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.
• 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 object of the present invention is to present a pressure medium powered rotary system according to which the pressure medium powered rotary apparatuses of the present invention, at least two apparatuses combined, can be used in combination, whereby the amount for operational uses and applications is greatly increased.
• 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.
• 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.
• Fig 1 is an exploded perspective view of the first embodiment of the 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 of Figs 2a and 2b in the direction perpendicular with respect to the axial direction of the pressure medium powered rotary apparatus;
• Fig 4 is an embodiment of the system of the present invention with apparatuses according to Fig. 2a as a sectional view taken along the common axis of the system of the combined apparatuses.
• 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 Ib penetrating (or crossing) the intermediate element 1 substantially in axial direction.
• the reference is made to the groove Ib in Fig.l; and to the grooves lba and lbb 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 Ia outside the groove Ib / the grooves lba and lbb (seen in radial direction) of the intermediate element 1.
• a piston arrangement 3c penetrating (or crossing) the groove Ib 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 lba and lbb, both, have the same kind of piston arrangements as shown in Fig.l.
• Most preferably the substantial main form of the partsl, 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, IR for a shaft 23 going thorough the said holes 2R, 6R, IR 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 Ib / grooves lba, lbb.
• 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 Ib / grooves lba, lbb 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 Ib/ grooves lba, lbb.
• 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 Ib forming the cylinder room.
• the fastening part such as a threaded screw section 3 a 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) Ib; lba, lbb (Fig.l 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 Ib forming the cylinder room having circular overall shape, wherein the centre of the circular radius of said at least one groove Ib. 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 Rl corresponds in a certain axial point of the intermediate element 1 to the position of the outer edge of the groove Ib and the radius of curvature R2 in the corresponding point to the position of the inner edge of said groove 1.
• Rl - R2 SL, where SL is the radial width of the cylinder room in that specific point of observation.
• the length of the groove Ib 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 lba, lbb 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 Ib, 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 Rl corresponds in a certain axial point of the intermediate element 1 to the position of the outer edge of the groove Ib and the radius of curvature R2 in the corresponding point to the position of the inner edge of said groove 1.
• Rl - R2 SL
• SL is the radial width of the cylinder room in that specific point of observation.
• the length of the grooves lba, lbb measured in direction of the periphery of the grooves lba, lbb is at most 175 degrees.
• the inner and/or outer surface of the groove(s) Ib; lba, lbb forming the cylinder room can be axial (a) or divergent from that AB, BA, BB, wherein the cross-section of the piston arrangement 3 c (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 IR 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 25a 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 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 3 c 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) Ib; lba, lbb.
• 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 3 a 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 Ib 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.
• the present invention also relates to a system to unite or connect at least two rotary apparatus units together to accomplish a functional entity.
• Fig. 4 shows an embodiment in which tree rotary apparatus units A, B 3 C of Fig.2a are connected.
• each of the rotary apparatus units A, B, C is coupled 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 IA 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 IB 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 5 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) Ib; lba, lbb 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) Ib; lba, lbb 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.
• 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 lba, lbb are in the successive rotary apparatus units A, B, C situated to partially one upon the other.

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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)

Priority Applications (4)

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Citations (5)

• 2005
  • 2005-10-14 FI FI20051042A patent/FI20051042A0/fi not_active Application Discontinuation
• 2006
  • 2006-10-13 AU AU2006301112A patent/AU2006301112A1/en not_active Abandoned
  • 2006-10-13 CN CN200680046766.7A patent/CN101331326B/zh not_active Expired - Fee Related
  • 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
• 2008
  • 2008-05-13 NO NO20082192A patent/NO20082192L/no not_active Application Discontinuation

Patent Citations (5)

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