US3854849A - Distribution of valve-gear systems for rotary machines - Google Patents

Distribution of valve-gear systems for rotary machines Download PDF

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Publication number
US3854849A
US3854849A US00328599A US32859973A US3854849A US 3854849 A US3854849 A US 3854849A US 00328599 A US00328599 A US 00328599A US 32859973 A US32859973 A US 32859973A US 3854849 A US3854849 A US 3854849A
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US
United States
Prior art keywords
crown
wheel
rotor
rotary machine
stator
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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.)
Expired - Lifetime
Application number
US00328599A
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English (en)
Inventor
M Brille
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Renault SAS
Regie Nationale des Usines Renault
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Renault SAS
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Publication date
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Publication of US3854849A publication Critical patent/US3854849A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • 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
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/104—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]

Definitions

  • the invention concerns a distribution system for a rotary machine of the type having a rotor with an epicycloidal profilecomprising N lobes and disposed eccentrically inside a stator having N l lobes, each lobe of the stator forming with the rotor a working chamber having a variable volume.
  • the distributor disc is driven in a circular movement of translation by a combination of two eccentric
  • the invention is applicable to rotating compressors
  • these rotary machines comprise quite naturally by their construction, contrary to piston machines, a number N l of working chambers which is fairly large, which gives them greater uniformity of working, but which necessitates a larger number of clapper valves.
  • These clapper valves generally arranged in a ring and which must be capable ofbeing dismantled for inspection or replacement, have with their manifolds a relative bulk which is excessive and which substantially reduces the advantage of 'small overall size of these rotary machines.
  • these clapper-valves considerably restrict the surface area of the casing which can be used for cooling highly desirable for the compressor.
  • the object of the present invention is a distributor which fulfills the same purpose as that described above, which to that end remains synchronized with the shaft, but in which the movement is a circular translation of low linear speed, utilizing the particular kinematics of the rotary machine in question.
  • the drive of the rotor is obtained from a gear having KN teeth where-K is a whole number, fixed on this rotor and engaging with a fixed crown-wheel having K (N l) teeth, rigidly fixed to the stator.
  • the distribution is effected by a distributor disc held against a friction face, mounted freely for rotation on an eccentric crank-pin of the central rotatingshaft of the machine and comprising a toothed crown-wheel fixed onthe said distributor, centered on the axis of the said eccentric crankpin and identical with the fixed crown-wheel of the stator, and driven by a pinion identical with the driving pinion of the rotor, also centered on the said rotor and rigidly fixed thereto, the i said distributor being displaced by the action of rotation of the central shaft at the same angular .speedfor all the points of its surface in a single circular movement of translation.
  • the gear of- KN teeth on the rotor is brought into engagement with a second crown-wheel of the same diameter as the first, having K (N l) teeth. If -the centre of. this second crown-wheel is held on the axis of the machine, it will remain stationary like the first, but if the centre of this second crown-wheel is displaced with respect to this axis, with the condition of maintenance of engagement, it will rotate with the shaft at the angular speed at and all the points of the crownwheel will describe the same small circles at the angular speed (0, and at a linear speed which becomes lower as the displacement of the centre becomes less.
  • the movement of the second crown-wheel will be a circular translation.
  • the distributor is the holding plate of this second crown-wheel. lt is itself maintained on its centre by an eccentric mounted on the main shaft and'having as'its eccentricity the above-mentioned displacement, it will have the same movement of circular translation as the crown-wheel.
  • Thisdistributor has N-l- 1 pairs of orifices, one for the intake of the gas and the other for its outlet, each pair being located in front of the outlet opening of the channel which communicates with each working chamber.
  • a second characteristic feature of the invention is the sliding swivel mounting of the working part of the distributor plate on the crown-wheel holding plate in accordance with a third characteristic feature of the invention.
  • the admission and exhaust manifolds are arranged in a circular manner in order that the-distributor may be automatically applied against its slide-fac'e by a chosen value of pressure of the gas compressed by the machine or of the driving gas.
  • This construction could be compared with the operation of a slide-valve of a steam engine, which valve has an alternating rectilinear movement which could be considered as a projection I of the circular movement of the present distributor, this movement permitting a single member to ensure the distribution for the N 1 working chambers of the machine.
  • a fourth characteristic feature of the invention is the coating of the slide-face with a non-metallic material having a very low coefficient of friction, for example a combination of Teflon and graphite. This eliminates the necessity of lubrication for the distributor. It should be noted that the use of such materials is permissible, since the temperature of the gases is always lower than 200C. 7
  • FIG. 1 is a diagrammatic representation in exploded perspective view of the kinematics of the operation of the distributor
  • FIG. 2 shows a view in longitudinal section of the whole of a compressor comprising a rotor with three lobes, namely N 3, following a preferred example of embodiment of the invention
  • FIG. 3 shows a front view in the direction of the arrow F of FIG. '2, of the corresponding distributor wheel, showing the profile of the distributionorifices.
  • the pinion f On the axis 00 of the rotor is keyed the pinion f having a pitch-circle radius equal to SE.
  • This pinion engages with the crown-wheel g having a pitch-circle radius of 4E fitted on the stator. It is known that the rotation ofthe shaft a -,-a at the speed to causes rotation of According to the invention, the axis 00 is extended to O and the pinion f is extended up to f,, the pitch circle of the pinion f, having thus the same radius 3E as the pitch circle ofthe pinion f and the same setting; it
  • La second crown-hweel 3 having the same pitchcircle radius g, that is to say.4E without first defining the position of its centre 1.
  • Its eccentricity OJ is equal to E, like 0 a, and 0 namely:
  • the plane j has a circular movement of translation.
  • the circle g is fixed as is also the circle g and its extension.
  • the plane j is stationary if a then 11' 2E and the amplitude of the circular translation is a maximum, as is also its linear speed.
  • a may be chosen in such manner that the linear speed of the plane is a minimum, while retaining however sufficient amplitude of movement to ensure correctly the action of distribution which is referred to below.
  • the plane j will be divided into four equal sectors, each of which will possess two orifices k and m communicating respectively and continuously with the inlet and outlet of the fluid at the front of the plane and successively covering and uncovering the orifice q of the conduit n of the working chamber corresponding to the sector of the plane considered.
  • the compressor is constituted by its stator 1 which carries the profile having the reference C on FIG. 1, by its rotor 2 which carries the profile reference d in FIG. 1, and by the side plates 3 and 4.
  • the central shaft 5 having its axis a -a is mounted on roller bearings 6 and 7 housed in the side-plate 3 and the casing 22. it carries the eccentric crank-pin 40 having its axis'at 0 -0 about which pivots the rotor 2 by its sleeve bearing 10. At its two extremities, the shaft 5 carries counterweights to balance the eccentric mass of the rotor. One ofthese weights is carried by the driving pulley 8 while the other has the reference 9.
  • the pinion 11 (referenced at fin FIG. 1) having a radius 3E is mounted fixed on the rotor '2 on the bearing 10.
  • the pinion 1 l engages on one side with the toothed crown-wheel 12 having a radius 4E (referenced g in FIG. 1) rigid with the side plate 4, andaccordingly fixed, and on the other sidewith the crown-wheel 13 having a radius 4E (referenced g in FIG. 1) fixed on the hub 14 of the distributor end-plate, which rotates on its sleeve-bearing 17 on the eccentric crank-pin 18 (having the axis'l 1 in FIG. 1).of the shaft 5.
  • the movement of the hub 14 is a circular translation movement; all the points of 14 describe circles having I a radius 1,, a
  • theexternal crownwheel 15 On the hub .14 is slidably keyed theexternal crownwheel 15 with a key 19 which also permits a slight swivel movement of this crown-wheel on the outer spherical face 20 of the hub 14.
  • This outer crownwheel 15 constitutes the distributor proper. Its mount- [4, namely a circular translation.
  • Bolts 26 clamp together in a single block the stack of v parts 21, 3, 1, 4 and 22 ensuring an easy and rapid dismantling of the assembly and good accessibility to all the parts.
  • the pulley 8 drives in rotation the shaft 5, the eccentric and the gear of which 11-12 drive the rotor 2 in its conjoint bearing in the stator 1.
  • the air or fluid to be compressed is successively drawn-in, compressed and evacuated from each chamber 27 of the stator through a single opening 28 formed in the side-plate 4 and the plate or friction slide-face 16.
  • FIG. 2 shows the chamber 27 at its maximum volume, the crown-wheel having just closed the-communication of the opening28 with an admission port 29 (FIG. 3) previously in the compression-delivery phase.
  • the diametrically-opposite chamber, the lobe of which is completely filled by that of the piston, has just completed its delivery phase, and the delivery port 30 moves away and is replaced by the adjacent admission port 29.
  • the other two chambers set perpendicularly and not being shown in FIG. 2, are set symmetrically,
  • the communication of the suction port 29 with the circular manifold 23 is effected through a circular channel 31 and grooves 32 formed in the interface of the crown-wheel l5 and the hub 14.
  • the communication of the exhaust port 30 with the circular delivery manifold is effected by a circular peripheral groove 33 in the crown-wheel 15.
  • the opening and closure of the ports 29 and is I contact permits, in certain applications, the slide-face 16 to be made of synthetic material with good friction properties, such as Teflon, and also the various lateral joints 34 of the rotor and the circular joints 35 of the crown-wheel 15, making it possible to eliminate any lubrication of these zones and any contamination of the compressed fluid.
  • the circular translation movement similar to a surface-finishing operation, tends to wipeout any accidental scratches in the slide-face 16 due to solid impurities, and thus to maintain good fluid-tightness.
  • Thisfluid-tightness is also ensured by the maintenance of the crown-wheel 15 under pressure against the slide-face 16, by a clapper-valve effect.
  • the simple pressure on the crown-wheel 15 of the joint 35 opposite to the slide-face 16 is sufficient to ensureits forcible application, subsequently effected by the delivery pressure.
  • the balancing of this pressure in order to reduce the friction losses can be regulated by the dimensioning of the pressure surface areas.
  • a non-return valve 42 is provided on the outlet circuit and a calibrated valve 40 is placed on the outlet 36 of the connection to free air of the rotorstator joints.
  • the shape of the delivery port 30 is chosen in such tor, this same orifice 30 is defined in such manner as to I ensure the chosen rate of expansion.
  • the single conduit 28 may be replaced by two conduits, one for the entry of fluid and the other for its outlet, and these con- I said rotor (K rotor by a first eccentric crank pin on which saidrotor is rotatable, v j 1 said rotor being driven in rotation by said'pinion, said pinion being concentric with an eccentric bearing and engaging said crown wheel, said stator having the same axis as therotatable shaft,
  • admission and evacuation ports communicate with at least one chamber of said stator through at least one opening in 'said side plate.
  • admission circuit is constituted by an annular manifold which-is closed on said distributor disc at the level of the hub to crown crown-wheel interface, said interface being provided with a plurality of grooves for communication with the opposite face of said disc.
  • a calibrated valve is mounted on the outlet of a circuit connecting rear cavities of rotor-stator sealing straps to free air,and a non-return valve mounted on said evacuation circuit, to ensure the operation of said machine, working as a compressor on no-load and at the ceiling pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
  • Rotary Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)
US00328599A 1972-02-08 1973-02-01 Distribution of valve-gear systems for rotary machines Expired - Lifetime US3854849A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7204093A FR2171592A5 (it) 1972-02-08 1972-02-08

Publications (1)

Publication Number Publication Date
US3854849A true US3854849A (en) 1974-12-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00328599A Expired - Lifetime US3854849A (en) 1972-02-08 1973-02-01 Distribution of valve-gear systems for rotary machines

Country Status (9)

Country Link
US (1) US3854849A (it)
JP (1) JPS5332527B2 (it)
BE (1) BE794675A (it)
DE (1) DE2306225C3 (it)
FR (1) FR2171592A5 (it)
GB (1) GB1425227A (it)
IT (1) IT978663B (it)
SE (1) SE383377B (it)
ZA (1) ZA73802B (it)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4507066A (en) * 1982-02-18 1985-03-26 Duffy James T Fluid expansion device
US5694890A (en) * 1996-10-07 1997-12-09 Yazdi; Kamran Internal combustion engine with sliding valves
US20070253855A1 (en) * 2006-04-27 2007-11-01 Hitachi, Ltd. Pump Apparatus and Power Steering

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2606172C2 (de) * 1976-02-17 1983-12-22 Danfoss A/S, 6430 Nordborg Rotationskolbenmaschine für Flüssigkeiten
US4087215A (en) * 1976-07-16 1978-05-02 Trw Inc. Gerotor gearset device
DE3744637A1 (de) * 1987-10-02 1989-04-13 Ruf Renate Drehkolbenverdichter
WO1990012210A1 (de) * 1989-03-31 1990-10-18 Imt Ingenieurgemeinschaft Für Motoren-Technik Gmbh Drehkolbenverdichter
JP2645925B2 (ja) * 1991-07-25 1997-08-25 三洋電機株式会社 冷却貯蔵庫の扉用フレーム装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2966860A (en) * 1957-04-03 1961-01-03 Lobee Pump & Machinery Co Pump for corrosive fluids
US3106163A (en) * 1960-04-04 1963-10-08 Roper Hydraulics Inc Pumps, motors and like devices
US3224421A (en) * 1961-06-29 1965-12-21 Renault Rotary engines with rotating distributors
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3658450A (en) * 1970-02-16 1972-04-25 George V Woodling Balanced fluid pressure valve means
US3671154A (en) * 1970-10-08 1972-06-20 Gen Motors Corp Epitrochoidal compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2966860A (en) * 1957-04-03 1961-01-03 Lobee Pump & Machinery Co Pump for corrosive fluids
US3106163A (en) * 1960-04-04 1963-10-08 Roper Hydraulics Inc Pumps, motors and like devices
US3224421A (en) * 1961-06-29 1965-12-21 Renault Rotary engines with rotating distributors
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3658450A (en) * 1970-02-16 1972-04-25 George V Woodling Balanced fluid pressure valve means
US3671154A (en) * 1970-10-08 1972-06-20 Gen Motors Corp Epitrochoidal compressor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4507066A (en) * 1982-02-18 1985-03-26 Duffy James T Fluid expansion device
WO1986005840A1 (en) * 1982-02-18 1986-10-09 Duffy James T Fluid expansion device
US5694890A (en) * 1996-10-07 1997-12-09 Yazdi; Kamran Internal combustion engine with sliding valves
US20070253855A1 (en) * 2006-04-27 2007-11-01 Hitachi, Ltd. Pump Apparatus and Power Steering
US7722342B2 (en) * 2006-04-27 2010-05-25 Hitachi, Ltd. Pump apparatus and power steering

Also Published As

Publication number Publication date
GB1425227A (en) 1976-02-18
SE383377B (sv) 1976-03-08
JPS4891605A (it) 1973-11-28
BE794675A (fr) 1973-05-16
ZA73802B (en) 1973-11-28
DE2306225C3 (de) 1975-08-21
IT978663B (it) 1974-09-20
DE2306225B2 (de) 1975-01-09
FR2171592A5 (it) 1973-09-21
JPS5332527B2 (it) 1978-09-08
DE2306225A1 (de) 1973-08-30

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