WO1993008373A1 - Machine rotative - Google Patents

Machine rotative Download PDF

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Publication number
WO1993008373A1
WO1993008373A1 PCT/AU1992/000578 AU9200578W WO9308373A1 WO 1993008373 A1 WO1993008373 A1 WO 1993008373A1 AU 9200578 W AU9200578 W AU 9200578W WO 9308373 A1 WO9308373 A1 WO 9308373A1
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WO
WIPO (PCT)
Prior art keywords
casing
rotary machine
axis
rotor assembly
piston
Prior art date
Application number
PCT/AU1992/000578
Other languages
English (en)
Inventor
Gosta Ingvald Hook
Kevin Barrett
Original Assignee
Gosta Ingvald Hook
Kevin Barrett
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gosta Ingvald Hook, Kevin Barrett filed Critical Gosta Ingvald Hook
Publication of WO1993008373A1 publication Critical patent/WO1993008373A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/06—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B27/0606—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders
    • F04B27/0612—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders rotary cylinder block
    • F04B27/0619—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders rotary cylinder block cylinder block and actuating cam rotating together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
    • F01B2009/045—Planetary gearings

Definitions

  • THIS INVENTION relates to a rotary machine having radial pistons.
  • the invention resides in a rotary machine comprising a shaft defining a first axis of rotation and a second axis of rotation offset with respect to the first axis, a casing, the casing and the shaft being rotatable relate to each other about the first axis, and a rotor assembly, the rotor assembly and the shaft being rotatable relative to each other about the second axis, the rotor assembly comprising a cylinder disposed generally radially with respect to the second axis and a piston mounted for reciprocation in the cylinder, the piston being coupled to the casing whereby the piston is caused to reciprocate within the cylinder upon relative rotation between the shaft and the casing, and a control means for controlling movement of the rotor assembly relative to the casing.
  • the machine may operate as a pump or compressor in which case rotational torque applied to the casing causes reciprocation of the piston within the cylinder thereby doing work on a fluid introduced into a working chamber defined between the piston and the cylinder.
  • the machine may operate as a motor in which case an expanding fluid acting on the piston causes relative rotation between the casing and the shaft.
  • the control means comprises a plurality of eccentric connections between the casing and the rotor assembly. The eccentric connections accommodate relative movement between the rotor assembly and the casing arising from the eccentricity between the first axis of rotation about which the casing and the shaft rotate relative to each other and the second axis of rotation about which the rotor assembly and the shaft rotate relative to each other.
  • the eccentric connections may each comprise a crank pin having a first pin section which defines a first axis and a second pin section which defines a .second axis eccentric to the first axis, the first pin section being rotatably mounted on an end wall of the casing and the second pin section being rotatably mounted onto the rotor assembly.
  • each eccentric connection may comprise a roller mounted on the rotor assembly and received within a circular recess formed within an end wall of the casing, the circular recess defining a circular path around which the roller can travel.
  • the roller may be mounted on an end wall of the casing and the circular recess may be provided on the rotor assembly.
  • the piston is preferably coupled to the casing by way of a connecting rod one end of which is pivotally connected to the piston and the other end of which is pivotally connected to the casing.
  • the rotor assembly may comprise a control plate onto which said eccentric connections are mounted.
  • the rotor assembly comprises three cylinders each having a respective piston.
  • the casing comprises a cylindrical side wall co-axial with said first axis and two side walls at the ends of the cylindrical side wall.
  • the casing is adapted to contain a fluid such as oil for the purposes of lubrication and cooling of the rotary machine.
  • the cooling is achieved by oil splashing onto the various parts of the machine as they rotate about the shaft, so extracting heat therefrom.
  • Each cylinder is preferably provided with cooling fins to assist in this regard.
  • each piston and cylinder defines a working chamber the volume of which varies according to reciprocation of the piston within the cylinder.
  • Means are provided for intaking a fluid into each working chamber and exhausting a fluid from the working chamber.
  • the fluid exhausted from each working chamber is the same as the fluid introduced into the working chamber other than it has had work performed on it.
  • the fluid introduced into each working chamber may comprise an air-fuel mixture and the fluid exhausted from the working chamber may comprise the products or combustion.
  • the intake and exhaust means may comprise an intake port provided within the shaft and communicating with an intake passage formed within the shaft.
  • the intake and exhaust means may comprise a discharge port communicating with a discharge passage also formed in the shaft in isolation from the intake passage.
  • the intake passage extends from one end of the shaft and the discharge passage extends to the other end of the shaft.
  • the machine is provided with an oil scavaging system for removing excess oil which may enter the casing as a result of, for example, leakage from the working chambers.
  • the scavaging system may comprise an oil scavaging disc rigidly mounted on the shaft within the casing.
  • the disc is preferably provided with at least one oil passage extending between the outer periphery of the disc and the inner periphery thereof for communication with the intake passage formed within the shaft.
  • the oil passage is preferably inclined at its outer end to face oncoming oil rotating within the casing.
  • the invention resides in a rotary machine comprising a first axis of rotation and a second axis of rotation offset with respect to the first axis, a casing mounted for rotation about the first axis, and a rotor assembly mounted for rotation about the second axis, the rotor assembly comprising a cylinder disposed generally radially with respect to the second axis and a piston mounted for reciprocation in the cylinder, the piston being coupled to the casing whereby the piston is caused to reciprocate within the cylinder upon rotation of the casing, and a control means for controlling movement of the rotor assembly relative to the casing.
  • the invention resides in apparatus for supplying compressed air, said apparatus including a rotary machine as set forth hereinbefore.
  • said apparatus further comprises an accumulator for receiving compressed air from the rotary machine, the accumulator having provision for separating oil from the compressed air delivered to it.
  • the accumulator comprises a cylindrical side wall and an internal wall positioned within the side wall so as to define an annular space therebetween into which compressed air from the rotary machine is delivered, the internal wall defining an outlet passage the bottom of which opens into the lower region of the accumulator and the top of which communicates with an outlet line.
  • oil trapped within the accumulator is recirculated to the rotary machine for lubrication purposes.
  • This may be done by way of an oil return line which has an inlet located at or in close proximity to the bottom of the accumulator so that it is immersed in oil accumulated therein and having an outlet communicating with the intake passage formed within the shaft.
  • oil may be forced along the oil return line to the intake passage under the influence of fluid pressure within the accumulator.
  • Fig. 1 is a perspective view of a rotary machine according to the first embodiment, with part of the machine casing removed to reveal some of the internal workings of the machine;
  • Fig. 2 is a front elevational view of the rotary machine in the condition shown in Fig. 1;
  • Fig. 3 is a cross-sectional view of the machine
  • Figs. 4, 5 and 6 reveal the internal workings of the machine in operation
  • Fig. 7 is a front elevational view showing the internal workings of the machine with one cylinder operating in an intake cycle
  • Fig. 8 is a view similar to Fig. 7 with the exception that the cylinder is shown at the completion of the intake cycle;
  • Fig. 9 is also a view similar to Fig. 7 with the exception that the cylinder is shown operating in a discharge cycle;
  • Fig. 10 is a perspective view of the shaft of the rotary machine
  • Fig. 11 is a schematic sectional view showing the rotary machine incorporated into an apparatus for supplying compressed air on demand;
  • Fig. 12 is a sectional view of an oil control valve employed in the apparatus of Fig. 11;
  • Fig. 13 is a sectional view of an air intake control valve employed in the apparatus of Fig. 11;
  • Fig. 14 is a cross-sectional view of an eccentric connection forming part of a rotary machine according to a second embodiment.
  • Fig. 15 is an elevational view of the eccentric connection of Fig. 14.
  • the first embodiment which is shown in Figs. 1 to 13, is directed to a rotary machine 11 which operates as an air compressor.
  • the rotary machine is incorporated into an apparatus 13 (as shown in Fig. 11) for supplying compressed air on demand to a device operated by air such as a shearing hand-piece (also not shown).
  • the rotary machine 11 comprises a shaft 15 supported adjacent its ends on stands 17.
  • the shaft 15 includes a first section 19 which defines a first axis of rotation 20, a second section 21 which defines a second axis of rotation 22, and a third section 23 which is coincident with the first section.
  • the shaft 15 has an air intake passage 25 extending inwardly from an opening 27 in the end face of the shaft to an intake port 31 provided in the second section 21.
  • the intake port 31 extends radially of the shaft from the intake passage 25 to the periphery of the shaft and diverges radially in the outward direction, as best seen in Fig. 10 of the drawings.
  • the shaft is also provided with an air discharge passage 33 which extends from a discharge port 35 provided within the second portion 21 of the shaft to an outlet opening 37 in the other end face of the shaft.
  • the discharge port 35 extends between the air discharge passage 33 and the periphery of the second portion of the shaft and also diverges in the outward direction, as best seen in Fig. 10.
  • the inlet port 31 and the outlet port 35 are axially spaced along the second section 21 of the shaft.
  • a casing 41 is mounted on the first and third sections the shaft 15 for rotation about the first axis 20.
  • the casing 41 is defined by a cylindrical side wall 43 and two end walls 45, 47 at the ends of the cylindrical side wall.
  • the end wall 45 is integral with the cylindrical side wall 43 and the end wall 47 is selectively removable to provide access to the interior of the casing.
  • Cooling fins are provided on the exterior surface of the cylindrical side wall 43.
  • the second portion 21 of the shaft 15 is accommodated within the casing and rotatably supports a rotor assembly 50 for rotation about the second axis 22.
  • the rotor assembly comprises a rotor 51 and a plurality of cylinders 53 (there being three in this embodiment) securely mounted on the rotor.
  • the cylinders 53 are disposed radially with respect to .the second axis 22 about which they rotate in unison with the rotor.
  • the exterior of each cylinder is provided with cooling fins 55.
  • Each cylinder 53 extends into the rotor 51 and has a cylinder port 57 at its inner end which opens onto the inner face of the rotor and which can communicate sequentially with the intake and delivery ports 31 and 35 respectively formed in the shaft.
  • a piston 61 is mounted for reciprocation within each cylinder 53.
  • Each piston in association with its respective cylinder defines a working chamber 63 which varies in volume according to reciprocation of the piston within the cylinder.
  • the pistons are each connected to the casing 41 by a connecting rod 65 one end of which is pivotally connected to the respective piston at 67 and the other end of which is pivotally connected to the casing at 69.
  • a drive means (not shown) is provided for rotating the casing.
  • the drive means may comprise an electric motor drivingly coupled to the casing in any suitable means such as a belt and pulley arrangement.
  • a control means 71 for controlling movement of the rotor assembly relative to the casing.
  • the control means 71 comprises a plurality of eccentric connections 73 between the casing and the rotor assembly.
  • the eccentric connections 73 accommodate relative movement between the rotor assembly and the casing arising from the eccentricity between the first axis of rotation 20 about which the casing rotates and the second axis of rotation 22 about which the rotor assembly rotates.
  • the eccentric connections function to control the movement of the rotor assembly relative to the casing.
  • each eccentric connections 73 comprises a crank pin 75 having a first pin section 77 which defines a first axis and a second pin section 79 which defines a second axis eccentric to the first axis.
  • the first pin section 77 is rotatably mounted on the end wall 45 of the casing.
  • the first pin section 77 is rotatably supported within a bearing 81 which is accommodated within a recessed bearing housing 83 formed in the end wall 45 of the casing.
  • the second pin section 79 is rotatably mounted on a control plate 85 which is rigidly mounted on the rotor 51 thereby to form part of the rotor assembly.
  • the control plate 85 extends beyond the rotor and is provided with a bearing housing 87 which accommodates a bearing for rotatably supporting the second pin section 79.
  • the eccentric connections 73 establish a rotational link between the rotor assembly and the casing and serve to control relative movement there between on rotation of the casing about its axis of rotation 20 and rotation of the rotor assembly about its axis of rotation 22.
  • This relationship can be seen in Figs. 4, 5 and 6 of the drawings from which it will be noted that the relationship between the first pin section 77 and the second pin section 79 of each eccentric connection 73 remains constant as the casing rotates about the first axis and the rotor assembly rotates about the second axis 22. This relationship is such that the first pin section remains vertically above the second pin section during rotation, as can be seen in the drawings.
  • the eccentricity between the first axis 20 and the second axis 22 causes the pistons 61 to reciprocate within their cylinders 53.
  • This causes the working chambers 63 to undergo expansion and compression strokes, as illustrated in Figs. 7, 8 and 9 of the drawings where a working chamber can be seen to move between an expansion stroke and a compression stroke as it rotates about the second axis 22.
  • each working chamber 63 rotates about the second axis 22 defined by the second section 21 of the shaft 15, the cylinder port 57 at inner end of the cylinder communicates sequentially with the intake port 31 and the discharge port 35.
  • the timing of rotation is such that each working chamber 63 communicates with the intake port 31 during an expansion stroke of the chamber (as shown in Fig. 7) and communicates with the discharge port 35 during a compression stroke of the working chamber (as shown in Fig. 9 of the drawings).
  • each working chamber can receive a charge of air (with oil entrained therein as will be explained later) via the air intake passage 25 and intake port 31 within the shaft during the intake stroke.
  • the timing is such that the working chamber commences a compression stroke to compress the air contained therein.
  • the working chamber is in the position shown in Fig. 8 of the drawings where it communicates with neither the intake port 31 nor the discharge port 35.
  • the working chamber continues to rotate air contained therein is further compressed until such time as the cylinder port 57 is exposed to the discharge port 35 whereupon the air under pressure within the working chamber discharges through the discharge port 35 and into the discharge passage 33 for further processing, as will be explained later.
  • a fluid such as oil is contained within the casing 41 for the purposes of lubrication and cooling of the rotary machine.
  • the cooling is achieved by oil splashing onto the pistons, cylinders and related parts as they rotate about the shaft, so extracting heat therefrom.
  • the heat extracted by the oil is dissipated through the casing 41 to the surrounding air. This heat dissipation is assisted by the exterior cooling fins (not shown) on the cylindrical side wall 43 of the casing.
  • the splashing oil serves a lubrication function which is supplemented by a lubrication system 91 which introduces oil into the intake air.
  • the oil is introduced into the intake air as it flows along air intake passage 25 and is subsequently removed form the air after compression.
  • An oil scavenging system 92 is provided for removing excess oil which may enter the casing 43 as a result of leakage from the working chambers.
  • the scavenging system 92 comprises an oil scavenging disc 93 rigidly mounted on the first portion 19 of the shaft within the casing. Because the disc 93 is rigidly mounted on the shaft, it does not rotate with the casing and the rotor assembly.
  • the oil contained within the casing rotates with the casing owing to friction between the oil and the casing, and under the influence of centrifugal forces forms in a rotating annular body against the cylindrical wall of the casing.
  • the depth of the rotation body of oil is controlled by the scavenging disc.
  • the disc 93 is provided with a plurality of circumferentially spaced oil passages 95 which extend between the outer periphery of the disc and a circumferential recess 97 at the inner periphery of the disc.
  • the recess 97 co-operates with a complementary recess in the periphery of the shaft to define a circumferential oil passage 99 into which oil can flow via the oil passages 95.
  • the oil passages 95 are inclined at their outer ends to face oncoming oil rotating with the casing. Because the outer ends of the oil passages 93 face the oncoming oil rotating with the casing, excess oil is scooped into the passages 93 and forced there along to the circumferential passage 99.
  • a radial oil passage 101 in the shaft extends between the circumferential passage 99 and the air intake passage 25 such that oil can be delivered into incoming air flowing the working chambers 63.
  • the oil delivered into the air is removed from the air at a subsequent stage, as will be explained later.
  • the rotary machine forms part of apparatus 13 shown in Fig. 11 of the drawings.
  • the apparatus 13 includes an accumulator 111 which receives compressed air from the rotary machine 11.
  • the accumulator 111 also has provision for separating oil from the compressed air which is delivered into it from the rotary machine.
  • the accumulator 111 comprises a cylindrical side wall 112 and an internal cylindrical wall 113 positioned within the side wall 112 so as to define an annular space 115 there between.
  • the internal cylindrical wall 113 is supported from the top wall 117 of the accumulator and terminates above the bottom wall 119 of the accumulator.
  • the internal cylindrical wall 113 defines an outlet passage 114 the bottom of which opens onto the lower region of the accumulator and the top of which communicates with an outlet line 120.
  • a fluid line 121 couples the outlet end of the outlet passage 33 of the rotary machine with the accumulator 111.
  • the fluid line 121 opens into the annular passage 115 at a location near the top thereof.
  • the outlet end of the fluid line 121 is so arranged that air with oil entrained therein entering the annular space 115 via the line 121 has a generally tangential path with respect to the annular space 115 such that a spiralling flow is generated as the air travels downwardly towards the bottom of the accumulator from where it can flow upwardly through the central outlet passage 114 defined by the cylindrical wall 113 to the outlet line 120.
  • the air with oil entrained therein spirals downwardly through the annular space 115, the one component is separated from the air and accumulates on the inner face of the outer wall 111 from where it runs downwardly and collects in the bottom of the accumulator.
  • a sight gauge 125 is provided to offer a visual indication of the level of oil within the accumulator.
  • a check valve 126 is incorporated in the fluid line 121 to close the fluid line against return flow [and hence loss of air pressure in the accumulator (11)] when the rotary machine has stopped rotating.
  • Oil within the accumulator is recirculated for lubrication of the rotary machine. This is done by way of the lubrication system 91 which is provided with an oil return line 127 which has an inlet 129 spaced close to the bottom of the accumulator so that it is immersed in oil accumulated therein.
  • the oil return line terminates at a oil entry port 131 which opens into the air intake passage 25. Oil is forced along the oil return line 127 to the air intake passage 25 because of fluid pressure within the accumulator.
  • an oil control valve 133 is provided to prevent such a situation.
  • the oil control valve is shown in Fig.
  • a piston 141 is slidably mounted within the body, the piston having a first piston head 143 disposed in the control chamber 137 and a second piston head 145 disposed in the operating chamber 139.
  • the first piston head 143 co-operates with a seat 147 to selectively block the return line 127 against oil flow.
  • a biassing means such as a spring 147 acts between the second piston head 145 and a wall of the chamber 139 so as to bias the piston into a position in which the first piston head 143 is in sealing engagement with the seat 147.
  • a fluid pressure line 151 extends between the fluid line 121 (at a location upstream of the check valve 126) and the chamber 139 in the oil control valve 133 so as to expose the second piston 145 to fluid pressure on the side thereof opposite the biassing means 147. With this arrangement, fluid pressure in the fluid line 121 is transferred to the chamber 139 by the line 151.
  • a particular useful feature of the apparatus shown in Fig. 11 is that the rotary machine can be allowed to free wheel when there is sufficient accumulated air in the accumulator 111. This avoids the need for the rotary machine to be continually started and stopped according to the amount of accumulated air, as is the case with conventional air compressor systems.
  • control valve (as shown in Fig. 13) provided at the inlet end of the air passage 25.
  • the control valve comprises a body 151 having a control chamber 153 and an operating chamber 155.
  • the control chamber 153 communicates with the air passage 25 by way of an elbow pipe section 157.
  • a valve seat 159 is defined at the entry end of the elbow section 157.
  • the body 151 is provided with a pair of ports 161 through which air can enter the control chamber 153.
  • the chamber 155 communicates with the accumulator 111 by way of fluid line 163 which opens into the upper end of the chamber.
  • a piston assembly 165 is mounted within the body 151.
  • the piston assembly 165 has a first piston head 167 which is adapted to co-operate with the valve seat 159 and a second piston head 169 which divides the chamber 155 into a first sub-chamber 171 and a second sub-chamber 172.
  • the fluid line 163 opens into the first sub-chamber 171 and a resilient means such as a compression spring 175 is positioned within the second sub-chamber 172 to act between the second piston head and a wall of the sub-chamber.
  • the spring serves to bias the piston into a position in which the first piston head 167 is out of engagement with the valve seat 159.
  • the lubrication system 91 continues to deliver oil via port 131 for lubrication purposes.
  • the air pressure within the accumulator will eventually drop as a result of use of an air operated device (such as a shearing hand-piece) coupled to the outlet line 120 of the accumulator and when the drop is sufficient to allow the spring 175 to overcome the fluid pressure in the first sub- chamber 171, the spring will move the piston away from the valve seat 159 and so move the first piston head 167 out of engagement with the valve seat. This allows air to again enter the valve body 151 through the ports 161 and so compression of air can recommence.
  • an air operated device such as a shearing hand-piece
  • each eccentric connection 73 comprises a roller 161 mounted on the control plate 85.
  • the roller 161 is received within a circular recess 163 formed within the end wall 45 of the casing.
  • the circular recess 163 defines a circular path 165 along which the roller can travel.
  • the circular recess 163 has a central axis 164 which is equivalent to the axis of the first section of the eccentric pin of the first embodiment and the roller has an axis of rotation 169 which is equivalent to axis of the second section of the crank pin.
  • Planetary movement of the axis 169 of the roller about the axis 164 of the circular recess 163 provides motion equivalent to that of the crank pin of the first embodiment. This then allows the eccentric connections to control motion of the rotor assembly relative to the casing upon rotation of the rotor assembly and the casing about their respective axis 22 and 20.

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

Abstract

Machine rotative destinée principalement à être utilisée comme compresseur d'air, comprenant un arbre (15) définissant un premier axe de rotation (20), et un deuxième axe de rotation (22) qui est décalé par rapport au premier axe (20). Un carter (41) est monté sur l'arbre (15) de manière à tourner autour du premier axe (20). Un ensemble de rotor (50) est monté sur l'arbre (15) de manière à tourner autour du deuxième axe (22). L'ensemble de rotor (50) comprend une pluralité de cylindres disposés radialement et un piston (61) monté de manière à effectuer un mouvement de va-et-vient dans chaque cylindre. Chaque piston (61) est couplé au carter (41) et par conséquent la rotation du carter (41) provoque le mouvement alternatif du piston (61) dans le cylindre. Un système de régulation (71) prévu pour réguler le mouvement relatif entre l'ensemble de rotor (5) et le carter (41) provoquée par l'excentricité existant entre les axes (20, 22), comprend plusieurs connexions (73) excentriques situées entre le carter (41) et l'ensemble de (50).
PCT/AU1992/000578 1991-10-25 1992-10-26 Machine rotative WO1993008373A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AUPK9143 1991-10-25
AUPK914391 1991-10-25

Publications (1)

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WO1993008373A1 true WO1993008373A1 (fr) 1993-04-29

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998023861A1 (fr) * 1996-11-26 1998-06-04 Lin Yng Lang Compresseur de gaz
WO2008153508A2 (fr) * 2007-06-12 2008-12-18 Nazif Oren Système d'entraînement formant un couple par l'intermédiaire du décalage d'un axe
CN111441865A (zh) * 2020-04-03 2020-07-24 贺坤山 旋转活塞燃气轮发动机

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU191355A1 (fr) *
GB237323A (en) * 1924-03-28 1925-07-28 Henry Selby Hele Shaw Improvements in rotary air compressors
US1901265A (en) * 1928-07-07 1933-03-14 Schneider Heinrich Transmission
GB570119A (en) * 1943-08-03 1945-06-22 William Warren Triggs Improvements in or relating to hydraulic devices for the transmission of power
US2452541A (en) * 1945-09-27 1948-11-02 Elek K Benedek Rotary hydraulic machine
GB650552A (en) * 1942-07-23 1951-02-28 Schweizerische Lokomotiv Improved liquid-pump of fixed stroke, for hydraulic power transmission purposes
US3148627A (en) * 1961-04-28 1964-09-15 Schweizerische Lokomotiv Reciprocating pump
EP0046463A1 (fr) * 1980-08-27 1982-03-03 Julio Alister Moteur à combustion interne sans vilebrequin avec deux éléments rotatifs accouplés et décalés parallèlement

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU191355A1 (fr) *
GB237323A (en) * 1924-03-28 1925-07-28 Henry Selby Hele Shaw Improvements in rotary air compressors
US1901265A (en) * 1928-07-07 1933-03-14 Schneider Heinrich Transmission
GB650552A (en) * 1942-07-23 1951-02-28 Schweizerische Lokomotiv Improved liquid-pump of fixed stroke, for hydraulic power transmission purposes
GB570119A (en) * 1943-08-03 1945-06-22 William Warren Triggs Improvements in or relating to hydraulic devices for the transmission of power
US2452541A (en) * 1945-09-27 1948-11-02 Elek K Benedek Rotary hydraulic machine
US3148627A (en) * 1961-04-28 1964-09-15 Schweizerische Lokomotiv Reciprocating pump
EP0046463A1 (fr) * 1980-08-27 1982-03-03 Julio Alister Moteur à combustion interne sans vilebrequin avec deux éléments rotatifs accouplés et décalés parallèlement

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
DERWENT ABSTRACT, Accession No. C5528 E/10, Class Q51, Q52; & EP,A,46 463 (ALISTER), 3 March 1982. *
DERWENT SOVIET INVENTIONS ILLUSTRATED, Section III, Mechanical & General, issued September 1967, Engines, Pumps, Boilers, Refrigerators, p. 12; & SU,A,191 355 (ERSHOV), July 1967. *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998023861A1 (fr) * 1996-11-26 1998-06-04 Lin Yng Lang Compresseur de gaz
WO2008153508A2 (fr) * 2007-06-12 2008-12-18 Nazif Oren Système d'entraînement formant un couple par l'intermédiaire du décalage d'un axe
WO2008153508A3 (fr) * 2007-06-12 2009-02-05 Nazif Oren Système d'entraînement formant un couple par l'intermédiaire du décalage d'un axe
CN111441865A (zh) * 2020-04-03 2020-07-24 贺坤山 旋转活塞燃气轮发动机

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