USRE23867E - Power steering booster of the - Google Patents

Power steering booster of the Download PDF

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Publication number
USRE23867E
USRE23867E US23867DE USRE23867E US RE23867 E USRE23867 E US RE23867E US 23867D E US23867D E US 23867DE US RE23867 E USRE23867 E US RE23867E
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Prior art keywords
valve
fluid
steering
pressure
motor
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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
    • 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
    • B62D5/08—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 type of steering valve used
    • B62D5/087—Sliding spool valves

Definitions

  • Hydraulic steering boosters of the prior art adapted for actuation and control by the steering wheel of a vehicle comprise generally a fluid motor usually consisting of a piston-cylinder assembly actuated by hydraulic fluid, the flow of which is controlled by valve mechanism connected with the steering wheel of the vehicle.
  • the motor and valve control are integrally connected and adapted for installation either in the drag link or at the base of the steering shaft.
  • a principal object of the present invention to provide a hydraulic steering booster adapted for utility and application to motor graders, truck, truck cranes, wheel-type tractors, or the like, comprising essentially a double acting hydraulic cylinder adapted for direct connection to the steered wheels or other parts of the vehicle and supplied with hydraulic power controlled by valve mechanism assembled in the drag link, whereby the valve assembly is in proximate association with its manually operable motivating force and the power of the system is applied directly to the work.
  • an object is to provide a fourway valve connected to a source of fluid under pressure and to a reservoir tank for the continuous circulation therethrough of the fluid, in combination with means for diverting the flow into, selectively, either end of a power cylinder to actuate the piston therein, the cylinder being normally in open communication with the circulating system whereby the normal caster of the steered wheels is permitted to return the latter to forward, intermediate alignment and to correspondingly reposition the piston for subsequent activation.
  • Another and highly important object is the provision of dual means for returning the valve to a neutral or inoperative position, comprising essentially normally balanced resilient elements arranged in opposition to one another, the balance of which is upset incident to operative adjustment of the valve, and fluid pressure elements actuated by the hydraulic circulating system, each of the two components of the composite mechanism being individually and jointly operable to produce a pre-determined measure of resistance to manual adjustment of the valve.
  • Still another and related object is the provision of a telescopic control valve comprising a pair of pressure actuated rings operable to normally bear against the complementary ends, respectively, of the telescopically related valve elements in response to pressure of the hydraulic system, relative longitudinal movement between the valve elements being effective to concentrate the pressure of the rings upon the extended ends of the individual elements, so as to utilize the pressure of the system for returning the valve to a neutral or normal position and induce a resistance against manual adjustment of the valve proportionate to the resistance of the load.
  • Fig. l is a perspective view of a preferred embodiment of my invention, illustrating a typical installation
  • Fig. 2 is a longitudinal section through the control valve assembly showing the elements of the valve in neutral positions
  • Fig. 3 is a fragmentary longitudinal section taken in a different plane from that of Fig. 1 illustrating the outlet passage formed in the valve cage;
  • Fig. 4 is a longitudinal section through the control valve depicting the valve elements in an extreme position in response to the thrust of an actuating force applied to the direction of the arrow;
  • Fig. 5 is a longitudinal sectional view through the control valve presenting the parts in their relative positions which are assumed as a result -of a tubular valve casing 26.
  • Fig. 1 a hydraulic telescopic valve l adapted for interposition in a composite drag link I8 of the vehicle for controlling the flow or hydraulic fluid to a double acting power cylinder-piston assembly generally indicated at II and connected between the axle I2 of the vehicle and a tie rod I3.
  • the valve I3 is actuated and controlled incident to longitudinal movement of the drag link, which movement is imparted thereto by a pitman arm I3 connected to the steering shaft I5 of the vehicle by a lateral shaft I6 through conventional worm reduction gearing generally indicated at I1. Rotation of the steering wheel (not shown) of the vehicle thus swings the pitman arm I4 arcuately forward or backward depending upon the direction of rotation of the wheel in accordance with conventional construction and operation.
  • the rear end of the drag link [3 is connected to the pitman arm I4 by a ball and socket joint indicated in Fig. 1 at l9.
  • the forward end of the drag link I8 is connected to the steered parts of the vehicle by the usual linkage which includes a steering arm 20 and the tie rod I3, above-referred to.
  • a closed hydraulic circulating system for supplying power to the cylinder-piston assembly II, and includes a pump 2
  • the fluid is drawn by the pump 2
  • With the control valve I3 in neutral position, later described, the pump 2
  • the valve II is operatable to divert hydraulic fluid under the pressure of the pump 2
  • the composite drag link I3 and control valve l3 assembly comprises a drag link section 23 carrying at its rearward end the socket 24 of the joint I9, accommodating the ball (not shown) of the pitman arm I4.
  • the forward end of the link section 23 is encircled by a collar 25, welded or otherwise secured thereto.
  • the collar is threadedly engaged with one end of the bore
  • the opposite or forward end of the casing 26 receives a socket sleeve 21 having a lateral opening 28 therein for projection of the ball 29 with which the steering arm 23 is equipped.
  • the steering arm 23 and ball 29 are permitted a limited range of movement relative to the pitman arm l4.
  • secured rigidly to opposite ends, respectively, of an intermediate valve cage 32 by screws 33.
  • the cage 32 is held rigidly with respect to the casing 26, sleeve 21 and link section 23 and moved longitudinally therewith in response to motivation by the pit- When i man arm l4.
  • a ported valve sleeve 34 is clamped between the valve heads 33 and 3
  • hoses 36, 31, 33 and 39 which are threadedly attached in complementary openings 43 of the valve 'cage 32.
  • Two of the hoses 36 and 31 are connected to the pump 2
  • the other two hoses 33 and 39 are connected through the bulkhead 4
  • the cylinder 42 is pivotally mounted as at 43 to the axle of the vehicle and incorporates a piston 44 (indicated in dotted lines in Fig. l).
  • the piston rod 44a is in turn connected by a ball and socket joint 45 to the tie rod I3.
  • an inlet passa e 50 extending longitudinally therethrough, which communicates the annular inlet recess 46 to an annular recess 5
  • the annular outlet recess 41 connected with the outlet hose 31, is similarly communicated with another annular recess 52 in the forward end of the bore of the valve cage 32, by an outlet passage 32 formed in the body of the cage for a purpose later described (Fig. 3).
  • Ports 93 in the sleeve register with the recess 52 so as to communicate the bore of the sleeve adjacent ports 83 with the outlet passage 82.
  • valve plunger 53 Within the bore of the valve sleeve 34 is a relatively reciprocable valve plunger 53, the rearward closed end of which projects slidably into the bore of the adjacent valve head 33 and is sealed therewith throughout the range of relative movement by a ring seal 54.
  • the opposite end of valve plunger 53 is threaded for attachment to the end of a rod 55 which seals the corresponding end of the bore of plunger 53 and projects forwardly through the hub 56 of a ball socket housing 51, relative to which the rod 55 is very slightly telescopically extensible and contractible.
  • a nut 53 threaded on the end of the rod 55 within the bore of the housing 51 limits extension of these parts.
  • the ball socket housing 51 is provided with a lateral opening 59 complementary to the opening 23 in the socket sleeve 21 so as to receive the steering arm 23.
  • a spring seat 63 Encircling the hub 56 of the socket housing 51 and the rod 55 is a spring seat 63 having an inner annular flange 6
  • a helical spring 64 interposed between the spring seat 63 and socket housing 51 maintains the spring seat in contact with the adjacent valve head 3
  • the sleeve 21 encloses a second spring seat 85 and a plug 65 threaded into the end of the sleeve.
  • the spring seat 65 slidably encircles a threaded axial boss 51 integral with the plug with which an inner annular flange 59 of the seat 85 is in slidable association.
  • the flange 98 is loosely confined between a nut 59 and the body of the plug 85.
  • a spring HI identical to the spring 64 encircles the spring seat 65 so as to exert an expansive urge against the plug 65 and urges the spring seat 85 against the adjacent end of the socket housing 51 in opposition to the urge of the spring 84.
  • the socket housing 51 encloses a pair of socket elements H and 12 adapted for reception therebetween of the ball 29 of the steering arm 20 comprising a part of the linkage by which the steered parts are normally actuated.
  • One element II is threaded in the end of the socket housing 51.
  • a helical spring 13 enclosed by a collar 14, fitted in the bore of the socket housing 51 between the base of the latter and the other socket element 12 bears against the back of the last-named element so as to resiliently confine the ball 29 of the steering arm.
  • I5 indicates a grease fitting by which the socket assembly may be lubricated.
  • the valve plunger 53 is formed with a pair of annular enlargements comprising valves 18 and 11, the former controlling flow through two series oi ports 18 and I9 in the valve sleeve 34 registering with the annular recess 48 communicated with the power hose 38, and the second valve 11 correspondingly controlling flow through two series of ports 80 and 8
  • the respective valve enlargements 16 and 11 are slidable with the bore of the valve sleeve 34 and are adapted in response to limited longitudinal relative movement between the valve elements to close and open simultaneously one or the other of a series of ports communicated with the respective annular recesses 48 and 49, as will appear.
  • the annular valves and 11 are of a length and are spaced apart on the plunger 2. distance proportioned with the spacing of the ports l8, I9, 90 and 8
  • Each end of the valve sleeve 34 is diametrically enlarged to accommodate pressure slip rings 84 and 85, slidably fitted between the plunger and sleeve.
  • the plunger is formed with a pair of annular enlargements 8G and 81 at opposite ends and with the valve in neutral position as seen in Fig. 2 are flush with the shoulders 88 and 89, respectively, formed by the diametric enlargement of the ends of the sleeve, whereby the ring at each end of the valve is normally adapted to contact both the adjacent enlargement and the shoulder.
  • the plunger is formed with ports 90 which are in alignment with the ports 83 and recess 5
  • are in open communication with the bore of the valve plunger 53 throughout the range of relative movement between the plunger and sleeve and accordingly, the rings 84 and 85 are, at all times, forced in response to the variable pressure of the pump 2
  • Any relative longitudinal displacement of the valve plunger 53 and sleeve 34 from their neutral relationship, wherein the enlargement and shoulder at each end of these respective parts are in flush relationship causes the ring at one end of the plunger to bear against the shoulder and simultaneously pressure is relieved upon the shoulder at the opposite end of the unit.
  • valves 16 and I1 are disposed intermediate the ports 'i8
  • the opposite ends of the power cylinder 42 are in opencommunica tion through the hoses 88 and 88 with the bore of the valve sleeve 84 between the valves 18 and 11 and the pressure within the cylinder at opposite sides of the piston 44 therein is equally maintained.
  • Fluid flowing through the ports '88 enters the output passage 82 through the ports 83 in the sleeve 34 and thence returns to the reservoir through hose '38.
  • fluid returning to the bore of the sleeve 84 through ports 19 flows through the port 84 in the sleeve into hose 88 and thence to the reservoir.
  • the steering wheel is turned in a conventional manner which is-operable to swing the pitman arm l4 in one direction or the other. If, for example, the steering wheel is turned in a counter-clockwise direction the arm I4 is swung forwardly so as to correspondingly advance the drag link section 28 (see Fig. 4). This movement is transmitted through the valve cage 82 and valve head 8
  • valve plunger 53 is momentarily held stationary while the valve sleeve 84 is shifted forwardly with the drag link section 23.
  • are thereby closed while the ports 18 and 88, normally partially restricted, by the respective valves II and I1 are opened more fully.
  • Pressure fluid is thus diverted from the ports 8
  • pressure at the opposite side of the piston 44 is relieved through the hose 3!, ports 80, port 83 and the outlet passage 82 connected to the reservoir 22 .by the hose 31.
  • the piston 44 is thus advanced so as to mechanically impel the turning of the steered wheels, directing the vehicle to the left, in conformance with the direction of manual actuation of the steering wheel.
  • the steered parts will continue to turn in the direction impelled by the piston-cylinder assembly as long as suflicient torque is applied to the steering wheel to maintain the valve plunger 83 in an out-ofneutral relationship with the valve sleeve 84.
  • the piston 44 of the power cylinder again extends or contracts the drag link in opposition to the initial urge in the pitman arm I4 and thus promptly returns all parts of the valve to neutral positions.
  • An important feature of the present invention resides in the back pressure created in the control valve and applied to the pitman arm I4 by the pressure rings 84 and 85 which transmit to the steering wheel a resistance to turning which is less than, but at all times roportionate to, the resistance to directional variation encountered by the vehicle wheels.
  • This proportionate resistance may thus be felt by the driver through the steering wheel so as to facilitate a more prompt response to his own requirements and thereby facilitate better handling of the vehicle without imposing any strain upon the driver greater than that required to operate the control valve.
  • slip rings 84 and 85 may be increased or decreased in size to present a correspondingly greater or lesser crosssectional area to the pressure of the pump and thereby modify the magnitude of the resistance to activation of the control unit in proportion to the resistance to turning of the steered elements, that the power cylinder may be connected to any of the linkage intermediate the drag link and wheels or directly to a steered part. and that any means may be substituted for the steering wheel-pitman arm assembly to effect the longitudinal movement of the drag link which is essential to the operation of the valve mechanismall without departing from the spirit of my invention as defined by the appended claims.
  • a steering booster tor a vehicle having a steered part, steering means connected to said steered part, a fluid motor comprising a piston and cylinder, means to connect said motor to the [steered part] steering means to actuate the [latter] steered part, a source of fluid under pressure, means of communication between said source of fluid under pressure and said fluid motor, a control valve interposed in said means of communication comprising a pair of telescopically-related elements operable in response to relative telescopic movement from relative neutral positions to vary the flow of fluid from said source to said motor, manually operable means to actuate said control valve, said manually operable means including a manually swingable pitman arm, a member movable with one of said valve elements and pivotally connected to said pitman arm at a pivot point thereon, and a member movable with the other of said valve elements and pivotally connected to said steering means at a pivot point thereon, and means to direct and transmit fluid pressure from said source against at least one of said elements of said valve in a
  • a fluid motor comprising a piston and a cylinder, means to connect said motor to the steered part to actuate the latter, a source of fluid under pressure, means of communication between said source of fluid under pressure and said fluid motor, a control valve interposed in said means of communication comprising ,a: pair of telescopically-related elements operable in response to relative telescopic movement to control the flow of fluid from said source to said motor, means to actuate said control valve, and means comprising a ring forming a part of said valve to transmit fluid pressure from said source against complementary surfaces of said valve elements to resist telescopic displacement of said elements from predetermined relative positions of the latter incident to activation of said actuating means.
  • a steering booster for a vehicle having a steered part, steering means connected to said steered part, a fluid motor comprising a piston and a cylinder, means to connect said motor to the [steered part] steering means to actuate the [latter] steered part, a source of fluid under pressure, means of communication between said source of fluid under pressure and said fluid motor, a control valve interposed in said means of communication comprising a pair of telescopically-related elements operable in response to relative telescopic movement to control the flow of fluid from said source to said motor, manually operable means to actuate said control valve, said manually operable means including a manually swingable pitman arm, a member movable with one of said valve elements and pivotally connected to said pitman arms at a pivot point thereon, and a member movable with the other of said valve elements and pivotally connected to said steering means at a pivot point thereon, said valve elements having a air of shoulders flush with one another when said valve is in a telescopically neutral
  • a fluid motor comprising a piston and a cylinder, means to-connectsaid motor to the steered part to actuate the latter, a source of fluid under pressure, means of communication between said source of fluid under pressure and said fluid motor, a control valve interposed in said means of communication comprising a pair of telescopically-related elements operable in response to relative telescopic movement to control the flow of fluid from said source to said motor, means to actuate said control valve, said valve elements forming a pair of annular shoulders disposed in offset relation when said valve is in a telescopically operative position, a slip ring encircling one of said elements to bear against one of said shoulders to urge said valve elements toward a neutral position in which said shoulders are flush with one another.
  • a booster for a vehicle having a steering arm-steered part assembly and manually actuated pitman arm, a fluid motor connected to said assembly to actuate said steered part, pump mechanism to supply pressure to said fluid motor to actuate the same in accordance with correspondingly varying load requirements, means of communication between said pump mechanism and said fluid motor, a drag link connected between said pitman arm and said first-named assembly, a control valve forming a part of said drag link and comprising a pair of telescopicallyrelated valve elements for controlling the flow between said pump mechanism and said motor in response to telescopic adjustment of said elements, and means to resist telescopic adjustment of said valve elements, actuated in response to fluid pressure from said [source] pump mechanism proportionate to but less than the pressure required to actuate said motor.
  • a steering booster for a vehicle comprising a pair of steered parts connected by a tie rod actuated by a steering arm, a fluid motor comprising a cylinder and a piston connected to said tie rod to actuate said steered parts, a source of fluid under pressure, means of communication between said source of pressure and said fluid motor, means comprising a drag link connected to said steering arm to actuate the same, said drag link comprising a pair of telescopically related valve elements forming a valve interposed in, and operable to control the flow through, said means of communication, resilient means forming a part of said valve to urge said valve elements toward neutral positions, and means actuated by fluid pressure from said source to exert a variable force in urging said valve elements toward neutral positions.
  • a fluid motor comprising a piston and cylinder, means to connect said motor to said steered part to actuate the latter, a pump to supply fluid under pressure, means of communication between said pump and said fluid motor, a control valve comprising a pair of telescopically-related valve elements carried by said drag link, said valve being interposed in said means of communication to control the flow of said pressure fluid to said motor incident to telescopic adjustment of said valve elements, a ring encircling one of said valve elements and normally bearing against each of said valve elements, and means to direct pressure of said pump against said ring whereby the latter is operable to produce a resistance to telescopic actuation of said valve proportionate to the load imposed upon said motor.
  • a steerining booster having a steered part and a manually operable drag link
  • a fluid motor comprising a piston and cylinder, means to connect said motor to said steered part to actuate the latter, a pump to supply fluid under pressure, means of communication between said pump and said fluid motor, a control valve comprising a pair of telescopically-related valve elements carried by said drag link, said valve being interposed in said means 01' communication'to control the flow 01' said pressure fluid to said motor incident to telescopic adjustment or said valve elements, a ring encircling one of said valve elements and normally bearing against each of said valve elements, means to direct pressure of said pump against said ring whereby the latter is operable to produce a resistance to telescopic actuation of said valve proportionate to the load imposed upon said motor,and resilient means to resist telescopic displacement of said valve elements from a predetermined relationship.
  • a fluid motor prising a cylinder and a piston connected to said tie rod to actuate said steered parts, a source of fluid under pressure, means 01' communication between said source of pressure and said fluid motor, means comprising a drag link connected to said steering arm to actuate the same, said drag link including a pair 01' telescopically-related valve elements comprising a valve interposed in. and operable to control the flow through, said means of communication, and means actuated by fluid pressure from said source to exert a force operable to move said valve elements toward relative neutral positions.
  • said means to direct and transmit fluid pressure includes biasing means having operative connections to said valve elements for urging said valve elements in opposite directions toward said relative neutral positions thereof.
  • a steering booster as defined in claim wherein said operative connections of said biasing means to said valve elements comprise direct mechanical engagement of said biasing means with said valve elements.
  • a steering booster for a vehicle havin a steered part, steering means connected to sa d steered part, and a pitman arm
  • a hydraulic motor connected to said steering means and to a fixed part of said vehicle to actuate said steered part; a source of fluid under pressure; a control valve interposed between and connected to said motor and said source and including a pair of telescopically related elements relatively movable in opposite directions from a neutral position to control the operation of said motor, said valve elements being connected to said members, respectively, to be moved thereby relative to said neutral position in response to any change in the distance between said points; and hydraulic means supplied with fluid from said source and acting on said members for opposin any change in the distance between said points.
  • a source of hydraulic fluid under pressure a hydraulic motor operatively connected to said steering means; a link having connections to said pitman arm and said steering means, said link including two structures which are relatively movable to vary from a normal the distance between said connections of said link to said pitman arm and said steering means, said link further including valve means interposed between and connected to said motor and said source for controlling the operation 0) said motor, said valve means including relatively movable valve elements respectively forming parts of said relatively movable structures and movable therewith from a neutral position in response to any variation in said distance from said normal to control the operation of said motor; and hydraulic means acting 'on said relatively movable structures and operable by said hydraulic fluid for biasing said relatively movable structures in such directions as to tend to restore said distance to said normal in response to any variation thereof from said normal.
  • valve means includes means for maintaining said hydraulic means in constant communication with said source.
  • a booster for a vehicle having a steered assembly and a pitman arm, a fluid motor connected to said assembly, pump mechanism to supply pressure to said fluid motor to actuate the same, means of communication between said pump mechanism and said fluid motor, a link' connected between said pitman arm and said assembly, a control valve forming a part of said link and comprising a pair of telescopicallyrelated valve elements for controlling the flow between said pump mechanism and said motor in response to telescopic adiustment of said elements, and means to resist telescopic adjustment of said valve elements and changing of the length of said link, said means being actuated by fluid pressure from said pump mechanism and acting on said valve elements.
  • a steerin booster as defined in claim 1 wherein the means last defined includes means constantly urged in one direction by pressure from said source and having lost-motion connections with said valve elements.

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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)
  • Power Steering Mechanism (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
US23867D 1952-01-07 Power steering booster of the Expired USRE23867E (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB495/52A GB709310A (en) 1952-01-07 1952-01-07 Power steering booster

Publications (1)

Publication Number Publication Date
USRE23867E true USRE23867E (en) 1954-09-14

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ID=9705351

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Application Number Title Priority Date Filing Date
US23867D Expired USRE23867E (en) 1952-01-07 Power steering booster of the

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US (1) USRE23867E (da)
BE (1) BE508959A (da)
CH (1) CH315783A (da)
FR (1) FR1049803A (da)
GB (1) GB709310A (da)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2954088A (en) * 1958-09-29 1960-09-27 Bros Inc Road roller
US3038544A (en) * 1958-11-03 1962-06-12 Ford Motor Co Tractor steering means
US3602326A (en) * 1969-08-22 1971-08-31 Garrison Mfg Co Inc Dual power steering system

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE964838C (de) * 1954-01-22 1957-05-29 Paul Leboucher Hydraulische Servosteuerung, insbesondere fuer Fahrzeuge
DE944702C (de) * 1955-03-13 1956-06-21 Wilhelm Winter Hydraulische Lenkung fuer Strassenfahrzeuge mit drehbarem Oberwagen, insbesondere fuer Krane od. dgl.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2954088A (en) * 1958-09-29 1960-09-27 Bros Inc Road roller
US3038544A (en) * 1958-11-03 1962-06-12 Ford Motor Co Tractor steering means
US3602326A (en) * 1969-08-22 1971-08-31 Garrison Mfg Co Inc Dual power steering system

Also Published As

Publication number Publication date
GB709310A (en) 1954-05-19
CH315783A (fr) 1956-08-31
BE508959A (da)
FR1049803A (fr) 1954-01-04

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