WO2002046580A1 - Unite de puissance commandee par pression - Google Patents

Unite de puissance commandee par pression Download PDF

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Publication number
WO2002046580A1
WO2002046580A1 PCT/FI2001/001051 FI0101051W WO0246580A1 WO 2002046580 A1 WO2002046580 A1 WO 2002046580A1 FI 0101051 W FI0101051 W FI 0101051W WO 0246580 A1 WO0246580 A1 WO 0246580A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure fluid
piston
cylinder space
transmission member
power unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/FI2001/001051
Other languages
English (en)
Inventor
Esko Raikamo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AU2002216133A priority Critical patent/AU2002216133A1/en
Publication of WO2002046580A1 publication Critical patent/WO2002046580A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/002—Oscillating-piston machines or engines the piston oscillating around a fixed axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/073—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having pawl-and-ratchet type drive

Definitions

  • the invention relates to a pressure-controlled, pressure-fluid- operated power unit comprising: an annular cylinder space sealed with first and second end flanges, at least two pistons moving relative to each other, the pistons forming a piston pair and being substantially of the shape and size of the cross-section of the circumference of the cylinder space, at least one of the pistons being arranged to rotate about the axis of the cylinder space such that the piston can move in the cylinder space in the direction of its circumference; a transmission shaft connected to rotate about the cylinder space axis together with said piston; a transmission member arranged to said piston; conduits for leading pressure fluid into and out of the spaces between the pistons.
  • Fl patent 102916 discloses a power unit comprising an annular cylinder space and pistons of the shape of the cross-section of the cylinder space, the pistons being arranged to rotate about the axis of the cylinder space. Further, the power unit comprises a transmission shaft for providing a rotational motion, and locking members, such as a one-way clutch, for locking a piston to an immobile state. Such a power unit is also suitable to be used as a stepper motor, and its structure is simple and reliable. [0003] It is an object of the present invention to provide an even simpler power unit.
  • the power unit of the invention is characterized in that at least one end flange is provided with a pressure fluid groove connected to a control conduit, the pressure fluid groove facing the transmission member such that the pressure fluid flowing from the control conduit is arranged to press the transmission member in the axial direction of the cylinder space against a counter surface, to lock the transmission member or to slow down its movement relative to the cylinder space.
  • the power unit comprises control conduits connected to annular grooves formed in the end flanges of the cylinder space, the grooves facing the transmission members such that the pressure fluid presses at least one transmission member in an axial direction against a counter surface to lock the transmission member or to slow down its motion relative to the cylinder space.
  • a preferred embodiment of the invention is based on the idea that the pistons of a piston pair are arranged to rotate about the axis of the cylinder space and that they are connected alternately to one of the transmission members arranged coaxially and rotationally relative to the axis of the cylinder space to allow each piston to move relative to the transmission member connected to the other piston of the piston pair; that the end flange of the cylinder space is the counter surface; and that the transmission member comprises locking members, which lock a piston rotating in a first direction to be substantially immovable relative to the transmission shaft and which are arranged, correspondingly, to release the first piston from the locking when the piston moves in the reverse direction.
  • a second preferred embodiment of the invention is based on the idea that the second piston of the piston pair is immovably attached to the cylinder space; that the counter surface is provided by means of a flange connected to the transmission shaft, the flange being arranged between the transmission member and the annular groove of the second end flange and a piston moving relative to the cylinder space being locked relative to the flange; that a second control conduit is arranged to lead between the flange and the second end flange such that pressure fluid supplied into the power unit substantially simultaneously from both the first and the second pressure fluid conduits presses the transmission member against the flange.
  • An advantage of the invention is that the structure of the power unit is extremely simple and, therefore, its costs of manufacture and maintenance are low and its reliability is excellent.
  • the power unit can be easily implemented in different variations regarding the number of cylinders and pistons to suit the requirements of its purposes of use, and it can be used to produce either a stepwise or a continuous rotational motion.
  • Figure 1 is a schematic, partly sectional side view of an embodiment of a power unit of the invention
  • Figure 2a is a schematic, partly sectional side view of a second embodiment of the power unit of the invention.
  • Figure 2b is a schematic, exploded perspective view of the power unit embodiment of Figure 2a
  • Figure 3 is a schematic, partly sectional side view of a third embodiment of the power unit of the invention.
  • Figure 4a is a schematic, partly sectional side view of a fourth embodiment of the power unit of the invention.
  • Figure 4b is a schematic, exploded perspective view of the power unit embodiment of Figure 4a.
  • FIG. 1 is a schematic, partly sectional side view of an embodiment of a power unit of the invention.
  • the power unit comprises an annular, sealed cylinder space 1 surrounded by a cylinder space casing 2.
  • a transmission shaft 4 is arranged rotationally and co-axially relative to the cylinder space 1 , the inner circumferences of locking members 8, in turn, being non-rotationally arranged to the transmission shaft.
  • the locking members 8 may be for example one-way clutches, multiple plate clutches, or other similar components, that provide a locking effect in one direction while allowing rotation to take place in the reverse direction. Both locking members 8 have the same locking direction, indicated by arrow L in the Figure.
  • both locking members 8 there are transmission members, or sleeves 10a, 10b, a piston 3 being further attached to both sleeves 10a, 10b.
  • a sleeve and a piston may form one integral piece, or they may be provided as separate elements attached to each other.
  • the pistons 3 form a piston pair rotating in the direction of the circumference of the cylinder space 1 , and they are substantially of the shape and size of the cylinder space 1.
  • a piston 3 and a sleeve 10a, 10b attached thereto are able to rotate relative to the cylinder space independently of the other piston of the piston pair and the sleeve 10a, 10b attached thereto, and vice versa, except in a situation where the pistons 3 meet.
  • the ends of the cylinder space 1 are sealed with a first and a second end flange 12a, 12b, which are immovably attached to the casing 2.
  • Both end flanges 12 and 13 comprise pressure fluid conduits 13a, 13b.
  • One end of the pressure fluid conduits 13a, 13b leads out of the power unit, whereas the other end leads to a pressure fluid groove 14a, 14b formed on the side of the respective end flange that faces the cylinder space, the pressure fluid groove circumventing the transmission shaft 4 and facing the end of the sleeve 0a, 10b.
  • pressure fluid is supplied through one of the pressure fluid conduits - for example through the first pressure fluid conduit 13a - into the first pressure fluid groove 14a and, further, through the flow conduit 16 into the cylinder space between the pistons 3.
  • the second pressure fluid conduit 13b is opened to serve as a discharge conduit to allow the pressure fluid to flow out from the other side of the pistons 3.
  • the pressure fluid flowing into the cylinder space 1 has two effects. First, its pressure tends to separate the pistons 3 from each other by rotating them in the direction of the circumference of the cylinder space, and, second, it tends to separate the sleeves 10 from each other in the axial direction by pushing them against the end flanges 12a, 12b.
  • the first and the second pressure fluid conduits 13a and 13b are thus used for feeding and discharging both the pressure fluid needed for turning the pistons 3 and the pressure fluid needed for producing the pressure difference required for locking the piston 3; in other words, the pressure fluid conduits 13a, 13b also serve as control conduits, the pressure of the pressure fluid flowing in them being used for controlling the locking of the pistons 3 relative to the cylinder space 1.
  • the reciprocal movement of the pistons decreases the size of the cylinder space 1 part connected to the second pressure fluid conduit 13b, some of the pressure fluid contained in the cylinder space thus flowing through the flow conduit of the second sleeve into the second pressure fluid groove 14b and further into the second pressure fluid conduit 13b and, finally, out of the power unit.
  • the transmission shaft 4 can be locked so as not to rotate in the direction opposite to the locking direction L by maintaining a pressure that is higher on one side of the pistons 3 than on the other side, whereby the pistons 3 rest against each other.
  • the pressure conduit 13a, 13b supplying the pressure fluid can be changed at a desired moment, the pressure to be supplied into the power unit can be varied by feeding it in pulses, the power unit then operating as a stepper motor.
  • Figure 2a is a schematic, partly sectional side view of a second embodiment of the power unit of the invention
  • Figure 2b is a schematic, exploded perspective view of the power unit embodiment of Figure 2a.
  • the casing 2 enclosing the cylinder space 1 is provided with second pistons 5 immovably attached to the casing at 180°, the pistons being substantially of the shape and size of the cross-section of the cylinder space 1.
  • the second pistons 5 may also form an integral piece with the casing 2, or they may be attached to the end flanges 12a, 12b sealing the ends of the cylinder space 1; the essential aspect is that the second pistons 5 are arranged to be immovable relative to the cylinder space 1.
  • the cylinder space comprises one sleeve 10, which is substantially of the same length as the cylinder space and arranged to be coaxial with the cylinder space 1.
  • a transmission shaft 4 which is arranged to rotate freely relative to the sleeve 10, is fitted with bearings to the end flanges 12a, 12b.
  • the sleeve 10 is provided with two first pistons 3 attached thereto at 180°.
  • the first pistons 3 and the second pistons 5 form two piston pairs, the pistons 3, 5 being arranged to move relative to each other.
  • the sleeve 10 and the transmission shaft 4 may be provided with a seal, for example, arranged between them.
  • the sleeve 10 may be fitted with bearings to the transmission shaft 4 to prevent wear.
  • Every other part between the pistons of the cylinder space 1 is a working part V1 and every other part between the pistons of the cylinder space 1 is a return part V2.
  • the volumes of the working part V1 and the return part V2 change when the first pistons 3 move in the cylinder space 1 , but their total volume remains the same all the time.
  • Return conduits 7 lead into the return parts V2 of the cylinder space.
  • the pressure fluid conduits 13 and the return conduits 7 enter the cylinder space through the casing 2 and via the second pistons 5; alternatively, they may enter partly or entirely via the first pistons 3 or the end flanges 12a, 12b, or the transmission shaft 4.
  • the return conduits 7 lead into a pressure fluid space, represented by a pressure accumulator 11 in the embodiment of the Figure. It is to be noted that for simplicity of presentation, the Figure only shows the principle of the pressure accumulator 11 and a part of a return conduit 7.
  • the pressure accumulator 11 maintains the pressure fluid at the pressure required in the return conduits 7 and in the return parts V2.
  • the structure and operation of the pressure accumulator 11 are known per se, and therefore they are not described in more detail in this context.
  • the pressure fluid circuit of the return part V2 may also be provided with a relief valve, which eliminates overpressure loads possibly appearing in the system.
  • the first end flange 12a is provided with a first control conduit 20a and, correspondingly, the second end flange 12b with a second control conduit 20b.
  • the control conduits 20a, 20b are connected to a first and a second pressure fluid groove formed in the end flanges 12a, 12b, the grooves being implemented similarly as in Figure 1.
  • the first and second control conduits 20a, 20b are connected to the pressure fluid circuit of the working part V1.
  • the transmission shaft 4 is provided with a rotationally symmetric flange 21 , which is arranged between the sleeve 10 and the second pressure fluid groove 14b.
  • the flange 21 is provided with a third pressure fluid groove 22 circumventing its outer edge and with a fourth pressure fluid groove 23 arranged on the flange side facing the cylinder space.
  • the third and the fourth pressure fluid grooves 22, 23 are interconnected by a conduit 24.
  • the third pressure fluid groove 22 is further connected to a third control conduit 25 arranged on the second end flange 12b and, from there, to the outside of the power unit, the conduit being connected to the pressure fluid circuit of the return part V2.
  • the third pressure fluid groove 22 is sealed against the second end flange with ring seals 26.
  • the working cycle of the power unit of Figures 2a and 2b comprises two strokes: a working stroke and a return stroke.
  • a working stroke is initiated by applying pressure to supply pressure fluid simultaneously through the first and the second control conduits 20a, 20b into the first and second pressure fluid grooves 14a, 14b.
  • a lower pressure prevails in the third control conduit 25.
  • the sleeve 10 and the flange 21 press against each other.
  • pressure fluid is supplied through the feed conduit 13 into the working parts V1 , the pressure of the fluid being higher than the pressure fluid pressure prevailing in the return parts V2.
  • the pressure of the pressure fluid in the working part V1 turns the first pistons 3 relative to the second pistons 5 in a first direction shown by arrow L, and, on the return part V2, pressure fluid flows out of the cylinder space into a return conduit 7 and from there into the pressure accumulator 11.
  • the flange 21 provides a counter surface against which the transmission member, i.e. the sleeve 10, presses when the pressure fluid is controlled in a suitable manner. Since the friction between the sleeve- I0 v and the flange 21 prevents the sleeve 10 from rotating relative to the fteirige 10, or at least slows down the rotation, the transmission shaft 4 makes a rotating motion in the first direction along with the first pistons 3. The first pistons and the transmission shaft 4 turn until the first pistons 3 reach the end position of the working stroke on the side of the second piston 5 that faces the return conduit 7.
  • the motion of the sleeve 10 and the first pistons attached thereto can be interrupted at any point by stopping the supply of the pressure fluid.
  • the return stroke in the second direction begins immediately when the pressure of the pressure fluid in the working part V1 drops below the pressure prevailing in the return part V2. During the return stroke, no rotating motion is transmitted to the transmission shaft 4 and therefore the rotating energy it receives is cyclic.
  • the transmission shaft 4 By connecting the transmission shaft 4 to a plural number of power units or cylinder spaces 1 that are on different strokes, a more continuous rotation of the transmission shaft is achieved.
  • the pressure fluid conduits 13 are connected to the pressure fluid circuit of the return part and the return conduits 7 to the pressure fluid circuit of the working part, the working parts V1 and the return parts V2 of the cylinder space being thus interchanged.
  • the power unit is then controlled and operated as described above. If there is an equal pressure in the conduits 20a, 20b and 25, the transmission shaft 4 is free to rotate in both directions.
  • FIG 3 is a schematic, partly sectional side view of a third embodiment of the power unit of the invention.
  • the embodiment is largely similar to the one shown in Figures 2a, 2b, only in this case the power unit does not comprise a third control conduit or grooves and conduits arranged to the flange 21.
  • the sleeve 10 and partly the first pistons 3 are provided with a through-conduit 27 connecting the return parts V2 to a gap 28 between the sleeve 10 and the flange 21. Consequently, the pressure of the return part V2 acts on the gap 28.
  • the first and the second control conduits 20, 20b operate in the same way as in the embodiments of the invention shown in Figures 2a, 2b.
  • the working pressure prevailing in the first and the second control conduits 20a, 20b exceeds the pressure of the return part V2 and presses the sleeve 10 and the flange 21 against each other, whereby the transmission shaft 4 makes a rotating motion in the first direction along with the pistons 3.
  • the returning pressure of the return part V2 detaches the sleeve 10 from the flange 47, and the transmission shaft 4 does not perform a rotating motion back in the second direction along with the first pistons 3.
  • the structure of the power unit is extremely simple, but the transmission shaft can only be rotated in one direction. If the conduits 14a, 14b and 7 contain an equal pressure, the transmission shaft 4 is free to rotate in both directions.
  • Figure 4a is a schematic, partly sectional side view of a fourth embodiment of the power unit of the invention
  • Figure 4b is a schematic, exploded perspective view of the embodiment of Figure 4a of the power unit.
  • the form of the transmission member resembles that of a bobbin: at both ends of the sleeve 10 there are provided perpendicular flange portions 29a, 29b.
  • the first and the second pistons 3, 5 are substantially of the shape and size of the cylinder space that remains between the flange portions 29a, 29b.
  • the first pistons 3 are immovably attached relative to the transmission member and, correspondingly, the second pistons 5 are immovably attached relative to the casing 2 of the cylinder space.
  • the pistons 3, 5 are thus similarly arranged as in the embodiments of the invention shown in Figures 2a, 2b and 3.
  • every other part between the pistons of the cylinder space 1 is a working part V1 and every other part is a return part V2.
  • the cylinder space is sealed by a first and a second end flange 12a, 12b, which are both provided with control conduits 20a, 20b, similarly as in the embodiments of the invention described above.
  • a flange 21 that is attached to the transmission shaft 4.
  • the radii of the flange portions 29a, 29b and the flange 21 are substantially equal.
  • the power unit shown in Figures 4a, 4b operates in the same way as the one shown in Figure 3.
  • the large friction surface between the second flange portion 29b and the flange 21 allow extremely high forces to be transmitted to the transmission shaft 4, because the friction force between them is proportional to the square of their radii.
  • the length of the cylinder space 1 and the pistons 3, 5 can be correspondingly increased, whereby an extremely powerful power unit is achieved.
  • the mass of the transmission member is relatively low, and thereby the mass forces during the operation of the power unit are low.
  • the pressure in the gap 28 between the second flange portion 29b and the flange 21 can also be controlled through a separate control conduit, i.e. with a solution that is substantially similar to the third control conduit shown in Figures 2a, 2b.
  • the power unit may comprise more than two cylinder spaces 1 one after another. The more cylinder spaces on different strokes, the smoother the running and torque provided by the transmission shaft 4.
  • the transmission shaft 4 can be rotated using one or more power units.
  • the cylinder spaces may comprise one or more piston pairs: increasing their number allows the torque to be increased, but the rotation angle provided by a single working stroke reduces correspondingly.
  • Different pressure fluids can be used as a pressure medium, such as oil or water, as well as gases or gas mixtures, for example compressed air.
  • the friction properties of the contact surfaces between the end flanges and the transmission members can be modified using friction-plates, for example, or other similar solutions known per se.
  • the external pressure fluid space of the embodiment of the invention shown in Figures 2a, 2b can also be implemented by providing the power unit with at least two cylinder spaces in which the pistons are on different strokes and the return parts V2 of which are interconnected by a return conduit: the pistons in the cylinder space that is on a working stroke press the pressure fluid of the return part V2 into the return part V2 of the cylinder space that is on a return stroke.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Abstract

L'invention concerne une unité de puissance commandée et régulée par un fluide sous pression, comprenant un espace annulaire (1) cylindrique, au moins deux pistons (3, 5) se déplaçant l'un par rapport à l'autre, au moins l'un des pistons étant agencé de façon à tourner autour de l'axe de l'espace cylindrique de sorte qu'il peut se déplacer dans ledit espace cylindrique dans le sens de sa circonférence. Un arbre de transmission (4) est relié de façon à tourner autour de l'espace cylindrique avec ledit piston. Un élément de transmission (10, 10a, 10b) est fixé au piston, cet élément étant concentrique à l'arbre de transmission. Au moins l'un des flasques d'extrémité (12a, 12b) de l'espace cylindrique est doté d'une rainure (14a, 14b) de fluide sous pression. Ladite rainure de fluide sous pression est opposée à l'élément de transmission (10, 10a, 10b) de sorte que le fluide sous pression est agencé de façon à pousser l'élément de transmission (10, 10a, 10b), dans un sens axial, contre une surface de réaction, afin de verrouiller cet élément de transmission (10, 10a, 10b), ou de ralentir son déplacement par rapport à l'espace cylindrique (1).
PCT/FI2001/001051 2000-12-08 2001-12-04 Unite de puissance commandee par pression Ceased WO2002046580A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2002216133A AU2002216133A1 (en) 2000-12-08 2001-12-04 Pressure-fluid-operated power unit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20002691 2000-12-08
FI20002691A FI110633B (fi) 2000-12-08 2000-12-08 Paineväliaineohjattu paineväliainetoiminen voimalaite

Publications (1)

Publication Number Publication Date
WO2002046580A1 true WO2002046580A1 (fr) 2002-06-13

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Family Applications (1)

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PCT/FI2001/001051 Ceased WO2002046580A1 (fr) 2000-12-08 2001-12-04 Unite de puissance commandee par pression

Country Status (3)

Country Link
AU (1) AU2002216133A1 (fr)
FI (1) FI110633B (fr)
WO (1) WO2002046580A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140271295A1 (en) * 2013-03-14 2014-09-18 Woodward, Inc. Rotary Vane Actuator With Fluid Actuated Mechanical Lock
EP3387266A4 (fr) * 2015-12-11 2019-01-16 Hudiksvalls Teknik Centrum Ab Agencement de palier pour une unité mutuellement tournante travaillant sous une pression élevée

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986006786A1 (fr) * 1985-05-08 1986-11-20 Hartwig Groeneveld Machine a pistons rotatifs
DE3900375A1 (de) * 1989-01-09 1989-07-27 Georg Prof Dipl Ing Hauck Schwingkolbenmotor
US5743370A (en) * 1995-09-14 1998-04-28 Valeo Hydraulic clutch release bearing for a motor vehicle diaphragm clutch

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986006786A1 (fr) * 1985-05-08 1986-11-20 Hartwig Groeneveld Machine a pistons rotatifs
DE3900375A1 (de) * 1989-01-09 1989-07-27 Georg Prof Dipl Ing Hauck Schwingkolbenmotor
US5743370A (en) * 1995-09-14 1998-04-28 Valeo Hydraulic clutch release bearing for a motor vehicle diaphragm clutch

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140271295A1 (en) * 2013-03-14 2014-09-18 Woodward, Inc. Rotary Vane Actuator With Fluid Actuated Mechanical Lock
US9915241B2 (en) * 2013-03-14 2018-03-13 Woodward, Inc. Rotary vane actuator with fluid actuated mechanical lock
EP3387266A4 (fr) * 2015-12-11 2019-01-16 Hudiksvalls Teknik Centrum Ab Agencement de palier pour une unité mutuellement tournante travaillant sous une pression élevée
US10422378B2 (en) 2015-12-11 2019-09-24 Hudiksvalls Teknikcentrum Ab Bearing arrangement for a mutually turnable unit working under high pressure

Also Published As

Publication number Publication date
AU2002216133A1 (en) 2002-06-18
FI20002691A0 (fi) 2000-12-08
FI20002691L (fi) 2002-06-09
FI110633B (fi) 2003-02-28

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