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WO1999030005A1 - Machines volumetriques rotatives - Google Patents

Machines volumetriques rotatives Download PDF

Info

Publication number
WO1999030005A1
WO1999030005A1 PCT/GB1998/003580 GB9803580W WO9930005A1 WO 1999030005 A1 WO1999030005 A1 WO 1999030005A1 GB 9803580 W GB9803580 W GB 9803580W WO 9930005 A1 WO9930005 A1 WO 9930005A1
Authority
WO
WIPO (PCT)
Prior art keywords
inlet
machine according
rotary positive
displacement machine
compartments
Prior art date
Application number
PCT/GB1998/003580
Other languages
English (en)
Inventor
Ronald William Driver
Ann Margaret Driver
Original Assignee
Driver Technology Limited
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
Priority claimed from GBGB9725675.4A external-priority patent/GB9725675D0/en
Priority claimed from GBGB9801092.9A external-priority patent/GB9801092D0/en
Application filed by Driver Technology Limited filed Critical Driver Technology Limited
Priority to CA002312741A priority Critical patent/CA2312741A1/fr
Priority to AU17683/99A priority patent/AU1768399A/en
Priority to JP2000524557A priority patent/JP2002505394A/ja
Priority to MXPA00005532A priority patent/MXPA00005532A/es
Priority to EP98962544A priority patent/EP1036253A1/fr
Priority to KR1020007006139A priority patent/KR20010052115A/ko
Publication of WO1999030005A1 publication Critical patent/WO1999030005A1/fr

Links

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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/14—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/38—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member
    • F01C1/39—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member with vanes hinged to the inner as well as to the outer member
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F01C21/183—Arrangements for supercharging the working space

Definitions

  • THIS INVENTION relates to rotary positive-displacement machines.
  • GB-A-1540057 describes a rotary positive-displacement machine having compartments which change volume cyclically as they are rotated. Inlet and outlet of gas to and from the compartments is through axial ports at one end of the machine.
  • a rotary positive-displacement machine has a rotor providing compartments whose volume changes cyclically as the rotor rotates, having gas inlet and outlet ports compartments and positioned so that gas outflow is away from gas inflow.
  • gas at elevated pressure may flow through an inlet port and a different gas may flow in through an angularly spaced port which also acts as an outlet port for a mixture of the gases.
  • an axial inlet port there may be an axial inlet port.
  • the machine may comprise a casing, the rotor comprising inner and outer drums rotatable together in the casing about offset axes, means defining the compartments between the drums, a peripheral wall of the outer drum providing radial inlet ports to the compartments, with end walls providing axial inlet and outlet ports.
  • the means defining the compartments may comprise generally U-shaped blades secured to peripheral walls of the inner and outer drums.
  • the securement may be by hinges.
  • coiled ends of the blades are embedded in flexible material.
  • a closure plate may be slidable peripherally on the casing for reducing the area of a radial outlet port, or slidable rotationally on an end wall for reducing the area of an axial outlet port.
  • the inlet is connected to atmosphere
  • the outlet is connected to the inlet manifold of an internal combustion engine and the rotor is operatively connected to the engine crankshaft.
  • Fig. 1 is a section through a machine
  • Fig. 2 is an end view of Fig. 1 with part removed;
  • Fig. 2a is a view taken on arrow A of Fig. 2.
  • Fig. 3 is a part view of a drum periphery
  • Fig. 4 is similar to Fig. 2 of a modified machine
  • Fig. 5, 5A and 5B show closure plates
  • Fig. 6 shows a flexible blade
  • Fig. 7 shows a modified form of blade.
  • Fig. 8 is a section through another rotary machine
  • Fig. 9 is a perspective view of the machine with part broken away;
  • Figs. 10, 11 show control plates
  • Fig. 12 is an axial view of an end plate
  • Fig. 13 shows a connection device
  • Figs. 14 to 17 show control devices
  • Fig. 18 shows a modified vane
  • Fig. 19 is a section of a further machine
  • a rotary positive-displacement fluid device 10 comprises a fixed casing 1 1 having a peripheral axial wall 12 and an end plate 13.
  • a drum 9 is rotatable in the casing 11 and has a peripheral axial wall 14 and end plates 16, 17.
  • a shaft 18 rotatable on axis 19 extends from wall 16 rotatably though plate 13.
  • a cylindrical part 20 extends from wall 17 and is rotatably received in fixed block 21 from which extends an axial rod 22 defining an axis 23.
  • An inner drum 24 is rotatable on the rod 22 about axis 23.
  • the axis 23 is offset from the axis 19, as seen in Fig. 2.
  • the drum 24 has a peripheral axial wall 25 and end walls 26, 27 operatively close to the inner surf aces of walls 16, 17 respectively.
  • Angularly spaced generally U-shaped or hair-pin shaped flexible blades 30 are located in the space 31 between walls 14 and 25 and the ends of the blades are secured at 42, 43 respectively to these walls.
  • the blades 30 divide the space 31 into angularly adjacent compartments or chambers 32.
  • Pin and slot connections 33 between walls 14 and 27 connect the drums 9 and 24 for rotation together when shaft 18 rotates. If the vanes are strong enough, drive between the drums may be transmitted through the vanes.
  • inlet and outlet of gas, which term includes air, to the chambers 32 is radially rather than axially.
  • the wall 14 may comprise a circumferential series of axial bars 36 with axial spaces 37 between adjacent bars 36 to allow inlet and outlet of gas from the space 31 and chambers 32.
  • the ports in wall 12 can vary depending on the intended use of the machine.
  • a circumferential slot 40 is provided in wall 12 for inlet of hot gas at elevated pressure. This mixes with the air, or air and gas mixture, in the successive chambers 32 as they pass the slot 40 and the gas expands to bottom centre (Fig. 1 ) at which each chamber has the maximum volume. This causes the shaft 18 to rotate.
  • An outlet port is formed by circumferential slot 41 and the gas/air mixture is expelled through the slot 41 by centrifugal action and ambient air is blown in through the slot 41.
  • the air can for example be blown in by a fan 39 driven by an electric motor 38.
  • the radial inlet and outlet ports provide improved scavenging of the compartments; as drawn the ports extend the greater part of the axial extent of the compartments.
  • the angular distance between successive connections 42 may be more or less than or equal to the angular extent of the slot 40.
  • Such a turbine can act as a turbocharger or exhaust turbine for an internal combustion engine in which hot exhaust gas from the engine is admitted at port 40 and the shaft 18 is operatively connected to the engine crankshaft for example by a belt round pulleys on the two shafts.
  • Another use of the machine in association with an internal combustion engine is to locate the machine so that the inlet slot 40 receives atmospheric air at ambient pressure and the outlet slot 41 is connected to deliver the air to the engine inlet manifold, at which the pressure is less than or equal to ambient. Fan 39 is omitted.
  • the pressure difference between ambient and the inlet manifold drives the machine and the shaft 18 is again operatively connected to the engine crankshaft to supply extra energy to the crankshaft and thus to recover some of the energy lost because the engine is producing the reduced pressure at the inlet manifold, so-called throttle loss.
  • Th ⁇ area of inlet slot 40 is increased as the throttle is opened in order to increase the air flow to the inlet manifold.
  • a plate 60A on casing 12 can be connected for sliding movement and operatively connected to the accelerator pedal if the engine is on a vehicle so that at full throttle the plate 60a is moved to increase the area of slot 40.
  • the volume of the chambers 32 at their minimum may be reduced for example by the use of blocks 50, 51 , Fig. 4 (for each chamber) (only some blocks shown) which are respectively secured to the walls 14, 25 or the walls of the blade 30.
  • the blades In the top centre or minimum position the blades may lie along a significant part of the surfaces of the blocks 50, 51.
  • the blocks 50, 51 are shaped to accommodate the change in shape of the blades because of the offset of the axes 19, 23.
  • the machine is used both as a turbine and as a compressor.
  • the machine in association with an internal combustion engine as above, at low or idling engine speed (part throttle) the machine is used as a turbine to recover throttle loss, as above, but at higher speeds, e.g. full or largely open throttle, the machine can act as a supercharger. This may enable the engine to act at a lower compression ratio e.g. 5 to 1 than the more normal 10 to 1.
  • the inlet port 40 is connected to ambient air.
  • the angular extent of outlet slot 41 is reduced at high or full throttle.
  • an arcuate plate 60A can be connected for sliding movement on the casing wall 12 and be operatively connected to the accelerator pedal if the engine is in a vehicle so that at full throttle the plate 60A is moved to increase the size of the slot 40 and increase the air flow to the inlet manifold.
  • the blocks 50, 51 have the effect of avoiding compressed air being discharged into the slot 40.
  • slot 41 is extended as at 41A Fig. 4 but at higher throttle opening the downstream part of the slot 41 is closed off so that compressed air is discharged to the inlet manifold.
  • additional arcuate sliding plates 60B, 60C are arranged alongside plate 60A to slide at higher throttle opening to close off part of slot 41.
  • the fixing points 42, 43 of blades 30 move circumferentially and radially relative to each other by twice the offset of axes 19, 23 and this may introduce high stresses in the blades 30 unless they are thin but if too thin they may not be able to act both in turbine and compressor mode.
  • the blades 30 may be hinged at 42, 43.
  • the ends of blades 30 can be coiled (Fig. 6) and embedded in an integral rubber boss 60 which is mounted on a fixed pin 61 secured at its ends in walls 16, 17.
  • the blades 30 may take a different form and be constructed, for example, from generally non-flexible material with hinges or from a spring steel member, such as is shown in Fig. 7 having straight arms 63 (flexible or non-flexible) and a curved flexible portion 62.
  • a rotary machine 70 Figs. 8 and 9 has cold air and hot gas inlets at one axial end and an outlet for air/gas mixture at the opposite axial end. This improves scavenging because the incoming air assists in expelling the mixture.
  • the machine 70 has an outer cylindrical casing 71 (not shown in Fig. 8) having opposed end plates 71 A, 71 B and providing an enclosure.
  • the inner drum at one end is supported in a static end plate 72 having an inlet port 73 for hot gas at elevated pressure supplied through conduit 74 to an inlet port in the axial end of the outer casing.
  • Cold (ambient) air is blown in (for example by a fan driven by an electric motor or from the engine crankshaft) through conduit 75 leading to an air inlet port in the outer casing and port 76 in the plate 72.
  • the port 76 can have an angular extent as appropriate, for example between sides 77, 78 of plate 72 (Fig. 10).
  • the vanes 30 are operatively sealed in relation to plate 72.
  • the outer drum 9 has an outlet port 79 for air/gas mixture leading to exhaust conduit 80 on the outer casing.
  • a blanking plate 81 (Fig. 11) is mounted between end faces 16, 26 of the drums and provides an outlet port 82.
  • the angular position of the port 82 can be adjusted to control the outflow of the mixture and the expansion of the gas.
  • the vanes 30 are operatively sealed in relation to plate 81.
  • the plate 81 can be linked to shaft 22 for adjustment.
  • the end face 16 of the outer drum 9 is in the form of a spoked aperture (Fig. 12).
  • the force to rotate the inner drum is transmitted to the inner drum from the outer drum through the vanes 30.
  • connection can be provided (Fig. 13) between the inner and outer drums which becomes effective on rapid deceleration.
  • the connection can be a peg, pin or plate device in which pegs 90 on the outer drum engage between pegs 91 on the inner drum but under normal working conditions transmit no drive but move into engagement on sudden slowing of the outer drum.
  • the pegs or pins can be of round or rectangular section.
  • the machine of Fig. 9 can be used as a combined exhaust turbine and supercharger.
  • an outlet 100 is provided from the inlet end of the outer casing for flow of air under pressure to the internal combustion engine so that, say, a piston /cylinder sized to produce a compression ratio of 6 to 1 can operate at a compression ratio of 10 to 1.
  • the usual butterfly valve in the air flow would be provided linked, in the case of a vehicle, to the accelerator pedal. Blocks 50, 51 are omitted.
  • Figs 14 to 17 indicate various positions for control rings 108, 109 which control the flow of compressed air for supercharging and air/gas exhaust mixture.
  • the end plate 72 has an annular ring 108 which can be angularly adjusted in response to movement of the accelerator pedal.
  • Fig. 14 shows the position of a gap 110 in the ring 108 for no supercharging.
  • the angular distance between one end 111 of the gap and the nearest end 112 of the inlet port 76 for air blown in by a fan is less than the angular distance between two adjacent points 42.
  • the volume of chambers 32 is a maximum at position 0 and least at position 180.
  • the ring 108 is moved to the position of Fig. 15 in which the gap 110 and air inlet port 76 are coincident as seen axially.
  • the exhaust mixture control ring 109 in circular disc end plate 81A has an annular gap 113.
  • the pressure of the gas/air mixture at the exit port is desirable for the pressure of the gas/air mixture at the exit port to be ambient.
  • the mixture exit port is just downstream of position 0 (after expansion).
  • the gap 1 13 is upstream of the port.
  • pressure operated pressure relief valves 114 are provided to prevent the pressure in the chambers 30 becoming sub-ambient (and thus retarding the drum) before reaching the port 80 by admitting ambient air.
  • Fig. 17 shows the gap 113 coincident with the port 80 at maximum power.
  • the hot gas inlet can for example be positioned at 210° rather than 180° to avoid the possibility of the mixture remaining above ambient pressure at the outlet and thus not allowing full recovery of the energy in the exhaust.
  • the increase in the volume of the chambers into which the hot gas is supplied assists in this.
  • each valve at any one time communicates with a single chamber 31.
  • air is blown into the machine by a fan, the flow of air expels the spent mixture of air and exhaust gas and is then trapped and compressed as the machine rotates. Some of the air is released from the machine to feed the engine and the remainder is retained. Exhaust gas from the engine enters the retained air which increases the air temperature and pressure. The mixture is expanded until the incoming fan air expels it and the cycle begins again.
  • This design enables one unit to be used without blocks or fillers 50, 51. If used on its own there would not be any throttle loss recovery.
  • the vanes 30 are in two parts 120, 121 hinged by coiling at 122.
  • the thinner part 120 can be disposed to lie on the outer drum surface so that the hinge 122 is not radially in a control region of the space 31 between the inner and outer drums and is radially spaced from the hot gas inlet as seen axially, to reduce wear on the hinge 122.
  • Fig. 19 air is blown in axially at 130, and the hot exhaust gas flows in radially at G and the gas/air mixtures flows out radially at H generally similarly to Fig. 9.
  • the radial outflow of mixture improves scavenging, as above.
  • the rotary machines above could be used in association with an engine arranged to charge the battery of a battery-driven vehicle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une machine volumétrique pouvant être reliée de manière fonctionnelle à un moteur à combustion interne pour fonctionner comme une turbosoufflante ou un surcompresseur. Cette machine comprend un carter extérieur (11) renfermant un rotor, qui comprend des tambours interne et externe (24, 9) tournant ensemble à l'intérieur dudit carter autour d'axes décalés (23, 19), avec des aubes souples (30) espacées angulairement entre deux surfaces opposées des tambours qui servent à définir des compartiments (32) entre les tambours; le volume de ces derniers change de façon cyclique à mesure que le rotor tourne, et ce grâce aux axes décalés. Des trous d'admission et d'évacuation de gaz (40, 73, 76) communiquant avec les compartiments sont placés de manière à permettre aux gaz de s'écouler de façon adéquate à travers les compartiments entre les trous d'admission et d'évacuation, éloignés les uns des autres pour assurer un mélangeage adéquat des gaz et le balayage des compartiments.
PCT/GB1998/003580 1997-12-05 1998-12-03 Machines volumetriques rotatives WO1999030005A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
CA002312741A CA2312741A1 (fr) 1997-12-05 1998-12-03 Machines volumetriques rotatives
AU17683/99A AU1768399A (en) 1997-12-05 1998-12-03 Rotary positive-displacement machines
JP2000524557A JP2002505394A (ja) 1997-12-05 1998-12-03 回転容積形機械
MXPA00005532A MXPA00005532A (es) 1997-12-05 1998-12-03 Maquinas giratorias de desplazamiento positivo.
EP98962544A EP1036253A1 (fr) 1997-12-05 1998-12-03 Machines volumetriques rotatives
KR1020007006139A KR20010052115A (ko) 1997-12-05 1998-12-03 회전식 정-변위 장치

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GBGB9725675.4A GB9725675D0 (en) 1997-12-05 1997-12-05 Rotary positive displacement machines
GB9725675.4 1997-12-05
GBGB9801092.9A GB9801092D0 (en) 1998-01-20 1998-01-20 Rotary positive displacement machines
GB9801092.9 1998-01-20

Publications (1)

Publication Number Publication Date
WO1999030005A1 true WO1999030005A1 (fr) 1999-06-17

Family

ID=26312711

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1998/003580 WO1999030005A1 (fr) 1997-12-05 1998-12-03 Machines volumetriques rotatives

Country Status (7)

Country Link
EP (1) EP1036253A1 (fr)
JP (1) JP2002505394A (fr)
KR (1) KR20010052115A (fr)
CN (1) CN1285893A (fr)
AU (1) AU1768399A (fr)
MX (1) MXPA00005532A (fr)
WO (1) WO1999030005A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001020167A1 (fr) 1999-09-11 2001-03-22 Driver Technology Limited Machine hydraulique rotative volumetrique

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8096288B2 (en) * 2008-10-07 2012-01-17 Eaton Corporation High efficiency supercharger outlet
KR100936129B1 (ko) * 2009-03-02 2010-01-12 정보경 송풍장치를 갖는 사계절용 전기 매트

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE626297A (fr) *
FR389585A (fr) * 1908-04-23 1908-09-12 Hermann Richard Sturm Machine dynamique rotative à combustion
FR1549241A (fr) * 1967-07-28 1968-12-13
US3437079A (en) * 1963-12-17 1969-04-08 Daisaku Odawara Rotary machine of blade type
GB1540057A (en) 1976-04-13 1979-02-07 Driver R Hot gas feed rotary engine
DE3205207A1 (de) * 1982-02-13 1983-09-08 Walter 7033 Herrenberg Neuffer Rotationskolben-brennkraftmaschine mit exzentrisch gelagertem kolben

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE626297A (fr) *
FR389585A (fr) * 1908-04-23 1908-09-12 Hermann Richard Sturm Machine dynamique rotative à combustion
US3437079A (en) * 1963-12-17 1969-04-08 Daisaku Odawara Rotary machine of blade type
FR1549241A (fr) * 1967-07-28 1968-12-13
GB1540057A (en) 1976-04-13 1979-02-07 Driver R Hot gas feed rotary engine
DE3205207A1 (de) * 1982-02-13 1983-09-08 Walter 7033 Herrenberg Neuffer Rotationskolben-brennkraftmaschine mit exzentrisch gelagertem kolben

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001020167A1 (fr) 1999-09-11 2001-03-22 Driver Technology Limited Machine hydraulique rotative volumetrique

Also Published As

Publication number Publication date
EP1036253A1 (fr) 2000-09-20
CN1285893A (zh) 2001-02-28
JP2002505394A (ja) 2002-02-19
KR20010052115A (ko) 2001-06-25
MXPA00005532A (es) 2003-04-25
AU1768399A (en) 1999-06-28

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