US2813519A - Hydraulic servo-motor - Google Patents

Hydraulic servo-motor Download PDF

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Publication number
US2813519A
US2813519A US569631A US56963156A US2813519A US 2813519 A US2813519 A US 2813519A US 569631 A US569631 A US 569631A US 56963156 A US56963156 A US 56963156A US 2813519 A US2813519 A US 2813519A
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openings
sleeve
pressure
main piston
motor
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Expired - Lifetime
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US569631A
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Persson Erik
Schiott Henning
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ABB Norden Holding AB
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ASEA AB
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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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2278—Pressure modulating relays or followers

Definitions

  • This invention relates to a hydraulic servo-motor of the sort comprising a main piston reciprocally movable in a cylinder under the influence of a pressure medium like oil, and obtaining a position determined by the position of a control means.
  • Servo-motors of this sort are often encountered in control and regulation applications, where they are used for amplifying the force from an electromagnetically operated control device so that valves or the like may be operated therefrom.
  • Another object of the invention is to provide a servomotor in which the control means is not influenced by the load upon the main piston.
  • a further object is to make the position of the main piston independent of normal variations in temperature and pressure of the pressure fluid.
  • the main piston is a doubleacting piston with two substantially equal and opposite areas, which are influenced by the pressure medium in two different chambers, which chambers through ducts having a substantial flow resistance is communicating with the source of the pressure medium, and through other ducts is communicating with each one group of openings in the envelope surface of a cylindrical body connected to the main piston, said cylindrical body being surrounded by a sleeve connected to the control means, and the openings in the envelope of said cylindrical body being so arranged, that the sleeve by its movements in relation to the cylindrical body closes one group of openings and opens for the other, so that the two pressures acting on the main piston become different, and the pressure difference influences the main piston in the direction in which the sleeve is moving.
  • Fig. l is a section through a servo-motor according to the invention.
  • Fig. 2 is a section through another servo-motor according to the invention, differing from the first only in the arrangement of the ducts connecting the pressure source with the chambers in which the pressure fluid acts upon the piston.
  • the numeral 2 designates a main piston being movable in a cylinder 1.
  • the main piston 2 is double-acting and its two opposite areas 6 and 7 are influenced by a pressure medium in chambers 4 and respectively.
  • the chambers 4 and 5 are communicating with the source 10 for the pressure medium through each one restricted duct 8 and 9, and is further through ducts 12 and 13 communicating with each one group of openings 14 and 15 in the envelope surface of a cylindrical body 11 connected to the main piston 2.
  • a sleeve 3 with small clearance surrounds the cylindrical body 11 and is connected to a coil 22, which is movable in the field from a magnet 23, and is suspended in springs 19.
  • the openings 14, 15 in the envelope surface of the cylindrical body 11 are so arranged that the sleeve 3 simultaneously may cover the openings 14 and the openings 15 to about 50 percent.
  • the pressure in the chambers 4 and 5 will have the same value, because the restrictions 8 and 9 have the same flow resistance, and this pressure is somewhat lower than the pressure at the source 10, suitably about half this pressure.
  • the two opposite piston areas 6 and 7 of the main piston are equal, and thus no resulting force influences the main piston in the described case.
  • the sleeve 3 moves away from the cylinder 1.
  • the main piston 2 is then influenced by a resulting force, which is proportional to the pressure difference in the chambers 4 and 5, and which is acting in the same direction as the sleeve 3 moved.
  • the main piston 2 thus follows the sleeve 3 and does not stop until a new equilibrium is obtained when the openings 14 and 15 again are equally choked.
  • the pressure medium passes an edge of the sleeve 3 at the outlet from one of the openings 14 and 15, it influences the sleeve with an axial force, the magnitude of which may be reduced by making the edge sharp and knife-like, but never can be entirely eliminated.
  • the sleeve 3 is influenced by two counteracting axial forces of this sort, one at the openings 14 and one at the openings 15, the resulting axial force of the sleeve becomes, however, negligible. Even though each of the said axial forces are pressureand temperature-dependent, the force with which the servo-motor reacts on the sleeve thus becomes practically constant and equal to zero.
  • Fig. 2 is shown another form of the invention, which differs from the form shown in Fig. 1 only in the arrangement of the restricted ducts 8 and 9.
  • the main piston 2 is in Fig. 2 provided with an annular groove between the piston areas 6 and 7, so that a chamber 20 is obtained, which is directly connected t0 the source for the pressure medium.
  • the restricted ducts 8 and 9 are arranged in the main piston 2 itself, and connects the chambers 4 and 5 with the chamber 20.
  • This form of the invention has certain manufacturing advantages over the form shown in Fig. l, but the manner of operation is entirely identical for the two forms.
  • the openings 14 and 15 are of course always arranged symmetrically around the axis of the cylindrical body 11, so that the sleeve 3 is not influenced by any resulting radial force which may give rise to friction between the sleeve 3 and the cylindrical body 11.
  • symmetrically arranged openings may be provided, discharging behind the inner surface of the sleeve 3, and in a known manner communicating through restricted ducts with one of the chambers 4 or 5, or better the chamber in Fig. 2.
  • Hydraulic servo-motor comprising a cylinder, and a double-acting piston reciprocatably movable in said cylinder and dividing the interior of said cylinder into two main chambers, means including a restricted passage for connecting each of said main chambers to a source of pressure iluid, a cylindrical body connected to said piston and protruding from said cylinder openings located in the peripheral surface of said cylindrical body and arranged in two axially displaced groups of openings, means for connecting each of said groups of openings to one of said main chambers, a sleeve fitting with small clearance on said cylindrical body and serving to cover and uncover said openings, said sleeve having an axial length substantially equal to the axial distance between said two groups of openings, and means for axially displacing said sleeve in dependence on a control magnitude.
  • Hydraulic servo-motor comprising a cylinder, and a double-acting piston having two substantially equal and counteracting working areas being reciprocatably movable in said cylinder and dividing the interior of said cylinder into two main chambers, an annular groove in said piston between said working areas, means for connecting said annular groove to a source of pressure fluid, restricted ducts connecting said annular groove and said main chambers, a cylindrical body connected to said piston and protruding from said cylinder, openings located in the peripheral surface of said cylindrical body and arranged in two axially displaced groups of openings, means for connecting each of said groups of openings to one of said main chambers, a sleeve fitting with small clearance on said cylindrical body and serving to cover and uncover said openings, said sleeve having an axial length substantially equal to the axial distance between said two groups of openings, and means for axially displacing said sleeve in dependence on a control magnitude.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)

Description

Nov. 19, 1957 E. PERSSON ETAL 2,313,519
mnmuuc SERVO-MOTOR Filed March 5, 1956 Fig I B kw United States Patent HYDRAULIC SERVO-MOTOR Erik Persson and Henning Scbiott, Vasteras, Sweden, as-
signors to Allmanna Svenska Elektriska Aktiebolaget, Vasteras, Sweden, a corporation of Sweden Application March 5, 1956, Serial No. 569,631 Claims priority, application Sweden March 8, 1955 2 Claims. (Cl. 121-41) This invention relates to a hydraulic servo-motor of the sort comprising a main piston reciprocally movable in a cylinder under the influence of a pressure medium like oil, and obtaining a position determined by the position of a control means. Servo-motors of this sort are often encountered in control and regulation applications, where they are used for amplifying the force from an electromagnetically operated control device so that valves or the like may be operated therefrom.
It is the main object of this invention to provide a servo-motor of the sort described having a very accurate relation between movement of the main piston and the control means.
Another object of the invention is to provide a servomotor in which the control means is not influenced by the load upon the main piston.
A further object is to make the position of the main piston independent of normal variations in temperature and pressure of the pressure fluid.
Also among the objects is the provision of a servomotor of the sort described being of simple construction and readily serviceable.
According to the invention the main piston is a doubleacting piston with two substantially equal and opposite areas, which are influenced by the pressure medium in two different chambers, which chambers through ducts having a substantial flow resistance is communicating with the source of the pressure medium, and through other ducts is communicating with each one group of openings in the envelope surface of a cylindrical body connected to the main piston, said cylindrical body being surrounded by a sleeve connected to the control means, and the openings in the envelope of said cylindrical body being so arranged, that the sleeve by its movements in relation to the cylindrical body closes one group of openings and opens for the other, so that the two pressures acting on the main piston become different, and the pressure difference influences the main piston in the direction in which the sleeve is moving.
The features of this invention which are believed to be novel are set forth with particularity in the appended claims. The invention itself, however, may best be understood by reference to the following description and the accompanying drawing, in which:
Fig. l is a section through a servo-motor according to the invention, and
Fig. 2 is a section through another servo-motor according to the invention, differing from the first only in the arrangement of the ducts connecting the pressure source with the chambers in which the pressure fluid acts upon the piston.
In Fig. 1 the numeral 2 designates a main piston being movable in a cylinder 1. The main piston 2 is double-acting and its two opposite areas 6 and 7 are influenced by a pressure medium in chambers 4 and respectively. The chambers 4 and 5 are communicating with the source 10 for the pressure medium through each one restricted duct 8 and 9, and is further through ducts 12 and 13 communicating with each one group of openings 14 and 15 in the envelope surface of a cylindrical body 11 connected to the main piston 2. A sleeve 3 with small clearance surrounds the cylindrical body 11 and is connected to a coil 22, which is movable in the field from a magnet 23, and is suspended in springs 19. The openings 14, 15 in the envelope surface of the cylindrical body 11 are so arranged that the sleeve 3 simultaneously may cover the openings 14 and the openings 15 to about 50 percent.
If the sleeve 3 chokes the openings 14 and the openings 15 to the same degree, the pressure in the chambers 4 and 5 will have the same value, because the restrictions 8 and 9 have the same flow resistance, and this pressure is somewhat lower than the pressure at the source 10, suitably about half this pressure. The two opposite piston areas 6 and 7 of the main piston are equal, and thus no resulting force influences the main piston in the described case.
If the coil 22 is fed by a current with such polarity that the coil is lifted against the force of the springs 19, the sleeve 3 moves away from the cylinder 1. Hereby it opens for the openings 15 and chokes the openings 14 more than previously, so that the pressure decreases in the chamber 5 and increases in the chamber 4. The main piston 2 is then influenced by a resulting force, which is proportional to the pressure difference in the chambers 4 and 5, and which is acting in the same direction as the sleeve 3 moved. The main piston 2 thus follows the sleeve 3 and does not stop until a new equilibrium is obtained when the openings 14 and 15 again are equally choked.
When the main piston 2 is loaded, it will be displaced to a new position of equilibrium, where the holes 14 and 15 are choked to a different degree, so that the pressure medium acts upon the main piston 2 with a force which is equal to and counteracting the load. This displacement of the position of equilibrium by loading is equivalent to a certain elasticity in the servo-motor.
When the pressure medium passes an edge of the sleeve 3 at the outlet from one of the openings 14 and 15, it influences the sleeve with an axial force, the magnitude of which may be reduced by making the edge sharp and knife-like, but never can be entirely eliminated. Because the sleeve 3 is influenced by two counteracting axial forces of this sort, one at the openings 14 and one at the openings 15, the resulting axial force of the sleeve becomes, however, negligible. Even though each of the said axial forces are pressureand temperature-dependent, the force with which the servo-motor reacts on the sleeve thus becomes practically constant and equal to zero.
As the ducts 8 and 9 may be made identically equal, their flow resistances become not only equal, but obtain even the same pressureand temperature-dependence. The same is true for the openings 14 and 15 with appurtenant choking edges of the sleeve 3. This symmetry provides for a compensation of a change in pressure in the chamber 4, caused by a change in temperature of pressure at the source 10, by an equal pressure change in the chamber 5. The resulting force on the main piston 2 and the position of the main piston in relation to the sleeve 3 thus becomes independent of pressure and temperature.
In Fig. 2 is shown another form of the invention, which differs from the form shown in Fig. 1 only in the arrangement of the restricted ducts 8 and 9. The main piston 2 is in Fig. 2 provided with an annular groove between the piston areas 6 and 7, so that a chamber 20 is obtained, which is directly connected t0 the source for the pressure medium. The restricted ducts 8 and 9 are arranged in the main piston 2 itself, and connects the chambers 4 and 5 with the chamber 20. This form of the invention has certain manufacturing advantages over the form shown in Fig. l, but the manner of operation is entirely identical for the two forms.
The openings 14 and 15 are of course always arranged symmetrically around the axis of the cylindrical body 11, so that the sleeve 3 is not influenced by any resulting radial force which may give rise to friction between the sleeve 3 and the cylindrical body 11. In order to eliminate such friction entirely, symmetrically arranged openings may be provided, discharging behind the inner surface of the sleeve 3, and in a known manner communicating through restricted ducts with one of the chambers 4 or 5, or better the chamber in Fig. 2.
We claim as our invention:
1. Hydraulic servo-motor comprising a cylinder, and a double-acting piston reciprocatably movable in said cylinder and dividing the interior of said cylinder into two main chambers, means including a restricted passage for connecting each of said main chambers to a source of pressure iluid, a cylindrical body connected to said piston and protruding from said cylinder openings located in the peripheral surface of said cylindrical body and arranged in two axially displaced groups of openings, means for connecting each of said groups of openings to one of said main chambers, a sleeve fitting with small clearance on said cylindrical body and serving to cover and uncover said openings, said sleeve having an axial length substantially equal to the axial distance between said two groups of openings, and means for axially displacing said sleeve in dependence on a control magnitude.
2. Hydraulic servo-motor comprising a cylinder, and a double-acting piston having two substantially equal and counteracting working areas being reciprocatably movable in said cylinder and dividing the interior of said cylinder into two main chambers, an annular groove in said piston between said working areas, means for connecting said annular groove to a source of pressure fluid, restricted ducts connecting said annular groove and said main chambers, a cylindrical body connected to said piston and protruding from said cylinder, openings located in the peripheral surface of said cylindrical body and arranged in two axially displaced groups of openings, means for connecting each of said groups of openings to one of said main chambers, a sleeve fitting with small clearance on said cylindrical body and serving to cover and uncover said openings, said sleeve having an axial length substantially equal to the axial distance between said two groups of openings, and means for axially displacing said sleeve in dependence on a control magnitude.
References Cited in the file of this patent UNITED STATES PATENTS 1,004,541 Martin Sept. 26, 1911 1,640,526 Bragg et al Aug. 30, 1927 2,615,466 Garde Oct. 28, 1952
US569631A 1955-03-08 1956-03-05 Hydraulic servo-motor Expired - Lifetime US2813519A (en)

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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2943607A (en) * 1957-03-25 1960-07-05 Woodward Governor Co Power actuated pressure measuring and indicating device
US2989987A (en) * 1956-05-07 1961-06-27 Sanders Associates Inc 2-stage hydraulic servo valve
US3029830A (en) * 1957-11-06 1962-04-17 Garrett Corp Servo valve
US3045651A (en) * 1960-06-03 1962-07-24 Sughrue Rothwell Mion & Zinn Servo motor
US3056416A (en) * 1958-07-11 1962-10-02 Nat Res Dev Control means for fluid pressure systems
US3123677A (en) * 1957-07-08 1964-03-03 Magnetic recording system
US3251274A (en) * 1962-03-16 1966-05-17 Garrett Corp Pneumatic remote position actuator
US3354785A (en) * 1964-03-27 1967-11-28 Kawasaki Heavy Ind Ltd Mechanism for mutual change between different types of displacement and an amplifier of force or torque
US3465644A (en) * 1966-03-09 1969-09-09 Boeing Co Vertical motion positioning system
US3515031A (en) * 1967-11-06 1970-06-02 Eaton Yale & Towne Hydraulic booster motor
US3800663A (en) * 1971-12-03 1974-04-02 Applied Power Ind Inc Proportional force amplifier
US3805835A (en) * 1972-05-12 1974-04-23 Garrett Corp Fluid control valve
US4095774A (en) * 1977-01-31 1978-06-20 Garnett Bruce L Cam regulated flow control valve
US4388942A (en) * 1980-01-22 1983-06-21 Tokyo Keiki Co., Ltd. Nozzle flapper valve
US4432033A (en) * 1982-07-01 1984-02-14 Brundage Robert W Power source for a solenoid controlled fluid pressure device
US4454800A (en) * 1978-11-08 1984-06-19 Feinmechanische Werke Mainz Gmbh Active mechanical hydraulic control apparatus
US4464977A (en) * 1980-11-12 1984-08-14 Brundage Robert W Fluid pressure device
US4553735A (en) * 1982-01-13 1985-11-19 Brundage Robert W Solenoid controlled valve
US4596271A (en) * 1980-10-02 1986-06-24 Brundage Robert W Fluid pressure device
US4722312A (en) * 1985-08-12 1988-02-02 Kabushiki Kaisha Toyota Chuo Kenkyusho Electro-pressure conversion control device

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1004541A (en) * 1911-03-22 1911-09-26 Frederick E Martin Fluid-pressure control.
US1640526A (en) * 1924-11-06 1927-08-30 Bragg Kliesrath Corp Power actuator
US2615466A (en) * 1942-09-10 1952-10-28 Asea Ab Balanced pilot valve for hydraulic main valves

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1004541A (en) * 1911-03-22 1911-09-26 Frederick E Martin Fluid-pressure control.
US1640526A (en) * 1924-11-06 1927-08-30 Bragg Kliesrath Corp Power actuator
US2615466A (en) * 1942-09-10 1952-10-28 Asea Ab Balanced pilot valve for hydraulic main valves

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2989987A (en) * 1956-05-07 1961-06-27 Sanders Associates Inc 2-stage hydraulic servo valve
US2943607A (en) * 1957-03-25 1960-07-05 Woodward Governor Co Power actuated pressure measuring and indicating device
US3123677A (en) * 1957-07-08 1964-03-03 Magnetic recording system
US3029830A (en) * 1957-11-06 1962-04-17 Garrett Corp Servo valve
US3056416A (en) * 1958-07-11 1962-10-02 Nat Res Dev Control means for fluid pressure systems
US3045651A (en) * 1960-06-03 1962-07-24 Sughrue Rothwell Mion & Zinn Servo motor
US3251274A (en) * 1962-03-16 1966-05-17 Garrett Corp Pneumatic remote position actuator
US3354785A (en) * 1964-03-27 1967-11-28 Kawasaki Heavy Ind Ltd Mechanism for mutual change between different types of displacement and an amplifier of force or torque
US3465644A (en) * 1966-03-09 1969-09-09 Boeing Co Vertical motion positioning system
US3515031A (en) * 1967-11-06 1970-06-02 Eaton Yale & Towne Hydraulic booster motor
US3800663A (en) * 1971-12-03 1974-04-02 Applied Power Ind Inc Proportional force amplifier
US3805835A (en) * 1972-05-12 1974-04-23 Garrett Corp Fluid control valve
US4095774A (en) * 1977-01-31 1978-06-20 Garnett Bruce L Cam regulated flow control valve
US4454800A (en) * 1978-11-08 1984-06-19 Feinmechanische Werke Mainz Gmbh Active mechanical hydraulic control apparatus
US4388942A (en) * 1980-01-22 1983-06-21 Tokyo Keiki Co., Ltd. Nozzle flapper valve
US4596271A (en) * 1980-10-02 1986-06-24 Brundage Robert W Fluid pressure device
US4464977A (en) * 1980-11-12 1984-08-14 Brundage Robert W Fluid pressure device
US4553735A (en) * 1982-01-13 1985-11-19 Brundage Robert W Solenoid controlled valve
US4432033A (en) * 1982-07-01 1984-02-14 Brundage Robert W Power source for a solenoid controlled fluid pressure device
US4722312A (en) * 1985-08-12 1988-02-02 Kabushiki Kaisha Toyota Chuo Kenkyusho Electro-pressure conversion control device

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