US3656405A - Pressurized medium motor - Google Patents

Pressurized medium motor Download PDF

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Publication number
US3656405A
US3656405A US88446A US3656405DA US3656405A US 3656405 A US3656405 A US 3656405A US 88446 A US88446 A US 88446A US 3656405D A US3656405D A US 3656405DA US 3656405 A US3656405 A US 3656405A
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United States
Prior art keywords
units
pressurized medium
passages
piston
cylinder
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Expired - Lifetime
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US88446A
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English (en)
Inventor
Karl Klinkhammer
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Gebr Dickertmann Hebezeugfabrik AG
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Gebr Dickertmann Hebezeugfabrik AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/02—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • F01B15/04—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 with oscillating cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B5/00—Reciprocating-piston machines or engines with cylinder axes arranged substantially tangentially to a circle centred on main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
    • F01B2009/045—Planetary gearings

Definitions

  • ABSTRACT A pressurized medium motor comprising a housing, a plurality of opposed pivotally mounted piston and cylinder units in the housing and adapted to be successively-supplied with pres surized medium, each unit acting on eccentric drive means geared positively or non-positively with the housing, the opposed piston and cylinder units with the eccentric drives'forming a polygon having a substantially constant circumference with varying side lengths, with an adjacent pair of units each having one piston end acting on a common eccentric part of an eccentric drive, each such unit being provided with at least one passage acting as a supply or discharge means for the pressurized medium, the said passage(s) being alternately connected automatically to pressure and exhaust passage, the said pressure and exhaust passages being connected in turn to all the units.
  • the invention concerns a motor adapted to be driven by means of a pressurized medium such as a liquid or air.
  • lt is an object of the invention to provide a pressurized medium motor which is relatively small but yet provides a high torque without the use of reduction gears and which can operate continuously.
  • a pressurized medium motor in a housing, having a plurality of opposed piston and cylinder units adapted to be supplied with pressurized medium, the units being pivotally mounted and connected with the eccentric drive means running on the inside surface ofthe housing, each opposed piston and cylinder unit being provided with at least one pressurized medium passage to act as inlet and outlet, the said passage being connected alternately and automatically to pressurized medium passages for the inlet and outlet of the pressurized medium associated with each opposed piston and cylinder unit.
  • each opposed piston and cylinder unit is provided with two pressurized medium passages which are alternately connected with a pressurized medium supply and medium discharge common to all such units.
  • the opposed piston and cylinder units with their eccentric drives form a polygon of varying shape, the lengths of the sides varying in dependence upon the positions of the various pistons while the circumference of the articulated polygon remains substantially constant.
  • Adjacent opposed piston and cylinder units each have a piston end supported on an eccentric part of a common drive, the pistons exerting pressure on the eccentric to produce the drive.
  • the drive means form with the housing a reduction gear; to this end the eccentrics may be provided with gear pinions which mesh with a toothed inside surface ofthe housing; alternatively the eccentrics are provided with friction gears which engage with a smooth inside surface of the housing to produce a friction drive.
  • Each opposed piston and cylinder unit and the eccentric drives are mounted pivotally or rotatably in common bearing plates.
  • Each opposed piston and cylinder unit has a cylinder block in the bore of which two opposed pistons are displaceably mounted, and held against the adjacent eccentrics by means ofa spring.
  • Two passages extending from the cylinder bore of each cylinder block towards the housing center act as supply and discharge passages and are connected alternately to two supply and discharge passages located within a bearing plate on different levels, and to an annular chamber connected to the supply or discharge passages which supplies the pressurized medium and provides a discharge path.
  • the pistons ofthe units are supplied in succession with the pressurized medium and each unit operates on particular eccentrics so that a substantially uniform drive results on the housing or bearing plate.
  • the associated opposed piston and cylinder units execute a pendulum motion about the region of the supply and discharge passages associated with each unit on the bearing plate, so that the passage from the cylinder block is alternately connected to the supply and discharge passages on the bearing plate side and hence to the central passages.
  • the motor of the invention is of simple structure, reliable in operation and economical to produce.
  • An advantage of the invention resides in that the motor is provided with a built-in reduction gear thus rendering additional gears superfluous.
  • This motor is a slow speed runner which has a high torque which is constant over its whole speed range. This torque is readily varied by varying of the operating medium.
  • a motor in accordance with the invention provides a shockproof start under load from any position, and permits an accurately predetermined acceleration and deceleration characteristic.
  • the motor also affords accurate load, speed, and revolution control and can be used as a positioning device.
  • the motor is applicable more particularly to lifting tackle, the lifting height and load being under exact control.
  • the motor may be incorporated as a direct drive in pulleys such as cable drums, wheel bosses or the like.
  • FIG. l is a cross section through a motor having a plurality of opposed piston and cylinder units pivotally mounted in a housing;
  • FIG. 2 is a section through an opposed piston and cylinder unit taken on the line I-I in FIG. 1,
  • FIG. 3 is a section through the same motor taken on the line II-II of FIG. l,
  • FIG. 4 is a developed view of the connecting passages in the region of the ringed portion A in FIG. 3.
  • a pressurized medium motor more particularly a hydraulic motor has a housing 10 in which a plurality of opposed piston and cylinder units 11, l2, 13, 14 and mounted pivotally and successively supplied with a pressurized medium such as oil or air.
  • the opposed piston and cylinder units 1l to 14 are connected with eccentric drives 15, 16, 17, 18 which are positively or frictionally coupled to the housing, so that the eccentric drives l5 to 18 produce a rotational connection between the units 11 to 14 and the housing l0.
  • the housing 10 is circular, but may also be made as an oval.
  • the housing 10 there are four opposed piston and cylinder units 11 to 14 together with four eccentric drives 15 to 18, so that each two adjacent units 1l to 14 cooperate with one eccentric drive 15 to 18.
  • the housing 10 is possible to provide the housing 10 with three or with ⁇ more than four, for example, six or eight units and corresponding eccentric drives.
  • Each opposed unit l1 to 14 is provided with at least one pressurized medium passage as supply or discharge, which is alternately and automatically connectable with fluid medium passages to effect forward motion or reverse motion of the units l1 to 14.
  • each opposing unit 14 is provided with two pressurized medium passages 19, 20 as supply or discharge passages, which are alternately connected automatically with a central medium forward motion passage 21 and a central medium reverse motion passage 22, the passages being common to all units.
  • the opposed piston and cylinder units 11 to 14 with their eccentric drives l5 to 18 form a movable polygon having sides of varying length while the circumference of the polygon remains substantially constant.
  • each unit 1l to 14 is provided with a cylinder block 23 which is pivotally mounted on lateral bearing plates 25a and 25b having two central bearings 24 aligned at right angles to the direction of piston movement.
  • Each unit 11 to 14 has a cylinder bore 26 in its cylinder block 23 in which two opposed pistons 27 are displaceably mounted.
  • each piston 27 has an abutment surface 27b which is of less cross-sectional area than the associated piston, and the end may be stepped.
  • the eccentric drives 15 to 18 with the housing 10 form a reduction gear.
  • the housing l0 is provided on the inside surface with an internal toothed ring 10a with which the eccentric drives 15 to 18 mesh by means of a high pinions 32 provided on both sides of the eccentric 30.
  • a non-positive connection between the eccentric drives 15 to 18 and housing l0 to form a reduction gear may be frictional, thus the inside surface of the housing is provided with a smooth surface and the pinions of the crank drives 15 to 18 are replaced by friction wheels or rollers.
  • the piston and cylinder units l1 to 14 and their mounting plates are stationary and the housing is rotatable.
  • the housing 10 may be stationary and the units 11 to 14 with their mounting plates may be rotatable within the housing 10.
  • Each unit 11 to 14 is provided in its cylinder block 23 with two pressurized medium passages 19, 20 acting as supply or discharge passages, these passages being preferably at right angles to the direction of piston movement and arranged radially and parallel, side by side, in the bearing extensions, in the region of a bearing plate 25a or 2517.
  • These two pressurized medium passages 19, 20 are connected to the chamber 26 via a common axial connecting passage 33.
  • each cylinder block 23 has two pressurized medium passages 34, 35 associated therewith as supply or return passages at different levels relative to one another, which passages are connected to the forward and reverse fluid passages 21, 22.
  • the two annular chambers 36, 37 are separated by a distance corresponding to the distance between the passages 19, 20, and are formed by axial annular grooves which on the casing side are located in a shaft 38 and connected by the upstream and downstream flow of the medium.
  • the passages 34, 35 alternately connect the pressurized medium passages 19, 20 of the cylinder blocks 23 to corresponding annular grooves 36, 37; the passages 34, 35 are spaced to correspond with the spacing of the passages 19, 20 and annular grooves 36, 37.
  • each unit 1l to 14 is at a greater radius than the length of the orifices of the supply and discharge passages 34, 35 together with the cylinder block-side passages 19, 20.
  • the inlet and outlet passages 21, 22 lead into the annular grooves 36, 37 via passages 21a, 22a extending outwards at an angle.
  • unit 11 is located in the charge position, i.e. the pistons 27 of unit 11 are being supplied with pressurized medium; they are pushing oppositely outwards and thus act on the two eccentric drives and 16.
  • Unit 12 is at the beginning of a power stroke i.e. the pistons 27 of this unit are located in the retracted position one against the other, and are about to be supplied with pressurized medium; unit 13 is connected to exhaust and unit 14 is about to be so connected.
  • the mode of operation ofthe motor is as follows:
  • unit ll is located in a driving position, with its pressurized fluid passage 19 connected to the annular supply groove 36 via the inclined supply passage 34, in which groove the supply passage 21 of the medium ends.
  • the pressurized medium flows from the passage 2l via the annular groove 36, the inclined passage 34, the supply passage 19 and the connecting passage 33 into the cylinder space 26, acts on the two opposed pistons 27 and presses them outwards.
  • These two pistons now act on the eccentric 30 of the two drives 15 and 16 which are positively connected to the housing, and impart rotation thereto (see direction of arrow on the eccentric, in FIG. 1).
  • the eccentric drives 15, 16 also engage the housing l0 and rotate it in the same direction (see external arrow, FIG. 1).
  • the action of the unit 11 rotates all the eccentric drives 15 to 18 and during this rotation all units 11 to 14 pivot about their bearing extensions 24.
  • the opposed pistons 27 of unit 11 continue to press on the two eccentric parts 30 of the drives 15, 16 until the unit assumes dead center position, i.e. until the eccentrics are fully extended in line with the longitudinal axes ofthe pistons. In this position filling the unit 11 and its action to rotate the eccentric drives are ended.
  • the rotation of the drives causes all units 11 to 14 to be pivotally moved, so that unit 12 now assumes a filling position and unit 14 an emptying position, while the two opposite units 11 and 13 are at a zero position.
  • unit 13 was in the emptying position and the two units 12, 14 passed through a zero posi tion their passages 19, 20 are blocked between the two inclined supply and discharge passages 34, 35.
  • Filling of unit 12 commences before unit 11 is completely filled, so that the piston driving actions merge into and overlap one another, one unit taking up the drive before the end of the drive of the previous unit to provide continuous rotation of the housing.
  • Unit 12 now progressively rotates the two eccentric parts 30 of the drives 16 and 17, all units 11 to 14 being pivoted, and unit 14 is emptied.
  • the two other units 11, 13 have their supply and discharge passages 19, 20 swung between the two inclined passages 34, 35 towards the upstream (or downstream) passage; thus unit 1l moves so as to become connected to the return exhaust passage 35, and unit 13 so as to become connected to the supply passage 34.
  • unit 13 has its supply passage 19 connected to the supply passage 34 and is filled in turn.
  • unit 11 has its discharge passage 20 coupled to exhaust passage 35 and can thus be emptied. After unit 13 is filled, the oscillation of the units moves unit 14 into the filling position while unit 12 is emptied.
  • the two supply and discharge passages 19, 20 of all units 1l to 14 thus move, due to the pivotal mounting of the cylinder blocks, between the inclined supply and exhaust passages 34, 35 associated with each unit 11 to 14 and hence the cylinders arrive successively in a filling position.
  • the annular groove 36 connected to the supply of the medium, and the supply passage 34 leading thereto, are constantly under pressure.
  • the movement of the supply and discharge passages 19, 20 on the cylinder block side is shown in FlG. 4 by the arrow.
  • a slight overlap of the supply passage 19 with the inclined supply passage initiates filling, and complete register of both passages 19, 34 provides maximum supply to the pistons 27 with pressurized medium.
  • the supply passage 19 swings over the supply passage 34 and thus becomes only partly in register therewith.
  • each unit 11 to 14 causes rotation of the eccentric drives l5 to 18 and hence rotation of the housing 10.
  • Each drive 15 to 18 is rotated through a predetermined angular region of rotation and then a subsequent unit takes over further rotation, so that the various drives are translated into a uniform rotary movement ofthe housing.
  • Compression springs 31 retain each unit 11 to 14 in connection with the drives l5 to 18, so that during rotation of the drives a corresponding pivotal movement of the units 11 to 14 occurs so that their two supply and discharge passages 19, 20 are caused sequentially to assume a filling position (connection of passage 19 with passage 34), a zero position (passage 19 assumes a position between the two passages 34, 35), or an emptying position (discharge passage 20 connected to discharge passage 35).
  • each unit 11 to 14 only with one passage to act as both inlet and outlet, and this passage may be bifurcated in the region of the supply and discharge passages 34, 35.
  • a pressurized medium motor comprising a housing, at least one base plate, a plurality of opposed piston and cylinder units within said housing and mounted on said base plate; bearing extensions on said units whereby each said unit can rock about a center; eccentric drives acted upon by said pistons, driving means interconnecting said drives and said housing, said piston and cylinder units together with said eccentric drives forming a polygon having a constant circumference but with sides of variable length depending on the positions of said pistons; one piston of each pair of adjacent piston and cylinder units acting on a single one of said eccentric drives; at least one pressurized medium passage to each unit; and fluid supply and exhaust passages alternately connectable to each piston and cylinder unit as a result of rotation of said motor.
  • a pressurized medium motor as recited in claim l further comprising two fluid passages for each said opposed piston and cylinder unit, a common pressurized medium supply and a common exhaust for all said units, and means for connecting said units in a predetermined sequence to said supply and exhaust via said two passages.
  • a pressurized medium motor as recited in claim l comprising a toothed ring located inside said housing, and at least one pinion wheel on each said eccentric drives meshing with said toothed ring to form a reduction gear.
  • a pressurized medium motor as recited in claim l comprising two parallel base plates, bearing pins on said eccentric drives and bearing extensions on said units, and bearing surfaces defined by said plates to receive said bearing pins and bearing extensions so that said eccentric drives can rotate and said units can rock.
  • each eccentric drive comprises an eccentric of cylindrical form, said eccentric being secured to said bearing pins and to at least one pinion wheel.
  • each opposed piston and cylinder unit consists of a cylinder block dening a bore therein; two oppositely moving pistons located in said bore; a compression spring between said pistons, a rod extension of each said piston of reduced section and extending outwards of said cylinder, and an eccentric-engaging surface on the outward end of each said rod extension.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
US88446A 1969-11-11 1970-11-10 Pressurized medium motor Expired - Lifetime US3656405A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT1057869A AT306472B (de) 1969-11-11 1969-11-11 Druckmittelmotor

Publications (1)

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US3656405A true US3656405A (en) 1972-04-18

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US88446A Expired - Lifetime US3656405A (en) 1969-11-11 1970-11-10 Pressurized medium motor

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US (1) US3656405A (fr)
AT (1) AT306472B (fr)
BE (1) BE758736A (fr)
CH (1) CH520263A (fr)
DE (1) DE2054358A1 (fr)
FR (1) FR2069166A5 (fr)
GB (1) GB1328656A (fr)
NL (1) NL7016518A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3827338A (en) * 1970-08-25 1974-08-06 Kawasaki Heavy Ind Ltd Fluid device
US3924516A (en) * 1972-07-06 1975-12-09 Deere & Co Hydraulic pump or motor
US4084485A (en) * 1974-06-25 1978-04-18 C. Van Der Lely N.V. Driving mechanisms and housings for such mechanisms
US20120237383A1 (en) * 2011-01-03 2012-09-20 Soilmec S.P.A. Hydraulic motor or pump with tangential pistons with annular or sectional shape on ordinary or planetary gear for high torque, and power performance and hydraulic and mechanical efficiency

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL2003330C2 (nl) * 2009-08-04 2011-02-07 Leendert Huuksloot Dubbelwerkende verbrandingsmotor.
ES2689224B2 (es) * 2017-05-09 2021-03-12 Follente Emilio Diez Motor hidráulico

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1341332A (en) * 1918-10-16 1920-05-25 Mcdonald Alexander Rotary engine
US1764324A (en) * 1929-09-28 1930-06-17 Harry E Stanley Air motor
US2731114A (en) * 1949-09-15 1956-01-17 Lambert & Brake Corp Fluid-operated brake and cushioning means therefor
US3336842A (en) * 1965-08-19 1967-08-22 Echlin Mfg Company Hydraulic actuator
DE1924837A1 (de) * 1968-05-17 1970-01-29 Hottelet Michel Verbrennungskraft- und Arbeits-Maschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1341332A (en) * 1918-10-16 1920-05-25 Mcdonald Alexander Rotary engine
US1764324A (en) * 1929-09-28 1930-06-17 Harry E Stanley Air motor
US2731114A (en) * 1949-09-15 1956-01-17 Lambert & Brake Corp Fluid-operated brake and cushioning means therefor
US3336842A (en) * 1965-08-19 1967-08-22 Echlin Mfg Company Hydraulic actuator
DE1924837A1 (de) * 1968-05-17 1970-01-29 Hottelet Michel Verbrennungskraft- und Arbeits-Maschine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3827338A (en) * 1970-08-25 1974-08-06 Kawasaki Heavy Ind Ltd Fluid device
US3924516A (en) * 1972-07-06 1975-12-09 Deere & Co Hydraulic pump or motor
US4084485A (en) * 1974-06-25 1978-04-18 C. Van Der Lely N.V. Driving mechanisms and housings for such mechanisms
US20120237383A1 (en) * 2011-01-03 2012-09-20 Soilmec S.P.A. Hydraulic motor or pump with tangential pistons with annular or sectional shape on ordinary or planetary gear for high torque, and power performance and hydraulic and mechanical efficiency
US9080560B2 (en) * 2011-01-03 2015-07-14 Soilmec S.P.A. Hydraulic motor or pump with tangential pistons with annular or sectional shape on ordinary or planetary gear for high torque, and power performance and hydraulic and mechanical efficiency
EP2472102B1 (fr) * 2011-01-03 2019-05-08 Soilmec S.p.A. Moteur ou pompe hydraulique avec pistons tangentiels ayant une forme annulaire ou sectorielle sur un engrenage ordinaire ou planétaire pour couple élevé, performance électrique et efficacité hydraulique et mécanique

Also Published As

Publication number Publication date
FR2069166A5 (fr) 1971-09-03
NL7016518A (fr) 1971-05-13
DE2054358A1 (de) 1971-06-03
AT306472B (de) 1973-04-10
BE758736A (fr) 1971-04-16
GB1328656A (en) 1973-08-30
CH520263A (de) 1972-03-15

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