EP0557598B1 - Machine de déplacement de fluide selon le principe de spirale - Google Patents

Machine de déplacement de fluide selon le principe de spirale Download PDF

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Publication number
EP0557598B1
EP0557598B1 EP92120595A EP92120595A EP0557598B1 EP 0557598 B1 EP0557598 B1 EP 0557598B1 EP 92120595 A EP92120595 A EP 92120595A EP 92120595 A EP92120595 A EP 92120595A EP 0557598 B1 EP0557598 B1 EP 0557598B1
Authority
EP
European Patent Office
Prior art keywords
input shaft
main shaft
casing
iron core
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 - Lifetime
Application number
EP92120595A
Other languages
German (de)
English (en)
Other versions
EP0557598A1 (fr
Inventor
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 EP0557598A1 publication Critical patent/EP0557598A1/fr
Application granted granted Critical
Publication of EP0557598B1 publication Critical patent/EP0557598B1/fr
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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F04C18/0223—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • 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

Definitions

  • the invention relates to a positive displacement machine for compressible media with a spiral housing arranged in a fixed housing, and with a displacement body assigned to the conveying body, consisting essentially of a disc with spiral strips arranged vertically on both sides, one opposite for guiding the displacement body relative to the housing a first eccentric arrangement with a second eccentric arrangement is provided, the guide shaft mounted in the housing is positively connected to the main shaft of the first eccentric arrangement, 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 invention has for its object to make a displacement machine of the type mentioned above can be switched off during engine operation.
  • 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.
  • the permanently rotating fan ensures ventilation and thus cooling of the encapsulated magnetic coupling insofar as, due to the special arrangement of the active fan part, the cooling air flows around the iron core in the greatest possible way and thus with the longest exposure time.
  • the fan is provided with a closed cover plate on the bearing side.
  • the bearings of the input shaft which are generally permanently lubricated roller bearings, are sealed off from the negative pressure generated by the fan. This prevents the bearings from drying out.
  • 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 skin shaft and 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.
  • the housing half 7b shown on the left in Fig. 3 is composed of two halves 7a, 7b, via fastening eyes 8 shown for receiving screw connections interconnected machine housing.
  • 9 symbolizes the holder for the drive shaft, 10 the holder for the guide shaft.
  • 11 and 11 ' denote the two delivery spaces, each offset by 180 °, which are worked into the two housing halves in the manner of a spiral slot. 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.
  • the working medium results in crescent-shaped working medium on both sides enclosing workspaces that are moved through the delivery chambers towards the outlet while the rotor is being driven. 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 has 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 which surrounds it on all sides.
  • the iron core ring is seated with an axial part 35a at its left end in a recess 38 in the bell 7d.
  • the iron core ring part 35a 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 radially extending ring web 35b forms the bearing-side boundary of the iron core ring.
  • the remaining parts of the iron core ring 35 are arranged in a rotationally fixed manner on the input shaft 21. These parts are the axially extending part 35c, which represents the radially inner boundary of the iron core ring, and the radially extending armature disk 33, which is limited in its outer diameter by the axial part 35a.
  • the two interconnected parts 35c and 33 are fastened to the input shaft 21 via spokes 34.
  • the armature disk 33 forms with its free end face, together with the free end face of an anchor ring 32, the actual clutch disks, including an air gap 44. This air gap is not recognizable, since the clutch is shown in the engaged state.
  • the armature ring 32 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. It is provided with continuous recesses 49, the outermost diameter of which corresponds to the inner diameter of the anchor ring 32.
  • 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 armature disk 33. The coupling process is thus completed and the rotary movement of the input shaft is transmitted to the main shaft.
  • the solenoid is de-energized, whereupon the leaf spring 46 retracts the anchor ring 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.
  • a shoulder is provided on the input shaft 21, which is axially displaceable to form the gap 44, against which the hub of a radial fan 45 abuts.
  • the hub bears against the inner ring 36 of the inner roller bearing 29.
  • the active part of this fan 45 i.e. the fan blades are located in a suction space 50 between the radial ring web 35b of the iron core ring and the radial part of the bell housing 7d.
  • a continuous cover plate 51 extends on the bearing side from the hub to the ends of the fan blades. By means of this cover plate 51, the storage space under atmospheric pressure is shielded from the suction space under vacuum.
  • the permanently rotating fan now draws in the cooling air from the interior of the housing cover 7c.
  • the coolant enters the suction space 50 through the recesses 49 of the driving disk 47, the free inner ring surface of the anchor ring 32 and through the spokes 34.
  • the rotating parts of the iron core ring are flowed around and cooled accordingly.
  • the armature disk 33 thanks to its large radial expansion, rotates at a relatively high peripheral speed in the well-ventilated interior of the housing cover 7c and is thus adequately cooled.
  • the cooling air flows radially outward from the suction space 50 and in the process sweeps past the radially extending annular web 35b of the iron core ring.
  • the coolant flowing out of the fan also acts on the outer surface of the housing bell 7d provided with cooling ribs 52. As a result, the heat of the axial iron core ring part 35a lying against this bell part can also be dissipated.

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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 (5)

  1. Machine de déplacement pour des fluides compressibles, avec des chambres de transport (11, 11') en forme de spirale disposées dans un boîtier fixe (7a, 7b), et avec un corps de déplacement (1-4) associé aux chambres de transport, se composant essentiellement d'un disque avec des volutes en forme de spirale disposées perpendiculairement sur ses deux faces, dans laquelle il est prévu un second dispositif excentrique (26, 27), disposé à distance par rapport à un premier dispositif excentrique (23, 24), pour le guidage du corps de déplacement par rapport au boîtier, dont l'arbre de guidage (27) supporté dans le boîtier est en liaison forcée avec l'arbre principal (24) du premier dispositif excentrique, et dans lequel l'arbre principal est entraîné par une poulie (19), caractérisée
    - en ce qu'entre l'arbre principal (24) et un arbre d'entrée (21) muni de la poulie (19), est prévu un accouplement magnétique (30), pour lequel une bobine magnétique (31) est disposée à poste fixe dans un couvercle (7c) du boîtier, une bague d'induit (32) est calée en rotation sur l'arbre principal (24) par l'intermédiaire d'un disque d'entraînement (47) et un disque d'induit (33) est calé en rotation sur l'arbre d'entrée (21),
    - et en ce que, sur l'arbre d'entrée (21), est fixé un ventilateur (45), dont la partie active se trouve entre un noyau de fer (35b) contenant la bobine magnétique (31), et le support (29) de l'arbre d'entrée (21).
  2. Machine de déplacement suivant la revendication 1, caractérisée en ce que le ventilateur (45) est pourvu d'une plaque de recouvrement fermée (51) du côté du palier.
  3. Machine de déplacement suivant la revendication 1, caractérisée en ce que le disque d'induit (33) est assemblé à l'arbre d'entrée (21) par l'intermédiaire de rayons (34).
  4. Machine de déplacement suivant la revendication 3, caractérisée en ce que le disque d'induit (33) est fixé aux rayons (34) par l'intermédiaire de la partie à orientation axiale, radialement intérieure (35c) du noyau de fer annulaire.
  5. Machine de déplacement suivant la revendication 1, caractérisée en ce que la bobine magnétique (31) est logée dans une cloche (7d) du couvercle (7c) du boîtier, le noyau de fer annulaire (35a) qui contient la bobine magnétique assurant, par son diamètre extérieur, le centrage mutuel du couvercle (7c) du boîtier avec le support de l'arbre d'entrée (21) et du boîtier (7b) du côté de l'entraînement avec le support de l'arbre principal (24).
EP92120595A 1992-02-24 1992-12-03 Machine de déplacement de fluide selon le principe de spirale Expired - Lifetime EP0557598B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4205541A DE4205541A1 (de) 1992-02-24 1992-02-24 Verdraengermaschine nach dem spiralprinzip
DE4205541 1992-02-24

Publications (2)

Publication Number Publication Date
EP0557598A1 EP0557598A1 (fr) 1993-09-01
EP0557598B1 true EP0557598B1 (fr) 1995-06-21

Family

ID=6452398

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92120595A Expired - Lifetime EP0557598B1 (fr) 1992-02-24 1992-12-03 Machine de déplacement de fluide selon le principe de spirale

Country Status (3)

Country Link
EP (1) EP0557598B1 (fr)
JP (1) JPH062674A (fr)
DE (2) DE4205541A1 (fr)

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
CN101765700B (zh) * 2007-07-26 2012-03-21 斯宾勒工程公司 具有两侧支承结构的按照螺旋原理的挤压机

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0899424B1 (fr) * 1997-08-26 2001-11-28 CRT Common Rail Technologies AG Machine de déplacement de fluide du type à spirale
DE102007043579A1 (de) * 2007-09-13 2009-03-19 Handtmann Systemtechnik Gmbh & Co. Kg Verdrängermaschine nach dem Spiralprinzip
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
CN110159528B (zh) * 2019-05-23 2020-11-17 浙江大学 一种双侧双槽并联式无油涡旋空压机
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 (6)

* 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
GB2167133B (en) * 1984-11-19 1988-04-07 Sanden Corp Scroll-type rotary fluid-machine
GB2167495B (en) * 1984-11-20 1988-11-09 Boc Group Plc Improvements in mechanical pumps
JPH0756274B2 (ja) * 1987-03-20 1995-06-14 サンデン株式会社 スクロール式圧縮機
DE3740365A1 (de) * 1987-11-27 1989-06-08 Knorr Bremse Ag Fluegelzellenverdichter fuer druckluft
DE3839252A1 (de) * 1988-11-21 1990-05-23 Asea Brown Boveri Verdraengermaschine nach dem spiralprinzip

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101765700B (zh) * 2007-07-26 2012-03-21 斯宾勒工程公司 具有两侧支承结构的按照螺旋原理的挤压机
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
EP2402611A3 (fr) * 2010-07-02 2013-06-26 Handtmann Systemtechnik GmbH & Co. KG Dispositif de chargement pour l'étanchéification d'air de suralimentation pour un moteur à combustion interne

Also Published As

Publication number Publication date
DE59202624D1 (de) 1995-07-27
DE4205541A1 (de) 1993-08-26
EP0557598A1 (fr) 1993-09-01
JPH062674A (ja) 1994-01-11

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