CA2127050A1 - Mechanical transmission for drive wheels, especially for mobile work machines - Google Patents
Mechanical transmission for drive wheels, especially for mobile work machinesInfo
- Publication number
- CA2127050A1 CA2127050A1 CA 2127050 CA2127050A CA2127050A1 CA 2127050 A1 CA2127050 A1 CA 2127050A1 CA 2127050 CA2127050 CA 2127050 CA 2127050 A CA2127050 A CA 2127050A CA 2127050 A1 CA2127050 A1 CA 2127050A1
- Authority
- CA
- Canada
- Prior art keywords
- mechanical transmission
- gear
- intermediate member
- drive shaft
- cylindrical surface
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
Landscapes
- Arrangement Of Transmissions (AREA)
- Structure Of Transmissions (AREA)
Abstract
ABSTRACT of the DISCLOSURE.
The invention relates to a mechanical transmission for drive wheels, especially for mobile work machines, comprising: a sprocket keyed on a drive shaft rotatably supported to a frame; an internally-cogged crown connected to a hub of a drive wheel of a work machine; at least one intermediate gear wheel coupled to the sprocket and the crown and rotatable supported by an intermediate member. Two gear couplings are provided, each of which is equipped with own externally-activated means for command, which gear couplings connect the intermediate member with the frame and the drive shaft.
The invention relates to a mechanical transmission for drive wheels, especially for mobile work machines, comprising: a sprocket keyed on a drive shaft rotatably supported to a frame; an internally-cogged crown connected to a hub of a drive wheel of a work machine; at least one intermediate gear wheel coupled to the sprocket and the crown and rotatable supported by an intermediate member. Two gear couplings are provided, each of which is equipped with own externally-activated means for command, which gear couplings connect the intermediate member with the frame and the drive shaft.
Description
BACKGROUND of the INVENTIO~ 12 ~
Tlle inverltion relates to a mechallical transmission for drive wheels, in particular in mobile wor . . .
;~.'. : , ~ ; ~
, . . . ~, , -2127 0~
machines.
Specifically but not exclusively the transmission is usefully applied to small mobile work machines, wherein the means for propulsion, usually wheels 05 or tracks, are used mainly for moving masses of small proportions as well as for moving the machine itself, quite slowly, from one work position to another (such as in the case of excavators).
For these purposes generally it is sufficient to use extremely simple and cheap traction means, constituted as a rule by a hydraulic rotary geared motor using the same hydraulic circuit that also activates the tool organs of the machine and which functions at constant or minimally-variable rotation speeds.
Prior art mechanical transmissions for the above-described purpose usually equip a gear mechanism comprising a sprocket, solid to the drive shaft, connected through an idler gear to an internally-cogged crown wheel solid to the hub, with the drive wheel being solidly constrained to the crown. The mechanical transmissions have a fixed gear ratio, so the machine has only one speed, which is the same as the relatively low speed .:.. , : . .. :::: . . . .
~ ' ' ` `:
Tlle inverltion relates to a mechallical transmission for drive wheels, in particular in mobile wor . . .
;~.'. : , ~ ; ~
, . . . ~, , -2127 0~
machines.
Specifically but not exclusively the transmission is usefully applied to small mobile work machines, wherein the means for propulsion, usually wheels 05 or tracks, are used mainly for moving masses of small proportions as well as for moving the machine itself, quite slowly, from one work position to another (such as in the case of excavators).
For these purposes generally it is sufficient to use extremely simple and cheap traction means, constituted as a rule by a hydraulic rotary geared motor using the same hydraulic circuit that also activates the tool organs of the machine and which functions at constant or minimally-variable rotation speeds.
Prior art mechanical transmissions for the above-described purpose usually equip a gear mechanism comprising a sprocket, solid to the drive shaft, connected through an idler gear to an internally-cogged crown wheel solid to the hub, with the drive wheel being solidly constrained to the crown. The mechanical transmissions have a fixed gear ratio, so the machine has only one speed, which is the same as the relatively low speed .:.. , : . .. :::: . . . .
~ ' ' ` `:
2~L27 ~
needed for it to perform its task or move about from one workplace to another.
The main drawback of the known work machines using such mechanical transmissions is that the machines 05 are not truly able to make long journeys under their own power; their speed would render such journeys epic. Hence the machines are u~ually loaded onto other, faster vehicles for such journeys.
PCT publication WO 91/0044 teaches a hub incorporating a planetary gear with two transmission ratios, selectable by means of a hydraulic clutch. This two-stage device is a very laborious solution, being neither highly function nor economical. ~`
SUMMARY of the INVENTION.
The main aim of the present invention is to obviate the above-mentioned drawbacks and limitations in the prior art by providing a mechanical transmission which is simple and economical to construct and apply to small work vehicles and machines, and which enables a simple and rapid variability of the transmission ratio ~.
2~27 0~ ~
between the drive shaft and the drive wheel activating it.
One advantage of the invention is that the speed change can be effected by a simple and rapid 05 manoeuvre.
A further advantageous characteristic of the invention consists in its combining in the same manoeuvring device both a speed-change function and a drive shaft brake.
A still further advantage of the invention is that it achieves its set aims through a mechanical transmission which is easily applicable to work machines already available on the market.
The above aims and more besides are all attained by the invention as it is characterized in the following claims.
HRIEF DESCRIPTION of th~ DRAWINGS.
Further characteristics and advantages of the present invention will better emerge from the detailed description that follows, of an embodiment of the invention, illustrated in the form of a non-limiting example in the accompanying drawings, in which:
.. ~.. . . . . .. , . . . .. .. . - . .
21%7 O~Q
figure 1 is a schematic view, partially sectioned according to an axial plane, of a first embodiment of the invention;
figure 2 i6 a schematic section according to a 05 perpendicular plane to the rotation axi6 of a second embodiment of the invention;
figure 3 is a schematic vertîcal~elevation section of a further embodiment of the invention.
DESCRIPTION of the PREFERRED EMBODIMENTS.
With reference to the figures, 1 denotes a rotary hydraulic motor of a mobile work machine, which activates a drive shaft 8 rotatably supported to a frame 13.
The motor 1 activates one of the drive wheels of a mobile work machine, not evidenced in the figures, through a mechanical transmission comprising a gearing mechanism having a power train, which is the same a~ an epicycloid gearing, provided in a first embodiment with a sun gear, one or more planetary gears, a spider and an external crown wheel.
In the example the sun gear is constituted by a 25 . sprocket 6, centrally situated and keyed on an end ~ ,~ .. . -2 ~ 2 ~ ~ ~
of the drive shaft 8, and representing the drive leader of the gearing. The follower of the gearing mechanism is represented by a crown exhibiting internal teeth 4, coaxial to the shaft 8, while 05 the planetary gears are constituted by intermediate wheels 5 coupled to the sprocket 6 and the crown wheel 4; the spider being constituted by an intermediate member 9 on which the intermediate gearwheels 5 are idly rotatably coupled. The intermediate gearwheels 5 are rotatably coupled on pivots 10 which are solidly connected by pins 15 to the intermediate member 9.
The crown 4 is constrained to the hub 2 bearing the wheel of the vehicle. The hub 2 i8 rotatably coupled through bearings on a frame 13, which frame 13 is in fact none other than the pivot of the wheel, solidly constrained to the motor 1.
The hub 2 exhibits a flange for connecting up to the wheel. A cap 14, coaxial to the crown 4, frontally closes the whole transmission.
The intermediate member 9 can be rotatingly connected with both the frame 13 and the drive shaft 8 by means of two multi-disk gear couplings
needed for it to perform its task or move about from one workplace to another.
The main drawback of the known work machines using such mechanical transmissions is that the machines 05 are not truly able to make long journeys under their own power; their speed would render such journeys epic. Hence the machines are u~ually loaded onto other, faster vehicles for such journeys.
PCT publication WO 91/0044 teaches a hub incorporating a planetary gear with two transmission ratios, selectable by means of a hydraulic clutch. This two-stage device is a very laborious solution, being neither highly function nor economical. ~`
SUMMARY of the INVENTION.
The main aim of the present invention is to obviate the above-mentioned drawbacks and limitations in the prior art by providing a mechanical transmission which is simple and economical to construct and apply to small work vehicles and machines, and which enables a simple and rapid variability of the transmission ratio ~.
2~27 0~ ~
between the drive shaft and the drive wheel activating it.
One advantage of the invention is that the speed change can be effected by a simple and rapid 05 manoeuvre.
A further advantageous characteristic of the invention consists in its combining in the same manoeuvring device both a speed-change function and a drive shaft brake.
A still further advantage of the invention is that it achieves its set aims through a mechanical transmission which is easily applicable to work machines already available on the market.
The above aims and more besides are all attained by the invention as it is characterized in the following claims.
HRIEF DESCRIPTION of th~ DRAWINGS.
Further characteristics and advantages of the present invention will better emerge from the detailed description that follows, of an embodiment of the invention, illustrated in the form of a non-limiting example in the accompanying drawings, in which:
.. ~.. . . . . .. , . . . .. .. . - . .
21%7 O~Q
figure 1 is a schematic view, partially sectioned according to an axial plane, of a first embodiment of the invention;
figure 2 i6 a schematic section according to a 05 perpendicular plane to the rotation axi6 of a second embodiment of the invention;
figure 3 is a schematic vertîcal~elevation section of a further embodiment of the invention.
DESCRIPTION of the PREFERRED EMBODIMENTS.
With reference to the figures, 1 denotes a rotary hydraulic motor of a mobile work machine, which activates a drive shaft 8 rotatably supported to a frame 13.
The motor 1 activates one of the drive wheels of a mobile work machine, not evidenced in the figures, through a mechanical transmission comprising a gearing mechanism having a power train, which is the same a~ an epicycloid gearing, provided in a first embodiment with a sun gear, one or more planetary gears, a spider and an external crown wheel.
In the example the sun gear is constituted by a 25 . sprocket 6, centrally situated and keyed on an end ~ ,~ .. . -2 ~ 2 ~ ~ ~
of the drive shaft 8, and representing the drive leader of the gearing. The follower of the gearing mechanism is represented by a crown exhibiting internal teeth 4, coaxial to the shaft 8, while 05 the planetary gears are constituted by intermediate wheels 5 coupled to the sprocket 6 and the crown wheel 4; the spider being constituted by an intermediate member 9 on which the intermediate gearwheels 5 are idly rotatably coupled. The intermediate gearwheels 5 are rotatably coupled on pivots 10 which are solidly connected by pins 15 to the intermediate member 9.
The crown 4 is constrained to the hub 2 bearing the wheel of the vehicle. The hub 2 i8 rotatably coupled through bearings on a frame 13, which frame 13 is in fact none other than the pivot of the wheel, solidly constrained to the motor 1.
The hub 2 exhibits a flange for connecting up to the wheel. A cap 14, coaxial to the crown 4, frontally closes the whole transmission.
The intermediate member 9 can be rotatingly connected with both the frame 13 and the drive shaft 8 by means of two multi-disk gear couplings
3 and 7, each of which i8 provided with its own command means activatable from the outside.
:-:,~ : - : . ~-: :
:. i........................................ : ::.: , ,:,.. :, . . : : -: ,~ . - :
~,. .:-: ,: ~
~.... .. .
2~2~a~
In detail, the first coupling 3 operates between the internal cylindrical surface of an annular projection 17 made on the frame 13, and the external cylindrical surface of an annular element 05 16 predisposed frontally on the intermediate member 9.
The second coupling 7 operated between the internal cylindrical surface of the annular element 15 and a portion of the external surface of the shaft 8.
The above-mentioned cylindrical surfaces, all coaxially disposed, are provided with longitudinal channels housing the radial teeth exhibited by the di~ks of the couplings 3 and 7.
The ~.lternated arrangement of the disk~ in both couplings 3 and 7 as well as the way they are con6trained are of a usual type.
The couplings 3 and 7 are hydraulically activated by hydraulic cylinders 11 and 12 arranged coaxially in the body 13. The cylinders 11 and 12 are advantageously supplied by the same pressurised oil source as the motor 1.
The cylinders 11 and 12 can be constituted by a series of small cylinders arranged on coaxial circumferences, or, as in the example, can be 2~2r~ Or~ ~
coaxially-disposed annular cylinders.
In a second embodiment, illustrated in figure 2, the gearing mechanism comprises an idler gear 18, interposed between each intermediate gear wheel 5 05 and the sprocket 6 and freely rotatingly coupled on the intermediate member 9 by a pivot 18'. In this embodiment the insertion of the idler gear 18 causes (with respect to the embodiment of figure 1) an inversion of the rotation direction of the gears 5 and, subsequently, the crown 4.
Figure 3 6hows a detail relating to a third embodiment of means for commanding the couplings 3 and 7, involving u~e of double-acting cylinders 11 and 12 equipped with pistons 11' and 12'. The cylinders 11 and 12 are supplied by delivery pipes 19 and 20: pressurised oil sent through the pipes 19 or 20 acts on the pistons 11' and 12' and causes the respective couplings 3 and 7 to disengage. Connection pipes 21 and 22 are provided between the cylinders 11 and 12 to link the front chamber of the cylinder 11 with the back chamber of the other cylinder 12, and the front chamber of cylinder 12 with the back chamber of cylinder 11.
Elastic element6 23 and 24 also act on the pistons 11' and 12~ to engage the couplings 3 and 7 as ~,~",, 12~
well as to function as parking brakes, since absence of oil in the pipes 19 and 20 causes the elastic elements 23 and 24 to keep the couplings 3 and 7 engaged at a predetermined pressure.
05 Engagement of coupling 3, commanded by activating annular cylinder 11, produces solidarity between the intermediate member 9 and the frame 13.
Engagement of coupling 7, commanded by annular cylinder 12, creates solidarity between the intermediate member 9 and the 6haft 8. Cylinders 11 and 12 can be piloted by a single hydraulic distributor able to send pres6urised liquid to one or the other of the circuit branches connected to the cylinders 3 and 7. The hydraulic distributor can be of the four-way three-position type, with an open centre, in which the four ways comprise: a ; connection with the circuit branch connected to cylinder 11; a connection with the circuit branch connected to cylinder 12; the inlet of the pressurised liquid, and the outlet of the same.
The three distributor positions are:
a) coupling 7 engaged (intermediate member 9 solid to the shaft 8) and coupling 3 disengaged;
b) coupling 3 engaged (intermediate member 9 solid ~ 25 to the frame 13) and coupling 7 disengaged;
.~ .
. . - ::
;", , , - - - ~ . . , . ,.. ~ .: ~-. : . -2~27 nr~3 c) both couplings 3 and 7 engaged ~shaft 8 solid to the frame 13). -The three above configurations correspond ~ respectively to:
1 05 a) fast speed with unitary transmission ratioI between the shaft 8 and hub 2, utilizable for'~ vehicle movement from one workplace to another;
b) 810w speed, for u~e during work operations;
c) brake.
By acting on a single command organ it is possible to govern the speed of the mobile work machine by changing the speed or operating the brake.
An advantageous characteristic of the invention i8 that apart from the three above configurations, a fourth, free one is possible, wherein both the couplings 3 and 7 are disengaged.
"~?
:-:,~ : - : . ~-: :
:. i........................................ : ::.: , ,:,.. :, . . : : -: ,~ . - :
~,. .:-: ,: ~
~.... .. .
2~2~a~
In detail, the first coupling 3 operates between the internal cylindrical surface of an annular projection 17 made on the frame 13, and the external cylindrical surface of an annular element 05 16 predisposed frontally on the intermediate member 9.
The second coupling 7 operated between the internal cylindrical surface of the annular element 15 and a portion of the external surface of the shaft 8.
The above-mentioned cylindrical surfaces, all coaxially disposed, are provided with longitudinal channels housing the radial teeth exhibited by the di~ks of the couplings 3 and 7.
The ~.lternated arrangement of the disk~ in both couplings 3 and 7 as well as the way they are con6trained are of a usual type.
The couplings 3 and 7 are hydraulically activated by hydraulic cylinders 11 and 12 arranged coaxially in the body 13. The cylinders 11 and 12 are advantageously supplied by the same pressurised oil source as the motor 1.
The cylinders 11 and 12 can be constituted by a series of small cylinders arranged on coaxial circumferences, or, as in the example, can be 2~2r~ Or~ ~
coaxially-disposed annular cylinders.
In a second embodiment, illustrated in figure 2, the gearing mechanism comprises an idler gear 18, interposed between each intermediate gear wheel 5 05 and the sprocket 6 and freely rotatingly coupled on the intermediate member 9 by a pivot 18'. In this embodiment the insertion of the idler gear 18 causes (with respect to the embodiment of figure 1) an inversion of the rotation direction of the gears 5 and, subsequently, the crown 4.
Figure 3 6hows a detail relating to a third embodiment of means for commanding the couplings 3 and 7, involving u~e of double-acting cylinders 11 and 12 equipped with pistons 11' and 12'. The cylinders 11 and 12 are supplied by delivery pipes 19 and 20: pressurised oil sent through the pipes 19 or 20 acts on the pistons 11' and 12' and causes the respective couplings 3 and 7 to disengage. Connection pipes 21 and 22 are provided between the cylinders 11 and 12 to link the front chamber of the cylinder 11 with the back chamber of the other cylinder 12, and the front chamber of cylinder 12 with the back chamber of cylinder 11.
Elastic element6 23 and 24 also act on the pistons 11' and 12~ to engage the couplings 3 and 7 as ~,~",, 12~
well as to function as parking brakes, since absence of oil in the pipes 19 and 20 causes the elastic elements 23 and 24 to keep the couplings 3 and 7 engaged at a predetermined pressure.
05 Engagement of coupling 3, commanded by activating annular cylinder 11, produces solidarity between the intermediate member 9 and the frame 13.
Engagement of coupling 7, commanded by annular cylinder 12, creates solidarity between the intermediate member 9 and the 6haft 8. Cylinders 11 and 12 can be piloted by a single hydraulic distributor able to send pres6urised liquid to one or the other of the circuit branches connected to the cylinders 3 and 7. The hydraulic distributor can be of the four-way three-position type, with an open centre, in which the four ways comprise: a ; connection with the circuit branch connected to cylinder 11; a connection with the circuit branch connected to cylinder 12; the inlet of the pressurised liquid, and the outlet of the same.
The three distributor positions are:
a) coupling 7 engaged (intermediate member 9 solid to the shaft 8) and coupling 3 disengaged;
b) coupling 3 engaged (intermediate member 9 solid ~ 25 to the frame 13) and coupling 7 disengaged;
.~ .
. . - ::
;", , , - - - ~ . . , . ,.. ~ .: ~-. : . -2~27 nr~3 c) both couplings 3 and 7 engaged ~shaft 8 solid to the frame 13). -The three above configurations correspond ~ respectively to:
1 05 a) fast speed with unitary transmission ratioI between the shaft 8 and hub 2, utilizable for'~ vehicle movement from one workplace to another;
b) 810w speed, for u~e during work operations;
c) brake.
By acting on a single command organ it is possible to govern the speed of the mobile work machine by changing the speed or operating the brake.
An advantageous characteristic of the invention i8 that apart from the three above configurations, a fourth, free one is possible, wherein both the couplings 3 and 7 are disengaged.
"~?
Claims (8)
1. A mechanical transmission for drive wheels, especially for mobile work machines, comprising:
- a sprocket keyed on a drive shaft rotatably supported on a frame;
- a crown wheel having internal cogging, being coaxial to the drive shaft and fixed to a hub of a work machine road wheel;
- at least one intermediate cogwheel coupled to the sprocket and to the crown and rotatingly supported by an intermediate member;
a first gear coupling for connecting the intermediate member to the frame;
a second gear coupling, for connecting the intermediate member to the drive shaft; each of the first and second gear couplings being externally commandable.
- a sprocket keyed on a drive shaft rotatably supported on a frame;
- a crown wheel having internal cogging, being coaxial to the drive shaft and fixed to a hub of a work machine road wheel;
- at least one intermediate cogwheel coupled to the sprocket and to the crown and rotatingly supported by an intermediate member;
a first gear coupling for connecting the intermediate member to the frame;
a second gear coupling, for connecting the intermediate member to the drive shaft; each of the first and second gear couplings being externally commandable.
2. A mechanical transmission as in claim 1, wherein the first and the second gear couplings are multi-disk gear couplings.
3. A mechanical transmission as in claim 2, comprising an annular element, coaxial to the drive shaft, frontally projecting from the intermediate member and provided with an external cylindrical surface and an internal cylindrical surface; the external cylindrical surface facing an internal cylindrical surface of an annular projection on the frame and the internal cylindrical surface facing an external cylindrical surface of the drive shaft; all of said cylindrical surfaces exhibiting longitudinal channels for slide-coupling with radial teeth on disks of the gear couplings.
4. A mechanical transmission as in claim 2, comprising two annular hydraulic cylinders disposed circumferentially and coaxially on the frame, and being predisposed for operating on the disks of the gear couplings.
5. A mechanical transmission as in claim 4, wherein the cylinders are commanded by a single command organ constituted by a four-way and three-position hydraulic distributor.
6. A mechanical transmission as in claim 4, wherein the cylinders are of a double-acting type and are supplied respectively by delivery pipes, a delivery of a pressurised fluid acting on respective pistons to cause a disengagement of the gear couplings; connecting pipes being provided to cross-link chambers of the cylinders.
7. A mechanical transmission as in claim 6, comprising at least one elastic element for each cylinder, which elastic element is predisposed to operate on a piston of a cylinder to engage a gear coupling.
8. A mechanical transmission as in claim 1, wherein an idler gear is interposed between each of the at least one intermediate cogwheel and the sprocket;
said idler gear being rotatably coupled on the intermediate member.
said idler gear being rotatably coupled on the intermediate member.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ITMO930034A IT1262598B (en) | 1993-03-23 | 1993-03-23 | FIXING DEVICE FOR CERAMIC TILES, MARBLE SLABS, GRANITE AND OTHER NATURAL OR ARTIFICIAL MATERIAL FOR THE CREATION OF VENTILATED CLADDINGS. |
| ITMO930099A IT1262648B (en) | 1993-07-30 | 1993-07-30 | Mechanical transmission for driving wheels, particularly for self-propelled machine tools |
| ITM093A000099 | 1993-07-30 | ||
| ITM093A000034 | 1994-03-16 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2127050A1 true CA2127050A1 (en) | 1995-01-31 |
Family
ID=26331721
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2127050 Abandoned CA2127050A1 (en) | 1993-03-23 | 1994-06-29 | Mechanical transmission for drive wheels, especially for mobile work machines |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN1041550C (en) |
| CA (1) | CA2127050A1 (en) |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3770075A (en) * | 1972-03-20 | 1973-11-06 | Eaton Corp | Free wheeling 2-speed motor wheel |
| DE2758556A1 (en) * | 1977-12-23 | 1979-07-05 | Mannesmann Ag | Hydrostatic drum drive for vehicle wheel - has two planetary gear trains with concentric hollow shafts couplable to input |
| US4162713A (en) * | 1978-04-03 | 1979-07-31 | Otis Engineering Corporation | Planetary transmission with hydraulic engagement and disengagement |
| US4414862A (en) * | 1980-04-29 | 1983-11-15 | Ford Motor Company | Planetary gear arrangement for a continuously variable transmission |
| US5024636A (en) * | 1989-06-27 | 1991-06-18 | Fairfield Manufacturing Company, Inc. | Planetary wheel hub |
| US5152725A (en) * | 1990-09-28 | 1992-10-06 | United States Of America | Compact, two-speed, reversible drive mechanism |
-
1994
- 1994-06-29 CA CA 2127050 patent/CA2127050A1/en not_active Abandoned
- 1994-07-28 CN CN94114991A patent/CN1041550C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1101609A (en) | 1995-04-19 |
| CN1041550C (en) | 1999-01-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5525115A (en) | Mechanical transmission for drive wheels, especially for mobile work machines | |
| CA1302736C (en) | Countershaft transmission | |
| US8172714B2 (en) | Speed changing transmission apparatus | |
| US8806864B2 (en) | Transmission | |
| US7537536B2 (en) | Two speed gearbox | |
| US5743142A (en) | Multi-ratio power-shiftable reversing gear | |
| CN101291825B (en) | Speed change transmission device | |
| JP4372072B2 (en) | Variable speed transmission | |
| US4676116A (en) | Countershaft transmission | |
| JP4740174B2 (en) | Variable speed transmission | |
| US4614133A (en) | Vehicle transmission having countershaft and planetary portions | |
| US6257080B1 (en) | Power-Shifted transmission for industrial vehicles | |
| CA1061602A (en) | Multi-speed planetary gear | |
| US4446758A (en) | Planetary transmission | |
| US4414862A (en) | Planetary gear arrangement for a continuously variable transmission | |
| US6935986B2 (en) | Two speed gearbox | |
| JPH02501764A (en) | countershaft transmission | |
| US5254056A (en) | Toroidal type continuously variable transmission | |
| US4192409A (en) | Clutch mechanism for winch | |
| US5011465A (en) | Wide speed-range multi-speed power shift transmission | |
| US4658673A (en) | Planetary transmission | |
| CA1177282A (en) | Planetary transmission | |
| CA2127050A1 (en) | Mechanical transmission for drive wheels, especially for mobile work machines | |
| KR102666858B1 (en) | Power transfer device, transmission and fixed structure of axle case | |
| JP5639445B2 (en) | Power transmission structure of work vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Dead |