Self-adapting pre-tightening force compensation mechanism for tapered roller bearing

Abstract

The application belongs to the technical field of mechanical design, and particularly relates to a self-adaptive pre-tightening force compensation mechanism for a tapered roller bearing. The compensation mechanism reduces the bearing friction torque by adjusting the influence of temperature rise on the matching of the tapered roller bearing, so as to improve the service life of the tapered roller bearing and the running accuracy of the rotating shaft of the transmission device. The compensation mechanism comprises a first structural member, a second structural member and a spring. The application proposes a self-adaptive pre-tightening force compensation mechanism for a tapered roller bearing according to the characteristics of large load and quick change of the tapered roller bearing in the front transmission component of a hydraulic mechanical integrated transmission device. The influence of the rotating speed is utilized by using the elastic strip and the convex end thereof, the influence of temperature on the expansion change amount of the tapered roller bearing is considered by using the wedge surface matching, and finally the stability of the running state of the tapered roller bearing and the improvement of the service life are realized.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of mechanical design, and particularly relates to a self-adaptive pre-tightening force compensation mechanism of a tapered roller bearing. BACKGROUND

[0002] The front transmission component in a hydro-mechanical integrated transmission device is a key component connecting an engine and a hydrodynamic torque converter, wherein a bevel gear is supported by a cantilever, so that a tapered roller bearing is selected to transmit power flow. In different working states of a vehicle such as idling, acceleration or high-speed driving, the front transmission component is always in a motion state, has large and rapidly changing load, and generates much heat, so that the installation precision of the tapered roller bearing changes. Because the expansion coefficients of the tapered roller and the inner and outer rings are different, the friction torque increases, the service life of the tapered roller bearing is reduced, the reliability of the transmission device is reduced, and the smooth completion of a task cannot be ensured.

[0003] The existing technical solutions for pre-tightening force adjustment of a rolling bearing include positioning pre-tightening, constant pressure pre-tightening, centrifugal force pre-tightening and the like. The positioning pre-tightening and the constant pressure pre-tightening have simple structures, but cannot adaptively adjust the pre-tightening force following the working condition change, so the pre-tightening effect is not outstanding. The centrifugal force pre-tightening and the expansion sleeve type pre-tightening respectively use speed and temperature to adaptively adjust the pre-tightening force, and both have achieved beneficial effects. Although high speed often brings high temperature, high speed and high temperature do not always coexist. To adapt to complex working conditions, the rolling bearing pre-tightening force adjustment structure considering both is particularly important. SUMMARY

[0004] (I) Technical problem to be solved

[0005] The technical problem to be solved by the application is how to provide a self-adaptive pre-tightening force compensation mechanism of a tapered roller bearing.

[0006] (II) Technical scheme

[0007] In order to solve the above technical problem, the application provides a self-adaptive pre-tightening force compensation mechanism of a tapered roller bearing. The compensation mechanism reduces the bearing friction torque by adjusting the influence of temperature rise on the tapered roller bearing fit, so as to improve the service life of the tapered roller bearing and the running precision of the rotating shaft of the transmission device.

[0008] The compensation mechanism comprises a first structural member (1), a second structural member (2) and a spring (3).

[0009] The main body of the first structural component (1) is a hollow cylindrical body. The right end of the first supporting ring disk extends radially outward. The inner ring of the first supporting ring disk extends axially to the left to form a first cylindrical body. The cross-sectional dimensions of the inner wall of the first cylindrical body are set to gradually increase from right to left, so that the inside of the first cylindrical body forms a first wedge-shaped surface. The wall of the first cylindrical body is formed by cutting off part of the material along the axial direction to form multiple ring-shaped elastic strips (6) with a certain deflection. The right end of each elastic strip (6) is integrally formed with the first supporting ring disk. The left end has a protrusion (4) formed radially outward, which is used to generate centrifugal force when rotating at high speed, so that the diameter of the wedge-shaped surface formed by the elastic strip (6) increases.

[0010] The main body of the second structural component (2) is also a hollow cylindrical body. The left end of the component is provided with a second supporting ring disk that extends radially outward. The inner ring of the second supporting ring disk extends axially to the right to form a second cylindrical body. The cross-sectional dimensions of the right outer wall of the second cylindrical body are formed to gradually decrease from left to right, thereby forming a second wedge-shaped surface on the outside of the second cylindrical body.

[0011] The spring (3) is a ring-shaped component, which is disposed between the first supporting ring disc and the second supporting ring disc. It is in a compressed state and is used to provide axial reaction force between the first structural component (1) and the second structural component (2).

[0012] The first structural component (1) and the second structural component (2) form an interference fit through the first wedge surface and the second wedge surface. The first structural component (1) forms a clearance fit with the support spindle of the roller bearing, pressing the second structural component (2) against the support spindle, thereby forming a power transmission between the support spindle and the compensation mechanism, ensuring the rotation of the compensation mechanism.

[0013] The interference fit between the first structural component (1) and the second structural component (2) is set to be greater than the reaction force of the spring (3) to ensure that the inner rings of the two tapered roller bearings are rigidly connected.

[0014] In this process, the initial preload is set by locking the inner ring of the tapered roller bearing. During the starting stage of the hydraulic mechanical integrated transmission device, the speed is low and the load is light, the temperature is almost constant, and the two bearings are rigidly connected, so the preload remains unchanged at this time.

[0015] When the speed of the hydraulic mechanical integrated transmission device increases and the load is light, the protrusion (4) of the first structural component (1) generates centrifugal force with the speed, and the interference fit force decreases. At this time, the spring (3) pushes the first structural component (1) to move to the right and pushes the second structural component (2) to move to the left. The first structural component (1) and the second structural component (2) transmit the spring force to the inner ring of the tapered roller bearings on the left and right sides, which reduces the force between the inner ring and the roller of the two tapered roller bearings, and thus reduces the heat generation at high speed and low load.

[0016] When the speed of the hydraulic-mechanical integrated transmission device decreases, the first structural component (1) and the second structural component (2) re-form an interference fit.

[0017] When the speed of the hydraulic mechanical integrated transmission device increases and it is under heavy load, the protrusion (4) of the first structural component (1) generates centrifugal force with the speed, and the spring force overcomes the interference fit force. The first structural component (1) and the second structural component (2) move to the right and left respectively, and the gap between the inner ring and the roller of the two tapered roller bearings increases.

[0018] Under high speed and heavy load, the heat generated by the tapered roller bearing increases, and the expansion deformation of the inner rings of the two tapered roller bearings due to the temperature rise also acts on the first structural component (1) and the second structural component (2) respectively.

[0019] When the force generated by the expansion deformation is greater than the spring force, the first structural component (1) moves to the left and the second structural component (2) moves to the right, thereby adaptively adjusting the preload of the tapered roller bearing; when the rotational speed and temperature decrease, the first structural component (1) and the second structural component (2) re-form an interference fit under the action of the spring force.

[0020] (III) Beneficial Effects

[0021] Compared with existing technologies, this invention, through its designed adaptive preload compensation mechanism for tapered roller bearings, can adaptively adjust the preload of the integrated transmission device during startup, high-speed no-load, and high-speed heavy-load, thereby reducing the frictional torque of the tapered roller bearing, reducing heat generation, and minimizing expansion changes. By compensating for expansion changes, the operating state of the tapered roller bearing is stabilized, and the transmission efficiency is improved.

[0022] This invention addresses the characteristics of tapered roller bearings in the front transmission components of hydraulic mechanical integrated transmission devices, which experience large and rapidly changing loads. It proposes an adaptive preload compensation mechanism for tapered roller bearings. By utilizing the influence of rotational speed through an elastic strip and a protrusion at one end, and by considering the influence of temperature on the expansion of the tapered roller bearing through a wedge-shaped surface fit, the invention ultimately achieves stable operation and extended service life of the tapered roller bearings. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the adaptive preload compensation mechanism for tapered roller bearings.

[0024] Figure 2a and Figure 2b This is a schematic diagram of the first structural component.

[0025] Figure 3a and Figure 3b This is a schematic diagram of the second structural component.

[0026] Figure 4 This is a schematic diagram illustrating the working principle of the adaptive preload compensation mechanism for tapered roller bearings.

[0027] Wherein, 5: the junction of the first wedge surface and the second wedge surface;

[0028] 7: The gap between the elastic strips. Detailed Implementation

[0029] To make the objectives, contents, and advantages of the present invention clearer, the specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples.

[0030] To address the aforementioned technical problems, this invention provides an adaptive preload compensation mechanism for tapered roller bearings, such as... Figure 1 As shown, the compensation mechanism reduces the bearing friction torque by adjusting the effect of temperature rise on the tapered roller bearing fit, thereby improving the service life of the tapered roller bearing and the running accuracy of the rotating shaft of the transmission device.

[0031] The compensation mechanism includes: a first structural component (1), a second structural component (2), and a spring (3);

[0032] like Figure 2a and Figure 2b As shown, the main body of the first structural component (1) is a hollow cylindrical body. The right end of the first supporting ring disk extends radially outward. The inner ring of the first supporting ring disk extends axially to the left to form a first cylindrical body. The cross-sectional dimensions of the inner wall of the first cylindrical body are set to gradually increase from right to left, so that the interior of the first cylindrical body forms a first wedge-shaped surface. The wall of the first cylindrical body is formed by cutting off part of the material along the axial direction to form multiple elastic strips (6) with a certain deflection arranged in a ring. The right end of each elastic strip (6) is integrally formed with the first supporting ring disk. The left end has a protrusion (4) formed radially outward, which is used to generate centrifugal force when rotating at high speed, so that the diameter of the wedge-shaped surface formed by the elastic strip (6) increases.

[0033] like Figure 3a and Figure 3bAs shown, the main body of the second structural member (2) is also a hollow cylindrical body. The left end of the second supporting ring disk extends outward in a radial direction. The inner ring of the second supporting ring disk extends to the right in an axial direction to form a second cylindrical body. The cross-sectional dimensions of the right outer wall of the second cylindrical body are formed to gradually decrease from left to right, so that the outside of the second cylindrical body is formed as a second wedge-shaped surface.

[0034] The spring (3) is a ring-shaped component, which is disposed between the first supporting ring disc and the second supporting ring disc. It is in a compressed state and is used to provide axial reaction force between the first structural component (1) and the second structural component (2).

[0035] The first structural component (1) and the second structural component (2) form an interference fit through the first wedge surface and the second wedge surface. The first structural component (1) forms a clearance fit with the support spindle of the roller bearing, pressing the second structural component (2) against the support spindle, thereby forming a power transmission between the support spindle and the compensation mechanism, ensuring the rotation of the compensation mechanism.

[0036] Among them, such as Figure 4 As shown, the interference fit force of the first structural component (1) and the second structural component (2) is set to be greater than the reaction force of the spring (3) to ensure that the inner rings of the two tapered roller bearings are rigidly connected.

[0037] In this process, the initial preload is set by locking the inner ring of the tapered roller bearing. During the starting stage of the hydraulic mechanical integrated transmission device, the speed is low and the load is light, the temperature is almost constant, and the two bearings are rigidly connected, so the preload remains unchanged at this time.

[0038] When the speed of the hydraulic mechanical integrated transmission device increases and the load is light, the protrusion (4) of the first structural component (1) generates centrifugal force with the speed, and the interference fit force decreases. At this time, the spring (3) pushes the first structural component (1) to move to the right and pushes the second structural component (2) to move to the left. The first structural component (1) and the second structural component (2) transmit the spring force to the inner ring of the tapered roller bearings on the left and right sides, which reduces the force between the inner ring and the roller of the two tapered roller bearings, and thus reduces the heat generation at high speed and low load.

[0039] When the speed of the hydraulic-mechanical integrated transmission device decreases, the first structural component (1) and the second structural component (2) re-form an interference fit.

[0040] When the speed of the hydraulic mechanical integrated transmission device increases and it is under heavy load, the protrusion (4) of the first structural component (1) generates centrifugal force with the speed, and the spring force overcomes the interference fit force. The first structural component (1) and the second structural component (2) move to the right and left respectively, and the gap between the inner ring and the roller of the two tapered roller bearings increases.

[0041] Under high speed and heavy load, the heat generated by the tapered roller bearing increases, and the expansion deformation of the inner rings of the two tapered roller bearings due to the temperature rise also acts on the first structural component (1) and the second structural component (2) respectively.

[0042] When the force generated by the expansion deformation is greater than the spring force, the first structural component (1) moves to the left and the second structural component (2) moves to the right, thereby adaptively adjusting the preload of the tapered roller bearing; when the rotational speed and temperature decrease, the first structural component (1) and the second structural component (2) re-form an interference fit under the action of the spring force.

[0043] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A conical roller bearing self-adapting preload compensation mechanism, characterized in that, The compensation mechanism reduces bearing friction torque by adjusting the influence of temperature rise on the matching of the tapered roller bearing, so as to prolong the service life of the tapered roller bearing and improve the running accuracy of the rotating shaft of the transmission device; The compensation mechanism comprises a first structural member (1), a second structural member (2) and a spring (3); The main body of the first structural member (1) is a hollow cylindrical body, and a first supporting circular disc body extends outward in the radial direction at the right end of the main body; the inner ring of the first supporting circular disc body extends leftward in the axial direction to form a first cylindrical body, and the inner wall of the first cylindrical body is gradually increased in size from right to left, so that a first wedge surface is formed inside the first cylindrical body; the wall surface of the first cylindrical body is cut in the axial direction to form a plurality of elastic strips (6) arranged in a ring shape and having a certain degree of flexibility; the right end of each elastic strip (6) is integrally formed with the first supporting circular disc body, and a protrusion (4) is formed on the left end of each elastic strip (6) and extends outward in the radial direction, so that the diameter of the wedge surface formed by the elastic strip (6) is increased due to the centrifugal force generated during high-speed rotation; The main body of the second structural member (2) is also a hollow cylindrical body, and a second supporting circular disc body extends outward in the radial direction at the left end of the main body; the inner ring of the second supporting circular disc body extends rightward in the axial direction to form a second cylindrical body, and the right outer wall of the second cylindrical body is gradually reduced in size from left to right, so that a second wedge surface is formed outside the second cylindrical body; The spring (3) is a ring body arranged between the first supporting circular disc body and the second supporting circular disc body and is in a compressed state, and is used to provide a reaction force in the axial direction between the first structural member (1) and the second structural member (2); The first structural member (1) and the second structural member (2) are in interference fit with each other through the first wedge surface and the second wedge surface, and the first structural member (1) is in clearance fit with the supporting main shaft of the roller bearing, so that the second structural member (2) is pressed against the supporting main shaft, thereby forming power transmission between the supporting main shaft and the compensation mechanism and ensuring rotation of the compensation mechanism; When the rotating speed of the hydro-mechanical comprehensive transmission device is increased and the load is light, the protrusion (4) of the first structural member (1) generates centrifugal force with the rotating speed, the interference fit force is reduced, the spring (3) pushes the first structural member (1) to move rightward and pushes the second structural member (2) to move leftward, the first structural member (1) and the second structural member (2) transmit the force of the spring to the inner rings of the two tapered roller bearings, so that the force of the inner rings and the rollers of the two tapered roller bearings is reduced, and the heat generated at high speed and low load is reduced.

2. The tapered roller bearing self-adapting preload compensation mechanism of claim 1, wherein, The interference fit force of the first structural member (1) and the second structural member (2) is greater than the reaction force of the spring (3), so that the two tapered roller bearings are rigidly connected to each other.

3. The tapered roller bearing self-adapting preload compensation mechanism of claim 1, wherein, The initial pre-tightening force is set by locking the inner rings of the tapered roller bearings, the hydro-mechanical comprehensive transmission device is started at low speed and light load, the temperature is almost unchanged, the two bearings are rigidly connected to each other, and therefore the pre-tightening force is unchanged.

4. The tapered roller bearing self-adapting preload compensation mechanism of claim 1, wherein, When the speed of the hydro-mechanical integrated transmission is reduced, the first structure (1) and the second structure (2) re-form the interference fit.

5. The tapered roller bearing self-adapting preload compensation mechanism of claim 1, wherein, When the speed of the hydro-mechanical integrated transmission is increased and under heavy load, the convex (4) of the first structure (1) generates centrifugal force with the speed, the spring force overcomes the interference fit force, the first structure (1) and the second structure (2) move right and left respectively, and the clearance between the inner ring and the roller of the two tapered roller bearings is increased.

6. The tapered roller bearing self-adapting preload compensation mechanism of claim 5, wherein, Under high speed and heavy load, the heat generated by the tapered roller bearings is increased, and the expansion deformation of the inner rings of the two tapered roller bearings due to the temperature rise also acts on the first structure (1) and the second structure (2) respectively; When the force generated by the expansion deformation is greater than the spring force, the first structure (1) moves left and the second structure (2) moves right, so as to adaptively adjust the pre-tightening force of the tapered roller bearings; when the speed and temperature are reduced, the first structure (1) and the second structure (2) re-form the interference fit under the action of the spring force.

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