut surface 124 at the end of the cross section 121 along the minor axis 123, so that the end of the cross section 121 along the minor axis 123 forms a cut edge 125.

[0045] The rotor 12 is coaxially arranged with the shaft 11, such that the rotation axis of the shaft 11 coincides with the rotation axis of the rotor 12. Rotor 12 rotation axis Figure 1 As shown by the dashed line.

[0046] The rotor 12 has an elliptical main outline in its cross-section 121 perpendicular to its rotation axis. This means that the basic shape of the cross-section 121 is not a strictly standard ellipse, but rather a shape close to an ellipse. The rotor 12 is a symmetrical structure with respect to its rotation axis. In this embodiment, the rotor 12 has a cut surface 124 at its end along the minor axis 123 of the cross-section 121, forming a cut edge 125 at the end of the cross-section 121 along the minor axis 123, rather than the elliptical arc end of a standard ellipse. The rotor 12 has a cut surface 124 at both ends along the minor axis 123 of the cross-section 121. Since the rotor 12 is symmetrical with respect to its rotation axis, the cut surfaces 124 at the two ends are symmetrical.

[0047] Section 121 has an elliptical main outline, and its geometric parameters are based on the definition of a standard ellipse. The major axis 122 of section 121 is the longest diameter of section 121, and it connects the two farthest vertices on section 121. For example... Figure 2 As shown by the dashed line, the length of the major axis 122 is 2a, where a represents the distance from the center of section 121 to the endpoint of the major axis 122, i.e., a is the length of the semi-major axis. The minor axis 123 of section 121 is the shortest diameter in section 121. The minor axis 123 is perpendicular to the major axis 122 and connects the two closest vertices on section 121. Figure 2 As shown by the dashed line, the length of the minor axis 123 is 2b, where b represents the distance from the center of section 121 to the endpoint of the minor axis 123, that is, b is the length of the semi-minor axis.

[0048] The compressor includes a cylinder 20 and a crankshaft 10. The cylinder 20 includes a cylinder body 30 and vanes. The cylinder body 30 has a cylinder cavity 40 and vane slots. The cylinder cavity 40 provides space for refrigerant compression. The vane slots accommodate vanes that can slide freely within the slots and abut against the rotor 12, dividing the cylinder cavity 40 into different spaces to achieve effective refrigerant compression. When the compressor is running, the rotor 12 of the crankshaft 10 can rotate within the cylinder cavity 40, and the rotation of the rotor 12 achieves refrigerant compression.

[0049] The crankshaft 10 for a compressor provided in this embodiment of the present disclosure allows the shaft 11 of the crankshaft 10 to rotate, driving the rotor 12 to rotate within the cylinder cavity 40, thereby compressing the refrigerant gas. By providing a cross-section 124 at the end of the rotor 12 along the short axis 123 of the cross-section 121, a larger compression space can be formed between the rotor 12 and the inner wall 41 of the cylinder cavity 40. This larger compression space allows the refrigerant gas to be compressed more fully during the compression process, thereby improving the compressor's compression efficiency. Simultaneously, the rotor 12 is coaxially arranged with the shaft 11, and the rotor 12 has a symmetrical structure relative to its rotation axis. This eliminates the need for an eccentric structure in the crankshaft 10, effectively avoiding centrifugal force imbalance caused by mass eccentricity. The symmetrical structure of the rotor 12 also improves the uniformity and stability of the refrigerant flow within the cylinder cavity 40, thereby reducing pressure fluctuations and vibrations during compression. This reduces the noise level during compressor operation and improves the smoothness of compressor operation. The rotor 12 has an elliptical main profile in cross-section 121 perpendicular to its rotation axis, allowing it to better adapt to the shape of the cylinder cavity 40. The combination of the long axis 122 and the short axis 123 enables differentiated compression volume changes of the refrigerant gas. This elliptical main profile makes the flow of refrigerant gas within the cylinder cavity 40 more uniform and stable, thus reducing vibration and improving the compressor's compression efficiency.

[0050] Optionally, the end face of the long shaft 122 and the end face of the short shaft 123 of the rotor 12 are smoothly connected.

[0051] During compressor operation, rotor 12 rotates within the cylinder cavity 40 of cylinder 20 and engages closely with the sliding vanes of cylinder 20. The end face of the long shaft 122 and the end face of the short shaft 123 of rotor 12 have a smooth transition connection, making the surface of rotor 12 more continuous and smooth. This continuity and smoothness of the rotor 12 surface ensures continuous contact between the sliding vanes and the outer surface of rotor 12, achieving sealing and compression functions and preventing vane jumps. This improves the operational stability of the vanes, thereby enhancing sealing performance and reducing vibration and noise.

[0052] Optionally, the end face of the long shaft 122 and the end face of the short shaft 123 of the rotor 12 are connected by an arc.

[0053] Using an arc connection can achieve a smooth transition between the end face of the long axis 122 and the end face of the short axis 123 of the rotor 12, and can also achieve curvature continuity at the connection between the end face of the long axis 122 and the end face of the short axis 123.

[0054] Optionally, the end face of the long shaft 122 and the end face of the short shaft 123 of the rotor 12 are connected by a multi-segment curve transition.

[0055] The use of multi-segment curved connections allows for a smoother and more natural connection between the end face of the long shaft 122 and the end face of the short shaft 123 of the rotor 12. This multi-segment curved connection method can be flexibly designed according to actual needs to meet different mechanical and aerodynamic performance requirements.

[0056] Optionally, combined Figure 1 and Figure 2 As shown, the cut surface 124 is a planar structure parallel to the major axis 122 of the cross section 121, and the cut edge 125 is a straight line segment parallel to the major axis 122 of the cross section 121.

[0057] The rotor 12 has a cut surface 124 at its end along the short axis 123 of section 121. The cut surface 124 is a planar structure parallel to the long axis 122 of section 121, and correspondingly, the cut edge 125 is a straight line segment parallel to the long axis 122 of section 121. The planar structure of the cut surface 124 provides a larger contact area, providing a stable support surface for the vane, reducing vane bounce and wobbling, and enabling the vane to work more smoothly with the rotor 12, thus improving the operating stability of the compressor. At the same time, the planar structure of the cut surface 124 is relatively simple and easy to process, reducing manufacturing difficulty.

[0058] It is understandable that the cut surface 124 can also be a concave surface that is recessed inward from the outer surface of the rotor 12, and the cut edge 125 is correspondingly a concave line segment that is recessed inward from the end of the short shaft 123 of the cross section 121. This can also increase the compression space of the rotor 12 at the end of the short shaft 123 of the cross section 121 and improve the compression efficiency.

[0059] Optionally, the two ends of the cut surface 124 are smoothly transitioned along the long axis 122 of the section 121.

[0060] This improves the surface continuity of rotor 12, reduces stress concentration, and thus improves the mechanical strength and durability of rotor 12.

[0061] Optionally, combined Figure 2 As shown, the length ratio between the tangent 125 and the major axis 122 of the section 121 is greater than 0 and less than or equal to 1.

[0062] The length of the cut edge is 125 as follows Figure 2 As shown in Figure c, the length of the straight segment formed after cutting section 121 along the minor axis 123 is the distance between the two endpoints of the cut edge 125. Figure 2 As shown in section 2a, the tangent 125 is located at the end of the minor axis 123 of section 121 and extends along the major axis 122 of section 121.

[0063] When the rotor 12 has a cross-section 124 along the direction of the minor axis 123 of the cross-section 121, a tangent 125 is formed at the end of the cross-section 121 along the direction of the minor axis 123. At this time, the length of the tangent 125 is greater than 0, and the length ratio c / 2a between the tangent 125 and the major axis 122 of the cross-section 121 is greater than 0. The presence of the cross-section 124 can increase the compression space of the rotor 12 at the end of the minor axis 123 of the cross-section 121, so that the gap between the rotor 12 and the inner wall surface 41 of the cylinder cavity 40 can be effectively utilized, increasing the compression volume of the refrigerant gas, thereby improving the compression efficiency.

[0064] When the length ratio c / 2a between the tangent edge 125 and the major axis 122 of the cross-section 121 is less than or equal to 1, the length of the tangent edge 125 can be kept within the diameter of the major axis 122 of the cross-section 121, maintaining the geometric continuity of the elliptical main profile of the cross-section 121. This avoids stress concentration or sealing failure caused by abrupt structural changes. Simultaneously, this also reduces the runout amplitude of the slider during operation, effectively improving slider noise.

[0065] The present invention specifies that the length ratio between the tangent 125 and the major axis 122 of the cross section 121 is greater than 0 and less than or equal to 1. This can improve the compression efficiency while reducing the runout amplitude of the vane during operation, thereby improving the overall performance of the compressor.

[0066] Optionally, the ratio between the length of the major axis 122 of section 121 and the length of the minor axis 123 of section 121 is greater than 1.

[0067] The ratio between the length 2a of the major axis 122 of section 121 and the length 2b of the minor axis 123 of section 121 is greater than 1, so that the length of the major axis 122 is greater than the length of the minor axis 123, thus enabling section 121 to maintain an elliptical main outline.

[0068] This disclosure provides a compressor, including a cylinder 20 and a crankshaft 10 for the compressor as described in any of the above-disclosed embodiments. The cylinder 20 includes a cylinder body 30, which has a cylinder cavity 40. The rotor 12 of the crankshaft 10 is disposed in the cylinder cavity 40, and the end face of the rotor 12 along the long axis 122 of the cross section 121 is in contact with the inner wall surface 41 of the cylinder cavity 40. The rotor 12 is capable of rotating in the cylinder cavity 40 to compress refrigerant.

[0069] The compressor provided in this disclosure embodiment, because it includes the crankshaft 10 for the compressor as described in any of the above-disclosed embodiments, has all the beneficial effects of the crankshaft 10 for the compressor as described in any of the above-disclosed embodiments.

[0070] The end face of rotor 12 along the long axis 122 of cross section 121 is in contact with the inner wall surface 41 of cylinder cavity 40. Cylinder cavity 40 is divided into independent compression chambers on both sides of rotor 12, allowing rotor 12 to rotate within cylinder cavity 40 to compress refrigerant. The close contact between rotor 12 and the inner wall surface 41 of cylinder cavity 40 also improves the compressor's sealing performance. Simultaneously, the symmetrical structure of rotor 12 and the elliptical profile of cross section 121 make the compressor operate more smoothly, reducing vibration and noise. The arrangement of cross section 124 also optimizes the utilization efficiency of the compression space, improving the overall performance and operating efficiency of the compressor. Furthermore, the rotor 12's placement within cylinder cavity 40 and direct participation in refrigerant compression reduces the use of piston structures in traditional compressors. This reduces the number of internal components and simplifies the compressor structure.

[0071] Optionally, combined Figure 3-7 As shown, the cylinder body 30 is provided with a first sliding vane groove 301, a second sliding vane groove 302, a first intake port 303, a second intake port 304, a first exhaust oblique cut 305, and a second exhaust oblique cut 306 that communicate with the cylinder cavity 40. The axis of the first sliding vane groove 301 intersects the axis of the second sliding vane groove 302, which can divide the cylinder cavity 40 into a first compression chamber 42 and a second compression chamber 43. The first intake port 303 and the first exhaust oblique cut 305 are connected to the first compression chamber 42, and the second intake port 304 and the second exhaust oblique cut 306 are connected to the first compression chamber 42. The cylinder 20 is connected to the second compression chamber 43 and also includes a first sliding vane 50 and a second sliding vane 51. The first sliding vane 50 is disposed in the first sliding vane groove 301 and can move towards or away from the cylinder cavity 40 relative to the first sliding vane groove 301. The second sliding vane 51 is disposed in the second sliding vane groove 302 and can move towards or away from the cylinder cavity 40 relative to the second sliding vane groove 302. During the rotation of the rotor 12 in the cylinder cavity 40, the first sliding vane 50 and the second sliding vane 51 are always in contact with the rotor 12.

[0072] Cylinder 20 adopts a design structure with double sliding vanes, double intake ports, and double oblique exhaust ports. The axial direction of the first sliding vane groove 301 is consistent with the movement direction of the first sliding vane 50. The axial direction of the second sliding vane groove 302 is consistent with the movement direction of the first sliding vane. For example... Figure 7As shown by the dashed line, the intersection of the axis of the first sliding vane groove 301 and the axis of the second sliding vane groove 302 divides the cylinder cavity 40 into a first compression chamber 42 and a second compression chamber 43. The first sliding vane 50, the second sliding vane 51, and the nearly elliptical rotor 12 further divide the cylinder cavity 40 into independent first compression chambers 42 and 43. The first intake port 303 and the first exhaust oblique cut 305 are connected to the first compression chamber 42, allowing refrigerant gas to enter the first compression chamber 42 through the first intake port 303 for compression and exit through the first exhaust oblique cut 305. The second intake port 304 and the second exhaust oblique cut 306 are connected to the second compression chamber 43, allowing refrigerant gas to enter the second compression chamber 43 through the second intake port 304 for compression and exit through the second exhaust oblique cut 306.

[0073] The rotor 12 is coaxially arranged with the cylinder cavity 40 in a near-elliptical shape. When the compressor motor drives the crankshaft 10's shaft 11 to rotate, the shaft 11 drives the rotor 12 to rotate synchronously. Figure 3-6 As shown, during the intake and compression processes, the first vane 50 and the second vane 51 are always in contact with the rotor 12. The first vane 50 and the second vane 51 are respectively in close contact with the outer periphery of the rotor 12, which can achieve isolation between the first compression chamber 42 and the second compression chamber 43. Each complete rotation cycle of the rotor 12 allows the first compression chamber 42 and the second compression chamber 43 to complete two complete cycles of intake, compression, and exhaust. The rotor includes a first end 126 and a second end 127 along its long axis. During one rotation cycle of the rotor 12, the first end 126 and the second end 127 of the rotor can contact the first vane 50 and the second vane 51 once each. In this way, the first compression chamber 42 and the second compression chamber 43 complete a total of four complete working cycles within one rotation cycle of the rotor 12, which can effectively improve the compression efficiency and output power of the compressor.

[0074] Cylinder 20, with its dual exhaust and dual intake structure, accelerates the refrigerant intake speed and total amount, thereby increasing the refrigerant circulation speed in the refrigeration system. This allows the compressor to fully utilize the latent heat of the refrigerant during compression, improving energy efficiency. In cooling mode, the low-temperature refrigerant in the evaporator is quickly and sufficiently drawn into the compressor for compression and heating, then transported to the condenser to release heat, increasing the rate of heat exchange and accelerating the decrease in indoor temperature. In heating mode, the high-temperature refrigerant in the condenser enters the indoor heat exchanger in a timely and substantial manner to release heat, thus accelerating the increase in indoor temperature. This meets users' needs for rapid cooling and heating.

[0075] Meanwhile, the dual exhaust and dual intake structure of cylinder 20 allows the refrigerant to enter the cylinder cavity 40 more evenly, achieving efficient and stable compressor operation at low frequencies. This also optimizes the airflow distribution and pressure balance inside the compressor, reducing unbalanced forces caused by low-frequency operation, thus enabling the compressor to maintain a relatively stable operating state even under low-frequency conditions, reducing noise and vibration interference, and extending the compressor's service life.

[0076] Optionally, combined Figure 2 and Figure 3 As shown, the length of the minor axis 123 of section 121 is greater than or equal to the width of the first slider 50.

[0077] The length of the minor axis 123 of section 121 is as follows Figure 2 As shown in Figure 2b, the width of the first slider 50 is as follows: Figure 3 As shown in section d, the length of the short axis 123 of section 121 is greater than or equal to the width of the first vane 50, ensuring sufficient contact area between the rotor 12 and the first vane 50 along the long axis 122 of section 121. This creates a more reliable sealing effect during rotor 12 rotation, improving the compressor's compression efficiency and operational stability.

[0078] Optionally, combined Figure 2 and Figure 3 As shown, the length of the minor axis 123 of section 121 is greater than or equal to the width of the second slider 51.

[0079] The length of the minor axis 123 of section 121 is as follows Figure 2 As shown in Figure 2b, the width of the second slider 51 is as follows: Figure 3 As shown in section e. This ensures that there is sufficient contact area between the rotor 12 and the second vane 51 along the long axis 122 of section 121. This results in a more reliable sealing effect during rotor 12 rotation, improving the compressor's compression efficiency and operational stability.

[0080] Optionally, combined Figure 1 and Figure 3-7 As shown, the first sliding vane groove 301 and the second sliding vane groove 302 are symmetrically arranged with respect to the rotation axis of the rotor 12.

[0081] The first vane groove 301 and the second vane groove 302 are symmetrically arranged with respect to the rotation axis of the rotor 12, meaning that the first vane groove 301 and the second vane groove 302 are symmetrically distributed at 180° with respect to the rotation axis of the rotor 12. The first vane 50 is slidably disposed in the first vane groove 301, and the second vane 51 is slidably disposed in the second vane groove 302, so that the first vane 50 and the second vane 51 are symmetrically arranged on opposite sides of the rotor 12 with respect to the rotation axis of the rotor 12. This can counteract the centrifugal torque generated by the movement of the first vane 50 and the second vane 51, improve the uniformity of the force on the rotor 12 during rotation, reduce the vibration amplitude and noise level of the rotor 12 during rotation, and thus improve the operating stability of the compressor.

[0082] Optionally, combined Figure 1 and Figure 7 As shown, the first suction port 303 and the second suction port 304 are symmetrically arranged with respect to the rotation axis of the rotor 12.

[0083] The first suction port 303 and the second suction port 304 are symmetrically arranged with respect to the rotation axis of the rotor 12, meaning that the first suction port 303 and the second suction port 304 are axially symmetrically distributed with respect to the rotation axis of the rotor 12 at 180°. The symmetrical arrangement of the first suction port 303 and the second suction port 304 can balance the flow distribution of refrigerant entering the first compression chamber 42 and the second compression chamber 43, avoiding pressure fluctuations caused by uneven flow, thereby improving the compression efficiency and operational stability of the compressor.

[0084] Optionally, combined Figure 1 and Figure 7 As shown, the first exhaust oblique cut 305 and the second exhaust oblique cut 306 are symmetrically arranged with respect to the rotation axis of the rotor 12.

[0085] The first exhaust oblique cut 305 and the second exhaust oblique cut 306 are symmetrically arranged with respect to the rotation axis of the rotor 12, meaning that the first exhaust oblique cut 305 and the second exhaust oblique cut 306 are symmetrically distributed at 180° with respect to the rotation axis of the rotor 12. The symmetrical arrangement of the first exhaust oblique cut 305 and the second exhaust oblique cut 306 can simultaneously release the exhaust pressure fluctuations of the first compression chamber 42 and the second compression chamber 43, thereby improving the operating stability of the compressor.

[0086] Optionally, the cylinder body 30 is further provided with a first intake oblique cut and a second intake oblique cut, the first intake oblique cut being connected between the first intake port 303 and the first compression chamber 42, and the second intake oblique cut being connected between the second intake port 304 and the second compression chamber 43.

[0087] A first intake oblique cut is provided between the first intake port 303 and the first compression chamber 42. The refrigerant flows from the first intake port 303 to the first intake oblique cut, and then enters the first compression chamber 42. A second intake oblique cut is provided between the second intake port 304 and the second compression chamber 43. The refrigerant flows from the second intake port 304 to the second intake oblique cut, and then enters the second compression chamber 43. The design of the first and second intake oblique cuts reduces the eddies and turbulence generated by the abrupt change in flow direction during refrigerant intake. This reduces energy loss during refrigerant intake, improves compressor compression efficiency, and also reduces noise and vibration.

[0088] Optionally, combined Figure 7 As shown, the first exhaust oblique cut 305 and the second exhaust oblique cut 306 are provided on the upper end face 309 of the cylinder block 30.

[0089] The first exhaust oblique cut 305 and the second exhaust oblique cut 306 are provided on the upper end face 309 of the cylinder block 30, which makes the refrigerant path more direct and smooth during the discharge process, reduces the energy loss of the refrigerant during the discharge process, and thus improves the exhaust efficiency.

[0090] Optionally, combined Figure 7 As shown, the first intake port 303 and the second intake port 304 are provided on the side wall 310 of the cylinder body 30.

[0091] The intake port is located on the side wall 310 of the cylinder block 30, allowing the refrigerant gas to enter the cylinder cavity 40 more directly, reducing refrigerant gas escape caused by pressure difference during intake. This optimizes the refrigerant flow path, reduces energy loss, and improves intake efficiency.

[0092] Optionally, combined Figure 8 As shown, the compressor also includes a main bearing 60, which has a first exhaust valve hole 61 and a second exhaust valve hole 62. The first exhaust valve hole 61 is connected to the first exhaust oblique cut 305 of the cylinder 30, and the second exhaust valve hole 62 is connected to the second exhaust oblique cut 306 of the cylinder 30.

[0093] The cylinder body 30 of cylinder 20 is equipped with a dual exhaust oblique cut structure. By setting a first exhaust valve hole 61 and a second exhaust valve hole 62 in the main bearing 60 that cooperate with the first exhaust oblique cut 305 and the second exhaust oblique cut 306 of the cylinder body 30, the flow path of the refrigerant can be optimized, allowing the refrigerant to be discharged from the compressor more smoothly. This reduces energy loss and thus improves exhaust efficiency.

[0094] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A crankshaft for a compressor, characterized in that, include: Shaft body; The rotor is coaxially arranged with the shaft and is symmetrical with respect to the rotor rotation axis. The rotor has an elliptical main outline in the cross section perpendicular to the rotor rotation axis, and the rotor has a cut surface at the end of the cross section along the minor axis direction so that the end of the cross section along the minor axis direction forms a cut edge.

2. The crankshaft for a compressor according to claim 1, characterized in that, The cut surface is a planar structure parallel to the major axis of the cross section, and the cut edge is a straight line segment parallel to the major axis of the cross section.

3. The crankshaft for a compressor according to claim 2, characterized in that, The ratio of the length of the cut edge to the major axis of the cross section is greater than 0 and less than or equal to 1; and / or, The ratio between the major axis length and the minor axis length of the cross section is greater than 1.

4. A compressor, characterized in that, include: A cylinder, including a cylinder body, the cylinder body having a cylinder cavity; The crankshaft for a compressor as described in any one of claims 1 to 3, wherein the rotor of the crankshaft is disposed in the cylinder cavity, the end face of the rotor along the long axis of the cross section is in contact with the inner wall surface of the cylinder cavity, and the rotor is capable of rotating in the cylinder cavity to compress the refrigerant.

5. The compressor according to claim 4, characterized in that, The cylinder body is provided with a first sliding vane groove, a second sliding vane groove, a first intake port, a second intake port, a first exhaust oblique cut, and a second exhaust oblique cut, all communicating with the cylinder cavity. The axes of the first and second sliding vane grooves intersect, dividing the cylinder cavity into a first compression chamber and a second compression chamber. The first intake port and the first exhaust oblique cut are connected to the first compression chamber, and the second intake port and the second exhaust oblique cut are connected to the second compression chamber. The cylinder also includes: The first sliding vane is disposed in the first sliding vane groove, and the first sliding vane can move toward or away from the cylinder cavity relative to the first sliding vane groove; The second slide is disposed in the second slide groove, and the second slide can move toward or away from the cylinder cavity relative to the second slide groove; During the rotation of the rotor in the cylinder cavity, the first and second sliding vanes are always in contact with the rotor.

6. The compressor according to claim 5, characterized in that, The length of the minor axis of the cross section is greater than or equal to the width of the first slider; and / or, The length of the minor axis of the cross section is greater than or equal to the width of the second slider.

7. The compressor according to claim 5, characterized in that, The first and second sliding vane slots are symmetrically arranged with respect to the rotor's axis of rotation; and / or, The first and second intake ports are symmetrically arranged with respect to the rotor's axis of rotation; and / or, The first and second exhaust oblique cuts are symmetrically arranged with respect to the rotor's axis of rotation.

8. The compressor according to claim 5, characterized in that, The cylinder block is also provided with a first intake oblique cut and a second intake oblique cut. The first intake oblique cut is connected between the first intake port and the first compression chamber, and the second intake oblique cut is connected between the second intake port and the second compression chamber.

9. The compressor according to claim 5, characterized in that, The first and second exhaust oblique cuts are located on the upper end face of the cylinder block; and / or The first and second intake ports are located on the side wall of the cylinder block.

10. The compressor according to any one of claims 5 to 9, characterized in that, Also includes: The main bearing is provided with a first exhaust valve hole and a second exhaust valve hole. The first exhaust valve hole is connected to the first exhaust oblique cut of the cylinder block, and the second exhaust valve hole is connected to the second exhaust oblique cut of the cylinder block.

Images