EP0545189B1 - Machine de déplacement de fluide du type à spirale - Google Patents

Machine de déplacement de fluide du type à spirale Download PDF

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Publication number
EP0545189B1
EP0545189B1 EP19920119876 EP92119876A EP0545189B1 EP 0545189 B1 EP0545189 B1 EP 0545189B1 EP 19920119876 EP19920119876 EP 19920119876 EP 92119876 A EP92119876 A EP 92119876A EP 0545189 B1 EP0545189 B1 EP 0545189B1
Authority
EP
European Patent Office
Prior art keywords
housing
shaft
primary shaft
main shaft
housing cover
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
EP19920119876
Other languages
German (de)
English (en)
Other versions
EP0545189A1 (fr
Inventor
Gregor Jetzer
Roland Kolb
Fritz Spinnler
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.)
Aginfor AG
Original Assignee
Aginfor AG fuer industrielle Forschung
Aginfor AG
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 Aginfor AG fuer industrielle Forschung, Aginfor AG filed Critical Aginfor AG fuer industrielle Forschung
Publication of EP0545189A1 publication Critical patent/EP0545189A1/fr
Application granted granted Critical
Publication of EP0545189B1 publication Critical patent/EP0545189B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines

Definitions

  • the invention relates to a displacer for compressible media with at least one spiral-like conveying chamber arranged in a fixed housing and with a spiral-like displacer associated with this conveying chamber, which is held on a disk-shaped rotor which can be driven eccentrically with respect to the housing in such a way that during operation each of its points is one of performs limited circular movement of the peripheral walls of the delivery chamber, and its curvature relative to that of the delivery chamber is dimensioned such that it almost touches the inner and outer peripheral walls of the delivery chamber on at least one sealing line that progresses continuously during operation, one opposite to guide the rotor relative to the housing a first eccentric arrangement at a distance from the second eccentric arrangement is provided, the guide shaft of which is mounted in the housing with the main shaft of the first eccentric arrangement is positively connected, and wherein the main shaft is driven by a pulley.
  • Displacement machines of the spiral type are known for example from DE-C-26 03 462.
  • a compressor constructed according to this principle is characterized by an almost pulsation-free conveyance of the gaseous working medium, which consists, for example, of air or an air-fuel mixture, and could therefore also be used with advantage for charging purposes of internal combustion engines, among other things.
  • the gaseous working medium which consists, for example, of air or an air-fuel mixture
  • the gaseous working medium which consists, for example, of air or an air-fuel mixture
  • the two peripheral walls of the displacement chamber which move from the inlet through the displacement chamber to the outlet, their volume constantly decreasing and the pressure of the work equipment is increased accordingly.
  • a machine of the type mentioned at the outset is known from DE-A-3 313 000.
  • a guide shaft of the second eccentric arrangement mounted in the housing is positively connected to the drive shaft via a toothed belt drive.
  • the main eccentric shaft is usually driven directly by a belt from the crankshaft of the internal combustion engine, usually an internal combustion engine.
  • a disadvantage of this type of drive, which is permanently engaged, is the loss of frictional power remaining in the partial load region, in which charging of the internal combustion engine is not required. This also applies in the event that excess air is blown at partial load.
  • displacement machines with a magnetic coupling between the pulley and the main shaft are already known (for example from EP-A-0 123 407), in which the air gap cannot be adjusted.
  • the invention is therefore based on the object of designing a displacement machine of the type mentioned at the outset to be switched off during engine operation.
  • an adjustable magnetic coupling is arranged between the main shaft and an input shaft provided with the drive pulley, a magnetic coil being arranged in a stationary manner in a housing cover and an anchor ring being connected in a rotationally fixed manner to the main shaft, and for the purpose of adjusting the air gap between the armature ring and a washer arranged on the input shaft, the input shaft is mounted axially displaceably in the housing cover.
  • connection concept is particularly suitable for orbiting machines because of the low moment of inertia of the rotating rotor. Acceleration shocks can also be handled with magnetic couplings of small dimensions.
  • Commercially available magnetic clutches are usually offered as a structural unit in which the air gap cannot be adjusted. Since, however, the size of the air gap is decisive for the correct functioning of the connection, it is advantageous to make the input shaft, which is in operative connection with the anchor ring via the holding disk, movable and thus adjustable.
  • the input shaft is mounted in the housing cover by means of a roller bearing, the inner ring of the roller bearing having a sliding seat on the input shaft, and if the input shaft is arranged by means of spring elements which are arranged between the inner ring of the roller bearing and a shoulder of the input shaft. is tense. This ensures the adjustability and adjustability of the air gap. This concept can avoid the otherwise required large number of narrow axial tolerances which the components determining the air gap would have to have.
  • the magnetic coil is housed in a bell on the housing cover.
  • the outer diameter of the iron core ring receiving the coil can then take over the mutual centering of the housing cover with the mounting of the input shaft and the drive-side housing with the mounting of the main shaft. This measure ensures the coaxiality of the input shaft and the chewing shaft and that the belt tension can be easily transferred to the housing via the centering points.
  • FIGS. 1 and 2 For the sake of clarity, the machine is shown in FIGS. 1 and 2 in the disassembled state.
  • the rotor of the machine is designated as a whole by 1.
  • two spiral-shaped displacers are arranged, which are offset by 180 ° to one another. These are strips 3, 3 'which are held vertically on the pane 2.
  • the spirals themselves are formed from a plurality of circular arcs adjoining one another. 4 with the hub is designated with which the disc 2 is mounted on a roller bearing 22. This bearing sits on an eccentric disk 23, which in turn is part of the main shaft 24. 5 with a radially outside of the strips 3, 3 'is designated for receiving a guide bearing 25 which is mounted on an eccentric bolt 26. This is in turn part of a guide shaft 27.
  • two openings 6 are provided in the disk so that the medium can get from one disk side to the other, for example in order to be drawn off in a central outlet 13 (FIG. 3) which is only arranged on one side.
  • FIG. 1 shows the housing half 7b shown on the left in FIG. 3 of the machine housing which is composed of two halves 7a, 7b and is connected to one another via fastening eyes 8 for receiving screw connections.
  • 9 symbolizes the holder for the drive shaft, 10 the holder for the guide shaft.
  • 11 and 11 ' denote the two in each case by 180 ° against each other staggered delivery spaces, which are incorporated in the manner of a spiral slot in the two housing halves. They each run from an inlet 12, 12 'arranged on the outer circumference of the spiral in the housing to an outlet 13 provided in the interior of the housing and common to both delivery spaces.
  • the drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements 23, 24 and. 26, 27.
  • the main shaft 24 is mounted in the roller bearing 17 and in the slide bearing 18.
  • Counterweights 20 are arranged on it to compensate for the inertial forces arising when the rotor is eccentrically driven.
  • the guide shaft 27 is inserted in a sliding bearing 28 within the housing half 7b.
  • the two eccentric arrangements are synchronized with precise angles. This is done via a toothed belt drive 16.
  • the double eccentric drive ensures that all points of the rotor disk and thus also all points of the two strips 3, 3 'perform a circular displacement movement.
  • crescent-shaped work spaces enclosing the working medium result on both sides of the strips, which are displaced by the delivery chambers during the drive of the rotor disk in the direction of the outlet .
  • the volumes of these working spaces decrease and the pressure of the working fluid is increased accordingly.
  • an adjustable magnetic coupling 30 is now installed between the input shaft 21 and the main shaft 24 according to the invention.
  • the housing cover 7c which is connected to the drive-side housing part 7b via the screw connection 39, is provided with a bell 7d.
  • the two roller bearings 29 for supporting the input shaft 21 with their outer rings are pressed into the central bore of this bell.
  • the bearings 29 are located in the plane of the drive pulley 19.
  • This pulley is connected to the input shaft 21 in a rotationally fixed manner via its hub 40 and a thread.
  • An additional anti-rotation device is provided in the form of a weld 41 between the hub and the shaft.
  • the input shaft is guided with a sliding fit in the inner rings 36 of the roller bearings and is therefore axially movable.
  • the magnetic coupling consists of a magnetic coil 31 which is arranged in a stationary manner in the housing cover 7c.
  • the magnetic coil is embedded in an iron core ring 35.
  • the iron core ring With its outer diameter, the iron core ring sits at one end in a recess 38 in the bell 7d. At its other end, the iron core ring sits with its outer diameter in a recess 42, which is incorporated in a support element 43 connected to the housing part 7b.
  • the iron core ring 35 thus fulfills a centering function for the housing cover 7c and the drive-side housing part 7b.
  • a shoulder 45 is provided on the axially displaceable input shaft 21, by means of which the shaft is braced with the housing cover.
  • the bracing is carried out via spring elements 34, here two disc springs, and via the inner rings 36 of the roller bearings 29.
  • a holding disk 33 Arranged on the input shaft 21 in the area of the magnetic coupling is a holding disk 33, the outer diameter of which is limited by the iron core ring.
  • This in Fig. 4 in Disc shown in section forms on its free face together with the free face of an anchor ring 32, the air gap 44. This air gap is not visible in Fig. 4, since the clutch is shown in the engaged state.
  • the anchor ring is in turn connected to the main shaft 24 in a rotationally fixed manner. This is done via a leaf spring 46, which is connected on the one hand to the anchor ring 32 and on the other hand to a drive plate 47 with fastening means, in the present case screws 48.
  • the connection is designed such that the armature ring 32 can move axially away from the drive plate 47 against the return force of the spring 46.
  • the drive plate 47 is rigidly attached to the main shaft 24 by conventional means.
  • the device works as follows: if, for example, the vehicle is driven from part load to full load, the magnet coil 31 is energized. The armature ring 32 is attracted by the magnet against the return force of the spring 46, bridges the air gap 44 and comes into contact with the holding disk 33. The coupling process is thus completed and the rotary movement of the input shaft is transmitted to the main shaft. When the main shaft is taken out of operation, the magnet coil is switched off, whereupon the leaf spring 46 pulls the armature ring back against the drive plate 47 and thereby restores the air gap 44. The activation and deactivation can take place automatically as a function of any suitable or process size.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Claims (3)

  1. Machine de déplacement pour des fluides compressibles avec au moins une chambre de transport (11, 11') en forme de spirale disposée dans un corps fixe (7a, 7b) et avec un corps de déplacement (1-4) an forme de spirale associé à la chambre de transport, qui est calé sur un rotor (1) en forme de disque pouvant être actionné de manière excentrique par rapport au corps de telle façon que, pendant le fonctionnement, chacun de ses points décrive un mouvement circulaire limité par les flancs de la chambre de transport et dont la courbure est dimensionnée par rapport à celle de la chambre de transport de telle façon qu'il touche presque les flancs intérieurs et extérieurs de la chambre de transport chacun suivant au moins une ligne d'étanchéité se déplaçant continuellement au cours du fonctionnement, dans laquelle il est prévu, pour le guidage du rotor par rapport au corps, un second dispositif excentrique (26, 27) disposé à distance par rapport à un premier dispositif excentrique (23, 24) et dont l'arbre de guidage (27) supporté dans le corps est en liaison forcée avec l'arbre principal (24) du premier dispositif excentrique, et dans laquelle l'arbre principal (24) est entraîné par l'intermédiaire d'une poulie (19), caractérisée en ce qu'entre l'arbre principal (24) et un, arbre d'entrée (21) pourvu de la poulie (19) est disposé un accouplement magnétique réglable (30), dans lequel une bobine magnétique (31) est disposée à poste fixe dans un couvercle (7c) du corps et un anneau d'induit (32) est calé en rotation sur l'arbre principal (24), et dans lequel l'arbre d'entrée (21) est mobile axialement dans le couvercle (7c) du corps dans le but de régler l'entrefer entre l'anneau d'induit (32) et un disque de maintien (33) disposé sur l'arbre d'entrée (21).
  2. Machine de déplacement suivant la revendication 1, caractérisée en ce que l'arbre d'entrée (21) est supporté dans le couvercle (7c) du corps au moyen d'un palier à roulement (29), dans lequel la bague intérieure (36) du palier à roulement est posée avec un ajustement appuyé sur l'arbre d'entrée (21), et en ce que l'arbre d'entrée (21) est maintenu au moyen d'éléments élastiques (34), qui sont disposés entre la bague intérieure (36) du palier à roulement et un épaulement (45) de l'arbre d'entrée (21).
  3. Machine de déplacement suivant la revendication 1, caractérisée en ce que la bobine magnétique (31) est placée dans une cloche (7d) du couvercle (7c) du corps, le noyau de fer annulaire (35) qui contient la bobine assurant par son diamètre extérieur le centrage mutuel du couvercle (7c) du corps avec le palier de l'arbre d'entrée (21) et du corps (7b) situé du côté du moteur avec le palier de l'arbre principal (24).
EP19920119876 1991-12-05 1992-11-23 Machine de déplacement de fluide du type à spirale Expired - Lifetime EP0545189B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3578/91 1991-12-05
CH357891 1991-12-05

Publications (2)

Publication Number Publication Date
EP0545189A1 EP0545189A1 (fr) 1993-06-09
EP0545189B1 true EP0545189B1 (fr) 1995-09-13

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920119876 Expired - Lifetime EP0545189B1 (fr) 1991-12-05 1992-11-23 Machine de déplacement de fluide du type à spirale

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EP (1) EP0545189B1 (fr)
DE (1) DE59203676D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402611A2 (fr) 2010-07-02 2012-01-04 Handtmann Systemtechnik GmbH & Co. KG Dispositif de chargement pour l'étanchéification d'air de suralimentation pour un moteur à combustion interne

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8464697B2 (en) * 2010-08-13 2013-06-18 Eaton Corporation Integrated clutch supercharger
US9086012B2 (en) 2010-08-13 2015-07-21 Eaton Corporation Supercharger coupling
EP2940337B1 (fr) * 2014-04-30 2018-06-27 Volvo Car Corporation Agencement d'embrayage de surcompresseur
CN116928096B (zh) * 2023-08-11 2024-03-15 广州市光裕汽车空调制造有限公司 一种高速高扭矩汽车空调涡旋压缩机

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2127011A1 (de) * 1971-06-01 1972-12-14 Robert Bosch Gmbh, 7000 Stuttgart Verdichter
JPS58144687A (ja) * 1982-02-24 1983-08-29 Nissan Motor Co Ltd 可変容量ロ−タリ−コンプレツサ
JPS59142483U (ja) * 1983-03-15 1984-09-22 サンデン株式会社 スクロ−ル型圧縮機の回転阻止機構
DE3313000A1 (de) * 1983-04-12 1984-10-18 Volkswagenwerk Ag, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien
DE3740365A1 (de) * 1987-11-27 1989-06-08 Knorr Bremse Ag Fluegelzellenverdichter fuer druckluft

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402611A2 (fr) 2010-07-02 2012-01-04 Handtmann Systemtechnik GmbH & Co. KG Dispositif de chargement pour l'étanchéification d'air de suralimentation pour un moteur à combustion interne
DE102011103165A1 (de) 2010-07-02 2012-01-05 Handtmann Systemtechnik Gmbh & Co. Kg Ladevorrichtung zur Verdichtung von Ladeluft für einen Verbrennungsmotor

Also Published As

Publication number Publication date
DE59203676D1 (de) 1995-10-19
EP0545189A1 (fr) 1993-06-09

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