Assembly for actuation and system for interlocking two gearbox shifter shafts

Abstract

The invention relates to an assembly (E) for actuating two fork shafts of a gearbox, comprising two rotary actuators (AR1, AR2) and a system (SI) for interlocking, having a first lever (L1) supporting a drive finger (D1) of a first fork and supporting a cam (C1) whose profile comprises a notch (CV1) for locking the first lever (L1), a second lever (L2) supporting a drive finger of a second fork and supporting a cam (C2) whose profile comprises a second notch (CV2) for locking the second lever (L2), and a pivoting interlocking rocker (B) supporting a locking pin (PV) which can interact with one or other of the two locking notches (CV1, CV2) in order to angularly lock the associated lever (L1, L2) when the other lever (L2, L1) is actuated in order to engage a transmission ratio.

Description

Technical Field

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

[0002] This invention can be notably applied to so-called automatic transmissions, in which each shift fork shaft is connected to an axle whose movement is caused by a motorized actuator managed by a control unit. Background Technology

[0003] To manage gear ratio changes, an internal control assembly is known, which consists, for example, of an actuator and a shift fork shaft or main shaft dedicated to the gear or gear ratio of the electric motor of the transmission of a motor vehicle (referred to as the electric gear or gear ratio with respect to the electric motor) and the gear or gear ratio of the hybrid drive; two shafts and two shift forks are dedicated to the gear of the combustion engine with respect to such hybrid drive, referred to as the combustion engine gear.

[0004] This "hybrid" transmission works by simultaneously changing the gear ratio of the combustion engine and the electric drive. However, both gears of the same type (electric or combustion engine) must be able to change simultaneously.

[0005] This involves a principle known as gear interlock.

[0006] This therefore involves two shafts and shift forks used to change the gears of the combustion engine.

[0007] In a known manner, each shift fork shaft is associated with a first motor that drives an eccentric finger to rotate, which in turn drives the shift fork shaft independently of the others.

[0008] Interlocking is provided primarily by managing each of the rotary actuators or motors.

[0009] To enhance safety, this invention proposes a mechanical interlock system design that can be integrated into motorized actuation components. Summary of the Invention

[0010] This invention proposes a system for interlocking the movement of two shafts of a gearbox shift fork, the system comprising:

[0011] -a) The first lever, the first lever:

[0012] -- Installed to be able to pivot about a first axis in two opposite directions to occupy at least one effective angular position relative to the neutral intermediate angular position;

[0013] --Supports a first eccentric axial finger portion, which is connected to the first drive shaft of the first shift fork;

[0014] --Support a first eccentric cam, the cam profile of which has a first notch for locking a first lever in a neutral position;

[0015] -b) The second lever:

[0016] -- Installed to be able to pivot in two opposite directions about a second axis parallel to the first axis to occupy at least one effective angular position relative to the neutral intermediate angular position;

[0017] --Supports the second eccentric axial finger, which is connected to the second drive shaft of the second shift fork;

[0018] --Support a second eccentric cam, the cam profile of which has a second notch for locking the second lever in a neutral position;

[0019] -c) and the interlocked joystick, which:

[0020] --- Installed to pivot in two opposite directions about a rocking axis parallel to the first axis to occupy one or the other of two opposite locking angular positions relative to the intermediate angular rest position, the interlocking rocker elastically reset toward the intermediate angular rest position;

[0021] ---The eccentric axial locking pin supports the interlocking rocker arm in its angular rest position and each drive lever in its neutral angular position, and is positioned to simultaneously face the first and second locking recesses.

[0022] In this system, angularly on either side of its locking recess, each cam profile of the lever has an effective portion that can interact with a locking pin to pivot the interlocking rocker and engage the locking pin in the locking recess of the cam of another lever, and then hold the locking pin in this locked engagement position to angularly lock the other lever in a neutral position.

[0023] Based on other characteristics of interlocking systems:

[0024] - Each cam profile has at least one effective portion in the shape of a convex arc, the convex arc being centered on the axis of the associated lever, the at least one effective portion being adjacent to the locking notch;

[0025] - Regardless of the angular position of each lever, the first axis, locking pin, and second axis are aligned;

[0026] - When the interlocking rocker is in its angular rest position and when each lever is in its neutral angular position, the first axis, the first locking notch, the locking pin, the second locking notch, and the second axis are aligned;

[0027] - Regardless of the angular position of each lever, the locking pin is received between the first cam profile and the second cam profile;

[0028] - Each lever is a lever used to drive the associated drive shaft of the shift fork;

[0029] - The first lever is mounted to be pivotable about the first axis in two opposite directions to occupy one or the other of two opposite effective angular positions relative to its neutral intermediate angular position, and the second lever is mounted to be pivotable about the second axis in two opposite directions to occupy one or the other of two opposite effective angular positions relative to its neutral intermediate angular position.

[0030] - Each cam profile has two active parts in the shape of a convex arc centered on the axis of the associated lever, and a locking notch is arranged between these active parts.

[0031] The present invention also proposes an assembly for two shafts of actuating a shift fork of a gearbox, characterized in that the assembly has:

[0032] - A first rotary actuator and a second rotary actuator, which are controlled, and the output shafts of the first rotary actuator and the second rotary actuator are parallel;

[0033] - and a system according to the invention for interlocking the movement of the two axes of the shift fork.

[0034] Furthermore, the first rotary actuator drives the first drive lever to pivot, and the second rotary actuator drives the second drive lever to pivot.

[0035] The rotation axes of the output shafts of the two rotary actuators are orthogonal to the parallel sliding axes of the two shift fork shafts. Attached Figure Description

[0036] Other features and advantages of the invention will become clear from the following detailed description, which will be understood with reference to the accompanying drawings, in which:

[0037] [ Figure 1 ]– Figure 1 This is a three-dimensional front view showing an exemplary embodiment of an assembly of three parallel shafts for actuating a shift fork for changing the gear position of a transmission, two of which are equipped with an interlocking system according to the invention.

[0038] [ Figure 2 ]– Figure 2 Is with Figure 1 A view similar to the view without a shift fork axis or associated shift fork;

[0039] [ Figure 3A ]– Figure 3A yes Figure 2 A three-dimensional front view of an interlocking system;

[0040] [ Figure 3B ]– Figure 3B yes Figure 2 A three-dimensional rear view of the interlocking system;

[0041] [ Figure 4A ]– Figure 4A yes Figure 3A and Figure 3B A front view of the interlocking system, showing two locking levers, each in its neutral position, and an interlocking rocker arm in its stationary position;

[0042] [ Figure 4B ]– Figure 4B yes Figure 4A Rear view of the interlocking system;

[0043] [ Figure 5A ]– Figure 5A Is with Figure 4A A view similar to the one shown, in which the first lever is in its effective position for shifting to the first gear, and the second lever is locked in its neutral position by an interlocking rocker arm in the locked position;

[0044] [ Figure 5B ]– Figure 5B yes Figure 5A Rear view of the interlocking system;

[0045] [ Figure 6A ]– Figure 6A Is with Figure 4A A view similar to the one in which the first lever is in another effective position as it changes to the second gear, and the second lever is locked in the neutral position by an interlocking rocker arm in the locked position;

[0046] [ Figure 6B ]– Figure 6B yes Figure 6A Rear view of the interlocking system;

[0047] [ Figure 7A ]– Figure 7A Is with Figure 4AA view similar to the one shown, in which the first lever is locked in a neutral position by an interlocking rocker arm in its other locked position, and the second lever is in its effective position for shifting to the third gear;

[0048] [ Figure 7B ]– Figure 7B yes Figure 7A Rear view of the interlocking system;

[0049] [ Figure 8A ]– Figure 8A Is with Figure 4A A view similar to the one shown, in which the first lever is locked in a neutral position by an interlocking rocker arm in its other locked position, and the second lever is in another effective position where it is shifted to the fourth gear.

[0050] [ Figure 8B ]– Figure 8B yes Figure 8A Rear view of the interlocking system. Detailed Implementation

[0051] By convention, the geometric axes indicated in the diagram are oriented front to back.

[0052] In the following description, the same, similar or analogous elements will be referred to by the same reference numerals.

[0053] Figure 1 The assembly E is shown, consisting of three parallel shafts AF1, AF2, and AF3 for actuating three shift forks F1, F2, and F3 belonging to a motor vehicle transmission.

[0054] In a known manner, each shift fork axis is fixed in terms of translational movement about the axis of its associated shift fork.

[0055] In a known manner and without limitation, each axis AF1, AF2 and AF3 drives axial shift forks F1, F2 and F3 to perform axial translational movement, which are themselves connected, in terms of translational movement, to gear shifting aids DA1, DA2 and DA3 of a well-known design, such as those gear shifting aids shown in document FR-A1-2.988.800.

[0056] By way of non-limiting example, two first torques AF1-F1 and AF2-F2 are used to change the gear ratio known as the "combustion engine" gear ratio, thereby changing the rotational speed of the combustion engine, while a third torque AF3-F3 is used to change the gear ratio known as the "electric" gear ratio, thereby changing the rotational speed of the electric motor, for example, the electric motor is part of a hybrid powertrain associated with the combustion engine.

[0057] In this configuration, each drive shaft can be driven axially in two directions relative to a neutral intermediate axial position, where the gear is not engaged.

[0058] The first torque AF1-F1 can, for example, cause a change in the first and second gears, while the second torque AF2-F2 can cause a change in the third and fourth gears.

[0059] In order to drive the first shaft AF1 and its associated fork F1, the actuation assembly E has a first controlled rotary actuator AR1, which is capable of driving the first lever L1 to pivot about the geometric pivot axis A1 in two opposite directions.

[0060] In order to drive the second shaft AF2 and its associated fork F2, the actuation assembly E has a second controlled rotary actuator AR2, which is capable of driving the second lever L2 to pivot about the geometric pivot axis A2 in two opposite directions.

[0061] The two rotary actuators AR1 and AR2 have parallel axes and are, for example, the output shafts of an electric motor (not shown) incorporated in the actuation assembly E.

[0062] According to the teachings of the present invention, the movement of the two axes AF1 and AF2 is associated with an interlocking system SI, which mainly consists of the following:

[0063] - First lever L1, which in this case is a lever used to drive the first shaft AF1 in both directions;

[0064] - Second lever L2, which in this case is a lever used to drive the second lever L2 in both directions;

[0065] - and interlocking joystick B.

[0066] like Figure 3A and Figure 3B As can be seen in detail, the first lever L1 supports the first axial drive finger D1, which is eccentric relative to the axis A1, extends axially to the front, and is connected to the first shaft AF1 of the first shift fork F1 via the auxiliary device DA1.

[0067] Here, opposite in diameter to the first drive finger D1, the first lever L1 supports the first cam C1, which is eccentric relative to the axis A1.

[0068] The convex cylindrical edge of the first cam C1 is the cam profile PC1, which sequentially has a first effective portion TA11 in the shape of a cylindrical arc, a first notch CV1 for angularly locking the first lever L1, and a second effective portion TA12 in the opposite cylindrical arc shape.

[0069] The first lever L1 also has a first centering drive rod TE1, which extends axially to the rear and is driven by a first rotary actuator AR1.

[0070] Similarly, the second lever L2 supports the second axial drive finger D2, which is eccentric relative to the axis A2, extends axially to the front, and is connected to the first shaft AF2 of the first shift fork F2 via the auxiliary device DA2.

[0071] Here, the second lever L2 supports the second cam C2, which is eccentric relative to the axis A2, and is offset from the second drive finger D2 at an angle to the ground.

[0072] The convex cylindrical edge of the second cam C2 is the cam profile PC2, which has a first effective portion TA21 in the shape of a cylindrical arc, a second notch CV2 for angularly locking the second lever L2, and a second effective portion TA22 in the opposite cylindrical arc shape.

[0073] The second lever L2 also has a second centering drive rod TE2, which extends axially to the rear and is driven by a second rotary actuator AR2.

[0074] The first lever L1 can occupy three separate functional angular positions, including a neutral position PM1 with the gear not engaged and two opposite effective angular positions: PA11, where the first gear is engaged; and PA12, where the second gear is engaged via the first shift fork F1.

[0075] The second lever L2 can occupy three separate functional angular positions, including a neutral position PM2 with the gear not engaged and two opposite effective angular positions: PA21, where the third gear is engaged; and PA22, where the fourth gear is engaged via the second shift fork F2.

[0076] The relative positioning and dimensions of the two levers L1 and L2 result in a constant minimum clearance EF between two opposing convex cylindrical cam profiles PC1 and PC2.

[0077] like Figure 3A , Figure 3B as well as Figure 4A , Figure 4BAs can be seen, 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.

[0078] Near its proximal end, an interlocking rocker arm B is installed, which is capable of pivoting relative to the housing of the drive assembly E about a rocking axis AB that is parallel to the pivot axes A1 and A2 of the two levers L1 and L2.

[0079] In this case, the interlocking rocker arm B is a plate that can pivot about the rocking axis AB in two opposite directions to occupy a position relative to... Figures 3A to 4B The figure shows one or the other of the two opposite angular locking positions PV1 and PV2 of the intermediate angular stationary position PR.

[0080] The interlocking rocker arm B is constantly and elastically reset toward its angular rest position PR by a reset system arranged on its rear surface.

[0081] By way of a non-limiting example, the reset system in this case has a reset spring R in the shape of a so-called hairpin, which interacts with a fixed stop BF supported by the housing of the drive assembly E.

[0082] Near its other distal end, interlocking rocker B supports an eccentric cylindrical locking pin PV, which extends axially to the front and between the two cam profiles PC1 and PC2 to interact with them.

[0083] The outer diameter of the locking pin PV is greater than the value of the clearance EF.

[0084] The positions and dimensions of the two levers L1 and L2 and the interlocking rocker arm B make:

[0085] - Regardless of the angular position of each lever L1, L2 and interlocking rocker B, the locking pin PV is always located between the two cam profiles PC1 and PC2;

[0086] - When the interlocking rocker B is in its angular rest position PR and when each drive lever L1, L2 is in its neutral angular 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 both the first locking notch CV1 and the second locking notch CV2 (see...). Figure 3A and Figure 4A ).

[0087] To ensure its elastic return to its angular rest position, the locking pin PV also extends axially to the rear, between the free ends of the two arms of the hairpin-shaped return spring R.

[0088] The fixed stop portion BF is arranged between the pivot axis AB and the rear portion TAPV of the locking pin PV.

[0089] At the angular rest position PR of the interlocking rocker B, the free ends of the two arms of the return spring R elastically abut against the cylindrical wall of the rear portion TAPV of the locking pin PV.

[0090] Operating Instructions

[0091] The driver component is in a neutral position. ( Figure 4A and Figure 4B ):

[0092] - Each lever L1, L2 is in its neutral angular position PM1, PM2, and the interlocking rocker B is in its rest position PR.

[0093] - The locking pin PV is positioned between two locking notches CR1 and CR2.

[0094] - Each lever L1, L2 pivots freely about its axis A1, A2 in one direction or the other.

[0095] i) Change of first gear ( Figure 5A and Figure 5B ):

[0096] - By leaving Figure 4A and Figure 4B At the position shown, the first rotary actuator AR1 drives the first lever L1 to pivot counterclockwise toward its first effective position PA11.

[0097] During this pivoting process, the first effective portion TA11 of the first cam profile PC1 interacts with the locking pin PV to cause the interlocking rocker B to rock counterclockwise and to engage the locking pin PV into the second locking notch CV2.

[0098] -The second lever L2 is then angularly locked in its neutral position PM2.

[0099] - By driving the first lever L1 clockwise again, the interlock system SI returns to its original position. Figure 4A and Figure 4B As shown in the diagram, rocker arm B is elastically reset by the return spring R toward its rest position PR.

[0100] ii) Change of second gear ( Figure 6A and Figure 6B ):

[0101] - By leaving Figure 4A and Figure 4BAt the position shown, the first rotary actuator AR1 drives the first lever L1 to pivot clockwise toward its second effective position PA12.

[0102] During this pivoting process, the second effective portion TA12 of the first cam profile PC1 interacts with the locking pin PV to cause the interlocking rocker B to rock counterclockwise and to engage the locking pin PV into the second locking notch CV2.

[0103] -The second lever L2 is then angularly locked in its neutral position PM2.

[0104] - By driving the first lever L1 counterclockwise again, the interlock system SI returns to its original position. Figure 4A and Figure 4B As shown in the diagram, rocker arm B is elastically reset by the return spring R toward its rest position PR.

[0105] iii) Change of third gear ( Figure 7A and Figure 7B ):

[0106] - By leaving Figure 4A and Figure 4B At the position shown, the second rotary actuator AR2 drives the second lever L2 to pivot counterclockwise toward its first effective position PA21.

[0107] During this pivoting process, the first effective portion TA21 of the second cam profile PC2 interacts with the locking pin PV to cause the interlocking rocker B to rock clockwise and to engage the locking pin PV into the first locking notch CV1.

[0108] -The first lever L1 is then angularly locked in its neutral position PM1.

[0109] - By driving the second lever L2 clockwise again, the interlock system SI returns to its original position. Figure 4A and Figure 4B As shown in the diagram, rocker arm B is elastically reset by the return spring R toward its rest position PR.

[0110] iv) Change of fourth gear ( Figure 8A and Figure 8B ):

[0111] - By leaving Figure 4A and Figure 4B In the position shown, the second rotary actuator AR2 drives the second lever L2 to pivot clockwise toward its second effective position PA22.

[0112] During this pivoting process, the first effective portion TA22 of the second cam profile PC2 interacts with the locking pin PV to cause the interlocking rocker B to rock clockwise and to engage the locking pin PV into the first locking notch CV1.

[0113] -The first lever L1 is then angularly locked in its neutral position PM1.

[0114] - By driving the second lever L2 counterclockwise again, the interlock system SI returns to its original position. Figure 4A and Figure 4B As shown in the diagram, rocker arm B is elastically reset by the return spring R toward its rest position PR.

[0115] The mechanical interlock system according to the invention is designed to be particularly robust and allows for the supplementation of interlocking functions associated with the control system and the management of motorized actuators.

[0116] The interlock system according to the present invention can be easily integrated into the existing drive assembly E, and the way this assembly is integrated into other parts of the gearbox remains unchanged.

[0117] In variations, within the scope of this invention, the interlocking system is not limited to the case where each shift fork shaft moves in two opposite directions to change two separate gears.

[0118] Each axis, or only one of two axes, can move in a single direction, for example.

[0119] The interlocking system according to the present invention is not limited to two levers L1 and L2 that are both levers used to drive two shift fork shafts and are part of the interlocking system.

[0120] A linear actuator can be used for each shift fork shaft AF1, AF2 and an interlocking system SI according to the invention can be arranged separately, wherein each finger D1, D2 is connected to the associated shaft AF1, AF2 only in terms of movement.

Claims

1. A system (SI) for interlocking the movement of two shafts (AF1, AF2) of a gearbox shift fork (F1, F2), the system comprising: - a) First lever (L1), the first lever: -- Installed to be able to pivot about the first axis (A1) in two opposite directions to occupy at least one effective angular position (PA11, PA12) relative to the neutral intermediate angular position (PM1). -- Supports the first eccentric axial finger (D1), which is connected to the first drive shaft (AF1) of the first shift fork (F1); -- Support a first eccentric cam (C1), the cam profile (PC1) of the first eccentric cam having a first locking notch (CV1) for locking the first lever (L1) in a neutral intermediate angular position (PM1). - b) The second lever (L2): -- Installed to be able to pivot in two opposite directions about a second axis (A2) parallel to the first axis (A1) to occupy at least one effective angular position (PA21, PA22) relative to the neutral intermediate angular position (PM2). -- Supports the second eccentric axial finger (D2), which is connected to the second drive shaft (AF2) of the second shift fork (F2); -- Support a second eccentric cam (C2), the cam profile (PC2) of the second eccentric cam having a second locking notch (CV2) for locking the second lever (L2) in a neutral intermediate angular position (PM2). - c) and the interlocking joystick (B), the interlocking joystick: --- Installed to pivot in two opposite directions about a rocking axis (AB) parallel to the first axis (A1) to occupy one or the other of two opposite locking angular positions (PV1, PV2) relative to the intermediate angular rest position (PR), the interlocking rocker (B) elastically resets toward the intermediate angular rest position; --- Support eccentric axial locking pin (PV), when the interlocking rocker (B) is in its intermediate angular rest position (PR) and when each drive lever (L1, L2) is in its neutral intermediate angular position (PM1, PM2), the eccentric axial locking pin is positioned to face both the first locking notch (CV1) and the second locking notch (CV2). In this system (SI) Angularly on either side of its locking recess (CV1, CV2), the cam profile (PC1, PC2) of each of the first and second levers (L1, L2) has an effective portion (TA11-TA12, TA21-TA22) that can interact with the locking pin (PV) to pivot the interlocking rocker (B) and engage the locking pin (PV) into the locking recess (CV2, CV1) of the eccentric cam (C2, C1) of the other lever (L2, L1), and then hold the locking pin (PV) in this locked engagement position to angularly lock the other lever (L2, L1) in a neutral intermediate angular position (PM2).

2. The system (SI) as claimed in claim 1, characterized in that, Each cam profile (PC1, PC2) has at least one effective portion (TA11-TA12, TA21-TA22) in the shape of a convex arc, the convex arc being centered on the axis (A1, A2) of its associated lever (L1, L2), the at least one effective portion being adjacent to the locking notch (CV1, CV2).

3. The system (SI) as described in any one of the preceding claims, characterized in that, Regardless of the angular position of each lever (L1, L2), the first axis (A1), the locking pin (PV), and the second axis (A2) are aligned.

4. The system (SI) as described in claim 3, characterized in that, When the interlocking rocker (B) is in its intermediate angular rest position (PR) and when each lever (L1, L2) is in its neutral intermediate angular 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.

5. The system (SI) as described in claim 2, characterized in that, Regardless of the angular position of each lever (L1, L2), the locking pin (PV) is received between the cam profile (PC1) of the first eccentric cam and the cam profile (PC2) of the second eccentric cam.

6. The system (SI) as described in any one of the preceding claims, characterized in that, Each lever is a lever (L1, L2) used to drive the associated drive shaft (AF1, AF2) of the shift fork (F1, F2).

7. The system as described in any one of the preceding claims, characterized in that, The first lever (L1) is mounted to pivot about the first axis (A1) in two opposite directions to occupy one or the other of two opposite effective angular positions (PA11, PA12) relative to its neutral intermediate angular position (PM1), and the second lever (L2) is mounted to pivot about the second axis (A2) in two opposite directions to occupy one or the other of two opposite effective angular positions (PA21, PA22) relative to its neutral intermediate angular position (PM2).

8. The system (SI) as described in claim 7, characterized in that, Each cam profile (PC1, PC2) has two active parts (TA11-TA12, TA21-TA22) that are in the shape of a convex arc centered on the axis (A1, A2) of its associated lever (L1, L2), and the locking notch (CV1, CV2) is arranged between these active parts.

9. An assembly (E) of two shafts (AF1, AF2) for an actuating gearbox shift fork (F1, F2), characterized in that, The component has: - A first rotary actuator (AR1) and a second rotary actuator (AR2), the first rotary actuator and the second rotary actuator being controlled, and the output shafts of the first rotary actuator and the second rotary actuator being parallel; - and the system (SI) as described in any of the preceding claims. It is characterized in that the first rotary actuator (AR1) drives the first lever (L1) to pivot, and the second rotary actuator (AR2) drives the second lever (L2) to pivot.

10. The component (E) as claimed in claim 9, characterized in that, The rotation axes of the output shafts of the two rotary actuators are orthogonal to the parallel sliding axes of the two axes (AF1, AF2) of these forks (F1, F2).

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