GB1586133A - Creation of Inventions and Patents with Artificial Intelligence

GB1586133A – Fluid drive assembly including a control system
– Google Patents

GB1586133A – Fluid drive assembly including a control system
– Google Patents
Fluid drive assembly including a control system

Download PDF
Info

Publication number
GB1586133A

GB1586133A
GB14123/78A
GB1412378A
GB1586133A
GB 1586133 A
GB1586133 A
GB 1586133A
GB 14123/78 A
GB14123/78 A
GB 14123/78A
GB 1412378 A
GB1412378 A
GB 1412378A
GB 1586133 A
GB1586133 A
GB 1586133A
Authority
GB
United Kingdom
Prior art keywords
valve member
fluid
chamber
actuator
source
Prior art date
1977-07-05
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.)

Expired

Application number
GB14123/78A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Caterpillar Inc

Original Assignee
Caterpillar Tractor Co
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.)
1977-07-05
Filing date
1978-04-11
Publication date
1981-03-18

1978-04-11
Application filed by Caterpillar Tractor Co
filed
Critical
Caterpillar Tractor Co

1981-03-18
Publication of GB1586133A
publication
Critical
patent/GB1586133A/en

Status
Expired
legal-status
Critical
Current

Links

Espacenet

Global Dossier

Discuss

Classifications

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16H—GEARING

F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing

F16H61/38—Control of exclusively fluid gearing

F16H61/40—Control of exclusively fluid gearing hydrostatic

F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation

F16H61/456—Control of the balance of torque or speed between pumps or motors

B—PERFORMING OPERATIONS; TRANSPORTING

B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS

B62D—MOTOR VEHICLES; TRAILERS

B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like

B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides

B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source

B62D11/10—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears

B62D11/14—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source

B62D11/18—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source the additional power supply being supplied hydraulically

B62D11/183—Control systems therefor

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F04—POSITIVE – DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS

F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS

F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 – F04B47/00

F04B49/002—Hydraulic systems to change the pump delivery

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16H—GEARING

F16H61/38—Control of exclusively fluid gearing

F16H61/40—Control of exclusively fluid gearing hydrostatic

F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity

F16H61/423—Motor capacity control by fluid pressure control means

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16H—GEARING

F16H61/38—Control of exclusively fluid gearing

F16H61/40—Control of exclusively fluid gearing hydrostatic

F16H61/46—Automatic regulation in accordance with output requirements

Description

PATENT SPECIFICATION
( 21) Application No 14123/78 ( 22) Filed 11 April 19 ^ ( 31) Convention Application No.
813 029 ( 32) Filed 5 Jul P ( 33) United States of America (US) x O ( 44) Complete Specification published 18 March 1981
00 ( 51) INT CL 3 F 16 H 39/46 U 4 ( 52) Index of acceptance F 2 W 026 154 178 186 194 22 ‘8 250 252 324 380 388 390 C 3 ( 72) Inventors CYRIL WILLIAM HABIGER LEON EUGENE HICKS ( 11) 1 586 133 ‘1977 in ( 54) A FLUID DRIVE ASSEMBLY INCLUDING A CONTROL SYSTEM ( 71) We, CATERPILLAR TRACTOR CO, a corporation organized and existing under the laws of the State of California, United States of America, of 100 N E Adams Street, Peoria, Illinois, 61629, United States of America do hereby declare the invention, for which we pray that a patent may be granted to us and the method by which it is to be performed, to be particularly described in and by the following statement:-
The invention relates to a fluid drive assembly.
Hydrostatic transmissions occasionally have a variable displacement motor or motors positionable at either a minimum or a maximum position for fast or slow output speeds respectively One of the problems associated with such transmissions is that of providing a control system which automatically shifts the transmission to the slow speed when the output pressure of the pumps gets too high and prevents the transmission from being shifted from the slow speed to the fast speed when the output pressure is too high Another problem is that once the transmission is shifted to the slow speed in response to a high output pressure of the pumps, the transmission should remain in the slow speed until the output pressure decreases to an intermediate pressure level It is desirable under some conditions to provide manual control for selectively shifting the transmission to either the slow or fast speed with the control system capable of shifting the transmission to the slow speed automatically when the output pressure gets too high.
According to the present invention a fluid drive assembly comprises a pump; a variable displacement two-speed motor having an actuator for controlling the displacement of the motor, the actuator being movable between a first position at which the displacement of the motor is at a preselected maximum and a second position at which the displacement of the motor is at a preselected minimum; a fluid circuit connecting the pump to the motor; a source of fluid, at a preselected pressure level in use; a valve connected to the source of fluid and to the actuator for controlling fluid flow therebetween, the valve having a valve member movable between a first position at which fluid flow to the actuator is blocked and a second position at which 55 fluid flow to the actuator is enabled; first means for moving the valve member to the first position in response to the fluid pressure in the fluid circuit exceeding a preselected value; and second means 60 for retaining the valve member in the first position until the fluid pressure in the fluid circuit decreases from the preselected value to a second preselected value.
Preferably, the second means includes 65 third means for continuously urging the valve member toward the second position, and fourth means for applying a force to the valve member in a direction urging the valve member toward the second position 70 only when the valve member is in the second position.
Four examples of fluid drive assemblies according to the invention will now be described with reference to the accompanying 75 drawings in which:Figure 1 is a diagrammatic view of a fluid drive assembly including a first control system with portions shown in section for illustrative convenience; and, 80 Figure 2, 3 and 4 are alternative embodiments of the control system.
A fluid drive assembly, such as a hydrostatic transmission 11, has a pair of variable displacement overcenter pumps 12 and a 85 pair of variable displacement two-speed motors 13 Each of the pumps is connected to one of the motors through a fluid circuit 14 including a pair of conduits 16, 17 Each of the pumps has an actuator 18 connected 90 to a pump control means 19 for controlling the displacement of the pumps Each of the motors has an actuator 21 for controlling the displacement of the motor The acuator 21 is movable between a first position at 95 which the displacement of the motor is at a preselected maximum and a second position at which the displacement of the motor is at a preselected minimum With the motor at its maximum displacement position, the 100 378 1 586 133 motor is operated at its slow speed and when the motor is at its minimum displacement, it operates at its fast speed.
A source of fluid such as a pump 22, draws fluid from a tank and delivers fluid through a conduit 23 to the pump control means 19 which maintains the pressure in the conduit 23 at a first preselected pressure level, for example approximately 350 psi The pump 22 is independent of the pumps 12.
A valve 26 includes a multi-part body 27 having a bore 28 therein A first passage 29 connects the bore with the conduit 23 and a second passage 31 connects the bore to the actuators 21 The first passage 29 can include an annulus 32 and a port 33.
The second passage 31 can include a port 34, a conduit 36, an orifice 37 positioned in the conduit 36 and a means 38 positioned within the conduit for dividing the fluid flow substantially equally between the actuators 21 of the motors 13.
A valve member 39 is slidably positioned in the bore 28 and has an annular groove 41 positioned intermediate first and second end portions 42, 43 A chamber 44 is formed in the body at the first end portion 42 of the valve member and is connected to the annulus 32 of the first passage 29 through a third passage 46 which includes passages 47, 48 and a connecting line 49.
Preferably, the third passage 46 is formed by suitable passages within the body.
The valve member 39 is movable between first and second positions At the first position, the annulus 32 of the first passage 29 is blocked from communication with the port 34 of the second passage 31 and the port 34 is in communication with a drain port 51 through the annulur groove 41 At the second position, the port 33 of the first passage 29 is in communication with the port 34 of the second passage 31 through the annular groove 41 and port 34 is blocked from communication with the drain port 51.
A bore 52 in the first end portion 42 of the valve member 39 slidably receives a plunger 53 defining a chamber 54 at the inner end thereof A passageway 56 in the valve member connects the chamber 54 with the annular groove 41 A stop member or pin 57 extends through an aperture in the plunger 53 Another stop member or washer 58 is suitably fixed to the body and positioned in the pathway of the end portion 42 of valve member 39 for stopping movement thereof at the first position and positioned in the pathway of the pin 57 for stopping movement of the plunger 53 as the valve member 39 is moved to its second position A means 59 is connected to valve member 39 for automatically moving the valve member to the first position in response to the fluid pressure in one of the conduits 16, 17 exceeding a second preselected pressure level Mains 59 can be an actuator 61 having a piston 62 slidably positioned within a 70 chamber 63 and having one end in abutment with the second end portion 43 of valve member 39 The chamber 63 is connected to a ball resolver 64 which in turn is connected to a pair of ball resolvers 66 Each 75 of the ball resolvers 66 are positioned between respective pairs of conduits 16, 17 in a manner that the highest pressure in any of the conduits is transmitted to chamber 63 80 A spring 67 is positioned at the second end portion 43 for urging the valve member 39 toward its first position.
Referring now to Fig 2, another embodiment has a two-position, three-way solenoid 85 actuated valve 68 positioned within the line 49 ‘ of the third passage 46 ‘ between passages 47 ‘, 48 ‘ and is connected to conduit 36 between the orifice 37 ‘ and means 38, Fig 1 The valve 68 is movable between a 90 first position at which chamber 44 ‘ is in communication with the conduit 36 and passage 47 ‘ is blocked from communication with passage 48 ‘ and a second position at which passage 47 ‘ is in communication with 95 passage 48 ‘ and passage 48 ‘ is blocked from communication with the conduit 36 Alternatively, the valve 68 can be of a type which is manually or fluid actuated.
Referring to Fig 3, another embodi 100 ment has a two-position, two-way solenoid actuated valve 71 positioned within the line 49 ” between passages 47 ” and 48 ” A port 72 connects the chamber 44 ” with the conduit 36 through an orifice 73 The valve 105 71 is movable between a first position at which fluid flow through the line 49 is blocked and a second position at which fluid can flow through the line 49 ” from passage 47 ” to passage 48 ” 110 Referring now to Fig 4, another embodiment of the valve means 26 “‘ has a spring 74 positioned within the chamber 44 “‘ for urging the valve member 39 “‘ to the second position A passageway 56 “‘ connects the 115 annular groove 41 “‘ directly with the chamber 44 “‘.
In the operation of the embodiment of Fig 1, when there is no fluid pressure in conduit 23, such as when the pump 22 is 120 not being driven, the spring 67 will bias the valve member 39 to the first position shown When the pump 22 is driven, such as when the vehicle engine is started and fluid pressure builds up in the conduit 23 125 to the first preselected pressure level, fluid flows through port 33, annulus 32, passage 47, line 49, passage 48 and into the chamber 44 Since at start up of the engine there is no fluid pressure in the conduits 16, 17 130 1 586 133 and hence no fluid pressure in the chamber 63, the fluid pressure in chamber 44 acting against the end portion 42 of the valve member 39 overcomes the bias of spring 67 and moves the valve member to the left to the second position This force urging the valve member to the second position is applied continuously while the pump 22 is running At this position of the valve member, fluid is delivered to the actuators 21 of the motors 13 for moving the motors to their second position Likewise, at this position of the valve member 39, fluid flows through passageway 56 into chamber 54 thereby adding an additional force urging the valve member to the second position.
When the fluid pressure in any one of the conduits 16, 17 exceeds a second preselected pressure level, for example approximately 4000 psi, the fluid pressure in the chamber 63 acting on the piston 62 is sufficient to overcome the force exerted on the valve member 39 by the fluid pressure in chambers 44, 54 and moves the valve member 39 to the right to its first position At this position, communication between ports 33, 34 is blocked and port 34 is connected with the drain port 51 with the net result being that the actuators 21 are moved to their second position at which the displacement of the motors is at maximum for obtaining slow speed.
At the first position of the valve member 39, the chamber 54 is also vented to the drain port 51 thereby removing a portion of the biasing force urging the valve member toward its second position Thus, the valve member is retained in the first position until the highest fluid pressure in the conduits 16, 17 decreases to below a third preselected pressure level, for example approximately 2100 psi With the fluid pressure in the conduit and thus chamber 63 below the third preselected pressure level, the force of the fluid pressure in chamber 44 acting on the end of the valve member 39 is sufficient to move the valve member 39 back to its second position.
The operation of the embodiment of Fig.
2 is similar to that described above with the exception that the solenoid valve 68 in its first position shown blocks fluid flow through the line 49 ‘ of the third passage 46 ‘ to the chamber 44 ‘ and connects chamber 44 ‘ to the drain port 51 ‘ Thus, upon start up of the engine, the valve member 39 ‘ will remain at the first position so that the motors 13 remain at their maximum displacement position.
Shifting the solenoid valve 68 to its second position passes fluid through line 49 ‘ to the chamber 44 ‘ The force generated by the pressurized fluid in chamber 44 ‘ against the end of the valve member 39 ‘ moves the valve member 39 ‘ to its second position However, once the valve member is moved to its second position, shifting the solenoid valve 68 back to its first position will not cause valve member 39 ‘ to be shifted back to its first position since cham 70 ber 44 ‘ is connected to the conduit 36 through the valve 68 Thus, the valve member 39 ‘ will remain in the second position until it is moved to the first position in response to the fluid pressure in any one of 75 the conduits 16, 17 exceeding the second preselected pressure level or in response to stopping the pump 22 such as when the engine is stopped.
The operation of the embodiment of Fig 80 3 is similar to that described above in conjunction with Fig 2 in that the valve member 39 ” will remain in the first position at the first position of the solenoid valve 71 due to the solenoid valve blocking fluid flow 85 through the line 49 ” from annulus 32 ” to the chamber 44 ” Shifting the solenoid valve 71 to its second position passes fluid through the line 49 ” to chamber 44 ” thereby moving the valve member 39 ” to its second 90 position However, at the second position of the valve member, since the chamber 44 ” is connected to the conduit 36 through the port 72 and orifice 73, the valve member 39 ” will remain in its second position even 95 though the solenoid valve 71 is shifted back to its first position As with the first two embodiments, the valve member 39 ” will be shifted to its first position in response to the fluid pressure in any one of the 100 conduits 16, 17 exceeding the second preselected pressure level.
In the operation of the embodiment of Fig 4, the valve member 39 “‘ is normally biased to the second position shown in the 105 drawings by the spring 74 Thus, at start up, the valve member 39 “‘ is already in the second position At the second position of the valve member 39 “, pressurized fluid from the conduit 23 passes through the pas 110 sageway 56 ” into the chamber 44 “‘ thereby adding to the force urging the valve member 39 “‘ to the left or second position.
When the fluid pressure in any one of the conduits 16, 17 exceeds the second pre 115 selected pressure level, the valve member 39 “‘ is shifted automatically to the first position At the first position of the valve member, communication between the annulus 32 “‘ and the passageway 56 ” is blocked 120 and the chamber 44 “‘ is vented to the drain port 51 “‘ Thus, the force of piston 62 “‘ on the valve member will retain the valve member at the first position until the highest fluid pressure in the conduits 16, 17 de 125 creases to the third preselected pressure level With the fluid pressure in the chamber 63 “‘ below the third preselected pressure level, the force of the spring 74 is sufficient to overcome the force of the piston 130 1 586 133 and moves the valve member back to its second position.

Claims (1)

WHAT WE CLAIM IS:-
1 A fluid drive assembly comprising a pump; a variable displacement two-speed motor having an actuator for controlling the displacement of the motor, the actuator being movable between a first position at which the displacement of the motor is at a preselected maximum and a second position at which the displacement of the motor is at a preselected minimum; a fluid circuit connecting the pump to the motor; a source of fluid, at a preselected pressure level in use; a valve connected to the source and to the actuator for controlling fluid flow therebetween, the valve having a member movable between a first position at which fluid flow to the actuator is blocked and a second position at which fluid flow to the actuator is enabled; first means for moving the valve member to the first position in response to the fluid pressure in the fluid circuit exceeding a preselected value; and second means for retaining the valve member in the first position until the fluid pressure in the fluid circuit decreases from the preselected value to a second preselected value.
2 An assmbly according to claim 1, wherein the second means includes third means for continuously urging the valve member toward the second position, and fourth means for applying a force to the valve member in a direction urging the valve member toward the second position only when the valve member is in the second position.
3 An assembly according to claim 2, wherein the valve member has first and second end portions, the third means including a first chamber at the first end of the valve member; the first chamber being connected to the source of fluid, the fourth means including an annular groove in the valve member intermediate the first and second end portions, a bore in the first end portion of the valve member, a plunger slidably positioned within the first bore and extending into the first chamber, a second chamber at the inner end of the second bore, a passageway connecting the annular groove with the second chamber, the annular groove being located to connect the source of fluid with the passageway and actuator at the second position of the valve member and for communicating the actuator and passageway with a drain at the first position.
4 An assembly according to claim 3, including a first stop member connected to the plunger, a second stop member positioned in the pathway of the valve member for limiting movement of the valve member 65 at the first position and in the pathway of the first stop member for limiting movement of the plunger in response to the valve member being moved to the second position 70 An assembly according to claim 3 or claim 4, including a further valve connected to the source of fluid, the actuator, and the first chamber, the further valve being movable between a first position at which the 75 first chamber is blocked from communication with the source of fluid and is in communication with the actuator and a second position at which the first chamber is blocked from communication with actuator 80 and is in communication with the source of fluid.
6 An assembly according to claim 3 or claim 4, including a further valve connected to the source of fluid and to the first cham 85 ber and being movable between a first position at which the source of fluid is blocked from communication with the first chamber and a second position at which the source of fluid is in communication with the first 90 chamber.
7 An assembly according to claim 2, wherein the third means includes a spring; the fourth means includes a first chamber at one end of the valve member, an annular 95 groove in the valve member, a passageway in the valve member connecting the annular groove with the first chamber, the annular groove being positioned at a location for communicating the source of fluid with the 100 passageway and the actuator at the second position of the valve member and for communicating the passageway and the actuator with a drain at the first position of the valve member 105 8 An assembly according to claim 2, wherein the first means includes a piston and a first chamber, the first chamber being connected to the fluid circuit and the piston being positioned to cause movement of the 110 valve member toward the first position.
9 An assembly according to claim 1, substantially as described with reference to any of the examples shown in the accompanying drawings 115 For the Applicants:
GILL, JENNINGS & EVERY, Chartered Patent Agents, 53 to 64 Chancery Lane, London WC 2 A 1 HN Printed for Her Majesty’s Stationery Office by The Tweeddale Press Ltd, Berwick-upon-Tweed, 1981.
Published at the Patent Office, 25 Southampton Buildings, London, WC 2 A l AY, from which copies may be obtained.

GB14123/78A
1977-07-05
1978-04-11
Fluid drive assembly including a control system

Expired

GB1586133A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

US05/813,029

US4096694A
(en)

1977-07-05
1977-07-05
Control system for a fluid drive

Publications (1)

Publication Number
Publication Date

GB1586133A
true

GB1586133A
(en)

1981-03-18

Family
ID=25211262
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB14123/78A
Expired

GB1586133A
(en)

1977-07-05
1978-04-11
Fluid drive assembly including a control system

Country Status (6)

Country
Link

US
(1)

US4096694A
(en)

JP
(1)

JPS5417467A
(en)

CA
(1)

CA1089327A
(en)

DE
(1)

DE2829368A1
(en)

FR
(1)

FR2396901B1
(en)

GB
(1)

GB1586133A
(en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

WO1981001311A1
(en)

1979-11-01
1981-05-14
Caterpillar Tractor Co
Fluid motor control system providing speed change by combination of displacement and flow control

US4354420A
(en)

1979-11-01
1982-10-19
Caterpillar Tractor Co.
Fluid motor control system providing speed change by combination of displacement and flow control

US4635441A
(en)

1985-05-07
1987-01-13
Sundstrand Corporation
Power drive unit and control system therefor

US4779419A
(en)

1985-11-12
1988-10-25
Caterpillar Inc.
Adjustable flow limiting pressure compensated flow control

FR2625541B1
(en)

1987-12-31
1992-02-21
Armef

HYDROSTATIC TRANSMISSION

JPH02225879A
(en)

1989-02-27
1990-09-07
Shin Caterpillar Mitsubishi Ltd
Running speed shift device of liquid pressure running vehicle

JPH0745652Y2
(en)

1990-03-09
1995-10-18
新キャタピラー三菱株式会社

Travel speed switching device

JP2818474B2
(en)

1990-07-04
1998-10-30
日立建機株式会社

Hydraulic drive circuit

USRE38632E1
(en)

1995-10-25
2004-10-19
Caterpillar Paving Products Inc
Propulsion control apparatus and method for a paver

US5787374A
(en)

1995-10-25
1998-07-28
Caterpillar Paving Products, Inc.
Propulsion control apparatus and method for a paver

US8500587B2
(en)

2010-12-20
2013-08-06
Caterpillar Inc.
Multiple-variator control for split power CVT and hydrostatic transmissions

Family Cites Families (5)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US3119414A
(en)

1960-06-29
1964-01-28
Auto Transmissions Ltd
Means for automatically controlling speed changes in variable speed power transmission mechanisms

DE1528473B2
(en)

1966-02-11
1974-10-17
Linde Ag, 6200 Wiesbaden

Setting device for an adjustable hydraulic motor

US3411297A
(en)

1967-03-20
1968-11-19
Sundstrand Corp
Hydrostatic transmission

US3768263A
(en)

1971-12-27
1973-10-30
Hyster Co
Hydraulic control system for two-speed winch

US3972186A
(en)

1975-02-28
1976-08-03
Caterpillar Tractor Co.
Speed override control for hydraulic motors

1977

1977-07-05
US
US05/813,029
patent/US4096694A/en
not_active
Expired – Lifetime

1978

1978-04-11
GB
GB14123/78A
patent/GB1586133A/en
not_active
Expired

1978-04-25
CA
CA301,887A
patent/CA1089327A/en
not_active
Expired

1978-05-23
JP
JP6068278A
patent/JPS5417467A/en
active
Granted

1978-06-21
FR
FR7818574A
patent/FR2396901B1/en
not_active
Expired

1978-07-04
DE
DE19782829368
patent/DE2829368A1/en
active
Granted

Also Published As

Publication number
Publication date

CA1089327A
(en)

1980-11-11

DE2829368C2
(en)

1992-03-12

DE2829368A1
(en)

1979-01-18

JPS5417467A
(en)

1979-02-08

JPS6244142B2
(en)

1987-09-18

US4096694A
(en)

1978-06-27

FR2396901B1
(en)

1985-11-08

FR2396901A1
(en)

1979-02-02

Contact information