US3846051A - Valving arrangement in a hydraulic device - Google Patents

Valving arrangement in a hydraulic device Download PDF

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Publication number
US3846051A
US3846051A US00320791A US32079173A US3846051A US 3846051 A US3846051 A US 3846051A US 00320791 A US00320791 A US 00320791A US 32079173 A US32079173 A US 32079173A US 3846051 A US3846051 A US 3846051A
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toothed member
passages
chambers
fluid
axial end
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Expired - Lifetime
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US00320791A
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English (en)
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H Mcdermott
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Eaton Corp
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Eaton Corp
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Priority to US00320791A priority Critical patent/US3846051A/en
Priority to CA189,014A priority patent/CA970219A/en
Priority to DE2365057A priority patent/DE2365057A1/de
Priority to JP49004832A priority patent/JPS4997907A/ja
Priority to BR1/74A priority patent/BR7400001D0/pt
Application granted granted Critical
Publication of US3846051A publication Critical patent/US3846051A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105—Details concerning timing or distribution valves

Definitions

  • ABSTRACT An improved valving arrangement for a fluid operated pulley motor of the gerotor type wherein an internallytoothed member having a number (N) of teeth eccentrically receives an externally-toothed member having one less (N-l) teeth.
  • the members are relatively movable to define a number (N) of contracting and expanding volume chambers formed by tooth interaction.
  • the externally toothed member is fixedly mounted on a stationary shaft having tubular portions at its opposite ends configured for attachment to a pressurized fluid supply and fluid exhaust respectively.
  • the internally toothed member is mounted for orbital and rotational motion about the axis of the externally toothed member to define a moving line of eccentricity which separates the expanding chambers from the contracting chambers.
  • a number (N) of equally spaced discontinuous recesses extend from each axial end face of the ring member and open to the volume chambers.
  • Each axial end face of the internally toothed member abuttingly engages a confronting face within the gerotor housing containing a similar number (N) of particularly disposed valving passages.
  • the passages and recesses are orientated and arranged so that orbital motion of the ring member provides fluid communication between certain of the passages adjacent one axial end face and all expanding volume chambers; and fluid communication between certain of the passages adjacent the other axial end face and all of the contracting chambers.
  • high pressure at one axial end face may be communicated to all of the expanding chambers at one side of a line of eccentricity while low pressure at the other axial end face communicates with all of the contracting chambers at the other side of the line of eccentricity.
  • the invention is particularly applicable for use as a pulley motor having a rotating housing which drives a timing belt or the like and will be described with particular reference thereto.
  • the valving arrangement may also be employed in any fluid-operated device wherein one displacement member orbits relative to another as in gerotor type devices.
  • Gerotor devices of the type to which invention relates comprise an internally-toothed ring member having a number (N) of teeth which eccentrically receives an externally-toothed star member of less number of teeth (N-l) to define N expanding and contracting volume chambers as one member orbits relative to an axis of the other.
  • An imaginary line extending between the axes of the members divides expanding volume chambers lying one one side of the line from contracting volume chambers on the other side and is known as the line of eccentricity.
  • the line of eccentricity rotates at the oribiting speed of the orbiting member of the device.
  • Fluid valving communicates high pressure to those chambers on one side of the line of eccentricity and low pressure to those chambers on the other side of the line.
  • a first member has a number (N) of fluid passages therein each of which communicate with a volume chamber at one end thereof.
  • the other end of the (N) passages is positioned to be sequentially placed in fluid communication and with 2(N-l) passages in a second member.
  • the 2(N-l) passages in the second member in turn communicate with the inlet and outlet ports.
  • the passages in the second member are alternately arranged with N-l passages communicating with the inlet port and N-] passages communicating with the outlet port.
  • Relative rotation of the gerotor members is used to drive the second member by a universal-joint dogbone shaft to achieve the desired valve timing and sequencing.
  • an elongated member having inlet and outlet portions at its opposite ends and an externally-toothed star member fixedly mounted at its central portion.
  • An internally toothed ring member is eccentrically disposed about the externally toothed star member and the teeth of the members intermesh to form expanding and contracting volume chambers during relative orbital and rotational movement therebetween. Because of the difference in the number of teeth, oribiting of the ring member about the axis of the star member results in rotation of the ring member which in turn is transmitted by roller joint connections to a casing which forms the pulley motor housing.
  • a number (N) of discontinuous recesses extend from each axial end face of the ring member and open to the internal periphery thereof at points adjacent volume chambers.
  • Each axial end face of the ring member is confronted by a fixed surface in the housing containing a like number (N) of passages.
  • the passages and recesses are orientated and arranged so that orbital motion of the ring member provides fluid communication be tween certain of the passages adjacent one axial end face and all expanding volume chambers; and fluid,
  • FIG. 1 is an end view of a motor
  • FIG. 2 is a sectional view of the motor taken along Line 2-2 of FIG. I;
  • FIG. 2 shows a pulley motor 10 for driving a conveyor belt (not shown).
  • the pulley motor 10 comprises a housing assembly A containing a fluid displacement gerotor assembly B, and a valving arrangement C.
  • Housing assembly A comprises hollow cylindrical end casing sections 14,15 abutting against a ring roller casing 16.
  • end section 14 or 15 would be subjected to inlet fluid pressure, the other would be ported to return pressure.
  • .lournalled within the end casing sections 14, 15 is a one-piece through shaft 12 having an externally toothed star member 18 integrally formed over its central portion. It will be appreciated that alternatively the externally toothed member could be formed separately and then fixedly attached to the shaft 12.
  • HOUSING ASSEMBLY Housing assembly A comprises hollow, cylindrically shaped inlet and outlet end casing sections 14,15 having inner axial end faces 30,31 and outer axial end faces 32,333, respectively.
  • a ring-roller cylindricallyshaped casing 16 is interposed the end faces 30,31 of casing end sections 14,15.
  • Spacing discs 36 between the casing sections 14,15 and ring-roller casing 16 protrude above the housing A and serve as guides for a multi-piece belt (not shown).
  • Spacing discs 36 and casing sections 14,15,16 are secured together by a suitable adhesive such as epoxy, to provide a compact design. It will be appreciated by those skilled in the art that other fastening means such as bolts or threaded ends of the casing sections could secure the housing assembly A together.
  • Inlet end casing 14 has a longitudinal chamber 38 extending from axial end face 32 and communicating with a larger inlet valve member opening 40 which extends to the inner axial end face of casing 14.
  • outlet end casing 15 has a longitudinal chamber 39 extending from the axial end face 33 and communieating with an outlet valve member opening 41 at the A drilled hole 53,54 in each inlet and outlet casing 14,15 extends from the exterior surface of each casing where it is plugged to a point beyond the inlet and outlet chambers 38,39 respectively.
  • a pair of longitudinally-extending lubricating passages 56,58 and 57,59 extend from each drilled hole 53,54 to the inner axial end faces 30,31 of the inlet and outlet casings 14,15 respectively and are adapted to lubricate the roller drive arrangement between internally toothed member 20 and ring-roller casing 16 by transferring leakage from high to low pressure across shaft clearances 60,61.
  • gerotor assembly B comprises an externally toothed star member 18 eccentrically disposed within an internally toothed member 20 which in turn is disposed within a ring-roller cas ing 16.
  • the internally toothed member 20 has a plurality of N internal roller teeth 21 and is eccentrically mounted relative to the externally toothed member 18 having a plurality of N-l external teeth with the eccentricity e of the device shown as the distance between internally toothed members axis 64 and the externally toothed members axis 65.
  • the interaction between the teeth of the members 18,20 define a plurality of N volume chambers 22 with all of the expanding chambers lying on one side of the Y-Y axis and all of the contracting volume chambers lying on the other side thereof.
  • the Y-Y axis may thus be defined as a moving line of eccentricity and always extends between the axis 64,65. lt should be apparent that this line of eccentricity moves as relative movement between the members occurs.
  • FIGS. 4,5
  • N designates the a number of chambers (14) and N-l designates the number of teeth (13) in the externally toothed member.
  • members 18,20 will interact with one another in the usual manner. More particularly with the member 18 fixed against rotation, the member 20 will orbit hypocycloidally about the member 18 whereby the axis 64 will define a circle about the axis 65 of radius equal to the eccentricity e. This movement of the member 20 will expand and contract each of the N volume chambers 22 while the member 20 rotates a peripheral distance equal to one tooth space. Furthermore, it will be appreciated that the Y-Y axis or line of eccentricity will also rotate at an angular velocity equal to the orbiting speed of the member 20.
  • the external surface of the member 20 has a plurality of circumferentially-spaced, axially-extending grooves 67 and the internal surface of ring-roller casing 16 has a like number of grooves 68.
  • the grooves 67,68 of member 20 and ring-roller casing 16 coact with one another to form a plurality of articulated holes 69.
  • Received within each hole is a drive pin which provides means for rotating ring-roller casing 16 in the same direction and with the same rotational speed as member 20.
  • the driving rollers 70 and articulated holes 69 are equal in number to the number of displacement chambers 22 and are located on radial center lines bisecting the angles between the roller teeth 21.
  • the effective diameter of each articulated hole 69 is equal to the diameter of the drive pin 78 plus the eccentricity e of the gerotor members 18,21). This relationship assures that only rotational and not orbital motion of the member will be transmitted to the ring-roller casing 16.
  • cylindrically-shaped valving members 24,25 are fixedly mounted within the stepped bores 40,41 respectively so that the axial end faces 72,73 of the valving members 24,25 are aligned with the axial end faces 30,31 of the end casing sections 14,15.
  • a central opening extends through valving members 24,25 to provide a slight clearance for receiving the shaft 12 therethrough.
  • the valving members 24,25 are securely fixed in the stepped bores 40,41 such as by a press fit whereby the members 24,25 rotate in unison with the housing 16. lmportantly the axial length of valving members 24,25 is slightly shorter than the axial length of the stepped counterbores 40,41 in the casing end sections 14,15 to define annular feed openings 74,75 respectively.
  • annular feed openings 74,75 communicate the valving passages 26,27 in the valving members 24,25 with four radially-extending passages 76,77 in the shaft 12.
  • the passages 76,77 in turn communicate with longitudinally-extending inlet and outlet passages 78,79, at opposite ends of shaft 12 respectively. Because the device of the subject invention is illustrated as a motor, all inlet valving passages 26 are adapted to be at high pressure while all outlet valving passages 27 are at low pressure.
  • the valving passages 26 in the valving member 24 are identical in dimensional size and are shown circumferentially-spaced in equal increments about the external periphery of valving member 24. lmportantly, the inlet valving member 24 is oriented in the inlet valve member opening 40 so that at assembly one valving passage 26a extends on one side of a line perpendicular to the line of eccentricity (in the position shown in FIG. 3 this is axis 64) and a diametrically opposed passage 26b extends from the other side of said line.
  • a line perpendicular to the line of eccentricity in the position shown in FIG. 3 this is axis 64
  • passage 26a extends upwardly from axis 64 and has one side substantially in line contact with axis 64 while passage 26b extends downwardly from axis 64 and also has one side substantially in line contact with axis 64.
  • the line is taken as an axis of housing 16 which is perpendicular to the line of eccentricity at final assembly.
  • valving passages 27 in valving member are identical in size to passages 26 and are circumferentially-spaced in equal increments about the external periphery of valving member 25. lmportantly, the outlet valving member 25 is orientated in the outlet valve member opening 41 in a mirror image of that previously stated for member 26.
  • one passage 270 extends substantially from one side of an axis of housing 16 perpendicular to the line of eccentricity in a direction opposite that of corresponding inlet passage 26a.
  • the corresponding diametricallyopposed passage 27b extends from the opposite side of the same line and in a direction opposite that of corresponding inlet passage 27a.
  • passage 27a has one side substantially in line contact with axis 64 and extends downwardly from axis 64 while passage 2712 has one side substantially in line contact with axis 64 and extends upwardly therefrom.
  • the phasing and arrangement of outlet passages 27 is thus the mirror image of the phasing and arrangement of inlet passages 26 and vice-versa.
  • internally toothed member 20 has a plurality of N discontinuous recesses 28,29 at each axial end face 80,81 thereof. The recesses 28,29 are adapted to coact with their corresponding valve passages 26,27.
  • the discontinuous recesses 28 are circumferentially-spaced in equal increments about the internal periphery of the member 20 and extend from the end face inwardly and open to the internal periphery of the member 20 to communicate with volume chambers 22.
  • the outlet recesses 29 are circumferentially-spaced in equal increments about the member 20 with each recess 29 extending inwardly from the end face 81 and opening to the internal periphery of the member 20.
  • one edge of the recesses 28 and 29 extends from a radius of member 20 so that the recesses 28,29 are spaced a slight angle 01 ahead of or behind the center of the associated chamber depending on the direction of rotation of member 21) and whether the recess 28 or 29 is an inlet or outlet passage.
  • each volume chamber 22 is defined as extending between adjacent roller teeth 21 of member 20, the width of each discontinuous recess 28,29 is shown as extending from a roller tooth 21 to a point defining one-half the distance between adjacent roller teeth. lmportantly the discontinuous recesses are so positioned with respect to the roller teeth 21 of the member 20 that the inlet side discontinuous recesses 28 appear as the mirror image of outlet side recesses 29 in the same manner as that discussed above for the inlet and outlet valving passages 26,27.
  • an inlet recess 28): is disposed adjacent roller tooth 21x as opposed to outlet recess 29x which is disposed adjacent roller tooth 21y.
  • the space between roller teeth 21x and 21y defines one volume chamber 22x. Additionally the height of each discontinuous recess 28,29 extend beyond the valving passages 26,27 a distance at least equal to the eccentricity e of the device.
  • N/2 inlet passages 26 will communicate with discontinuous recesses 28 leading to expanding volume chambers lying on one side of the line of eccentricity and N/2 outlet passages 27 will communicate with discontinuous recesses leading to contracting volume chambers on the other side of the line of eccentricity. This relationship is assured in the embodiment illustrated by the dimensional sizing of passages 26,27 and recesses 28,29.
  • the width of a volume chamber is defined as that peripheral distance betwen radial lines extending from the center of the housing or axis 64 and bisecting adjacent rollers, and approximately one-half of that distance is occupied by the roller teeth, the remaining half-distance is divided equally between the discontinuous recesses 28,29.
  • the valving passages 26,27 also encompass substantially the same width as recesses 28,29 to assure adequate fluid flow therebetween. It will be appreciated by those skilled in the art that valve timing may be adjusted by varying the widths of passages 26,27 and recesses 28,29.
  • each particular inlet passage 26a is always associated with the same recess 28x and the same volume chamber 22x. The same relationship is true at the outlet side. This materially aids in simplifying manufacture and assembly of the device.
  • Fluid supplied under pressure from a pump is introduced into the inlet passage 78 whereupon it travels through the inlet radially-extending passages 76 into the inlet annular feed opening 74 and from thence into inlet valving passages 26, all valving passages 26 being under high pressure. Because of the geometrical relationship between valving passages 26,27 and recesses 28,29 as shown in FIGS. 4 and 6, communication of high pressure occurs only between those inlet valving passages 26 and inlet recesses 28 which are aligned with expanding volume chambers 22 lying on one side of the line of eccentricity (YY axis in FIGS. 4 6).
  • the contracting volume chambers 22 communicate only with outlet valving passages 27 via their respective outlet recesses 29.
  • the fluid is then exhausted from the device by passing from the outlet valving passages 27 through the outlet annular feed opening 75 into the outlet radially-extending passages 78 and from thence through the outlet passage 79 to a reservoir (not shown).
  • the members 24 and 25 rotate in synchronism with both the housing 16 and internally toothed member 20.
  • the inlet and outlet recesses 28,29 in member 20 each have a complex orbiting motion with respect to their associated inlet or outlet passages 26,27. It is this complex relative motion which provides the fluid communication necessary for operation of the device.
  • drive pins 70 are lubricated by fluid leaking from the slight shaft clearance on the high pressure side of the device which is communicated to the drive pin via the inlet drilled hole 52 and inlet lubricating passages 56,58.
  • the fluid is exhausted from the clearance between the member 20 and ring-roller casing 16 by the outlet drilled hole 53 and lubricating passages 57,59 in the outlet casing 15.
  • the fluid travels from the shaft clearance 61 into the annular outlet feed opening thence through the radially-extending outlet passages 77 into the outlet passage 79.
  • axial end face leakage occuring on the high pressure side of the gerotor arrangement B is transferred by a pressure relief groove 86 to the low pressure axial end face where it is exhausted through outlet valving chambers 27, in the normal manner. While the invention has been described with reference to a motor application thereof, it is apparent that the device could similarly function as a pump by supplying fluid to the device at low pressure and rotating the housing assembly A.
  • a pulley motor of the gerotor type comprising:
  • a one-piece shaft having an externally-toothed member extending over a central portion thereof, said shaft having tubular portions at its opposite ends to define a fluid inlet and a fluid outlet for said motor;
  • first hollowed cylindrical casing section disposed around said shaft at one side of said externally toothed member and journalling said shaft therein;
  • a cylindrical ring casing member interposed and secured to said first and second casing sections to define a housing
  • an internally-toothed member having more teeth than said externally toothed member and being eccentrically disposed for movement relative to said externally toothed member, the teeth of said members interenmeshing to define contracting and expanding volume chambers during relative movement therebetween;
  • said internally toothed member being disposed within said ring casing member
  • valve means operable between said inlet at one end of said shaft and said outlet at the other end of said shaft to connect said inlet to the expanding volume chambers and said outlet to contracting volume chambers to cause said internally toothed member to hypocycloidally move about said externally toothed member;
  • valve means including first and second valve a shaft member journalled in said housing for rotation relative thereto and defining a fluid inlet and disposed for rotational and orbital motion relative to said externally toothed member;
  • valve means including a first valve member havp u p e e i ng ing a plurality of first fluid passages therein, a secchambers and their associated passages in said first 0nd valve member having a plurality of Second galve and bgwzen the coniracting cham' fluid passages therein, all of said first passages havers an associate Passages m Said second ing constant fluid communication with said inlet vaive mam-be?
  • a fluid opergted device of the gerotor type second valve members being fixedly secured in said prising. housing to prevent relative motion therebetween, a hol'ming. and each axial end face of said internally toothed a ring casing member forming a portion of said hous- 222:?

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US00320791A 1973-01-03 1973-01-03 Valving arrangement in a hydraulic device Expired - Lifetime US3846051A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US00320791A US3846051A (en) 1973-01-03 1973-01-03 Valving arrangement in a hydraulic device
CA189,014A CA970219A (en) 1973-01-03 1973-12-27 Valving arrangement in a hydraulic device
DE2365057A DE2365057A1 (de) 1973-01-03 1973-12-28 Druckmittelbetaetigte maschine, insbesondere parallel- und innenachsige rotationskolbenkraftmaschine oder -pumpe mit kaemmeingriff
JP49004832A JPS4997907A (pt) 1973-01-03 1973-12-28
BR1/74A BR7400001D0 (pt) 1973-01-03 1974-01-02 Uido e motor de polia do tipo roto-gerador do a fluido do tipo roto-gerador, dispositivo operado a flarranjo aperfeicoado de valvulas para um dispositivo oper

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Application Number Priority Date Filing Date Title
US00320791A US3846051A (en) 1973-01-03 1973-01-03 Valving arrangement in a hydraulic device

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US3846051A true US3846051A (en) 1974-11-05

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US00320791A Expired - Lifetime US3846051A (en) 1973-01-03 1973-01-03 Valving arrangement in a hydraulic device

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US (1) US3846051A (pt)
JP (1) JPS4997907A (pt)
BR (1) BR7400001D0 (pt)
CA (1) CA970219A (pt)
DE (1) DE2365057A1 (pt)

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DE2829417A1 (de) * 1978-07-05 1980-01-17 Rexroth Gmbh G L Kreiskolbenmaschine
US4282777A (en) * 1979-01-02 1981-08-11 Compudrive Corporation Pancake planetary drive
WO1981003046A1 (en) * 1980-04-21 1981-10-29 Zaporozh Kt I Selskokh Mash Planetary hydromotor
WO1982000172A1 (en) * 1980-07-08 1982-01-21 Erasov F Planetary hydromotor
US4439119A (en) * 1979-08-13 1984-03-27 Danfoss A/S Gerotor machine with commutating valving through the ring gear
US4561833A (en) * 1982-04-07 1985-12-31 Sumitomo Heavy Industries, Ltd. Fluid pressure device
US4563136A (en) * 1982-07-02 1986-01-07 Parker-Hannifin Corporation High torque low speed hydraulic motor with rotary valving
US4824347A (en) * 1987-09-24 1989-04-25 Parker Hannifin Corporation Internal gear machine with reinforced housing
US4843817A (en) * 1987-11-18 1989-07-04 Shivvers, Inc. Integrated hydraulic transmission
US4896506A (en) * 1987-11-18 1990-01-30 Shivvers, Inc. Transmission with integrated gear reduction
US7052256B2 (en) 2004-01-28 2006-05-30 Eaton Corporation Synchronized transaxle hydraulic motor
US20090078066A1 (en) * 2006-05-19 2009-03-26 Keiper Gmbh & Co. Kg Gear train for an actuator
US20110085928A1 (en) * 2009-10-09 2011-04-14 Parker Hannifin Corporation Geroller hydraulic motor with anti-cogging structure
US20140112813A1 (en) * 2012-10-22 2014-04-24 Parker-Hannifin Corporation Hydraulic motor
US20170159439A1 (en) * 2015-12-03 2017-06-08 Parker-Hannifin Corporation Eccentrically piloted hydraulic commutator
US10422414B2 (en) * 2015-04-14 2019-09-24 Delta Electronics, Inc. Speed reducer
US20230141065A1 (en) * 2018-11-07 2023-05-11 Delta Electronics, Inc. Speed reducer

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US4087215A (en) * 1976-07-16 1978-05-02 Trw Inc. Gerotor gearset device
DE9201060U1 (de) * 1992-01-29 1992-03-19 Voulgaris, Andres, 8164 Hausham Hydraulischer Motor
DE4202466C2 (de) * 1992-01-29 1994-10-20 Andres Voulgaris Hydraulischer Motor
DE202005009540U1 (de) * 2005-06-17 2006-10-26 Kinshofer Greiftechnik Gmbh & Co. Kg Hydraulischer Drehmotor

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US3389618A (en) * 1966-05-11 1968-06-25 Char Lynn Co Torque transmitting device
US3514234A (en) * 1968-06-10 1970-05-26 Char Lynn Co Fluid operated devices
DE1811386A1 (de) * 1968-11-28 1970-06-11 Danfoss As Drehkolbenmaschine
US3552893A (en) * 1969-05-07 1971-01-05 Lamina Inc Rotary casing orbital gear-rotor motor
US3775031A (en) * 1971-05-14 1973-11-27 Danfoss As Rotary fluid pressure device

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US3516765A (en) * 1966-01-26 1970-06-23 Bendix Corp Fluid actuated actuator
US3383931A (en) * 1966-09-16 1968-05-21 Char Lynn Co Drive mechanism

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Publication number Priority date Publication date Assignee Title
US3233524A (en) * 1962-09-05 1966-02-08 Germane Corp Fluid operated motor
US3389618A (en) * 1966-05-11 1968-06-25 Char Lynn Co Torque transmitting device
US3514234A (en) * 1968-06-10 1970-05-26 Char Lynn Co Fluid operated devices
DE1811386A1 (de) * 1968-11-28 1970-06-11 Danfoss As Drehkolbenmaschine
US3552893A (en) * 1969-05-07 1971-01-05 Lamina Inc Rotary casing orbital gear-rotor motor
US3775031A (en) * 1971-05-14 1973-11-27 Danfoss As Rotary fluid pressure device

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2829417A1 (de) * 1978-07-05 1980-01-17 Rexroth Gmbh G L Kreiskolbenmaschine
US4282777A (en) * 1979-01-02 1981-08-11 Compudrive Corporation Pancake planetary drive
US4439119A (en) * 1979-08-13 1984-03-27 Danfoss A/S Gerotor machine with commutating valving through the ring gear
WO1981003046A1 (en) * 1980-04-21 1981-10-29 Zaporozh Kt I Selskokh Mash Planetary hydromotor
DE3144423T1 (de) * 1980-04-21 1983-11-03 Zaporožskij konstruktorsko-technologicheskij institut selskochozyaistvennogo mašinostroenia, Zaporož'e Planetenhydromotor
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Also Published As

Publication number Publication date
JPS4997907A (pt) 1974-09-17
DE2365057A1 (de) 1974-07-11
BR7400001D0 (pt) 1974-08-15
CA970219A (en) 1975-07-01

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