High-speed differential lubricating structure and differential

Abstract

The utility model discloses a high-speed differential lubrication structure and a differential, and belongs to the field of differential lubrication. The lubricating structure comprises a carrier, an oil groove is formed in one side of the carrier, the oil groove comprises a flowing oil channel and a closed oil channel, the flowing oil channel is communicated with the closed oil channel, the flowing oil channel penetrates through the edge of the carrier to be communicated with the outside, and the edge of the carrier blocks the end of the closed oil channel; and the cover plate covers the oil groove. The technical problem that a matched friction pair is sintered due to the fact that a traditional lubricating structure is large in heat productivity and insufficient in lubrication is solved.

Description

Technical Field

[0001] The utility model relates to the technical field of differential lubrication, in particular to a high-speed differential lubrication structure and a differential. Background Art

[0002] When the differential lock is not opened, the left and right half-shaft gears inside the differential will have different speeds due to different external loads, and the speed transmitted by the differential to the output ends on both sides of the rear axle is inconsistent. At this time, there will be a certain speed difference between the half-shaft gears and the differential housing. In general design, the maximum speed difference of the differential in the CVT working section is between 400-500r / min. In order to adapt to the differential, a wear-resistant gasket will be designed between the differential housing and the half-shaft gears. The wear-resistant gasket can rotate relative to the differential housing and the half-shaft gears. During this period, the differential is internally sloughed by the rotation of the gear train and the differential housing, so that there is a certain lubrication between the friction pairs and the heat generated by the friction pairs is reduced. The end face of the half-shaft gear is usually a smooth plane, and the gasket has a certain lubrication groove or no lubrication oil groove. However, the speed difference of the mating friction pair on the differential applicable to CVT can reach more than 800r / min. Therefore, the traditional lubrication structure will cause the mating friction pair to sinter due to high heat generation and insufficient lubrication, and then fail. Utility Model Content

[0003] The main purpose of the utility model is to provide a high-speed differential lubrication structure and a differential, aiming to improve the technical problem of insufficient lubrication of the traditional lubrication structure.

[0004] In order to achieve the above object, the utility model proposes a high-speed differential lubrication structure, the lubrication structure comprising:

[0005] A carrier, wherein an oil groove is provided on one side of the carrier, the oil groove comprises a circulating oil passage and a closed oil passage, the circulating oil passage is communicated with the closed oil passage, the circulating oil passage passes through the edge of the carrier and is communicated with the outside, and the edge of the carrier blocks the end of the closed oil passage;

[0006] A cover plate covers the oil tank.

[0007] Optionally, in an embodiment of the present invention, the carrier is a half-shaft gear, and the oil groove is opened on the friction pair end surface of the half-shaft gear.

[0008] Optionally, in an embodiment of the utility model, the oil flow channel is an arc-shaped structure, the arc-shaped structure protrudes toward the axial direction of the end surface, and both ends of the arc-shaped structure pass through the edge of the end surface to connect to the outside of the half-shaft gear.

[0009] Optionally, in an embodiment of the present invention, the midpoint of the arc-shaped structure is connected to the closed oil channel.

[0010] Optionally, in an embodiment of the utility model, at least two oil flow passages are provided.

[0011] Optionally, in an embodiment of the present utility model, two oil circulation passages are provided, and the two oil circulation passages are symmetrically distributed.

[0012] Optionally, in one embodiment of the utility model, a mounting hole is opened at the axis center of the end face, and the closed oil channel includes a linear oil channel and a surrounding oil channel. The surrounding oil channel is opened around the outer circumference of the mounting hole, one end of the linear oil channel is connected to the surrounding oil channel, and the edge of the end face closes the other end of the linear oil channel.

[0013] Optionally, in an embodiment of the present invention, the cover plate rotates synchronously with the half-shaft gear.

[0014] Optionally, in an embodiment of the utility model, the cover plate is provided with a regular hexagonal limiting hole.

[0015] To achieve the above object, the utility model also proposes a differential, comprising the lubrication structure described above.

[0016] Compared with the prior art, the utility model can at least achieve the following beneficial effects. The lubrication structure is mainly used in high-speed differentials. When the speed difference of the differential is large, a large amount of heat will be generated at the half-axle gear due to high-speed rotation. In order to speed up the heat dissipation, the lubrication structure is designed so that the lubricating oil can lubricate the differential and take away the heat when the differential is working. When the speed difference is large, the high-speed rotation of the differential will promote the circulation speed of the lubricating oil to improve the heat dissipation effect. However, the flow speed of the lubricating oil in the oil groove is not the faster the better. The high-speed rotation of the differential also makes the lubricating oil pass through the oil groove quickly, so that the oil film cannot be generated at the oil groove, resulting in direct contact between adjacent surfaces and friction, which increases the generation of heat and causes wear, which is contrary to the original intention of the lubrication structure design. In order to solve the above problems, the lubrication structure proposed in this scheme includes a circulating oil channel and a closed oil channel. During the circulation of the lubricating oil, the circulating oil channel plays the role of supplying oil to the closed oil channel and provides a path for the circulation of the lubricating oil. The lubricating oil in the circulating oil channel flows quickly when the differential runs at high speed to dissipate heat. The lubricating oil in the closed oil channel is difficult to be thrown out by the high-speed running differential. Therefore, it can form an oil film between adjacent surfaces to prevent direct contact between adjacent surfaces and provide lubrication, thereby solving the technical problems of high heat generation and insufficient lubrication of the current lubrication structure when applied to high-speed differentials. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying creative work.

[0018] Figure 1 This is a schematic diagram of the structure of a high-speed differential lubrication structure of the utility model;

[0019] Figure 2 It is the front view of the oil tank;

[0020] Figure 3 is a schematic diagram of the cover plate structure;

[0021] Figure 4 It is the structural schematic diagram of the friction pair of the half-shaft gear;

[0022] Figure 5 for Figure 4 A partial enlarged view of point A in the middle.

[0023] Description of Figure Numbers:

[0024] 100, carrier; 110, end face; 111, mounting hole; 200, oil groove; 210, circulating oil channel; 220, closed oil channel; 221, linear oil channel; 222, surrounding oil channel; 300, cover plate; 310, limiting hole;

[0025] The realization of the purpose, functional features and advantages of the utility model will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0026] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0027] It should be noted that all directional indications (such as up, down, left, right, front, back...) in the embodiments of the present invention are only used to explain the relative position relationship, movement status, etc. between the various components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0028] In the present invention, unless otherwise clearly specified and limited, the terms "connection", "fixation", etc. should be understood in a broad sense. For example, "fixation" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0029] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the utility model, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In addition, the meaning of "and / or" appearing in the full text includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme that satisfies both A and B. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the utility model.

[0030] Reference Figure 1~Figure 5 The utility model proposes a high-speed differential lubrication structure, the lubrication structure comprising:

[0031] The carrier 100 has an oil groove 200 formed on one side of the carrier 100. The oil groove 200 includes a circulating oil passage 210 and a closed oil passage 220. The circulating oil passage 210 is connected to the closed oil passage 220. The circulating oil passage 210 penetrates the edge of the carrier 100 and is connected to the outside. The edge of the carrier 100 blocks the end of the closed oil passage 220.

[0032] The cover plate 300 covers the oil tank 200 .

[0033] This lubrication structure is mainly used in high-speed differentials. When the speed difference of the differential is large, a large amount of heat will be generated at the half-axle gear due to high-speed rotation. In order to speed up the heat dissipation, the lubrication structure is designed so that the lubricating oil can lubricate the differential and take away the heat when the differential is working. When the speed difference is large, the high-speed rotation of the differential will promote the circulation speed of the lubricating oil to improve the heat dissipation effect. However, the flow speed of the lubricating oil in the oil groove 200 is not as fast as possible. The high-speed rotation of the differential also makes the lubricating oil pass through the oil groove 200 quickly, so that the oil film cannot be generated at the oil groove 200, resulting in direct contact between adjacent surfaces and friction, which increases the heat generation and causes wear, which is contrary to the original intention of the lubrication structure design. In order to solve the above problems, the lubrication structure proposed in this scheme includes a circulating oil channel 210 and a closed oil channel 220. During the circulation of the lubricating oil, the circulating oil channel 210 plays the role of supplying oil to the closed oil channel 220 and provides a path for the circulation of the lubricating oil. The lubricating oil in the circulating oil passage 210 flows rapidly when the differential is running at high speed to dissipate heat, and the lubricating oil in the closed oil passage 220 is difficult to be thrown out by the high-speed running differential, so it can form an oil film between adjacent surfaces to prevent direct contact between adjacent surfaces and provide lubrication, thereby solving the technical problems of high heat generation and insufficient lubrication of the current lubrication structure when applied to high-speed differentials.

[0034] The surface of the carrier 100 where the oil groove 200 is formed is adjacent to the bonding surface of the cover sheet 300 .

[0035] Furthermore, the carrier 100 is a half-shaft gear, and the oil groove 200 is opened on the friction pair end surface 110 of the half-shaft gear.

[0036] In this embodiment, the carrier 100 is selected as a side gear, that is, the flow oil passage 210 and the closed oil passage 220 are directly opened on the end surface 110 of the side gear friction pair.

[0037] In the prior art, an oil groove 200 is usually opened on the gasket to provide a path for the flow of lubricating oil. However, the hardness of the gasket is usually greater than that of the half-shaft gear, and the thickness of the gasket is smaller than the end face 110 of the friction pair. Therefore, the process complexity of opening the oil groove 200 on the gasket is relatively high. Opening the oil groove 200 directly on one side of the end face 110 can reduce the processing difficulty, improve mass production efficiency and reduce costs.

[0038] In addition, there is usually relative rotation between the gasket and the differential, which not only causes wear on the differential, but also generates a certain amount of heat due to rotational friction.

[0039] In order to form an oil film with the end surface 110, a cover plate 300 is installed on the side of the end surface 110 where the oil groove 200 is opened, and the cover plate 300 is designed to rotate synchronously with the side gear, that is, there is no relative rotation between the two. The cover plate 300 does not rotate relative to the side gear, which can avoid wear and unnecessary heat caused by relative rotation friction.

[0040] Here, a structure is proposed in which the cover plate 300 rotates synchronously with the half-shaft gear. The limiting hole 310 of the cover plate 300 is a polygonal structure (such as a regular hexagon). The cover plate 300 with a polygonal structure will not rotate relative to the shaft after being installed on the shaft. It should be noted that the half-shaft gear and the cover plate 300 can also be designed as other structures that can rotate synchronously, such as a fixed connection between the two. As long as the synchronous rotation can be achieved, the implementation structure is not limited here.

[0041] Specifically, two circulating oil passages 210 are arranged, and one closed oil passage 220 is arranged.

[0042] The oil flow passage 210 is an arc-shaped structure and protrudes toward the axial direction of the end surface 110 , and the midpoint of the protrusion is also the midpoint of the entire arc-shaped structure. The closed oil passage 220 is composed of a surrounding oil passage 222 and two straight oil passages 221 .

[0043] Among them, the surrounding oil passage 222 is opened around the outer periphery of the mounting hole 111 of the end face 110, the two straight oil passages 221 extend along the direction of a certain diameter of the surrounding oil passage 222, and the two circulation oil passages 210 can be opened symmetrically with the straight oil passage 221 as the symmetry axis. This arrangement structure can provide the lubricating oil with the largest possible heat exchange area and improve the heat dissipation capacity. During the flow of the lubricating oil, since both ends of the circulation oil passage 210 pass through the edge of the end face 110, the lubricating oil outside the differential flows into the oil groove 200 of the friction pair through the circulation oil passage 210, and flows into the closed oil passage 220 through the circulation oil passage 210, and the lubricating oil in the closed oil passage 220 forms an oil film.

[0044] In addition to preventing direct contact between adjacent surfaces, reducing friction resistance, preventing sintering of friction surfaces, and extending their service life, the flow of lubricating oil in the oil film can also take away the heat generated by the friction pair and play a cooling role, which helps prevent component damage caused by overheating.

[0045] To achieve the above objectives, the utility model also proposes a differential, which includes the lubrication structure described above. Since the differential adopts all the technical solutions of the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, which will not be described one by one here.

[0046] The above are only optional embodiments of the present invention, and do not limit the patent scope of the present invention. All equivalent structural changes made by using the contents of the present invention specification and drawings under the inventive concept of the present invention, or directly / indirectly used in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A high-speed differential lubrication structure, characterized in that: The lubrication structure comprises: A carrier (100), wherein an oil groove (200) is provided on one side of the carrier (100), wherein the oil groove (200) comprises a circulating oil passage (210) and a closed oil passage (220), wherein the circulating oil passage (210) is in communication with the closed oil passage (220), wherein the circulating oil passage (210) passes through the edge of the carrier (100) and is in communication with the outside, and wherein the edge of the carrier (100) blocks the end of the closed oil passage (220); A cover plate (300), wherein the cover plate (300) covers the oil tank (200).

2. The high-speed differential lubrication structure according to claim 1, characterized in that: The carrier (100) is a half-axle gear, and the oil groove (200) is opened on the friction pair end surface (110) of the half-axle gear.

3. The high-speed differential lubrication structure according to claim 2, characterized in that: The oil flow channel (210) is an arc-shaped structure, the arc-shaped structure protrudes toward the axial direction of the end surface (110), and both ends of the arc-shaped structure penetrate the edge of the end surface (110) to communicate with the outside of the half-shaft gear.

4. The high-speed differential lubrication structure according to claim 3, characterized in that: The midpoint of the arc-shaped structure is connected to the closed oil passage (220).

5. The high-speed differential lubrication structure according to claim 3, characterized in that: At least two oil circulation passages (210) are provided.

6. The high-speed differential lubrication structure according to claim 5, characterized in that: Two oil circulation passages (210) are provided, and the two oil circulation passages (210) are symmetrically distributed.

7. The high-speed differential lubrication structure according to claim 2, characterized in that: A mounting hole (111) is provided at the axis of the end surface (110); the closed oil passage (220) comprises a linear oil passage (221) and a surrounding oil passage (222); the surrounding oil passage (222) is provided around the periphery of the mounting hole (111); one end of the linear oil passage (221) is connected to the surrounding oil passage (222); and the edge of the end surface (110) closes the other end of the linear oil passage (221).

8. The high-speed differential lubrication structure according to claim 7, characterized in that: The cover plate (300) rotates synchronously with the side gear.

9. The high-speed differential lubrication structure according to claim 8, characterized in that: The cover plate (300) is provided with a regular hexagonal limiting hole (310).

10. A differential, characterized in that: The differential comprises the lubrication structure according to any one of claims 1-9.

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