Crankshaft oil guide assembly and compressor

Abstract

The present invention provides a crankshaft oil guide assembly and a compressor, the crankshaft oil guide assembly includes a crankshaft and a vane; the crankshaft has an oil guide passage arranged axially through the interior, the vane is arranged axially in the oil guide passage, the crankshaft has a first end in the radial direction, the first end has a first recessed portion, one end of the vane has a first protrusion arranged in the radial direction, the first protrusion is used to snap into the first recessed portion to limit the circumferential freedom of the vane relative to the crankshaft. The present invention has the advantages of low processing requirements, high pass rate, and high installation precision, and can solve the problems of the prior art that special processing equipment and professional installers are required, the pass rate is low, and the installation precision cannot be guaranteed.

Description

Technical Field

[0001] The invention relates to the field of compressors, and in particular to a crankshaft oil guide assembly and a compressor. Background Art

[0002] In existing refrigeration compressors, whether reciprocating piston compressors, rotary piston compressors or scroll compressors, the centrifugal oiling method of installing spiral vanes in the crankshaft center oil hole has more advantages than the oil pump oiling method and is the current mainstream structure. With the expansion of rotary compressors into different fields, the displacement range of rotary compressors is getting larger and larger, and the lubrication environment of large-displacement rotary compressors is more severe, and the requirements for pump oil lubrication are getting higher and higher. It mainly focuses on two aspects. First, after the installation is completed, a high installation accuracy needs to be guaranteed. Second, during the installation process, it is hoped that its processing is simple and the qualified rate is high.

[0003] The centrifugal oiling structure currently used in the industry adopts an interference fit, which requires special processing equipment and professional installation personnel, has a low pass rate, and cannot guarantee installation accuracy. Summary of the invention

[0004] The purpose of the present invention is to provide a crankshaft oil guide assembly and a compressor to solve the problem that the current centrifugal oiling structure requires special processing equipment and professional installers, resulting in the inability to ensure installation accuracy.

[0005] In order to solve the above technical problems, the present invention provides a crankshaft oil guide assembly, including a crankshaft and a rotary vane; the interior of the crankshaft has an oil guide channel arranged axially through, the rotary vane is axially arranged in the oil guide channel, the crankshaft has a first end in the radial direction, the first end has a first recessed portion, one end of the rotary vane has a first protrusion arranged in the radial direction, the first protrusion is used to engage in the first recessed portion to limit the circumferential freedom of the rotary vane relative to the crankshaft.

[0006] Optionally, the crankshaft has a base surface, and the base surface passes through the central axis of the oil guide channel and the first recessed portion; the side wall of the crankshaft has at least one oil outlet hole connected to the oil guide channel; the base surface and at least one of the oil outlet holes satisfy the following relationship:

[0007] tan(θ-εH)≥0

[0008] Wherein, θ is the angle between at least one of the oil outlet holes and the base surface along the rotation direction of the vane, ε is the curvature of the vane, and H is the axial distance between the same oil outlet hole and the first end.

[0009] Optionally, the side wall of the crankshaft has more than two oil outlet holes, and each of the oil outlet holes satisfies: tan(θ-εH)≥0.

[0010] Optionally, the crankshaft includes an end cover, which is arranged at the first end and is used to limit the axial freedom of the rotor toward the first end.

[0011] Optionally, the end cover includes more than two claws, which are arranged at one end of the end cover close to the crankshaft and distributed along the circumference of the end cover, and the end cover is interference fit with the oil guide channel through the claws.

[0012] Optionally, the first recessed portion is disposed at an end of the end cover close to the crankshaft.

[0013] Optionally, a second recessed portion is provided on the side wall of the oil guide channel, and a second protruding portion is provided at one end of the end cover close to the crankshaft, and the second protruding portion is used to engage with the second recessed portion to limit the circumferential freedom of the end cover relative to the crankshaft.

[0014] Optionally, the first recessed portion is disposed on a side wall of the oil guiding channel.

[0015] Optionally, the first recessed portion and the first raised portion are both trapezoidal in cross-section along the axial direction of the oil guiding passage, wherein the shorter bottom side of the trapezoid is away from the first end.

[0016] In order to solve the above technical problem, the present invention further provides a compressor, comprising the above crankshaft oil guide assembly and an oil storage chamber, wherein the first end is arranged in the oil storage chamber.

[0017] Compared with the prior art, the crankshaft oil guide assembly and the compressor provided by the present invention include a crankshaft and a vane; the crankshaft has a first recessed portion, and one end of the vane has a first protrusion, and the first protrusion is used to engage in the first recessed portion to limit the circumferential freedom of the vane relative to the crankshaft. The above scheme replaces the scheme of limiting the circumferential freedom of the vane relative to the crankshaft by using an interference fit, and solves the problem that the current centrifugal oiling structure requires special processing equipment and professional installers, resulting in the inability to ensure installation accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Those skilled in the art will appreciate that the accompanying drawings are provided for a better understanding of the present invention and do not constitute any limitation on the scope of the present invention.

[0019] Figure 1 It is a front view of the crankshaft of the first embodiment of the present invention;

[0020] Figure 2 It is a cross-sectional view of the crankshaft oil guide assembly along the axial direction according to the first embodiment of the present invention;

[0021] Figure 3a is a schematic diagram of the angle θ of the first embodiment of the present invention;

[0022] Figure 3b is another schematic diagram of the angle θ according to the first embodiment of the present invention;

[0023] Figure 4 It is a schematic diagram of one end of a rotary vane having a first protrusion according to a second embodiment of the present invention;

[0024] Figure 5 is a schematic cross-sectional view of a first recessed portion of a second embodiment of the present invention;

[0025] Figure 6 is a schematic diagram of a crankshaft according to a third embodiment of the present invention;

[0026] Figure 7 is a schematic diagram of an end cover according to a third embodiment of the present invention;

[0027] Figure 8 This is a front view of the crankshaft oil guide assembly and the crankshaft of the third embodiment of the present invention.

[0028] In the attached figure:

[0029] 10-crankshaft; 20-rotor; 30-base surface; 40-end cover;

[0030] 11 - oil guide channel; 12 - first end; 13 - first recessed portion; 14 - oil outlet hole; 15 - second recessed portion; 21 - first raised portion; 41 - claw; 42 - second raised portion. DETAILED DESCRIPTION

[0031] In order to make the purpose, advantages and features of the present invention clearer, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the drawings are all in a very simplified form and are not drawn to scale, and are only used to conveniently and clearly assist in explaining the purpose of the embodiments of the present invention. In addition, the structure shown in the drawings is often a part of the actual structure. In particular, the emphasis of each drawing is different, and sometimes different scales are used.

[0032] As used in the present invention, the singular forms "one", "an" and "the" include plural objects, the term "or" is generally used to include the meaning of "and / or", the term "several" is generally used to include the meaning of "at least one", and the term "at least two" is generally used to include the meaning of "two or more". In addition, the terms "first", "second" and "third" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first", "second" and "third" may explicitly or implicitly include one or at least two of the features, "one end" and "the other end" and "the proximal end" and "the distal end" generally refer to two corresponding parts, which include not only the endpoints, and the terms "installed", "connected" and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral body; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. In addition, as used in the present invention, an element disposed on another element generally only indicates that there is a connection, coupling, cooperation or transmission relationship between the two elements, and the connection, coupling, cooperation or transmission between the two elements may be direct or indirect through an intermediate element, and cannot be understood as indicating or implying the spatial position relationship between the two elements, that is, one element may be in any orientation such as inside, outside, above, below or on one side of another element, unless otherwise clearly indicated in the content. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0033] The core idea of ​​the present invention is to provide a crankshaft oil guide assembly and a compressor to solve the problems of the current centrifugal oiling structure, which requires special processing equipment and professional installation personnel, has a low pass rate and cannot guarantee installation accuracy.

[0034] The following description is given with reference to the accompanying drawings.

[0035] [Example 1]

[0036] Please refer to Figures 1 to 3b ,in, Figure 1 It is a front view of the crankshaft of the first embodiment of the present invention; Figure 2 It is a cross-sectional view of the crankshaft oil guide assembly along the axial direction according to the first embodiment of the present invention; Figure 3a is a schematic diagram of the angle θ of the first embodiment of the present invention; Figure 3b FIG. 4 is another schematic diagram of the angle θ according to the first embodiment of the present invention.

[0037] Figure 1 and Figure 2A crankshaft oil guide assembly is shown, including a crankshaft 10 and a rotary vane 20; the crankshaft 10 has an oil guide passage 11 axially extending therethrough, the rotary vane 20 is axially arranged in the oil guide passage 11, the crankshaft 10 has a first end 12 radially, the first end 12 has a first recessed portion 13, one end of the rotary vane 20 has a first protrusion 21 radially arranged, the first protrusion 21 is used to engage in the first recessed portion 13 to limit the circumferential freedom of the rotary vane 20 relative to the crankshaft 10.

[0038] Need to understand, Figure 1 The observation direction is from the outside of the first end 12 to the first end 12 . Figure 2 is along Figure 1 The base surface 30 shown in FIG. 1 is cut at a position where the base surface 30 is located, and for the convenience of explanation, Figure 2 The outer contour structure of the crankshaft is not shown. Those skilled in the art can understand and set the outer structure of the crankshaft using the existing technology, so it is not described in detail here.

[0039] With such configuration, the matching mode of the vane 20 and the oil guide channel 11 is replaced from interference fit to limited assembly, which obtains many benefits. First, the interference fit has high processing accuracy requirements for the width of the vane 20 and the inner diameter of the oil guide channel 11. If the width of the vane 20 is too wide or the inner diameter of the oil guide channel 11 is too narrow, the two cannot be assembled; on the contrary, the bonding force between the two is too small, and it is easy to loosen during work, thus causing the entire mechanism to fail. By adopting the scheme in this embodiment, the relationship between the width of the vane 20 and the inner diameter of the oil guide channel 11 becomes a clearance fit, which reduces the processing accuracy requirements. Secondly, the interference fit also has high requirements for the assembler. As a specially designed part, the vane 20 has high requirements for its shape and size during work. Interference assembly often requires a large external force, so this external force used for assembly is likely to affect the vane 20, causing it to deform significantly, affecting its working performance, and in more serious cases, it may cause the vane 20 to break, resulting in a waste of materials and time. In addition, if the coaxiality of the vane 20 and the oil guide channel 11 is not guaranteed during the assembly process, the vane 20 will also be deformed due to the restraining force of the side wall of the oil guide channel 11, affecting the working performance. It is found from the current production practice that even if specially designed processing equipment is used with experienced assemblers, the final assembly result is not ideal and the off-line rate is high. However, by adopting the scheme in this embodiment, there is almost no requirement for the assembler, the required assembly force is also very small, and no specially designed processing equipment is required. Finally, since the current compressor has high requirements for lubrication, there are also high requirements for the oil output of the oil guide assembly, and thus there are also high requirements for the relative position of the vane 20 and the oil guide channel 11. In the interference assembly process, there is a lack of reference objects, and it is difficult to assemble the vane 20 to a better angle. By adopting the scheme in this embodiment, the first recessed portion 13 can also be used as a reference standard for positioning. As long as it is ensured to be in a better position when processing the first recessed portion 13, it can be ensured that the finally assembled vane 20 is also in a better position. In summary, compared with the prior art, the solution shown in this embodiment has the advantages of low processing requirements, high pass rate, and high installation precision. It can solve the problems in the prior art that special processing equipment and professional installers are required, the pass rate is low, and the installation precision cannot be guaranteed.

[0040] In an exemplary embodiment, the crankshaft 10 has a base surface 30, and the base surface 30 passes through the central axis of the oil guide channel 11 and the first recessed portion 13; the side wall of the crankshaft 10 has at least one oil outlet hole 14 connected to the oil guide channel; the base surface 30 and at least one of the oil outlet holes 14 satisfy the following relationship:

[0041] tan(θ-εH)≥0

[0042] Wherein, θ is the angle between at least one of the oil outlet holes 14 and the base surface 30 along the rotation direction of the rotary vane 20 , ε is the curvature of the rotary vane, and H is the axial distance between the same oil outlet hole 14 and the first end 12 .

[0043] θ rotates along the rotation direction of the rotary vane 20, and can be combined with Figure 3a and 3b understand, Figure 3a and 3b The observation direction and Figure 1 Same. Figure 3a In the embodiment, the rotary blade 20 is right-handed (not shown in the figure). Figure 3a Observed from the observation direction, the rotation direction of the rotary vane is counterclockwise. At this time, the central axis of the oil outlet hole 14 is rotated counterclockwise until it meets the base surface 30. The angle it passes is θ. If observed from the opposite direction, the rotation direction of the rotary vane is clockwise. At this time, the central axis of the oil outlet hole 14 also needs to be rotated clockwise until it meets the base surface 30. From the above description, it can be found that no matter the observation direction selected by the technician is Figure 3a The direction of observation is still related to Figure 3a In the opposite direction, the direction of rotation of the angle θ is always the same as the direction of rotation of the rotor. Figure 3b ,exist Figure 3b In the embodiment, the rotary blade 20 is left-handed (not shown in the figure). Figure 3b From the observation direction, the rotation direction of the vane is clockwise. At this time, the central axis of the oil outlet hole 14 starts to rotate clockwise until it encounters the base surface 30. The angle it passes through is θ. If observed from the opposite direction, the rotation direction of the vane is counterclockwise. At this time, the central axis of the oil outlet hole 14 also needs to be rotated counterclockwise until it encounters the base surface 30. In summary, the following conclusion can be drawn, regardless of whether the vane 20 is left-handed or right-handed, and the observation direction is from the outside of the first end 12 to the first end 12 or vice versa, the angle θ is the same as the rotation direction of the vane 20. Therefore, the reference standard for obtaining the angle θ can be set to the rotation direction of the vane. In addition, the vane curvature ε can be obtained by the following formula, which is an inherent property of the vane 20:

[0044] The curvature of the vane ε = the total angle of the vane rotation / the length of the rotating part of the vane.

[0045] The arrangement of the oil outlet hole 14 is related to the specific structure of the compressor. Generally speaking, an oil outlet hole should be arranged at each part that needs lubrication. Through experiments, the inventors found that when the angle between the cross section of the rotor 20 at the oil outlet hole 14 and the oil outlet hole 14 is within 90°, a higher oil output can be ensured, thereby ensuring a better oil output effect. The angle can be obtained as follows:

[0046] Step 1) Calculate

[0047] Step 2) Add or subtract an integer of 180° until it falls on [0,180°). In summary, in order to obtain a better oiling effect, you can first perform steps 1) and 2), and then:

[0048] Step 3) Order By solving the equation, the optimal positioning size of the first recessed portion 13 can be obtained.

[0049] After observation, step 1), step 2) and step 3) can be combined and simplified to make tan(θ-εH)≥0. Therefore, it is only necessary to change the positioning size of the first recessed portion 13 to make tan(θ-εH)≥0 to obtain a better oil discharge effect.

[0050] Preferably, the side wall of the crankshaft is provided with more than two oil outlet holes 14 , and each of the oil outlet holes 14 satisfies: tan(θ-εH)≥0.

[0051] When the positioning size of the first recessed portion 13 is reasonably selected so that the above criterion holds true for each of the oil outlet holes 14 , the components corresponding to each of the oil outlet holes 14 can obtain better lubrication effects, thereby enabling the compressor in which the crankshaft oil guide assembly is located to obtain better lubrication effects overall.

[0052] Preferably, please refer to Figure 2 The crankshaft 10 includes an end cover 40, which is disposed at the first end 12 and is used to limit the axial freedom of the rotor 20 toward the first end.

[0053] Preferably, the end cover includes more than two claws 41 , which are disposed at one end of the end cover 40 close to the crankshaft 10 and distributed along the circumference of the end cover 40 , and the end cover 40 is interference fit with the oil guide channel 11 through the claws 41 .

[0054] Through the above configuration, it is firstly ensured that the end cover 40 and the oil guide channel 11 do not have axial displacement, and further, the axial freedom of the rotor 20 is limited by the end cover 40. At the same time, the existence of the claw 41 also facilitates subsequent maintenance and disassembly.

[0055] In combination with the above description, the main purpose of this embodiment is to replace the cooperation mode of the rotary vane 20 and the oil guide channel 11 from interference fit to limit assembly by setting the first recessed portion 13 and the first raised portion 21, which has the advantages of low processing requirements, high qualified rate and high installation precision, and can solve the problems in the prior art that special processing equipment and professional installers are required, the qualified rate is low, and the installation precision cannot be guaranteed.

[0056] [Example 2]

[0057] Please refer to Figure 4 and Figure 5 ,in Figure 4 It is a schematic diagram of one end of a rotary vane having a first protrusion according to a second embodiment of the present invention; Figure 5 FIG. 4 is a schematic cross-sectional view of a first recessed portion according to a second embodiment of the present invention.

[0058] This embodiment provides a crankshaft oil guide assembly. In this embodiment, the first recessed portion 13 is disposed on the side wall of the oil guide passage 11. The first recessed portion 13 and the first raised portion 21 are both trapezoidal in cross-section along the axial direction of the oil guide passage 11, wherein the shorter bottom side of the trapezoid is away from the first end 12.

[0059] Such a configuration can better limit the circumferential and axial freedom of the rotary vane 20 and can further reduce the precision requirements on parts during processing.

[0060] [Example 3]

[0061] Please refer to Figures 6 to 8 ,in Figure 6 is a schematic diagram of a crankshaft according to a third embodiment of the present invention; Figure 7 is a schematic diagram of an end cover according to a third embodiment of the present invention; Figure 8 This is a front view of the crankshaft oil guide assembly and the crankshaft of the third embodiment of the present invention.

[0062] This embodiment provides a crankshaft oil guide assembly. In this embodiment, the first recessed portion 13 is disposed at one end of the end cover 40 close to the crankshaft 10. A second recessed portion 15 is provided on the side wall of the oil guide passage 11, and a second protruding portion 42 is provided at one end of the end cover 40 close to the crankshaft 10. The second protruding portion 42 is used to engage in the second recessed portion 15 to limit the circumferential freedom of the end cover 40 relative to the crankshaft.

[0063] Need to understand, Figure 7 In the embodiment, the two claws 41 are configured as the second protrusions 42 in order to save processing costs. However, the second protrusions 42 may also be a structure independent of the claws 41.

[0064] Through the above analysis, there is an optimal solution for the relative position relationship between the first recessed portion 13 and the crankshaft 10, but this optimal solution has a functional relationship with the vane curvature ε of the vane 20, that is, when the vane curvature of the vane 20 changes, this optimal solution will also change accordingly. If you want to continue to maintain a better oil discharge effect, the position and size of the first recessed portion 13 need to change accordingly. Imagine the following scenario: a compressor has an original vane 20 with a vane curvature of ε1, but all other parts are intact. At this time, there is only a vane 20 with a vane curvature of ε2 in the factory. If the first recessed portion 13 is set on the side wall of the oil guide channel 11, if you want to maintain a better oil discharge effect, then you must reprocess the main part of the crankshaft 10, and the maintenance cost is relatively high.

[0065] In this embodiment, the first recessed portion 13 is disposed on the end cover 40, avoiding the above-mentioned risks. Under the premise of maintaining a relatively good oil discharge effect, if the vane curvature ε of the vane 20 changes, only a new end cover 40 with a changed positioning size of the first recessed portion 13 is required to match the new vane curvature ε, and the maintenance cost is low. In general, such a configuration decouples the intrinsic functional relationship between the dimensional parameters of the crankshaft 10 and the curvature ε of the vane 20, making it convenient to match the same crankshaft 10 with different vanes 20, making the design more flexible and lowering the maintenance cost.

[0066] [Example 4]

[0067] The present embodiment provides a compressor, including a crankshaft oil guide assembly and an oil storage chamber. The specific structural details of the crankshaft oil guide assembly can refer to Example 1, Example 2 or Example 3. Among them, the first end is arranged in the oil storage chamber. When stationary, the first end 12 of the crankshaft 10 is already filled with engine oil. When the crankshaft rotates, the engine oil moves upward along the inclined surface formed by the vane 20, and when encountering the oil outlet 14, it is thrown out of the oil guide channel 11 by the action of centrifugal force, thereby providing lubrication for other parts of the compressor. The compressor also has the beneficial effects brought by the crankshaft oil guide assembly. Those skilled in the art can set other components and structures of the compressor according to the actual existing technology, which will not be described in detail here.

[0068] It should be noted that the various embodiments in this specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments, and the same and similar parts between the various embodiments can be referred to each other. The above description is only a description of the preferred embodiments of the present invention, and does not limit the scope of the present invention. Any changes and modifications made by ordinary technicians in the field of the present invention based on the above disclosure are within the scope of protection of the claims.

Claims

1. A crankshaft oil guide assembly, characterized in that: The invention comprises a crankshaft and a rotary vane; the crankshaft has an oil guide passage which is axially penetrated therein, the rotary vane is axially arranged in the oil guide passage, the crankshaft has a first end, the first end has a first recessed portion, one end of the rotary vane has a first protrusion which is radially arranged, the first protrusion is used to engage in the first recessed portion, so as to limit the circumferential freedom of the rotary vane relative to the crankshaft; The crankshaft has a base surface, and the base surface passes through the central axis of the oil guide channel and the first recessed portion; the side wall of the crankshaft has more than two oil outlet holes connected to the oil guide channel; the base surface and each of the oil outlet holes satisfy the following relationship: ； Wherein, θ is the angle between each oil outlet hole and the base surface along the rotation direction of the vane, ε is the curvature of the vane, and H is the axial distance between the same oil outlet hole and the first end; The crankshaft includes an end cover, which is arranged at the first end and is used to limit the axial freedom of the rotor toward the first end.

2. A crankshaft oil guide assembly according to claim 1, characterized in that: The end cover includes more than two claws, which are arranged at one end of the end cover close to the crankshaft and distributed along the circumference of the end cover. The end cover is interference-fitted with the oil guide channel through the claws.

3. A crankshaft oil guide assembly according to claim 1, characterized in that: The first recessed portion is disposed at one end of the end cover close to the crankshaft.

4. A crankshaft oil guide assembly according to claim 3, characterized in that: A second recessed portion is provided on the side wall of the oil guide channel, and a second protruding portion is provided at one end of the end cover close to the crankshaft. The second protruding portion is used to engage in the second recessed portion to limit the circumferential freedom of the end cover relative to the crankshaft.

5. A crankshaft oil guide assembly according to claim 1, characterized in that: The first recessed portion is disposed on a side wall of the oil guiding channel.

6. A crankshaft oil guide assembly according to claim 5, characterized in that: The axial cross-sections of the first recessed portion and the first raised portion along the oil guiding passage are both trapezoidal, wherein the shorter bottom side of the trapezoid is away from the first end.

7. A compressor, characterized in that: It comprises a crankshaft oil guide assembly and an oil storage cavity as described in any one of claims 1 to 6, wherein the first end is arranged in the oil storage cavity.

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