US3645167A - Control arrangement for hydraulic motors - Google Patents

Control arrangement for hydraulic motors Download PDF

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Publication number
US3645167A
US3645167A US886623A US3645167DA US3645167A US 3645167 A US3645167 A US 3645167A US 886623 A US886623 A US 886623A US 3645167D A US3645167D A US 3645167DA US 3645167 A US3645167 A US 3645167A
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United States
Prior art keywords
control
return flow
flow
piston
control arrangement
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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
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US886623A
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English (en)
Inventor
Helmut Espenschied
Joseph Sauer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Priority claimed from DE19681815915 external-priority patent/DE1815915C3/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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Publication of US3645167A publication Critical patent/US3645167A/en
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions

Definitions

  • a directional valve communicates with both sides of the piston of the motor and is actuated by the fluid flow.
  • the control slide of the directional valve is urged, through spring action, into a neutral inoperative position, in which a fluid inflow duct to the directional valve is closed.
  • the control slide connects two ports leading to hydraulically operated devices, with the inflow duct, when in operating positions. Flow chambers at both ends of the control slide communicate with the ports and the inflow duct through throttling passages.
  • the present invention resides in a control arrangement for a hydraulic motor with a piston head which is controlled and actuated on both sides, and with valves controlling the return flow from the hydraulic motor.
  • a control device for a double-acting hydraulic motor in which the motor can assume two operating positions, and is centered or takes a central position by being subjected to pressure.
  • the chambers on both sides of the operating piston in this conventional device are always in communication with a pressure source through two 3/2 directional valves, when the operating piston is in its central position. These two chambers on both sides of the operating piston are alternatingly relieved to a return flow, in the operating position of the pistons.
  • This control arrangement does not make possible any intermediate positions of the operating piston, and involves particularly complex construction as a result of centering the operating piston through fluid means.
  • control unit for a hydraulic motor which may be dis placed or positioned by any desired amount. It is also an object of the present invention to provide such a control unit which is simple in construction and possesses substantially short response times.
  • a directional valve is provided, furthermore, which is actuated by the controlling fluid under pressure.
  • the direction valve has a control slide which closes or shuts an inflow port, when in its neutral position.
  • the control slide furthermore, has operating positions in which it connects the inflow port with one of two ports of hydraulically operated devices.
  • chambers are provided which communicate with the designated port of the hydraulically operated device, and through a throttling passage with the inflow port.
  • control unit in accordance with the present invention, can possess short response times, in addition to being simple in construction.
  • the arrangement of the present invention furthermore, makes possible precise positioning of the operating piston.
  • a hydraulic control arrangement for use in conjunction with a hydraulic motor.
  • the motor has a piston which may be subjected to fluid pressure on both sides thereof.
  • a return flow duct communicates with the motor through return flow passages and controlling valves located within the passages.
  • a directional valve communicates with both sides of the piston for the purpose of controlling fluid flow to these sides of the piston.
  • the directional valve has a control slide which is urged into a neutral central position through spring action, whereas in the operative position of the control slide, a fluid inflow duct communicates with the directional valve. In the operating positions of the control slide, furthermore, two fluid flow ports are connectable to the fluid inflow duct through the control slide. Fluid chambers on both sides of the control slide communicates with the ports and the fluid inflow duct, through throttling passages.
  • a switching valve may connect a plurality of return flow ports from the motor to the return flow duct.
  • FIG. 1 is a sectional view, in simplified schematic form, of
  • FIG. 2 is a sectional view, in simplified schematic form, of another embodiment of the control arrangement shown in FIG. I;
  • FIG. 3 is a sectional view through a directional valve used in conjunction with the control arrangement of the present invention.
  • control arrangement of FIG. 1 consists essentially of a directional valve 11 which is actuated for the purpose of controlling the fluid under pressure, a double-acting hydraulic motor 12 for actuating an injection pump 13, and two electromagnetically actuated valves 14 and 15.
  • the directional valve 11 has an axial slide 16 which is centered through spring action, and has three head-shaped sliding sections l7, l8 and 19.
  • the middle slide section 118 blocks a port 21, in the neutral position of the axial or longitudinal slide 16.
  • the port 21 serves as an entrance for a flow 22.
  • the slide section 18, furthermore, isolates a chamber 23 from another chamber 24, when in the neutral position of the longitudinal slide 16.
  • Two chambers 25 and 26 on both frontal sides 27 and 28 of the axial slider 16 communicate with the chambers 23 and 24 respectively.
  • Lines 29 and 31 shaped to form throttling elements furthermore, connect the chambers 25 and 26, respectively, with the inflow 22.
  • a conventional return arrangement is, moreover, situated within the chambers 25 and 26, and consists essentially of prestressed springs 32, sleeves 33, and supporting rings 34 secured to the housing.
  • the hydraulic motor 12 has an operating head 35 communicating on one side, with an actuating space of chamber 36 which communicates, in turn with the port 23 through a line 37.
  • This port 23 is associated with the first hydraulically operated device.
  • the other actuating side of the operating head 35 faces the chamber 39 which communicates with the second port 24 of the first hydraulically operated device, through a line 41.
  • the piston rod 38 is linked to a lever 42 of the injection pump 13.
  • the lever 42 is coupled through a spring to a one-armed lever 43, so that they are both oriented along the same axis.
  • the lever 43 is loosely held and is actuated through a conventional driving pedal, not shown.
  • lines 44 and 45 lead to a return flow 46.
  • the chambers 36 and 39 are interconnected through a line 47 which passes around the return flow line 46.
  • a first electromagnetically actuated valve i4 is situated in the line 44 between the actuating chamber 36 and the return flow line 46.
  • a similar electromagnetically actuated valve 15 is situated in the line 45 between the chamber 39 and the return flow line 46.
  • Each electromagnetically actuated valve 14 and 15 possesses a piston slide 48 and 49, respectively, which is spring loaded on one side. Through these piston slides 48 and 49, these elec tromagnetically actuated valves 14 and 15 also influence the flow line 4'7 which passes around the return flow line 46. In the initial position of the piston slide 48 and 49, as shown in the drawing, the line 44 and 45 are cut off from the return flow line 46, whereas the flow line 47 is opened.
  • the pressure in the inflow channel 22 is derived from a pressure source, and is applied to the directional valve 11, when in its neutral position, through the throttling lines 29 and 31.
  • the pressure is applied to both frontal sides 27 and 28 of the axial or longitudinal slide 16.
  • the pressure also builds up simultaneously at both sides of the operating head 35 which does not function as a differential piston. Since the electromagnetic valves 14 and 15 retain the flow line 47 open, when they are not actuated, the operating piston 35 can follow the position corresponding to that assumed by the driving pedal.
  • Fluid under pressure consequently flows from the inflow 22 through the directional valve 11 and into the line 41. After passing through the line 41, the fluid under pressure flows into the chamber 39 of the hydraulic motor 12 and forces the operating piston 35 towards the left, provided that the piston 35 has initially assumed the position illustrated in FIG. 1 of the drawing. When the piston 35 is positioned at the left abutment position, it becomes then moved towards the right through actuation of the clectromagnetically energized valve 14.
  • the operating piston 35 By actuating the electromagnetic valve 15, the operating piston 35 is displaced in a corresponding reverse manner and in the opposite direction, depending upon its initial position.
  • the displacement motion of the operating piston or head 35 can be damped in one or both directions, when the electromagnetically operated valves 14 and 15 are not actuated.
  • the control unit shown in FIG. 2 serves for the purpose of controlling a motor vehicle drive, and differs from the control unit shown in FIG. 1, through a different hydraulic motor 61 and a switching valve 62.
  • the directional valve 11 is identical to that used for the arrangement of FIG. 1. Identical parts of this valve, consequently, are denoted with identical reference numerals.
  • four return flow lines 63, 64, 65 and 66 are provided at the hydraulic motor 61, next to the two ports for the lines 37 and 41 from the directional valve 11.
  • the four return flow lines are spaced from each other.
  • An operating piston 67 of the hydraulic motor 61 can open and close each one of these return flow lines 63 to 66.
  • lines lead to the switching valve 62.
  • the latter has a slide which is actuated through a stepping magnetic device, not further shown, so as to selectively connect one of these return flow lines 63 to 66 to a return flow duct 68.
  • the operating piston 67 which is always subjected to pressure on both sides, is always displaced by the switching valve 62 in a direction to that one of the return flow ports 63 to 66 which is relieved to the return flow duct 68. Shortly before arriving into its designated position, the operating piston 67 becomes braked or decelerated through the application of opposing pressure.
  • the functional operation of the directional valve 11 is, thereby, identical to that of this device in the control arrangement of FIG. 1.
  • FIG. 3 shows the cross-sectional view of an embodiment of a directional valve 71 actuated and controlled through fluid under pressure.
  • This directional valve 71 differs from the directional valve 11 of FIG. 1, essentially through a shorter control piston or head 72, and the arrangement of a first and second port 73 and 74, respectively, of hydraulically operated devices.
  • Chamber 75 and 76 receive or contain a return device. These chambers 75 and 76 are on both sides of the control head or piston 72, and passages or channels 77 and 78 form sleeves 79 and 30 of the return device.
  • the functional operation of the direction valve 71 corresponds to that of the directional valve 11.
  • fluid under pressure flows from the inflow channel 22, through the passage which lies on the other side of the control piston head 72 and to one port of a hydraulically operated device. The fluid then flows further to the hydraulic motor.
  • a control arrangement for a neutral motor comprising, in combination, a hydraulic motor comprising a cylinder and a piston subjectable to pressure on both sides of said piston; return flow means from said motor; control valve means for controlling flow from said motor to said return flow means; directional valve means communicating with both sides of said piston for controlling fluid flow to said sides of said piston, said fluid flow actuating said piston; control slide means in said directional valve means and having a neutraul inoperative position and operating positions; fluid inflow means communicating with said directional valve means and closed when said control slide means is in said neutral inoperative position; two fluid flow ports connectable to said fluid inflow means through said control slide means in said operating positions of said control slide means; and chamber means on both end sides of said control slide means and communicating with said ports and said fluid inflow means.
  • control arrangement as defined in claim 1 including throttling means between said chamber means and said fluid inflow means.
  • control arrangement as defined in claim 1 including spring means acting on said control slide means and urging said control slide means into said neutral inoperative position.
  • control valve means comprises an electromagnetically actuated valve.
  • control arrangement as defined in claim 1 including flow line means connecting both sides of said piston of said motor; and said control valve means comprising auxiliary valve means in said flow line means for controlling fluid flow from said motor to said return flow means.
  • auxiliary valve means comprises electromagnetically actuated valve means with displaceable slide means.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
US886623A 1968-12-20 1969-12-19 Control arrangement for hydraulic motors Expired - Lifetime US3645167A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19681815915 DE1815915C3 (de) 1968-12-20 Steuerung für einen Druckmittelmotor

Publications (1)

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US3645167A true US3645167A (en) 1972-02-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
US886623A Expired - Lifetime US3645167A (en) 1968-12-20 1969-12-19 Control arrangement for hydraulic motors

Country Status (5)

Country Link
US (1) US3645167A (de)
CH (1) CH486638A (de)
FR (1) FR2026624A1 (de)
GB (1) GB1282947A (de)
SE (1) SE352143B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3808952A (en) * 1971-04-30 1974-05-07 Reproth G Gmbh Regulating apparatus for a hydraulic machine
US4206827A (en) * 1977-10-17 1980-06-10 Cam Gears Limited Steering gears
US4222309A (en) * 1976-09-07 1980-09-16 Theodore Ongaro Hydraulic power system
US5226346A (en) * 1991-05-30 1993-07-13 Mercedes-Benz Ag Axial piston type pressure medium servomotor control device
WO2010130288A1 (en) * 2009-05-12 2010-11-18 Richard Bernard Schaper Method for operating a cylinder, system and mannequin robot comprising the same
CN103758799A (zh) * 2014-01-26 2014-04-30 天津大学 双电机驱动的电反馈伺服液压马达

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4126697A1 (de) * 1991-08-13 1993-02-18 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2398997A (en) * 1943-02-22 1946-04-23 Gen Electric Variable-speed gear transmission
US3015317A (en) * 1958-02-11 1962-01-02 Hydraulic Res And Mfg Company Pressure control servo valve
US3045650A (en) * 1957-12-23 1962-07-24 Lear Inc Fluid actuating device
US3156157A (en) * 1961-04-11 1964-11-10 Burroughs Corp Positioning control system and apparatus

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2398997A (en) * 1943-02-22 1946-04-23 Gen Electric Variable-speed gear transmission
US3045650A (en) * 1957-12-23 1962-07-24 Lear Inc Fluid actuating device
US3015317A (en) * 1958-02-11 1962-01-02 Hydraulic Res And Mfg Company Pressure control servo valve
US3156157A (en) * 1961-04-11 1964-11-10 Burroughs Corp Positioning control system and apparatus

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3808952A (en) * 1971-04-30 1974-05-07 Reproth G Gmbh Regulating apparatus for a hydraulic machine
US4222309A (en) * 1976-09-07 1980-09-16 Theodore Ongaro Hydraulic power system
US4206827A (en) * 1977-10-17 1980-06-10 Cam Gears Limited Steering gears
US5226346A (en) * 1991-05-30 1993-07-13 Mercedes-Benz Ag Axial piston type pressure medium servomotor control device
WO2010130288A1 (en) * 2009-05-12 2010-11-18 Richard Bernard Schaper Method for operating a cylinder, system and mannequin robot comprising the same
CN103758799A (zh) * 2014-01-26 2014-04-30 天津大学 双电机驱动的电反馈伺服液压马达
CN103758799B (zh) * 2014-01-26 2015-10-28 天津大学 双电机驱动的电反馈伺服液压马达

Also Published As

Publication number Publication date
CH486638A (de) 1970-02-28
DE1815915B2 (de) 1975-10-09
FR2026624A1 (de) 1970-09-18
SE352143B (de) 1972-12-18
DE1815915A1 (de) 1970-07-02
GB1282947A (en) 1972-07-26

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