EP0613527B1 - Kolbenmaschine anwendbar als verdichter oder motor - Google Patents

Kolbenmaschine anwendbar als verdichter oder motor Download PDF

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Publication number
EP0613527B1
EP0613527B1 EP93901789A EP93901789A EP0613527B1 EP 0613527 B1 EP0613527 B1 EP 0613527B1 EP 93901789 A EP93901789 A EP 93901789A EP 93901789 A EP93901789 A EP 93901789A EP 0613527 B1 EP0613527 B1 EP 0613527B1
Authority
EP
European Patent Office
Prior art keywords
piston
fixed
machine
cylinder
joint
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93901789A
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English (en)
French (fr)
Other versions
EP0613527A1 (de
Inventor
Claude Trapp
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Seref
Original Assignee
Seref
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Filing date
Publication date
Application filed by Seref filed Critical Seref
Publication of EP0613527A1 publication Critical patent/EP0613527A1/de
Application granted granted Critical
Publication of EP0613527B1 publication Critical patent/EP0613527B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/02—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders
    • F04B19/027—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders cylinders oscillating around an axis perpendicular to their own axis
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/02—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders
    • F04B19/022—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders reciprocating cylinders
    • 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
    • F04B25/00—Multi-stage pumps
    • 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
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • F04B3/003—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/147—Mounting or detaching of piston rod

Definitions

  • the invention is in the field of machines with piston-cylinder pairs intended to carry out an energy exchange between a pressurized fluid and a mechanical member, and more particularly with a view to producing an air compressor or any other gas, without however excluding the realization of a motor powered by the energy of a generally gaseous fluid.
  • Machines with pistons connected to mechanical energy organs most often use the classic rod-crank system or sometimes a plate which oscillates around an oblique crank in rotation around an axis parallel to the piston-cylinder couple.
  • sliding or cam systems There are also known sliding or cam systems. All these systems introduce transverse forces, that is to say radial forces on the pistons relative to their axis, which is a friction factor with wear and creation of dust.
  • a rectilinear guide cancels the transverse forces between piston and cylinder, but it requires lubrication which is a source of pollution, and it makes the whole heavy and bulky.
  • the object of the invention is to avoid any systematic friction between cylinder and piston, to minimize the wear of these elements and allow their operation for a long period, in particular for non-lubricated machines and without seal between piston. and cylinder therefore without pollution by oil or particles from the wear of these elements.
  • This embodiment for example for gas compression, even at very high pressures, is allowed by a very precise adjustment of the surfaces facing the cylinder and piston, and over a significant length of the opposite between these two elements.
  • gear de LA HIRE consisting of a fixed crown internally toothed with a half size satellite pinion and a point on the pitch diameter of which describes a straight line which passes through the center of the crown.
  • connection is rigid, it is necessary either to align the mechanical member with a better positioning tolerance than the piston-cylinder clearance, which is in practice impracticable when this clearance is a few ⁇ m, especially as the dilations and deformations in operation aggravate the problem, that is to leave to the mechanical member a freedom of transverse positioning, but then its mass is added to that of the driven element, from where radial forces due to gravity or to vibrations, which creates friction between piston and cylinder.
  • Document WO 85/01336 discloses a floating coupling system between a reciprocating plunger and the piston, coaxial with this plunger, of a plunger type pump.
  • the piston is integral with a sphere introduced into a recess machined in the pusher, so that the only connection between the movable pusher and the piston carrying the sphere is a longitudinal connection in the direction of the axis of the pusher. This arrangement compensates for any misalignment of the piston with the axis of the pusher.
  • the invention frees, within alignment and transverse mechanical positioning limits of medium precision, the element driven with the rectilinear movement part carried by the mechanical member.
  • the transverse positioning limits can be fixed at a few 1 / 10ths of a mm, and therefore allow a transverse clearance of the same value between the driven element and the part of the mechanical member to which it is connected, without the radial component of the efforts of the movable element become troublesome.
  • the invention is thus characterized firstly by the use of a ball joint or an equivalent joint having two degrees of angular freedom between one of the elements of a piston-cylinder couple and the part with rectilinear movement of a mechanical organ to which it is connected. This job allows the alignment of this body with the piston-cylinder couple without creating oblique force on the element connected to it.
  • a Cardan joint can be used, for example, with two crossed axes.
  • such an articulation is used simultaneously with each of the two elements of the couple, one with the part with rectilinear movement, the other with a fixed part of the machine.
  • the invention is also characterized either by a connecting rod interposed between the aforementioned articulation and the piece with rectilinear movement, or by an articulation which comprises two degrees of freedom in the direction of a movement perpendicular to the movement, it is to say in the transverse direction to the efforts.
  • These transverse movements can be ensured by a flat base of the joint, which rests on a transverse plate provided on the corresponding element, or else by balls interposed between cooperating linear guide surfaces and perpendicular to the reciprocating movement.
  • the transverse displacements are advantageously limited to a value slightly greater than the precision of the positioning of the mechanical member.
  • ball joints used according to the invention makes it possible to have inside a large diameter piston a blind cylindrical conduit, that is to say closed at one end, of small diameter, parallel to the piston and which constitutes the cylinder of a second couple with variable volume, with a circuit for transferring the fluid under pressure to this second couple.
  • the piston of this second couple is then connected to the cylinder head of the first couple by a ball joint or an equivalent device, which allows an achievable tolerance of the parallelism of the elements and the alignment of their axes.
  • the compressor shown diagrammatically in FIG. 1 comprises a cylindrical casing 1 sealingly bearing a cylinder head 2.
  • the bore of the casing which is shown cut in a plane of symmetry, constitutes a first cylinder in which moves a first piston 3 which is itself even bored concentrically to form a second cylinder also carrying with sealing a second cylinder head 4.
  • the peripheries of the cylinder head 4 and most of the piston 3 are adjusted to the same diameter and with very little play in the cylinder 1.
  • the surfaces in with respect to these elements carry surface treatments or materials capable of allowing friction without lubrication.
  • the end 5 of the piston 3, opposite the second cylinder head 4, has a gas inlet 6, in relation to the interior of the casing 1 and supports two ball joints such as 7.
  • a cut-out, shown for the first piston 3 and the first cylinder head 4, makes it possible to see the ball joint 7, a connecting rod 8 articulated on the piston 3 by this ball joint and a second connecting rod 8 'symmetrical to the connecting rod 8 relative to the axis piston 3.
  • the tear-off further discovers a second piston 9 which cooperates with the bore of the first piston 3, to constitute a second compression stage, in the same way as the piston 3 and the bore of the casing 1 constitute a first compression stage, and with the same adjustments with very small clearance of the surfaces facing these pairs of elements.
  • the piston 9 is fixed, being retained by a ball joint 10 articulated in a transverse wall 11 of the casing 1.
  • This wall 11 has two orifices such as 12 to allow the sliding with clearance, therefore without guidance, of the connecting rods 8 and 8 '.
  • These are driven by means of a mechanical member 13 which comprises a movable part 14 having an alternating rectilinear movement, and by means of a lifting beam 15 for balancing the forces of the connecting rods, the latter being connected to it by ball joints 16 and 16 'symmetrical with respect to the middle of the lifter.
  • the latter is connected by a ball joint 17 to the movable part 14.
  • the piston 3 further comprises two identical conduits 18 and 18 'symmetrical with respect to its axis, parallel to the latter and each closed on the side of the end 5. These conduits constitute cylinders respectively receiving pistons 19 and 19' with very low backlash adjustments to form a third compression stage together.
  • the two variable volume couples which they constitute are connected in parallel by a gas intake circuit 20 and by a discharge circuit 21, the latter being drilled in the cylinder head 2.
  • the variable pressures are identical in each of these volumes, which balances the forces on the piston 3.
  • the pistons 19 and 19 ' are retained on the fixed cylinder head 2 by ball joints 22 and 22', with two degrees of angular freedom and in addition two degrees of transverse freedom, including one exemplary embodiment is drawn in FIG. 2 and which also equips the piston 9 with its retention on the wall 11 by the ball joint 10.
  • pistons 9, 19 and 19 are aligned in the opposite cylinders only by their respective adjustments, their supports on the fixed parts 11 and 2 taking themselves the position which minimizes the radial forces between pistons and cylinders, even in the case of relatively poor machining resulting in uncertainty about the positions of the ball joints on these fixed parts.
  • a fourth compression stage also exists inside the piston 9.
  • the cylinder head 4 carries on its axis a ball joint similar to the previous three, which retains a fourth piston 23, of small diameter, which cooperates with an adjusted cylinder. which is constituted by a bore of the fixed piston 9 of the second stage.
  • This piston 23 is therefore mobile like the piston 3, and driven by it.
  • the circuits connecting the four compression stages are susceptible of various variants.
  • the suction of the first stage is done through the orifice 6 with a conduit inside the piston 3 to supply a suction valve 24 carried by it.
  • the compressed gas is evacuated by a discharge valve 25 then in a circuit passing first through the fixed cylinder head 2, then a heat exchanger 26 and a filter 27, to be introduced into a line 28 of the fixed piston 9 up to a valve suction 29 of the second floor.
  • the piston 9 is cut to show this pipe and this valve, as well as the entire length of the mobile piston 23.
  • the discharge of the second stage passes through a valve 30 carried by the movable cylinder head 4 then a circuit passing through this cylinder head then the piston 3 to join at 31 the circuit 20 for supplying parallel volumes of variable volumes of the third stage, with for each of these ci suction valves 32 and 32 'housed inside the piston 3 in the bottoms of the cylinders receiving the pistons 19 and 19'.
  • the gas passes through a heat exchanger 34 and a filter 35, is introduced into the fixed piston 9 and into the variable volume of the fourth stage by a suction valve 36 at the bottom of the bore of this piston.
  • the discharge passes through a contiguous valve 37 and it is evacuated towards use by the pipe 38.
  • the bottom of the cylinder head 2, perpendicular to the axis of the piston 19, is of a diameter slightly greater than that of the thrust piece 74, so that the latter can move transversely with two degrees of freedom and thus adjust the axis of the piston 23 with that of the other element of the torque, that is to say the conduit 18.
  • the different parts are drilled axially to form a circulation channel for the pumped fluid, a channel which can lead to a non-return valve.
  • FIG. 3 and 4 there is shown a machine with a piston 40 which can slide with very little play in a cylinder 41, which is held in a sleeve 42 between a shoulder of this sleeve and a nut 43.
  • a connector 44 carries the suction and discharge valves, not shown, which can be contiguous like those designated at 36 and 37 in FIG. 1.
  • the sheath 42 is suspended in a fixed console 45 by means of a so-called Cardan suspension.
  • This comprises in a known manner a movable ring 46 connected to the sheath by two diametrically opposite pins such as 47 and to the console by two other diametrically opposed pins in a perpendicular plane, such as 48.
  • This assembly is equivalent to a ball joint with two degrees of angular freedom for the cylinder 41.
  • the piston 40 carries a tail 49 enclosed in a clamp 50 with clamping screws 51 and 52, the pliers constituting an extension of a rod 53.
  • a ball bearing 54 cooperates without longitudinal play with a hole 55 in the rod 53.
  • This bearing is driven by a Watt connecting rod assembly of a known type, connecting rod assembly constituted here by a connecting rod 56 almost parallel to the longitudinal movement and each of whose ends is carried by a crank 57 or 58.
  • cranks are articulated by a ball bearing at one of said ends of the connecting rod 56 and by another bearing at an axis fixed 59 or 60, these fixed axes being on either side of the connecting rod 56, so that the offsets of the positions of the mobile ends of the cranks, relative to the axis of the rectilinear movement, compensate each other in the middle of the connecting rod.
  • a stud 61 carries the bearing 54, which is thus driven by a very substantially rectilinear longitudinal movement.
  • This movement is in exchange for energy with a mechanical member constituted here by a belt 62 connected to a motor which is not shown and which drives a pulley 63 carrying an eccentric crankpin 64 to actuate the crank 58 in alternating oscillation by means of a connecting rod 65 articulated on the crankpin 64 and on the extension of the crank 58.
  • the bearing 54 can be mounted without play in the rod 53, which guides the latter precisely in a rectilinear movement compatible with that of the piston 40 in the cylinder 41, even in the event of misalignment due to the mounting of the cardan shaft of the cylinder. 41.
  • the rod 53 can actuate a second piston-cylinder couple by means of a second clamp 66.
  • a second universal joint assembly supports the second couple and it precisely defines the axis of the reciprocating rectilinear movement of the two pistons.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)

Claims (9)

  1. Maschine zum Austauschen von Energie zwischen einerseits einem mechanischen Organ, welches ein bewegliches Teil (14,61) umfaßt, das eine geradlinige, alternierende Beweglichkeit hat, und andererseits einen zum Transferieren eines Fluids unter Druck mit einem Zylinder (3) zusammenarbeitenden Kolben (9), mit einer Verbindung eines von diesen mit dem beweglichen Teil (14) und einer Verbindung des anderen mit einem festen Teil (11), wobei die Verbindung des Kolbens (9) ein Gelenk (10) mit zwei Abwinkelungs-Freiheitsgraden umfaßt,
    dadurch gekennzeichnet,
    daß die Verbindung des Zylinders (3) ebenfalls ein Gelenk mit zwei Abwinkelungs-Freiheitsgraden umfaßt, wie ein Pfannengelenk (7, 7', 10, 22, 22', 54, 73) oder Kardangelenk (46).
  2. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß wenigstens eines der Gelenke außerdem zwei Bewegungsfreiheitsgrade senkrecht zur geradlinigen Bewegung durch zu dieser Bewegung senkrechte Flächen und eine gegenseitig wirkende Gleitlagerung umfaßt.
  3. Maschine nach Anspruch 1 oder Anspruch 2, dadurch gekennzeichnet, daß der bewegliche Teil (14) einen Teil eines Getriebes bildet, welches durch ein Innenzahn-Leitrad gebildet ist, das mit einem Satellitenrad halber Dimension zusammenarbeitet.
  4. Maschine nach Anspruch 1 oder Anspruch 2, dadurch gekennzeichnet, daß das bewegliche Teil (54) einen Teil einer Watt'sehen Geradführung bildet.
  5. Maschine nach irgendeinem der Ansprüche 1 bis 4, mit einem ersten beweglichen Kolben (3) in einem feststehenden Gehäuse (1) und umfassend eine Bohrung, die mit einem fixierten Kolben (9) zusammenarbeitet, dadurch gekennzeichnet, daß der erste Kolben (3) durch zwei Pleuel (8, 8') angetrieben ist, die mit ihm durch zwei Pfannengelenke (7, 7') verbunden sind, und daß der fixierte Kolben (9) über ein Pfannengelenk (10) mit einer Wandung (11) verbunden ist, die am Gehäuse (1) fixiert ist.
  6. Maschine nach Anspruch 5, dadurch gekennzeichnet, daß die Pleuel (8, 8') durch zwei Pfannengelenke (16, 16') über eine Traverse (15) mit einem beweglichen Stück (14) verbunden sind, welches eine geradlinige Bewegbarkeit hat.
  7. Maschine nach Anspruch 5 oder Anspruch 6, dadurch gekennzeichnet, daß der erste Kolben (3) und das Gehäuse (1) eine Stufe zur Transferierung von Fluid unter Druck bilden.
  8. Maschine nach irgendeinem der Ansprüche 5 bis 7, gekennzeichnet durch mehrere identische Führungen (18, 18') in dem Kolben (3), die miteinander durch Schleifen (20, 21) verbunden sind und jeweils einen Kolben (19, 19') empfangen haben, der durch ein Pfannengelenk (22, 22') fixiert ist, das mit einem Bodenstück (2) verbunden ist, das vom Gehäuse (1) getragen wird.
  9. Maschine nach irgendeinem der Ansprüche 5 bis 8, dadurch gekennzeichnet, daß der fixierte Kolben (9) eine Bohrung umfaßt, die mit einem beweglichen Kolben (23) zusammenarbeitet, der durch ein Pfannengelenk mit einem Bodenstück (4) verbunden ist, das am ersten Kolben (3) fixiert ist.
EP93901789A 1991-11-22 1992-11-20 Kolbenmaschine anwendbar als verdichter oder motor Expired - Lifetime EP0613527B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9114385A FR2684140A1 (fr) 1991-11-22 1991-11-22 Machine a piston utilisable en compresseur ou en moteur.
FR9114385 1991-11-22
PCT/FR1992/001077 WO1993010353A1 (fr) 1991-11-22 1992-11-20 Machine a piston utilisable en compresseur ou en moteur

Publications (2)

Publication Number Publication Date
EP0613527A1 EP0613527A1 (de) 1994-09-07
EP0613527B1 true EP0613527B1 (de) 1996-04-10

Family

ID=9419202

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93901789A Expired - Lifetime EP0613527B1 (de) 1991-11-22 1992-11-20 Kolbenmaschine anwendbar als verdichter oder motor

Country Status (5)

Country Link
US (1) US5479846A (de)
EP (1) EP0613527B1 (de)
DE (1) DE69209848T2 (de)
FR (1) FR2684140A1 (de)
WO (1) WO1993010353A1 (de)

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB131020A (en) * 1918-03-21 1919-08-21 George Constantinesco Improved Means for Lubricating Internal Combustion Engines.
US1494741A (en) * 1920-08-25 1924-05-20 Willis W Hale Air compressor
US2146133A (en) * 1936-06-01 1939-02-07 Waterbury Tool Co Power transmission
GB636247A (en) * 1946-03-07 1950-04-26 Dunlop Rubber Co Improvements relating to fluid operated jacks
FR1057693A (fr) * 1951-06-11 1954-03-10 Lindes Eismaschinen Ag Pompe à double effet pour gaz liquéfiés
US3115296A (en) * 1959-12-11 1963-12-24 Linde Eismasch Ag Process and apparatus for the prevention of fires in oxygen high-pressure compressors
US3168014A (en) * 1962-09-11 1965-02-02 Alkon Products Corp Mounting arrangement for hydraulic piston and cylinder
US3314336A (en) * 1963-05-20 1967-04-18 Licentia Gmbh Ball and socket joint for cylinder head
US3414302A (en) * 1966-12-23 1968-12-03 Universal Fluid Dynamics Compa Coupling for misaligned reciprocal shafts
DE2019242A1 (de) * 1969-04-21 1971-02-25 Peugeot Kolbenstange mit Kolben fuer hydraulische Pumpen oder Motoren
DE2159869A1 (de) * 1971-12-02 1973-06-07 Siemens Ag Hydraulische oder pneumatische verstellvorrichtung
FR2429925A1 (fr) * 1978-06-29 1980-01-25 Charbonnages De France Articulation a rotule pour transmission d'efforts en appui et en traction
DE3124035A1 (de) * 1981-06-19 1983-01-05 Saarbergwerke AG, 6600 Saarbrücken "stopfbuchsenpackung und -anordnung"
US4443163A (en) * 1982-07-15 1984-04-17 Gaither Luis A Fluid motor or pump
US4511276A (en) * 1983-05-04 1985-04-16 Doutt Kingsley A Cylinder piston rod coupler
US4790236A (en) * 1983-09-12 1988-12-13 Beckman Instruments, Inc. Floating piston coupling for plunger type pumps
DE8816661U1 (de) * 1988-02-24 1990-03-01 Borsig Gmbh, 1000 Berlin, De

Also Published As

Publication number Publication date
FR2684140B1 (de) 1995-06-02
DE69209848T2 (de) 1996-11-21
FR2684140A1 (fr) 1993-05-28
EP0613527A1 (de) 1994-09-07
WO1993010353A1 (fr) 1993-05-27
US5479846A (en) 1996-01-02
DE69209848D1 (de) 1996-05-15

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