Assembly for actuation and system for interlocking two gearbox fork shafts

Abstract

The present invention relates to an assembly (E) for actuating two fork shafts of a gearbox, the assembly (E) comprising two rotating actuators (AR1, AR2) and a system (S1) comprising a first lever (L1) supporting a drive finger (D1) of a first fork and a cam (C1), the profile of which comprises a notch (CV1) for locking the first lever (L1); and a second lever (L2). Thus, the second lever (L2) supports the drive finger of the second fork and a cam (C2), the profile of which comprises a second notch (CV2) for locking the second lever (L2); and a pivoting body (B) supporting a locking pin (PV) which can interact with one or the other of the two locking notches (CV1, CV2) to angularly lock the associated lever (L1, L2) when the other lever (L2, L1) is actuated to engage the gear ratio.

Description

[Technical Field]

[0001] The present invention relates to an assembly for actuating at least two forks of a gearbox having a mechanical interlocking system.

[0002] The invention is particularly applicable to so-called automatic gearboxes, in which each fork shaft is connected to a shaft whose movement is caused by an electric actuator managed by a control unit. [Background technology]

[0003] To manage the gear changes, internal control assemblies are known, consisting of an actuator and a fork shaft or spindle, for example, for a ratio or gear called the electric ratio or gear for the transmission of the motor vehicle and the electric motor of the hybrid drive, and two shafts and two forks for a ratio called the combustion engine ratio for the combustion engine of this hybrid drive.

[0004] The principle of such a "hybrid" gearbox is to allow the combustion engine ratio and the electric gear ratio to be changed simultaneously, however, two ratios of one and the same category (electric or combustion engine) must not be changeable at the same time.

[0005] This involves a principle called ratio interlocking.

[0006] It therefore concerns two shafts and a fork for changing the combustion engine ratio.

[0007] In known manner, each fork shaft is associated with a first motor which drives the rotation of an eccentric finger which drives the fork shaft independently of the others.

[0008] The interlocking function is provided in the first place by managing each of the rotary actuators or motors. Summary of the Invention

[0009] The present invention proposes a design for a mechanical interlocking system that can be incorporated into an electrically actuated assembly to improve safety.

[0010] The present invention proposes a system for linking the movement of two shafts of a fork of a gearbox, the system comprising: a) a first lever, mounted so as to be pivotable about a first axis in two opposite directions to assume at least one operating angular position relative to a neutral intermediate angular position; supporting a first eccentric axial finger connected to the first drive shaft of the first fork; a first eccentric cam, the cam profile of the first eccentric cam having a first notch for locking the first lever in its neutral position; First lever and; b) a second lever, being mounted so as to be pivotable in two opposite directions about a second axis parallel to the first axis to assume at least one operating angular position relative to a neutral intermediate angular position; supporting a second eccentric axial finger connected to the second drive shaft of the second fork; a second eccentric cam, the cam profile of the second eccentric cam having a second notch for locking the second lever in its neutral position; with the second lever; c) A continuous moving object, the coupling swing body is mounted so as to be pivotable in two opposite directions about a swing axis parallel to the first axis so as to take one or the other of two opposite locking angular positions relative to an intermediate rest angular position to which the coupling swing body elastically returns; An eccentric axial locking pin is supported, the eccentric axial locking pin being positioned so as to simultaneously face the first locking notch and the second locking notch when the linking body is in its rest angle position and each drive lever is in its neutral angle position. Continuously moving bodies and Equipped with In the system, each cam profile of the lever has, on either side of its locking notch, an actuating portion which interacts with the locking pin to pivot the linkage and cause the locking pin to engage the locking notch of the cam of the other lever, and then hold the locking pin in this locking engagement position so as to angularly lock the other lever in its neutral position.

[0011] Other features of the interlocking system include: Each cam profile has at least one actuating portion having a convex arc shape centered on the axis of the associated lever adjacent the locking notch; Regardless of the angular position of each lever, the first shaft, the locking pin, and the second shaft are aligned, When the coupling swing body is in its rest angle position and each lever is in its neutral angle position, the first shaft, the first locking notch, the locking pin, the second locking notch and the second shaft are aligned; The locking pin is received between the first cam profile and the second cam profile regardless of the angular position of each lever; each lever for driving an associated drive shaft of a fork; the first lever is mounted so as to be pivotable about a first axis in two opposite directions to assume one or other of two opposite operating angular positions relative to its neutral intermediate angular position, and the second lever is mounted so as to be pivotable about a second axis in two opposite directions to assume one or other of two opposite operating angular positions relative to its neutral intermediate angular position; Each cam profile has two working portions, each having a convex arc shape centered on the axis of the associated lever, and a locking notch disposed between the two working portions.

[0012] The invention also proposes an assembly for actuating two shafts of a fork of a gearbox, said assembly comprising: a controlled first rotary actuator and a second rotary actuator, the output shafts of which are parallel; A system for linking the movement of the two shafts of a fork according to the invention; and The first rotary actuator drives the pivoting of the first drive lever, and the second rotary actuator drives the pivoting of the second drive lever.

[0013] The rotation axes of the output shafts of the two rotary actuators are perpendicular to the parallel sliding axes of the two fork shafts.

[0014] Further features and advantages of the present invention will become apparent from a reading of the following detailed description, for understanding which reference should be made to the accompanying drawings, in which: [Brief explanation of the drawings]

[0015] [Figure 1] FIG. 1 is a perspective front view illustrating an exemplary embodiment of an assembly for actuating three parallel shafts of a fork to change the ratio of a gearbox, two of which are equipped with a linkage system according to the present invention. [Figure 2] FIG. 2 is a view similar to that of FIG. 1, but omitting the fork shaft or associated fork. [Figure 3A] FIG. 3 is a perspective front view of the interlocking system of FIG. 2. [Figure 3B] FIG. 3 is a perspective rear view of the interlocking system of FIG. 2. [Figure 4A] 3A and 3B, showing each of the two locking levers in its neutral position and the linkage body in its rest position. FIG. [Figure 4B]FIG. 4B is a rear view of the interlocking system of FIG. 4A. [Figure 5A] A view similar to that of FIG. 4A, in which the first lever is in its operating position to change to the first ratio, and the second lever is locked in its neutral position with the coupling in a locked position. [Figure 5B] FIG. 2 is a rear view of the interlocking system 5A. [Figure 6A] A view similar to that of Figure 4A, in which the first lever is in another operating position to change to a second ratio, and the second lever is locked in its neutral position by the coupling in a locked position. [Figure 6B] FIG. 10 is a rear view of the interlocking system 6A. [Figure 7A] A view similar to that of FIG. 4A, in which the first lever is locked in its neutral position with the coupler in the other locked position, and the second lever is in its actuated position to change to the third ratio. [Figure 7B] FIG. 2 is a rear view of the interlocking system 7A. [Figure 8A] A view similar to that of FIG. 4A, in which the first lever is locked in its neutral position with the coupling in the other locked position and the second lever is in the other operating position to change to the fourth ratio. [Figure 8B] FIG. 10 is a rear view of the interlocking system 8A. DETAILED DESCRIPTION OF THE INVENTION

[0016] By convention, the geometric axes shown in the drawings run from rear to front.

[0017] In the following description, identical, similar or like elements are represented by the same reference numerals.

[0018] FIG. 1 illustrates an assembly E for actuating three parallel shafts AF1, AF2 and AF3 of three forks F1, F2 and F3 belonging to a gearbox of a motor vehicle.

[0019] In known practice, each fork shaft is fixed for translational movement about the axis of its associated fork.

[0020] In known manner, but without limitation, each shaft AF1, AF2 and AF3 drives the axial translational movement of an axial fork F1, F2 and F3, which in turn are connected for translational movement to ratio-changing auxiliary devices DA1, DA2 and DA3 of generally known design, such as the one shown in document FR-A1-2.988.800.

[0021] As a non-limiting example, the two first torques AF1-F1 and AF2-F2 are used to change a gear ratio, called the "combustion engine" gear ratio, in order to vary the rotational speed of a combustion engine, and the third torque AF3-F3 is used to change a gear ratio, called the "electric" gear ratio, in order to vary the rotational speed of, for example, an electric motor that is part of a powertrain, called a hybrid, associated with the combustion engine.

[0022] In this case, each transmission shaft can be driven axially in two directions relative to an intermediate axial position called neutral, in which no ratio is engaged.

[0023] The first torque AF1-F1 may, for example, result in a change of the first and second ratios, and the second torque AF2-F2 may result in a change of the third and fourth ratios.

[0024] To drive the first shaft AF1 and its associated fork F1, the actuation assembly E has a first controlled rotary actuator AR1 that can drive the pivoting of the first lever L1 in two opposite directions about the geometric pivot axis A1.

[0025] To drive the second shaft AF2 and its associated fork F2, the actuation assembly E has a second controlled rotary actuator AR2 capable of driving the pivoting of a second lever L2 in two opposite directions about the geometric pivot axis A2.

[0026] The two rotary actuators AR1 and AR2 have parallel axes, each of which is, for example, the output shaft of an electric motor (not shown) incorporated in the actuation assembly E.

[0027] According to the teachings of the present invention, the movements of the two shafts AF1 and AF2 are linked to a linkage system SI, which basically comprises: a first lever L1, in this case a lever for driving a first shaft AF1 in two directions; a second lever L2, in this case a lever for driving the second lever L2 in two directions; Continuously moving object B and It consists of:

[0028] As can be seen in detail in Figures 3A and 3B, the first lever L1 carries a first axial drive finger D1, which is eccentric with respect to the axis A1, extends axially forward and is connected via an auxiliary device DA1 to the first shaft AF1 of the first fork F1.

[0029] Here, diametrically opposite the first drive finger D1, the first lever L1 bears a first cam C1 that is eccentric with respect to the axis A1.

[0030] The convex cylindrical edge of the first cam C1 is a cam contour PC1 having successively a first actuating portion TA11 having a cylindrical arcuate shape, a first notch CV1 for angularly locking the first lever L1, and an opposite second actuating portion TA12 also having a cylindrical arcuate shape.

[0031] The first lever L1 also has a first central drive rod TE1 which extends axially rearward and is driven by a first rotary actuator AR1.

[0032] Similarly, the second lever L2 carries a second axial drive finger D2, which is eccentric to the axis A2, extends axially forward and is connected to the first shaft AF2 of the first fork F2 via an auxiliary device DA2.

[0033] Here, angularly offset relative to the second drive finger D2, the second lever L2 bears a second cam C2 that is eccentric relative to the axis A2.

[0034] The convex cylindrical edge of the second cam C2 is a cam contour PC2 having successively a first actuating portion TA21 having a cylindrical arcuate shape, a second notch CV2 for angularly locking the second lever L2, and an opposite second actuating portion TA22 also having a cylindrical arcuate shape.

[0035] The second lever L2 also has a second central drive rod TE2 which extends axially rearward and is driven by a second rotary actuator AR2.

[0036] The first lever L1 can assume three distinct functional angular positions, including one neutral position PM1 in which no ratio is engaged, and two opposite operating angular positions, namely an operating angular position PA11 in which the first ratio is engaged by the first fork F1 and an operating angular position PA12 in which the second ratio is engaged.

[0037] The second lever L2 can assume three distinct functional angular positions, including one neutral position PM2 in which no ratio is engaged, and two opposite operating angular positions, namely operating angular position PA21 in which the third ratio is engaged by the second fork F2 and operating angular position PA22 in which the fourth ratio is engaged.

[0038] The relative positioning of the two levers L1 and L2 and their dimensions are such that a certain minimum gap EF exists between the two opposite convex cylindrical cam profiles PC1 and PC2.

[0039] As can be seen from Figures 3A, 3B, 4A and 4B, when each lever L1, L2 is in its neutral angular position PM1, PM2, the first axis A1, the first locking notch CV1, the second locking notch CV2 and the second axis A2 are aligned.

[0040] Near its proximal end, the swinging body B is mounted so as to be pivotable relative to the housing of the drive assembly E about a swing axis AB parallel to the pivot axes A1 and A2 of the two levers L1 and L2.

[0041] In this case, the swinging body B is a plate that can be pivoted in two opposite directions about the swing axis AB to assume one or the other of two opposite locking angular positions PV1 and PV2 relative to its intermediate rest angular position PR, which are illustrated in Figures 3A to 4B.

[0042] The swinging body B is always elastically returned to its rest angle position PR by a return system arranged on its rear surface.

[0043] By way of non-limiting example, the return system in this case comprises a return spring R having a so-called hairpin shape, which interacts with a fixed stop BF bearing against the housing of the drive assembly E.

[0044] Near its other distal end, the rocker B carries an eccentric cylindrical locking pin PV, which extends axially forward between and interacts with the two cam profiles PC1 and PC2.

[0045] The outer diameter of the locking pin PV is greater than the value of the gap EF.

[0046] The positions and dimensions of the two levers L1 and L2 and the connecting swing body B are as follows: Regardless of the angular position of each lever L1, L2 and the connecting member B, the locking pin PV is always located between the two cam contours PC1 and PC2. When the coupled swinging body B is in its rest angle position PR and each drive lever L1, L2 is in its neutral angle position PM1, PM2, the first axis A1, the first locking notch CV1, the locking pin PV, the second locking notch CV2 and the second axis A2 are aligned, and the locking pin PV is positioned to face the first locking notch CV1 and the second locking notch CV2 simultaneously (see Figures 3A and 4A).

[0047] To ensure elastic return towards its rest angular position, the locking pin PV also extends axially rearward between the free end portions of the two arms of the hairpin-shaped return spring R.

[0048] A fixed stop BF is arranged between the pivot axis AB and the rear part TAPV of the locking pin PV.

[0049] In the rest angular position PR of the swinging body B, the free end portions of the two arms of the return spring R elastically lean against the cylindrical wall portion of the rear portion TAPV of the locking pin PV.

[0050] How it works When the drive assembly is in the neutral position (Figures 4A and 4B): Each lever L1, L2 is in its neutral angle position PM1, PM2, and the moving body B is in its rest position PR. The locking pin PV is disposed between the two locking notches CR1 and CR2, Each lever L1, L2 is pivotable in one direction or the other about its axis A1, A2.

[0051] i) When changing the first ratio (Figures 5A and 5B): By leaving the position shown in Figures 4A and 4B, the first rotary actuator AR1 drives the first lever L1 to pivot counterclockwise towards its first operating position PA11, During this rotation, the first operating portion TA11 of the first cam profile PC1 interacts with the locking pin PV to swing the swinging body B counterclockwise, and the locking pin PV enters the second locking notch CV2. The second lever L2 is then angularly locked in its neutral position PM2, By again driving the first lever L1 in a clockwise direction, the interlocking system SI returns to the state shown in Figures 4A and 4B, and the rocker B returns elastically towards its rest position PR by the return spring R.

[0052] ii) When changing the second ratio (Figures 6A and 6B): By leaving the position shown in Figures 4A and 4B, the first rotary actuator AR1 drives the first lever L1 to pivot in a clockwise direction towards its second operating position PA12, During this pivoting, the second actuating portion TA12 of the first cam profile PC1 interacts with the locking pin PV to swing the swinging body B counterclockwise, so that the locking pin PV enters the second locking notch CV2; The second lever L2 is then angularly locked in its neutral position PM2, By again driving the first lever L1 counterclockwise, the interlocking system SI returns to the state shown in Figures 4A and 4B, and the rocker B returns elastically towards its rest position PR by the return spring R.

[0053] iii) When changing the third ratio (Figure 7A and Figure 7B): By leaving the position shown in Figures 4A and 4B, the second rotary actuator AR2 drives the second lever L2 to pivot counterclockwise towards its first operating position PA21, During this pivoting, the first actuating portion TA21 of the second cam profile PC2 interacts with the locking pin PV to swing the swinging body B clockwise, so that the locking pin PV enters the first locking notch CV1; The first lever L1 is then angularly locked in its neutral position PM1, By again driving the second lever L2 in a clockwise direction, the interlocking system SI returns to the state shown in Figures 4A and 4B, and the rocker B returns elastically towards its rest position PR by the return spring R.

[0054] iv) When changing the fourth ratio (Figure 8A and Figure 8B): By leaving the position shown in Figures 4A and 4B, the second rotary actuator AR2 drives the second lever L2 to pivot in a clockwise direction towards its second operating position PA22, During this pivoting, the first actuating portion TA22 of the second cam profile PC2 interacts with the locking pin PV to swing the swinging body B clockwise, so that the locking pin PV enters the first locking notch CV1; The first lever L1 is then angularly locked in its neutral position PM1, By again driving the second lever L2 counterclockwise, the interlocking system SI returns to the state shown in Figures 4A and 4B, and the rocker B returns elastically towards its rest position PR by the return spring R.

[0055] The design of the mechanical linkage system according to the invention is particularly robust and allows the linkage to be complemented by a control system linked to manage the electrically operated actuators.

[0056] The interlocking system according to the present invention is easily retrofitted to an existing drive assembly E without modifying the way in which this assembly is joined to the other components of the gearbox.

[0057] In variations within the scope of the present invention, the linkage system is not limited to the case where each fork shaft moves in two opposite directions to change two separate ratios.

[0058] For example, each shaft or only one of the two shafts may move in a single direction.

[0059] Furthermore, the interlocking system according to the invention is not limited to the case where both levers L1 and L2 are levers that drive two fork shafts and are part of the interlocking system.

[0060] For example, a linear actuator may be used for each fork shaft AF1, AF2, with each finger D1, D2 having a separate arrangement of a linkage system SI according to the invention connected exclusively for movement to the associated shaft AF1, AF2.

Claims

1. A system (SI) for coupling the movement of two shafts (AF1, AF2) of a gearbox fork (F1, F2), said system comprising: a) a first lever (L1), mounted so as to be pivotable in two opposite directions about a first axis (A1) to assume at least one operating angular position (PA11, PA12) relative to a neutral position (PM1); carrying a first eccentric axial finger (D1) connected to the first drive shaft (AF1) of the first fork (F1); a first eccentric cam (C1) whose first cam contour (PC1) carries a first eccentric cam (C1) having a first locking notch (CV1) for locking the first lever (L1) in its neutral position (PM1); a first lever (L1); b) a second lever (L2), mounted so as to be pivotable in two opposite directions about a second axis (A2) parallel to said first axis (A1) so as to assume at least one operating angular position (PA21, PA22) relative to a neutral position (PM2); carrying a second eccentric axial finger (D2) connected to the second drive shaft (AF2) of the second fork (F2); a second eccentric cam (C2) whose second cam contour (PC2) has a second locking notch (CV2) for locking the second lever (L2) in its neutral position (PM2); a second lever (L2); c) A continuous moving body (B), The swingable body (B) is mounted so as to be pivotable in two opposite directions about a swing axis (AB) parallel to the first axis (A1) so as to take one or the other of two opposite locking angular positions (PV1, PV2) relative to an intermediate rest angular position (PR) to which the swingable body (B) elastically returns; An eccentric axial locking pin (PV) is supported, the locking pin (PV) being positioned so as to simultaneously face the first locking notch (CV1) and the second locking notch (CV2) when the swinging body (B) is in its rest angle position (PR) and the first lever (L1) and the second lever (L2) are each in their neutral positions (PM1, PM2). Continuously moving object (B) Equipped with In the system (SI), the first cam profile (PC1) of the first lever (L1) and the second cam profile (PC2) of the second lever (L2) each have actuating portions (TA11-TA12, TA21-TA22) at angles on both sides of their locking notches (CV1, CV2), and the actuating portions (TA11-TA12, TA21-TA22) are in contact with the locking pin (PV). A system (SI) that can interact with the other levers (L2, L1) to pivot the moving body (B) and engage the locking pin (PV) with the locking notch (CV2, CV1) of the eccentric cam (C2, C1) of the other lever (L2, L1), and then hold the locking pin (PV) in this locking engagement position so as to angularly lock the other lever (L2, L1) in its neutral position (PM2, PM1).

2. The system (SI) described in claim 1, characterized in that each of the first cam contour (PC1) and the second cam contour (PC2) has at least one operating portion (TA11-TA12, TA21-TA22) having a convex arc shape centered on the axis (A1, A2) of the associated lever (L1, L2) adjacent to the locking notch (CV1, CV2).

3. 3. A system (SI) according to claim 1 or 2, characterized in that the first axis (A1), the locking pin (PV) and the second axis (A2) are aligned regardless of the angular position of each lever (L1, L2).

4. 4. The system (SI) according to claim 3, characterized in that when the coupling swing body (B) is in its rest angular position (PR) and each lever (L1, L2) is in its neutral position (PM1, PM2), the first axis (A1), the first locking notch (CV1), the locking pin (PV), the second locking notch (CV2) and the second axis (2) are aligned.

5. 3. A system (SI) according to claim 2, characterized in that the locking pin (PV) is received between the first cam contour (PC1) and the second cam contour (PC2), regardless of the angular position of each lever (L1, L2).

6. A system (SI) according to any one of claims 1 to 5, characterized in that each lever (L1, L2) is a lever for driving an associated drive shaft (AF1, AF2) of a fork (F1, F2).

7. 7. A system (SI) according to claim 1, characterized in that the first lever (L1) is mounted so as to be pivotable in two opposite directions about the first axis (A1) to assume one or the other of two opposite operating angular positions (PA11, PA12) relative to its neutral position (PM1), and the second lever (L2) is mounted so as to be pivotable in two opposite directions about the second axis (A2) to assume one or the other of two opposite operating angular positions (PA21, PA22) relative to its neutral position (PM2).

8. A system (SI) as described in claim 7, characterized in that each of the first cam contour (PC1) and the second cam contour (PC2) has two operating parts (TA11-TA12, TA21-TA22), the two operating parts (TA11-TA12, TA21-TA22) have a convex arc shape centered on the axis (A1, A2) of the associated lever (L1, L2), and the locking notch (CV1, CV2) is positioned between the two operating parts (TA11-TA12, TA21-TA22).

9. Assembly (E) for actuating two shafts (AF1, AF2) of a gearbox fork (F1, F2), said assembly (E) comprising: a first rotary actuator (AR1) and a second rotary actuator (AR2) to be controlled, the output shafts of which are parallel; A system (SI) according to any one of claims 1 to 8 for coupling the movement of the two shafts (AF1, AF2) of the forks (F1, F2), and and Assembly (E), characterized in that said first rotary actuator (AR1) drives the pivoting of said first lever (L1) and said second rotary actuator (AR2) drives the pivoting of said second lever (L2).

10. 10. An assembly (E) according to claim 9, characterized in that the rotation axes of the output shafts of the first rotary actuator (AR1) and the second rotary actuator (AR2) are perpendicular to the parallel sliding axes of the two shafts (AF1, AF2) of the forks (F1, F2).

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