Friction plate pair with oleophobic grooves and wet clutch

Abstract

The invention discloses a friction plate pair with an oleophobic groove and a wet clutch, the friction plate pair comprises a friction plate and a dual steel sheet, and the friction plate and the dual steel sheet are mounted in a matched manner; a plurality of radial grooves and circumferential grooves which are communicated in a staggered mode are formed in the two side faces of the friction plate or the dual steel plate, the radial grooves divide the circumferential grooves into a plurality of fan-shaped sections, the groove depth of the circumferential grooves and the radian value of the positions where the circumferential grooves are located change periodically, a linear relation is formed in each fan-shaped section, and the radial grooves and the circumferential grooves are communicated in a staggered mode. The groove depth and the radius of the radial groove are linearly related, and the groove depth of the radial groove is larger than that of the circumferential groove. According to the invention, the groove depth is gradually increased, so that the speed gradient can be reduced, the oil shearing force is reduced, the oil film shearing heat is further reduced, the belt discharge torque is inhibited, and higher reliability and longer service life are provided for long-term use of the wet clutch.

Description

Technical Field

[0001] The invention belongs to the technical field of friction plates, in particular to a friction plate pair with oil-repellent grooves and a wet clutch. Background Art

[0002] Wet clutches have been widely used in the fields of ships, engineering machinery, heavy trucks, etc. due to their advantages such as smooth transmission, small size, large torque transmission, and long service life. The main failure form of wet clutches is overheating between friction pairs. One of the main reasons for overheating is that the friction plate and the dual steel plate generate a large amount of heat due to mutual sliding, and another reason is the shear heat generated by the oil film during idling. In addition to the above-mentioned overheating failure problem, the existence of the displacement torque is also a problem that cannot be ignored. As long as there is cooling lubricating oil, the displacement torque will exist, which is an inevitable inherent defect. The existence of the displacement torque will reduce the transmission efficiency, wear the friction elements and increase the oil temperature. Excessive temperature will cause ablation of the friction plate, and the surface of the friction lining may be glued and adhered, which will affect the normal flow of the cooling oil, forming a vicious circle, and directly affecting the normal use of the wet clutch.

[0003] Research on these issues shows that the oil groove design on the friction plate pair surface has an important influence on the performance of the friction pair. The oil groove not only plays the role of scraping oil, cooling and chip removal, but also significantly affects the friction characteristics of the clutch. A reasonable groove structure can improve the friction performance of the wet clutch friction pair, enhance the cooling effect, and reduce the influence of the pull-out torque.

[0004] At present, in the surface design of the friction plate pair of the wet clutch, in order to optimize the oil flow, improve the heat dissipation efficiency and adjust the friction characteristics, different forms of oil grooves are opened on the surface. These oil groove designs not only affect the thermal management performance of the clutch, but also directly affect its stability and durability during operation. The mainstream oil groove forms include radial grooves, spiral grooves, waffle grooves, etc. However, traditional oil groove structures have certain disadvantages: the radial groove oil channel is short, and the flow path of the oil on the friction pair surface is limited, resulting in limited heat dissipation capacity and low friction coefficient; the spiral groove flow channel is too long, causing the oil to stay on the friction surface for too long, and the oil cannot quickly take away the heat, affecting the cooling effect; the waffle groove has a small friction coefficient and is not applicable to application scenarios that require higher friction, resulting in its relatively limited scope of application. Summary of the invention

[0005] The purpose of the present invention is to provide a friction plate pair and a wet clutch with oil-repellent grooves to solve the problems of limited heat dissipation capacity and large belt torque in the prior art.

[0006] In order to achieve the above object, the present invention adopts the following technical solutions:

[0007] A friction plate pair with an oil-repellent groove comprises a friction plate and a dual steel plate, wherein the friction plate and the dual steel plate are installed in coordination;

[0008] A plurality of radial grooves and circumferential grooves which are interconnected are provided on both side surfaces of the friction plate or the dual steel plate. The radial grooves divide the circumferential grooves into a plurality of sector segments. The groove depth of the circumferential grooves varies periodically with the arc value of the position, and is linearly related within each sector segment. The groove depth of the radial grooves is linearly related to the radius, and the groove depth of the radial grooves is greater than the groove depth of the circumferential grooves.

[0009] Furthermore, a friction plate core plate is arranged on the friction plate, friction lining plates are arranged on both side surfaces of the friction plate core plate, and the radial grooves and circumferential grooves are both opened on the friction lining plates.

[0010] Furthermore, an annular base is provided on the dual steel sheets, friction surfaces are provided on both side surfaces of the annular base, and the radial grooves and circumferential grooves are both opened on the friction surfaces.

[0011] Furthermore, the center line of the radial groove points to the center of the friction plate core plate on the friction plate or the center of the annular base on the dual steel plate.

[0012] Furthermore, the circumferential grooves are arranged in concentric rings at equal intervals, and the center of the circumferential groove is the center of the friction plate core plate or the center of the annular base.

[0013] Furthermore, an oleophobic coating is provided on the inner surfaces of the radial groove and the circumferential groove.

[0014] Furthermore, the method for setting the oleophobic coating includes acid-base etching, electrospinning technology, polymer deposition and electrochemical method.

[0015] Furthermore, the groove depth at the oil inlet of each sector segment is smaller than the groove depth at the oil outlet, and there is a position difference between the oil outlet of each sector segment and the oil inlet of the next sector segment.

[0016] Furthermore, the cross-sections of the radial groove and the circumferential groove are both rectangular.

[0017] A wet clutch comprises the friction plate pair with oil-repellent grooves.

[0018] Compared with the prior art, the present invention has the following beneficial effects:

[0019] The present invention provides a friction plate pair with oil-repellent grooves. By opening a plurality of groups of radial grooves and circumferential grooves that are interconnected and staggered on the friction plate or the dual steel plate, a relatively large friction coefficient is maintained while having a low belt-displacement torque and a good heat dissipation effect. The groove depth of the circumferential groove varies periodically with the arc value of the position, the groove depth of the radial groove is linearly related to the radius, and the groove depth of the radial groove is greater than the groove depth of the circumferential groove. According to Newton's law of internal friction, the present invention gradually increases the groove depth to reduce the velocity gradient, which in principle reduces the shear force of the oil, thereby reducing the shear heat generated by the oil film and suppressing the belt-displacement torque. According to the principle of fluid continuity, the oil inlet area of ​​each oil groove is smaller than the corresponding outlet area. This "expansion" flow process will lead to a decrease in the oil flow rate, an increase in static pressure, improved flow stability, and a reduction in flow resistance, that is, a reduction in the belt-displacement torque. The friction plate pair with an oil-repellent groove structure proposed in the present invention is particularly suitable for a wet clutch system. It can optimize the flow characteristics of the oil, enhance the heat dissipation efficiency, and reduce the heat and belt torque generated by friction, thereby effectively reducing the heat generation and belt dissipation during operation, and providing higher reliability and longer service life for the long-term use of the wet clutch.

[0020] Furthermore, the oil-repellent treatment of the oil groove reduces the adhesion effect between the oil groove wall and the oil in the oil groove, reduces the oil flow resistance, and reduces the belt displacement torque.

[0021] Furthermore, there is a position difference between the oil outlet of each sector of the circumferential groove and the oil inlet of the next sector, which directly affects the stability of the flow. The higher temperature oil flowing out of the previous sector is fully mixed with the lower temperature oil flowing in the radial groove, so that the oil temperature is lower than that when it flows out of the previous sector, which is conducive to the next sector to take away more heat and increase the overall cooling effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for use in the embodiments are briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without creative work.

[0023] Figure 1 It is a schematic diagram of the structure of the friction plate with oil-repellent grooves of the present invention.

[0024] Figure 2 It is a schematic diagram of the structure of the dual steel sheets with oil-repellent grooves of the present invention.

[0025] Figure 3 For the present invention Figure 1 A partial enlarged view of part A.

[0026] Figure 4 It is a schematic diagram of the cutaway position of the friction plate of the present invention.

[0027] Figure 5 For the present invention Figure 4 (a) is the partial cross-sectional diagram of the AA position, and (b) is the partial cross-sectional diagram of the BB position.

[0028] Figure 6 It is a schematic diagram of the oil-repellent surface position of the oil tank according to the present invention.

[0029] Figure 7 Schematic diagram of the flow velocity distribution of the oil in the inclined oil tank and the conventional oil tank of the present invention, Figure 7 (a) is a schematic diagram of the flow velocity distribution of the oil in the inclined oil tank. Figure 7 (b) is a schematic diagram of the flow velocity distribution of oil in a conventional oil tank.

[0030] Figure 8 Schematic diagram of oil flow rate on the non-oleophobic surface and the oleophobic surface of the present invention, Figure 8 (a) is a schematic diagram of the oil flow rate when the oleophobic surface is set on a stationary wall. Figure 8 (b) Schematic diagram of the oil flow rate when the oleophobic surface is set on the moving wall.

[0031] Fig. 9 It is a schematic diagram of a partial cross-section of the friction plate of the present invention, (a) is a schematic diagram of the EE position, and (b) is a schematic diagram of a partial cross-section of the EE position.

[0032] Among them: 1-friction plate core, 2-friction lining, 3-radial groove, 4-circumferential groove, 5-dual steel plate. DETAILED DESCRIPTION

[0033] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings here can be arranged and designed in various different configurations.

[0034] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention claimed for protection, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0035] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, further definition and explanation thereof is not required in subsequent drawings.

[0036] In the description of the embodiments of the present invention, it should be noted that if the terms "upper", "lower", "horizontal", "inner", etc. indicate an orientation or positional relationship based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product of the invention is usually placed when in use, it is only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, the terms "first", "second", etc. are only used to distinguish the description, and cannot be understood as indicating or implying relative importance.

[0037] In addition, if the term "horizontal" appears, it does not mean that the component must be absolutely horizontal, but can be slightly tilted. For example, "horizontal" only means that its direction is more horizontal than "vertical", which does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0038] In the description of the embodiments of the present invention, it is also necessary to explain that, unless otherwise clearly specified and limited, the terms "set", "install", "connect", and "connect" 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 mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal connection of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0039] The present invention is further described in detail below in conjunction with the accompanying drawings:

[0040] See also Figure 1 The present invention provides a friction plate pair with an oil-repellent groove, including a friction plate and a dual steel plate 5, wherein the friction plate and the dual steel plate are both arranged in a circular ring shape, and the friction plate and the dual steel plate 5 are installed in coordination to adapt to the rotational working characteristics of the wet clutch.

[0041] The friction plate includes a friction plate core plate 1 and a friction lining 2. The friction plate core plate 1 is used as a core support structure to withstand various mechanical loads when the wet clutch is working. Both sides of the friction plate core plate 1 are provided with friction surfaces, and a layer of friction lining 2 is connected to the friction surface to increase the friction contact area and durability. Figure 2As shown, an annular base is provided on the dual steel plate 5, and friction surfaces are provided on both sides of the annular base to form a close fit with the friction plate. When the clutch is working, the friction lining 2 and the friction surface of the dual steel plate 5 are in close contact and rotate relative to each other, generating sufficient friction to transmit torque.

[0042] A plurality of interlaced radial grooves 3 and circumferential grooves 4 are provided on the friction surface of the friction lining 2 or the dual steel plate 5. The radial grooves 3 and the circumferential grooves 4 are connected to form an efficient oil flow network. Figure 3 As shown. The oil circulation network can change the flow state of the oil, and the circumferential groove 4 ensures the uniform distribution and rapid flow of the oil in the circumferential direction. The center line of the radial groove 3 points to the center of the friction plate core plate 1 or the center of the annular matrix, ensuring that the oil can be effectively dispersed along the radial direction, which not only helps to accelerate the flow of the oil, but also improves the heat dissipation efficiency. The circumferential grooves 4 are arranged in concentric rings with equal spacing, and the center of the circumferential groove 4 coincides with the center of the friction plate core plate 1 or the center of the annular matrix, which promotes the uniform distribution of the oil in the circumferential direction. The radial grooves 3 and the circumferential grooves 4 cooperate with each other to ensure a relatively fast flow of the oil and absorb as much heat as possible generated by the sliding of the friction element.

[0043] like Fig. 9 As shown, the depth of the radial groove 3 is linearly related to the distance from the center of the friction plate core plate 1. The depth of the radial groove 3 increases with the increase of the radius. This gradual groove depth design makes the groove depth at the oil outflow greater than the groove depth at the oil inflow, which reduces the oil flow rate, increases the static pressure, improves the flow stability, and reduces the flow resistance. At the same time, Figure 4 and Figure 5 As shown, the radial groove 3 divides the circumferential groove 4 into a plurality of sectors. The groove depth of the circumferential groove 4 varies periodically with the arc value of the position, and is linearly related in each sector. The groove depth of each sector gradually increases along the flow direction of the oil in the circumferential groove 4, so that the cross-sectional area at the oil inlet is smaller than the cross-sectional area at the outlet, that is, the groove depth at the oil inlet of each sector of the circumferential groove 4 is smaller than the groove depth at the oil outlet. Figure 7 As shown. By increasing the depth of each sector segment along the oil flow direction, the thickness of the oil film in the circumferential groove 4 along the oil flow direction is increased and the flow velocity gradient is reduced, thereby reducing the viscous friction of the oil flow in the circumferential groove 4 and the friction plate torque. Reasonable setting of the basic size of the oil groove has a great influence on the flow of the oil and the strength of the friction pair. The gradient oil groove depth is conducive to reducing the velocity gradient of the oil, reducing the shear force of the oil film, and has a positive effect on reducing the torque of the friction plate. A larger oil groove cross-sectional area is conducive to the flow of oil and is more beneficial to heat dissipation. At the same time, a reasonable oil groove size can ensure that the strength of the friction part meets the use requirements.

[0044] The depth of the radial groove 3 is greater than that of the circumferential groove 4, which is conducive to the smooth discharge of the oil in the circumferential groove 4 with a larger flow resistance, avoiding the long-term stay of some oil in the circumferential groove 4, which is conducive to the oil taking away heat. This not only improves the flow efficiency of the oil, but also reduces the temperature of the clutch. At the same time, the reasonable setting of the oil groove size can also ensure that the strength of the friction part meets the use requirements, ensuring the reliability and durability of the clutch.

[0045] like Figure 6 As shown, the inner surfaces of the radial groove 3 and the circumferential groove 4 are both provided with an oleophobic coating, which is applied by a variety of processes such as acid-base etching, electrospinning, polymer deposition, and electrochemical methods. Figure 8 As shown in the figure, compared with the non-oleophobic surface, the presence of the oleophobic coating reduces the flow friction resistance, making the oil flow smoother; it reduces the interaction between the radial groove 3 and the circumferential groove 4 on the internal oil, reduces the friction between the oil and the groove surface, and the oil flow velocity gradient, and finally reduces the belt torque. In addition, the oleophobic structure changes the oil flow velocity in the oil groove, which helps the oil to be more evenly distributed in the groove, promotes the smooth flow of the oil in the groove, and helps the oil to fully absorb the heat generated by the friction element, thereby improving the heat dissipation effect.

[0046] In addition, there is a position difference in the depth of the oil groove between the oil outlet of each sector segment of the circumferential groove 4 and the inlet of the next sector segment, which causes disturbances in the flow of the oil, and the oil flow here is no longer stable. The higher temperature oil flowing out of the previous sector segment of the circumferential groove 4 is fully mixed with the lower temperature oil in the radial groove 3. The intersection of high temperature oil and low temperature oil helps the heat exchange between the oils, so that the temperature of the oil entering the next sector segment is lower than the oil flowing out of the previous sector segment, and the ability of the oil to absorb heat is improved. This design of balanced temperature distribution helps to improve the stability of the oil and the service life of the clutch.

[0047] The cross-sections of the radial groove 3 and the circumferential groove 4 are both rectangular. The rectangular oil groove cross-section allows the lubricating oil to flow into and out of the radial groove 3 and the circumferential groove 4 more smoothly. The smooth flow helps to improve the heat dissipation and cooling effect. The rectangular oil groove cross-section also makes the oil more evenly distributed in the groove, which is conducive to the transfer and dissipation of heat. This smooth flow state reduces the energy loss and friction loss of the oil during the flow process, improves the efficiency of the system, and helps to extend the service life of the friction element and the stability of the system.

[0048] The present invention also proposes a wet clutch, comprising the above-mentioned friction plate pair with the oil-repellent groove structure. When the wet clutch is in use, it can not only increase the heat dissipation effect, but also reduce the belt displacement torque when the clutch is working, thereby effectively improving the reliability and life of the wet clutch.

[0049] The friction plate pair with oil-repellent grooves of the present invention is particularly suitable for wet clutches that require high torque transmission and stable friction performance. For example, in the fields of heavy vehicles, engineering machinery or ships, the performance of the clutch is directly related to the reliability and efficiency of the entire transmission system. The use of the friction plate pair of the present invention can not only improve the durability and friction efficiency of the clutch, but also reduce maintenance costs and failure rates.

[0050] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A friction plate pair with oil-repellent grooves, characterized in that: It comprises a friction plate and a dual steel plate (5), wherein the friction plate and the dual steel plate (5) are installed in coordination; A plurality of radial grooves (3) and circumferential grooves (4) which are interconnected are provided on both side surfaces of the friction plate or the dual steel plate (5); the radial grooves (3) divide the circumferential grooves (4) into a plurality of sector segments; the groove depth of the circumferential grooves (4) varies periodically with the arc value of the position, and is linearly related within each sector segment; the groove depth of the radial grooves (3) is linearly related to the radius, and the groove depth of the radial grooves (3) is greater than the groove depth of the circumferential grooves (4).

2. The friction plate pair with oil-repellent grooves according to claim 1, characterized in that: A friction plate core plate (1) is arranged on the friction plate, friction linings (2) are arranged on both side surfaces of the friction plate core plate (1), and the radial grooves (3) and circumferential grooves (4) are both opened on the friction linings (2).

3. The friction plate pair with oil-repellent grooves according to claim 1, characterized in that: An annular base is provided on the dual steel sheets (5), friction surfaces are provided on both side surfaces of the annular base, and the radial grooves (3) and circumferential grooves (4) are both provided on the friction surfaces.

4. The friction plate pair with oil-repellent grooves according to claim 1, characterized in that: The center line of the radial groove (3) points to the center of the friction plate core plate (1) on the friction plate or the center of the annular base on the dual steel plate (5).

5. The friction plate pair with oil-repellent grooves according to claim 4, characterized in that: The circumferential grooves (4) are arranged in concentric rings at equal intervals, and the center of the circumferential grooves (4) is the center of the friction plate core plate (1) or the center of the annular base.

6. The friction plate pair with oil-repellent grooves according to claim 1, characterized in that: An oleophobic coating is provided on the inner surfaces of the radial groove (3) and the circumferential groove (4).

7. The friction plate pair with oil-repellent grooves according to claim 6, characterized in that: The methods for setting the oleophobic coating include acid-base etching, electrospinning technology, polymer deposition and electrochemical methods.

8. The friction plate pair with oil-repellent grooves according to claim 1, characterized in that: The groove depth at the oil inlet of each sector segment is smaller than the groove depth at the oil outlet, and there is a position difference between the oil outlet of each sector segment and the oil inlet of the next sector segment.

9. The friction plate pair with oil-repellent grooves according to claim 1, characterized in that: The cross sections of the radial groove (3) and the circumferential groove (4) are both rectangular.

10. A wet clutch, characterized in that: It comprises the friction plate pair with oil-repellent grooves as described in any one of claims 1 to 9.

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