Crankshaft, compressor and refrigeration equipment

Abstract

The present application provides a crankshaft, a compressor and a refrigeration device. The crankshaft includes a crank, a main shaft and an eccentric shaft. An oil suction cavity is provided at one end of the main shaft, a distribution oil passage is provided in the eccentric shaft, two spiral grooves with opposite spiral directions are provided on the main shaft, a first oil hole communicating the spiral groove with the distribution oil passage and a second oil hole communicating the spiral groove with the oil suction cavity are provided on the main shaft; the two spiral grooves intersect to form an intersection area; the crankshaft further includes a movable blocking member rotatably disposed in the intersection area, and the movable blocking member is used to connect the lower side walls of two sections of the spiral groove corresponding to the intersection area, where the spiral direction of the spiral groove is opposite to the rotation direction of the crankshaft. For the crankshaft of the present application, when the crankshaft rotates, the movable blocking member rotates in the intersection area to connect the lower side walls of two sections of the spiral groove with the rotation direction opposite to that of the crankshaft, and block a section of the other spiral groove close to the oil suction cavity in the intersection area, so that oil can be pumped smoothly and continuously along the entire spiral length of the spiral groove. Furthermore, the spiral angle of the spiral groove can be set larger to improve the ability to pump lubricating oil.

Description

Technical Field

[0001] This application belongs to the technical field of compressors. More specifically, it relates to a crankshaft, a compressor, and a refrigeration device. Background Art

[0002] When a compressor operates, lubricating oil needs to be supplied to each friction pair to reduce the frictional loss during the operation of each component, and the lubricating oil can also play a certain role in cooling and heat dissipation. Generally, spiral grooves are provided on the crankshaft of the compressor, and through the oil pumping action of the spiral grooves, oil is supplied to the distribution oil passage in the eccentric shaft of the crankshaft, and then to each friction pair. In a compressor, due to the relationship of variable frequency and variable capacity, its motor and crankshaft not only need to rotate forward, but also often need to rotate in reverse. In related technologies, generally, a pair of spiral grooves with opposite spiral directions are provided on the main shaft of the crankshaft. In this structure, when one spiral groove pumps lubricating oil in the direction of the eccentric shaft, the other spiral groove will pump the lubricating oil back in the opposite direction, which easily leads to a reduction in the lubricating oil entering the oil passage in the eccentric shaft and affects lubrication. To overcome this influence, in related technologies, the two spiral grooves are spaced apart to avoid the backflow of oil caused by the intersection of the two spiral grooves with opposite spiral directions. However, this makes the spiral angle of the two spiral grooves less than 180 degrees, and when the spiral angle of the spiral groove is small, the oil pumping capacity is weak. Summary of the Invention

[0003] The purpose of the embodiments of this application is to provide a crankshaft, a compressor, and a refrigeration device to solve the problem in the prior art that the spiral angles of the positive and negative bidirectional spiral grooves on the crankshaft of a compressor that can rotate forward and backward are small, and the oil pumping capacity is weak.

[0004] To achieve the above purpose, the technical solution adopted in the embodiments of this application is: to provide a crankshaft, including a crank, a main shaft provided on one side of the crank, and an eccentric shaft provided on the other side of the crank. An oil suction cavity is provided at one end of the main shaft away from the eccentric shaft. A distribution oil passage extending into the main shaft is provided in the eccentric shaft. Two spiral grooves are axially formed on the outer peripheral surface of the main shaft along the axis of the main shaft. The two spiral grooves have opposite spiral directions. A first oil hole communicating the spiral groove with the distribution oil passage and a second oil hole communicating the spiral groove with the oil suction cavity are provided on the main shaft. The two spiral grooves intersect to form an intersection area. The intersection area is axially located between the first oil hole and the second oil hole on the main shaft. Each spiral groove is divided into two segments at the intersection area. The crankshaft further includes a movable blocking member rotatably placed in the intersection area. The movable blocking member is used to connect the lower side walls of the two segments corresponding to the intersection area of the spiral groove with a spiral direction opposite to the rotation direction of the crankshaft. The end of the movable blocking member close to the oil suction cavity is installed on the main shaft.

[0005] In an alternative embodiment, the lower end of the movable stopper is located at the intersection of the lower side walls of the two spiral grooves.

[0006] In an alternative embodiment, a first rotating shaft is provided at the lower end of the movable stopper, a first shaft hole is correspondingly formed on the main shaft, and the first rotating shaft is rotatably installed in the first shaft hole.

[0007] In an alternative embodiment, the movable stopper is a stop bar or a baffle.

[0008] In an alternative embodiment, the two spiral grooves intersect to form a convergence area; alternatively, the two spiral grooves intersect to form a plurality of convergence areas, and the plurality of convergence areas are spaced along the axial direction of the main shaft, and each convergence area is provided with the movable stopper.

[0009] In an alternative embodiment, the number of the first oil holes is one, one end of the two spiral grooves intersects and communicates with the first oil hole, the crankshaft further includes a separator for separating one end of the two spiral grooves close to the first oil hole, and the separator is arranged on the main shaft.

[0010] In an alternative embodiment, positioning grooves are formed on opposite sides of the inner surface of the first oil hole, and two sides of the separator are respectively inserted into the two positioning grooves.

[0011] In an alternative embodiment, a second rotating shaft is provided at the lower end of the separator, a second shaft hole is correspondingly formed on the main shaft, and the second rotating shaft is rotatably installed in the second shaft hole.

[0012] In an alternative embodiment, the length of the separator along the axial direction of the main shaft is greater than the width of the spiral groove, and the length of the separator along the axial direction of the main shaft is less than the inner diameter of the first oil hole.

[0013] In an alternative embodiment, the separator includes a separating section fitted between the two spiral grooves and an inserting section inserted into the first oil hole, and the inserting section is fixed in the first oil hole.

[0014] In an alternative embodiment, two first oil holes are formed on the main shaft, the two first oil holes are arranged at intervals, the two first oil holes are respectively communicated with the two spiral grooves, and the two first oil holes are both communicated with the distribution oil passage.

[0015] In an alternative embodiment, the number of the second oil holes is one, and the other ends of the two spiral grooves intersect and communicate with the second oil hole.

[0016] In an alternative embodiment, the pitches of the two spiral grooves are equal.

[0017] Another object of the embodiments of the present application is to provide a compressor, including a crankshaft as described in any of the foregoing embodiments.

[0018] Another object of the embodiments of the present application is to provide a refrigeration device, including a compressor as described in the foregoing embodiments.

[0019] The beneficial effect of the crankshaft provided by the embodiments of the present application is that: compared with the prior art, in the crankshaft of the present application, two helical grooves with opposite helix directions are arranged on the main shaft, and the two helical grooves are arranged to intersect, and a movable stopper is rotatably arranged in the intersection area where the two helical grooves intersect. When the crankshaft rotates, the movable stopper rotates in the intersection area, so as to form a connection with the lower side walls of two sections of the helical groove with a helix direction opposite to the rotation direction of the crankshaft, and at the same time, it can block a section of the other helical groove (i.e., the helical groove with the same helix direction as the rotation direction of the crankshaft) close to the oil suction cavity in this intersection area. In this way, it is ensured that the entire helical length of the helical groove with a helix direction opposite to the rotation direction of the crankshaft can pump oil smoothly and continuously, and further, the helix angle of the helical groove can be set to be greater than 180 degrees, or even larger, thereby improving the ability to pump lubricating oil.

[0020] The beneficial effect of the compressor provided by the embodiments of the present application is that: compared with the prior art, the compressor of the present application uses the above-mentioned crankshaft, has a strong oil pumping ability, and can ensure a good oil supply volume during both forward rotation and reverse rotation, so that the compressor operates stably.

[0021] The beneficial effect of the refrigeration device provided by the embodiments of the present application is that: compared with the prior art, the refrigeration device of the present application uses the above-mentioned compressor, operates more stably and has a high service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following will briefly introduce the drawings required for use in the embodiments or exemplary technical descriptions. Obviously, the drawings in the following description are only some embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0023] Figure 1 It is a front view structural schematic diagram of a crankshaft provided by an embodiment of the present application;

[0024] Figure 2 For Figure 1 The front view structural schematic diagram when the crankshaft shown rotates forward;

[0025] Figure 3 For Figure 1 The front view structural schematic diagram when the crankshaft shown rotates in reverse;

[0026] Figure 4 For Figure 1 The side view structural schematic diagram of the crankshaft shown;

[0027] Figure 5 For Figure 1 The structural schematic diagram of the movable stopper in the crankshaft shown;

[0028] Figure 6 For Figure 1 The structural schematic diagram of the separator in the crankshaft shown;

[0029] Figure 7 The side view structural schematic diagram of the crankshaft provided by another embodiment of the present application;

[0030] Figure 8 For Figure 7 The structural schematic diagram of the separator in the crankshaft shown;

[0031] Figure 9 The front view structural schematic diagram of the crankshaft provided by another embodiment of the present application;

[0032] Figure 10 For Figure 9 The side view structural schematic diagram of the crankshaft shown.

[0033] Figure 11 For Figure 10 The enlarged view of part A in;

[0034] Figure 12 The structural schematic diagram of a partial area of the crankshaft provided by another embodiment of the present application;

[0035] Figure 13 The structural schematic diagram of a partial area of the crankshaft provided by another embodiment of the present application;

[0036] Figure 14 The structural schematic diagram of a partial area of the crankshaft provided by another embodiment of the present application;

[0037] Figure 15 The structural schematic diagram of a partial area of the crankshaft provided by another embodiment of the present application;

[0038] Figure 16 The front view structural schematic diagram of the crankshaft provided by another embodiment of the present application;

[0039] Figure 17 The front view structural schematic diagram of the crankshaft provided by another embodiment of the present application.

[0040] Among them, the main reference signs in each drawing are:

[0041] 10 - Crankshaft;

[0042] 11 - Spindle; 111 - Oil suction chamber; 112 - Spiral groove; 1120 - Confluence area; 1121 - First spiral groove; 1122 - Second spiral groove; 113 - First oil hole; 1131 - Sub - oil hole; 114 - Second oil hole; 115 - First shaft hole; 116 - Second shaft hole; 117 - Positioning groove; 12 - Eccentric shaft; 121 - Oil distribution channel; 13 - Crank; 14 - Movable stopper; 141 - First rotating shaft; 15 - Separator; 151 - Separation section; 152 - Insertion section; 153 - Second rotating shaft. Detailed implementation manner

[0043] In order to make the technical problems, technical solutions and beneficial effects to be solved by this application clearer and more understandable, the following further details this application in combination with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this application and are not used to limit this application.

[0044] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.

[0045] In the description of this application, "a plurality" means two or more, unless otherwise specifically defined. "Several" means one or more, unless otherwise specifically defined. The terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. The orientation or positional relationship indicated by terms such as "center", "length", "width", "thickness", "upper", "lower", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description, rather than indicating or implying that the indicated device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to this application.

[0046] In the description of this application, it should be noted that unless otherwise clearly specified and limited, the terms "installation", "connection", and "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium, and can be the internal communication of two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0047] References to "one embodiment", "some embodiments" or "an embodiment" in the description of this application mean that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of this application. Thus, statements such as "in one embodiment", "in some embodiments", "in other some embodiments", "in still other embodiments", etc. that appear in different places in this specification are not necessarily all referring to the same embodiment, but rather mean "one or more but not all embodiments", unless otherwise specifically emphasized. In addition, in one or more embodiments, specific features, structures, or characteristics may be combined in any suitable manner.

[0048] Please refer to Figures 1 to 6 , Figure 1 which is a front view structural schematic diagram of the crankshaft 10 provided for this embodiment, where part of the structure is a perspective structure to show the flow path of the lubricating oil. Figure 2 which is a front view structural schematic diagram of the crankshaft 10 when rotating forward for this embodiment. Figure 3 which is a front view structural schematic diagram of the crankshaft 10 when rotating backward for this embodiment. Figure 4 which is a side view structural schematic diagram of the crankshaft 10 provided for this embodiment. Figure 5 which is a structural schematic diagram of the movable blocking member 14 in the crankshaft 10 provided for this embodiment. Figure 6 which is a structural schematic diagram of the partition member 15 in the crankshaft 10 provided for this embodiment.

[0049] Please refer to Figure 1 and Figure 4 , and now the crankshaft 10 provided by this application will be described. The crankshaft 10 includes a main shaft 11, a crank 13, and an eccentric shaft 12. Among them, the main shaft 11 and the eccentric shaft 12 are respectively installed on both sides of the crank 13, and the eccentric shaft 12 is connected to the main shaft 11 through the crank 13, so as to drive the eccentric shaft 12 to rotate when the main shaft 11 rotates.

[0050] An oil suction cavity 111 is provided in the main shaft 11. The oil suction cavity 111 is located at one end of the main shaft 11, and the oil suction cavity 111 is at the end of the main shaft 11 far from the eccentric shaft 12. When the main shaft 11 rotates, the oil suction cavity 111 can suck lubricating oil from the oil sump of the compressor.

[0051] A distribution oil passage 121 is provided in the eccentric shaft 12, so that the lubricating oil can enter each friction pair from the distribution oil passage 121 to supply oil to each friction pair, reduce the wear of each friction pair, and play a role in cooling and heat dissipation.

[0052] Please refer to Figures 1 to 3, two spiral grooves 112 are provided on the outer peripheral surface of the main shaft 11. The spiral grooves 112 extend spirally along the axial direction of the main shaft 11, and the spiral directions of the two spiral grooves 112 are opposite, so that when the main shaft 11 rotates forward or backward, one of the spiral grooves 112 can play a role in pumping lubricating oil, that is, play a role in pumping oil. The distribution oil passage 121 extends into the main shaft 11, and the main shaft 11 is also provided with a first oil hole 113 and a second oil hole 114. The two ends of the spiral groove 112 are respectively communicated with the first oil hole 113 and the second oil hole 114. The first oil hole 113 is communicated with the distribution oil passage 121, so as to communicate the spiral groove 112 with the distribution oil passage 121 for pumping lubricating oil into the distribution oil passage 121. The second oil hole 114 is communicated with the oil suction cavity 111, so as to communicate the spiral groove 112 with the oil suction cavity 111, so that when the spiral groove 112 pumps oil, lubricating oil can be sucked from the oil suction cavity 111.

[0053] Please refer to Figures 1 to 3 , the two spiral grooves 112 have an intersecting intersection area 1120. Along the axial direction of the main shaft 11, the intersection area 1120 is located between the first oil hole 113 and the second oil hole 114. That is to say, the spiral angles of the two spiral grooves 112 are relatively large. For example, the spiral angle of the spiral groove 112 can be set to be greater than 180 degrees. One spiral groove 112 divides the other spiral groove 112 into two sections, then the intersection area 1120 divides the lower side wall of each spiral groove 112 into two sections, that is, the lower side wall of each spiral groove 112 is divided into two sections spaced apart along the axial direction of the main shaft 11 by the intersection area 1120, and the two sections of the lower side wall of each spiral groove 112 are also located on both sides of the other spiral groove 112, that is, each spiral groove 112 divides the lower side wall of the other spiral groove 112 into two sections at the intersection area 1120. The lower side wall of the spiral groove 112 refers to the side wall of the spiral groove 112 away from the eccentric shaft 12 along the axial direction of the main shaft 11.

[0054] Please refer to Figure 1 , Figure 4 and Figure 5, the crankshaft 10 further includes a movable stopper 14, and the movable stopper 14 is used to connect two lower sidewalls of the spiral groove 112. The two lower sidewalls are separated by the corresponding intersection area 1120, and the spiral direction of the spiral groove 112 is opposite to the rotation direction of the crankshaft 10; that is to say, the movable stopper 14 is used to connect two lower sidewalls of the spiral groove 112 with a spiral direction opposite to the rotation direction of the crankshaft 10, which are separated by another spiral groove 112 at the intersection area 1120. The movable stopper 14 is located in the intersection area 1120, and the lower end of the movable stopper 14 is rotatably installed on the main shaft 11. The lower end of the movable stopper 14 refers to the end of the movable stopper 14 close to the oil suction cavity 111. The movable stopper 14 can swing in the intersection area 1120. Since when the crankshaft 10 rotates, the spiral groove 112 with a spiral direction opposite to the rotation direction of the crankshaft 10 pumps oil to the distribution oil passage 121, and the movable stopper 14 connects the two lower sidewalls of the spiral groove 112, the lubricating oil pumped by the spiral groove 112 can flow through the movable stopper 14, so that the spiral groove 112 can pump oil smoothly and continuously, and further the entire spiral length of the spiral groove 112 can pump oil, improving the oil pumping capacity. In addition, the movable stopper 14 can also block one end of another spiral groove 112 in the intersection area 1120 and away from the eccentric shaft 12, preventing the lubricating oil from entering another spiral groove 112 from the intersection area 1120 and flowing back.

[0055] Please refer to Figures 1 to 3 , for the convenience of description, the two spiral grooves 112 are respectively defined as the first spiral groove 1121 and the second spiral groove 1122. Please refer to Figure 2 , when the crankshaft 10 rotates forward, the second spiral groove 1122 pumps oil to the distribution oil passage 121, and the movable stopper 14 swings in the intersection area 1120 in the direction opposite to the rotation direction of the crankshaft 10. Then the movable stopper 14 connects two lower sidewalls of the second spiral groove 1122 separated at the intersection area 1120, and blocks a part of the first spiral groove 1121 close to the second oil hole 114. In this way, the lubricating oil pumped by a section of the second spiral groove 1122 close to the second oil hole 114 can flow through the movable stopper 14 to a section of the second spiral groove 1122 away from the second oil hole 114, so as to realize the smooth and continuous oil pumping of the entire spiral length of the second spiral groove 1122 and improve the oil pumping capacity.

[0056] Similarly, please refer to Figure 3, when the crankshaft 10 rotates in the reverse direction, the first helical groove 1121 pumps oil towards the distribution oil passage 121. The movable stopper 14 swings in the direction opposite to the rotation direction of the crankshaft 10 in the intersection area 1120. Then the movable stopper 14 connects the lower sidewalls of the two segments of the first helical groove 1121 divided in this intersection area 1120, and blocks the part of the second helical groove 1122 close to the second oil hole 114. In this way, the lubricating oil pumped by the segment of the first helical groove 1121 close to the second oil hole 114 can flow through the movable stopper 14 to the segment of the first helical groove 1121 far from the second oil hole 114, so as to achieve smooth and continuous oil pumping along the entire helical length of the first helical groove 1121 and improve the oil pumping capacity.

[0057] Compared with the prior art, the crankshaft 10 provided in this application has two helical grooves 112 with opposite helix directions arranged on the main shaft 11, and the two helical grooves 112 intersect. An movable stopper 14 is rotatably arranged in the intersection area 1120 where the two helical grooves 112 intersect. When the crankshaft 10 rotates, the movable stopper 14 rotates in the intersection area 1120, so that the lower sidewalls of the two segments of the helical groove 112 with the helix direction opposite to the rotation direction of the crankshaft 10 are connected. At the same time, it can block a segment of the other helical groove 112 (i.e., the helical groove 112 with the same rotation direction as the crankshaft 10) close to the oil suction cavity 111 in this intersection area 1120. In this way, it is ensured that smooth and continuous oil pumping can be achieved along the entire helical length of the helical groove 112 with the helix direction opposite to the rotation direction of the crankshaft 10. Furthermore, the helix angle of the helical groove 112 can be set to be greater than 180 degrees, or even larger, so as to improve the ability to pump lubricating oil.

[0058] In one embodiment, the lower end of the movable stopper 14 is located at the intersection of the lower sidewalls of the two helical grooves 112. That is to say, the lower end of the movable stopper 14 is rotatably installed at the intersection of the lower sidewalls of the two helical grooves 112. In this way, it only needs the upper end of the movable stopper 14 to be able to overlap on the lower sidewall of the segment of the helical groove 112 far from the second oil hole 114. This can facilitate the determination of the length of the movable stopper 14 and the installation of the movable stopper 14, which is convenient for assembly. It can be understood that the position of the movable stopper 14 close to the lower end can also be rotatably installed on the main shaft 11, as long as the two ends of the movable stopper 14 can connect the lower sidewalls of the two segments of the helical groove 112 with the helix direction opposite to the rotation direction of the crankshaft 10 divided by the other helical groove 112 in this intersection area 1120.

[0059] In one embodiment, please refer to Figure 4 and Figure 5, a first rotating shaft 141 is connected to the lower end of the movable stopper 14. A first shaft hole 115 is provided on the corresponding main shaft 11. The first rotating shaft 141 is inserted into the first shaft hole 115, and the first rotating shaft 141 can rotate in the first shaft hole 115, so that the movable stopper 14 can swing in the intersection area 1120. This structure is simple, easy to process and manufacture, low in cost, and convenient for assembly. Understandably, a shaft pin can also be provided on the main shaft 11, and the movable stopper 14 is rotatably connected to the shaft pin, or the movable stopper 14 can be rotatably installed on the main shaft 11.

[0060] In one embodiment, the movable stopper 14 can be a stop rod or a baffle. Of course, the movable stopper 14 can also be a stop shaft, as long as it can guide the lubricating oil flow in one spiral groove 112 and block the other spiral groove 112.

[0061] In one embodiment, the two spiral grooves 112 can have one, two, three, four, five or other numbers of intersection areas 1120. Specifically, it can be set according to needs, and a movable stopper 14 is provided in each intersection area 1120. For example, when one intersection area 1120 is set, the spiral angle of each spiral groove 112 is 360 degrees. The more the number of intersection areas 1120 is set, and the multiple intersection areas 1120 are arranged at intervals along the axial direction of the main shaft 11, the larger the spiral angle of the corresponding spiral groove 112 is.

[0062] In one embodiment, the first rotating shaft 141 and the movable stopper 14 can be integrally formed to facilitate processing and manufacturing and ensure the connection strength between the first rotating shaft 141 and the movable stopper 14.

[0063] In one embodiment, please refer to Figures 1 to 4, there is one first oil hole 113. One ends of two spiral grooves 112 intersect at the first oil hole 113, and one ends of the two spiral grooves 112 communicate with the first oil hole 113. The crankshaft 10 further includes a separator 15. The separator 15 is arranged on the main shaft 11. The separator 15 separates one ends of the two spiral grooves 112, that is, the separator 15 separates one ends of the two spiral grooves 112 close to the first oil hole 113. That is to say, the corresponding end of one spiral groove 112 is located on one side of the separator 15, and the corresponding end of the other spiral groove 112 is located on the other side of the separator 15. Thus, when the crankshaft 10 rotates, the oil suction cavity 111 sucks lubricating oil. Under the action of centrifugal force, the lubricating oil moves along the inner wall of the oil suction cavity 111, and then enters the spiral groove 112 through the second oil hole 114. Since the two spiral grooves 112 have opposite spiral directions, when the crankshaft 10 rotates, there must be one spiral groove 112 that pumps oil towards the eccentric shaft 12. When one spiral groove 112 pumps the lubricating oil to the first oil hole 113, it is blocked by the separator 15 and will enter the first oil hole 113, and will not directly enter the other spiral groove 112, so that the lubricating oil gradually accumulates in the first oil hole 113. When the crankshaft 10 rotates, the distribution oil passage 121 in the eccentric shaft 12 is farther away from the rotation center axis of the crankshaft 10. Under the action of centrifugal force, the suction force generated by it at the first oil hole 113 will be greater than the suction force of the other spiral groove 112 at the first oil hole 113. Furthermore, most of the lubricating oil in the first oil hole 113 will enter the distribution oil passage 121 to ensure good oil supply volume, and good oil supply can be realized during both forward and reverse rotations of the crankshaft 10.

[0064] In one embodiment, please refer to Figures 2 to 4 , a second rotating shaft 153 is arranged on the separator 15, and the second rotating shaft 153 is located at the lower end of the separator 15. The lower end of the separator 15 refers to the end of the separator 15 close to the oil suction cavity 111. Thus, the separator 15 can be supported by the second rotating shaft 153. A second shaft hole 116 is formed on the main shaft 11. The second rotating shaft 153 is inserted into the second shaft hole 116, and the second rotating shaft 153 can rotate in the second shaft hole 116, so that the separator 15 can rotate on the main shaft 11.

[0065] Please refer to Figure 2 and Figure 3 , when the separator 15 can rotate on the main shaft 11 and the lower end of the separator 15 is rotatably installed on the main shaft 11, when the crankshaft 10 rotates, the separator 15 swings reversely under the action of centrifugal force. As Figure 2As shown, when the crankshaft 10 rotates forward, the second helical groove 1122 pumps oil towards the distribution oil passage 121, and the partition 15 swings towards the first helical groove 1121, thereby reducing the area of communication between the first helical groove 1121 and the first oil hole 113 to increase the resistance of the lubricating oil in the first oil hole 113 to enter the first helical groove 1121. Alternatively, the partition 15 can block the connection between the first helical groove 1121 and the first oil hole 113 to prevent the lubricating oil in the first oil hole 113 from entering the first helical groove 1121, so that more lubricating oil enters the distribution oil passage 121.

[0066] Similarly, as Figure 3 shown, when the crankshaft 10 rotates in reverse, the first helical groove 1121 pumps oil towards the distribution oil passage 121, and the partition 15 swings towards the second helical groove 1122, thereby reducing the area of communication between the second helical groove 1122 and the first oil hole 113 to increase the resistance of the lubricating oil in the first oil hole 113 to enter the second helical groove 1122. Alternatively, the partition 15 can block the connection between the second helical groove 1122 and the first oil hole 113 to prevent the lubricating oil in the first oil hole 113 from entering the second helical groove 1122, so that more lubricating oil enters the distribution oil passage 121.

[0067] In one embodiment, the length of the partition 15 is less than the inner diameter of the first oil hole 113. Here, the length of the partition 15 refers to the length of the partition 15 along the axial direction of the main shaft 11. Of course, the length of the partition 15 refers to the length along the radial direction of the second rotating shaft 153. The length of the partition 15 is set to be less than the inner diameter of the first oil hole 113 so that the partition 15 can swing flexibly on the main shaft 11. For example, when the crankshaft 10 rotates forward, the partition 15 can swing towards the first helical groove 1121, and when the crankshaft 10 rotates in reverse, the partition 15 can swing towards the second helical groove 1122.

[0068] The length of the partition 15 is greater than the width of the helical groove 112. Here, the length of the partition 15 refers to the length of the partition 15 along the axial direction of the main shaft 11. Of course, the length of the partition 15 refers to the length along the radial direction of the second rotating shaft 153. The length of the partition 15 is set to be greater than the width of the helical groove 112. Then, when the partition 15 rotates towards one helical groove 112, the side wall of the helical groove 112 can support the partition 15 to block the helical groove 112. For example, when the crankshaft 10 rotates forward, the partition 15 can swing towards the first helical groove 1121, and the end face of the first helical groove 1121 can limit the partition 15 to support the partition 15; when the crankshaft 10 rotates in reverse, the partition 15 can swing towards the second helical groove 1122, and the end face of the second helical groove 1122 can limit the partition 15 to support the partition 15.

[0069] Please refer toFigure 4 and Figure 6 The spacer 15 includes a separating section 151, an insertion section 152 and a second rotating shaft 153. The separating section 151 is located between the two spiral grooves 112. The second rotating shaft 153 is connected to the separating section 151 to support the separating section 151. The insertion section 152 is connected to the separating section 151. The insertion section 152 is inserted into the first oil hole 113. When the spacer 15 swings towards one of the spiral grooves 112, the communication area between the spiral groove 112 and the first oil hole 113 can be better reduced, or the communication part between the spiral groove 112 and the first oil hole 113 can be blocked. Moreover, the inner surface of the first oil hole 113 can also support and position the insertion section 152, and further support and position the spacer 15.

[0070] In one embodiment, please refer to Figure 1 and Figure 4 . The pitches of the two spiral grooves 112 are equal. In this way, when the crankshaft 10 rotates forward and backward, when its rotational speeds are approximately equal, the oil pumping amounts are also approximately equal, which is convenient for control. It can be understood that the pitches of the two spiral grooves 112 can also be set to be unequal. For example, the ends of the two spiral grooves 112 close to the oil suction cavity 111 are separated, and the two spiral grooves 112 are respectively communicated with the oil suction cavity 111 through two second oil holes 114.

[0071] In one embodiment, please refer to Figure 1 and Figure 4 . The number of the second oil holes 114 is one. The ends of the two spiral grooves 112 far from the eccentric shaft 12 intersect at the second oil hole 114, and the ends of the two spiral grooves 112 far from the eccentric shaft 12 are communicated with the second oil hole 114. In this way, the lubricating oil in the oil suction cavity 111 can directly reach the two spiral grooves 112 through the second oil hole 114, which is convenient for processing and manufacturing. In addition, only setting one second oil hole 114 can also ensure good strength of the main shaft 11. It can be understood that two second oil holes 114 can also be provided on the main shaft 11. The two second oil holes 114 are arranged at intervals, and the two spiral grooves 112 are respectively communicated with the two second oil holes 114. In this way, the lubricating oil can be respectively led to the two spiral grooves 112 through the two second oil holes 114, and the positions of the ends of the spiral grooves 112 far from the eccentric shaft 12 can be conveniently arranged.

[0072] Please refer to Figures 7 to 8 , Figure 7 which is the schematic side view structure of the crankshaft 10 provided in this embodiment. Figure 8 which is the schematic structure of the spacer 15 in the crankshaft 10 provided in this embodiment. The structure of this embodiment is in Figure 4Modifications based on [the previous structure]. In this embodiment, the separator 15 includes a separating section 151 and a second rotating shaft 153. The separating section 151 is located between two spiral grooves 112, and the second rotating shaft 153 is connected to the separating section 151 to support the separating section 151. When the separator 15 swings towards one spiral groove 112, the separating section 151 is supported and positioned by the end face of this spiral groove 112, so as to reduce the communication area between this spiral groove 112 and the first oil hole 113, or block the communication part between this spiral groove 112 and the first oil hole 113. The structure of this separator 15 is simpler, easier to manufacture, has a low cost, and is also convenient to assemble, and can rotate more flexibly on the main shaft 11.

[0073] Please refer to Figures 9 to 11 , Figure 9 which is a front view structural schematic diagram of the crankshaft 10 provided in this embodiment, where part of the structure is a perspective structure to show the flow path of the lubricating oil. Figure 10 which is a side view structural schematic diagram of the crankshaft 10 provided in this embodiment. Figure 11 is Figure 10 the enlarged view of part A in Figure 1 The structure of this embodiment is a modification based on

[0074] Please refer to Figure 9 , one end of the first spiral groove 1121 close to the first oil hole 113 is located on one side of the separator 15, and one end of the second spiral groove 1122 close to the first oil hole 113 is located on the other side of the separator 15; one end of the first spiral groove 1121 close to the first oil hole 113 and one end of the second spiral groove 1122 close to the first oil hole 113 are separated by the separator 15. When the lubricating oil is pumped to the first oil hole 113 through the first spiral groove 1121, it is blocked by the separator 15 and will not directly enter the second spiral groove 1122. In this way, the lubricating oil pumped by the first spiral groove 1121 will gather and enter the first oil hole 113. And the rotation radius of the second spiral groove 1122 is smaller than the rotation radius of the distribution oil passage 121 in the eccentric shaft 12. Then, under the action of centrifugal force, the suction force generated by the distribution oil passage 121 at the first oil hole 113 is greater, so that most of the lubricating oil in the first oil hole 113 will enter the distribution oil passage 121 to supply oil to each friction pair to ensure sufficient oil supply.

[0075] In one embodiment, please refer to Figure 10 and Figure 11, the separator 15 partially extends into the first oil hole 113, so that not only can the two spiral grooves 112 be better separated, but also the lubricating oil entering the first oil hole 113 from one spiral groove 112 can be better prevented from flowing back into the other spiral groove 112, increasing the path length and damping of the lubricating oil reaching the other spiral groove 112, and further enabling more lubricating oil in the first oil hole 113 to enter the distribution oil passage 121. It can be understood that when the width at the intersection of the two spiral grooves 112 is greater than the inner diameter of the first oil hole 113, the width at the intersection of the two spiral grooves 112 here refers to the width along the axial direction of the main shaft 11 at the intersection of the two spiral grooves 112. The separator 15 can also be installed only on the main shaft 11 and separate the two spiral grooves 112.

[0076] In one embodiment, the separator 15 partially extends into the distribution oil passage 121, that is, a partial structure of the separator 15 extends into the distribution oil passage 121. The separator 15 is entirely located at the corresponding position between the two spiral grooves 112 to separate the two spiral grooves 112. Therefore, the part of the separator 15 extending into the distribution oil passage 121 is also located at the corresponding position between the two spiral grooves 112. Extending the separator 15 into the distribution oil passage 121 can increase the path length and damping of the lubricating oil being sucked into the spiral groove 112, better prevent the lubricating oil from flowing back, and thus ensure sufficient oil supply.

[0077] In one embodiment, please refer to Figure 9 and Figure 11 , positioning grooves 117 are respectively formed on the opposite sides of the inner surface of the first oil hole 113. The opposite sides of the inner surface of the first oil hole 113 are the side of the first oil hole 113 close to the eccentric shaft 12 and the side far from the eccentric shaft 12. In this way, when installing the separator 15, the two sides of the separator 15 can be respectively inserted into the two positioning grooves 117, so as to install the separator 15 on the main shaft 11, which is convenient for assembly and can conveniently separate the two spiral grooves 112.

[0078] In one embodiment, please refer to Figure 9 and Figure 11 , the separator 15 divides the first oil hole 113 into two sub-oil holes 1131. For example, the separator 15 can be inserted into the first oil hole 113, and the parts of the first oil hole 113 on both sides of the separator 15 form two sub-oil holes 1131. The two sub-oil holes 1131 are respectively communicated with the two spiral grooves 112 to better prevent the lubricating oil pumped into the first oil hole 113 from one spiral groove 112 from entering the other spiral groove 112. The two sub-oil holes 1131 are communicated with the distribution oil passage 121 so that the lubricating oil in the sub-oil holes 1131 can enter the body distribution oil passage 121.

[0079] In one embodiment, two sub-oil holes 1131 arranged at intervals can be machined, and two spiral grooves 112 are respectively connected to the two sub-oil holes 1131. The portion between the two sub-oil holes 1131 forms a separator 15. This structure makes the separator 15 and the main shaft 11 an integral structure, ensuring the firm connection between the separator 15 and the main shaft 11.

[0080] In one embodiment, the separator 15 can use a flat part, such as a plate part. The separator 15 is inserted into the first oil hole 113 to divide the first oil hole 113 into two sub-oil holes 1131, and this structure can facilitate processing and production.

[0081] In one embodiment, the width of the separator 15 along the axial direction of the first oil hole 113 is less than the depth of the first oil hole 113. After installing the separator 15 in this way, the two sub-oil holes 1131 are connected at the bottom in the depth direction of the first oil hole 113. This can also enable each sub-oil hole 1131 to have a larger communication space with the distribution oil hole, so that the lubricating oil in the first oil hole 113 can enter the distribution oil hole.

[0082] Please refer to Figure 12 , Figure 12 FIG. is a schematic structural diagram of a partial area of the crankshaft 10 provided in the embodiment, which shows the structure of the first oil hole 113 and the separator 15. The structure of this embodiment is a modification based on Figure 11 . In this embodiment, the width of the separator 15 along the axial direction of the first oil hole 113 is greater than or equal to the depth of the first oil hole 113. After the separator 15 is installed in the first oil hole 113, the first oil hole 113 can be divided into two sub-oil holes 1131, and the two sub-oil holes 1131 are not connected within the range of the first oil hole 113. In this way, the lubricating oil pumped by one spiral groove 112 into the corresponding sub-oil hole 1131 can enter the distribution oil passage 121 more, reducing and avoiding the lubricating oil pumped by one spiral groove 112 from entering another spiral groove 112 and flowing back.

[0083] Please refer to Figure 13 , Figure 13 FIG. is a schematic structural diagram of a partial area of the crankshaft 10 provided in the embodiment, which shows the structure of the first oil hole 113 and the separator 15. The structure of this embodiment is a modification based on Figure 11Modifications based on this. In this embodiment, the separator 15 includes a separating section 151 and an inserting section 152. The inserting section 152 is connected to the separating section 151, and the inserting section 152 is inserted into the first oil hole 113 to facilitate fixing the inserting section 152 in the first oil hole 113, thereby supporting the separating section 151 and enabling the separating section 151 to separate the ends of the two spiral grooves 112 close to the crank 13. The inserting section 152 is provided to facilitate fixing the separator 15. The separating section 151 is provided to better cooperate in separating the two spiral grooves 112. Additionally, when the width at the intersection of the two spiral grooves 112 is greater than the inner diameter of the first oil hole 113, that is, when the width at the intersection of the two spiral grooves 112 close to the eccentric shaft 12 is greater than the inner diameter of the first oil hole 113, the width at the intersection of the two spiral grooves 112 here refers to the width along the axial direction of the main shaft 11 at the intersection of the two spiral grooves 112. The separating section 151 is provided to better separate the two spiral grooves 112.

[0084] In one embodiment, the inserting section 152 is connected to the first oil hole 113 by an interference fit to fix the inserting section 152 in the first oil hole 113 for convenient assembly.

[0085] In one embodiment, the inserting section 152 can be welded to the first oil hole 113 to fix the separator 15 to the main shaft 11. Of course, the separating section 151 can also be welded to the main shaft 11 to fix the separator 15 to the main shaft 11.

[0086] In one embodiment, the inserting section 152 can be adhered to the first oil hole 113 to fixedly install the separator 15. Of course, the separating section 151 can also be adhered to the main shaft 11 to fix the separator 15 to the main shaft 11.

[0087] In one embodiment, a fastening structure can also be provided. The fastening structure is fixed to the main shaft 11, and then the separator 15 is fixed to the main shaft 11. The fastening structure can be a pin shaft. Pin holes are respectively formed in the separator 15 and the main shaft 11 to fix the separator 15 to the main shaft 11 through the pin shaft. The fastening structure can also be a bushing, and the separator 15 is pressed against the main shaft 11 through the bushing to fix the separator 15 to the main shaft 11.

[0088] Please refer to Figure 14 , Figure 14 which is a schematic structural diagram of a partial area of the crankshaft 10 provided in the embodiment, showing the structure of the first oil hole 113 and the separator 15 part. The structure of this embodiment is based on Figure 9Modifications based on [the previous structure]. In this embodiment, the width at the intersection of the two spiral grooves 112 is less than or equal to the inner diameter of the first oil hole 113. The width at the intersection of the two spiral grooves 112 here refers to the width along the axial direction of the main shaft 11 at the intersection of the two spiral grooves 112. The separator 15 is inserted into the first oil hole 113, and the separator 15 divides the first oil hole 113 into two sub-oil holes 1131, that is, the two spiral grooves 112 are separated. The corresponding separator 15 only needs to be installed in the first oil hole 113, which is convenient for assembly and also convenient for the processing and manufacturing of the main shaft 11. For example, when machining the first oil hole 113, it only needs the inner diameter of the first oil hole 113 to be greater than or equal to the width at the intersection of the two spiral grooves 112.

[0089] In one embodiment, the separator 15 can use a flat shaft pin. Inserting it into the first oil hole 113 can separate the two spiral grooves 112, which is convenient for processing and manufacturing and has a low cost.

[0090] Please refer to Figure 15 , Figure 15 FIG. [shows] a schematic structural diagram of a partial area of the crankshaft 10 provided by the embodiment, in which the structure of the first oil hole 113 and the separator 15 is shown. The structure of this embodiment is a modification based on Figure 14 the previous structure. In this embodiment, the width at the intersection of the two spiral grooves 112 is less than or equal to the inner diameter of the first oil hole 113. The width at the intersection of the two spiral grooves 112 here refers to the width along the axial direction of the main shaft 11 at the intersection of the two spiral grooves 112. The separator 15 is inserted into the first oil hole 113 and divides the first oil hole 113 into two sub-oil holes 1131. The thickness of the separator 15 near the crank 13 is greater than the thickness of the separator 15 far from the crank 13. In this way, the connection area between each sub-oil hole 1131 and the corresponding spiral groove 112 can be larger, so as to facilitate the lubricating oil pumped by the spiral groove 112 to enter the sub-oil hole 1131; while the connection area between the sub-oil hole 1131 and the distribution oil passage 121 is smaller, which can increase the damping of the lubricating oil in the distribution oil passage 121 entering the sub-oil hole 1131. When the crankshaft 10 rotates, one spiral groove 112 pumps lubricating oil and accumulates in the corresponding sub-oil hole 1131, and the distribution oil passage 121 will form a negative pressure at the sub-oil hole 1131 to suck the lubricating oil. And the damping of the lubricating oil in the distribution oil passage 121 entering the other sub-oil hole 1131 increases, which can better prevent the lubricating oil from being sucked back by the other spiral groove 112.

[0091] In one embodiment, in the direction from the spiral groove 112 towards the crank 13, the thickness of the separator 15 is gradually increased. In this way, the lubricating oil can be guided into the distribution oil passage 121 through the side surface of the separator 15, which is beneficial for oil supply. And this structure is also convenient for the processing and manufacturing of the separator 15.

[0092] Please refer to Figure 16, Figure 16 Front view structural schematic diagram of the crankshaft 10 provided for the embodiment. The structure of this embodiment is a modification based on Figure 1 . In this embodiment, two first oil holes 113 are opened on the main shaft 11. The two first oil holes 113 are arranged at intervals, and the two first oil holes 113 are respectively communicated with the distribution oil passage 121, while the two spiral grooves 112 are respectively communicated with the two first oil holes 113. Thus, the two first oil holes 113 respectively communicate the two spiral grooves 112 with the distribution oil passage 121, so that the lubricating oil pumped by the spiral grooves 112 can enter the distribution oil passage 121 through the first oil holes 113. Since the two first oil holes 113 are arranged at intervals, when the crankshaft 10 rotates, the oil suction cavity 111 sucks the lubricating oil, and under the action of centrifugal force, the lubricating oil moves along the inner wall of the oil suction cavity 111 and then enters the spiral groove 112 through the second oil hole 114. Since the two spiral grooves 112 have opposite helix directions, when the crankshaft 10 rotates, there must be one spiral groove 112 that pumps oil towards the eccentric shaft 12. When one spiral groove 112 pumps the lubricating oil through the corresponding first oil hole 113 into the distribution oil passage 121, since the distribution oil passage 121 in the eccentric shaft 12 is farther from the rotation center axis of the crankshaft 10, under the action of centrifugal force, the suction force generated at the position close to the first oil hole 113 is greater than the suction force of the other spiral groove 112 at the first oil hole 113. As a result, most of the lubricating oil in the first oil hole 113 will enter the distribution oil passage 121 to ensure good oil supply and can achieve good oil supply during both forward and reverse rotations of the crankshaft 10. In addition, the two spiral grooves 112 are communicated with the same distribution oil passage 121 through the two first oil holes 113, which can reduce redundant processing, ensure the structural strength of the eccentric shaft 12, and can increase the turning radius of the end of the distribution oil passage 121 away from the main shaft 11, so that more lubricating oil can enter the eccentric shaft 12 to improve the oil supply capacity.

[0093] Please refer to Figure 17 , Figure 17 Front view structural schematic diagram of the crankshaft 10 provided for the embodiment. The structure of this embodiment is a modification based on Figure 16 . In this embodiment, there are two distribution oil passages 121, that is, two distribution oil passages 121 arranged at intervals are provided in the eccentric shaft 12, and the two distribution oil passages 121 are respectively communicated with the two first oil holes 113. In this way, the two spiral grooves 112 can pump oil to the two distribution oil passages 121 respectively, better avoiding the lubricating oil reflux in the distribution oil passage 121 to improve the oil supply capacity.

[0094] The crankshaft 10 of the embodiment of the present application has strong oil pumping ability and can achieve good oil pumping during both forward and reverse rotations. During forward and reverse rotations, it can ensure sufficient lubricating oil supply, improve the service life of the compressor using the crankshaft 10, and ensure the stable operation of the compressor.

[0095] An embodiment of the present application further provides a compressor. Please refer to Figure 1 at the same time. The compressor includes the crankshaft 10 described in any of the above embodiments. The compressor uses the crankshaft 10 of any of the above embodiments and has a strong ability to pump lubricating oil. When the compressor rotates forward and backward, it can ensure a good oil supply, ensure stable operation, and extend the service life. The compressor also has the technical effects of the crankshaft 10 of the above embodiments, which will not be elaborated here.

[0096] An embodiment of the present application further provides a refrigeration device, which includes the compressor described in any of the above embodiments. The refrigeration device uses the above compressor, operates more stably, has a long service life, and also has the technical effects of the compressor of the above embodiments, which will not be elaborated here.

[0097] The refrigeration device of the embodiment of the present application can be an air conditioner, a refrigerator, an outdoor unit, etc.

[0098] The above are only optional embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A crankshaft, comprising a crank, a main shaft provided on one side of the crank, and an eccentric shaft provided on the other side of the crank. An oil suction cavity is provided at one end of the main shaft away from the eccentric shaft. A distribution oil passage extending into the main shaft is provided in the eccentric shaft. Two spiral grooves are axially formed on the outer peripheral surface of the main shaft along the axis of the main shaft. The spiral directions of the two spiral grooves are opposite. A first oil hole communicating the spiral groove with the distribution oil passage and a second oil hole communicating the spiral groove with the oil suction cavity are formed on the main shaft; characterized in that, The two spiral grooves intersect to form an intersection area which is axially located between the first oil hole and the second oil hole along the main shaft. Each spiral groove is divided into two segments at the intersection area. The crankshaft further includes a movable stopper rotatably disposed in the intersection area. The movable stopper is used to connect the lower side walls of the two segments corresponding to the intersection area of the spiral groove whose spiral direction is opposite to the rotation direction of the crankshaft. The end of the movable stopper close to the oil suction cavity is mounted on the main shaft.

2. The crankshaft according to claim 1, characterized in that: The lower end of the movable stopper is located at the intersection of the lower side walls of the two spiral grooves.

3. The crankshaft according to claim 1, characterized in that: A first rotating shaft is provided at the lower end of the movable stopper. A first shaft hole is correspondingly formed on the main shaft. The first rotating shaft is rotatably mounted in the first shaft hole.

4. The crankshaft according to claim 1, characterized in that: The movable stopper is a stop bar or a baffle plate.

5. The crankshaft according to claim 1, characterized in that: The two spiral grooves intersect to form one intersection area; alternatively, the two spiral grooves intersect to form a plurality of intersection areas, and the plurality of intersection areas are spaced apart axially along the main shaft. Each intersection area is provided with the movable stopper.

6. The crankshaft according to any one of claims 1-5, characterized in that: The number of the first oil holes is one. One ends of the two spiral grooves intersect and communicate with the first oil hole. The crankshaft further includes a separator for separating one ends of the two spiral grooves close to the first oil hole. The separator is disposed on the main shaft.

7. The crankshaft according to claim 6, characterized in that: Positioning grooves are formed on opposite sides of the inner surface of the first oil hole. Two sides of the separator are respectively inserted into the two positioning grooves.

8. The crankshaft according to claim 6, characterized in that: A second rotating shaft is provided at the lower end of the separator. A second shaft hole is correspondingly formed on the main shaft. The second rotating shaft is rotatably mounted in the second shaft hole.

9. The crankshaft according to claim 8, characterized in that: The length of the separator along the axial direction of the main shaft is greater than the width of the spiral groove and less than the inner diameter of the first oil hole.

10. The crankshaft according to claim 6, characterized in that: The separator includes a separating section fitted between the two spiral grooves and an inserting section inserted into the first oil hole. The inserting section is fixed in the first oil hole.

11. The crankshaft according to any one of claims 1-5, characterized in that: Two first oil holes are formed on the main shaft. The two first oil holes are spaced apart. The two first oil holes are respectively communicated with the two spiral grooves. Both of the two first oil holes are communicated with the distribution oil passage.

12. The crankshaft according to any one of claims 1-5, characterized in that: The number of the second oil holes is one. The other ends of the two spiral grooves intersect and communicate with the second oil hole.

13. The crankshaft according to any one of claims 1-5, characterized in that: The pitches of the two spiral grooves are equal.

14. A compressor, characterized in that: Comprising a crankshaft according to any one of claims 1-13.

15. A refrigeration device, characterized in that: Comprising a compressor according to claim 14.

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