EP1957804B1 - Pressure medium powered rotary apparatus unit and system - Google Patents

Pressure medium powered rotary apparatus unit and system Download PDF

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Publication number
EP1957804B1
EP1957804B1 EP06794109A EP06794109A EP1957804B1 EP 1957804 B1 EP1957804 B1 EP 1957804B1 EP 06794109 A EP06794109 A EP 06794109A EP 06794109 A EP06794109 A EP 06794109A EP 1957804 B1 EP1957804 B1 EP 1957804B1
Authority
EP
European Patent Office
Prior art keywords
rotary apparatus
flange
pressure medium
shaft
apparatus 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.)
Not-in-force
Application number
EP06794109A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1957804A1 (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
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Individual
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Publication date
Application filed by Individual filed Critical Individual
Publication of EP1957804A1 publication Critical patent/EP1957804A1/en
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Publication of EP1957804B1 publication Critical patent/EP1957804B1/en
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Anticipated expiration legal-status Critical

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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
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
    • F15B15/125—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type of the curved-cylinder type

Definitions

  • the subject of the present invention is a pressure medium powered rotary apparatus more closely defined in the preamble of the independent claim 1.
  • the pressure medium powered rotary apparatus of the present invention can be utilised to use different kinds of implements having rotational movement involved.
  • Prior art publication DE 29 28 642 B1 discloses a solution according to preamble of the independent claim 1.
  • This cited publication comprises a pressure medium powered rotary apparatus unit having two oppositely positioned flange components within an axial distance from each other and connected to each other, further an outer casing part between the flange components for coupling said flanges to each other and a cylinder room and a piston arrangement.
  • This rotary apparatus unit further comprising a channel system arrangement for feeding a pressure medium into the cylinder room and for removing the pressure medium from said room, and that an intermediate element substantially having a overall shape of flange is positioned between the flanges wherein the intermediate element comprises at least one curved, elongated groove penetrating the intermediate element substantially in axial direction, said groove forming the cylinder room and, that the piston arrangement positioned into the groove is attached to at least to one flange component.
  • the object of the present invention is to present a pressure medium powered rotary apparatus, which can by easily operable means, as to the construction, be modified and functionally controlled with regard to the functional needs of the application in question.
  • the pressure medium powered rotary apparatus of the present invention is mainly characterised in accordance with the characteristic part of claim 1.
  • the pressure medium powered rotary system of the present invention is mainly characterised in accordance with the characteristic part of the independent claim defining the system.
  • the main advantage of the present invention is to provide an easily operable and adjustable means in construction for machinery a multipurpose basic solution for several fields of needs and uses.
  • the sophisticated entity to be used as to the angle of rotation, the momentum needed (the force of rotation), the speed of rotation etc. is a result of evaluation of the specific needs and uses of application in question.
  • the pressure medium powered rotary apparatus unit comprises as main components at least two oppositely positioned flange components 2, 6, which are situated apart from each other within an axial distance (perpendicular with respect to the main common active level of the same).
  • the flange components 2, 6 are connected to each other in a manner described later on herebelow.
  • An outer casing part (the construction differs in accordance with the embodiment in question) is arranged between the said flange components 2, 6 to connect the said flange components (2, 6), whereby a possibility for a cylinder room with a piston arrangement is accomplished.
  • the rotary apparatus unit is further comprising a channel system arrangement 16a, 16b, 14, 20, 19 for feeding a pressure medium, preferably hydraulic, into the cylinder room and for removing the pressure medium from the cylinder room.
  • An intermediate element 1 substantially having a overall shape of flange is positioned between the flange components 2, 6.
  • the intermediate element 1 comprises at least one curved (preferably constant radius), elongated groove 1b penetrating (or crossing) the intermediate element 1 substantially in axial direction.
  • the reference is made to the groove 1b in Fig.1 ; and to the grooves 1ba and 1bb in Figs. 2a and 2b .
  • the intermediate element 1 partially thus functionally forms at least a section of the outer casing part between the flange components 2, 6 i.e. the outer part 1a outside the groove 1b / the grooves 1ba and 1bb (seen in radial direction) of the intermediate element 1.
  • a piston arrangement 3c penetrating (or crossing) the groove 1b in axial direction is attached to at least to one of the flange components 2, 6, suitably to both of them.
  • Figs. 2a , 2b show that the partial grooves 1ba and 1bb, both, have the same kind of piston arrangements as shown in Fig.1 .
  • Most preferably the substantial main form of the parts1, 2 and 6 is plate-like round discus, either having constant or varying thickness.
  • Both of the flange components 2, 6 and the intermediate element 1 likewise are provided with an axial centre hole 2R, 6R, 1R for a shaft 23 going thorough the said holes 2R, 6R, 1R in axial direction.
  • the shaft 23 is arranged, as a part (reference numerals 16a, 16b, 14a, 14b, construction of which is explained herebelow) of said channel system arrangement 16a, 16b, 14, 20, 19, to feed and remove pressure medium to and from the groove 1b / grooves 1ba, 1bb.
  • the parts 16a, 16b, 14a, 14b are in pressure medium flow contact with the channel extensions 19, 20 in the intermediate element 1.
  • the shaft 23 can be used additionally with reference to the foregoing (or instead of it) for the power output of the rotary apparatus.
  • the flange components 2, 6 are connected with at least one elongated substantially axially placed part 3, (only one in Fig. 1 ; two in Figs. 2a , 2b ) having the overall shape of a pivot, whose opposite ends are connected to the flange component 2, 6 in question.
  • the centre region (in axial direction) of the part 3 that is, the region, which crosses the intermediate element 1 is situated in the groove 1b / grooves 1ba, 1bb and at that region essentially forms the piston arrangement 3c, together with the sealing arrangement 5, which is suitably composed out of at least two axial gaskets 5, which seal the piston arrangement 3c in radial direction against the inner and outer surfaces of the groove 1b/ grooves 1ba, 1bb.
  • each of the flange components 2, 6 has penetrating holes 2a, 6a; 2b, 6b, going thorough said flange components 2, 6 both in circumferential and radial directions in juxtaposed positions.
  • the pivot-shaped part 3 is placed through the penetrating holes 2a, 6a; 2b, 6b and the corresponding groove 1b forming the cylinder room.
  • the fastening part such as a threaded screw section 3a on the outer surface of the pivot-shaped part 3 or alike, at least at the other end of the pivot-shaped part 3 protrudes in axial direction outwards from the outer surface of the flange component 2, 6 in question or from immersed groove in the flange component 2, 6 in question at said penetrating hole.
  • Each screw section 3a is connected to a corresponding screwed tension nut 4 or alike for tightening and tensioning purposes.
  • the rotation of the pivot-shaped part 3 around the axial direction is prevented for instance by means of the radial lock screw system 28 ( Fig. 4 ) between the flange component 6 and the pivot-shaped part 3 in question.
  • a ring-like sealing area 8 preferably a pair formation, is arranged to the inner surfaces of both of the flange components 2, 6 surfaces facing towards the intermediate element 1 i.e. most optimally inner surfaces in both flange components 2, 6 have circular grooves or alike with different predetermined radius.
  • Each of the grooves is equipped with a corresponding circular gasket 8a, 8b.
  • the sealing area is constructionally so arranged that the groove(s) 1b; 1ba, 1bb ( Fig.1 and Figs. 2a , 2b ) forming the cylinder room of the intermediate element 1 is/are situated in radial direction between the separate gaskets 8a, 8b of the sealing area 8.
  • the intermediate element 1 of the rotary apparatus unit has at least one groove 1b forming the cylinder room having circular overall shape, wherein the centre of the circular radius of said at least one groove 1b, seen in section perpendicular to the axial direction (orthogonal) of the rotary apparatus unit, is in the centre of the intermediate element 1.
  • the radius of curvature R1 corresponds in a certain axial point of the intermediate element 1 to the position of the outer edge of the groove 1b and the radius of curvature R2 in the corresponding point to the position of the inner edge of said groove 1.
  • R1 - R2 SL
  • SL is the radial width of the cylinder room in that specific point of observation.
  • the length of the groove 1b measured in direction of the periphery of the groove is at least 120 degrees ⁇ 60 degrees, suitably 210 degrees ⁇ 30 degrees, most suitably 295 degrees ⁇ 45 degrees.
  • the intermediate element 1 of the rotary apparatus has two grooves 1ba, 1bb forming the cylinder room together, and having the same equal radius with regard to each other having circular overall shape, wherein the centre of the circular radius of said at least one groove 1b, seen in section perpendicular to the axial direction (orthogonal) of the rotary apparatus unit, is in the centre of the intermediate element 1.
  • the radius of curvature R1 corresponds in a certain axial point of the intermediate element 1 to the position of the outer edge of the groove 1b and the radius of curvature R2 in the corresponding point to the position of the inner edge of said groove 1.
  • R1 - R2 SL
  • SL is the radial width of the cylinder room in that specific point of observation.
  • the length of the grooves 1ba, 1bb measured in direction of the periphery of the grooves 1ba, 1bb is at most 175 degrees.
  • the inner and/or outer surface of the groove(s) 1b; 1ba, 1bb forming the cylinder room can be axial (a) or divergent from that AB, BA, BB, wherein the cross-section of the piston arrangement 3c (seen as sectional axial view or in radial direction) is respectively essentially rectangle A, trapezium AB, BA or the parallelogram BB.
  • a support ring 21 or alike is arranged at the site of the intermediate member 1 between the flange components 2, 6, to circumference at least partially the said member 1, wherein the flange components 2, 6 are attached together with the tightening means suitably with tightening bolts 22 (eight bolts, a hole-punching in the flange components 2, 6 corresponding to the situation of the hole-punching in the support ring 21 or alike).
  • the output of the rotational movement out of the rotary apparatus has been arranged through the axial centre hole 1R in the intermediate member 1 by using the element 31 attached to it.
  • the element 31 to be used for the output of the rotational movement is a tubular piece or alike, which is projecting outwards from the end of the rotary apparatus, and into which the shaft 23 is situated.
  • the shaft 23 has been locked in a non-rotational manner to the flange component 6, by using the locking parts 24a, 24b.
  • the reference numeral 26 shows a rotational wheel or the end of a rotational shaft, to which the element 31 is attached.
  • the reference numeral 25 shows a base to which the opposite flange component 2 is attached by using the tubular flange a projecting outwards from the end of the said second flange component 2.
  • the shaft 23 is used in the circulation of the pressure medium in a manner that the shaft 23 is provided with two tubular conduits 23a, 23b separated from each other and being arranged in the longitudinal direction of the shaft 23.
  • the first one of the conduits 23a is connected with the flange component 2 and the second one of the conduits 23b is connected with the opposite flange component 6.
  • Both of the tubular conduits 23a, 23b has been provided with a radial tubular conduit 16a, 16b or alike apart from each other in the longitudinal direction of the shaft 23.
  • Each of the radial tubular conduits 16a, 16b has the first end at the outer surface of the tubular conduit 23a, 23b in question and the second end at the surface of the shaft 23.
  • the first radial tubular conduit 16a is positioned at the flange component 2 seen in the in the radial direction and the second radial tubular conduit 16b is positioned at the opposite flange component 6 seen in the in the radial direction, both of the radial tubular conduits 16a, 16b in a pressure medium flow contact with continuation conduits 19, 20 in connection with the flange component 2, 6 in question.
  • the outer surface of the shaft 23, at the site of each of the radial tubular conduits 16a, 16b is provided with a ring-shaped groove 14a, 14b or alike each of them situated in a plane perpendicular with the axial direction of the shaft 23.
  • the outer surface of the shaft 23 is provided with ring-shaped sealing grooves 15 or alike with corresponding ring-shaped gaskets on both sides (seen in the axial direction) of each of the ring shaped grooves 14a 14b or alike.
  • the said sealing grooves 15 with gaskets are situated in the assembled position of the shaft at the flange component 2, 6 in question (see Fig. 4 ).
  • both the first and the second one of the ring-shaped grooves 14a, 14b or alike are situated at the site of the first end of the continuation conduits 19, 20 in the respective flange component 2, 6.
  • Each of the continuation conduits 19, 20 is in pressure medium flow contact with a pressure effected side of the piston arrangement 3c in a manner that the pressure medium going through the continuation conduits 19, 20 is rotating the flange components 2, 6 and the intermediate element 1 with respect to each other.
  • each continuation conduit 19, 20 comprises within each flange component 2, 6 substantially radial first bore 20 or alike, the fist end 20a of which is at the surface of the centre axial hole 2R, 6R of the flange component 2, 6 in question during the pressure medium flow trough the shaft 23.
  • the first end 20b of the substantially radial bore 20 or alike is situated on the outer surface of the flange component 2, 6 in question.
  • the continuation conduit 19, 20 further comprises in both embodiments within each flange component 2, 6 a substantially axial second bore 19 or alike in a pressure medium flow contact with the first bore 20.
  • the second bore 19 is situated beside the piston arrangement 3c in connection with the groove(s) 1b; 1ba, 1bb.
  • the second bore 19 is more precisely situated beside the through hole(s) 2a, 6a; 2b, 6b ( Fig. 3 ) penetrating the flange components 2, 6 and intended for receiving the pivot-shaped part 3.
  • the second bore is formed as a groove at the side of each of the through hole(s) 2a, 6a; 2b, 6b.
  • the intermediate part in the longitudinal direction ( Fig. 1 ) in the pivot-shaped part 3 in both sides of the piston arrangement 3c, between the said piston arrangement 3c and the threaded screw sections 3a are situated in the assembled position into the hole(s) 2a, 6a; 2b, 6b.
  • the first bore 20 or alike can in practice be a radial bore penetrating the flange component 2, 6 starting from the surface of the centre hole 2R, 6R and ending to the outer surface of the flange component 2, 6 in question.
  • either end of the first bore 20 is closed in accordance with the embodiment in question.
  • the inner opening 20a at the surface of the centre hole 2R, 6R in question is closed, and the pressure medium flow is directed to/from the groove 1b via the outer opening 20b.
  • the outer opening 20b is closed, wherein the pressure medium flow is directed through the inner opening 20a of the first bore 20 into the shaft 23.
  • Outer valve means (not shown) is used to regulate the directions of the pressure medium flow in accordance with the needs.
  • Fig 2b (utilising the basic solution of Fig. 2a , with two grooves) shows an embodiment of the power output in accordance with the present invention.
  • the power output is arranged by using a sleeve-shaped gearing means 27 surrounding the first flange component 2 and the intermediate element 1.
  • the sleeve-shaped gearing means 27 is attached to the intermediate element 1 at the first end of the same, for instance, by means of radial screw fixation.
  • the output of the rotational force is arranged through the second end 27a of the sleeve-shaped gearing means 27 well known in the art.
  • the flange component 6, not situated inside the sleeve-shaped gearing means 27 has been attached to a firm base 25 or alike.
  • FIG. 4 shows an embodiment in which three rotary apparatus units A, B, C of Fig. 2a are connected.
  • each of the rotary apparatus units A, B, C is couple to the same common shaft 23A, 23B, 23C.
  • the shaft 23A, 23B, 23C comprises in its longitudinal direction sequentially as described in detail hereabove a) radial drillings 16a, 16b or equivalent, b) circular grooves 25a, 25b and also c) seal grooves 15 or equivalent groups for each rotary apparatus unit A, B, C to be coupled into the system.
  • the rotary apparatus units are connected with the means mediating the rotation 12 supplying the rotational effect for each of the rotary apparatus units A, B, C coupled to the system or combination in order to combine single rotations of the apparatus units A, B, C into the coupled rotation of the system.
  • the rotary apparatus units A and C at the opposite ends of the combination are combined by a frame construction 13, suitably by a shielding tube.
  • the flange components 2, in the rotary apparatus units A and C at the opposite ends of the combination, facing outwards from the combination are attached in connection with the frame construction 13; the first one (the rotary apparatus unit A, the flange components 2, in Fig.
  • the combination of the separate rotational movements of the individual apparatus units is arranged in accordance with the embodiment of Fig. 4 in a manner the intermediate element 1A of the first apparatus unit A which is fixedly attached to the frame construction 13 as described hereabove, is connected by means 12 mediating the rotation, (suitably by covering tube with peripheral radial screw attachments 12a in both ends of the same) to the next, second rotary unit B, more precisely to the intermediate element 1B of the same, attached to the shaft 23A, 23B, 23C.
  • the means 12 mediating the rotation between the rotary apparatus units in sequence hereafter B to C have been arranged in a manner that the flange component 6 inside the tubular frame construction 13 of the preceding rotary apparatus (for instance B, in Fig. 4 ) facing towards the next rotary apparatus unit in axial direction (for instance C, in Fig. 4 ) is attached to the intermediate element (for instance 1C, in Fig. 4 ) of the said next rotary apparatus unit.
  • the regulation of the pressure medium flow through the tubular conduits 23a, 23b can be arranged by a regulating valve (not shown).
  • the groove(s) 1b; 1ba, 1bb in each rotary apparatus unit A, B, C are situated in order to accomplish a combinatory rotational movement so that the overall rotation angle of the system desired is achieved, suitably by consecutive series of movements and/or so that the groove(s) 1b; 1ba, 1bb are in the rotational direction at least partially situated to co-operate (one upon the other seen in perpendicular section with respect to the axial direction) simultaneously for instance in order to accomplish a momentary change in moment or momentum during the rotation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Actuator (AREA)
  • Joints Allowing Movement (AREA)
EP06794109A 2005-10-14 2006-10-13 Pressure medium powered rotary apparatus unit and system Not-in-force EP1957804B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20051042A FI20051042A0 (fi) 2005-10-14 2005-10-14 Paineväliainekäyttöinen kiertolaiteyksikkö ja sovitelma kiertolaiteyksikköjen käyttämiseksi
PCT/FI2006/000333 WO2007042612A1 (en) 2005-10-14 2006-10-13 Pressure medium powered rotary apparatus unit and system

Publications (2)

Publication Number Publication Date
EP1957804A1 EP1957804A1 (en) 2008-08-20
EP1957804B1 true EP1957804B1 (en) 2013-03-06

Family

ID=35185182

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06794109A Not-in-force EP1957804B1 (en) 2005-10-14 2006-10-13 Pressure medium powered rotary apparatus unit and system

Country Status (6)

Country Link
EP (1) EP1957804B1 (fi)
CN (1) CN101331326B (fi)
AU (1) AU2006301112A1 (fi)
FI (1) FI20051042A0 (fi)
NO (1) NO20082192L (fi)
WO (1) WO2007042612A1 (fi)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102192214B (zh) * 2011-04-02 2015-04-01 肇庆市志成气动有限公司 一种高可靠的摆动气缸
PT2820310T (pt) * 2012-02-28 2019-01-24 Vincent Luc Antoine Tadino Dispositivo de ar comprimido para o controle de válvulas
ES2435340B1 (es) * 2012-06-15 2014-12-05 Gamesa Innovation & Technology, S.L. Sistema de fijación para aerogeneradores y método de colocación del mismo
CN111425462B (zh) * 2020-03-31 2021-06-18 佛山市云米电器科技有限公司 一种出风阵列机构及应用其的出风设备

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU490457B2 (en) * 1976-07-02 1976-10-14 Abex Corporation T. a control valve
DE2928642C2 (de) * 1979-07-16 1983-12-15 Kücke, Günther, Ing.(grad.), 4811 Oerlinghausen Hydraulische oder pneumatische Schwenkkolben-Kraftmaschine
US4492150A (en) * 1983-07-01 1985-01-08 Yates Harlan W Actuator for mechanical apparatus
FR2607200B1 (fr) 1986-11-26 1991-09-06 Applic Mach Motrices Dispositif actionneur hydraulique rotatif a palette, destine notamment a l'entrainement d'une gouverne d'aeronef
US5101862A (en) * 1991-08-08 1992-04-07 Leete Barrett C Rotary actuator and valve control system

Also Published As

Publication number Publication date
AU2006301112A1 (en) 2007-04-19
FI20051042A0 (fi) 2005-10-14
NO20082192L (no) 2008-07-04
WO2007042612A1 (en) 2007-04-19
CN101331326A (zh) 2008-12-24
EP1957804A1 (en) 2008-08-20
CN101331326B (zh) 2013-01-02

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