EP1957804B1 - Pressure medium powered rotary apparatus unit and system - Google Patents
Pressure medium powered rotary apparatus unit and system Download PDFInfo
- 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.)
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Classifications
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- 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
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- 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
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- 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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Description
- 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. As to the prior art known in the field, reference is made to publications
US-4492150 ,US-4825754 andUS-5101862 . These publications concern some actuator devices for limited purposes. - 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. - In this publication hydraulic pressure medium is led through a flange into the cylinder room. This can cause difficulties when additional casing is mounted to cover the apparatus. In the present invention pressure medium is led by new way without possible problems described above.
- 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.
- For achieving these purposes the pressure medium powered rotary apparatus of the present invention is mainly characterised in accordance with the characteristic part of claim 1.
- The dependent claims concerning the pressure medium powered rotary apparatus of the invention present some advantageous embodiments.
- For achieving these purposes 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 dependent claims concerning the pressure medium powered rotary system of the invention present some advantageous embodiments.
- The main advantage of the present invention, as to the pressure medium powered rotary apparatus and system, 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.
- As to the determinations used hereinafter, the following remarks should be taken in account in considering the semantics of the same:
- "An intermediate element substantially having a overall shape of flange" means that the intermediate element is having a substantially functional planar formation (linear and/or non-linear) and is reaching outwards in radial direction from the centre axis (substantially perpendicular or inclined with respect to the main level of the flange components) of the apparatus in question; and
- "a pivot-shaped part" means that the part has an overall form of a rod or shaft and which is co-operating in the accomplishing the rotational movement.
- The pressure medium powered rotary apparatus and the system of the present invention are more closely explained in the following description, made with reference to the accompanying drawings illustrating some, non-limiting embodiments of the present invention, wherein
-
Fig 1 is an exploded perspective view of a pressure medium powered rotary apparatus according to the present invention, -
Figs 2a ,2b present the second embodiment of the pressure medium powered rotary apparatus according to the present invention; an exploded perspective view of the rotary apparatus (Fig. 2a ) of the second embodiment; and the power output applied in connection with the second embodiment also as an exploded perspective view (Fig.2b ), -
Fig. 3 is a sectional view of the flange of the second embodiment ofFigs 2a and2b in the direction perpendicular with respect to the axial direction of the pressure medium powered rotary apparatus; and -
Fig 4 is an embodiment of the system of the present invention with apparatuses according toFig. 2a as a sectional view taken along the common axis of the system of the combined apparatuses. - With reference to the enclosed drawings the pressure medium powered rotary apparatus unit comprises as main components at least two oppositely positioned
flange components flange components flange components - The rotary apparatus unit is further comprising a
channel system arrangement - An intermediate element 1 substantially having a overall shape of flange is positioned between the
flange components elongated groove 1b penetrating (or crossing) the intermediate element 1 substantially in axial direction. The reference is made to thegroove 1b inFig.1 ; and to the grooves 1ba and 1bb inFigs. 2a and2b . The intermediate element 1 partially thus functionally forms at least a section of the outer casing part between theflange components outer part 1a outside thegroove 1b / the grooves 1ba and 1bb (seen in radial direction) of the intermediate element 1. - To achieve the full function of the apparatus a
piston arrangement 3c (Fig.1 ) penetrating (or crossing) thegroove 1b in axial direction is attached to at least to one of theflange components Figs. 2a ,2b show that the partial grooves 1ba and 1bb, both, have the same kind of piston arrangements as shown inFig.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 theflange components axial centre hole shaft 23 going thorough the saidholes shaft 23 is arranged, as a part (reference numerals channel system arrangement groove 1b / grooves 1ba, 1bb. Theparts channel extensions 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 part 3, (only one inFig. 1 ; two inFigs. 2a ,2b ) having the overall shape of a pivot, whose opposite ends are connected to theflange component part 3 that is, the region, which crosses the intermediate element 1 is situated in thegroove 1b / grooves 1ba, 1bb and at that region essentially forms thepiston arrangement 3c, together with thesealing arrangement 5, which is suitably composed out of at least twoaxial gaskets 5, which seal thepiston arrangement 3c in radial direction against the inner and outer surfaces of thegroove 1b/ grooves 1ba, 1bb. - To connect the pivot-
shaped part 3 to theflange components flange components holes flange components shaped part 3 is placed through the penetratingholes corresponding groove 1b forming the cylinder room. The fastening part, such as a threadedscrew section 3a on the outer surface of the pivot-shaped part 3 or alike, at least at the other end of the pivot-shapedpart 3 protrudes in axial direction outwards from the outer surface of theflange component flange component screw section 3a is connected to a correspondingscrewed 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 theflange 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 flange components circular gasket Fig.1 andFigs. 2a ,2b ) forming the cylinder room of the intermediate element 1 is/are situated in radial direction between theseparate gaskets - With reference to the embodiment in
Fig. 1 (see specially the enlarged detail A) the intermediate element 1 of the rotary apparatus unit has at least onegroove 1b forming the cylinder room having circular overall shape, wherein the centre of the circular radius of said at least onegroove 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 thegroove 1b and the radius of curvature R2 in the corresponding point to the position of the inner edge of said groove 1. Thus the equation, with reference toFig. 1 , shows that R1 - R2 = SL, where SL is the radial width of the cylinder room in that specific point of observation. The length of thegroove 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. - Correspondingly with reference to
Figs. 2a ,2b (see specially the enlarged detail B) 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 onegroove 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 thegroove 1b and the radius of curvature R2 in the corresponding point to the position of the inner edge of said groove 1. Thus the equation, with reference toFig. 1 , shows that R1 - R2= SL, where 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. - Further with reference to
Fig. 1 ,Figs. 2a ,2b , together with the principal idea of the present invention (actual possibility towards embodiments having more than two grooves) between the ends of the groove(s) 1b; 1ba, 1bb there is apartition wall 1c, which can be validly in equation described in a following manner: 2·π·R = n·(UPS + VSPS), where UPS is the length of thegroove 1b; 1ba, 1bb in the direction of the mean curvature radius R and VSPS is the length of thepartition wall 1c in the same direction and n is the quantity of thegrooves 1b; 1ba, 1bb and simultaneously the same ofpartition elements 1c. - Further, 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. - With reference to the embodiment of
Fig. 1 , asupport ring 21 or alike is arranged at the site of the intermediate member 1 between theflange components flange components flange components support ring 21 or alike). The output of the rotational movement out of the rotary apparatus has been arranged through theaxial centre hole 1R in the intermediate member 1 by using theelement 31 attached to it. Theelement 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 theshaft 23 is situated. Theshaft 23 has been locked in a non-rotational manner to theflange component 6, by using thelocking parts reference numeral 26 shows a rotational wheel or the end of a rotational shaft, to which theelement 31 is attached. Further thereference numeral 25 shows a base to which theopposite flange component 2 is attached by using the tubular flange a projecting outwards from the end of the saidsecond flange component 2. - As to the main principle of the present invention, in the first hand feeding the pressure medium into the cylinder room of the rotary apparatus; and in the second hand removing the pressure medium from the cylinder room of the rotary apparatus, is arranged by using the
opposite flange components - According to the embodiments of
Figs 2a ,2b (see alsoFigs 3 and4 ) theshaft 23 is used in the circulation of the pressure medium in a manner that theshaft 23 is provided with twotubular conduits shaft 23. The first one of theconduits 23a is connected with theflange component 2 and the second one of theconduits 23b is connected with theopposite flange component 6. Both of thetubular conduits tubular conduit shaft 23. Each of the radialtubular conduits tubular conduit shaft 23. When the commonaxial centre hole flange components shaft 23 in the assembled position the first radialtubular conduit 16a is positioned at theflange component 2 seen in the in the radial direction and the second radialtubular conduit 16b is positioned at theopposite flange component 6 seen in the in the radial direction, both of the radialtubular conduits continuation conduits flange component Fig. 3 ). Further, the outer surface of theshaft 23, at the site of each of the radialtubular conduits groove shaft 23. Yet further, the outer surface of theshaft 23 is provided with ring-shaped sealinggrooves 15 or alike with corresponding ring-shaped gaskets on both sides (seen in the axial direction) of each of the ring shapedgrooves 14agrooves 15 with gaskets are situated in the assembled position of the shaft at theflange component Fig. 4 ). - Further in the assembled state of the
shaft 23 both the first and the second one of the ring-shapedgrooves continuation conduits respective flange component continuation conduits piston arrangement 3c in a manner that the pressure medium going through thecontinuation conduits flange components - With reference to
Figs. 2a ,2b andFig. 3 eachcontinuation conduit flange component first bore 20 or alike, thefist end 20a of which is at the surface of the centreaxial hole flange component shaft 23. In accordance withFig. 1 , wherein theshaft 23 is not used in feeding and removal of the pressure medium thefirst end 20b of the substantiallyradial bore 20 or alike is situated on the outer surface of theflange component continuation conduit flange component second bore 19 or alike in a pressure medium flow contact with thefirst bore 20. Thesecond bore 19 is situated beside thepiston arrangement 3c in connection with the groove(s) 1b; 1ba, 1bb. Thesecond bore 19 is more precisely situated beside the through hole(s) 2a, 6a; 2b, 6b (Fig. 3 ) penetrating theflange components part 3. Thus 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-shapedpart 3 in both sides of thepiston arrangement 3c, between the saidpiston arrangement 3c and the threadedscrew sections 3a are situated in the assembled position into the hole(s) 2a, 6a; 2b, 6b. Thefirst bore 20 or alike can in practice be a radial bore penetrating theflange component centre hole flange component first bore 20 is closed in accordance with the embodiment in question. With reference toFig. 1 theinner opening 20a at the surface of thecentre hole groove 1b via theouter opening 20b. With reference to the embodiments inFigs. 2a ,2b theouter opening 20b is closed, wherein the pressure medium flow is directed through theinner opening 20a of thefirst bore 20 into theshaft 23. Outer valve means (not shown) is used to regulate the directions of the pressure medium flow in accordance with the needs. - Especially
Fig 2b (utilising the basic solution ofFig. 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 thefirst 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 thesecond end 27a of the sleeve-shaped gearing means 27 well known in the art. Correspondingly theflange component 6, not situated inside the sleeve-shaped gearing means 27 (theflange component 2, inFig.2b ), has been attached to afirm base 25 or alike. - It is also possible also to unite or connect at least two rotary apparatus units together to accomplish a functional entity.
Fig. 4 shows an embodiment in which three rotary apparatus units A, B, C ofFig. 2a are connected. Hereby, each of the rotary apparatus units A, B, C is couple to the samecommon shaft shaft radial drillings 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 therotation 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. In accordance with theFig. 4 the rotary apparatus units A and C at the opposite ends of the combination are combined by aframe construction 13, suitably by a shielding tube. In practice, theflange 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 theframe construction 13; the first one (the rotary apparatus unit A, theflange components 2, inFig. 4 ) fixedly; and the second one (the rotary apparatus unit C, theflange components 2, inFig. 4 ) in a manner that rotation of the same is allowed in the axial direction with respect to theframe construction 13. Those flange components 2 (in A, and C inFig. 4 ), which are facing outwards from the system, so called end flange components have a greater radius than those flange components 6 (in A, one component; in B, both components; and in C, one component) situated inside thetubular frame construction 13. Additionally the radiuses of the intermediate elements 1 in the system are smaller than the radiuses of theend flange components 2 facing outwards from the system, but greater than or equal to the radiuses of theflange components 6 inside thetubular frame construction 13. - 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 theintermediate element 1A of the first apparatus unit A which is fixedly attached to theframe construction 13 as described hereabove, is connected by means 12 mediating the rotation, (suitably by covering tube with peripheralradial screw attachments 12a in both ends of the same) to the next, second rotary unit B, more precisely to theintermediate element 1B of the same, attached to theshaft flange component 6 inside thetubular frame construction 13 of the preceding rotary apparatus (for instance B, inFig. 4 ) facing towards the next rotary apparatus unit in axial direction (for instance C, inFig. 4 ) is attached to the intermediate element (forinstance 1C, inFig. 4 ) of the said next rotary apparatus unit. The regulation of the pressure medium flow through thetubular conduits - 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.
- For instance by using the embodiment according to
Fig. 4 an overall rotation angle of 270 degrees is easily achieved, wherein the peripheral length of the individual groove in each single pair of grooves is approximately 125 degrees, i.e. the grooves 1ba, 1bb are in the successive rotary apparatus units A, B, C situated to partially one upon the other.
Claims (5)
- A pressure medium powered rotary apparatus unit, comprising at least two oppositely positioned flange components (2, 6) within an axial distance from each other and connected to each other, an outer casing part between the flange components (2, 6) to connect said flange components (2, 6), a cylinder room and a piston arrangement, the 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 the cylinder room, and wherein an intermediate element (1) substantially having a overall shape of flange is positioned between the flange components (2, 6), wherein the intermediate element (1) comprises at least one curved, elongated groove (1b) penetrating the intermediate element (1) substantially in axial direction, said groove (1b) forming the cylinder room and, wherein the piston arrangement (3c) positioned into the groove (1b) is attached to at least to one flange component (2, 6), characterized in that both the flange components (2, 6) and the intermediate element (1) are provided with an axial centre hole (2R, 6R, 1R) for a shaft (23), and 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), wherein the first one of the conduits (23a) is connected with the first flange component (2, 6) and the second one of the conduits (23b) is connected with the opposite second flange component (6, 2) that both of the tubular conduits (23a, 23b) are provided with a radial tubular conduit (16a, 16b) apart from each other in the longitudinal direction of the shaft (23), that 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), wherein the common axial centre hole (2R, 6R, 1R) in the flange components (2, 6) and in the intermediate member (1) receives the shaft (23) in the assembled position the first radial tubular conduit (16a) is positioned at the first flange component (2, 6) seen in the radial direction, and the second radial tubular conduit (16b) is positioned at the opposite second flange component (6, 2) seen in the radial direction, both of the radial tubular conduits (16a, 16b) being in a pressure medium flow contact with continuation conduits (19, 20) in connection with the flange component (2, 6) in question, 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.
- The rotary apparatus unit in accordance with patent claim 1, characterized in that said shaft (23) is arranged, as apart of the said channel system arrangement (16a, 16b, 14, 20, 19), to feed and remove pressure medium to/from the groove (1b) forming the cylinder room in the intermediate element (1) of the rotary apparatus and/or that through which shaft (23) the power output of the rotary apparatus unit is arranged.
- The rotary apparatus unit in accordance with patent claim 1 characterized in that to connect the piston arrangement (3c) in the form of a pivot-shaped part (3) to the flange components (2, 6), the flange component has through holes (2a, 6a; 2b, 6b), which both circumferentially and in radial direction are in an opposed position, that the pivot-shaped part (3) is positioned through the said holes (2a, 6a;2b, 6b) and the corresponding groove (1b) forming the cylinder room and that at least the other end of the pivot-shaped part (3) is equipped with a fastening part suitably a threaded screw part (3a) which protrudes axially out of the outer surface of the respective flange component (2, 6) or concealed fastenings therein, whereby the threaded screw part (3a) is arranged to receive tension nut (4) or equivalent tensioning elements.
- The rotary apparatus unit in accordance with patent claim 1, characterized in that the pressure medium feed into the rotary apparatus unit and the removal of the same from the rotary apparatus unit is arranged through different opposing flange components (2, 6).
- The rotary apparatus unit in accordance with any of the patent claims 1 - 4, characterized in that the length of the grooves (1ba, 1bb) in the intermediate element (1) of the rotary apparatus measured in direction of the periphery of the grooves (1ba, 1bb) is at most 175 degrees.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FI20051042A FI20051042A0 (en) | 2005-10-14 | 2005-10-14 | Pressure medium driven rotary drive unit and arrangement for operating the rotary drive unit |
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 (en) |
CN (1) | CN101331326B (en) |
AU (1) | AU2006301112A1 (en) |
FI (1) | FI20051042A0 (en) |
NO (1) | NO20082192L (en) |
WO (1) | WO2007042612A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102192214B (en) * | 2011-04-02 | 2015-04-01 | 肇庆市志成气动有限公司 | High-reliability oscillating cylinder |
PL2820310T3 (en) * | 2012-02-28 | 2019-04-30 | Tadino Vincent Luc Antoine | Compressed-air device for controlling valves |
ES2435340B1 (en) * | 2012-06-15 | 2014-12-05 | Gamesa Innovation & Technology, S.L. | Fixing system for wind turbines and method of placement |
CN111425462B (en) * | 2020-03-31 | 2021-06-18 | 佛山市云米电器科技有限公司 | Air outlet array mechanism and air outlet equipment applying same |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU490457B2 (en) * | 1976-07-02 | 1976-10-14 | Abex Corporation | T. a control valve |
DE2928642C2 (en) * | 1979-07-16 | 1983-12-15 | Kücke, Günther, Ing.(grad.), 4811 Oerlinghausen | Hydraulic or pneumatic oscillating piston power machine |
US4492150A (en) * | 1983-07-01 | 1985-01-08 | Yates Harlan W | Actuator for mechanical apparatus |
FR2607200B1 (en) * | 1986-11-26 | 1991-09-06 | Applic Mach Motrices | ROTARY PALLET HYDRAULIC ACTUATOR DEVICE, IN PARTICULAR FOR DRIVING AN AIRCRAFT GOVERNOR |
US5101862A (en) | 1991-08-08 | 1992-04-07 | Leete Barrett C | Rotary actuator and valve control system |
-
2005
- 2005-10-14 FI FI20051042A patent/FI20051042A0/en not_active Application Discontinuation
-
2006
- 2006-10-13 EP EP06794109A patent/EP1957804B1/en not_active Not-in-force
- 2006-10-13 WO PCT/FI2006/000333 patent/WO2007042612A1/en active Application Filing
- 2006-10-13 AU AU2006301112A patent/AU2006301112A1/en not_active Abandoned
- 2006-10-13 CN CN200680046766.7A patent/CN101331326B/en not_active Expired - Fee Related
-
2008
- 2008-05-13 NO NO20082192A patent/NO20082192L/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
FI20051042A0 (en) | 2005-10-14 |
CN101331326A (en) | 2008-12-24 |
WO2007042612A1 (en) | 2007-04-19 |
NO20082192L (en) | 2008-07-04 |
CN101331326B (en) | 2013-01-02 |
AU2006301112A1 (en) | 2007-04-19 |
EP1957804A1 (en) | 2008-08-20 |
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