EP0184484B1 - Drehkolbenmaschine und mit der Kurbel gekoppelter Ring - Google Patents

Drehkolbenmaschine und mit der Kurbel gekoppelter Ring Download PDF

Info

Publication number
EP0184484B1
EP0184484B1 EP85402172A EP85402172A EP0184484B1 EP 0184484 B1 EP0184484 B1 EP 0184484B1 EP 85402172 A EP85402172 A EP 85402172A EP 85402172 A EP85402172 A EP 85402172A EP 0184484 B1 EP0184484 B1 EP 0184484B1
Authority
EP
European Patent Office
Prior art keywords
piston
crank
crown wheel
axis
shaft
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
Application number
EP85402172A
Other languages
English (en)
French (fr)
Other versions
EP0184484A1 (de
Inventor
Jean Claude Janicki
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.)
Sanofi SA
Original Assignee
TECNALOR SA
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 TECNALOR SA filed Critical TECNALOR SA
Priority to AT85402172T priority Critical patent/ATE41695T1/de
Publication of EP0184484A1 publication Critical patent/EP0184484A1/de
Application granted granted Critical
Publication of EP0184484B1 publication Critical patent/EP0184484B1/de
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the present invention relates to rotary piston machines, in particular to rotary piston compressors, comprising a cylindrical chamber, in which are arranged an eccentric or crank part of a shaft coaxial with said chamber, an annular rotary piston being able to roll in contact. of the wall of the chamber and a crown for driving the piston mounted with clearance inside thereof, the timing of the piston on its raceway being ensured by elastic means.
  • French patent 2,280,808 only delaying the detachment of the piston by maintaining the angle formed between the line connecting the center of the chamber to the center of the piston with the line connecting the latter center to the center of the eccentric at an optimal value between 20 ° and 40 °.
  • the rotor is constituted by a cylindrical jacket freely mounted in the chamber around the shaft and kept in contact with the wall of said chamber by means of a rolling device with movable mounting, which consists in a lever wedged on the shaft and carrying at one end a roller and at the other end an arm ending in a roller, a spring being provided to separate the arm from the lever.
  • French patent 2,223,570 which constitutes the state of the art and recommends the mounting of the rotary piston on an eccentric drive ring secured to the eccentric of the shaft, the angle made by the straight line. connecting the axis of the shaft to the axis of the eccentric part with the straight line which connects the latter axis to the central axis of the eccentric crown is between 70 ° and 110 °, so that the piston rolls in applying to the inner wall of the housing and that, once a certain release pressure is reached, the piston moves away from the wall of the housing.
  • Such a compressor does not perform mechanical setting of the piston in operation, but only drives the piston by means of the eccentric ring.
  • the present invention relates to a machine in which one realizes both a good drive of the piston and its setting on the bore of the chamber, while preventing its detachment in the high pressure zone, without this embodiment comprising the mounting mechanical with adjustment of the eccentric or mounting on ball bearings directly on the eccentric, necessarily requiring costly precision in terms of machining and assembly of the machine.
  • the rotary piston machine in particular rotary piston compressor, comprising a cylindrical chamber, in which are arranged an eccentric or crank part of a shaft coaxial with said chamber, an annular rotary piston being able to roll in contact with the wall of the chamber and a coaxial ring for driving the piston in contact with the internal wall of the piston over its entire circumference and mounted inside the latter, so as to be able to slide relative to the piston, the setting of the piston on its raceway being provided by elastic compensation means bearing on the crank or the shaft and on the bore of the crown, the machine further comprising a flap dividing the free space around the piston into two compartments to variable volume is the crown being driven in rotation by means of a journal, the axis of the journal extending in the longitudinal direction of the machine and being located in an eccentric position p ar relative to the crown, characterized in that the pin is mounted in a yoke making the coupling of the crown and the crank.
  • the coupling member is a pin mounted in a yoke.
  • the journal is mounted in a bore of the crank and in a yoke secured to the crown.
  • a clevis secured to the crank and a bore made in the crown.
  • the timing of the piston on its raceway can be ensured by elastic means of compensation with various progressive adjustment.
  • a spring is mounted transversely upstream of the point of contact of the piston and of the wall of the chamber with respect to the direction of rotation, bearing on the crown and on the crank, so that the straight line d he action of the spring passes through the axis of the shaft and is perpendicular to the right connecting the center of the piston and the center of the journal.
  • the spring is housed between a centering stud fixed to the crown and a cylindrical housing with counterbore made in the crank, the bottom of the housing being parallel to the right connecting the centers of the piston and the crank.
  • the elastic wedging means consist of at least one wedge with a conical slope urged by a spring working in compression along a line of action transverse to the axis of the shaft.
  • one of the longitudinal faces of the crank has two concave longitudinal flats inclined relative to the axis of the shaft and forming with the bore of the crown a housing, two wedges being housed at the ends of said housing, each having an inner face with a slope of angle corresponding to that of the inclined flat, a spring being disposed between the shims.
  • the part of the crown on which the wedges bear has a flat, while the outer face of each wedge which bears has a rounded profile.
  • the compressor of a refrigeration machine according to the invention shown in FIGS. 1 and 2 comprises a central body of compressor 2 provided with two external flanges before 11 and rear 12, crossed by a motor shaft 4 of axis 0 1 , Body 2 contains a coaxial cylindrical chamber of the shaft 4, the internal wall 10 of which constitutes the raceway of the piston.
  • the shaft 4 is made integral with an eccentric or crank 3.
  • a rotary piston 5 of axis 0 2 of diameter smaller than that of the chamber is placed inside of the latter, so as to be able to roll in contact with the wall of the chamber, while a movable drive ring 6 is mounted inside the piston 5, so as to be able to slide relative to the piston according to the sliding surface 7.
  • the crown 6 is provided with a yoke 8, 9 and the end of the crank 3 with a bore 24, so as to be able to couple the crown 6 and the crank 3 by means of a pin pin 0 3 which can freely rotate in bore 24.
  • the virtual piston drive rod 5 is represented by the right connecting the center of the crown and of the piston 0 2 to the center of the journal 0 3 .
  • the body of the compressor 2 contains under the cylinder head 34 provided with cylinder head gasket 37 of the organs usual, such as suction and discharge conduits, the latter provided with two valves 17, HP outlets 41, 42, as well as a separation flap 15 rocking around its axis 16 and provided with sealing segments 54.
  • the shutter 16 separates the interior of the cylinder in the HP chamber 13 and the BP chamber 14, the point of contact of the end of the shutter and of the piston 5 being effected by means of the bearing surface 29 of the shutter cut in bevel, in the central axis of the cylinder at point G.
  • the usual equipment of a compressor comprises a lubricant reservoir 38 with its level control plug 39.
  • the motor shaft 4 rests in bearings 43, 44, it is provided with rotary seals 31 and a bubbling spoon 32 and a balancing weight 33.
  • Centering feet 35 equip the rear and front flanges of the stator.
  • Spider legs 40 serve to lubricate the plain bearing of the movable crown and of the piston.
  • the lateral sealing of the piston 5 is ensured by circular segments 36.
  • the wedging means used to take up the initial mounting clearance and the wear clearance consist, according to FIGS. 2 and 3, of a compensating spring 30 working in compression, whose axis of action 23 (FIG. 11) is perpendicular to the right connecting the center of the crown 0 2 and the center of the pin 0 3 .
  • One of the ends of the spring 30 bears on a centering shoe 52, integral with the crown 6 and the other in a centering counterbore 53 present on the motor shaft 4.
  • the compressor of FIG. 3 represents an alternative embodiment in which the piston 5 is mounted on a needle bearing 22 and the compensation device comprises a pair of wedges with conical slopes 55 urged by a locking spring 57 with an axis 61, the outer surface 60 of the wedge 55 of rounded shape bearing on a contact shoe 59 secured to the crown (see FIG. 14).
  • a line O 1 can be drawn connecting the center 0 1 from the tree to point E. It is with respect to this straight line that we define the wedging angle ⁇ 1 ' between the line 0 1 E and the line 0 1 0 3 connecting the center 0 1 of l tree in the center of the trunnion.
  • the angle ⁇ 1 is therefore the angle by which the axis of the journal 0 3 is offset, relative to the straight line 0 1 E in the direction of rotation of the shaft.
  • this angle must be carefully chosen. Indeed, the angle ⁇ 1 is mathematically linked to the value of the clearance J between the piston and the wall of the chamber. This clearance J is calculated and measured when, the effects produced by elastic compensation means being canceled, the axis of the piston 0 2 is located in alignment with the axes 0 1 and 0 3 of the shaft and the journal, on the line of alignment of these axes. This play can be observed, when the crank is pivoted around the axis 0 3 to bring the center of the piston 0 2 to the right O 1 O 3 .
  • the graph in FIG. 5 represents a curve 48 giving the variation of the clearance J in 10 -1 mm as a function of the angle a, in radians. We see that the variation is almost linear for values of J greater than 1 mm.
  • the values of J and a are mathematically linked and can be calculated for given dimensions of the chamber, the crank arm and other construction parameters.
  • FIG. 4 represents, for a clearance of 2.5 mm corresponding to an angle ⁇ 1 of approximately 36 °, a variation of the reaction force Re expressed in decanewton at the sliding contact point E of the piston on the wall of the chamber as a function of the crank angle w in radians, i.e. the instantaneous angular position of the straight line 0 1 E.
  • This curve shows an equilibrium point 45 for a crank angle value w, to which the force diagram of FIG. 10 corresponds, where the reaction force Re at the contact point E is zero.
  • the curve has a maximum at 46 corresponding to a value of the crank angle w located between 0 ° and w, for which the reaction force Re at the contact point E is maximum.
  • This negative reaction force Re has a minimum at 47, the effect of which must be combated by the use of elastic compensation means, such as springs or a combination of shims and springs (see the force diagram, FIG. 11).
  • FIG. 6 presents a curve 49 of variations in the compression efficiency in percent as a function of the setting angle a, in radians.
  • the ascending part of the curve corresponds to the low values of a, which should theoretically be the choice.
  • the reaction force Re the variations of which as a function of the crank angle w are shown in FIG. 4, can reach prohibitive values incompatible with the tolerable forces that can be imposed on the materials due to their resistance. to break and wear quickly.
  • ⁇ 1 equal to or less than 20 °
  • the reaction on the motor shaft is too strong and as a result of the increase in mechanical forces the efficiency decreases.
  • the smaller a i the greater the forces exerted on the piston and the journal which generate energy losses by transformation into friction heat.
  • FIGS. 7 and 8 show the curves 50 and 51 showing the variations of the forces Re expressed in decanewton as a function of the value of the clearance J in 10 -1 mm, corresponding respectively to the maximum reaction force at the contact point E ( point 46 of the curve according to FIG. 4) and at the maximum negative reaction force (point 47 of the same curve).
  • the positive reaction force Re decreases when the clearance J increases. This force tends to infinity for zero play, which would direct the manufacturer towards the greatest possible play.
  • the piston is in equilibrium for a crank angle w between 0 ° and w 1 ( Figure 4). It is subjected to a torque resulting from the positive force FPc which represents the pressure force prevailing in the HP chamber and passing through the center of the piston 0 2 .
  • the letter a indicates the arm of the lever which makes it possible to calculate the torque acting on the axis O 3 of the journal and which keeps the piston applied on its raceway for a rotation of the crankshaft corresponding to an angle of 0 ° to w 1 in radians.
  • FIG. 10 represents the piston in equilibrium for an angle w equal to w 1, that is to say just before the detachment of the piston.
  • FIG. 11 represents a force diagram for an angle w comprised between w 1 and w 2 , that is to say in the separation zone.
  • the force Re becomes negative and reaches its maximum for an angle w 2 .
  • This force is exerted via the lever arm b and forms a torque tending to detach the piston from its point of contact E with the cylinder.
  • the effect of the negative force Re is compensated for by the action of one or more springs 30 ( Figures 11 and 12), whose torque FR x O 1 O 3 cos a 3 is equal to the torque Re x b.
  • the bearing face 62 of the spring 30 on the crown is parallel to the straight line 25 connecting the centers of the piston 0 2 and of the pin O 3 and its line of action 23 passing through the center 0 1 of the shaft is perpendicular to the right 25.
  • the calculation of the spring force must take into account several factors, such as the working pressure in the HP chamber and the dimensions of the chamber and the piston.
  • the spring 30 is disposed upstream of the contact point E with respect to the direction of the piston bearing (FIG. 2), its axis 67 passes through the axis O 1 of the shaft and is perpendicular to the straight line 25. It is housed between a centering stud 65 fixed to the crown and a cylindrical housing with counterbore 64 formed in the crank and the bottom 66 of which is parallel to the straight line 25 (FIG. 12).
  • the device using one or more springs to keep the piston applied on its raceway and to compensate for the negative force Re represents a first solution for setting the piston.
  • Other compensation and setting means consist in using wedges with conical slopes urged by one or more springs and allow a progressive setting of setting.
  • a concave housing formed by two inclined longitudinal flats 58 to accommodate a pair of wedges 55 with conical slopes 58 of opposite direction.
  • the crank block has two slopes at the location of the housing, the angle of orientation of each corresponding to the slope of the wedge which is housed there.
  • the conical slopes of the housing and of the shims are inclined at an angle a 4 with respect to the axis O 1 of the shaft 4. At the two transverse ends of the housing are housed the shims 55.
  • the faces of the shims opposite the faces with a slope d 'angle a 4 and bearing on a flat 62 or shoe that has the crown 6 at this location are convex and rounded, so that the wedges are supported on their shoes according to a generatrix designated by K.
  • the plane of symmetry 63 longitudinal of shims passes through the center 0 1 .
  • the two wedges 55 are biased in opposite directions by a spring 57 working under compression, the centering axis 61 of which is housed at the two ends in the wedges.
  • the thrust of the wedges 55 exerted against the shoe 62 of the crown is per pendulum to the right connecting the axis of the piston 0 2 and the axis of the pin 0 3 .
  • FIG. 15 and 16 Another embodiment of shims is shown in Figures 15 and 16. Instead of being oriented at an angle a 4 relative to the axis 0 1 of the shaft 4, the slope 71 of the shim 70 is inclined transversely by with respect to the axis 0 1 and in particular of an angle a5 relative to the straight line connecting the center 0 3 of the journal and the center O2 of the piston. To this end, the housing provided for the shim is between the longitudinal flat 71 of the crank 3 and the flat 72 that has the bore of the crown 6.
  • the shim 70 one longitudinal face of which has a slope of angle a5 , is pierced on a lateral face of the two blind housings 73 to accommodate the ends of the two springs 74 working under compression, the opposite ends of which are retained by centering studs 75 placed on a flat part of the crown 6.
  • wedges The action of wedges is exerted along a transverse straight line with respect to the axis of the shaft 4 and has the effect of pushing the crown 6 of the crank in the direction perpendicular to said straight line.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Compressor (AREA)
  • Hydraulic Motors (AREA)
  • Transmission Devices (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Acyclic And Carbocyclic Compounds In Medicinal Compositions (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (11)

1. Drehkolbenmaschine, insbesondere Drehkolbenkompressor, mit einer zylindrischen Kammer (13, 14), in welcher eine Exzenterscheibe oder Kurbel (3) mit einer eine koaxial zur Kammer liegende Achse 01 aufweisenden Welle (4), ein in Kontakt mit der Wand (10) der Kammer laufender ringförmiger Drehkolben (5), und ein auf seinem gesamten Umfang in Kontakt mit der Innenwand des Kolbens und in dessen Innerem angebrachten, relativ zum Kolben gleitfähigen Ring (6) zum Antreiben des Kolbens (5) angeordnet sind, wobei die Stellung des Kolbens auf seinem Laufweg durch sich auf der Kurbel oder auf der Welle und in der Öffnung des Ringes (6) abstützende elastische Kompensationsteile (30, 55 und 57, 70 und 74) gesichert ist, weiterhin mit einer den freien Raum um den Kolben herum in zwei Abteilungen (13, 14) mit variablem Volumen aufteilenden Klappe (15), bei der der Ring mittels eines Zapfens (1), dessen Achse 03 sich in Längsrichtung der Maschine erstreckt und relativ zum Ring in einer exzentrischen Position angeordnet ist, rotierend antreibbar ist, dadurch gekennzeichnet, dass der Zapfen in einer Ring (6) und Kurbel (3) koppelnden Kappe (8, 9) untergebracht ist.
2. Maschine nach Anspruch 1, dadurch gekennzeichnet, dass der Zapfen (1 ) in einer Bohrung (24) mit Achse 03 der Kurbel (3) und in einer mit dem Ring (6) kraftschlüssig verbundenen Kappe (8, 9) untergebracht ist.
3. Maschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Winkel al der Anstellwinkel der Achse 03 des Zapfens gegenüber der der Stellung des Kolbens entsprechenden Kontaktstelle E auf der Wand (10) der Kammer ist, dessen Wert mathematisch mit dem Wert des Spieles J verknüpft ist, das bei mit den Achsen 01 der Welle und O3 des Zapfens aufgrund Fehlens der von den elastischen Kompensationsteilen erzeugten Wirkungen fluchtender Achse 02 des Kolbens zwischen dem Kolben und der Wand vorhanden wäre, wobei man für einen Arbeitsdruck, eine Drehzahl und für gegebene Radiuslängen des Kolbens und der Kammer einen Winkel α1 grösser als 20° wählt, dem ein Spiel J von ungefähr 1 mm entspricht, um zu vermeiden, dass die Materialien zu starken mechanischen Beanspruchungen unterworfen werden.
4. Maschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die elastischen Einstellteile wenigstens eine Feder (30) aufweisen, welche in bezug auf den Drehsinn des Kolbens quer oberhalb des Kontaktpunktes E angebracht ist, wobei sie sich einerseits an der Kurbel (3) und andererseits am Ring (6) so abstützt, dass die Wirkungslinie der Feder die Achse 01 der Welle schneidet und senkrecht zur Verbindungslinie (25) vom Mittelpunkt 02 des Kolbens und dem Mittelpunkt O3 des Zapfens verläuft.
5. Maschine nach Anspruch 4, dadurch gekennzeichnet, dass die Stützfläche (62) der Feder auf dem Ring parallel zur Verbindungslinie vom Mittelpunkt 02 des Kolbens zum Mittelpunkt 03 des Zapfens liegt.
6. Maschine nach Anspruch 4, dadurch gekennzeichnet, dass die Feder (30) zwischen einer am Ring befestigten Zentrierklemme (65) und einer in der Kurbel ausgesparten zylindrischen Ausnehmung mit Führung (64) angebracht ist, deren Bodenfläche (66) parallel zur Verbindungslinie von 02 und 03 liegt.
7. Maschine nach einem derAnsprüche 1 bis 3, dadurch gekennzeichnet, dass die elastischen Einstellteile aus wenigstens einem durch eine längs einer Wirkungslinie quer in bezug auf die Achse 0, der Welle (4) auf Druck arbeitende Feder belasteten Keil mit konischen Keilflächen bestehen, wobei der Keil in einer Ausnehmung zwischen der Kurbel und dem Ring untergebracht ist, dessen eine Wand eine konische Keilfläche darstellt.
8. Maschine nach Anspruch 7, dadurch gekennzeichnet, dass eine der Längsflächen der Kurbel zwei in Längsrichtung sich erstreckende konkave, unter einem Winkel 04 in bezug auf die Achse 0, der Welle geneigte Abflachungen (58) aufweist, welche mit der Öffnung des Ringes (6) eine Aufnahme bilden, wobei an beiden Enden der Aufnahme je ein Keil (55) mit einer der geneigten Abflachung (58) entsprechenden inneren Fläche mit Abflachungswinkel a4 untergebracht und zwischen den Keilen (55) eine druckbelastete Feder (57) angeordnet ist.
9. Maschine nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass der Teil des Ringes, auf dem sich die Keile abstützen, eine einen Fuss bildende Abflachung (62) aufweist, während die sich auf dem Fuss abstützende Aussenfläche jedes Keils abgerundet ist.
10. Maschine nach Anspruch 7, dadurch gekennzeichnet, dass zwischen der Öffnung des Ringes und der Kurbel eine Lagerung für einen Keil (70) mit abgeschrägten Längsflächen vorgesehen ist, bei der die Keilfläche (71 ) der Lagerung an der Kurbel in Querrichtung um einen Winkel a5 in bezug auf die Verbindungslinie von Mittelpunkt 02 des Kolbens und Mittelpunkt O3 des Zapfens geneigt ist, wobei die Kraft des durch wenigstens eine Feder (74) belasteten Keils (70) längs einer quer zur Welle (4) liegenden Linie angreift.
11. Maschine nach Anspruch 10, dadurch gekennzeichnet, dass in eine Seitenfläche des Keils (70) wenigstens eine Blindausnehmung (73) gebohrt ist, die ein Ende der Feder (74) aufnimmt, während das andere Ende der Feder sich auf einer Zentrierklemme (75) abstützt, die kraftschlüssig mit einer Abflachung (72) des Ringes (6) verbunden ist.
EP85402172A 1984-11-13 1985-11-12 Drehkolbenmaschine und mit der Kurbel gekoppelter Ring Expired EP0184484B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85402172T ATE41695T1 (de) 1984-11-13 1985-11-12 Drehkolbenmaschine und mit der kurbel gekoppelter ring.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8417307A FR2573137B1 (fr) 1984-11-13 1984-11-13 Machine a piston rotatif et couronne accouplee a la manivelle.
FR8417307 1984-11-13

Publications (2)

Publication Number Publication Date
EP0184484A1 EP0184484A1 (de) 1986-06-11
EP0184484B1 true EP0184484B1 (de) 1989-03-22

Family

ID=9309551

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85402172A Expired EP0184484B1 (de) 1984-11-13 1985-11-12 Drehkolbenmaschine und mit der Kurbel gekoppelter Ring

Country Status (12)

Country Link
US (1) US4759697A (de)
EP (1) EP0184484B1 (de)
JP (1) JPS61126391A (de)
KR (1) KR920001968B1 (de)
CN (1) CN1005074B (de)
AT (1) ATE41695T1 (de)
BR (1) BR8505704A (de)
DE (1) DE3569011D1 (de)
ES (1) ES8706906A1 (de)
FR (1) FR2573137B1 (de)
IE (1) IE56884B1 (de)
PT (1) PT81477B (de)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03113527A (ja) * 1989-09-27 1991-05-14 Yokogawa Electric Corp 回転磁気メモリの制御装置
JPH0744427A (ja) * 1993-07-30 1995-02-14 Nec Corp ディスクのデータ整列方式
CN1267792A (zh) * 1999-03-22 2000-09-27 彭力丰 滚动转子式压缩机
CN100441871C (zh) * 2003-06-17 2008-12-10 乐金电子(天津)电器有限公司 密封旋转式压缩机的偏心活塞装置
CN104074762A (zh) * 2014-06-12 2014-10-01 珠海凌达压缩机有限公司 旋转式压缩机的泵体结构及旋转式压缩机
CN105545739A (zh) * 2016-01-29 2016-05-04 南通广兴气动设备有限公司 一种旋压真空泵
CN105604982A (zh) * 2016-01-29 2016-05-25 南通广兴气动设备有限公司 一种旋压高压气泵
RU2664727C2 (ru) * 2017-02-07 2018-08-22 Общество с ограниченной ответственностью Научно-производственное предприятие "Норд-инжиниринг" (ООО НПП "Норд-инжиниринг") Роторно-поршневой двигатель
CN112983816B (zh) * 2021-03-05 2023-05-09 珠海格力节能环保制冷技术研究中心有限公司 压缩机
CN113339429B (zh) * 2021-07-09 2025-01-10 绍兴铁安汽配制造有限公司 一种制动器的楔块总成
FR3164737A1 (fr) * 2024-07-22 2026-01-23 Valeo Japan Co., Ltd. Compresseur a piston roulant

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR582267A (fr) * 1924-05-23 1924-12-15 Dispositif de compresseur d'air, rotatif, à piston cylindrique
US1692639A (en) * 1926-12-11 1928-11-20 Henry L Elsner Pump
FR655802A (fr) * 1927-05-11 1929-04-24 Vacuum Compressor Ab Dispositif au moyen duquel on obtient un contact étanche entre le piston et les parties fixes d'une machine rotative telle qu'un compresseur, une pompe, ou un moteur
GB380313A (en) * 1931-12-11 1932-09-15 John Ekeloef Improvements in rotary pumps or compressors
FR1256125A (fr) * 1960-02-05 1961-03-17 Perfectionnement apporté aux machines rotatives à rotor excentré
US3924977A (en) * 1973-06-11 1975-12-09 Little Inc A Positive fluid displacement apparatus
DE2437559A1 (de) * 1974-08-03 1976-02-19 Bosch Gmbh Robert Kompressor
DE2509536A1 (de) * 1975-03-05 1976-09-16 Bosch Gmbh Robert Kompressor mit einem zu seiner antriebswelle exzentrischen rollkolben
JPS5392914A (en) * 1977-01-25 1978-08-15 Nippon Air Brake Co Eccentric driving mechanism of rotary piston type compressor
DE2853915C2 (de) * 1978-12-14 1985-05-30 Erich 7812 Bad Krozingen Becker Rollkolbenpumpe
DE2944198A1 (de) * 1979-11-02 1981-05-07 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Rollkolbenverdichter
DE2946906C2 (de) * 1979-11-21 1985-02-14 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Rollkolbenverdichter
JPS5867903A (ja) * 1981-10-20 1983-04-22 Sanden Corp 起動時アンロ−デイングを可能にした容積式流体装置

Also Published As

Publication number Publication date
IE56884B1 (en) 1992-01-15
KR920001968B1 (ko) 1992-03-07
CN85108179A (zh) 1986-08-27
BR8505704A (pt) 1986-08-12
PT81477A (fr) 1985-12-01
ES548747A0 (es) 1987-07-01
JPS61126391A (ja) 1986-06-13
PT81477B (pt) 1991-05-22
ATE41695T1 (de) 1989-04-15
FR2573137A1 (fr) 1986-05-16
KR860004245A (ko) 1986-06-18
DE3569011D1 (en) 1989-04-27
CN1005074B (zh) 1989-08-30
ES8706906A1 (es) 1987-07-01
IE852819L (en) 1986-05-13
EP0184484A1 (de) 1986-06-11
US4759697A (en) 1988-07-26
FR2573137B1 (fr) 1987-02-13

Similar Documents

Publication Publication Date Title
EP0184484B1 (de) Drehkolbenmaschine und mit der Kurbel gekoppelter Ring
EP1169549B1 (de) Mechanische transmissionsvorrichtung für motoren mit variablem hubraum
EP0060822A1 (de) Motor mit geradliniger Bewegung und Taumelscheibe dafür
FR3066792B1 (fr) Dispositif de lubrification de palier
FR2763102A1 (fr) Compresseur pour une installation de climatisation d'un vehicule automobile
EP0052387B1 (de) Motor mit mindestens einem linearbewegten Kolben und einerTaumelscheibe
EP0220094A1 (de) Federungsaggregat mit Schwingenarm für Fahrzeuge
EP0426540B1 (de) Brennkraftmaschine mit variablem Hub
FR2534637A1 (fr) Machine a pistons axiaux notamment du type de construction a disque reglable
FR3042238A1 (fr) Roulement de pied de pale, systeme oscillant et systeme tournant
FR2999661A1 (fr) Systeme tribologique d'un module de piston et machine hydrostatique a pistons radiaux ainsi equipee
FR2668553A1 (fr) Machine tournante a butee axiale auto-eclipsable a membrane flexible soumise a la pression d'un fluide.
FR2817233A1 (fr) Dispositif de montage d'un pied de pale d'helice dans un moyeu
FR2950926A1 (fr) Moteur a pistons rotatifs
EP1167756A1 (de) Axialkolbenpumpe
WO1982003250A1 (fr) Machine a piston rotatif, notamment moteur thermique, compresseur ou pompe
FR3034153A1 (fr) Moyeu a roue libre avec dispositif de reduction de bruit
WO2026008949A1 (fr) Systeme a etancheite dynamique comprenant un segment d'etancheite ameliore
FR3055925A1 (fr) Dispositif a pistons radiaux hydrauliques
FR3160388A1 (fr) Hélice munie de pales et aéronef comportant au moins une hélice
FR3047789A1 (fr) Systeme d'etancheite ameliore pour carter et palier de machine hydraulique
FR3102814A1 (fr) Bielle à longueur variable pour moteur à rapport volumétrique piloté
FR2988789A1 (fr) Dispositif de calage axial d'un roulement soumis a un debattement angulaire
EP3724506A1 (de) Spiralverdrängermaschine
BE623247A (de)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19851118

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE GB IT LI LU NL SE

17Q First examination report despatched

Effective date: 19870921

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 41695

Country of ref document: AT

Date of ref document: 19890415

Kind code of ref document: T

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3569011

Country of ref document: DE

Date of ref document: 19890427

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: CH

Ref legal event code: PUE

Owner name: SANOFI, SOCIETE ANONYME

ITPR It: changes in ownership of a european patent

Owner name: CESSIONE;SANOFI

NLS Nl: assignments of ep-patents

Owner name: SANOFI, SOCIETE ANONYME TE PARIJS, FRANKRIJK.

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732

ITF It: translation for a ep patent filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19921023

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19921106

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19921119

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19921121

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19921126

Year of fee payment: 8

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19921130

Year of fee payment: 8

Ref country code: LU

Payment date: 19921130

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19921215

Year of fee payment: 8

EPTA Lu: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19931112

Ref country code: GB

Effective date: 19931112

Ref country code: AT

Effective date: 19931112

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19931113

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19931130

Ref country code: CH

Effective date: 19931130

Ref country code: BE

Effective date: 19931130

BERE Be: lapsed

Owner name: S.A. TECNALOR

Effective date: 19931130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19940601

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19931112

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19940802

EUG Se: european patent has lapsed

Ref document number: 85402172.2

Effective date: 19940610