US3880554A - Operating mechanism for steering systems or the like - Google Patents

Operating mechanism for steering systems or the like Download PDF

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Publication number
US3880554A
US3880554A US409698A US40969873A US3880554A US 3880554 A US3880554 A US 3880554A US 409698 A US409698 A US 409698A US 40969873 A US40969873 A US 40969873A US 3880554 A US3880554 A US 3880554A
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US
United States
Prior art keywords
central bore
piston
rotary
casing
star
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US409698A
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English (en)
Inventor
Poul Erik Termansen
Johannes Vagn Baatrup
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.)
Danfoss AS
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Danfoss AS
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Publication date
Application filed by Danfoss AS filed Critical Danfoss AS
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Publication of US3880554A publication Critical patent/US3880554A/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/09—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by means for actuating valves
    • B62D5/093—Telemotor driven by steering wheel movement
    • B62D5/097—Telemotor driven by steering wheel movement gerotor type
    • 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

Definitions

  • ABSTRACT Ma Primary Exumim'r.
  • the invention relates to a metering type control unit for a power steering system.
  • Units of this type most commonly utilize gerotor type gear sets for the metering operation.
  • a problem with this unit is that highly pressurized fluid leaks from the expansible chambers formed between the star and ring members of the gerotor to the central bore of the star.
  • Control units of this type require a universal drive between the rotatable valve thereof and the star which has a combination rotating and orbiting movement
  • the universal drive has a sealing flange associated therewith which serves to enclose the central bore of the star so that a fluid tight chamber is formed Fluid is trapped in this central bore with the result that the pressure differential between the expansible chambers and this central bore is minimized and leakage is consequently minimized
  • the invention relates to an operating mechanism for steering systems or the like in which the pressure medium for moving a work motor is passed to the supply side through a rotary-piston metering motor.
  • the rotat ing and circulating piston of which is connected by way of a compensating coupling, which extends into a cavity in the piston, to an outer rotary-slide sleeve which, together with a bore in the casing of the mechanism, forms a distributor valve for the metering motor, and in which a steering shaft is connected to an inner rotary-slide sleeve which is rotatable relatively to the outer rotary-slide sleeve, against the force of a return spring, through an angle delimited by stops and which. together with this sleeve, forms a reversing valve optionally having neutral-position holes.
  • the rotary piston which takes the form of an externally toothed wheel is connected to the outer rotary-slide sleeve by way of a universal-joint shaft and a pin extending through the inner rotary-slide sleeve. there being clearance between the pin and sleeve.
  • the return spring consists of two curved strips which extend substantially in the diametral direction and which pass through complementary openings in the two rotary-slide sleeves.
  • the pump-side port communicates with an outer channel in the outer rotary-slide sleeve from which extend on the one hand the neutral-position holes and on the other further pressure-side distributing openings.
  • the cavity in the piston and the interior of the inner rotary-slide sleeve are connected to the discharge-side port by way of openings, extending through the two sleeves, and annular channels.
  • the object ofthe present invention is to increase the operating accuracy of a mechanism of this kind.
  • this object is achieved by bringing a seal between the inner cavity in the piston and the discharge-side port, at least while the metering motor is operating.
  • the seal in question does not need to be absolutely tight; it suffices if a flow restricting seal is created the effect of which is so pronounced that a pressure building up in the cavity in the piston is permitted to relax very slowly towards the discharge side.
  • the leakages from the metering motor are extremely small. Consequently rotation of the metering motor constitutes a precise image of the displacement of the working motor. Since the metering motor is disposed on the supply side, a pressure in the order of magnitude of I atmos, e.g. 7O I40 atmos, obtains in its displacement chambers.
  • the cavity in the piston is normally filled with oil. Because of the presence of the seal this oil acquires a pressure corresponding to that in the displacement chambers as soon as a trace of leaked oil passes along the end face of the piston and into the cavity. However, any further leakage is thus inhibited or kept negligibly small. Instead of this, the pressure in the cavity can be constantly held at a correspondingly high level by means of a suitable connection with the pumpside port.
  • the compensating coupling is a cross-disc-type coupling (Oldham coupling), and the seal is formed along the periphery of a part coaxial with the rotary-slide sleeves. Even with a simple sliding fit, the cavity in the piston can be closed off satisfactorily.
  • the co-axial part carries a sealing flange which is disposed on that side of the end disc remote from the piston.
  • the interior of the inner rotary-slide sleeve is connected to the pump-side port.
  • this rotary-slide sleeve acts as a sealing element which permits the pressure in the cavity in the piston to be maintained irrespective of whether the interior of the sleeve communicates directly with the cavity in the piston or whether it communicates with the pressure chamber adjoining the sealing flange.
  • FIG. 1 is a longitudinal section through an operating mechanism of the invention, on the line HH of FIG. 2-
  • FIG. 2 is an end view from the left of the mechanism shown in FIG. 1,
  • FIG. 3 is a section on the line 33 of FIG. 1,
  • FIG. 4 is a section on the line 44 of FIG. 1,
  • FIG. 5 is a section on the line 5-5 of FIG. 1,
  • FIG. 6 is a section on the line 66 of FIG. 1.
  • FIG. 8 is a section on the line 88 of FIG. 1,
  • FIG. 9 is a section on the line 9-9 of FIG. I
  • FIG. 10 is a section on the line 10-10 of FIG. 2.
  • the operating mechanism has a casing l which includes a port 2 for connection to a pump 3, a port 4 for discharge of oil into a tank 5, and ports 6 and 7 for connection to a working motor 8.
  • An internally toothed ring 10 with an end plate II is screwed onto one end of the casing, an end disc 9 being interposed between the ring and the casing.
  • a cover plate I2 is secured to the opposite end face of the casing. The parts are held together by means of screw-bolts 13.
  • a steering shaft 14 is formed integrally with a valve tube I5 which together with a closure tube I6 forms an inner rotary-slide sleeve 17. The latter is surrounded by an outer rotary-slide sleeve 18 which in turn is accommodated in a bore 19 of the casing.
  • the outer rotary-slide sleeve 18 is connected by means of a compensating coupling 20 to a rotary piston 21 in the form of an externally toothed wheel. Displacement chambers are formed between this wheel and the toothed ring 10.
  • the piston 21 has a cavity 22 which, with the piston, is able to execute a circulating and rotary movement.
  • the compensating coupling is designed as a cross-disc-type or Oldham coupling. It
  • first part 23 which is disposed co-axially with the rotary-slide sleeves I7 and I8 and has a projection 24 which extends into a complementary channel in an intermediate part 25 which in turn. by way of a projection 26 extending at right angles to the projection 24, is displaceable in a channel formed in the piston 2I.
  • the interior 3] of the sleeve 17 can be caused to communicate with the dischargeside port 4 only by way of neutral-position holes 34 which are formed in the rotary-slide sleeves 17 and 18 and are gradually closed as the steering shaft 14 is rotated. and by way of an annular channel 35 formed at that end of the bore 19 in the casing remote from the metering motor.
  • Part 23 of the coupling also has a radial projection 36 which engages in matching recesses 37 at the uncovered end face of the outer rotary-slide sleeve 18 and in larger recesses 38 at the uncovered end face of the inner rotary-slide sleeve 17. Consequently the outer rotary-slide sleeve 18 is connected to the coupling part 23 so that the two rotate together. Furthermore, relative rotation of the inner and outer rotary-slide sleeves 17 and 18 is possible, this rotation being limited by the recesses 38.
  • a return spring 39 is formed as a ring, the in wardiy bent ends 40 of which engage in mutually similar openings 41 and 42 at the uncovered end-faces of the two rotary-slide sleeves 17 and 18. This spring returns both sleeves to their neutral positions upon completion of each steering movement (FIG. 9).
  • a combination valve 43 Also provided in the casing is a combination valve 43, and the only fact concerning this valve that is of interest here is that its closing member 44 operates as a return valve and opens when the neutral-position holes 34 are throttled. A duct leading to an annular channel 45 in the casing is then opened and is connected. through radial bores 46 in the outer rotary-slide sleeve 18 (FIG. 4) and axial channels 47 in the inner rotaryslide sleeve 17, to each second control opening 49a in the outer rotary-slide sleeve 18, each of these second control openings, together with the control openings 49b, disposed between them.
  • control openings 4% are connected to an annular channel 56 in the bore 19 of the casing (FIG. 5) by way of bores 52a in the valve tube 15, axial channels 53a in the closure tube 16 (FIG. 3), bores 54a in the valve tube 15 and bores 55 in the outer rotary-slide sleeve 18.
  • Bores 52b and axial channels 53b are used when the mechanism is operating in the other direction when, instead of the annular channel 56, the annular channel 57 alongside it and formed in the bore 19 of the casing, is connected to the discharge side of the metering motor.
  • Each of the annular channels 56 and 57 is connected to one side of the working motor 8. Disposed between them is a two-way excess-pressure valve which is likewise accommodated in the casing 1.
  • FIGS. 5 and 6 show similar constructions with bores 54b and 60b. The functions of the corresponding ducts are transposed when the direction of rotation changes.
  • the inner rotary-slide sleeve 17 is turned so far relatively to the outer rotaryslide sleeve 18 in the position illustrated that the metering motor turns in one of the directions corresponding to the rotation of the steering shaft 14, and when this happens the motor causes the outer rotary-slide sleeve to follow the inner rotary'slide sleeve.
  • the neutral position is reached, the neutral-position holes 34 move into register again on the one hand, whereas on the other hand the axial channels 47 (FIG. 3) in the inner rotary-slide sleeve 17 are separated from the control openings 49a in the outer rotary-slide sleeve 18.
  • a metering unit for steering systems comprising a casing, a rotary piston in said casing having a rotatable movement relative to its own axis and an orbitable movement relative to the casing axis, a toothed ring member surrounding said piston, said piston having a central bore.
  • a disk having a central bore attached to one side of said ring member, and a closure member attached to the other side of said ring member, said disk and said closure member constituting walls for expansible chambers formed between said rotary piston and said ring member, a rotary valve rotatable about said casing axis, a drive mechanism between said valve and said piston, said drive mechanism being in sealing engagement with said disk to enclose said piston central bore along with said closure member so that said piston central bore forms a fluid tight chamber.
  • neutral position valve means for selectively providing fluid communication between said rotary valve means central bore and said outlet port.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Multiple-Way Valves (AREA)
  • Power Steering Mechanism (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Hydraulic Motors (AREA)
US409698A 1972-11-02 1973-10-25 Operating mechanism for steering systems or the like Expired - Lifetime US3880554A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2253575A DE2253575C3 (de) 1972-11-02 1972-11-02 Hydraulische Steuereinrichtung für Lenkungen, insbesondere für Fahrzeuglenkungen

Publications (1)

Publication Number Publication Date
US3880554A true US3880554A (en) 1975-04-29

Family

ID=5860621

Family Applications (1)

Application Number Title Priority Date Filing Date
US409698A Expired - Lifetime US3880554A (en) 1972-11-02 1973-10-25 Operating mechanism for steering systems or the like

Country Status (11)

Country Link
US (1) US3880554A (enrdf_load_stackoverflow)
JP (1) JPS5245575B2 (enrdf_load_stackoverflow)
BE (1) BE805774A (enrdf_load_stackoverflow)
CH (1) CH561853A5 (enrdf_load_stackoverflow)
DD (1) DD112500A5 (enrdf_load_stackoverflow)
DE (1) DE2253575C3 (enrdf_load_stackoverflow)
DK (1) DK133199C (enrdf_load_stackoverflow)
FR (1) FR2205877A5 (enrdf_load_stackoverflow)
GB (1) GB1446880A (enrdf_load_stackoverflow)
IT (1) IT996865B (enrdf_load_stackoverflow)
NL (1) NL7315018A (enrdf_load_stackoverflow)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4076462A (en) * 1976-07-26 1978-02-28 W. H. Nichols Company Combined distributor and bypass valve for fluid actuated pump or motor
US4494915A (en) * 1979-06-25 1985-01-22 White Hollis Newcomb Jun Hydrostatic steering unit with cylindrical slide member within clindrical valve sleeve
US4579040A (en) * 1983-04-28 1986-04-01 Jidosha Kiki Co., Ltd. Power steering device
US4606896A (en) * 1984-02-07 1986-08-19 Charbonnages De France Apparatus for supplying a controlled flow of gas to a fluidized grid
US4671747A (en) * 1985-02-14 1987-06-09 Danfoss A/S Control device for hydrostatic power assisted steering
US5136844A (en) * 1990-10-11 1992-08-11 Eaton Corportaion Controller with reduced travel limit slip
US20050088041A1 (en) * 2003-10-23 2005-04-28 Xingen Dong Housing including shock valves for use in a gerotor motor
US20100150761A1 (en) * 2008-12-17 2010-06-17 Sauer-Danfoss Aps Hydraulic machine
CN101885349A (zh) * 2010-07-12 2010-11-17 尹凤金 整体式多功能全液压转向器
CN105805351A (zh) * 2016-04-19 2016-07-27 沈阳工业大学通益科技有限公司 一种油田多通阀
US12024243B2 (en) 2018-10-09 2024-07-02 Nishina Industrial Co., Ltd. Power steering valve

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3931711A (en) * 1974-11-06 1976-01-13 Trw Inc. Controller assembly
DE2825006C2 (de) * 1977-06-11 1986-08-28 Bendiberica, S.A., Barcelona Steuerventil, insbesondere für Hilfskraftlenkungen
DE2830292C2 (de) * 1978-07-10 1980-08-07 Danfoss A/S, Nordborg (Daenemark) Hydraulisches Steuergerät für den Servomotor einer Lenkeinrichtung
DE2906183C2 (de) 1979-02-17 1986-09-18 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydrostatische Lenkeinrichtung für Kraftfahrzeuge
DE3031230C2 (de) * 1980-08-19 1986-03-13 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hydrostatische Hilfskraftlenkeinrichtung
DE3228345C2 (de) * 1982-07-29 1987-04-09 Günter 8882 Lauingen Stein Steuervorrichtung für flüssiges oder gasförmiges Medium
DE3930147A1 (de) * 1989-09-09 1991-03-21 Danfoss As Hydraulische lenkeinheit

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3286645A (en) * 1965-07-09 1966-11-22 Char Lynn Co Rotary fluid pressure device
US3289542A (en) * 1963-10-29 1966-12-06 Lawrence Machine & Mfg Company Hydraulic motor or pump
US3302584A (en) * 1965-09-01 1967-02-07 Char Lynn Co Valving arrangement for fluid pressure device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3289542A (en) * 1963-10-29 1966-12-06 Lawrence Machine & Mfg Company Hydraulic motor or pump
US3286645A (en) * 1965-07-09 1966-11-22 Char Lynn Co Rotary fluid pressure device
US3302584A (en) * 1965-09-01 1967-02-07 Char Lynn Co Valving arrangement for fluid pressure device

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4076462A (en) * 1976-07-26 1978-02-28 W. H. Nichols Company Combined distributor and bypass valve for fluid actuated pump or motor
US4494915A (en) * 1979-06-25 1985-01-22 White Hollis Newcomb Jun Hydrostatic steering unit with cylindrical slide member within clindrical valve sleeve
US4579040A (en) * 1983-04-28 1986-04-01 Jidosha Kiki Co., Ltd. Power steering device
US4606896A (en) * 1984-02-07 1986-08-19 Charbonnages De France Apparatus for supplying a controlled flow of gas to a fluidized grid
US4671747A (en) * 1985-02-14 1987-06-09 Danfoss A/S Control device for hydrostatic power assisted steering
US5136844A (en) * 1990-10-11 1992-08-11 Eaton Corportaion Controller with reduced travel limit slip
US20050088041A1 (en) * 2003-10-23 2005-04-28 Xingen Dong Housing including shock valves for use in a gerotor motor
US7255544B2 (en) * 2003-10-23 2007-08-14 Parker-Hannifin Housing including shock valves for use in a gerotor motor
US20100150761A1 (en) * 2008-12-17 2010-06-17 Sauer-Danfoss Aps Hydraulic machine
US8444404B2 (en) * 2008-12-17 2013-05-21 Sauer-Danfoss Aps Hydraulic machine
CN101885349A (zh) * 2010-07-12 2010-11-17 尹凤金 整体式多功能全液压转向器
CN105805351A (zh) * 2016-04-19 2016-07-27 沈阳工业大学通益科技有限公司 一种油田多通阀
US12024243B2 (en) 2018-10-09 2024-07-02 Nishina Industrial Co., Ltd. Power steering valve

Also Published As

Publication number Publication date
CH561853A5 (enrdf_load_stackoverflow) 1975-05-15
DE2253575B2 (de) 1974-09-12
DD112500A5 (enrdf_load_stackoverflow) 1975-04-12
DK133199B (da) 1976-04-05
JPS4976236A (enrdf_load_stackoverflow) 1974-07-23
GB1446880A (en) 1976-08-18
DE2253575A1 (de) 1974-05-22
FR2205877A5 (enrdf_load_stackoverflow) 1974-05-31
DE2253575C3 (de) 1975-04-24
NL7315018A (enrdf_load_stackoverflow) 1974-05-06
IT996865B (it) 1975-12-10
DK133199C (da) 1976-09-13
JPS5245575B2 (enrdf_load_stackoverflow) 1977-11-17
BE805774A (fr) 1974-02-01

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