US3849985A - Control system for multiple motor hydraulic means - Google Patents

Control system for multiple motor hydraulic means Download PDF

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Publication number
US3849985A
US3849985A US00311791A US31179172A US3849985A US 3849985 A US3849985 A US 3849985A US 00311791 A US00311791 A US 00311791A US 31179172 A US31179172 A US 31179172A US 3849985 A US3849985 A US 3849985A
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United States
Prior art keywords
valve
fluid
discharge
motors
motor
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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 - Lifetime
Application number
US00311791A
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English (en)
Inventor
F Ratliff
J Mcburnett
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.)
TYRONE HYDRAULICS INC US
Dana Inc
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Tyrone Hydraulics Inc
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Publication date
Application filed by Tyrone Hydraulics Inc filed Critical Tyrone Hydraulics Inc
Priority to US00311791A priority Critical patent/US3849985A/en
Priority to JP48130310A priority patent/JPS5760486B2/ja
Priority to GB5614273A priority patent/GB1454407A/en
Application granted granted Critical
Publication of US3849985A publication Critical patent/US3849985A/en
Assigned to DANA CORPORATION A CORP OF VA reassignment DANA CORPORATION A CORP OF VA MERGER (SEE DOCUMENT FOR DETAILS). Assignors: TYRONE HYDRAULICS, INC. A DE CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/08—Driving gear incorporating fluid motors

Definitions

  • This invention relates to fluid pressure control systems for power means having first and second hydraulic motors both connected to deliver power to a power shaft, the control system providing alternatively for operation of one motor only or for operation of both motors.
  • the equipment of the present invention is especially adapted to employment in load lifting equipment as employed for example, in various winches, for instance in winch drives such as those used on hydraulic cranes.
  • the present invention is concerned with a system of the general kind above referred to and has as a major objective the provision of a control system which insures a gradual changeover from either condition ofoperation to the other, thereby virtually eliminating abrupt or jolting action in the handling of loads, especially at those times when a transition is made from one condition of operation to the other.
  • the invention also provides for changeover by means of a selectively controllable valve mechanism which has no neutral or intermediate setting in which neither of the two operating conditions prevails. This is in contrast to certain prior control systems for this general purpose, in which the control valve has a neutral condition which may even permit momentary dropping of the load.
  • control system and the various valve devices employed therein are arranged with reference to the motors so that the control system and the motors are reversible, and will provide the desired operating characteristics with either direction of operation of the motors.
  • FIG. 1 is a sectional view through a multiple motor hydraulic power means of a kind with which the control system of the invention is adapted to be used;
  • FIG. 2 is a diagram of the control system with two of the valve devices illustrated in section and with the main control valve in the position providing for high speed operation, i.e., operation by only one of the two motors;
  • FIG. 3 is a fragmentary diagrammatic view of the main control valve shown in FIG. 2, but positioned to provide low speed multiple motor operation;
  • FIG. 4 is a fragmentary sectional view of one of the valve devices shown in FIG. 2, but with the valve in a different position as compared with FIG. 2.
  • the body or enclosure for a hydraulic gear motor is indicated generally by the reference numeral 5.
  • the details of construction of the motor need not be considered herein, but it is pointed out that the motor assembly comprises two motors, the first of which is made up of a pair of meshing gears 6,7 mounted by means of shafts 8 and 9, the latter of which has a projecting end 10 constituting the power output shaft for the system.
  • the other motor includes a pair of meshing gears 11 and 12 mounted by means of shafts l3 and 14, the latter of which is connected with the shaft 9 of the first motor by means of spline coupling 15.
  • passages are provided at opposite sides of both of the motors, so that the motors may be supplied with the hydraulic operating fluid and so that the fluid may be delivered from the motors and returned to reservoir.
  • valve devices which are advantageously incorporated in the body 5 of the motor itself. These valve devices are not shown in FIG. 1, but are illustrated in section in FIG. 2 in positions facilitating the diagrammatic representation of the control system-shown in FIG. 2.
  • the two valve devices are illustrated generally in FIG. 2 by the reference numerals l6 and 17, the former also being shown in FIG. 4, but with the valve in a different position.
  • valve device 16 is serving as the supply valve for the motors and that the valve device 17 is serving as the discharge valve for the motors.
  • This condition is established by positioning of the reversing valve R in the position in which the section of the valve indicated at R3 is in position to cooperate with the supply and discharge lines connected with the reversing valve. This is the condition shown in FIG. 2.
  • the passages 18 and 19 respectively represent the supply passages for the first and second motors which are diagrammatically represented at M-1, M-2 in FIG. 2.
  • valve device 16 there are two cavities 20 and 21 which are respectively connected with the motor passages 18 and 19 and which are adapted to be interconnected by the port 22 having a valve seat 23 with which the poppet valve 24 cooperates, so that the cavities 20 and 21 and thus the passages 18 and 19 may be either separated or interconnected according to the position of the valve 24.
  • a pump 25 deriving hydraulic fluid from the reservoir 26 communicates with the pasage 18 and thus with cavity 20 through connection 27, the reversing valve R, and connection 27a.
  • the connection 28 which may be arranged internally of the body 5 delivers operating fluid to the inlet side of the motor M-1, and it will be noted that this delivery will be maintained regardless of the position of the valve 24.
  • When the valve 24 is open operating fluid will pass from the cavity 20 through the port 22 into the cavity 21 and thus to the inlet side of the second motor as by the passage 29, which, again may be located internally of the body 5 ofthe motor assembly.
  • valve device l7 at the left of the Figure occupies the position of the discharge valve for the motors, and here it will be seen that the motor passages 30 and 31 communicate with cavities 32 and 33 having an interconnecting port 34 with a seat 35 adapted to be controlled by a valve 36.
  • Passages formed internally of the motor body 5 include the passage 37 from the first motor to the cavity 32 and passage 30, and passage 38 from the second motor to the passage 31 and cavity 33.
  • An external connection 39a extends to the reversing valve R and communicates with connection 39, thereby providing for delivery of operating fluid from the passage 30 and thus from the cavity 32 of the valve 17 back to reservoir as indicated at 26. It will be seen that fluid discharging from the motor M-l passes directly to reservoir regardless of the position of valve 36 and further that when the valve 36 is open fluid may be discharged from both motors and returned to reservoir through the connection 39a and 39.
  • the control system also includes a primary manually operated control valve indicated generally at 40, and this valve is shown in FIG. 2 in the position providing for high speed operation, i.e., operation ofonly the first motor indicated at M-l in FIG. 2.
  • a primary manually operated control valve indicated generally at 40 In explaining the operation of this manual control valve attention is now directed to the fact that each of the valve devices 16 and 17 includes a piston 41 and 42 connected respectively with the poppet valves 24 and 36 and serving to seat and unseat the poppet valves.
  • Behind piston 41 is a chamber 43 and behind piston 42 is a chamber 44, these chambers comprising pressure fluid chambers serving, in cooperation with the springs 45 and 46, to control the motion of the pistons 41 and 42 and thus of the poppet valves 24 and 26. 36.
  • Chamber 43 has a port 47 communicating with a discharge pipe 48 through a branch 48a.
  • chamber 44 has a port 49 communicating with the discharge pipe 48 through a branch 48!).
  • Branch 48a has a restricted port or orifice 50 and a similar orifice 51 is provided in the branch 48b.
  • These two branches also have check valves 52 and 53, the check valve 52 permitting free flow of fluid from the chamber 43 to the discharge pipe 48 but preventing reverse flow, and the check valve 53 permitting free flow of fluid from the chamber 44 to the discharge pipe 48 but preventing reverse flow.
  • a discharge pipe 54 has two branches 54a and 54b which are extended respectively to the cavities 21 and 33 in the valve devices 16 and 17.
  • the interconnection between the discharge pipe 54 and its branches 54a and 54b comprises a double acting check valve indicated at 55, which valve serves to permit flow of pressure fluid from cavity 21 or cavity 33 to-the discharge pipe 54 and to prevent flow in either direction between the cavities 21 and 33.
  • the two discharge pipes 48 and 54 extend to the main control valve 40 and in accordance with the position of that valve, one or the other of the discharge pipes is connected with the return line 56 extended to reservoir, as is indicated.
  • the discharge pipe 48 is shut off, but the discharge pipe 54 is connected through passage 57 with the return line 56.
  • the discharge pipe 54 is closed and the discharge pipe 48 is connected with the return line 56 through the passage 58.
  • restricted port 59 which extends through the base of the cylinder 41 of the valve device 16, and interconnects the chamber 43 with the cavity 20.
  • a restricted port 60 interconnects the chamber 44 with the cavity 32.
  • Each of the valves 24 and 36 is also provided with a peripherally notched portion, respectively indicated at 61 and 62, and serving as metering grooves for the flow of hydraulic fluid from the cavity 20 or 32, to the cavity 21 or 33 while the respective valves are in transition (opening or closing). These passages contribute to the smoothness of shift, when the control system is adjusted to change the mode of operation from single motor to two motor operation or from two motor operation to single motor operation. It is to be noted that in FIG. 4 the control valve 24 is shown part-way open. The opening movement will normally continue until the rear end of the piston 41 abuts against the closure cap, at which time the grooved portion 61 of the valve will be displaced somewhat to the right of the valve seat 23.
  • the restricted passages 59 and 60 should not be substantially larger than the restrictions and 51.
  • the metering grooves 61 and 62 are also important in providing against abrupt transition between the two conditions of operation.
  • the symmetry of the control system is of advantage in permitting the entire system including the motors to operate in either direction.
  • Such reversal in operation is effected by means of the reversing valve, the position illustrated in FIG. 2 in which the valve section R3 is in operation providing for supply of pressure fluid through the valve 16 and discharge of fluid from the motors through the valve 17.
  • the reversing valve R By shifting the reversing valve R to bring the valve section R1 into registry with the passages 27-39a and 27a-39, the pressure fluid supplied by the pump 25 will be delivered to the valve 17 and the discharge will occur through valve 16.
  • the valve R may also have a shut-off position, provided, for example, by the section R2 of the valve, in which position the pressure fluid from the pump 25 will merely be recirculated to reservoir.
  • the main control valve In normal operation of the system when the reversing valve R is positioned for either direction of operation, the main control valve is employed for changing the condition of operation from one-motor operation to two-motor operation, or vice versa.
  • the arrangement of the valves 24 and 36 and of the passages and connections associated therewith is such that even during shift of valve 40 from one condition to the other, the motors will not experience a neutral condition tending to result in dropping of the load.
  • a fluid control system for power means having first and second hydraulic motors connected to deliver power to a power shift and each of said motors having first and second passages extended from opposite sides thereof for supply and discharge of operating fluid
  • the control system comprising first and second valve devices each having first and second cavities and a valve seat around a port interconnecting the first and second cavities, the first and second cavities of the first valve device being connected respectively with the first passages of the two motors and the first and second cavities of the second valve device being connected respectively with the second passages of the two motors, and each of said devices having a valve cooperating with said seat and movable to open and close said port
  • first connection means providing for connection of the first cavity of the first valve device with a source of hydraulic operating fluid
  • second connection means providing for connection of the first cavity of the second valve device with reservoir
  • said two valve devices providing for operation of only the first motor when the two valves are closed and for operation of both motors when the two valves are open
  • each of said valve devices having fluid pressure means for operating the valves including a pressure
  • a fluid control system for power means having first and second hydraulic motors connected to deliver power to a power shaft and each of said motors having first and second passages extended from opposite sides thereof for supply and discharge of operating fluid
  • the 25 control system comprising a valve device having first and second cavities and a valve seat around a port interconnecting the first and second cavities, the first and second cavities of the valve device being connected respectively with the first passages of the two motors, and the valve device having a valve cooperating with said seat and movable to open and close said port
  • first connection means providing for connection of the first cavity of the valve device with a source of hydraulic operating fluid
  • said valve device providing for supply of op- 35 crating fluid to only the first motor when the valve is closed, and for operation of both motors when the valve is open
  • the valve device having fluid pressure means for operating its valve including a pressure fluid chamber at that side of the valve acting to move the 4 valve against the valve seat and therebyrclose the port upon build-up of pressure in said pressure fluid chamber, the valve device having a restricted or
  • a fluid control system for power means having first and second hydraulic motors connected to deliver power to a power shaft and each having passages extended therefrom for supply and discharge of operating fluid
  • the control system comprising supply and discharge valve means providing alternatively for operation of the first motor only and for operation of both motors, and including a valve adapted in a first position to shut off the fluid with respect to one motor and a second position to establish a fluid flow with respect to both motors, and control mechanism for said valve viding alternatively for build-up and discharge of pressure in said chamber, each of said supply and discharge connections having a restriction therein providing'respectively for retarded build-up and discharge of pres- 0 sure in the control chamber.
  • a fluid control system for power means having first and second hydraulic motors connected to deliver power to a power shaft and each having passages ex tended therefrom for supply and discharge of operating 5 fluid
  • the control system comprising supply and discharge valve means providing alternatively for operation of the first motor only and for operation of both motors, and including valve chambers respectively connected with the supply passages for the two motors and 0 one of which is a pressure fluid supply chamber, a port between the valve chambers, a control valve for opening and closing said port and thereby provide alternatively for supply of pressure fluid to one motor and to both motors, said valve also having means cooperating with said port to provide metering grooves for restricting flow from the pressure fluid supply chamber to the other chamber during opening and closing movement of the valve, and means for actuating said control valve including a fluid pressure control chamber having a supply connection and a discharge connection, and a manually controllable valve in one of said connections providing alternatively for build-up and discharge of pressure in said chamber, each of said supply and discharge connections having a restriction therein providing respectively for retarde
  • a fluid control system for power means having a plurality of hydraulic motors connected to deliver 0 power to a power shaft and each of said motors having passages extended therefrom for supply of operating fluid and for discharge of operating fluid to reservoir
  • the control system comprising supply and discharge valve means providing alternatively for operation of 5 one motor only and for operation of more than one motor, and including a valve adapted in a first position tov shut off the fluid flow with respect to all but one motor and a second position to establish fluid flow with respect to more than one motor
  • the control system fur- O ther including manually controllable means for effecting movement of said valve between its first position and its second position, and for each motor means providing for discharge of operating fluid from any inactive motor to reservoir independently of the discharge 5 from an active motor, and thus for operation of any inactive motor in the absence of pressure fluid at times when the valve is in its position to shut off fluid flow with respect to more than one motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
US00311791A 1972-12-04 1972-12-04 Control system for multiple motor hydraulic means Expired - Lifetime US3849985A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US00311791A US3849985A (en) 1972-12-04 1972-12-04 Control system for multiple motor hydraulic means
JP48130310A JPS5760486B2 (enrdf_load_stackoverflow) 1972-12-04 1973-11-21
GB5614273A GB1454407A (en) 1972-12-04 1973-12-04 Control system for multiple motor hydraulic power means

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Application Number Priority Date Filing Date Title
US00311791A US3849985A (en) 1972-12-04 1972-12-04 Control system for multiple motor hydraulic means

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US3849985A true US3849985A (en) 1974-11-26

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US00311791A Expired - Lifetime US3849985A (en) 1972-12-04 1972-12-04 Control system for multiple motor hydraulic means

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US (1) US3849985A (enrdf_load_stackoverflow)
JP (1) JPS5760486B2 (enrdf_load_stackoverflow)
GB (1) GB1454407A (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4015679A (en) * 1975-05-16 1977-04-05 J. I. Case Company Drive range and lock control system
US4136855A (en) * 1976-12-03 1979-01-30 The Manitowoc Company Inc. Hoist drum drive control
FR2468769A1 (fr) * 1979-11-05 1981-05-08 Commercial Shearing Circuit a moteurs bidirectionnels
US5255590A (en) * 1990-06-23 1993-10-26 Ing. Guenter Klemm Bohrtechnik Gmbh Control device for the load- dependent connection of a hydraulic stand by motor to a base-load motor
US5435135A (en) * 1993-06-09 1995-07-25 Poclain Hydraulics Reversible pressurized fluid mechanism such as a motor or a pump and having at least two operating cylinder capacities
US20160115672A1 (en) * 2013-06-03 2016-04-28 Volvo Construction Equipment Ab A power system for a working machine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5677569A (en) * 1979-11-28 1981-06-25 Tokyo Keiki Co Ltd Variable capacitance type fluid pressure rotary device
CN116336041B (zh) * 2023-04-03 2025-02-07 南通理工学院 一种基于plc的换料柱机电气控制系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2370526A (en) * 1942-02-20 1945-02-27 Gen Electric Hydraulic torque transmission arrangement
US2830784A (en) * 1954-09-30 1958-04-15 Placette Theodore General purpose flow valve with alternative fluid pressure or manual control
US3344805A (en) * 1965-03-24 1967-10-03 Fischer & Porter Co Automatic flow rate control system
US3473442A (en) * 1967-11-03 1969-10-21 Cascade Corp Hydraulic motor drive

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2370526A (en) * 1942-02-20 1945-02-27 Gen Electric Hydraulic torque transmission arrangement
US2830784A (en) * 1954-09-30 1958-04-15 Placette Theodore General purpose flow valve with alternative fluid pressure or manual control
US3344805A (en) * 1965-03-24 1967-10-03 Fischer & Porter Co Automatic flow rate control system
US3473442A (en) * 1967-11-03 1969-10-21 Cascade Corp Hydraulic motor drive

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4015679A (en) * 1975-05-16 1977-04-05 J. I. Case Company Drive range and lock control system
US4136855A (en) * 1976-12-03 1979-01-30 The Manitowoc Company Inc. Hoist drum drive control
FR2468769A1 (fr) * 1979-11-05 1981-05-08 Commercial Shearing Circuit a moteurs bidirectionnels
US5255590A (en) * 1990-06-23 1993-10-26 Ing. Guenter Klemm Bohrtechnik Gmbh Control device for the load- dependent connection of a hydraulic stand by motor to a base-load motor
US5435135A (en) * 1993-06-09 1995-07-25 Poclain Hydraulics Reversible pressurized fluid mechanism such as a motor or a pump and having at least two operating cylinder capacities
US20160115672A1 (en) * 2013-06-03 2016-04-28 Volvo Construction Equipment Ab A power system for a working machine
US9765502B2 (en) * 2013-06-03 2017-09-19 Volvo Construction Equipment Ab Power system for a working machine

Also Published As

Publication number Publication date
JPS4986775A (enrdf_load_stackoverflow) 1974-08-20
GB1454407A (en) 1976-11-03
JPS5760486B2 (enrdf_load_stackoverflow) 1982-12-20

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AS Assignment

Owner name: DANA CORPORATION A CORP OF VA

Free format text: MERGER;ASSIGNOR:TYRONE HYDRAULICS, INC. A DE CORP.;REEL/FRAME:004243/0378

Effective date: 19831221