US3747477A - Variable volume hydraulic apparatus - Google Patents

Variable volume hydraulic apparatus Download PDF

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Publication number
US3747477A
US3747477A US00039225A US3747477DA US3747477A US 3747477 A US3747477 A US 3747477A US 00039225 A US00039225 A US 00039225A US 3747477D A US3747477D A US 3747477DA US 3747477 A US3747477 A US 3747477A
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United States
Prior art keywords
control ring
fluid
control
conduit
pressure
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Expired - Lifetime
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US00039225A
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English (en)
Inventor
U Aldinger
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/128—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the cylinders, e.g. by moving a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/08—Control regulated by delivery pressure

Definitions

  • ABSTRACT A hydraulic pump or motor of the radial piston type has a control ring for the pistons whose eccentricity to the axis of the rotor determines the transported volume of fluid. Two pistons are diametrically disposed in an axial plane and abut the control ring.
  • the pistons are respectively connected with a source of fluid whose pressure is variable, and with the high pressure side of the hydraulic apparatus so as to vary the eccentricity of the control ring while the same is guided by two supporting means which are diametrically disposed in an axial plane perpendicular to the first-mentioned axial plane.
  • Another object of the invention is to provide operating means for displacing the control ring while compensating deformations of the same caused by the action of the operating means and by the supporting means of the ring. 7
  • Another object of the invention is to provide hydraulic operating meansfor displacing the control ring for varying the volume of fluid transported by the apparatus.
  • Another object of the invention is to provide operating means including at least one operating piston abutting the control ring and controlled by pressure fluid whose pressure is selectable and adjustable.
  • control ring means is supported on a plurality of supporting means which inwardly project from the housing, and at least some of which are movable radially with respect to the control ring.
  • a preferred embodiment of the invention comprises a rotor having an axis, peripheral chambers, and piston elements mounted in the chambers for substantially radial movement; a control ring surrounding the rotor and having an inner control surface engaged by the pis ton elements so that the latter move in the respective chambers when the center of the control ring is located eccentric to the axis of the rotor; housing means having an inner surface for ming an inner cavity in which the control ring and rotor are located, and including fluid supply means and fluid delivery means communicating with the chambers; a pair of supporting means mounted in the housing diametrically disposed in an axial control plane inwardly projecting from the inner surface of the housing means, and having free inner ends abutting the outer surface of the control ring for guiding the same in a controlled direction with the center of the control ring moving in an other axial plane perpendicular to the axial control plane between a neutral position in which the center of the control ring coincides with the axis and a plurality of operative positions in which
  • slide shoes are used to which pressure fluid is supplied so that a hydrostatic pressure area forms on the inner face of the shoe which is in contact with the outer surface of the control ring.
  • FIG. 1 is a schematic cross sectional view illustrating a first embodiment of a pump according to the invention
  • FIG. 2 is a cross-sectional view illustrating a second embodiment of the invention
  • FIG. 3 is a cross-sectional view illustrating a third embodiment of the invention.
  • FIG. 4 is a cross-sectional view illustrating a fourth embodiment of the invention.
  • FIGS. 1 to 4 operate as pumps, but the apparatus can also be used as a hydraulic motor.
  • the general constructions of the embodiment of FIGS. 1 4 is-the same, and corresponding parts will be designated by like reference numerals.
  • a rotor 4 is driven from a prime mover to rotate about an axis at which the axial planes l3 and 14 intersect at right angles.
  • a valve means 5 is stationarily mounted in a cylindrical bore of rotor 4, and is located in the axial plane 14 to separate the high pressure conduit 7 and the low pressure conduit 6 from each other.
  • Conduits 6 and 7 communicate with supply means and delivery means for a fluid, depending on whether the apparatus is operated as a pump or motor.
  • the cylindrical rotor body has peripheral radially extending bores 8, forming cylinder chambers in which pistons 9 are mounted for radial movement.
  • FIGS. 1 to 4 show only one cylinder 8 and piston 9, but it will be understood that a plurality of angularlyspaced cylinder chambers and pistons therein is provided angularly spaced about the periphery of the cylindrical, rotor 4, only one piston being shown for the sake of simplicity in view of the conventional nature of this arrangement.
  • the cylinder chambers 8 on one side of the axial plane 14 are connected by openings 10 either with the low pressure supply conduit 6 or with the high pressure delivery conduit 7 during each revolution of rotor 4.
  • Each piston 9 has a spherical seat engaged by a spherical head on a piston rod 11 to which a slide shoe 12 is secured.
  • the outer surface of slide shoe 12 is partcircular, so that its contour matches the circular inner surface of a control ring 3, located in a cavity 2 of a housing means 1 which is large enough to permit translatory movement of control ring 3 in the direction of the axial plane 14.
  • a pair of diametrically arranged supporting means and 16 is located in the axial control plane 13 which extends at right angles to axial plane 14.
  • the inner end faces of abutment means 15 and 16 engage diametrically located portions of control ring 3, guiding the same for translatory movement with the center of control ring 3 moving in the direction of axial plane 14 between a position coinciding with the axis of rotor 4, and a plurality of eccentric positions, one eccentric end position being shown in the drawing.
  • supporting means 15 and 16 project from the inner surface of housing 1, they cause only little wear of the control ring.
  • the length of the inner end faces of supporting means 15 and 16 is preferably three to four times the maximum eccentricity of the center of control ring 3 in relation to the axis of rotor 4.
  • Supporting means 15, 16 may be inserts consisting of a wear resistant material, or be integral parts of the housing 1 and cast with the same. 4
  • Two diametrically disposed operating pistons 17 and 18, which also constitute supporting means for control ring 3, are located in the-axial plane 14.
  • Operating pistons l7 and 18 are mounted for radial movement in corresponding cylinders formed on housing 1, and are urged by springs and 19, respectively, into engagement with control ring 3, even if no pressure fluid is supplied to the cylinders of pistons 17 and 18.
  • Piston 18 has a greater effective surface and a larger spring 19 than piston 17 and spring 20 so that control ring 3 is biased toward the illustrated eccentric end position.
  • pistons 21 and 22 are provided in corresponding cylinders of housing 1, and are biassed by springs 23 and 24 toward engagement with control ring 3.
  • Pistons 21 and 22 are located in the two quadrants on the high pressure side of the pump, and of axial plane 14, and spaced angles of 45 from planes 13 and 14.
  • the cylinders of pistons 17, 22 and 21 are connected by high pressure conduit means 101 with a radial high pressure conduit 7a communicating with the high pressure delivery conduit 7'.
  • Another conduit means 102 communicates with the cylinder of operating piston 18, and contains valve means 103 for selectively varying and adjusting the pressure of the pressure fluid supplied to piston 18.
  • valve means 103 for selectively varying and adjusting the pressure of the pressure fluid supplied to piston 18.
  • Control ring 3 is not pressed against the inner surface 1 of easing 1, but against the end face of piston 17.
  • control ring 3 pressure of control ring 3 is distributed to a greater number of supported points.
  • piston 17 moves control ring 3 against the action of spring 19 to a neutral position in which the center of control ring 3 coincides with the rotor axis, and the pump idles and delivers no fluid.
  • FIG. 2 corresponds to the embodiment of FIG. 1, the pistons 21 and 22 being omitted, while pistons 47 and 48 are provided with slide shoes 55 and 56, respectively. It will be understood that pistons 21 and 22 could also be provided in the embodiment of FIG. 2.
  • the control ring 33 is supported and guided by supporting means 45 and 46, and is operated by pistons 48, 56 and 47, 55 to move between positions of different eccentricity, as explained with reference to FIG. 1.
  • a selectively variable control pressure is supplied to the cylinder of piston 48, and high pressure fluid is supplied by conduit 101 to the cylinder of piston 47.
  • Springs 49 and 50 urge the pistons 48 and 47, respectively, toward control ring 33.
  • Piston 48 has a cylindrical or spherical seat engaged by a corresponding cylindrical spherical head 56' of slide shoe 56
  • piston 47 has a spherical or cylindrical seat engaged by aspherical or cylindrical head 55' of slide shoe 55.
  • a duct connects each cylinder with a pressure area at the end face of each slide shoe so that the pressure of conduit 102 prevails under slide shoe 56, and the pressure of conduit 101 prevails on the slide face of slide shoe 55. Due to the produced hydrostatic pressure, the friction during the displacement of control ring 33 is reduced, and a lesser adjusting force required. During the pumping operation, control ring 33 cannot rotate since it is braked by piston 47, 55.
  • the axis or center of the cylindrical or spherical head 55, 56' is located on the outer circular surface of control ring 33. Due to this fact, the slide shoes cannot be tilted by control ring 33 which rotates during adjustment of the apparatus.
  • FIG. 3 shows an embodiment of the invention in which the operating pistons 77 and 78 are provided with slide shoes 85 and 86, as explained with reference to FIG. 2.
  • slide shoes 75, 76 are provided in the axial plane 13 in diametrical position in relation to control ring 63.
  • Slide shoes and 76 have spherical or cylindrical heads mounted in corresponding seats in the inner surface 67 of the housing.
  • the duct in slide shoe 75 on the high pressure side of the pump is connected with high pressure conduit 101 which communicates with the delivery conduit 7 of the pump through radial conduit 7a.
  • the duct in slide shoe 76 is connected by a conduit 119 with a radial conduit 60 which communicates with the low pressure supply conduit 6 of the pump.
  • Conduits 101 and 119 are connected over check valves 87 and 88 with the cylinder in which piston 77 is mounted.
  • high pressure fluid from conduit 101 enters the cylinder of piston 77 through the opening check valve 87, but cannot enter the low pressure conduit 119 due to the provision of check valve 88.
  • conduit 119 becomes the high pressure conduit
  • conduit 101 becomes the low pressure conduit
  • piston 77 is operated by the high pressure produced by the pump since check valve 88 opens and checkvalve 87 closes.
  • control ring 63 is completely hydrostatically supported, so that very small friction forces occur, permitting rotation of control ring 63 even during operation of the pump.
  • Control ring 63 rotates at an intermediate speed, lower than the rotary speed of rotor 4, so that slide shoe 1?. slides at a comparatively low speed on the inner annular surface of control ring 63.
  • pressure fluid can be discharged from the pressure area in the curved face of slide shoe 76 abutting the outer surface of control ring 63, so that the same is lubricated and cooled along its periphery.
  • pressure fluid at a selectable control pressure is supplied to the cylinder in which piston 78 is mounted.
  • FIG. 4 combines features of the embodiments of FIGS. 1, 2 and 3.
  • Supporting slide shoes 105 and 106 are arranged and constructed as the slide shoes 75 and 76 in FIG. 3.
  • Operating pistons 107 and 108 correspond to operating pistons 77 and 78 of the embodiment in FIG. 3, and have corresponding slide shoes.
  • Pistons 111 and 112 are also provided with slide shoes, and correspond to piston 21 and 22 in the embodiment of FIG. 1, preventing deformation of control ring 93 which is located in the cavity of the housing having the inner surface 92.
  • Pressure conduit means 101 connects the delivery conduit 7 with the cylinders of pistons 111 and 112, and over a check valve 117 with the cylinder of piston 107.
  • a low pressure conduit 119 connects the cylinders of pistons 113 and 114 with the low pressure supply conduit 6, and over a check valve 118 with a cylinder of operating piston 107.
  • High pressure conduit 101 is also connected with a duct of supporting slide shoe 105, and low pressure conduit 119 is also connected with the duct of supporting slide shoe 106.
  • the cylinder of piston 108 is connected with a, source of pressure fluid at a selectable control pressure.
  • Pistons 111, 112, l13-and 114 prevent a deformation of control ring 93 by the pressure between pistons 107 and 108.
  • the slide shoes around the periphery of control ring 93 support control ring 93 for translatory movement from the eccentric end position shown in FIG. 4 to a position in which the center of control ring 93 coincides with the axis of rotor 5.
  • high pressure fluid is supplied to pistons 113, 114, and 107, and also to the supporting slide shoe 106, while low pressure fluid is supplied to pistons 11], 112 and supporting slide shoe 105.
  • the effective surface of pistons 111, 112, 113 and 114 is selected in accordance with the occurring deformation of control ring 93- so that the same remains exactly circular.
  • FIGS. 3 and 4 which permit rotation of control rings 63 and 93, respectively, are particularly suited for high pressure and high rotary speed.
  • the illustrated apparatus has been described for operation as a pump, but it is evident that the apparatus can also serve as a hydraulic motor.
  • Variable volume hydraulic apparatus comprising a rotor having an axis, chambers, and piston elements mounted in said chambers for substantially radial movement; a control ring surrounding said rotor and having an inner control surface engaged by said piston elements so that the latter move in said chambers when the center of said control ring is located eccentric to said axis; housing means having an inner surface forming an inner cavity in which said control ring and said rotor are located, and including a fluid supply conduit and a fluid delivery conduit communicating with said chambers; at least two supporting means mounted in said housing means disposed symmetrically to an axial control plane inwardly projecting from the inner surface of said housing means, and having free inner ends abutting the other surface of said control ring for guiding the same in one direction with the center of said control ring moving in an other axial plane perpendicular to said axial control plane between a neutral position, in which the center of said control ring coincides with said axis, and a plurality of operative positions in which said center is eccentric to said
  • first conduit means including a pressure adjusting valve means connected with a source of pressure fluid and being operable for supplying to one of said cylinders pressure fluid at selected control pressures
  • second conduit means connected with said supply and delivery conduits in said housing for supplying to the respective other cylinder high pressure fluid from the one of said supply and delivery conduits at which high pressure prevails so that the displacement of said control ring by said operating pistons in said other axial plane, and the volume displaced by said piston elements depends on the adjusting of said pressure adjust-ing valve and on the selected control pressure of the fluid in said first conduit means overcoming the pressure in said second conduit means;
  • each supporting means and each operating piston including a movable slide shoe having a curved face on said inner end matching the curvature of said outer surface of said control ring and slidingly engaging the same, each slide shoe being formed with a duct for receiving pressure fluid, said duct ending at said curved face forming on the same a hydrostatic pressure area.
  • each slide shoe has a cylindrical or spherical mounting portion having the center of curvature thereof located on said outer surface of said control ring.
  • Hydraulic apparatus as claimed in claim 1 comprising two diametrically disposed supporting means in said axial control plane; wherein ducts in said slide shoes of said two supporting means respectively communicate with said supply and delivery conduits so that the ducts in slide shoes on the high pressure side of said other axial plane receive high pressure fluid and the ducts on the low pressure side of said other axial plane receive low pressure fluid.
  • said second conduit means include two conduits connecting said supply and delivery conduits, respectively, with said ducts, and two check valves in said conduits, respectively, so that high pressure fluid is supplied to said ducts irrespective of which of said conduits contains high pressure fluid during operation of the apparatus as pump or motor.
  • Variable volume hydraulic apparatus comprising a rotor having an axis, chambers, and piston elements mounted in said chambers for substantially radial movement; an integral control ring surrounding said rotor and having an inner control surface engaged by said piston elements so that the latter move in said chambers when the center of said control ring is located eccentric to said axis; housing means having an inner surface forming an inner cavity in which said control ring and said rotor are located, and includ-ing a fluid supply conduit and a fluid delivery conduit communicating with said chambers; at least two supporting means mounted in said housing means disposed symmetrically to an axial control plane inwardly projecting from the inner surface of said housing means, and having free inner ends abutting the outer surface of said control ring for guiding the same in one direction with the center of said control ring moving in an other axial plane perpendicular to said axial control plane between a neutral position, in which the center of said control ring coincides with said axis, and a plurality of operative positions in which said center is eccentric

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US00039225A 1969-05-28 1970-05-21 Variable volume hydraulic apparatus Expired - Lifetime US3747477A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691927074 DE1927074A1 (de) 1969-05-28 1969-05-28 Radialkolbenpumpe mit rotierendem Laufring

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US3747477A true US3747477A (en) 1973-07-24

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US00039225A Expired - Lifetime US3747477A (en) 1969-05-28 1970-05-21 Variable volume hydraulic apparatus

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US (1) US3747477A (de)
CH (1) CH505987A (de)
DE (1) DE1927074A1 (de)
FR (1) FR2047337A5 (de)
GB (1) GB1313682A (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4056042A (en) * 1975-04-02 1977-11-01 Sulzer Brothers Limited Rotary hydrostatic piston machine with eccentrically movable guide means
US4227864A (en) * 1978-02-17 1980-10-14 Lucas Industries Limited Pump for liquids
US5012724A (en) * 1988-05-19 1991-05-07 Bruno Giamello Radial piston hydraulic motor of variable cylinder capacity
US5136932A (en) * 1988-05-19 1992-08-11 Bruno Giamello Radial piston hydraulic motor of variable cylinder capacity
US5249512A (en) * 1992-05-18 1993-10-05 Christenson Howard W hydrostatic pump and motor
US20140034779A1 (en) * 2012-08-02 2014-02-06 Bell Helicopter Textron Inc. Independent blade control system with hydraulic cyclic control
US9061760B2 (en) 2012-08-02 2015-06-23 Bell Helicopter Textron Inc. Independent blade control system with rotary blade actuator
US9162760B2 (en) 2012-08-02 2015-10-20 Bell Helicopter Textron Inc. Radial fluid device with multi-harmonic output
US9376205B2 (en) 2012-08-02 2016-06-28 Bell Helicopter Textron Inc. Radial fluid device with variable phase and amplitude
CN108590995A (zh) * 2018-04-11 2018-09-28 王长健 变量泵及液压系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT341886B (de) * 1973-05-04 1978-03-10 Salice Arturo Spa Topfförmiger scharnierteil für möbelscharniere
DE2607780C2 (de) * 1976-02-26 1981-11-19 Robert Bosch Gmbh, 7000 Stuttgart Verstelleinrichtung für eine Radialkolbenpumpe
DE3247885C2 (de) * 1982-12-23 1986-12-18 Mannesmann Rexroth GmbH, 8770 Lohr Flügelzellen- oder Radialkolbenpumpe

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB109849A (en) * 1916-09-30 1917-10-01 Gogu Constantinesco Improved Alternating Liquid Current Motors.
US2009851A (en) * 1933-10-28 1935-07-30 American Eng Co Ltd Fluid control mechanism
US2164888A (en) * 1936-02-24 1939-07-04 Cincinnati Grinders Inc Variable delivery pump
US2433484A (en) * 1944-11-24 1947-12-30 Borg Warner Movable vane variable displacement pump
US2509256A (en) * 1946-06-17 1950-05-30 Clarence S Sorensen Variable displacement piston pump and control system for the same to control the pump in both a highpressure phase and a low-pressure phase
US2630681A (en) * 1950-11-04 1953-03-10 Oilgear Co Rotary pump and motor hydraulic drive having a substantially constant output speed
US2716945A (en) * 1952-10-17 1955-09-06 Bendix Aviat Corp Variable stroke rotary cylinder pump
US3028814A (en) * 1957-10-17 1962-04-10 Houdaille Industries Inc High speed variable displacement pump
US3087437A (en) * 1959-10-12 1963-04-30 North American Aviation Inc High temperature variable displacement pump
US3155047A (en) * 1962-03-15 1964-11-03 Keel Adolf Power transmission

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB109849A (en) * 1916-09-30 1917-10-01 Gogu Constantinesco Improved Alternating Liquid Current Motors.
US2009851A (en) * 1933-10-28 1935-07-30 American Eng Co Ltd Fluid control mechanism
US2164888A (en) * 1936-02-24 1939-07-04 Cincinnati Grinders Inc Variable delivery pump
US2433484A (en) * 1944-11-24 1947-12-30 Borg Warner Movable vane variable displacement pump
US2509256A (en) * 1946-06-17 1950-05-30 Clarence S Sorensen Variable displacement piston pump and control system for the same to control the pump in both a highpressure phase and a low-pressure phase
US2630681A (en) * 1950-11-04 1953-03-10 Oilgear Co Rotary pump and motor hydraulic drive having a substantially constant output speed
US2716945A (en) * 1952-10-17 1955-09-06 Bendix Aviat Corp Variable stroke rotary cylinder pump
US3028814A (en) * 1957-10-17 1962-04-10 Houdaille Industries Inc High speed variable displacement pump
US3087437A (en) * 1959-10-12 1963-04-30 North American Aviation Inc High temperature variable displacement pump
US3155047A (en) * 1962-03-15 1964-11-03 Keel Adolf Power transmission

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4056042A (en) * 1975-04-02 1977-11-01 Sulzer Brothers Limited Rotary hydrostatic piston machine with eccentrically movable guide means
US4227864A (en) * 1978-02-17 1980-10-14 Lucas Industries Limited Pump for liquids
US5012724A (en) * 1988-05-19 1991-05-07 Bruno Giamello Radial piston hydraulic motor of variable cylinder capacity
US5133244A (en) * 1988-05-19 1992-07-28 Bruno Giamello Radial piston hydraulic motor of variable cylinder capacity
US5136932A (en) * 1988-05-19 1992-08-11 Bruno Giamello Radial piston hydraulic motor of variable cylinder capacity
US5249512A (en) * 1992-05-18 1993-10-05 Christenson Howard W hydrostatic pump and motor
US20140034779A1 (en) * 2012-08-02 2014-02-06 Bell Helicopter Textron Inc. Independent blade control system with hydraulic cyclic control
CN103661940A (zh) * 2012-08-02 2014-03-26 贝尔直升机德事隆公司 具有液压周期控制的独立桨叶控制系统
US8973864B2 (en) * 2012-08-02 2015-03-10 Bell Helicopter Textron Inc. Independent blade control system with hydraulic cyclic control
US9061760B2 (en) 2012-08-02 2015-06-23 Bell Helicopter Textron Inc. Independent blade control system with rotary blade actuator
US9162760B2 (en) 2012-08-02 2015-10-20 Bell Helicopter Textron Inc. Radial fluid device with multi-harmonic output
CN103661940B (zh) * 2012-08-02 2016-02-24 贝尔直升机德事隆公司 具有液压周期控制的独立桨叶控制系统
US9376205B2 (en) 2012-08-02 2016-06-28 Bell Helicopter Textron Inc. Radial fluid device with variable phase and amplitude
CN108590995A (zh) * 2018-04-11 2018-09-28 王长健 变量泵及液压系统

Also Published As

Publication number Publication date
CH505987A (de) 1971-04-15
DE1927074A1 (de) 1970-12-03
GB1313682A (en) 1973-04-18
FR2047337A5 (de) 1971-03-12

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