Spring force system of clutch actuating mechanism

Abstract

The invention relates to a spring force system of a clutch actuating mechanism, and solves the technical problem that the fluctuation of a clutch displacement output curve in the prior art is too large, so that the loading performance has certain defects. According to the spring force system of the clutch actuating mechanism provided by the invention, the combination and separation processes of a clutch are analyzed, and parameters such as spring force proportions of a balance spring and a wave spring clamp, parameter design, displacement of a piston and the like are subjected to experimental comparison; the relation between values of a balance spring and a wave spring clamp and a clutch displacement output curve is defined, the range of a sliding safety coefficient K and the range of a self-aligning safety coefficient J are provided, and the problem that the clutch displacement output curve fluctuates excessively is solved.

Description

Technical Field

[0001] The invention relates to an AMT clutch, and in particular to a clutch actuator spring force system. Background Art

[0002] With the rapid development of intelligent products, the clutch actuator, as one of the core parts of intelligent products, has attracted much attention. The performance of the clutch actuator directly determines the smoothness of the AMT shifting gear. The clutch actuator is evaluated by performance indicators such as slip resistance, cylinder output force, clutch displacement output curve, among which the stability of the clutch displacement output curve is crucial. There are certain shortcomings in the installation performance of most existing clutch actuators, and the main reason is that the fluctuation of the clutch displacement output curve is too large. For example, Chinese patent CN112360876A discloses an AMT clutch release bearing unit for commercial vehicles, including a closed bearing assembly, a piston assembly with a leather ring installed, a cylinder assembly with an air inlet, a bearing connection wave spring clip and a position sensor assembly with a movable block. The spring force system contained in its disclosure belongs to the traditional structure.

[0003] The main reason affecting the clutch displacement output curve is that the design of the spring force system of the clutch actuator is not reasonable. Therefore, it is necessary to conduct a detailed analysis and design of the spring force system and clarify the optimal design of the parameters of each spring component. Summary of the invention

[0004] The purpose of the present invention is to solve the technical problem in the prior art that the clutch displacement output curve fluctuates too much, thereby causing certain deficiencies in vehicle loading performance, and to provide a clutch actuator spring force system.

[0005] In order to achieve the above purpose, the technical solution provided by the present invention is as follows:

[0006] A clutch actuator spring force system, comprising:

[0007] An outer shell, a piston, a release bearing and a flange sleeved on the transmission; the outer shell is coaxially arranged on the flange, and the outer shell is provided with an air hole for communicating with an external air source through the air hole; the piston is coaxially embedded in the outer shell; a balance spring is provided between the outer shell and the inner end of the piston, and the balance spring is normally in a compressed state; the release bearing is coaxially embedded in the piston; the inner ring of the release bearing is used for contacting and cooperating with the clutch release finger, and the outer ring is connected to the outer end of the piston through a wave spring clamp;

[0008] A displacement sensor is installed on the flange through a sensor bracket; a limit groove parallel to the axial direction is opened on the sensor bracket, and a magnetic steel component is arranged in the limit groove to match the limit groove with the clearance; the magnetic steel component is connected to the piston; the displacement sensor determines the position of the piston by detecting the axial position of the magnetic steel component in the limit groove, thereby outputting the displacement of the release bearing and obtaining the clutch displacement output curve;

[0009] Its special features are:

[0010] When the clutch is in the engaged state, the axial spring force applied by the balance spring to the piston is F1, and the critical spring force at which there is no relative sliding between the inner ring of the release bearing and the clutch release finger is F0. Then the parameters of the balance spring meet the condition: F1>F0;

[0011] When the clutch is in the disengaged state, the axial spring force applied by the wave spring clamp on the piston is F4, and the centering force exerted on the inner ring of the release bearing by the clutch release finger is T. Then the parameters of the wave spring clamp meet the condition: F4>T.

[0012] Further, F1 = K × F0, where K is the sliding safety factor, which satisfies the condition: 1.8 ≤ K ≤ 5;

[0013] F4=J×T, where J is the self-aligning safety factor, satisfying the condition: 2≤J≤4.

[0014] Furthermore, 2≤K≤3; 2.5≤J≤3.5.

[0015] Further, K=2.5; J=3.

[0016] Furthermore, a concave spring clamping boss is provided inside the outer shell, and a spring mounting ring cavity is correspondingly opened on the piston; two ends of the balance spring are respectively clamped on the outer side wall of the spring clamping boss and the inner side wall of the spring mounting ring cavity.

[0017] Furthermore, the wave spring clamp includes a wave ring and six limit claws evenly arranged on the wave ring; the wave crests of the wave ring constitute the top surface, the wave troughs constitute the bottom surface, the limit claws are arranged at a position corresponding to the top surface, and the bottom surface contacts the outer ring of the release bearing; F4 is the axial spring force applied by the limit claws to the piston.

[0018] Furthermore, the outer shell and the flange are fixedly connected by riveting; the flange, the sensor bracket and the displacement sensor are connected by bolts.

[0019] The beneficial effects of the present invention compared with the prior art are as follows:

[0020] A clutch actuator spring force system provided by the present invention analyzes the engagement and disengagement processes of the clutch, experimentally compares the spring force specific gravity, parameter design, and piston displacement of a balancing spring and a wave spring clamp, clarifies the relationship between the values ​​of the balancing spring and the wave spring clamp and the clutch displacement output curve, and proposes the ranges of the sliding safety factor K and the self-aligning safety factor J, thereby solving the problem of excessive fluctuation in the clutch displacement output curve. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a force analysis diagram of a clutch actuator spring force system embodiment of the present invention during the engagement process;

[0022] Figure 2 is a force analysis diagram of an embodiment of the present invention during a separation process;

[0023] Figure 3 Schematic diagram of the installation of the displacement sensor in the embodiment of the present invention, wherein A is a top view and B is a sectional view of the three-dimensional structure;

[0024] Figure 4 is a force analysis diagram of a wave spring clip in an embodiment of the present invention;

[0025] Figure 5 It is an experimental relationship diagram between the centering safety factor and the fluctuation amount in the embodiment of the present invention.

[0026] Figure Number:

[0027] 1-Balance spring; 2-Outer shell; 3-Piston; 4-Wave spring clamp, 41-Wave ring, 42-Limiting claw, 43-Top surface, 44-Bottom surface; 5-Release bearing; 6-Clutch release finger; 7-Magnetic steel assembly; 8-Flange; 9-Sensor bracket; 10-Displacement sensor. DETAILED DESCRIPTION

[0028] The specific technical solutions in the embodiments of the present invention will be further described below in conjunction with the accompanying drawings.

[0029] Figure 1-Figure 2A clutch actuator spring force system provided in an embodiment of the present invention comprises an outer shell 2, a piston 3, a release bearing 5 and a flange 8 sleeved on a transmission; the outer shell 2 is coaxially arranged on the flange 8, and the outer shell 2 is provided with an air hole for communicating with an external air source through the air hole; the piston 3 is coaxially embedded in the outer shell 2; a balance spring 1 is provided between the inner ends of the outer shell 2 and the piston 3, and the balance spring 1 is normally in a compressed state, which plays an axial guiding role. An inner concave spring clamping boss is provided inside the outer shell 2, and a spring mounting ring cavity is correspondingly provided on the piston 3; the two ends of the balance spring 1 are respectively clamped on the outer side wall of the spring clamping boss and the inner side wall of the spring mounting ring cavity. The release bearing 5 is coaxially embedded in the piston 3; the inner ring of the release bearing 5 is used for contacting and cooperating with the clutch release finger 6, and the outer ring is connected to the outer end of the piston 3 through a wave spring clamp 4.

[0030] refer to Figure 3 A displacement sensor 10 is installed on the flange 8 through a sensor bracket 9; a limiting groove parallel to the axial direction is opened on the sensor bracket 9, and a magnetic steel component 7 is provided in the limiting groove to match the limiting groove with a clearance; the magnetic steel component 7 is connected to the piston 3; the displacement sensor 10 determines the position of the piston 3 by detecting the axial position of the magnetic steel component 7 in the limiting groove, thereby outputting the displacement of the release bearing 5 and obtaining the clutch displacement output curve.

[0031] refer to Figure 4 The wave spring clamp 4 includes a wave ring 41 and a plurality of limit claws 42 evenly arranged on the wave ring 41 (the number of which depends on the actual size); the wave crest of the wave ring 41 constitutes the top surface 43, the wave trough constitutes the bottom surface 44, the limit claws 42 are arranged at a position corresponding to the top surface 43, and the bottom surface 44 contacts the outer ring of the release bearing 5; F4 is the axial spring force applied by the limit claw 42 to the piston 3. The outer shell 2 is fixedly connected to the flange 8 by riveting; the flange 8, the sensor bracket 9 and the displacement sensor 10 are connected by bolts.

[0032] The spring force system provided in this embodiment is analyzed during the clutch engagement and disengagement process:

[0033] 1. Binding state

[0034] Clutch engagement status Figure 1 As shown, the balance spring 1 compresses and pushes the piston 3 and the release bearing 5 to contact the clutch release finger 6, and the clutch release finger 6 drives the inner ring of the release bearing 5 to rotate together, so the clutch release finger 6 will transmit the vibration to the release bearing 5 and then affect the displacement fluctuation of the sensor.

[0035] If the spring force of the balance spring 1 is too small, relative sliding will occur between the clutch release finger 6 and the inner ring of the release bearing 5, resulting in large fluctuations in the clutch displacement output curve.

[0036] In the engaged state, the axial spring force applied by the balance spring 1 to the piston 3 is F1, the critical spring force between the inner ring of the release bearing 5 and the clutch release finger 6 without relative sliding is F0, and the parameters of the balance spring 1 meet the conditions: F1 = K × F0, where the sliding safety factor K has a value range of 2≤K≤3, which can be 2.5. As the clutch wears, the engagement position in the figure will continue to move to the right, and at this time the new spring force F1' is always greater than F1, so only the spring force F1 when the clutch is not worn needs to be considered.

[0037] 2. Separation state

[0038] Clutch disengagement status Figure 2 As shown, the gas flow input from the external gas source and the balance spring 1 together push the piston 3 to move and overcome the clutch separation force Q. When stopped at a certain separation position, the release bearing 5 is in a force balance state, at this time F3+F2=Q, where F3 is the cylinder pressure, and F2 is the spring force of the balance spring 1. Since F2 is smaller in magnitude than F3 and Q, it can be ignored.

[0039] At this time, the clutch release finger 6 will align the release bearing 4 through the inner ring during the rotation process. In the separated state, the axial spring force (that is, the positive pressure) applied by the wave spring clamp 4 to the piston 3 is F4, and the inner ring of the release bearing 5 is subjected to the aligning force from the clutch release finger 6 as T. The parameters of the wave spring clamp 4 meet the conditions: F4=J×T, where the aligning safety factor J is 3.

[0040] Under the premise of a certain self-aligning force T, the greater the self-aligning safety factor J, the greater F4.

[0041] The relationship curve between the centering safety factor J and the fluctuation rate obtained by the experiment is as follows: Figure 5 As shown in the figure, as the self-aligning safety factor J increases from 1 to 2.5, the fluctuation decreases exponentially.

[0042] When the self-aligning safety factor J is greater than 2.5, the fluctuation amount shows a slow downward trend and is close to being stable. However, as the self-aligning safety factor J increases, the larger F4 becomes, and disassembly and assembly become more and more difficult.

[0043] When the safety factor is greater than 3.5, on-site assembly is quite difficult and the assembly efficiency is greatly reduced.

[0044] Therefore, the self-aligning safety factor J is designed to be within the range of 2.5-3.5, which can reduce the clutch displacement fluctuation and improve product performance to meet the needs without affecting the assembly efficiency.

[0045] The above content is only an embodiment of the present invention and is not intended to limit the protection scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings, or directly or indirectly applied in other related technical fields, are included in the patent protection scope of the present invention.

Claims

1. A clutch actuator spring force system, comprising: An outer casing (2), a piston (3), a release bearing (5), and a flange (8) sleeved on the transmission; The outer shell (2) is coaxially arranged on the flange (8), and the outer shell (2) is provided with an air hole for communicating with an external air source through the air hole; The piston (3) is coaxially embedded in the outer shell (2); A balance spring (1) is provided between the outer shell (2) and the inner end of the piston (3), and the balance spring (1) is normally in a compressed state; The release bearing (5) is coaxially embedded in the piston (3); the inner ring of the release bearing (5) is used to contact and cooperate with the clutch release finger (6), and the outer ring is connected to the outer end of the piston (3) through a wave spring clamp (4); A displacement sensor (10) is mounted on the flange (8) via a sensor bracket (9); a limit groove parallel to the axial direction is provided on the sensor bracket (9), and a magnetic steel component (7) is provided in the limit groove to be clearance-matched with the limit groove; the magnetic steel component (7) is connected to the piston (3); the displacement sensor (10) determines the position of the piston (3) by detecting the axial position of the magnetic steel component (7) in the limit groove, thereby outputting the displacement of the release bearing (5) and obtaining a clutch displacement output curve; Features: When the clutch is in the engaged state, the axial spring force applied by the balance spring (1) to the piston (3) is F1, and the critical spring force at which there is no relative sliding between the inner ring of the release bearing (5) and the clutch release finger (6) is F0, then the parameters of the balance spring (1) meet the condition: F1>F0; When the clutch is in the disengaged state, the axial spring force applied by the wave spring clamp (4) to the piston (3) is F4, and the centering force exerted on the inner ring of the release bearing (5) by the clutch release finger (6) is T. Then, the parameters of the wave spring clamp (4) satisfy the condition: F4>T.

2. A clutch actuator spring force system according to claim 1, characterized in that: F1=K×F0, where K is the sliding safety factor, satisfying the condition: 1.8≤K≤5; F4=J×T, where J is the self-aligning safety factor, satisfying the condition: 2≤J≤4.

3. A clutch actuator spring force system according to claim 2, characterized in that: 2≤K≤3； 2.5≤J≤3.5。 4. A clutch actuator spring force system according to claim 3, characterized in that: K=2.5; J=3.

5. The clutch actuator spring force system according to claim 1, characterized in that: The outer shell (2) is provided with a concave spring clamping boss inside, and the piston (3) is correspondingly provided with a spring mounting ring cavity; the two ends of the balance spring (1) are respectively clamped on the outer side wall of the spring clamping boss and the inner side wall of the spring mounting ring cavity.

6. A clutch actuator spring force system according to claim 1, characterized in that: The wave spring clamp (4) comprises a wave ring (41) and six limiting claws (42) evenly arranged on the wave ring (41); the wave crests of the wave ring (41) form a top surface (43), the wave troughs form a bottom surface (44), the limiting claws (42) are arranged at positions corresponding to the top surface (43), and the bottom surface (44) contacts the outer ring of the release bearing (5); The F4 is the axial spring force applied by the limiting claw (42) to the piston (3).

7. A clutch actuator spring force system according to claim 1, characterized in that: The outer shell (2) and the flange (8) are fixedly connected by riveting; The flange (8), the sensor bracket (9) and the displacement sensor (10) are connected by bolts.

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