US3589243A - Hydraulic drive system - Google Patents

Hydraulic drive system Download PDF

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Publication number
US3589243A
US3589243A US815251*A US3589243DA US3589243A US 3589243 A US3589243 A US 3589243A US 3589243D A US3589243D A US 3589243DA US 3589243 A US3589243 A US 3589243A
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Prior art keywords
gear
ring gear
housing
valve
inner gear
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US815251*A
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English (en)
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Spencer Bowman
Anthony Nevulis
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XEROTOL INVESTMENT Inc
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XEROTOL INVESTMENT Inc
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Assigned to XEROTOL INVESTMENT INC., reassignment XEROTOL INVESTMENT INC., ASSIGNMENT OF A PART OF ASSIGNORS INTEREST Assignors: WHEELOCK, EUGENE K.,(TRUSTEE)
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders
    • F03C1/0531—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders with cam-actuated distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
    • F03C1/2407—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H43/00—Other fluid gearing, e.g. with oscillating input or output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference

Definitions

  • HYDRAULIC DRIVE SYSTEM This invention relates to the field of hydraulic motors and, more particularly, to a hydraulic motor capable of generating a high level of torque at low speeds with high volumetric efficiency.
  • the invention is particularly applicable to apparatus such as a winch in which there is a high torque requirement at the start of its operating cycle and the invention will be described with particular reference to this type of apparatus although it will be appreciated that the invention has broader application and may be used whenever a hydraulic motor is found to be ad vantageous.
  • Hydraulic motors of various constructions are well known; however, the hydraulic motors which have been developed up to this time have an extremely poor volumetric efficiency in the lower speed ranges.
  • a typical prior art hydraulic motor operated at a speed of l revolution per minute might well have a volumetric efficiency as low as percent. It is normally necessary to operate the prior art hydraulic motors at speeds in the range of 300 rpm. before the volumetric efflciency begins to reach an acceptable value. It is not until these motors are operated at the speeds of 2000-3000 r.p.m. that the volumetric efficiency begins to look rather good.
  • a winch is a typical example in which the drive system must be capable of delivering a sufficiently high level of torque at low speeds at the very start of the operating cycle of the winch. In such circumstances it is not satisfactory to have the drive system come up to speed before applying the load.
  • the prior art has approached this problem by employing a high-speed high-torque drive together with a gear reducer which, in combination, provided the necessary low-speed high-torque output.
  • gear reducers employed, depending on the amount of gear reduction tend to be rather large units and are relatively expensive.
  • the present invention contemplates a new and improved hydraulic motor which overcomes all the above referred to problems, as well as others, and which provides a low speed drive having a high volumetric efficiency and capable of generating a high output torque at the start ofits operating cy cle.
  • the present invention is relatively simple in construction and economical to manufacture and has a broad range of potential applications.
  • a hydraulic motor comprising a housing, an output shaft rotatably supported in the housing and first inner gear means operatively connected to the shaft for rotation therewith.
  • a second ring gear means is disposed in the housing with the inner gear means having external teeth and the ring gear meanshaving internal teeth.
  • the ring gear means is supported for orbital movement into and out of meshing engagement with the inner gear means.
  • the orbital movement of the ring gear means is achieved by a hydraulic motor.
  • the number of teeth on one of the gear means is less than the number of teeth on the other of the gear means thereby effecting a gear reduction.
  • the hydraulic motor drive is so designed that leakage may be readily controlled thereby obtaining a high volumetric efficiency.
  • the hydraulic drive system provides a hydraulic lock which, in combination with the meshing gears, provide a self-locking feature.
  • a novel support arrangement for the ring gear which support is, in effect, a parallelogram or pantograph whereby the ring gear may move to positions of eccentricity relative to the longitudinal axis of the inner gear.
  • valve means which, in turn, are driven by the ring gear.
  • One of the principal objects of the invention is to provide a hydraulic motor which is capable of producing high torque at low speeds with a high volumetric efficiency.
  • Still a further object of the invention is to provide a drive system which is capable of delivering high torque at low speeds at the start of its operating cycle.
  • the invention may take physical form in certain parts and arrangement of parts, a preferred embodiment of which will be described in detail hereinafter and illustrated in the accompanying drawings which form a part hereof.
  • FIG. 1 is an end elevation view of a hydraulic device incorporating the principles of this invention, as applied to a winch;
  • FIG. 2 is a sectional view along line 2-2 of FIG. 1;
  • FIG. 3 is an elevation view, partially in section, illustrating the support for the meshing gears
  • FIG. 4 is a sectional view taken along line 44 of FIG. 1,
  • FIG. 4A is a sectional view of one of the valve housings
  • FIG. 5 is a side elevation view partially in section of a modified form of the invention
  • FIG. 6 is a sectional view along line 6-6 of FIG. 5.
  • winches typify the type of environment in which the present invention may find particular utility, it is to be understood that the invention has far broader application.
  • a winch assembly As shown in FIG. 2, a winch assembly, indicated generally by the reference numeral 10, includes a cylindrical drum 12 with spaced apart radially extending flanges 14. The drum 12 is rotatably supported by bearings 16 for rotation relative to a fixed or stationary housing, indicated generally by the reference numeral 20.
  • the housing may be considered to be in two parts, a first part 21 which is the winch housing and a second part 22 which comprises the housing for the winch drive unit.
  • first part 21 which is the winch housing
  • second part 22 which comprises the housing for the winch drive unit.
  • the two portions 21, 22 of the housing may be integral and supported on a common base 23.
  • the winch portion of the housing includes a first end wall 24 and a second end wall 25 with the end wall 25 being common to the drive portion 22 of the housing 20.
  • a shaft 26 is rotatably supported by a bearing 27 in the end wall 24 and by a bearing 28 in the end wall 25. As is apparent from FIG. 2, the shaft 26 extends through the cylindrical winch drum l2 and includes portions 29 on which the bearings 16 are supported.
  • a hydraulically actuated friction blutch assembly indicated by the reference numeral 30.
  • This clutch assembly includes a piston member 32 which is slidably received over the shaft 26 with the piston member including a rearwardly extending cylindrical tail portion 33 which cooperates with the portion 29 of the housing 21 to define therebetween a fluid chamber 34.
  • a plurality offriction plates 36, 38 are positioned between the cylindrical drum l2 and the shaft 26.
  • the friction plates 36 include external teeth adapted to cooperate with the drum 12 while the friction plates 38 have internal teeth cooperating with the shaft 26. It will be appreciated that as the friction plates 36, 38 are brought into frictional engagement, drive will be transmitted through the friction plates from the shaft 26 to the drum I2.
  • a source of fluid pressure which may be selectively introduced into the fluid chamber 34 through fluid passages 41,
  • This drive unit is carried within the drive portion 22 of the housing 20.
  • the drive unit includes an externally toothed inner gear 52 which is secured for rotation by splines 53 or similar means to one end of the shaft 26.
  • An internally toothed outer or ring gear 54 is received over the inner gear 52.
  • the inner diameter of the outer gear 54 is substantially larger than the outer diameter of the inner gear 52 and gear 54 has a greater number of teeth than gear 52, for a purpose hereinafter discussed.
  • This support comprises a pair of links 56 which are pivotally connected at 57 to the housing 20.
  • the other end of each link 56 is pivotally connected at 58 to a support ring 59.
  • the ring 59 is supported for swinging movement transverse to the longitudinal axis of shaft 26.
  • the support ring 59 in turn pivotally supports at 61 one end of each of a pair of links 60.
  • the other end of each of the links 60 is connected by a pivot pin 62 to the ring gear 54 so that the gear 54 may swing through a path that is transverse to the path of movement ofring 59.
  • the pivot pins 62 are spaced 180 around the periphery of the ring gear 54.
  • the pivot pins 58 for the two links 56 are spaced by 180 around the support ring 59 with each link 56 being circumferentially spaced by 90 from one of the links 60.
  • the combination of the links 56 and 60, together with the supporting ring, in effect, comprises a pantograph or parallelogram support for the ring gear 54.
  • each point on the ring gear 54 moves through a path which is elliptical or orbital in shape.
  • the ring gear 54 is driven through its orbital path by a plurality of hydraulically actuated pistons 64.
  • pistons 64 In the embodiment shown, eight pistons are employed, only one of which is illus trated. However, it will be appreciated that the number of such pistons may be varied depending upon the particular plication of the drive unit.
  • a connecting rod 65 is pivotally connected at its inner end to the ring gear 54 and at its outer end by a pin 66 to the piston 64.
  • the piston 64 is slidably received in a cylinder 68 carried by the cylindrical sidewall 69 of the housing 20. It will be appreciated that as the piston 64 reciprocates in cylinder 68, the longitudinal sliding movement of the piston 64 is translated into the desired orbital movement of ring gear 54 through the pivotal connections oflinks 56, 60.
  • a manifold ring 70 which is secured to the side wall 69 of housing 20.
  • This manifold'ring includes a pair of annular grooves constituting an inlet or high pressure passage 72 and an outlet or low pressure passage 74.
  • the passage 72 is connected by suitable means to a source ofhigh pressure fluid while the passage 74 is connected back to sump or tank.
  • valve mechanism 76 Associated with each piston 64 and cylinder 68 is a valve mechanism, indicated generally by the reference numeral 76.
  • This valve mechanism comprises a valve housing 78 having a valve chamber 80 in which a valving element 82 is slidably received.
  • This valving element comprises a spool valve having cylindrical end portions 83,84 interconnected by a reduced diameter portion 85.
  • Three annular grooves are spaced along the cylindrical bore or valve chamber 80 with the first groove 86 being associated with the end 83, the second groove 87 being concentric to the reduced diameter portion and the third groove 88 being associated with the end 84.
  • the groove 86 is connected by a fluid passage 89 to the annular high pressure passage 72 while the groove 88 is connected by fluid passage 90 with the low pressure annular passage 74.
  • the groove 87 is connected by fluid passage 91 with the interior 92 ofthe hydraulic cylinder 68.
  • the movement ofthe spool valve 82 is controlled and coordinated by a cam plate, indicated generally by the reference numeral 95.
  • This cam plate is secured by appropriate means to the ring gear 54 and, hence, has an orbital movement which corresponds to that of the ring gear.
  • the periphery ofcam plate 95 has a plurality of rectangular cutout portions 96 which are defined by opposed arms 97.
  • the arms 97 are spaced apart a distance equal to the length of the spool valve 82 with the facing surfaces 98 of the arms being adapted to slidably engage the outer extremities of the spool valve 82.
  • the orbital movement ol'cam plate 95 causes the cam plate to move, in sequence, radially toward and away from each of the valve housings 78, which radial movement is accommodated by the slotted or cutout portions 96.
  • the orbital movement also the plate to move a limited amount circuml'erentially, thereby causing the arms 97 to impart'longitudinal reciprocation to the spool valves 82.
  • the foregoing described mechanism operates in the following manner to transmit drive to winch 12. Assuming the parts to be in the condition illustrated in FIGS. 1 and 2 it is apparent that the piston in the 12 oclock position is at bottom dead center while the piston at the 6 oclock position is at top dead center and the spool valves 82 associated with each ofthe two pistons are centered in their valve housings with both the inlet and outlet ports blocked. The other valves and pistons are in various intermediate positions.
  • the spool valve 82 at the 9 o'clock position is fully shifted to the left whereby the interior of cylinder 68 is in communication with the high pressure 72, while the opposed valve 82 at the 3 oclock position is fully shifted to the right whereby the interior of that cylinder is in communication'with the low pressure passage 74.
  • the pistons exposed to the high pressure are caused to reciprocate which, in turn, causes ring gear 54 to shift on its pivoted linkage supports carrying with it the cam plate 95.
  • the arms 97 associated therewith cause the spool valves 82 also to shift.
  • the shifting of the ring gear 54 and the cam plate 95 causes the cam plate to move up and in a clockwise direction as viewed in FIG.
  • the ring gear 54 is moved through its orbital path whereby the teeth of the ring gear progressively engage and disengage the teeth of the inner gear 52.
  • the wedging effect which results from the meshing of the inclined surfaces on the teeth imparts a rotative movement to gear 52.
  • This rotative move ment is supplemented by the limited arcuate movement of gear 54, all of which combines to rotate both gear 52 and shaft 26.
  • the tooth differential may vary, one specific example is to employ 60 teeth on the ring gear and 54 teeth on gear 52, thereby giving a tooth differential of 6.
  • the ring gear having 60 teeth, it is apparent that the ring gear must oscillate through its orbital path nine times or 54/6 to produce 1 revolution of the inner gear.
  • each piston completes 1 cycle for each orbital oscillation of the ring gear, it is apparent that each piston cycle nine times for each output revolution of the shaft.
  • the hydraulic motor operates at relatively high speeds while the winch is driven at relatively low speeds.
  • FIGS. 5 and 6 a modified form of the invention is illustrated.
  • the winch construction illustrated in FIG. 5 is the same as that illustrated in the embodiment of FIGS. 1 to 4 and, hence, a description of that portion of the embodiment will be omitted.
  • the modifications reside in the support for the meshing gears and the valve and piston arrangement to actuate the meshing of the gears.
  • one end of the shaft 100 has a radial extension 101 to which is secured, by fastening means 102, an inner gear 103 having external teeth.
  • An outer or ring gear 105 is received over the inner gear 103 and, as in the embodiment of FIG. 1, the ring gear 105 has internal teeth adapted to mesh with the teeth on the inner gear. Also as in the embodiment of FIG.
  • the outer gear 105 is supported by links 106 on a support ring 108.
  • the support ring 108 is supported by links 110 on the housing so that the ring gear 105 may describe an orbital path in the same manner as that described in connection with the embodiment of FIG. 1.
  • a stub shaft 112 is rotatably supported in one end wall 114 of the housing 116 with the gear 103 being received over and secured to the shaft 112.
  • a plurality of hydraulic pistons 118 are received in circumferentially spaced hydraulic cylinders 120 formed in the gear 103. As shown in FIG. 5, each piston 118 includes a spring 122 normally biasing the piston radially outward. A roller 124 is secured on the outer extremity of each piston with the rollers 124 being adapted to be received in a roller groove 126 formed on the inner periphery ofthe ring gear 105.
  • a plurality of fluid inlet passages or ports 130 are formed in the gear 103 and are in communication with the interior of each of the cylinders 120.
  • a valve plate 132 is rotatably received within a bearing 134 carried by the outer ring gear assembly 105.
  • the valve plate 132 is eccentric in configuration, as is apparent from FIG. 6, and includes a pair of arcuate grooves or passages 136, 138.
  • the grooves 136,138 are concentric to the stub shaft 112 and are adapted to rotate into and out of communication with the inlet ports or passages 130.
  • a manifold ring is received over the external end of the stub shaft 112 and rotates with the shaft.
  • This manifold ring includes a high pressure passage or groove 142 and low pressure passage or groove 14147
  • a fluid passage: 146 in the stub shaft is in communication with the high pressure groove 142 while a second fluid passage 148 is in communication with the low pressure groove 144.
  • Rotation of valve plate 132 is achieved by the orbital move ment of ring gear 105, much in the manner of a crankshaft, with the valve plate rotating through 1 revolution for each orbital cycle of the ring gear.
  • the inner gear 103 and shaft 112 with their associated passages are rotated at a reduced speed which corresponds to the particular speed reduction of the unit.
  • said inner gear means being operatively connected to said shaft and said outer gear means comprising a ring gear received over said inner gear means
  • the inner diameter of said ring gear being substantially greater than the outer diameter of said inner gear means whereby said ring gear may assume a position eccentric to the longitudinal axis of the inner gear means
  • linkage means pivotally connected to said ring gear and said housing and supporting said ring gear for orbital movement relative to said inner gear means whereby the teeth of said ring gear progressively engage and disengage the teeth of said inner gear means
  • said linkage means comprising a parallelogram support for said ring gear.
  • a drive mechanism comprising: a housing, an output shaft rotatably supported in said housing, inner and outer gear means in said housing, said inner gear means being operatively connected to said shaft and said outer gear means comprising a ring gear received over said inner gear means, the inner diameter of said ring gear being substantially greater than the outer diameter of said inner gear means whereby said ring gear may assume a position eccentric to the longitudinal axis of the inner gear means, linkage means pivotally connected to said ring gear and said housing and supporting ring gear for orbital movement relative to said inner gear means whereby the teeth of said ring gear progressively engage and disengage the teeth of said inner gear means, and means for driving said ring gear through its orbital path whereby said inner gear means and thereby said shaft is rotated, the improvement comprising:
  • said linkage means comprising a support ring and supporting links interconnecting said ring, ring gear and housing.
  • a drive mechanism comprising: a housing, an output shaft rotatably supported in said housing, inner and outer gear means in said housing, said inner gear means being operatively connected to said shaft and said outer gear means comprising a ring gear received over said inner gear means, the inner diameter of said ring gear being substantially greater than the outer diameter of said inner gear means whereby said ring gear may assume a position eccentric to the longitudinal axis of the inner gear means, means supporting said ring gear for orbital movement relative to said inner gear means whereby the teeth of said ring gear progressively engage and disengage the teeth of said inner gear means, means for driving said ring gear through its orbital path whereby said inner gear means and thereby said shaft is rotated, said means for driving said ring gear comprising a plurality of hydraulically actuated piston means including pistons and cylinders angularly spaced around and drivingly engaged with said ring gear, the improvement comprising:
  • a drive mechanism comprising: a housing, an output shaft rotatably supported in said housing, inner and outer gear means in said housing, said inner gear means being operatively connected to said shaft and said outer gear means comprising a ring gear received over said inner gear means, the inner diameter of said ring gear being substantially greater than the outer diameter of said inner gear means whereby said ring gear may assume a position eccentric to the longitudinal axis of the inner gear means, means supporting said ring gear for orbital movement relative to said inner gear means whereby the teeth of said ring gear progressively engage and disengage the teeth of said inner gear means, means for driving said ring gear through its orbital path whereby said inner gear and thereby said shaft is rotated, said means for driving said ring gear comprising a plurality of hydraulically actuated piston means including pistons and cylinders angularly spaced around and drivingly engaged with said ring gear,
  • valve means for controlling the flow of fluid into and out of said cylinders for said pistons, and means coordinating the operation of said valve means with the movement of said ring gear, the improvement comprising: said valve means comprising a valve plate having fluid passages therein, said piston means including fluid passages in communication with the interior of said cylinders, said valve plate being supported for movement relative to said piston means whereby the passages in said valve plate are sequentially moved into and out of communication with the passages associated with said piston means.
  • a drive mechanism comprising: a housing, an output shaft rotatably supported in said housing, inner and outer gear means in said housing, said inner gear means being operatively connected to said shaft and said outer gear means comprising a ring gear received over said inner gear means, the inner diameter of said ring gear being substantially greater than the outer diameter of said inner gear means whereby said ring gear may assume a position eccentric to the longitudinal axis of the inner gear means, means supporting said ring gear for orbital movement relative to said inner gear means whereby the teeth of said ring gear progressively engage and disengage the teeth of said inner gear means, means for driving said ring gear through its orbital path whereby said inner gear and thereby said shaft is rotated, said means for driving said ring gear comprising a plurality of hydraulically actuated piston means including pistons and cylinders angularly spaced around and drivingly engaged with said ring gear, valve means for controlling the flow of fluid into and out of said cylinders for said pistons, and means coordinating the operation of said valve means with the movement
  • a drive mechanism comprising: a housing, an output shaft rotatably supported in said housing, inner and outer gear means in said housing, said inner gear means being operatively connected to said shaft and said outer gear means comprising a ring gear received over said inner gear means, the inner diameter of said ring gear being substantially greater than the outer diameter of said inner gear means whereby said ring gear may assume a position eccentric to the longitudinal axis of the inner gear means, means supporting said ring gear for orbital movement relative to said inn'er gear means whereby the teeth of said ring gear progressively engage and disengage the teeth of said inner gear means, means for driving said ring through its orbital path whereby said inner gear and thereby said shaft is rotated,
  • said means for driving said ring gear comprising a plurality of hydraulically actuated piston means including pistons and cylinders angularly spaced aroundand drivingly engaged with said ring gear, valve means for controlling the flow of fluid into and out of said cylinders for said pistons, and means coordinating the operation of said valve means with the movement of said ring gear
  • said valve means comprising a valve housing associated with each of said pistons and cylinders, each of said valve housings having fluid passages formed therein, one of said passages communicating with the interior of said cylinder while another of said passages communicates with a source of high pressure and still another of said passages communicates with a source of low pressure, and a valve element in said housing operable to selectively intercommunicate the passages, the improvement comprising: said valve element comprising a slidable spool valve hav ing portions at either end thereof extending outwardly of said housing,
  • said coordinating means comprising a cam plate carried by said ring gear, and recess means formed in the periphery of said plate with said valve housing being received in the recess and said extending portions of said valve being in engagement with the walls of said recess.
  • valve means for selectively and sequentially interconnecting each of said cylinders with said pressure source
  • valve means comprising a valve housing associated with each of said pistons and cylinders,
  • each of said valve housing having fluid passages formed therein,
  • one of said passages communicating with the interior of said cylinder while another of said passages communicates with a source of high pressure and still another of said passages communicates with a source of low pressure
  • valve element in said housing operable to selectively intercommunicate the passages, the improvement comprising: said valve element including portions thereof protruding from said valve housing, said controlling means comprising a cam plate carried by said first driven member and having abutment means in engagement with said protruding portions of said valve element, 8.
  • said controlling means comprising a cam plate carried by said first driven member and having abutment means in engagement with said protruding portions of said valve element
  • a housing a plurality of angularly spaced hydraulic cylinders in said housing, piston means slidably received in each of the cylinders, first and second driven members in said housing, means operatively connecting each of said piston means to said first driven member whereby drive is imparted to said first driven member as said pistons reciprocate, said first driven member drivingly engaging said second driven member, a source of hydraulic fluid pressure,
  • valve means for selectively and sequentially interconnecting each of said cylinders with said pressure source
  • valve means comprising a valve housing associated with each of said pistons and cylinders,
  • each of said valve housings having fluid passages formed therein
  • valve element in said housing operable to selectively intercommunicate the passages, the improvement comprising: said valve element comprising a slidable spool valve, said controlling means comprising a cam plate carried by said first driven member,
  • an orbital drive system comprising in combination a stationary housing structure, a rotatable driven shaft, a driven gear, appropriate bearings and structure for supporting said shaft and gear, an orbital gear engaging the driven gear, and means for driving said orbital gear in, and constraining said orbital gear to, orbital driving engagement with said driven gear; the improvement in said last named means comprising a floating element, a first pair of substantially parallel links connecting said element to the housing, a second pair of links lying at about right angles to the said first pair of links and connecting said element to the orbital gear, hydraulic motors reacting between said housing and said orbital gear for driving said orbital gear, valve means for said motors, and valve actuating means carried by said orbital gear.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Electromagnetism (AREA)
  • Hydraulic Motors (AREA)
US815251*A 1969-03-17 1969-03-17 Hydraulic drive system Expired - Lifetime US3589243A (en)

Applications Claiming Priority (1)

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US81525169A 1969-03-17 1969-03-17

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US3589243A true US3589243A (en) 1971-06-29

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US815251*A Expired - Lifetime US3589243A (en) 1969-03-17 1969-03-17 Hydraulic drive system

Country Status (6)

Country Link
US (1) US3589243A (de)
CH (1) CH505277A (de)
DE (2) DE2009605A1 (de)
FR (1) FR2038087A1 (de)
GB (1) GB1242519A (de)
NL (1) NL7003139A (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3743310A (en) * 1970-09-24 1973-07-03 Smolka & Co Wiener Metall Sole support device
US3762488A (en) * 1972-04-13 1973-10-02 Fairfield Mfg Wheel drive unit
US4506590A (en) * 1982-07-28 1985-03-26 Shimadzu Coporation Hydraulic rotary actuator
US20070034046A1 (en) * 2005-08-09 2007-02-15 The Johns Hopkins University Pneumatic stepper motor
US20120048983A1 (en) * 2009-09-25 2012-03-01 Bianco James S Overhead power cable management system
US8926465B2 (en) 2013-01-07 2015-01-06 Timex Group Usa, Inc. Bidirectional MEMS driving arrangement
US20150076428A1 (en) * 2012-10-02 2015-03-19 Olko-Maschinentechnik Gmbh Drum hoist with a driven main shaft
US10144137B2 (en) * 2015-10-01 2018-12-04 Korea Institute Of Science And Technology Apparatus for converting a plurality of linear movement into two degree of freedom movement

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3960470A (en) * 1975-03-17 1976-06-01 Trw Inc. Hydraulic motor brake
DE4311997C2 (de) * 1993-04-13 2001-07-12 Sauer Sundstrand Gmbh & Co Hydraulikmotor
DE9414601U1 (de) * 1994-09-08 1995-10-19 Siemens AG, 80333 München Linear- oder Drehantrieb

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US533317A (en) * 1895-01-29 Flue-expander
US666553A (en) * 1899-05-12 1901-01-22 Automatic Air Carriage Company Motor.
US834033A (en) * 1905-04-03 1906-10-23 James Dwight Lamb Rotary engine.
US1260243A (en) * 1917-03-02 1918-03-19 Edward Y Moore Hoisting mechanism.
US1528836A (en) * 1922-03-02 1925-03-10 Charles T Mcelvaney Single-acting reversible steam engine
US1865493A (en) * 1929-07-24 1932-07-05 Whitfield Johnson Motor Compan Internal combustion engine
US1874336A (en) * 1927-09-19 1932-08-30 Continental Motors Corp Internal combustion engine
US1921092A (en) * 1931-03-23 1933-08-08 New York Air Brake Co Multiple-way valve
US2011820A (en) * 1931-10-08 1935-08-20 Continental Motors Corp Engine
US2069007A (en) * 1934-07-16 1937-01-26 Fontana Cesare Device for automatically changing transmission ratio
US2105846A (en) * 1934-11-19 1938-01-18 Fred Golden Radial engine
US2382482A (en) * 1944-02-14 1945-08-14 Erwin W Henry Speed reduction gear
US2760439A (en) * 1953-03-20 1956-08-28 Exxon Research Engineering Co Energy absorber and braking device
US3052138A (en) * 1960-04-11 1962-09-04 Gen Motors Corp Speed reducing gearing
US3058429A (en) * 1960-02-08 1962-10-16 Charles F Rocheville Coupling for rotatable members
US3272080A (en) * 1963-09-20 1966-09-13 Rush Metal Products Inc Torque drive mechanism
US3320828A (en) * 1964-07-14 1967-05-23 Allied Machine & Eng Corp Speed reducer or increaser
US3431863A (en) * 1965-03-05 1969-03-11 Danfoss As Guide means

Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US533317A (en) * 1895-01-29 Flue-expander
US666553A (en) * 1899-05-12 1901-01-22 Automatic Air Carriage Company Motor.
US834033A (en) * 1905-04-03 1906-10-23 James Dwight Lamb Rotary engine.
US1260243A (en) * 1917-03-02 1918-03-19 Edward Y Moore Hoisting mechanism.
US1528836A (en) * 1922-03-02 1925-03-10 Charles T Mcelvaney Single-acting reversible steam engine
US1874336A (en) * 1927-09-19 1932-08-30 Continental Motors Corp Internal combustion engine
US1865493A (en) * 1929-07-24 1932-07-05 Whitfield Johnson Motor Compan Internal combustion engine
US1921092A (en) * 1931-03-23 1933-08-08 New York Air Brake Co Multiple-way valve
US2011820A (en) * 1931-10-08 1935-08-20 Continental Motors Corp Engine
US2069007A (en) * 1934-07-16 1937-01-26 Fontana Cesare Device for automatically changing transmission ratio
US2105846A (en) * 1934-11-19 1938-01-18 Fred Golden Radial engine
US2382482A (en) * 1944-02-14 1945-08-14 Erwin W Henry Speed reduction gear
US2760439A (en) * 1953-03-20 1956-08-28 Exxon Research Engineering Co Energy absorber and braking device
US3058429A (en) * 1960-02-08 1962-10-16 Charles F Rocheville Coupling for rotatable members
US3052138A (en) * 1960-04-11 1962-09-04 Gen Motors Corp Speed reducing gearing
US3272080A (en) * 1963-09-20 1966-09-13 Rush Metal Products Inc Torque drive mechanism
US3320828A (en) * 1964-07-14 1967-05-23 Allied Machine & Eng Corp Speed reducer or increaser
US3431863A (en) * 1965-03-05 1969-03-11 Danfoss As Guide means

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3743310A (en) * 1970-09-24 1973-07-03 Smolka & Co Wiener Metall Sole support device
US3762488A (en) * 1972-04-13 1973-10-02 Fairfield Mfg Wheel drive unit
US4506590A (en) * 1982-07-28 1985-03-26 Shimadzu Coporation Hydraulic rotary actuator
US20070034046A1 (en) * 2005-08-09 2007-02-15 The Johns Hopkins University Pneumatic stepper motor
US8061262B2 (en) * 2005-08-09 2011-11-22 The Johns Hopkins University Pneumatic stepper motor
US10024160B2 (en) 2005-08-09 2018-07-17 The Johns Hopkins University Pneumatic stepper motor
US9457674B2 (en) * 2009-09-25 2016-10-04 Control Module, Inc. Overhead power cable management system
US20120048983A1 (en) * 2009-09-25 2012-03-01 Bianco James S Overhead power cable management system
US20150076428A1 (en) * 2012-10-02 2015-03-19 Olko-Maschinentechnik Gmbh Drum hoist with a driven main shaft
US9624075B2 (en) * 2012-10-02 2017-04-18 Olko-Maschinentechnik Gmbh Drum hoist with a driven main shaft
JP2016509542A (ja) * 2013-01-07 2016-03-31 タイメックス グループ ユーエスエイ，インコーポレイテッド 双方向性の微小電気機械システム（ｍｅｍｓ）による電子機器駆動用装置
US8926465B2 (en) 2013-01-07 2015-01-06 Timex Group Usa, Inc. Bidirectional MEMS driving arrangement
US10144137B2 (en) * 2015-10-01 2018-12-04 Korea Institute Of Science And Technology Apparatus for converting a plurality of linear movement into two degree of freedom movement

Also Published As

Publication number Publication date
CH505277A (de) 1971-03-31
FR2038087A1 (de) 1971-01-08
NL7003139A (de) 1970-09-21
GB1242519A (en) 1971-08-11
DE2009605A1 (de) 1970-09-24
DE7007483U (de) 1970-10-29

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Owner name: XEROTOL INVESTMENT INC., DEARBORN, MI

Free format text: ASSIGNMENT OF A PART OF ASSIGNORS INTEREST;ASSIGNOR:HANNA, MIREILLE;REEL/FRAME:004055/0011

Effective date: 19820521

Owner name: XEROTOL INVESTMENT INC., 10 BENNINGTON LN. DEARBOR

Free format text: ASSIGNMENT OF A PART OF ASSIGNORS INTEREST;ASSIGNOR:WHEELOCK, EUGENE K.,(TRUSTEE);REEL/FRAME:004055/0012

Effective date: 19651120