WO2014063729A1 - Transmission dotée d'un frein - Google Patents

Transmission dotée d'un frein Download PDF

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Publication number
WO2014063729A1
WO2014063729A1 PCT/EP2012/071059 EP2012071059W WO2014063729A1 WO 2014063729 A1 WO2014063729 A1 WO 2014063729A1 EP 2012071059 W EP2012071059 W EP 2012071059W WO 2014063729 A1 WO2014063729 A1 WO 2014063729A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
planetary stage
drive shaft
driving gear
transmission housing
Prior art date
Application number
PCT/EP2012/071059
Other languages
German (de)
English (en)
Inventor
Albert Pfeiffer
Roland Hartmann
Original Assignee
Zollern Gmbh & Co.Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zollern Gmbh & Co.Kg filed Critical Zollern Gmbh & Co.Kg
Priority to PCT/EP2012/071059 priority Critical patent/WO2014063729A1/fr
Publication of WO2014063729A1 publication Critical patent/WO2014063729A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
    • B60T1/062—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels acting on transmission parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel

Definitions

  • the invention relates to a driving gear with a brake, which has a service brake function and preferably also a holding brake function.
  • the driving gear is preferably attached to a rim of a wheel.
  • the transmission may be a wheel gear, which on a wheel (drive wheel) of a z.
  • Driving gears for arrangement on a wheel of a vehicle are already known from the prior art.
  • a known from the prior art driving gear is shown, which has a bearing housing 1, which is in particular secured against rotation about the axis of rotation of a drive shaft 2 to a vehicle.
  • a driven housing 10 by means of rotary bearings 11, 12 is rotatably mounted about the axis of rotation of the drive shaft 2.
  • the drive shaft 2 is the drive side coupled to a motor, and the output side rotatably connected to a sun gear 3 of a first planetary stage 3, 4, 5, wherein the planet carrier 6 of the first planetary stage 3, 4, 5 a sun gear 7 of a second planetary stage 7, 8, 9th forms.
  • the axis of rotation of the planetary gear 8 of the second planetary stage 7, 8, 9 is formed by the bearing housing 1.
  • the ring gear 5 of the first planetary stage 3, 4, 5 and the ring gear 9 of the second planetary stage 7, 8, 9 are rotatably mounted on the output housing 10.
  • a rotation of the drive shaft 2 relative to the bearing housing 1 effected by means of the first and second planetary stages 3, 4, 5; 7, 8, 9 that the output housing 10 rotates at a lower rotational speed relative to the bearing housing 1 than the drive shaft 2. This reduction in speed causes an increase in torque on the output housing 10 in comparison to the drive shaft 2.
  • the known from the prior art transmission of Figure 1 has a braking device 13 a, 13 b, which is designed as a multi-disc brake, the first fins 13 a rotationally fixed to the drive shaft. 2 are connected and whose second fins 13b are rotatably connected to the bearing housing 1.
  • the braking device 13a, 13b is designed as a holding brake, which is actuated when the gear is stopped by means of a pressure body 14 or piston and thus prevents rotation of the drive shaft 2 and the output housing 10.
  • the braking device 13a, 13b is configured as a spring-loaded brake, which presses the slats 13a, 13b against each other by means of a pretensioned spring 15, provided that a pressure chamber 16 is unprinted.
  • the spring 15 is compressed, and the pressure body 14 of the slats 13 a, 13 b moved away, so that the slats 13 a, 13 b are no longer pressed against each other.
  • the drive shaft 2 can then be rotated relative to the bearing housing 1.
  • the holding brake of the transmission of Figure 1 has the disadvantage that it can brake only at a standstill due to the relatively high speed of the drive shaft 2 relative to the bearing housing 1, the transmission.
  • the invention is based on a drive gear for arrangement on a wheel of a vehicle.
  • the driving gear can thus be arranged on a wheel of a vehicle.
  • the vehicle may be, for example, an IC motor vehicle, in particular a rubber-tired or chain-driven motor vehicle.
  • the driving gear can also be referred to as axle or hub gear.
  • the driving gear comprises a transmission housing, also referred to as a bearing housing, and an output housing, which is rotatable relative to the gear housing about an axis of rotation.
  • the output housing is preferably rotatably supported on the transmission housing, the latter can also be referred to as a bearing housing.
  • the gear housing and / or the output housing can each be designed pot-shaped.
  • the driving gear further comprises a drive shaft which is rotatable relative to the gear housing about the same axis of rotation as the output housing.
  • the drive shaft and the output housing are preferably in a fixed speed or reduction ratio to each other.
  • the transmission housing forms a passage for the drive shaft, in particular through the bottom of the cup-shaped gear housing.
  • the drive shaft can be rotatably supported on the transmission housing.
  • the gear housing can form or record a rotary bearing for the drive shaft.
  • the drive shaft preferably protrudes from the bottom of the cup-shaped gear housing and may, for example, means such.
  • a clutch with which the drive shaft with a motor or another part of a drive train, which leads from the engine to the drive gear, can be connected or is connectable.
  • At least one planetary stage in particular a single, two, three or even more planetary stages, arranged.
  • the at least one Planentenlie causes the input speed of the transmission, that is, the speed which makes the drive shaft relative to the transmission housing, is down to the output housing down.
  • the output speed of the transmission which executes the output housing relative to the transmission housing, is lower than the input speed of the transmission.
  • the output housing may be arranged concentrically around the drive shaft.
  • the drive shaft On the drive side of the at least one planetary stage, the drive shaft is arranged.
  • the output housing and / or the transmission housing are arranged on the output side of the at least one planetary stage. The input speed transmitted by the engine to the drive shaft is thus reduced to the output housing via the at least one planetary stage.
  • the driving gear comprises a braking device, which is designed as a service brake, so that a rotation of the output housing relative to the transmission housing during operation or the running of the transmission can be braked.
  • the previously known driving gear are equipped with a holding brake, that is, with a brake that does not slow down the transmission during operation or running, but only during the stoppage of the transmission notes.
  • the range of uses of the drive gear can be extended, since the braking device can be used in addition to the fact that it is designed as a service brake, as a holding or parking brake.
  • the braking device may be attached to two parts which, in particular during operation or running, rotate relative to one another at a lower rotational speed than the drive shaft rotates relative to the transmission housing.
  • This arrangement of the braking device is advantageous in particular without limitation to a service brake, so that the applicant reserves the right to pursue this arrangement on the basis of the features a) to d) of claim 1.
  • the brake can be thermally designed as a service brake, with a compact design can be maintained.
  • the at least one planetary stage may preferably comprise a first planetary stage, wherein a sun gear of the first planetary stage is rotatably connected to the input shaft and the braking device is disposed on the output side of the first planetary stage, in particular kinematically, between the first planetary stage and the transmission housing.
  • the arrangement of the braking device on the output side of the first planetary stage can be advantageously achieved that two parts rotate at a lower speed relative to each other than the drive shaft rotates relative to the transmission housing.
  • a further, in particular a second or even a third planetary stage can be provided, wherein the further planetary stage can be arranged on the output side of the first planetary stage.
  • the second planetary stage may be arranged on the output side of the first planetary stage. If a third planetary stage is present, the third planetary stage can be arranged on the output side of the second planetary stage. Consequently, the braking device can be arranged on the output side of the second planetary stage or on the output side of the third planetary stage, in particular kinematically between the second or third planetary stage and the transmission housing.
  • the speed between the two parts can be further reduced and increase the torque, whereby the heat in the brake designed as a brake can be further reduced.
  • the braking device can on the output side of the at least one planetary stage and kinematically between the planet carrier, the at least one Planetary stage, z. B. the first, second or third planetary stage, and be arranged the transmission housing.
  • the two relatively rotating parts may be the gear housing and the planet carrier of the first, second or third planetary stage.
  • the braking device may be arranged on the output side of the at least one planetary stage preferably kinematically between the gear housing and the output housing.
  • the two relatively rotating parts to which the brake device is attached may be the transmission housing and the output housing.
  • the brake device may be a multi-disc brake.
  • the multi-disc brake comprises first fins and second fins, wherein the second fins are rotatably connected to one of the relatively rotating parts, such as with the transmission housing.
  • the first fins may be non-rotatably connected to the other of the relatively rotating parts, such as the output housing or the planet carrier of the at least one planetary stage, in particular the first, second or third planetary stage.
  • the braking device comprises a plurality of first slats and a plurality of second slats, wherein the first and second slats are arranged alternately, so that a first slat between two second slats is arranged touching and a second slat between two first slats is arranged touching.
  • the first and second blades are as stated rotationally fixedly connected to the respective part, but preferably to the part to which they are attached or to which they are connected, axially displaceable.
  • the lamellae are preferably annular around the drive shaft or the axis of rotation about which the drive shaft rotates, in particular arranged concentrically.
  • the lamella heating is more uniform and faster at different outside temperatures and at cold start. This results in a smaller temperature-related Reibwertschwankung and thus a better control behavior of the braking device.
  • the fins can run in a lubricant, such as in an oil bath, so that there is improved heat dissipation and the heat is dissipated to other components. Due to the existing parts of the drive gear and the oil is a large heat storage available. Due to the oil bath, there is less wear on the friction linings of the lamellae. Thus, a low-maintenance braking device can be realize.
  • the brake structure is simple because no additional components such as a caliper or the like need to be attached. By integrating the braking device in the drive gear, the brake can be sealed so that it is protected against environmental influences, in particular against pollution.
  • the multi-disc brake further comprises an electrically, hydraulically or pneumatically driven pressure piece, in particular a pressure piston, by means of which the blades can be pressed against each other.
  • the pressure piece is preferably arranged in the transmission housing, in particular rotatably connected to the transmission housing about the rotational axis of the drive shaft or mounted on the transmission housing. By pressing the slats together a braking effect of the braking device is achieved. Depending on the contact pressure of the pressure piece on the slats, the strength of the braking effect can be varied.
  • the driving gear can, for example, have a connection with which it can be connected to the service brake system of a vehicle. The connection is coupled to the pressure piece in such a way that the contact pressure of the pressure piece on the slats can be controlled and / or regulated.
  • the pressure piece is pressed by means of a spring, in particular a mechanical spring, such as a spiral spring against the slats, whereby the slats are pressed against each other.
  • the spring is designed to exert enough force on the blades to stop or stop the transmission.
  • the contact pressure exerted by the spring on the slats can be reduced electrically, hydraulically or pneumatically, whereby the brake is opened.
  • the spring causes the brake to brake.
  • a safety device is given.
  • Such a safety device is often referred to as spring storage.
  • a pressure chamber may be provided which is hydraulically or pneumatically printable and is at least partially formed by the pressure piece or the piston, whereby by pressure of the pressure chamber, the pressure piece against the force of the spring is displaceable or on the pressure piece of the spring force counteracting, preferably variable, force is exercised.
  • the output housing may be rotatably supported by means of at least one rotary bearing, such as a first and second pivot bearing on the transmission housing.
  • the pivot bearing disposed between the output housing and the transmission housing may be a roller bearing.
  • the braking device can be arranged with respect to the radial on the axis of rotation about which the drive shaft rotates, between the at least one pivot bearing, with which the output housing is supported on the gear housing and the drive shaft or the planet carrier of at least one planetary stage. This makes it possible to achieve a particularly compact design of the braking device, wherein the driven housing is supported on a relatively large diameter of the bearing housing, whereby a support is particularly stable.
  • the at least one rotary bearing relative to the radial on the axis of rotation about which the drive shaft rotates be arranged between the brake device and the drive shaft.
  • the diameter of the braking device can be increased while maintaining the compact design of the drive gear, wherein the increased diameter provides for an increased braking torque, whereby the brake itself is space-saving interpretable.
  • the pressure piece is arranged with respect to a rotatability about the drive shaft fixed to the transmission housing.
  • the pressure piece is displaceable along, in particular parallel to but spaced from the axis of rotation relative to the transmission housing.
  • the driving gear can be configured as a hub gear for a rolling on a surface wheel or a sprocket.
  • the output housing may be adapted to be attached to the rim of a wheel, in particular to be screwed.
  • the output housing can form the rim of the wheel.
  • a rubber tire such as solid rubber or an inflatable rubber tires may be arranged.
  • the driving gear can have a first planetary stage and a second planetary stage.
  • the ring gear of the first planetary stage and / or the Ring gear of the second planetary stage may be rotatably connected to the output housing or disposed on the output housing.
  • the planet carrier of the first planetary stage may, for example, be rotatably connected to the sun gear of the second planetary stage or form the sun gear of the second planetary stage.
  • the planet carrier of the second planetary stage may preferably be rotatably connected to the transmission housing or formed by the transmission housing.
  • FIG. 1 shows a drive gear known from the prior art
  • FIG. 2a shows a first embodiment of a traveling gear according to the invention with a single-acting cylinder
  • Figure 2b shows a variant of the first embodiment with a double-acting
  • Figure 3a is a second embodiment of a drive transmission according to the invention with a single-acting cylinder
  • Figure 3b shows a variant of the second embodiment with a double-acting
  • FIGS. 2a, b and 3a, b disclose various embodiments of a traveling gear according to the invention.
  • the drive gear comprises a transmission housing 1, which may also be referred to as a bearing housing, and a driven housing 10 which rotatably by means of a first pivot bearing 1 1 and a second pivot bearing 12 in particular a side wall of the preferably cup-shaped gear housing 1 is supported.
  • a transmission housing 1 which may also be referred to as a bearing housing
  • a driven housing 10 which rotatably by means of a first pivot bearing 1 1 and a second pivot bearing 12 in particular a side wall of the preferably cup-shaped gear housing 1 is supported.
  • Through the bottom of the gear housing 1 protrudes a drive shaft 2, which is rotatably mounted on or in the transmission housing 1.
  • Drive side of the Drive shaft 2 an engine or a leading to the engine drive train in particular a motor vehicle, in particular a transport vehicle can be attached.
  • a sun gear 3 of a first planetary stage 3, 4, 5 is arranged on the drive shaft 2, which is non-rotatable with respect to the drive shaft 2.
  • the first planetary stage 3, 4, 5 has planet wheels 4, which are arranged on a planet carrier 6 of the first planetary stage 3, 4, 5 and a ring gear 5, which is non-rotatably attached to the output housing 10.
  • the planet gears 4 mesh with both the sun gear 3 and the ring gear 5.
  • the planet carrier 6 is rotatably supported on the drive shaft 2 from.
  • the planet carrier 6 forms a sun gear 7 of a second planetary stage 7, 8, 9, which has a ring gear 9 which is non-rotatably mounted on the output housing 10, and planetary gears 8 which mesh with the sun gear 7 and the ring gear 9.
  • the planet gears 8 are rotatably mounted on a planet carrier of the second planetary stage 7, 8, 9.
  • the planet gears 8 each sit on an axis of rotation about which they are rotatable, wherein the respective axes of rotation are stationary with respect to the transmission housing 1.
  • the planet carrier of the second planetary stage 7, 8, 9 is arranged rotatably on the transmission housing 1.
  • the input speed of the drive gear, d. H. the speed of the output shaft 2 is reduced relative to the housing 1 to the output housing 10 out, so that the output speed, which performs the output housing 10 relative to the transmission housing 1, is less than the input speed. Due to the reduced speed, the torque increases accordingly.
  • the second planetary stage 7, 8, 9 is arranged on the output side of the first planetary stage 3, 4, 5.
  • the drive shaft 2 is the drive side of the first planetary stage 3, 4, 5 are arranged.
  • the bearing housing 10 is integrated in a wheel 17, 18 of a vehicle.
  • the wheel 17, 18 has a rim 18 and a rubber tire 17 which is disposed over the outer periphery of the rim 18.
  • the output housing 10 is adapted to be connected to the rim 18.
  • fastening means such. B. screws are used, which connect the output housing 10 with the rim 18.
  • the wheel 17, 18 rolls on a ground or a lane 19 from.
  • the transmission case 1 when installed in the vehicle, is connected to the vehicle so as to be secured against rotation with respect to the vehicle or the vehicle frame about the rotation axis about which the drive shaft 2 is rotatable.
  • the driving gear has a braking device 13a, 13b, which is configured as a multi-disc brake and can be used as a service brake, ie, that the brake is designed so that it can decelerate the driving gear during operation.
  • the multi-disc brake has first fins 13a and second fins 13b, wherein the fins 13a, 13b are each arranged annularly and concentrically about the axis of rotation of the drive shaft 2.
  • first lamellae 13a and second lamellae 13b are arranged alternately so that a second lamella 13b is arranged between two first lamellae 13a and a first lamella 13a is arranged between two second lamellae 13b.
  • the lamellae 13a, 13b are axially displaceable along the axis of rotation of the drive shaft 2.
  • the slats 13a, 13b can be pressed against one another with a desired pressing force, so that between the first slats 13a and the second slats 13b, a frictional force or a frictional torque is adjustable in the desired height.
  • the pressure body 14 is axially displaceable relative to the housing 1 along the axis of rotation of the drive shaft 2 and secured against rotation relative to the housing 1, in particular secured against rotation about the axis of rotation of the drive shaft 2.
  • the pressure body 14 may, for. B. electrically, hydraulically or pneumatically acted upon by a force with which the pressure body 14, the slats 13 a, 13 b pressed against each other.
  • the braking device in FIGS. 2b and 3b comprises a first pressure chamber 16 and a second pressure chamber 20, which can each be printed with pressurized fluid, ie hydraulically or pneumatically.
  • pressurized fluid ie hydraulically or pneumatically.
  • the pressure ratio between the pressure in the second pressure chamber 20 and the pressure in the first pressure chamber 16 is changed, especially increased.
  • the force difference caused due to the change in the pressure ratio presses the pressure body 14 in the direction or against the slats 13a, 13b or increases the contact pressure with which the slats 13a, 13b are pressed against each other.
  • the pressure ratio between the pressure in the second pressure chamber 20 and the pressure in the first pressure chamber 16 is changed, in particular reduced.
  • the force difference caused due to the change in the pressure ratio reduces the pressing force with which the slats 13a, 13b are pressed against each other, or moves the pressure body 14 away from the slats 13a, 13b.
  • the pressure ratio may e.g. be controlled by pressing the brake pedal of the service brake system.
  • the pressure body 14 forms a displaceable wall of the first and / or second pressure chamber 16, 20.
  • the wall may be disposed between the first pressure chamber 16 and the second pressure chamber 20 or separate these pressure chambers from each other.
  • this embodiment of the pressure hull 14 may be referred to as a double-acting piston.
  • the braking device further comprises a prestressed spring 15 which acts on the pressure body 14 with a force directed towards the lamellae 13a, 13b.
  • a prestressed spring 15 which acts on the pressure body 14 with a force directed towards the lamellae 13a, 13b.
  • FIGS. 2a and 3a have the pressure body 14, the first pressure chamber 16 and the spring 15, but not the second pressure chamber 20 of the embodiments from FIGS. 2b and 3b.
  • the pressure body 14 is not acted upon by a second pressure chamber 20 but by the prestressed spring 15 with a force which is directed to the blades 13a, 13b out.
  • the pressurized fluid exerts on the pressure body 14 a force corresponding to the force the prestressed spring 15 is opposite.
  • the force exerted on the blades 13 a, 13 b pressing force of the pressure body 14 can be adjusted, whereby the friction between the fins 13 a, 13 b and thus the braking effect of the braking device 13 a, 13 b can be adjusted.
  • the pressing force exerted on the lamellae 13a, 13b by the pressure body 14 results from the force of the prestressed spring minus the force exerted by the pressure fluid in the pressure chamber 16 on the pressure body 14.
  • the pressure in the pressure chamber 16 may be e.g. be controlled by pressing the brake pedal of the service brake system.
  • FIGS. 2a to 3b have the advantage that in the event of a defect in the pneumatic or hydraulic line which supplies the first pressure chamber 16 with the pressure fluid, the spring 15 presses the pressure body 14 so strongly against the lamellae 13a, 13b, that the drive gear is braked to a standstill.
  • the driving gear in particular the gear housing 1 can advantageously have at least one connection for a fluid line, in particular a hydraulic or pneumatic line, which is connected to the pressure chamber 16 and / or the pressure chamber 20 fluidaskedd or fluid leading, so that the pressure in the pressure chamber 16, 20 is controlled or regulated via the vehicle brake system, whereby the braking effect of the braking device 13a, 13b is adjustable.
  • a fluid line in particular a hydraulic or pneumatic line
  • the driving gear can, for example, have a pressure body 14 and a further pressure body 14, wherein the pressure bodies 14 can be connected to different brake systems of the vehicle.
  • one of the pressure bodies 14 may or may not be coupled to the service brake system, and another of the pressure bodies 14 may or may not be coupled to the parking brake system of the vehicle.
  • the driving gear, in particular the gear housing 1 can advantageously have at least one connection for a fluid line of the service brake system, in particular a hydraulic or pneumatic line, which is fluid-conductively or fluid-conductingly connected to the pressure chamber 16, 20, and / or at least one connection for a fluid line of the Parking brake system, in particular a hydraulic or pneumatic line, which is connected to the further pressure chamber 16, 20 fluid-carrying or fluid-conducting.
  • the output housing 10 is supported with a first pivot bearing 11 and a second pivot bearing 12 on the outer periphery of the transmission housing 1 from.
  • the braking device 13a, 13b is arranged relative to the radial on the axis of rotation of the drive shaft 2 in particular geometrically between the rotary bearings 11, 12 and the drive shaft 2 and / or the planet carrier 6.
  • the first fins 13a are secured against rotation with the planet carrier 6 of the first planetary stage 3, 4, 5 or the sun gear 7 of the second planetary stage 7, 8, 9 but in particular axially slidably mounted along the drive shaft 2.
  • the second fins 13b are secured against rotation on the transmission housing 1 and in particular mounted axially displaceable along the drive shaft 2. This arrangement results in a very compact design of the drive gear, resulting in a relatively stable arrangement due to the support of the drive housing 10 on the outer circumference of the gear housing 1.
  • the output housing 10 is supported with a first pivot bearing 11 and a second pivot bearing 12 on the portion of the transmission housing 1, which leads or supports the drive shaft 2 and which can also be referred to as a hollow shaft.
  • the first and second pivot bearing 11, 12 is, based on the radial on the output shaft 2 in particular geometrically disposed between the brake device 13 a, 13 b and the output shaft 2 or formed as a hollow shaft portion of the transmission housing 1.
  • the diameter of the slats 13 a, 13 b are increased at the same Kompaktheitsgrad of the drive gear, whereby the brake 13 a, 13 b develops an even better braking effect.
  • the first lamellae 13a are rotationally fixed and in particular axially displaceable along the drive shaft 2 attached to the output housing 10 or at least connected thereto.
  • the second fins 13b are rotationally fixed and in particular axially slidably mounted on the transmission housing 1 along the drive shaft 2 or at least connected thereto.
  • the planet carrier 6 rotatably supported on the drive shaft 2 from.
  • the braking device 13 a, 13 b As described in Figures 2a, b and 3a, b, the braking device 13a, 13b while maintaining the compactness of the drive gear as a service brake, which allows the drive gear down to a standstill to be braked.
  • this arrangement allows that the braking device 13 a, 13 b including the pressure body 14 can be arranged within the transmission housing 1.
  • the braking device 13 a, 13 b can also be used as a holding brake.
  • the braking device 13a, 13b in particular the slats 13a, 13b are arranged between two parts which rotate relative to each other slower than the drive shaft 2 rotates relative to the transmission housing 1, only allows the braking device 13 a, 13b can be designed as a service brake, ie unlike the braking device shown in Figure 1 13 a, 13 b can be designed only as a holding brake, since the thermal load on the braking device 13 a, 13 b would be too high due to the high speed of the drive shaft 2.

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  • Transportation (AREA)
  • Mechanical Engineering (AREA)
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Abstract

L'invention concerne une transmission destinée à être disposée sur une roue d'un véhicule, comprenant : a) un carter de transmission (1) et un carter de sortie (10), qui peut tourner par rapport au carter de transmission (1), b) un arbre d'entraînement (2), qui peut tourner par rapport au carter de transmission (1) autour du même axe de rotation que le carter de sortie (10), c) au moins un étage planétaire (3, 4, 5; 7, 8, 9) étant agencé entre le carter de sortie (10) et l'arbre d'entraînement (2), ledit étage planétaire démultipliant la vitesse de rotation d'entrée de la transmission qui anime l'arbre d'entraînement (2) par rapport au carter de transmission (1), vers le carter de sortie (10), de telle sorte que le carter de sortie (10) est animé d'une vitesse de rotation plus faible par rapport au carter de transmission (1) que l'arbre d'entraînement (2), et d) un dispositif de freinage (13a, 13b), e) le dispositif de freinage (13a, 13b) étant conçu comme frein de service de telle sorte qu'une rotation du carter de sortie (10) par rapport au carter de transmission (1) peut être freinée pendant le fonctionnement.
PCT/EP2012/071059 2012-10-24 2012-10-24 Transmission dotée d'un frein WO2014063729A1 (fr)

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PCT/EP2012/071059 WO2014063729A1 (fr) 2012-10-24 2012-10-24 Transmission dotée d'un frein

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Application Number Priority Date Filing Date Title
PCT/EP2012/071059 WO2014063729A1 (fr) 2012-10-24 2012-10-24 Transmission dotée d'un frein

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WO2014063729A1 true WO2014063729A1 (fr) 2014-05-01

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4212375A1 (fr) * 2022-01-14 2023-07-19 Rögelberg Holding GmbH & Co. KG Transmission pour chaîne cinématique pour un véhicule agricole ou lourd ainsi que chaîne cinématique et véhicule correspondants

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999003699A1 (fr) * 1997-07-18 1999-01-28 Volvo Construction Equipment Components Ab Transmission a engrenages planetaires destinee a un vehicule
WO2007039730A1 (fr) * 2005-10-04 2007-04-12 Nexxtdrive Limited Moyeux pour véhicules électriques hybrides
WO2008069707A1 (fr) * 2006-12-06 2008-06-12 Volvo Construction Equipment Ab Unité de moyeu et transmission pour un véhicule

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999003699A1 (fr) * 1997-07-18 1999-01-28 Volvo Construction Equipment Components Ab Transmission a engrenages planetaires destinee a un vehicule
WO2007039730A1 (fr) * 2005-10-04 2007-04-12 Nexxtdrive Limited Moyeux pour véhicules électriques hybrides
WO2008069707A1 (fr) * 2006-12-06 2008-06-12 Volvo Construction Equipment Ab Unité de moyeu et transmission pour un véhicule

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4212375A1 (fr) * 2022-01-14 2023-07-19 Rögelberg Holding GmbH & Co. KG Transmission pour chaîne cinématique pour un véhicule agricole ou lourd ainsi que chaîne cinématique et véhicule correspondants

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