JP2003507671A - Transmissions, especially for land vehicles - Google Patents

Abstract

(57) [Summary] The present invention provides an application force defined by a centrifugal counterweight (29) when a torque to be transmitted by a transmission exceeds a value that can be directly transmitted by a drive clutch (18). In view of this, the clutch slides, the planetary pinion carrier (13) connected to the output shaft (2b) is decelerated, the planetary gear (9) is further decelerated and finally restrained by the freewheel (16). Transmission system. As a result, the reaction force (Pac) of the tooth portion of the ring (8) being biased releases the clutch (18) via the axial stop (B2), so that all of the clutches (18) are released. The resulting deceleration takes effect while eliminating friction. The axial movement of the ring (8) is relative to the engine (5) while allowing the member (17a) supporting the ring (8) to slide with respect to the input member (17b). Enabled by a coupling device (17) that transmits torque. The connection device (17) is a frictionless device that functions by, for example, deforming an elastic material. The present invention is useful in enhancing smooth engagement for changing transmission ratios by eliminating axial motion friction, which often increases non-linearly with transmitted torque.

Description

Detailed Description of the Invention

[0001]   The present invention relates to a transmission, especially for land vehicles.

More particularly, the present invention is not limited, but relates to an automatic transmission in which the characteristics of transmission ratio changes, especially with regard to progressiveness, are improved even after extended use.

Particularly in transmissions such as automatic transmissions, changing the transmission ratio is performed by activating a selective coupling device and releasing another selective coupling device. These selective coupling devices can be in particular multi-plate clutches or brakes.

The characteristics of the transmission ratio change, especially the smoothness, depend on how well the movement of the movable member that clamps the disc stack is controlled in the case of a multi-disc clutch. In certain applications, such a clamping member is also a torque transmission member, which slides via a spline against another transmission member which is axially fixed with respect to the transmission casing.

According to the present invention, it has been discovered that these splines, although commonly used, have many disadvantages and drawbacks in practice.

That is, if the spline is formed along the circumference of a small diameter, the guiding in sliding is correct and the pressure between the side portions of the spline does not exceed a predetermined limit value.
It is necessary to give each spline a long axial length. These problems can be overcome to some degree by forming splines on the circumference of a large diameter, but the weight and radial dimensions of the connection can be prohibitive. Further, since the induction deteriorates with time when each spline starts to wear and play, the characteristics of the transmission ratio change caused by the sliding movement of the spline deteriorates due to the time change of the transmission.

It is an object of the present invention that the transmission ratio change characteristic is improved when the transmission is new and is maintained well during the aging of the transmission, especially for land vehicles. To suggest.

According to the present invention, each torque transmission member having a rotation input shaft and a rotation output shaft, and a selective coupling means mounted between two of the torque transmission members, A tooth row meshingly connected to at least some of the torque transmitting members, the input member and the output depending on whether the selective connecting means is in a connected state or a released state. A transmission, especially for a land vehicle, comprising a tooth row which forms two transmission ratios between the members, wherein the first transmission member of the transmission members is the state of the selective coupling means. Is mounted so as to be controlled by axial displacement, and rotation is connected between the first transmission member and the second transmission member of each transmission member to allow relative axial displacement. The transmission, in particular for land vehicles, equipped with means is Connection means, characterized in that it is essentially frictionless type with respect to the axial direction displacement of the first transmission member with respect to said second transmission member.

According to a first form, the connecting means comprises at least one deformable element having a variable dimension parallel to the axis.

The deformable element transmits rotational torque about the axis while the second element
During the axial movement of the first transmission member with respect to the transmission member, such movement is allowed without significant friction between the transmission members.

[0011]   According to the second mode, the connecting means is a rolling type.

Each element mounted for rolling between a first track which is a part of the first transmission member and a second track which is a part of the second transmission member is Transmits rotational torque to the other. Here again, any significant friction between the two transmission members is eliminated during the relative axial displacement between the two transmission members.

Other features and advantages of the invention will become more apparent from the following description of non-limiting examples.

A transmission having a two-step transmission ratio, which is particularly intended for motor vehicles and which is shown in FIG. 1, has an input shaft aligned along a common axis of rotation 12 which constitutes the main axis of the device.
2a and output shaft 2b. The input shaft 2a is connected to the output shaft of the vehicle engine 5 via the input clutch 48 and possibly other transmission means not shown. Output shaft 2b
Are intended to drive the drive wheels of the vehicle directly or indirectly. Output shaft
2b and each wheel of the vehicle, for example, another transmission having a transmission ratio of two stages or more, and / or a manually controlled forward drive / reverse drive reversing mechanism, and / or each vehicle A differential may be interposed that distributes motion between the drive wheels.

The input shaft 2a and the output shaft 2b are axially constrained with respect to the casing 4 of the transmission, which is shown only partly.

The transmission includes a differential gear mechanism formed by a planetary gear train (epicyclic train) 7. The gear train 7 includes a crown gear 8 having internal teeth and a sun gear 9 having external teeth, and both gears mesh with planetary gears 11 distributed around an axis 12 of the transmission. Each planetary gear 11 is rotatably supported by each eccentric journal 14 of a planetary gear holder 13 rigidly connected to the output shaft 2b. The sun gear 9 is free to rotate with respect to the output shaft 2b about an axis 12 of the transmission and surrounds the output shaft 2b. However, the reverse rotation of the sun gear 9, that is, the reverse rotation of the input shaft 2a with respect to the casing 4 of the transmission described above, is prevented by the free wheel device 16.

The crown gear 8 is connected to the input shaft 2 by the substantially solidified connecting device 17 in FIGS.
It is connected so that it can rotate in common with respect to a, but slidably in the axial direction.
7 is particularly the subject of the present invention and is therefore described in more detail below with reference to the other figures.

The connecting device 17 is formed between a first transmission member 17a that firmly carries the crown gear 8 and a second transmission member 17b that is rigidly integrated with the input shaft 2a.

The crown gear 8 is selectively connected to the planetary gear holder 13 by a multi-plate clutch 18.

The interleaved stack of discs 19 and discs 22 of the clutch 18 has an axial direction between a retaining plate 26 integral with the planetary gear holder 13 and a movable plate 27 which is part of the cage 20. The movable plate 27 is connected to the planetary gear holder 13 for common rotation, but can slide with respect to the planetary gear holder 13.
The cage 20 carries each inner spline 23, to which the peripheral teeth of each disc 22 and the peripheral teeth 24 of the holding plate 26 mesh. The first transmission member 17a carries each outer spline 33, and the inner peripheral tooth portion of each disk 19 meshes with each outer spline 33.

The cage 20 includes a cage 20 around the main axis 12, and thus a planetary gear holder 13.
Of the output shaft 2b and the axial compressive clamping force of the output shaft 2b, which changes according to the rotation speed.
, 22 supporting a centrifugal actuator 25 intended to be applied to the stack. Centrifugal actuator 25 comprises each centrifugal governor weight 29 arranged in a crown formation around clutch 18. Since each speed control weight is supported by the cage 20, it is restrained by the rotation of the output shaft 2b of the transmission.

Each speed control weight can be visually identified by a dotted line in FIG. 1 from the rest position E _R (solid line in FIGS. 1 and 2) defined by the contact of the stop 36 of each speed control weight with the cage 20. Rotation of the planetary gear holder 13 around the main axis 12 causes the main body 31 of each centrifugal speed control weight 29 to move under the action of centrifugal force in order to move it to the position E which is slightly expanded in the radial direction. There is a tendency to pivot radially outward about a tangential pivot axis 28 of the body.

As a result, a relative axial displacement occurs between the protrusion 32 of each governor weight and the pivot axis 28 of the governor weight. This displacement, which brings the projection 32 closer to the movable plate 27, corresponds to the compression of the spring element 34 mounted between the projection 32 and the holding plate 26 and / or the compression clamping direction of the clutch 18. At, the displacement of the movable plate 27 towards the holding plate 26 can be accommodated. In the illustrated embodiment, the spring element 34 is constituted by two countersunk washers mounted in series and opposite one another.

When the transmission is in the resting state shown by the solid line in FIG. 1, the spring element 34 pre-stresses the cage 20 via the respective centrifugal speed control weights 29 in their respective resting positions E _R. This preliminary suppression force applies torque so that the input shaft 2a of the transmission is connected to the rotation with the output shaft 2b and a predetermined maximum value defined by the preliminary suppression force of the spring element 34. The clutch 18 is compressed and sandwiched so that the transmission constitutes a direct drive which can be transmitted.

The teeth of the crown gear 8, the planetary gears 11 and the sun gear 9 are of spiral type. Therefore, in each pair of teeth that mesh under load, shafts in mutually opposite directions proportional to the transmitted circumferential force and thus proportional to the torque on the input shaft 2a and the torque on the output shaft 2b. Mental thrust appears. The helical inclination direction of each tooth is such that the axial thrust Pac (FIG. 2) generated in the crown gear 8 when the crown gear 8 is transmitting the drive torque is the first transmission member 17a.
And the axial thrust bearing B2, the crown gear 8 is selected to be applied in the direction for disengaging the clutch 18 by pressing each movable plate 27 in the direction for separating the plates 26 and 27. It The force Pac also tends to bring the protrusions 32 of each centrifugal governor 29 and the holding plate 26 closer to each other, thus bringing or maintaining each centrifugal governor 29 in their rest position E _R. With the tendency to compress the spring element 34. Each planetary gear 11 that meshes not only with the crown gear 8 but also with the sun gear 9 receives two axially counteracting reactions PS1 and PS2 that are opposed and balanced, and the sun gear 9 meshes with each planetary gear 11 Considering this, the axial gear thrust Pac of the crown gear 8 has the same strength and receives the axial thrust Pap in the opposite direction. The thrust Pap of the sun gear 9 is transmitted to the casing 4 via the axial thrust bearing B3.

Such a situation is shown in FIG. Next, the basic operation of the present transmission will be described assuming that the above operating state has been achieved. As long as the torque transmitted by the input shaft 2a is such that the axial thrust Pac of the crown gear 8 is sufficient to push back each projection 32 of each centrifugal speed governor 29 via the spring element 34, The separation between the holding plate 26 and the movable plate 27 of the clutch is such that the disks 19 and 22 slide relative to each other without transmitting torque between the disks 19 and 22.

Therefore, the planetary gear holder 13 can rotate at a speed different from the speed of the input shaft 2a, and
The planetary gear holder 13 tends to be constrained by the load that the output shaft 2b should drive. As a result, each planetary gear 11 tends to behave as a motion inverter, that is, the sun gear 9 tends to rotate in the direction opposite to the rotation direction of the crown gear 8. However, this is prevented by the free wheel 16. Therefore, the sun gear 9 is constrained by the free wheel 16, and the planetary gear holder 13 has the zero speed of the sun gear 9 and the crown gear 8 and the input shaft 2a.
Rotates at a speed intermediate to that of. Therefore, the transmission operates as a reduction gear unit. For example, if the rotational speed increases and the torque does not change, the centrifugal force of each centrifugal speed governor 29 causes the axial thrust Th of the holding plate 26 against the movable plate 27.
At the time when the axial compressive clamping force larger than c is generated, each centrifugal speed governing weight 25 rises to their position E (FIG. 1), and the movable plate 27 is pressed toward the holding plate 26. As a result, a direct drive different from that shown in FIG. 1 is achieved only in that the spring is further compressed by the protrusions 32 of the speed control weights.

The clutch 18 moves from the crown gear 8 constrained by the input shaft 2a to the planetary gear holder 13 constrained by the output shaft 2b as the clutch 18 is engaged during the change to the direct drive. Directly and incrementally transmitting power. Therefore, the action of each tooth of the planetary gear train 7 is gradually reduced, that is, the force transmitted by each tooth is gradually reduced.
The axial thrust Pac gradually decreases and eventually disappears. Therefore, the axial thrust due to the centrifugal force can be completely applied to clamp the plates 26 and 27 against each other.

In that case, the rotational speed of the output shaft 2b is reduced and / or the torque to be transmitted to a level at which each centrifugal speed control weight 29 no longer provides a sufficient compressive clamping force in the clutch 18 to transmit the torque. Can increase. In this case, the clutch 18 begins to slip. The speed of the sun gear 19 decreases until it disappears. In that case, the freewheel 16 restrains the sun gear and the tooth thrust Pac reappears to disengage the clutch so that the transmission operates as a reduction gear. Therefore, each time the operation of the reduction gear device changes to the operation of direct drive or vice versa,
The axial thrust Pac changes to stabilize the newly established transmission ratio. This is very advantageous on the one hand to avoid excessively frequent switching at a certain critical operating point and, on the other hand, to cause the sliding situation of the clutch 18 only transiently.

In the embodiment shown in FIGS. 3 and 4, the connecting device 17 comprises an element 17a which both has a region forming a radial plate with respect to the axis 12 according to the more schematic illustration of FIG. Mounted between and 17b.

The connecting device 17 comprises each flexible blade 37, each flexible blade 37 having a first end 37a rigidly connected to the first transmission member 17a by a rivet 41a and a second transmission 37b by a rivet 41b. It has a member 17b and a second end 37b firmly connected to it. Between the first and second transmission members 17a, 17b, each flexible blade 37 has a region 37c curved toward the second transmission member 17b in the vicinity of the first end portion 37a and a second end portion 37b. In the other direction in the vicinity, i.e.
1 has a region 37d that is curved toward the transmission member 17a. When the first transmission member 17a moves in the axial direction with respect to the second transmission member 17b, the curvatures of the regions 37c and 37d increase or decrease. As shown in FIG. 3, the blades 37 shown in FIG. 4 have several sets distributed around the axis 12.

Each flexible blade 37 is oriented somewhat tangentially to transmit drive torque due to tensile stress in the blade 37. The arrow 39 indicates the direction of drive torque. Also, as indicated by the dotted line, in order to transfer the negative torque (opposite direction 39) generated by the engine when the engine is operating in the braking mode by the tensile stress of each flexible blade 37, Each other blade 37e may be deployed starting from the transmission member 17b and oriented circumferentially in the other direction. Without such additional blades 37e, it is each blade 37 that transmits this torque by compressive stress.

The thickness, length, width and material of each blade 37 are selected to provide the following functions and results: -during the axial displacement of the first transmission member 17a with respect to the second transmission member 17b. Each blade 37 elastically bends without any practical resistance, and each blade 37 transfers the rotational torque of the engine 5 from the second transmission member 17b to the first transmission member 17b.
and each blade 37 provides sufficient centering of the first transmission member 17a about the axis 12.

To this end, each blade 37 is extremely thin to be extremely flexible,
Regardless of the thinness of the blade, it has a relatively wide width so as to have a transverse cross section sufficient to transmit torque, and has any axial position with respect to the first and second transmission members 17a, 17b. It is long enough to remain somewhat in the radial plane.

According to one embodiment, each blade 37 has, for example, a width of 0 mm to allow an axial travel of about 2 mm.
It can be made from spring steel with a thickness of 0.7 mm and a length of 3-4 cm. As shown, the blades are preferably laminated in at least one pair. A stack of two blades 37 has the same torque transmission function as a single blade of double thickness, but with greater flexibility.

In use, the crown gear 8 is the planetary gear 1 angularly distributed around the axis 12.
It has a tendency to center the crown gear 8 itself around 1. This centering effect is due to the tooth part repulsive force directed in the radial direction with respect to the shaft center 12, and the tooth part repulsive force generated between the tooth part of the crown gear 8 and the tooth part of each planetary gear 11. . Therefore, the connecting device 17 only partially provides the centering of the first transmission member 17a with respect to the second transmission member 17b.

If desired, complementary sliding centering means can be provided without impairing the good results of the invention, since this complementary centering hand device is still transmitted exclusively by the device 17. This is because the generated torque is arranged so as not to be transmitted.

In the embodiment shown in FIG. 5, blade 37 has a greater thickness at ends 37a and 37b than at flexible regions 37c and 37d.

In the embodiment shown in FIG. 6, the device 17 comprises a metal bellows 47, which for this purpose has a tip shaped like a shaft along the axis 12. Comprises a tubular tip 47a welded to the first transmission member 17a and a second tubular tip 47b welded to the second transmission member 17b which also terminates in the shape of a shaft end for this purpose. . The bellows 47 is compressible in the axial direction without such elastic resistance, while being able to transmit the rotational torque of the engine without excessive deformation in the torsional direction and the shaft end of the first transmission member 17a with respect to the axial center 12 of the shaft. Ensure proper centering of parts.

In the embodiment shown in the upper part of FIG. 7, the connecting device 17 comprises a disc 57 having an annular undulation about the axis 12. The annular disc 57 has an outer peripheral edge portion 57a welded to the first transmission member 17a and an inner peripheral edge portion 57b welded to the second transmission member 17b. According to the disk 57, the first transmission member 17a can move in the axial direction with respect to the second transmission member 17b by flexing without such elastic resistance, while the first transmission member 17a can move in the axial direction with respect to the second transmission member 17b around the axial center 12. 1 Appropriate centering of the transmission member 17a is ensured, and torque is transmitted from the transmission member 17b to the transmission member 17a without any practical deformation.

The variant shown on the lower side of FIG. 7 is different from the case shown in FIGS. 1 and 2 in that the first transmission member 17 a carries a group of outer teeth, for example carried by the shaft 59. 58
The case where the first transmission member 17a and the first transmission member 17a are integrally formed is distinguished from each other. Thus, one of the transmission members (17a in the illustrated embodiment) is provided with a rigid collar 61 connecting the shaft 59 to the welding region of the contoured disc 57 to the outer peripheral edge 57a.

In the variant shown in FIG. 8, the disc 57e is flat. In this variant, the axial displacement is very small, or the available radial dimensions allow the production of large-diameter discs, or the torque to be transmitted is again relatively small. If the disk can be made thinner than that of FIG. 7, it may be suitable.

In the embodiment shown in FIGS. 9 and 10, the connecting device 17 comprises spherical balls 67 arranged in four axial rows distributed around the axial center 12. Each row is arranged in a generally cylindrical channel, half of which is the first transmission member 1
It is formed by a groove 68a having a semicircular cross section which is a part of 7a, and the other half is formed by a groove 68b having a semicircular cross section which is a part of the second transmission member 17b. Grooves 68a and 68b are each ball 67
It has a slightly larger diameter. The groove 68a formed on the cylindrical bore of the first transmission member 17a opens in the radial direction toward the shaft center 12. The groove 68b formed on the male cylindrical surface of the second transmission member 17b opens in the radial direction away from the shaft center 12. First transmission member 17a
Between the cylindrical wall portion 69a of the bore and the male cylindrical wall portion 69b that is slidably arranged in the bore 69a and is a part of the second transmission member 17b. There is radial play 71. Each spherical ball 67 is mounted with substantially no radial play between the respective tracks 68a and 68b, thus ensuring centering of the first transmission member 17a with respect to the second transmission member 17b without friction. Due to the presence of at least two balls 67 in each row, the connecting device 17 also ensures a precise axial alignment of the first transmission member 17a with respect to the second transmission member 17b.

When the first transmission member 17a slides in the axial direction with respect to the second transmission member 17b, each ball 67 installed between the two raceways 68a and 68b rolls on the raceways 68a and 68b.

While the rotational torque according to arrow 39 is transmitted, one surface 72b of each groove 68b is attached to each ball 68b.
It abuts the side of 67 and presses each ball 67 against the facing surface 72a of each groove 68a. surface
72a and 72b are inclined with respect to the circumferential direction around the axis 12. Each ball 67 made of steel, for example of the type used for ball bearings, has a transmission member 17
The resistance of each ball 67 to the shear stress along the cylindrical interface between a and 17b and the compressive stress between the surfaces 72b and 72a of each groove causes a rotational torque from the transmission member 17b to the first transmission member 17a. introduce.

Since the axial travel of the transmission member 17a is limited for other reasons, there is no risk that the transmission member 17a will deviate beyond the end of the transmission member 17b. In contrast, 2 for each channel
There is a risk of each ball 67 deviating from the left end of FIG. 9 where the two grooves 68a and 68b are formed open. In order to prevent this, the elastic retaining ring 74 mounted in an appropriate groove of the first transmission member 17a has an axial stop portion for the ball 67 placed closest to this end of each channel 68. Play a role of. At the other end of the illustrated embodiment, that is, at the right end, each groove 68b that is a part of the second transmission member 17b is closed and formed at 75.

In the embodiment shown in FIGS. 11 and 12, the connecting device 17 comprises each tubular needle 77, the axis 77 a of the tubular needle 77 being radial with respect to the axis 12. Each needle 77 is distributed within four channels 78 having a rectangular cross section parallel to the axis 12 in four rows equiangularly spaced about the axis 12. Each channel has a first transmission member 1
It is defined in cooperation by the inner diameter surface 69a of 7a and the outer diameter surface 69b of the second transmission member 17b.

Each channel 78 is defined by two concave biplanar structures 78a, 78b, one of which is part of the first transmission member 17a and the other of which is part of the second transmission member 17b. is there. Each biplanar structure has a flat running track 82a, 82b and end thrust surface for each needle 77.
Equipped with 83a and 83b. Since the running tracks 82a and 82b are parallel to the radius passing through the axis of each needle 77, they are orthogonal to the circumferential direction around the axis 12. End thrust surface 83a
And 83b are oriented tangentially with respect to the axis 12. In each running track 82a of the first transmission member 17a, the needles 77 of the two channels 78 that are diametrically opposed to each other transmit the rotational torque in one direction, and the needles 77 of the other two channels rotate in the other direction. Is transmitted in the clockwise and counterclockwise directions about the axis 12 alternately. As each needle transmits torque, each needle is compressed and stressed between the two opposing tracks 82a and 82b of its respective channel 78. Figure 1
4 shows that each needle 77 of the same channel can be mounted in a cage 84, but in cage 84 each needle can rotate about itself. First and second
As the transmission members 17a and 17b move axially with respect to each other, the cage 84 moves within its respective channel 78 at the intermediate speed of the two members 17a and 17b.

In the embodiments of FIGS. 15 to 18, only the parts different from the above-mentioned embodiments will be described. When the first transmission member 17a performs the entire axial sliding with respect to the second transmission member 17b, the needles 77 in each row have a radius R (sufficient to pivot the roller 87 by about 15 ° to 20 °. 18) with a single roller 87. Therefore, the roller need not have a perfect cylindrical surface, but only have two radially opposed cylindrical rolling arcs 87a and 87b separated by two opposed parallel flats 87c. There is. In the use state shown in FIG. 15, the two flat portions 87c are laterally oriented with respect to the axis 12. Therefore, the axial dimension of the connecting device 17 according to this embodiment is particularly short. The distance between the opposing tracks 82a and 82b in each channel 78 is equal to 2R and is therefore significantly larger than the embodiment of FIGS. 11-14.

In such an embodiment, it is necessary to ensure that each roller 87 rolls on each track rather than sliding on each track. To do this, each rolling surface 87a or 87b has a mating pattern 89a or 89b near the middle of one of the curved edges of the surface 87a or 87b.
Carry. In the illustrated embodiment, each of the meshing patterns 89a or 89b is a meshing tooth portion shaped like a circular involute. Tooth 89a in use
Alternatively, 89b is engaged with a complementary meshing pattern (hollow teeth) 91a or 91b formed in the corresponding track 82a or 82b. Two teeth 89a and 89b of the same roller 87
The pitch circle C _P (FIG. 18) of ∘ corresponds to the circumference of the rolling surface 87a or 87b.

Therefore, as shown in FIG. 17, each of the cylindrical ends of the roller has a cross-hatched area for rolling contact with the corresponding track 82a or 82b and an area not cross-hatched in parallel with the area. In the center of the latter region, there is a hollow tooth 91a or 9 for angularly indexing the roller with respect to the two transmission members 17a, 17b.
The tooth portion that meshes with 1b is arranged. The diameter of the pitch circle C _P and the geometry of the teeth are related to the expected axial travel between the two transmission members 17a and 17b and the relative axial direction between the two members 17a and 17b. Throughout the entire stroke, the teeth 89a and 89b are selected to remain in mesh with the corresponding hollow teeth 91a and 91b.

The embodiment shown in FIG. 19 is in the form of a crown in which the second transmission member 17b is radially inside and the first transmission member 17a firmly carries the tooth 8 of FIG. Only the points are different from the embodiment of FIG.

The embodiment of FIG. 20 has two differences with respect to the embodiment of FIG. 16, which can be used independently of one another: two large diameter rollers 87d and two other small diameter rollers 87e. And alternate. The large-diameter roller 87d is a roller under stress for transmitting driving torque, and the other two rollers 87e are rollers to which stress is applied during transmission of braking mode torque smaller than driving torque. The rollers are eccentric with respect to each diameter D intersecting the axis 12, one of the two rollers being eccentric in one circumferential direction and the other two rollers being eccentric in another circumferential direction. . Therefore, the rollers are grouped into two groups instead of being regularly distributed around the axis 12. As a result, the inner transmission member (17a in this embodiment) becomes even more compact, and thus has a more reliable shape than the shape resulting from the embodiment of FIG.

In the embodiment of FIG. 20, indexing teeth for each roller are not shown, but such teeth may be provided.

FIGS. 21 and 22 show improvements that can be applied to the embodiment of FIGS. 15-20 to ensure the stability of the connection prior to assembly of the transmission.

From FIG. 15, in particular, the indexing teeth ensure the stability of the connection only if the first transmission member 17a is prevented from moving too far to the left in the drawing. Be understood to do. In the embodiment of FIG. 19, it is also necessary to prevent the transmission member 17a from moving too far to the right and distally. Such excessive movement is prevented, at least in the embodiments of FIGS. 1 and 2, by the rest of the transmission. However, there is a risk that it will occur prior to assembly. In order to prevent this, a spring wire holding device 92 is provided, but the spring wire holding device 92 has a radially inner transmission member.
A central compartment 93 fixed to (17b in this example) and two retaining tabs 94 arranged on each side of the central compartment 93, more specifically to the flat part 87c of each roller. Two retaining tabs 94 that abut in a groove 96 formed for this purpose on the flat. The central section 93 penetrates a milling 97 that vertically cuts the second transmission member 17b, and forms a hook-shaped loop 98 on the other side of the member 17b. Central compartment 93 and each wing 94
In between, the spring wire passes below the positioning hook 99 formed on the corresponding front surface of the transmission member 17b.

According to this device, when the first transmission member 17a moves in the axial direction in the direction in which each roller 87 is moved to the side where each holding tab 94 is arranged, each holding tab 94 first moves. It is elastically deformed and finally prevents further movement of the roller. When the roller is indexed by the teeth 89a and 89b with respect to the two transmission members 17a and 17b, the roller is fixed so that a further relative axial direction between the two transmission members 17a and 17b is obtained. Movement is prevented.

FIG. 21 is also positioned on the other surface of the transmission member 17b so as to limit relative axial movement in movement in the other direction by abutting against the other side of each roller. It is also shown that other contemplated retention devices may be installed within the same milling 97.

Theoretically, it would be sufficient to constrain a single roller to constrain the two transmission members axially with respect to each other. Each holding device shown constrains two rollers for movement in one direction. This constraint can be further reinforced by mounting one or two holding devices on the other two rollers of the connecting device.

In the embodiment of FIGS. 23 and 24, where rollers such as 87 have been omitted to simplify the display, the retention device consists of a U-shaped spring wire 102. U above
The shaped central compartment 103 is held by a hook 109 on the front surface of one of the transmission members (17b). The two U-shaped ends 94 form elastic axial thrust stop tabs on the other corresponding front face (17a) of the transmission unit. There can be two radially opposite holding devices (only one shown) and possibly two other holding devices (not shown) on the front side of the other of the members 17a and 17b.

Of course, the invention is not limited to the embodiments described and illustrated. In particular, the application of the invention is not limited to the transmission described with reference to FIGS. For example, the first transmission member may be integral with the sun gear 9 of the planetary gear train. In addition, the number of rows of blades, rollers, balls or needles is
It may differ from that shown in various embodiments.

[Brief description of drawings]

FIG. 1 is a schematic longitudinal cross-sectional cutaway view of a power drive unit in an idle state, which includes an engine and a two-stage transmission ratio transmission according to the present invention.

[Fig. 2]   FIG. 2 is a view similar to FIG. 1 regarding the deceleration operation.

FIG. 3 is a schematic partial cross-sectional view of the transmission of FIGS. 1 and 2.
4 shows a deformable connecting means in an embodiment.

[Figure 4]   FIG. 4 is a view substantially taken along line IV-IV of FIG.

[Figure 5]   FIG. 5 is a vertical sectional view of a modified embodiment of each blade.

[Figure 6]   FIG. 6 is a partial vertical sectional view of a second embodiment of the connecting means.

FIG. 7 is a diagram showing two modified embodiments of the third embodiment of the connecting means in two cross sections.

[Figure 8]   FIG. 8 is a partial vertical sectional view showing a fourth embodiment of the connecting means.

[Figure 9]   FIG. 9 is a vertical sectional view showing another embodiment of the connecting means.

[Figure 10]   FIG. 10 is a sectional view of the embodiment of FIG.

FIG. 11   FIG. 11 is a vertical sectional view showing another embodiment of the connecting means.

[Fig. 12]   FIG. 12 is a sectional view of the embodiment of FIG.

[Fig. 13]   FIG. 13 is a sectional view taken along line XIII-XIII in FIG.

FIG. 14   FIG. 14 is a perspective view of the roller / needle holding cage.

FIG. 15   FIG. 15 is a vertical sectional view showing another embodiment of the connecting means.

FIG. 16   16 is a sectional view of the embodiment of FIG.

FIG. 17 is a perspective view of the truncated roller of the embodiment shown in FIGS. 15 and 16.

FIG. 18   FIG. 18 is a plan view of the roller shown in FIG.

FIG. 19   FIG. 19 is a vertical cross-sectional view of a modified example of the embodiment shown in FIG.

FIG. 20   FIG. 20 is a sectional view of a modification of the arrangement shown in FIG.

FIG. 21   FIG. 21 is a partial side view showing the roller holding means.

FIG. 22   22 is a sectional view taken along line XXII-XXII in FIG.

FIG. 23   FIG. 23 is a partial front view showing another embodiment of the holding means.

FIG. 24   FIG. 24 is a partial perspective view showing the holding means of FIG.

[Procedure amendment]

[Submission Date] March 12, 2002 (2002.3.12)

[Procedure Amendment 1]

[Document name to be amended] Statement

[Name of item to be amended] Claims

[Correction method] Change

[Contents of correction]

[Claims]

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0006

[Correction method] Change

[Contents of correction]

That is, if the spline is formed along the circumference of a small diameter, the guiding in sliding is correct and the pressure between the side portions of the spline does not exceed a predetermined limit value.
It is necessary to give each spline a long axial length. These problems can be overcome to some degree by forming splines on the circumference of a large diameter, but the weight and radial dimensions of the connection can be prohibitive. Further, since the induction deteriorates with time when each spline starts to wear and play, the characteristics of the transmission ratio change caused by the sliding movement of the spline deteriorates due to the time change of the transmission. Automatic transmission described in French Patent Publication No. 2768210 (FR-A-2 768 210)
In the above, the spline allows the predetermined member to move in the axial direction, and engages and disengages the clutch . The movement of the movable member is the result of applying a plurality of axial forces . In such arrangement, some faulty lever to the operation of the spline, the effect of addition of axially force is inhibited.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0008

[Correction method] Change

[Contents of correction]

According to the present invention, each torque transmission member having a rotation input shaft and a rotation output shaft, and a selective coupling means mounted between two of the torque transmission members, A tooth row meshingly connected to at least some of the torque transmitting members, the input member and the output depending on whether the selective connecting means is in a connected state or a released state. A transmission, especially for a land vehicle, comprising a tooth row which forms two transmission ratios between the members, wherein the first transmission member of the transmission members is the state of the selective coupling means. Is mounted so as to be controlled by axial displacement, and rotation is connected between the first transmission member and the second transmission member of each transmission member to allow relative axial displacement. The transmission, in particular for land vehicles, equipped with means is Continued means have at least one of the elements, at least one of the elements is in the non-sliding relationship with respect to said first transmission member and said second transmission member, the first transfer to the second transmission member It is characterized by having at least one of mobility and deformability so that the element can absorb the axial displacement of the member.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0009

[Correction method] Change

[Contents of correction]

[0009] According to a first aspect, the at least one connection means is at least one of the deformable elements having a parallel variable dimension and the axis.

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0011

[Correction method] Change

[Contents of correction]

According to the second aspect, the at least one connecting means is of the rolling type.

[Procedure correction 6]

[Document name to be corrected] Drawing

[Name of item to be corrected] Figure 1

[Correction method] Change

[Contents of correction]

[Figure 1]

─────────────────────────────────────────────────── ─── Continued front page    (81) Designated countries EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, I T, LU, MC, NL, PT, SE), OA (BF, BJ , CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, GM, K E, LS, MW, MZ, SD, SL, SZ, TZ, UG , ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AG, AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, BZ, C A, CH, CN, CR, CU, CZ, DE, DK, DM , DZ, EE, ES, FI, GB, GD, GE, GH, GM, HR, HU, ID, IL, IN, IS, JP, K E, KG, KP, KR, KZ, LC, LK, LR, LS , LT, LU, LV, MA, MD, MG, MK, MN, MW, MX, MZ, NO, NZ, PL, PT, RO, R U, SD, SE, SG, SI, SK, SL, TJ, TM , TR, TT, TZ, UA, UG, US, UZ, VN, YU, ZA, ZW [Continued summary] It is useful in strengthening the smooth engagement for further replacement.

Claims (29)

[Claims] 1. A torque transmission member equipped with a rotation input shaft (2a) and a rotation output shaft (2b), respectively, and a selection mounted between two of the torque transmission members (17a, 13). A connecting means (18) and a tooth row (7) meshingly connected to at least some of the torque transmitting members, and whether the selective connecting means (18) is in a connected state. Depending on whether it is in the released state, the tooth row (7 that forms two transmission ratios between the input member and the output member).
And a first transmission member (17a) of the transmission members controls the state of the selective coupling means (18) by axial displacement. Means for connecting relative rotation between the first transmission member (17a) and the second transmission member (17b) of each transmission member, which enables relative axial displacement. (17) is installed, particularly in a land vehicle transmission, the connecting means (17) is essential for axial displacement of the first transmission member (17a) with respect to the second transmission member (17b). A transmission which is characterized by being frictionless. 2. Device according to claim 1, characterized in that the connecting means comprises at least one deformable element (37, 47, 57) having a variable dimension parallel to the axis (12). . 3. The deformable element is a bellows (47),
The device according to claim 2. 4. Device according to claim 2, characterized in that the deformable element is a thin disc (57, 57e). 5. Device according to claim 4, characterized in that the disc (57) has at least one annular undulation centered on the axis (12). 6. The at least one deformable element is at least one flexible blade (37) having a thickness arranged in the axial direction, the first transmission member (17).
The first end (37a) fixed to (a) and the second end (37b) fixed to the second transmission member (17b)
Device according to claim 2, characterized in that it comprises at least one flexible blade (37) having 7. The at least one deformable element is at least two flexible blades (37) having a thickness arranged in the axial direction, each of which is the first transmission member (17a). The first end (37a) fixed to the second end fixed to the second transmission member (17b)
Device according to claim 2, characterized in that it comprises at least two flexible blades (37) grouped into at least one stack having an end (37b). 8. The at least one deformable element (37, 47, 57), once attached, rotates between the first torque transmitting member (17a) and the second torque transmitting member (17b). 8. Device according to any one of claims 2 to 7, characterized in that it is substantially torsionally rigid about the axis (12) so as to be able to transmit torque. 9. The relative direction of rotation of said at least one deformable element (37e), at least when mounted, between said first transmission member (17a) and said second transmission member (17b). Device according to claim 8, characterized in that it is more rigid with respect to the other direction. 10. The centering of the at least one deformable element (37, 37e, 47, 57) with respect to the axis (12) between the first transmission member (17a) and the second transmission member (17b). Device according to any one of claims 2-9, characterized in that it is mounted to at least partially secure. 11. Device according to claim 1, characterized in that the connection means (17) are of the rolling type. 12. The first connecting member is a part of the first transmitting member (17a).
Tracks (67a, 78a, 82a) and a second track (68b, 78b, 8) that is a part of the second transmission member (17b).
Device according to claim 11, characterized in that it comprises an element (67, 77, 87, 87d, 87e) mounted for rolling between it and 2b). 13. Each of the orbits has a facing surface (72a, 72a,
72b, 82a, 82b). 14. The facing surfaces (82a, 82b) are flat and the elements (77, 8) are flat.
Device according to claim 13, characterized in that 7, 87d, 87e) are cylindrical. 15. The element according to claim 12, wherein the element (67) has a convex running surface and the track is a groove (68a, 68b) having a corresponding curved cross section.
The apparatus according to item 3. 16. Device according to claim 15, characterized in that the tracks (68a, 68b) are radially open. 17. The track (82a, 82b) is oriented along a direction forming an angle with respect to a tangent when viewed in a transverse cross section.
The apparatus according to claim 1. 18. The first transmission member (17a) and the second transmission member (17b) each generate a rotational torque in both rotation directions between the first transmission member (17a) and the second transmission member (17b). 18. Device according to claim 17, characterized in that it carries at least two tracks (82a, 82b) oriented in opposite directions for transmission. 19. Each of said elements (87, 87d, 87e) is sufficient to carry out only a part of the rotation when said first and second transmission members have traveled in their full axial travel relative to each other. A device according to any one of claims 11 to 18, characterized in that it has a long radius (R) and that each element is cut by two opposing flats (87c). . 20. The rolling element comprises a meshing pattern (tooth 89a, 98b) having a pitch circle (C _P ) coinciding with the running surface (87a or 87b), and the corresponding track is a complementary meshing pattern. Device according to claim 19, characterized in that it has (recesses 91a, 91b). 21. Engaging means (89a, 89b) between at least some of the rolling elements (87) and at least one of the two raceways (82a, 82b) with which they are interposed.
Device according to any one of claims 11 to 19, characterized by: 91a, 91b). 22. The engagement means (89a, 89b; 91a, 91b) occupy only part of the width of the track (82a, 82b) and the corresponding dimensions of the rolling element (87). Device according to claim 20 or 21. 23. At least two rolling elements between two tracks (68a, 68b; 82a, 82b), each of which is part of one of said first and second transmission members (17a, 17b). Element (67
, 77) is present. 24. The at least two rolling elements (77) comprise the two raceways (82a).
Device according to claim 23, characterized in that it is held in a translatable cage (84) with respect to each of the two (82, 82b). 25. Holding means (74; 92) carried by one of the first and second transmission members, the holding means (74; 92) preventing the rolling elements (67; 87) from deviating from the respective tracks. Device according to any one of claims 11 to 24, characterized by means (74; 92). 26. Holding means (74; 92) carried by one of said first and second transmission members, said holding means (74; 92) preventing said transmission members from deviating from one another before assembly. Device according to any of claims 11 to 24, characterized by: 92). 27. The first transmission member (17a) is axially constrained with respect to a spiral tooth portion (8) forming a part of the tooth row (7). Items 1-26
The apparatus according to claim 1. 28. Device according to claim 27, characterized in that the spiral tooth (8) is rigidly integral with the first transmission member (17a). 29. The first transmission member (17a), through the axial thrust bearing (B2),
The spiral tooth portion (8) is in contact with the movable plate (27) of the selective connection means (18).
29. A device according to claim 27 or 28, characterized in that the axial reaction of said acts on said movable plate (27) in the opposite direction of the activation force.