FR3096421A1 - Transmission box and self-propelled rolling machine equipped with such a box - Google Patents

Abstract

Transmission housing (1) positionable between the primary motor shaft and the wheels of a rolling machine, said housing (1) at least partially housing an output shaft (2) formed of two sections (2A, 2B) of shaft, two progressive friction clutch mechanisms (3A, 3B), and a clutch control device (4A, 4B), each clutch mechanism (3A, 3B) comprising an integral driven element (5A, 5B) in rotation of the section (2A, 2B) of the shaft which carries it and a rotating element (6A, 6B). The housing (1) at least partially accommodates a mechanism (7) for reversing the direction of rotation of the output shaft (2) comprising a control member for driving the output shaft (2) forward. , a drive control member (9) in reverse of the output shaft (2), and mounted on said output shaft (2), two counter-rotating driving members (10, 11) and a sliding gear (13) reverser mounted integral in rotation with the elements (6A, 6B) driving the clutch mechanisms (3A, 3B) and configured to engage with one or the other of the counter-rotating members (10, 11). Figure for the abstract: Fig. 7

Description

Description Title of the invention: Transmission box and rolling self-propelled machine equipped with such a box

The invention relates to a positionable transmission housing between the primary motor shaft and the wheels of a rolling machine, as well as a rolling self-propelled machine equipped with such a transmission housing.

[0002] It relates, in particular, to a positionable transmission casing between the primary motor shaft and the wheels of a rolling machine, said casing comprising, housed at least partially inside said casing, a so-called output shaft wheel drive formed of at least two coaxial shaft sections mounted free to rotate relative to each other, two progressive friction clutch mechanisms carried one by one of the shaft sections , the other, via the other of the shaft sections, a clutch control device, each clutch mechanism comprising a so-called driven element integral in rotation with the shaft section which carries it and a so-called driving element rotary, said driving and driven elements being configured to pass from a disengaged state in which they are spaced apart from each other to an engaged state in which they are engaged with each other under the action of the clutch control device.

A transmission box of the type described above allows a transmission differential function.

Indeed, the coaxial shaft sections are capable of being driven at different speeds, even in the engaged state of the clutch mechanisms, when the driven and driving elements of each clutch mechanism are engaged, i.e. that is to say in bearing contact by friction, which allows the driving of each wheel of the machine at a different speed, in particular when cornering.

Furthermore, such a transmission unit is increasingly fitted to machines equipped with a forward rotation drive control and a reverse rotation drive control for the output shaft of the wheels of the gear.

The easy solution then consists in providing two independent transmission boxes, each mounted on an axle of wheels to allow one, the forward drive of the machine, the other, the reverse drive of the machine. gear.

This solution is bulky and limits the tractive effort.

An object of the invention is to provide a transmission housing of the aforementioned type whose design allows a simple and space-saving way forward and reverse drive of the output shaft of the housing.

[0005] To this end, the subject of the invention is a transmission casing that can be positioned between the driving primary shaft and the wheels of a rolling machine, said casing delimited by walls comprising, housed at least partially inside said casing, a so-called wheel drive output shaft 2 formed of at least two coaxial shaft sections, mounted free in rotation with respect to each other, two progressive friction clutch mechanisms carried one , by one of the shaft sections, the other, by the other of the shaft sections, and a clutch control device, each clutch mechanism comprising a so-called driven element integral in rotation with the section shaft which carries it and a so-called rotary driving element, said driving and driven elements being configured to pass from a disengaged state in which they are separated from each other to a engaged state in which they are engaged with each other under the action of the clutch control device, characterized in that the housing further comprises, housed at least partially inside said housing, a mechanism for reversing the direction of rotation of the output shaft for forward or reverse drive of said output shaft, this direction inversion mechanism comprising a control member for driving the output shaft forward, a control member for reverse drive of the output shaft, and mounted on said output shaft, two so-called driving contra-rotating members and a reversing slider, said reversing slider being configured to come into engagement with one of the counter-rotating members in the actuated state of the output shaft forward drive control member, and with the other of the contra-rotating members in the actuated state of the output shaft reverse drive control member , and the reversing slider being mounted integral in rotation with the driving elements of the clutch mechanisms to allow the engaging state of the reversing sliding gear with any one of the counter-rotating members and in the engaged state of the clutch mechanisms, the transmission of the rotational movement of the reversing slider via the clutch mechanisms to each of the shaft sections, independently of the direction of rotation of said reversing slider.

[0006] The output shaft thus carries the driving and driven elements of the clutch mechanisms, the reversing slider and the counter-rotating members of the direction reversing mechanism.

This results in compactness and simplicity of construction.

The housing thus acts as a reduction gear, a differential, and a rotational drive direction inverter for the output shaft.

Friction clutch mechanisms allow shaft sections to be driven at different speeds, even in the engaged state when the driving and driven elements are in frictional bearing contact engagement.

These clutch mechanisms are also configured to be active, that is to say to present a clutched state, both in forward gear, that is to say in the engaged state of the reversing sliding gear with one of the counter-rotating members, and in reverse, that is to say in the state in which the reversing player engages with the other of the counter-rotating members.

Each clutch mechanism is therefore configured to transmit, to the shaft section which carries it, the rotational movement of the reversing sliding gear 3 independently of the direction of rotation of the reversing sliding gear.

Each clutch mechanism is therefore configured to transmit the rotational movement of one of the counter-rotating members and the rotational movement of the other of the counter-rotating members to the shaft section which carries said clutch mechanism according to the counter-rotating member engaged with the reversing sliding gear.

One and the same clutch mechanism therefore allows, per shaft section, a transmission to said shaft section, of a driving movement in forward rotation, and of a driving movement in reverse. , depending on the rotational drive direction desired for said shaft section.

Each clutch mechanism is therefore active in forward and reverse.

This results in a simplicity of said housing.

[0007] According to one embodiment of the invention, the forward drive control member, or respectively the reverse drive control member, of the output shaft is configured to form, in addition to the control member for the engagement of the reversing slider with one of the counter-rotating members, at least part of the clutch control device of the clutch mechanisms.

Again, this results in simplicity of the transmission housing.

The use of the direction inversion control to control the clutch makes it possible to control in a safe manner, according to a predetermined order, the direction inversion control and the clutch, the direction inversion control operating before the clutch to avoid jerks.

According to one embodiment of the invention, the reversing slider is arranged on the output shaft between the driving elements of the clutch mechanisms.

This design allows versatility of the clutch mechanisms, that is to say their use in both forward and reverse.

According to one embodiment of the invention, the counter-rotating driving members are arranged on the output shaft between the driving elements of the clutch mechanisms.

The reversing slider is mounted axially on the output shaft.

The driving counter-rotating elements are preferably immobilized in axial movement or limited in axial movement on the output shaft to facilitate the reversing sliding gear coming into engagement with one or the other of the counter-rotating members.

According to one embodiment of the invention, the reversing slider, the counter-rotating driving members and the driving elements of the clutch mechanisms are arranged on the output shaft between the driven elements of the clutch mechanisms.

Again, this design allows versatility of the clutch mechanisms, that is to say their use both in forward and reverse.

[0011] According to one embodiment of the invention, the reversing slider, the contra-rotating driving members, the driving elements and the driven elements of the clutch mechanisms are arranged on the output shaft between at least a part of the forward drive controller and part of the output shaft reverse drive controller.

[0012] According to one embodiment of the invention, the counter-rotating members each take the form of a wheel or a rotating pinion provided with a central recess for free rotational mounting on the output shaft and each counter-rotating member is, at its central recess, crossed right through by the reversing player.

[0013] Thus, the reversing slider, movably mounted axially on the output shaft, is, over at least part of its axial displacement stroke, mounted independent in axial displacement of the counter-rotating members.

This reversing slider, mounted axially on the output shaft in the actuated state of the drive control member in forward gear or of the drive control member in reverse gear of the output shaft, is configured to, by axial movement along said output shaft, engage one of the counter-rotating members in the actuated state of the output shaft forward drive control member, and with the other of the counter-rotating members, in the actuated state of the reverse drive control member of the output shaft.

This reversing slider can thus be moved axially on the output shaft without axial movement of the counter-rotating members.

According to one embodiment of the invention, the reversing slider takes the form of a sleeve, coaxial with the output shaft, and mounted on said axially movable output shaft and free to rotate.

The counter-rotating members can thus be mounted on said sleeve and surround the sleeve.

[0015] According to one embodiment of the invention, the mechanism for reversing the direction of rotation of the output shaft is a clutch mechanism and the reversing slider which forms a mobile clutch of the clutch mechanism and which affects the form of a sleeve is provided at each of the ends of the sleeve with dog teeth, the dog teeth formed at one of the ends of the sleeve being configured to cooperate with dog teeth arranged opposite on one of the counter-rotating members driving elements, in the actuated state of the forward drive control member of the output shaft, and the dog teeth provided at the other of the ends of the sleeve being configured to cooperate with dog teeth disposed facing each other of the counter-rotating members leading to the actuated state of the drive control member in reverse gear of the output shaft.

[0016] Generally, the sleeve is provided at each of its ends with dog teeth provided on a collar of said sleeve.

These dog teeth are, on each collar, arranged on the face of the collar facing the other collar.

Thus, the dog teeth formed at one of the ends of the sleeve on one of the collars are configured to cooperate, that is to say come into engagement, with dog teeth arranged opposite on one of the contra-rotating driving members, in the actuated state of the forward drive control member of the output shaft, and the dog teeth provided at the other end of the sleeve on the other of the flanges are configured to cooperate, that is to say, come into engagement with dog teeth disposed opposite each other of the counter-rotating members leading to the actuated state of the drive control member in reverse gear of the output shaft.

This coming into engagement takes place each time by axial displacement of the reversing slider along the output shaft in the direction of one of the ends of the output shaft in the actuated state of the control member of forward drive of the output shaft and towards the other of the ends of the output shaft in the actuated state of the reverse drive control member of the output shaft.

According to one embodiment of the invention, each clutch mechanism is a cone clutch mechanism.

[0018] According to one embodiment of the invention, the reversing slider and the driving and driven elements of the clutch mechanisms in coaxial arrangement on the output shaft form a stack on said shaft and the drive control member. forward drive of the output shaft, or respectively, the reverse drive control member of the output shaft, is a member, such as a fork, movable at an angle, this member being configured to exert, during its angular displacement in the direction of said stack, an axial compressive force of the stack formed of the reversing slider and the driving and driven elements of the clutch mechanisms in coaxial arrangement on the output shaft.

At least two of the walls of the casing arranged facing each other form one, an axial stop abutment of the stack, in the state subjected to said stack to an axial compressive force resulting from the angular displacement in the direction of said stack of the drive control member in forward operation of the output shaft, the other, an axial stop of the stack, in the state subjected to said stack to a compressive force axial resulting from the angular displacement in the direction of said stack of the reverse drive control member of the output shaft.

[0019] According to one embodiment of the invention, the casing comprises, for the rotational drive of the counter-rotating driving members of the direction reversal mechanism, a rotational drive system housed at least partially inside the casing. .

According to one embodiment of the invention, the counter-rotating driving members of the direction reversing mechanism each take the form of a toothed wheel mounted freely to rotate on the output shaft.

It should be noted that by contra-rotating members is meant rotating members which rotate in opposite directions of rotation.

[0021] Another object of the invention is a rolling self-propelled machine, in particular a walk-behind machine, such as a lawn mower, said machine comprising a primary motor shaft 6 and a positionable transmission housing between the primary motor shaft and the wheels of said machine, characterized in that the transmission box conforms to that described above.

The invention will be better understood on reading the following description of exemplary embodiments, with reference to the appended drawings in which: Brief description of the drawings

[0022] [fie.11 represents a perspective view of a rolling machine equipped with a transmission box according to the invention,

[0023] [fie.21 shows a perspective view of a transmission housing according to the invention in the actuated state of the drive control member in forward operation of the output shaft, [0024J [ fig.3] shows a view of the inside of the case taken from the counter-rotating component side, the case having been omitted,

[0025] [fig.4] shows a view of the inside of the housing taken from the device side for driving the counter-rotating members in rotation, the housing having been omitted,

[0026] [fig.51 represents a front view of the inside of the case, the case having been omitted,

[0027] [fig.6] shows a view of the inside of the housing in the exploded position of the elements, the housing having been omitted,

[0028] [fig.7] shows a sectional view of the housing, in the neutral position of the direction reversal mechanism, that is to say in the non-actuated state of the forward drive control members and reverse drive of the output shaft,

[0029] [fig.8] shows a sectional view of the housing, in the forward position of the reversing mechanism, that is to say in the actuated state of the drive control member in forward motion of the output shaft for the forward rotational drive of the output shaft,

[0030] [fig.9] shows a sectional view of the housing, in the reverse position of the reversing mechanism, that is to say in the actuated state of the drive control member in reverse gear of the output shaft for reverse drive of the output shaft,

[0031] [fig.10] shows an exploded view of the reversing slider, the counter-rotating members and the driving and driven elements of the clutch mechanisms,

[0032] [fig.11] shows a perspective view of a counter-rotating member being interconnected with a reversing player,

[0033] [fig.12] shows a perspective view of an inverter walkman.

As mentioned above, the transmission housing 1 object of the invention is more particularly intended to apply to rolling machines 30 including 7 walk-behind.

These gears are generally called push gears.

The driver acts in this case on a driving member of the machine, such as a handlebar.

Figure 1 shows the application of such a transmission box to a lawnmower.

This lawnmower has a rolling frame, the rear wheels of this frame being shown at 33 in Figure 1.

[0036] A motor equips the machine.

The motor output shaft 31, also called the primary motor shaft 31, carries, on the one hand, a cutting blade, and, on the other hand, a drive pulley connected via a belt to a driven pulley.

This driven pulley is itself mounted on an input shaft intended to be housed at least partially in the housing 1 of the transmission.

This input shaft is here formed by an endless screw shown in Figure 3.

This input shaft is coupled by meshing to a second input shaft also formed by a worm.

Thanks to this connection by meshing, the input shafts fitted to the transmission housing 1 are input shafts driven in rotation, one in a direction called forward, the other in an opposite direction called reverse.

These input shafts form, with the belt transmission 32 arranged between one of the input shafts of the housing and the motor shaft 31, the system 15 for driving in rotation the counter-rotating members 10, 11 which will be described below, these counter-rotating members 10, 11 being said to be driving because of their rotational drive by the rotational drive motor system 15 .

The transmission housing 1, fitted with these input shafts, is positioned between the primary motor shaft 31 and the wheels 33 of the rolling machine 30.

This transmission box 1 is delimited by walls shown at 21 in the figures.

In the examples shown, this housing 1 is formed of two shells assembled by a joint plane and connected to each other by screwing and / or gluing.

This transmission housing 1, generally made of synthetic material, comprises, partially housed inside the housing 1, an output shaft 2 which projects from the housing at each of its ends.

This output shaft 2 is, at each of its ends, coupled directly or indirectly in particular via a reduction gear to the wheels of the machine.

This shaft 2 therefore forms the output shaft 2 for driving the wheels of the machine.

This output shaft 2 is formed of two coaxial shaft sections 2A, 2B, mounted free to rotate one pai- relative to the other.

These shaft sections 2A, 2B each have a blind central bore and are fitted onto a connecting rod or pin 2C for free mounting in rotation with respect to each other.

This rod 2C is visible in Figure 7.

Thus, the two free shaft sections in rotation with respect to each other are kept aligned by means of the connecting axis 2C.

The transmission housing 1 further houses two progressive friction clutch mechanisms 3A, 3B carried, one, by one of the shaft sections, namely the shaft section 8 2A for the mechanism 3A clutch, the other, by the other of the shaft sections, namely the shaft section 2B for the clutch mechanism 3B.

The transmission housing 1 also houses a clutch control device shown at 4A and 4B in the figures.

Each clutch mechanism 3A or 3B comprises an element SA or 5B called driven, integral in rotation with the shaft section 2A or 2B which carries it and an element 6A or 6B called driving, rotating.

The driving elements 6A and driven 5A of the clutch mechanism 3A, as well as the driving elements 6B and driven 5B of the clutch mechanism 3B are configured to pass from a disengaged state, in which they are separated from one another. 'other, in a clutched state, in which they are in engagement with each other, by bearing contact by friction with variable clamping, under the action of the device 4A or 4B clutch control.

In the engaged position corresponding to the engaged state, the driving and driven elements of a clutch mechanism are in variable-tightening bearing contact.

In the examples shown, the progressive friction clutch mechanisms 3A and 3B are clutch mechanisms with cones 19, 20.

They could have been replaced by a disc clutch mechanism in particular.

The clutch mechanism 3A is carried by the shaft section 2A and the clutch mechanism 3B is carried by the shaft section 2B.

These clutch mechanisms 3A and 3B are similar and have, for their similar part, the same references with the letter A for the parts belonging to the clutch mechanism 3A and the letter B for the parts belonging to the clutch mechanism. 3B clutch.

Each clutch mechanism 3A or 3B therefore comprises a driven element SA or SB formed by a so-called male cone 19, centrally recessed to be able to be threaded onto the section 2A or 2B of the shaft which carries it.

This driven element, represented in SA for the clutch mechanism 3A and in SB for the clutch mechanism 3B is mounted integral in rotation with the section 2A or 2B which carries it, by a pin.

Alternatively, the central recess of each male cone 19 forming the driven element 5A or 5B could have been provided with splines capable of cooperating with the splines of the shaft section which carries the cone 19, for an integral assembly in rotation .

The driving element shown at 6A for the clutch mechanism 3A and at GB for the clutch mechanism 3B has meanwhile a conical bearing surface fitted internally to a crown to form a cone 20 called female.

The conical bearing of the female cone 20 cooperates by bearing contact controlled with the conical outer peripheral surface of the male cone 19 constituting the driven element in the engaged state of the clutch mechanism, that is to say at the close state of the driving and driven elements.

In the examples shown, the driving element 6A of the clutch mechanism 3A 9 or 6B of the clutch mechanism 3B therefore has the shape of a ring mounted freely to rotate on the shaft section which carries it.

This crown is internally provided with the conical bearing surface which partially overlaps the outer peripheral surface of the male cone 19 in the engaged state of the clutch mechanism.

This crown with its conical seat therefore forms the female cone 20 of the clutch mechanism 3A or 3B.

The transmission housing 1 further comprises, housed at least partially inside the housing, a direction reversal mechanism 7 to allow the output shaft 2 to be driven in rotation in a first direction of rotation called forward and in a second opposite direction of rotation called reverse.

This direction reversing mechanism 7 comprises a drive control member 8 in forward gear of the output shaft 2 and a drive control member 9 in reverse gear of the output shaft and, mounted on said output shaft 2, two counter-rotating members 10 and 11 called driving and a sliding gear 13 inverter.

In the examples shown, the counter-rotating members 10, 11 driving the direction reversal mechanism 7 each have the form of a toothed wheel mounted freely to rotate on the output shaft 2.

Each of these counter-rotating members 10, 11, mounted on the free-rotating output shaft 2, is in permanent engagement with one of the input shafts of the box described above.

The input shafts are therefore each formed of a worm and each worm tangent a toothed wheel forming one of the counter-rotating members.

Thus, the counter-rotating members 10, 11 are driven, one in one direction of rotation, the other in an opposite direction of rotation.

In the examples shown, it is the endless screw forming the output shaft of the belt transmission which engages with the counter-rotating member 10 which rotates in a direction of rotation corresponding to the forward motion of the output shaft 2 and, consequently, of the gear.

In forward gear, that is to say in the state actuated by the driver of the machine of the drive control member 8 in forward gear of the output shaft 2, it is therefore the rotational movement of the counter-rotating member 10 which is transmitted to the output shaft, while in reverse, that is to say in the actuated state of the drive control member 9 in reverse of the output shaft 2, it is the rotational movement of the counter-rotating member 11 which is transmitted to the output shaft 2.

To allow such transmission of motion, the direction reversal mechanism 7 comprises a sliding gear 13 inverter, also mounted on the output shaft 2.

This inverter slider 13 is mounted integral in rotation with the driving elements 6A and 6B of the clutch mechanisms 3A and 3B and is configured to come into engagement with one of the counter-rotating members, in this case the counter-rotating member 10 at the actuated state of drive control member 8 in the forward direction of output shaft 2 and with the other of the rotary members, in this case counter-rotating member 11 in the actuated state of member 9 reverse drive control of the output shaft 2 via the clutch mechanisms.

As the sliding gear 13 is mounted integral in rotation with the driving elements of the clutch mechanisms 3A, 3B, in the driven state in rotation of the sliding gear 13 reverser engaged with any of the members 10, 11 counter-rotating and in the engaged state of the clutch mechanisms 3A, 3B, the rotational movement of the inverter slider 13 is transmitted to the output shaft 2.

In the examples shown, the counter-rotating members 10, 11 each take the form of a toothed wheel or a rotary pinion provided with a central recess 12 for free-to-rotate mounting on the output shaft and each counter-rotating member 10, 11 is, at its central recess 12, crossed right through by the player 13 inverter.

This player 13 inverter affects meanwhile the form of a coaxial sleeve to the shaft 2 output.

This inverter slider 13 is mounted on said output shaft 2 which is axially movable and free to rotate.

The sleeve is therefore surrounded by counter-rotating members 10, 11 which are threaded onto the sleeve and can slide inside the central recess 12 of each counter-rotating member.

Thanks to this assembly, the sliding gear 13 inverter can be moved axially on the output shaft 2, independently of the counter-rotating members 10.

These counter-rotating members 10 can, conversely, be immobilized or axially limited in movement along the output shaft 2 .

This impediment or this limitation in axial displacement are, in the examples shown, obtained using a washer through which the output shaft passes and arranged on the output shaft, between the counter-rotating members.

This washer is retained in position, in particular immobilized axially in position inside the housing 1, by cooperating with the walls of the housing.

The direction reversal mechanism 7 is a claw mechanism comprising a movable dog formed by the player 13 inverter.

The counter-rotating members 10, 11 form the equivalent of so-called fixed jaws of said jaw mechanism.

The sliding gear 13 reverser is in the form of a sleeve provided at each of its ends with dog teeth provided on a flange fitted to the sleeve.

These dog teeth are, on each collar, arranged on the face of the collar facing the other collar.

These teeth are shown at 14A on the collar formed at one end of the sleeve and at 14B on the collar formed at the other end of the sleeve.

The counter-rotating members 10 and 11 are arranged side by side on the sleeve, between the collars of the sleeve, with possible play between the collars and the counter-rotating members 10, 11, 11.

These counter-rotating members 10 have teeth 16A and 16B arranged each time on the face of the counter-rotating member, in this case on the face of the toothed wheel opposite to that facing the other counter-rotating member.

These teeth 16A and 16B form, at the level of each counter-rotating member 10, 11 which carries them, a crenellation capable of cooperating with a facing crenellation formed by the teeth 14A or 14B fitted to a flange of the sleeve of the sliding gear 13 inverter.

This cooperation takes place by axial displacement of the sliding gear 13 inverter, in the actuated state of the member 8 for forward drive control or 9 for reverse drive control of the output shaft 2 .

[0062] The player 13 inverter, axially movably mounted on the output shaft 2 in the actuated state of the drive control member 8 in forward gear or of the drive control member in reverse gear of the output shaft 2 is configured to, by axial movement along said output shaft 2, come into engagement with one of the counter-rotating members 10, 11 in the actuated state of the drive control member 8 in the forward direction of the output shaft 2 and with the other of the members 10, 11 counter-rotating in the actuated state of the drive control member 9 in reverse gear of the output shaft 2.

Because a clearance is provided between the contra-rotating members 10, 11 and the flanges of the sleeve constituting the sliding gear 13, the sliding gear 13 can thus be moved axially on the output shaft 2 without axial movement of the bodies 10, 11 counter-rotating.

Thus, in the actuated state of drive control member 8 in forward operation of output shaft 2, an axial displacement of sliding gear 13 is generated.

This axial displacement of the sliding gear 13 reverser is operated in the direction of a rapprochement of the teeth 14A provided at one of the ends of the sleeve of the sliding gear 13 reverser of the teeth 16A opposite the counter-rotating member 10 rotating in forward gear, until in a dog clutch position in which the tooth crenellations interpenetrate, so that the forward rotational movement of the counter-rotating member 10 is transmitted to the reversing slider 13 and, consequently, to the elements 6A, GB driving the mechanisms clutch whose inverter 13 is integral in rotation.

Similarly, in the actuated state of the reverse drive control member 9 of the output shaft 2, an axial displacement of the sliding gear 13 is generated.

This axial displacement of the sliding gear 13 reverser takes place in the direction of a rapprochement of the teeth 14B of the sliding gear 13 provided at the other end of the sleeve of the sliding gear reverser of the teeth 16B opposite the counter-rotating member 11 rotating in reverse until in a dog clutch position in which the crenellation of the teeth of the reversing slider 13 and the crenellation of the teeth of the counter-rotating member 11 interpenetrate, so that the reverse rotational movement of the counter-rotating member 11 is transmitted to the slider 13 inverter and, consequently, to the 12 elements 6A, 6B driving the clutch mechanisms 3A, 3B with which the slider 13 inverter is integral in rotation.

In the examples shown, the element 6A or 6B leading mechanisms 3A or 3B clutch is a ring gear as described above, which is mounted integral in rotation with the sliding gear 13 inverter via teeth 18A or 18B forming the crenellation of the crown, these teeth 18A or 18B engaging with teeth 17A or 17B of a crenellation of the slider 13 inverter.

These teeth of the inverter slider 13 which form a crenellation for rotational connection with the taking element of one of the clutch mechanisms are provided each time on the face of the flange of the inverter slider opposite to that facing on the other collar.

Alternatively, at least part of the sliding gear 13 inverter and the driving elements of the clutch mechanisms could have been made in one piece.

[0067] Note that in the examples shown, the sleeve of the reversing player is made in two parts, integral in rotation, assembled by abutment to allow positioning of the counter-rotating members 10, 11 on the sleeve, before assembly of the parts between them and maintenance of the counter-rotating members 10, 11 inside the interval formed by the flanges of the sleeve.

In the examples shown, the drive control member 8 in forward motion of the output shaft 2 is an angularly movable member inside the housing, around an axis orthogonal to the shaft 2 Release.

This member 8 is formed by a fork.

This fork has a C-shape surrounding the output shaft.

This fork exerts, by angular displacement, a thrust force on the elements mounted on the output shaft 2.

This fork is itself controlled in angular displacement by a lever 81 arranged outside the housing, on the housing, and with which it is integral in angular displacement. This lever 81 is itself connected by a transmission of movement, such as a cable 82, to a control member, such as a control lever, positioned on a driving member of the machine, such as the handlebar of the machine in the case of a lawn mower.

11 is the same for the reverse drive control member 9 of the output shaft 2, this control member 9 being formed by a fork integral in angular displacement with a lever 91 operable by a 92 cable.

The drive control members 8 in forward gear and 9 for drive control in reverse gear of the output shaft are arranged on the output shaft 2, so that the sliding gear 13 inverter, the members 10, 11 contra-rotating drives, the driving elements 6A, 6B and the driven elements 5A, 5B of the clutch mechanisms 3A, 3B are arranged on the output shaft 2, between at least a part of the drive control member 8 13 in forward gear and part of the reverse drive control member 9 of the output shaft, these two control members framing the driving 6A, 6B and driven SA, 5B elements of the mechanisms 3A, 3B of clutch, the organs 10, 11 counter-rotating and the player 13 inverter.

The inverter slider 13 and the driving 6A, 6B and driven elements SA, 5B of the clutch mechanisms 3A, 3B in coaxial arrangement on the output shaft 2 form a stack on said shaft 2.

[0072] Thus, the actuation of one of the control levers located on the handlebars by the driver of the machine, namely the control lever in forward gear of the machine causes the angular displacement of the member 8 of forward drive control in the direction of an axial compressive force of the stack formed by the reversing slider and the driving and driven elements of the clutch mechanisms in coaxial arrangement on the output shaft.

This axial compressive force of the stack is exerted in the direction of drive control member 9 in reverse gear of output shaft 2 .

One of the walls of the casing forms an abutment for stopping this stack.

[0073] Similarly, r actuation of the other of the control levers located on the handlebars, namely the reverse control lever, by the driver of the machine causes the angular displacement of the control member 9 of reverse drive in the direction of an axial compressive force of the stack formed by the slider 13 inverter and the driving and driven elements of the clutch mechanisms 3A, 3B in coaxial arrangement on the shaft 2 output.

This axial compressive force of the stack is exerted in the direction of drive control member 8 in forward motion of output shaft 2 .

One of the walls of the casing forms an abutment for stopping this stack.

[0074] Thus, two of the walls of the housing arranged opposite each other form one, an axial stop of the stack in the state subjected to said stack to an axial compressive force resulting from the angular displacement in the direction of said stack of the drive control member 8 in forward operation of the output shaft 2, the other an axial stop of the stack in the state subject said stack to a force of axial compression resulting from the angular displacement in the direction of said stack of the drive control member 9 in reverse gear of the output shaft 2 .

Each time, the inverter slider 13 disposed between the clutch mechanisms 3A, 3B is driven in axial movement by one of the clutch mechanisms and drives the other clutch mechanism in movement under the effect of the axial compressive force of the stack generated by the drive control member 8 in forward gear or the drive control member 9 in reverse gear of the output shaft 2 .

[0076] The detail of the stack is more particularly visible in Figure 6.

The inverter slider 13 on the sleeve of which the contra-rotating members 10, 11 are arranged is arranged between the driving elements 6A, 6B of the clutch mechanism 3A, 3B, so that the contra-rotating driving elements 10, 11 are arranged on the shaft 2 output, between the elements 6A, 6B leading mechanisms 3A, 3B clutch.

The sliding gear 13, the counter-rotating driving elements 10, 11 and the driving elements 6A, 6B of the clutch mechanisms 3A, 3B are arranged on the output shaft, between the driven elements 5A, 5B of the mechanisms 3A, 3B clutch.

Finally, the inverter slider 13, the counter-rotating driving members 10, 11, the driving elements 6A, 6B and the driven elements 5A, 5B of the clutch mechanisms 3A, 3B are arranged on the output shaft, between the least a part of the drive control member 8 in forward gear and a part of the drive control member 9 in reverse gear of the output shaft 2 .

As shown in Figure 6, additional parts such as bearings or washers are provided at this stack to optimize the realization of this stack.

Thus, each fork, during its angular movement, acts by thrust via a bearing on the driven element of one of the clutch mechanisms which constitutes the beginning of the stack.

[0080] Due to the design of the forks constituting the members 8 for drive control in forward gear of the output shaft and 9 for drive control in reverse gear of the output shaft arranged on either side other of the stack, the result is that when a fork is controlled in movement to pass from an inactive position to an active position in which it exerts a compression force of the stack, the other fork follows the axial movement of the stack and is moved angularly in the direction of a spacing of the stack.

The follower movement of this fork can result from the axial force exerted by said stack on said fork, this follower fork then being spring-loaded to return to a neutral position, once the controlled or driving fork is free from any stress on the part of the driver of the machine.

[0081] The following movement of this fork can, as a variant, result from the design of the transmission of movement between the forks and the control levers, the actuation of one of the control levers generating, in parallel with the controlled movement of one of the forks in the direction of an approximation of the stack to generate an axial compression of said stack, an angular displacement of the other of the forks in the direction of a separation of said fork from the stack.

The mounting of the driving and driven elements of the clutch mechanisms 3A, 3B, of the inverter slider 13 and of the counter-rotating members 10, 11 on the output speed 2 therefore allows, in addition to the direction reversal control, the clutch control.

Indeed, the drive control member 8 in forward gear, or respectively, the drive control member 9 in reverse gear of the output shaft 2 are each configured to form, in addition to the member control of the coming into engagement of the player 13 inverter with one of the counter-rotating members, at least part of the clutch control device of the mechanisms 3A, 3B clutch.

[0083] It can be seen that this assembly allows the forward drive control member 8 of the output shaft 2 or the reverse drive control member 9 of the output shaft 2 output which controls the reversal of direction, by exerting an axial compressive force on the stack, to also control the bringing together of the driving and driven elements of the clutch mechanism, and consequently, the passage from the disengaged position to the engaged position of the clutch mechanisms 3A, 3B.

The transmission of motion between the primary motor shaft 31 and the wheels 33 of the machine therefore operates as follows: it is assumed that the primary motor shaft 31 rotates.

The movement of the primary motor shaft 31 is therefore transmitted via the system 15 for driving the counter-rotating members 10, 11 in rotation to the said counter-rotating members 10, 11 in order to drive them in rotation in two opposite directions.

In particular, the rotational movement of the primary motor shaft 31 is transmitted via the belt transmission to one of the endless screws which constitutes one of the input shafts of the housing and via meshing between the first and the second worm screw to the second worm screw which constitutes the second input shaft of the housing, so that the first and second worm screws rotate in opposite directions.

These first and second worm screws tangent the constituent toothed wheels of the counter-rotating members 10, 11.

The counter-rotating members 10, 11 rotate in opposite directions, the direction of rotation of the counter-rotating member 10 corresponding to the forward drive direction of the output shaft 2, the direction of rotation of the counter-rotating member 11 corresponding in the reverse drive direction of the output shaft 2.

[0086] The actuation by the driver of the machine of the control lever in forward gear located at the level of the driving member, that is to say the handlebars of the machine, drives by traction on the cable connecting the control lever to the lever 81, a pivoting of the lever 81 associated with the forward drive control member 8 of the output shaft 2 itself formed by a fork and, consequently, a displacement angular of said fork around an axis orthogonal to the longitudinal axis of the output shaft 2. 16

This fork then exerts an axial compressive force on the stack formed of the driving and driven elements of the clutch mechanisms 3A and 3B and of the reversing slider.

More precisely under the effect of the angular displacement of the fork forming the drive control member 8 in forward operation of the output shaft 2, the driven element 5A is moved axially by the fork against the driving element 6A which itself is moved with the inverter slider 13 with which it is integral in rotation against the toothed wheel constituting the counter-rotating drive member 10 in the forward direction of the output shaft 2, so that the rotational movement of the toothed wheel constituting the counter-rotating drive member 10 in forward motion of the output shaft 2 is transmitted to the sliding gear 13 inverter.

The counter-rotating member 10 is limited in axial movement on the output shaft by means of the washer interposed between said counter-rotating members 10, 11.

The axial displacement of the reversing slider continues, and the driving element 6B of the other clutch mechanism 3B is moved against the driven element 5B of this other clutch mechanism 3B which itself drives in angular displacement in the direction of a separation of the stack the drive control member 9 in reverse gear, if this has not already been the case during the actuation of the control member 8 in forward gear of the output shaft.

The axial movement of the stack is stopped by one of the walls of the casing which acts as an axial stop.

The conical surfaces of the male cones constituting the driven elements of the clutch mechanisms cooperate by bearing contact with the conical bearing surfaces of the female cones constituting the driving elements of the clutch mechanisms.

Due to the friction forces between the driving and driven elements, in particular between the male cones and the conical surfaces of the clutch mechanisms, the two shaft sections and therefore the wheels are driven in rotation in the forward direction.

[0090] Because the clutches are friction clutches and the shaft sections 2A, 2B are separate and not integral in rotation, the wheels can rotate at different speeds, even when the clutch mechanisms are engaged.

[0091] Furthermore, because the male cones can constantly slip on the conical bearing surfaces in the engaged state, each wheel is capable of receiving a minimum drive torque, regardless of the grip of the surfaces on which the the wheels.

Driving the machine, and in particular taking turns, is thus facilitated.

[0092] It is also noted that, because the dog clutch takes place before the clutch, the selection of the drive control direction can take place smoothly.

Of course, operation in reverse is similar, except that it is no longer the drive control member 8 in forward gear of the output shaft which is controlled in movement to exert a force of compression on the stack, but the drive control member 9 in reverse gear 17 of the output shaft.

The principle of axial compression of the stack is identical.

The axial force on the stack is not exerted either from the forward drive control member 8 of the output shaft towards the reverse drive control member 9 of the output shaft. output, but from the output shaft reverse drive control member 9 to the output shaft forward drive control member 8.

Thanks to the design of the transmission housing 1 as described above, a compact assembly is obtained, the operation of which remains perfectly safe.

18 [Claim 1]

Claims (1)

CLAIMS Transmission housing (1) positionable between the primary drive shaft (31) and the wheels (33) of a rolling machine (30), said housing (1) delimited by walls (21) comprising, housed at least partially inside said casing (1), a so-called wheel drive output shaft (2) formed of at least two coaxial shaft sections (2A, 2B) mounted free in rotation relative to each other, two progressive friction clutch mechanisms (3A, 3B) carried one (3A) by one (2A) of the shaft sections, the other (3B) by the other (2B) of the shaft sections shaft, and a clutch control device (4A, 4B), each clutch mechanism (3A, 3B) comprising a so-called driven element (5A, 5B) integral in rotation with the section (2A, 2B) of shaft which carries it and an element (6A, 6B) called a rotary drive, said driving (6A, 6B) and driven (5A, 5B) elements being configured to pass from a disengaged state in which they are separated from one another the other to a clutched state in which they are engaged with each other under the action of the clutch control device (4A, 4B), characterized in that the housing (1) further comprises, housed at least partially inside said casing (1), a mechanism (7) for reversing the direction of rotation of the output shaft (2) for driving said shaft (2) in forward or reverse gear output, this direction inversion mechanism (7) comprising a drive control member (8) in the forward direction of the output shaft (2), a drive control member (9) in reverse direction of the the output shaft (2), and mounted on said output shaft (2), two counter-rotating members (10, 11) called driving members and an inverter sliding gear (13), said reversing sliding gear (13) being configured to come into engagement with one (10) of the counter-rotating members (10, 11) in the actuated state of the forward drive control member (8) of the output shaft (2), and with the other (11) of the counter-rotating members in the actuated state of the drive control member (9) in reverse gear of the output shaft (2), and the reversing sliding gear (13) being mounted integrally rotation of the driving elements (6A, 6B) of the clutch mechanisms (3A, 3B) in order to allow the reversing sliding gear (13) to be in engagement with any one of the counter-rotating members (10, 11) and to engaged state of the clutch mechanisms (3A, 3B), the transmission of the rotational movement of the inverter slider (13) via the clutch mechanisms (3A, 3B) to each of the shaft sections (2A, 2B), 19 [Claim 2] [Claim 3] [Claim 4] [Claim 5] [Claim 6] [Claim 7] [Claim 8] independently of the direction of rotation of said sliding gear (13) inverter. Transmission housing (1) according to claim 1, characterized in that the drive control member (8) in forward gear, or respectively (9) drive control in reverse gear, of the shaft (2 ) output is configured to form, in addition to the control member of the coming into engagement of the player (13) inverter with one of the members (10, 11) counter-rotating, at least part of the device (4A, 4B ) clutch control mechanisms (3A, 3B) clutch. Transmission box (1) according to one of Claims 1 or 2, characterized in that the reversing slider (13) is arranged on the output shaft (2) between the driving elements (6A, 6B) of the mechanisms (3A , 3B) clutch. Transmission box (1) according to one of Claims 1 to 3, characterized in that the contra-rotating driving members (10, 11) are arranged on the output shaft (2) between the driving elements (6A, 6B) of the clutch mechanisms (3A, 3B). Transmission case (1) according to one of Claims 1 to 4, characterized in that the reversing slider (13), the driving counter-rotating members (10, 11) and the driving elements (6A, 6B) of the mechanisms (3A, 3B) are arranged on the output shaft (2) between the driven elements (SA, 5B) of the clutch mechanisms (3A, 3B). Transmission case (1) according to one of Claims 1 to 5, characterized in that the reversing slider (13), the counter-rotating driving elements (10, 11), the driving elements (6A, 6B) and the driving elements (SA , SB) driven clutch mechanisms (3A, 3B) are disposed on the output shaft (2) between at least a portion of the forward drive control member (8) of the shaft ( 2) output and part of the member (9) reverse drive control of the shaft (2) output. Transmission case (1) according to one of Claims 1 to 6, characterized in that the counter-rotating drive members (10, 11) each take the form of a wheel or a rotary pinion provided with a recess (12 ) central for free rotational mounting on the output shaft (2) and in that each counter-rotating member (10, 11) is, at its central recess (12), crossed right through by the player ( 13) inverter. Transmission box (1) according to one of Claims 1 to 7, characterized in that the inverter player (13) takes the form of a a sleeve coaxial with the output shaft (2) and mounted on said output shaft (2) which is axially movable and free to rotate. Transmission box (1) according to one of Claims 1 to 8, characterized in that the mechanism (7) for reversing the direction of rotation of the output shaft (2) is a dog clutch mechanism and in that the reversing slider (13) which forms a movable dog clutch of the dog clutch mechanism and which assumes the shape of a sleeve is provided at each of the ends of the sleeve with dog dog teeth (14A, 14B), the dog dog teeth (14A) formed at one of the ends of the sleeve being configured to cooperate with dog teeth (16A) arranged opposite on one (10) of the counter-rotating driving members (10, 11), in the actuated state of the member ( 8) forward drive control of the output shaft (2), and the dog clutch teeth (14B) formed at the other end of the sleeve being configured to cooperate with dog clutch teeth (16B) arranged facing the other (11) of the counter-rotating members (10, 11) leading to the actuated state of the member (9) for driving the output shaft (2) in reverse gear. Transmission case (1) according to one of Claims 1 to 9, characterized in that each clutch mechanism (3A, 3B) is a clutch mechanism with cones (19, 20). Transmission box (1) according to one of Claims 1 to 10, characterized in that the reversing slider (13) and the driving (6A, 6B) and driven (SA, 5B) elements of the mechanisms (3A, 3B) d clutch in coaxial arrangement on the output shaft (2) form a stack on said shaft (2) and in that the forward drive control member (8) of the output shaft (2) , or respectively, the reverse drive control member (9) of the output shaft (2) is a member, such as a fork, which can be moved angularly, this member (8, 9) being configured to exert, during its angular displacement in the direction of said stack, an axial compressive force of the stack formed of the sliding gear (13) inverter and the driving (6A, 6B) and driven (SA, 5B) elements of the mechanisms (3A, 3B) clutch in coaxial arrangement on the output shaft (2). Transmission case (1) according to one of Claims 1 to 11, characterized in that it comprises, for driving the counter-rotating driving members (10, 11) of the direction reversing mechanism (7) in rotation, a system (15) rotary drive (15) housed at least partly [Claim 13] inside the housing (1). [Claim 14] Transmission housing (1) according to one of Claims 1 to 12, characterized in that the counter-rotating driving members (10, 11) of the direction reversing mechanism (7) each take the form of a toothed wheel rotatably mounted on the output shaft (2). Rolling self-propelled machine (30), in particular a walk-behind machine, such as a lawn mower, said machine (30) comprising a primary motor shaft (31) and a transmission housing (1) positionable between the shaft (31) primary engine and the wheels (33) of said machine (30), characterized in that the transmission housing (1) conforms to one of claims 1 to 13.