EP0101345A1 - Screw compressor - Google Patents

Screw compressor Download PDF

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Publication number
EP0101345A1
EP0101345A1 EP83401448A EP83401448A EP0101345A1 EP 0101345 A1 EP0101345 A1 EP 0101345A1 EP 83401448 A EP83401448 A EP 83401448A EP 83401448 A EP83401448 A EP 83401448A EP 0101345 A1 EP0101345 A1 EP 0101345A1
Authority
EP
European Patent Office
Prior art keywords
rotor
compressor according
compressor
rotors
recess
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.)
Granted
Application number
EP83401448A
Other languages
German (de)
French (fr)
Other versions
EP0101345B1 (en
Inventor
Jean-Jacques Carre
Pierre Courbot
Roland Levrai
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.)
Bendix France SA
Original Assignee
Bendix France SA
DBA 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 Bendix France SA, DBA SA filed Critical Bendix France SA
Publication of EP0101345A1 publication Critical patent/EP0101345A1/en
Application granted granted Critical
Publication of EP0101345B1 publication Critical patent/EP0101345B1/en
Expired 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/086—Carter
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating

Definitions

  • the present invention relates to compressors and, more particularly, to volumetric screw compressors or blowers.
  • Screw compressors traditionally comprise at least one cooperating pair of parallel rotors with helical threads rotating in synchronism, by means of distribution gears, in two cylindrical chambers interconnecting longitudinally.
  • This type of compressor of generally robust design, is used in industrial applications to provide pressures of the order of several bars per stage. Therefore, the rotors are usually cut in one piece with their shaft or, as described for example in French Patent No. 1,243,471, have a hollow hub and are fitted on a long shaft projecting from both sides. 'other of the longitudinal ends of the rotor to rotate in bearings of the housing and allow the mounting of the distribution gears.
  • the rotors of this type have a high inertia, generally accentuated by the number of helical threads for obtaining high pressure rates, so that the compressor is driven on the main or male rotor, with thick thread bodies, which does most of the compression work.
  • the object of the present invention is to propose a screw compressor designed for the supply of low overpressures, less than 1 bar, of particularly compact structure, with rotary assemblies of low inertia, providing good volumetric efficiency, in particular at low speed, and allowing a mass production, in particular for use in the field of volumetric supercharging internal combustion engines.
  • the screw compressor of the type comprising a housing defining two parallel cylindrical chambers intercommunicating longitudinally and closed, at one end, by a rear bottom wall of the housing, as well as passages of 'inlet and outlet of the fluid communicating with the chambers, two rotors with helical threads with hollow hub, the hub of each rotor being supported and driven in rotation by a shaft means having a first end swiveling in a partition attached to the front of the housing and closing the two chambers opposite said rear bottom wall, these first ends being coupled by cooperating toothed wheels, is characterized in that each rotor hub comprises a longitudinal longitudinal traversing, each shaft means comprising a rear bearing assembly received in the corresponding end of the recess of the rotor hub, and mounted in leaktight manner on an axis element fixed on the rear bottom wall of the housing , and a front shaft element, passing through the front partition, secured to the corresponding rotor and extending in the front part of the
  • each rotor has a hollow hub and the shaft line of each rotor is broken down into two separate end parts, thus making it possible to significantly reduce the inertia of each assembly rotating the axial dimensions of the compressor which can be considerably reduced, in particular due to the integration of the rear bearing assembly into the internal through recess of the rotor hub.
  • the movement input is via the front shaft element of the female rotor, which thus causes an increase, proportional to the ratio of the number of teeth of the toothed wheels for driving the male and female rotors, of the rotation of the male rotor and, therefore, of the displacement per revolution of the compressor.
  • the rotary screw compressor of the type comprising a male rotor and a female rotor arranged in two parallel intercommunicating chambers formed in. a housing and closed, at their axially opposite ends, by a rear front partition and a front front partition, each rotor being supported and driven in rotation by a shaft means comprising a first end passing through the front partition, these first ends being provided of cooperating toothed wheels for the synchronous drive of the rotors, is characterized in that at least the internal walls of the chambers - and advantageously also the walls of the threads of the rotors, are coated with an extra layer of coating material erodible containing dry lubricant particles, the drive gear wheels being mutually coupled without angular play.
  • the compressor comprises a housing body 1, of substantially parallelepiped shape, open at one end and closed at the other end by a rear bottom wall 2, the body housing 1 defining two parallel cylindrical chambers 3 and 4 interconnecting longitudinally.
  • a male rotor body 5 and a female rotor body 6 respectively.
  • the male rotor body 5 comprises four helical threads
  • the female rotor body comprising six helical threads.
  • the male rotor 5 and female rotor 6 bodies are hollow and crossed by a longitudinal recess 7 and 8, respectively, ending, at the rear end, by a cylindrical seat 9 forming an internal shoulder 10 and intended to receive an assembly rear bearing 11 fixed to the rear wall 2.
  • Each rear bearing assembly 11 comprises a tubular axis 12, on the front end of which is mounted a bearing 13 whose inner cage is locked against a shoulder 14 of the axis by the head of a screw 15 whose threaded end screwed into the tubular axis 12 projects from the rear wall 2 to receive, in the embodiment shown, a nut 16 ensuring the blocking of the rear bearing assembly 11 on this rear wall 2, against the internal face of which bears an end shoulder 17 of the axis element 12.
  • the rear bearing 13 of each rotor 5 or 6 is thus placed inside the latter, between internal staff 9 and the element nt axis 12 which itself is mounted cantilever on the rear wall 2 by means of the screw 15 which passes entirely through it. As shown in FIG.
  • a seal 18 is also disposed between the axis element 12 and the internal bearing 9, inside the recess of the rotor, this seal being held in the axial position, for example by a ring 19 screwed into an internal thread of the end of the internal smooth surface 9.
  • the male rotor 5 and female rotor 6 bodies have their front ends fixed to a front shaft element 20 and 21, respectively.
  • Each front shaft element 20, 21 has a head of enlarged diameter 22, having for example peripheral grooves, fitted, in the example shown, into a cylindrical enlarged mounting part 23 of the front part of the internal recess 7 or 8 defining an abutment shoulder 24 directed towards the front, against which it carries the front end of the enlarged head 22 of the shaft elements 20 and 21.
  • the enlarged head 22 of the elements shaft 20 or 21 is locked in the corresponding retor body by a ring 25 screwed into a thread in the front end part of the recess 7 or 8 of the rotor body.
  • the chambers 3 and 4 are closed, on the front side, by a front partition 26, belonging for example to a front housing element 27 defining the housings for the synchronous drive gears of the rotors.
  • the front partition 26 comprises a projecting tubular part 28 extending in the widened front end part of the recess 7 of the male rotor body 5 and forming a smooth bearing for a bearing 29 and a seal 30 mounted on the front shaft element 20, the outer end portion 31 of which protrudes forward, beyond the front wall 26, for mounting, in the embodiment shown, two coaxial gear take-up wheels clearance 32 and 33 necessary to avoid the driving contacts between the rotor threads 3 and 4 and cooperating in meshing with a driving toothed wheel 34 fixed on the end part 35 of the shaft element 21 of the rotor female 6 projecting forwardly beyond the front partition 26 and extended, in this direction, for mounting a pulley 36 intended to be coupled to the motor drive device of the compressor.
  • the toothed wheel 34 has a hub 37 fitted on the shaft element 21 and on which are mounted a bearing 38 and a seal 39 bearing externally on corresponding bearing surfaces formed by the front partition 26, at minus the area of the seal 39 being at least partially integrated in the front part of the recess 8 of the rotor 6.
  • the housings of the timing gears 34 and 32-33 are closed by a front cover 40, a seal 41 being disposed between a bearing surface of this front cover 40 and the end part 35 of the shaft element 21 of the female rotor 6. It will be noted, in particular in relation to the male rotor 5, that the front seals 30 and 39 are substantially integrated into the interior space of the housing defined by the front partition 26.
  • the ratio of the original diameters of the toothed wheels of distribution 34 and 32, 33 is the same as the ratio of the number of helical threads of the rotors 5 and 6.
  • the drive being effected by the female rotor 6, via the toothed wheel attack 34, this results in a 50% increase in the speed of rotation of the male rotor 5, namely, for an input speed of pulley 36 of 15,000 revolutions per minute, a speed of rotation of the rotor male 5 of 22,500 rpm, which is allowed by reducing the inertia of the rotating assemblies.
  • the front shaft elements 20 and 21 are partially hollow and have internal recesses 42 and 43,. respectively, these shaft elements being produced for example by cold stamping.
  • the housing body 1 can be made in two parts, with a joint plane at the level of the rear bottom wall 2.
  • FIG. 1 an embodiment is shown with the intake 45 and exhaust 46 lights made on the central box body 1, on either side of it, these lights being able to be made in variant on the faces of the casing or on a face and a zone of the housing 1.
  • the compressor arrangement according to the invention makes it possible to produce the rotor bodies 5 and 6 in light alloy, in particular based on aluminum, but also, taking into account the compressor class considered, in rigid plastic material, for example. in phenolic resin or polyamides with glass fillers.
  • the design of the two-part shaft lines according to the invention also makes it possible, in this case, to produce the rotor bodies 5 and 6 by overmolding on the corresponding front shaft elements 20 and 21, thus ensuring immediate attachment between these crews.
  • the walls of the chambers 3 and 4, as well as the surfaces of the threads of the rotors 5 and 6, are, prior to mounting, coated, as shown in 50, with an extra layer of a coating material erodible by the adjacent external surface areas of the cooperating elements.
  • This arrangement makes it possible to largely overcome the problems of machining tolerance during assembly, the rotor threads ensuring, by lapping effect, their passage through the thickness of the erodible coating material of the walls of the housing and, between them, the optimal cooperation between male and female threads for automatically obtaining the necessary functional clearance between the threads of the rotors.
  • the erodible coating material contains particles of dry lubricant ensuring flexible operation and without significant heating of the compressor .
  • the erodible coating material consists for example of a combination of a resin, a dissolved graphite binder and / or of in a volatile solvent, of molybdenum / disulphide particles and is applied by immersion, brushing or spraying.

Abstract

Le compresseur, à ensembles tournants de faible inertie et à structure compacte, comprend deux rotors creux (5 ; 6), réalisés par exemple en matériau plastique, fixés respectivement sur un élément d'arbre avant (20 ; 21) tourillonnant dans une cloison avant (26) et supportés chacun, à l'arrière, par un ensemble de palier arrière (11) fixé sur la paroi frontale arrière (2) et entièrement intégré dans l'évidement interne (7 ; 8) du rotor. L'entraînement s'effectue par le rotor femelle (6).The compressor, with low inertia rotary assemblies and compact structure, comprises two hollow rotors (5; 6), made for example of plastic material, fixed respectively on a front shaft element (20; 21) journalled in a front partition (26) and each supported at the rear by a rear bearing assembly (11) fixed to the rear front wall (2) and fully integrated in the internal recess (7; 8) of the rotor. The drive is carried out by the female rotor (6).

Description

La présente invention concerne les compresseurs et, plus particulièrement, les compressuers ou soufflantes volumétriques à vis.The present invention relates to compressors and, more particularly, to volumetric screw compressors or blowers.

Les compresseurs à vis comprennent traditionnellement au moins une paire coopérante de rotors parallèles à filets hélicoïdaux tournant en synchronisme, au moyen d'engrenages de distribution, dans deux chambres cylindriques intercommuniquant longitudinalement. Ce type de compresseurs, de conception généralement robuste, est utilisé dans des applications industrielles pour fournir des pressions de l'ordre de plusieurs bars par étage. De ce fait, les rotors sont habituellement taillés d'une seule pièce avec leur arbre ou, comme décrit par exemple dans le brevet français N° 1 243 471, présentent un moyeu creux et sont emmanchés sur un arbre long faisant saillie de part et d'autre des extrémités longitudinales du rotor pour tourillonner dans des paliers du carter et permettre le montage des engrenages de distribution. Dans tous les cas, les rotors de ce type présentent une inertie importante, généralement accentuée par le nombre de filets hélicoïdaux pour l'obtention de taux de pression élevés, de sorte que l'entraînement du compresseur se fait sur le rotor principal ou mâle,à corps de filets épais,qui effectue la plus grande partie du travail de compression.Screw compressors traditionally comprise at least one cooperating pair of parallel rotors with helical threads rotating in synchronism, by means of distribution gears, in two cylindrical chambers interconnecting longitudinally. This type of compressor, of generally robust design, is used in industrial applications to provide pressures of the order of several bars per stage. Therefore, the rotors are usually cut in one piece with their shaft or, as described for example in French Patent No. 1,243,471, have a hollow hub and are fitted on a long shaft projecting from both sides. 'other of the longitudinal ends of the rotor to rotate in bearings of the housing and allow the mounting of the distribution gears. In all cases, the rotors of this type have a high inertia, generally accentuated by the number of helical threads for obtaining high pressure rates, so that the compressor is driven on the main or male rotor, with thick thread bodies, which does most of the compression work.

La présente invention a pour objet de proposer un compresseur à vis conçu pour la fourniture de faibles surpressions, inférieures à 1 bar, de structure particulièrement compacte, à ensembles tournants de faible inertie, fournissant un bon rendement volumétrique, notamment à bas régime, et permettant une production en grande série, notamment pour une' utilisation dans le domaine de la suralimentation volumétrique de moteurs thermiques.The object of the present invention is to propose a screw compressor designed for the supply of low overpressures, less than 1 bar, of particularly compact structure, with rotary assemblies of low inertia, providing good volumetric efficiency, in particular at low speed, and allowing a mass production, in particular for use in the field of volumetric supercharging internal combustion engines.

Pour ce faire, selon une caractéristique de l'invention, le compresseur à vis, du type comprenant un boîtier définissant deux chambres parallèles cylindriques intercommuniquant longitudinalement et fermées, à une extrémité, par une paroi de fond arrière du boîtier, ainsi que des passages d'entrée et de sortie du fluide communiquant avec les chambres, deux rotors à filets hélicoïdaux à moyeu creux, le moyeu de chaque rotor étant supporté et entraîné en rotation par un moyen d'arbre comportant une première extrémité tourillonnant dans une cloison rapportée sur l'avant du boîtier et fermant les deux chambres à l'opposé de ladite paroi de fond arrière, ces premières extrémités étant couplées par des roues dentées coopérantes, est caractérisé en ce que chaque moyeu de rotor comprend un évidenient longitudinal traversant, chaque moyen d'arbre comprenant un ensemble de palier arrière reçu dans l'extrémité correspondante de l'évidement du moyeu de rotor, et monté de façon étanche sur un élément d'axe fixé sur la paroi de fond arrière du boitier,et un élément d'arbre avant, traversant la cloison avant, solidarisé au rotor correspondant et s'étendant dans la partie avant de l'évidement du moyeu du rotor.To do this, according to a characteristic of the invention, the screw compressor, of the type comprising a housing defining two parallel cylindrical chambers intercommunicating longitudinally and closed, at one end, by a rear bottom wall of the housing, as well as passages of 'inlet and outlet of the fluid communicating with the chambers, two rotors with helical threads with hollow hub, the hub of each rotor being supported and driven in rotation by a shaft means having a first end swiveling in a partition attached to the front of the housing and closing the two chambers opposite said rear bottom wall, these first ends being coupled by cooperating toothed wheels, is characterized in that each rotor hub comprises a longitudinal longitudinal traversing, each shaft means comprising a rear bearing assembly received in the corresponding end of the recess of the rotor hub, and mounted in leaktight manner on an axis element fixed on the rear bottom wall of the housing , and a front shaft element, passing through the front partition, secured to the corresponding rotor and extending in the front part of the recess of the rotor hub.

Avec cet agencement, chaque rotor comporte un moyeu creux et la ligne d'arbre de chaque rotor est décomposée en deux parties d'extrémité distinctes, permettant ainsi de réduire notablement l'inertie de chaque ensemble tournant l'encombrement axial du compresseur pouvant être considérablement réduit, notamment du fait de l'intégration de l'ensemble de palier arrière dans l'évidement interne traversant du moyeu de rotor. Du fait de la faible inertie des ensembles tournants, qui peut être encore réduite en réalisant les rotors en matériau plastique, avantageusement surmoulé sur l'élément d'arbre avant, conformément à une autre caractéristique de l'invention, concourant à la réduction d'encombrement du compresseur, l'entrée de mouvement se fait par l'élément d'arbre avant du rotor femelle, ce qui provoque ainsi un accroissement, proportionnel au rapport du nombre de dents des roues dentées d'entraînement des rotors mâle et femelle, de la rotation du rotor mâle et, donc, de la cylindrée par tour du compresseur.With this arrangement, each rotor has a hollow hub and the shaft line of each rotor is broken down into two separate end parts, thus making it possible to significantly reduce the inertia of each assembly rotating the axial dimensions of the compressor which can be considerably reduced, in particular due to the integration of the rear bearing assembly into the internal through recess of the rotor hub. Due to the low inertia of the rotating assemblies, which can be further reduced by making the rotors made of plastic material, advantageously overmolded on the front shaft element, in accordance with another characteristic of the invention, contributing to the reduction of size of the compressor, the movement input is via the front shaft element of the female rotor, which thus causes an increase, proportional to the ratio of the number of teeth of the toothed wheels for driving the male and female rotors, of the rotation of the male rotor and, therefore, of the displacement per revolution of the compressor.

Selon une autre caractéristique de l'invention, le compresseur volumétrique à vis, du type comprenant un rotor mâle et un rotor femelle disposés dans deux chambres parallèles intercommunicantes formées dans. un boîtier et fermées, à leurs extrémités axialement opposées, par une cloison frontale arrière et une cloison frontale avant, chaque rotor étant supporté et entraîné en rotation par un moyen d'arbre comportant une première extrémité traversant la cloison avant, ces premières extrémités étant munies de roues dentées coopérantes pour l'entraînement synchrone des rotors, est caractérisé en ce qu'au moins les parois internes des chambres - et avantageusement également les parois des filets des rotors, sont revêtues d'unè couche en surépaisseur d'un matériau de revêtement érodable contenant des particules de lubrifiant sec, les roues dentées d'entraînement étant couplées mutuellement sans jeu angulaire.According to another characteristic of the invention, the rotary screw compressor, of the type comprising a male rotor and a female rotor arranged in two parallel intercommunicating chambers formed in. a housing and closed, at their axially opposite ends, by a rear front partition and a front front partition, each rotor being supported and driven in rotation by a shaft means comprising a first end passing through the front partition, these first ends being provided of cooperating toothed wheels for the synchronous drive of the rotors, is characterized in that at least the internal walls of the chambers - and advantageously also the walls of the threads of the rotors, are coated with an extra layer of coating material erodible containing dry lubricant particles, the drive gear wheels being mutually coupled without angular play.

De cette façon, le montage du compresseur s'effectue très simplement et rapidement, en limitant les jeux résultant. de variations de tolérance et sans poser, par la suite, problèmes particuliers de calage angulaire entre les rotors, permettant ainsi une production en grande série, convenant notamment à l'industrie automobile.In this way, the mounting of the compressor takes place very simply and quickly, limiting the resulting clearances. tolerance variations and without subsequently posing particular problems of angular setting between the rotors, thus allowing mass production, particularly suitable for the automotive industry.

D'autres caractéristiques et avantages de la présente invention ressortiront de la description suivante d'un mode de réalisation, donnée à titre illustratif mais nullement limitatif, faite en relation avec les dessins annexés, sur lesquels :

  • - la figure 1 est une vue en plan d'un compresseur volumétrique selon l'invention ;
  • - la figure 2 est une vue similaire mais en coupe longitudinale ; et
  • - la figure 3 est une vue en coupe transversale suivant la ligne III-III de la figure 2.
Other characteristics and advantages of the present invention will emerge from the following description of an embodiment, given by way of illustration but in no way limiting, made in relation to the appended drawings, in which:
  • - Figure 1 is a plan view of a positive displacement compressor according to the invention;
  • - Figure 2 is a similar view but in longitudinal section; and
  • - Figure 3 is a cross-sectional view along line III-III of Figure 2.

Comme représenté sur les dessins, le compresseur selon l'invention comprend un corps de boîtier 1, d'allure sensiblement parallélipé- dique, ouvert à une extrémité et fermé, à l'autre extrémité, par une paroi de fond arrière 2, le corps de boîtier 1 définissant deux chambres parallèles cylindriques 3 et 4 intercommuniquant longitudinalement. Dans les chambres 3 et 4 sont reçus respectivement un corps de rotor mâle 5 et un corps de rotor femelle 6, respectivement. Dans l'exemple représenté, le corps de rotor mâle 5 comprend quatre filets hélicoïdaux, le corps de rotor femelle comprenant six filets hélicoïdaux. Les corps de rotor mâle 5 et de rotor femelle 6 sont creux et traversés par un évidement longitudinal 7 et 8, respectivement, se terminant, à l'extrémité arrière, par une portée cylindrique 9 formant un épaulement interne 10 et destinée à recevoir un ensemble de palier arrière 11 fixé sur la paroi arrière 2. Chaque ensemble de palier arrière 11 comprend un axe tubulaire 12,sur l'extrémité avant duquel est monté un roulement 13 dont la cage intérieure est bloquée contre un épaulement 14 de l'axe par la tête d'une vis 15 dont l'extrémité filetée vissée dans l'axe tubulaire 12 fait saillie hors de la paroi arrière 2 pour recevoir, dans le mode de réalisation représenté, un écrou 16 assurant le blocage de l'ensemble de palier arrière 11 sur cette paroi arrière 2, contre la face interne de laquelle vient porter un épaulement d'extrémité 17 de l'élément d'axe 12. Le roulement arrière 13 de chaque rotor 5 ou 6 est ainsi disposé à l'intérieur de ce dernier, entre la portée interne 9 et l'élément d'axe 12 qui lui-même est monté en porte-à-faux sur la'paroi arrière 2 au moyen de la vis 15 qui le traverse entièrement. Comme représenté sur la figure 2, un joint 18 est également disposé entre l'élément d'axe 12 et la portée interne 9, à l'intérieur de l'évidement du rotor, ce joint étant maintenu en position axiale, par exemple par une bague 19 vissée dans un taraudage de l'extrémité de la portée lisse interne 9.As shown in the drawings, the compressor according to the invention comprises a housing body 1, of substantially parallelepiped shape, open at one end and closed at the other end by a rear bottom wall 2, the body housing 1 defining two parallel cylindrical chambers 3 and 4 interconnecting longitudinally. In chambers 3 and 4 are received respectively a male rotor body 5 and a female rotor body 6, respectively. In the example shown, the male rotor body 5 comprises four helical threads, the female rotor body comprising six helical threads. The male rotor 5 and female rotor 6 bodies are hollow and crossed by a longitudinal recess 7 and 8, respectively, ending, at the rear end, by a cylindrical seat 9 forming an internal shoulder 10 and intended to receive an assembly rear bearing 11 fixed to the rear wall 2. Each rear bearing assembly 11 comprises a tubular axis 12, on the front end of which is mounted a bearing 13 whose inner cage is locked against a shoulder 14 of the axis by the head of a screw 15 whose threaded end screwed into the tubular axis 12 projects from the rear wall 2 to receive, in the embodiment shown, a nut 16 ensuring the blocking of the rear bearing assembly 11 on this rear wall 2, against the internal face of which bears an end shoulder 17 of the axis element 12. The rear bearing 13 of each rotor 5 or 6 is thus placed inside the latter, between internal staff 9 and the element nt axis 12 which itself is mounted cantilever on the rear wall 2 by means of the screw 15 which passes entirely through it. As shown in FIG. 2, a seal 18 is also disposed between the axis element 12 and the internal bearing 9, inside the recess of the rotor, this seal being held in the axial position, for example by a ring 19 screwed into an internal thread of the end of the internal smooth surface 9.

Egalement conformément à l'invention, les corps de rotor mâle 5 et rotor femelle 6 ont leur extremité avant fixée sur un élément d'arbre avant 20 et 21, respectivement. Chaque élément d'arbre avant 20, 21 comporte une tête de diamètre élargi 22, présentant par exemple des cannelures périphériques, emmanchée, dans l'exemple représenté, dans une partie cylindrique de montage élargie 23 de la partie avant de l'évidement interne 7 ou 8 définissant un épaulement de butée 24 dirigé vers l'avant, contre.lequel vient porter l'extrémité frontale de la tête élargie 22 des éléments d'arbre 20 et 21. Dans le mode de réalisation représenté, la tête élargie 22 des éléments d'arbre 20 ou 21 est bloquée dans le corps de re- tor correspondant par une bague 25 vissée dans un taraudage de la partie d'extrémité avant de l'évidement 7 ou 8 du corps de rotor.Also according to the invention, the male rotor 5 and female rotor 6 bodies have their front ends fixed to a front shaft element 20 and 21, respectively. Each front shaft element 20, 21 has a head of enlarged diameter 22, having for example peripheral grooves, fitted, in the example shown, into a cylindrical enlarged mounting part 23 of the front part of the internal recess 7 or 8 defining an abutment shoulder 24 directed towards the front, against which it carries the front end of the enlarged head 22 of the shaft elements 20 and 21. In the embodiment shown, the enlarged head 22 of the elements shaft 20 or 21 is locked in the corresponding retor body by a ring 25 screwed into a thread in the front end part of the recess 7 or 8 of the rotor body.

Les chambres 3 et 4 sont fermées, du côté avant, par une cloison avant 26, appartenant par exemple à un élément de boîtier avant 27 définissant les logements pour les engrenages d'entraînement synchrone des rotors. La cloison avant 26 comporte une partie tubulaire en saillie 28 s'étendant dans la partie d'extrémité avant élargie de l'évidement 7 du corps de rotor mâle 5 et formant une portée lisse pour un roulement 29 et un joint 30 montés sur l'élément d'arbre avant 20, dont la partie d'extrémité extérieure 31 fait saillie vers l'avant, au-delà de la paroi avant 26, pour le montage, dans le mode de réalisation représenté, de deux roues dentées coaxiales de rattrapage de jeu 32 et 33 nécessaires pour éviter les contacts d'entraînement entre les filets de rotors 3 et 4 et coopérant en engrènement avec une roue dentée d'entraînement 34 fixée sur la partie d'extrémité 35 de l'élément d'arbre 21 du rotor femelle 6 faisant saillie vers l'avant au-delà de la cloison avant 26 et prolongée, dans cette direction, pour le montage d'une poulie 36 destinée à être couplée au dispositif moteur d'entraînement du compresseur. Dans l'exemple représenté, la roue dentée 34 comporte un moyeu 37 emmanché sur l'élément d'arbre 21 et sur lequel sont montés un roulement 38 et un joint 39 prenant appui extérieurement sur des portées correspondantes formées par la cloison avant 26, au moins la zoné de portée du joint 39 étant au moins partiellement intégrée dans la partié avant de l'évidement 8 du rotor 6. Les logements des roues dentées de distribution 34 et 32-33 sont fermés par un couvercle avant 40, un joint 41 étant disposé entre une portée de ce couvercle avant 40 et la partie d'extrémité 35 de l'élément d'arbre 21 du rotor femelle 6. On notera, notamment err relation avec le rotor mâle 5, que les joints avant 30 et 39 sont sensiblement intégrés dans 1.'espace intérieur du boîtier défini par la cloison avant 26. Le rapport des diamètres primitifs des roues dentées de distribution 34 et 32, 33 est le même que le rapport du nombre des filets hélicoïdaux des rotors 5 et 6. Dans l'agencement selon l'invention, l'entraînement s'effectuant par le rotor femelle 6, via la roue dentée d'attaque 34, il s'ensuit un accroissement de 50 % de la vitesse de rotation du rotor mâle 5, à savoir, pour une vitesse de rotation d'entrée à la poulie 36 de 15 000 tours par minute, une vitesse de rotation du rotor mâle 5 de 22 500 tours par minute, ce qui est autorisé par la réduction de l'inertie des ensembles tournants. Pour réduire encore cette inertie, comme on le voit sur la figure 2, les éléments d'arbre avant 20 et 21 sont partiellement creux et comportent des évidements internes 42 et 43,. respectivement,ces éléments d'arbre étant réalisés par exemple par frappe à froid. En variante de l'exemple représenté, le corps de boîtier 1 peut être réalisé en deux parties, avec un plan de joint au niveau de la paroi de fond arrière 2.The chambers 3 and 4 are closed, on the front side, by a front partition 26, belonging for example to a front housing element 27 defining the housings for the synchronous drive gears of the rotors. The front partition 26 comprises a projecting tubular part 28 extending in the widened front end part of the recess 7 of the male rotor body 5 and forming a smooth bearing for a bearing 29 and a seal 30 mounted on the front shaft element 20, the outer end portion 31 of which protrudes forward, beyond the front wall 26, for mounting, in the embodiment shown, two coaxial gear take-up wheels clearance 32 and 33 necessary to avoid the driving contacts between the rotor threads 3 and 4 and cooperating in meshing with a driving toothed wheel 34 fixed on the end part 35 of the shaft element 21 of the rotor female 6 projecting forwardly beyond the front partition 26 and extended, in this direction, for mounting a pulley 36 intended to be coupled to the motor drive device of the compressor. In the example shown, the toothed wheel 34 has a hub 37 fitted on the shaft element 21 and on which are mounted a bearing 38 and a seal 39 bearing externally on corresponding bearing surfaces formed by the front partition 26, at minus the area of the seal 39 being at least partially integrated in the front part of the recess 8 of the rotor 6. The housings of the timing gears 34 and 32-33 are closed by a front cover 40, a seal 41 being disposed between a bearing surface of this front cover 40 and the end part 35 of the shaft element 21 of the female rotor 6. It will be noted, in particular in relation to the male rotor 5, that the front seals 30 and 39 are substantially integrated into the interior space of the housing defined by the front partition 26. The ratio of the original diameters of the toothed wheels of distribution 34 and 32, 33 is the same as the ratio of the number of helical threads of the rotors 5 and 6. In the arrangement according to the invention, the drive being effected by the female rotor 6, via the toothed wheel attack 34, this results in a 50% increase in the speed of rotation of the male rotor 5, namely, for an input speed of pulley 36 of 15,000 revolutions per minute, a speed of rotation of the rotor male 5 of 22,500 rpm, which is allowed by reducing the inertia of the rotating assemblies. To further reduce this inertia, as can be seen in FIG. 2, the front shaft elements 20 and 21 are partially hollow and have internal recesses 42 and 43,. respectively, these shaft elements being produced for example by cold stamping. As a variant of the example shown, the housing body 1 can be made in two parts, with a joint plane at the level of the rear bottom wall 2.

Sur la figure 1, on a représenté un mode de réalisation avec les lumières d'admission 45 et d'échappement 46 réalisées sur le corps de boîtier central 1, de part et d'autre de celui-ci, ces lumières pouvant être réalisées en variante sur les faces du carter ou sur une face et une zone du boîtier 1.In FIG. 1, an embodiment is shown with the intake 45 and exhaust 46 lights made on the central box body 1, on either side of it, these lights being able to be made in variant on the faces of the casing or on a face and a zone of the housing 1.

L'agencement de compresseur selon l'invention permet de réaliser les corps de rotor 5 et 6 en alliage léger, notamment à base d'Aluminium, mais également, compte tenu de la classe de compresseur.considéré, en matériau plastique rigide, par exemple en résine phénolique ou en polyamides avec charges de verre. La conception des lignes d'arbre en deux parties selon l'invention permet en outre, dans ce cas, de réaliser les corps de rotor 5 et 6 par surmoulage sur les éléments d'arbre avant 20 et 21 correspondants, assurant ainsi la solidarisation immédiate entre ces équipages.The compressor arrangement according to the invention makes it possible to produce the rotor bodies 5 and 6 in light alloy, in particular based on aluminum, but also, taking into account the compressor class considered, in rigid plastic material, for example. in phenolic resin or polyamides with glass fillers. The design of the two-part shaft lines according to the invention also makes it possible, in this case, to produce the rotor bodies 5 and 6 by overmolding on the corresponding front shaft elements 20 and 21, thus ensuring immediate attachment between these crews.

Selon une autre caractéristique de l'invention, les parois des chambres 3 et 4, ainsi que les surfaces de filets des rotors 5 et 6, sont, préalablement au montage, revêtues, comme figuré en 50, d'une couche en surépaisseur d'un matériau de revêtement érodable par les zones de surfaces externes adjacentes des éléments coopérants. Cet agencement permet de s'affranchir grandement des problèmes de tolérance d'usinage lors de l'assemblage, les filets de rotors assurant, par effet de rodage, leur passage dans l'épaisseur du matériau de revêtement érodable des parois du boîtier et, entre eux, la coopération optimale entre filets mâles et femelles pour l'obtention automatique du jeu fonctionnel nécessaire entre les filets des rotors. De ce fait, à l'assemblage, les rotors sont associés imbriqués l'un dans l'autre et installés dans le boîtier légèrement à force, les premiers tours d'actionnement assurant la création, par enlèvement local du matériau de revêtement. des jeux nécessaires, le calage angulaire convenable entre rotors étant assuré par le couplage mutuel sans jeu angulaire entre les roues dentées 34 et 32, 33. Le matériau de revêtement érodable contient des particules de lubrifiant sec assurant un fonctionnement souple et sans échauffement notable du compresseur. Le matériau de revêtement érodable est par exemple constitué d'une combinaison d'une résine, d'un liant dissout graphite et/ou de dans un solvant volatile, de particules de/bisulfure de molybdène et est appliqué par immersion, badigeonnage ou pulvérisation.According to another characteristic of the invention, the walls of the chambers 3 and 4, as well as the surfaces of the threads of the rotors 5 and 6, are, prior to mounting, coated, as shown in 50, with an extra layer of a coating material erodible by the adjacent external surface areas of the cooperating elements. This arrangement makes it possible to largely overcome the problems of machining tolerance during assembly, the rotor threads ensuring, by lapping effect, their passage through the thickness of the erodible coating material of the walls of the housing and, between them, the optimal cooperation between male and female threads for automatically obtaining the necessary functional clearance between the threads of the rotors. Therefore, during assembly, the rotors are associated nested one inside the other and installed in the housing slightly by force, the first actuation turns ensuring the creation, by local removal of the material. coating. necessary clearances, the suitable angular setting between rotors being ensured by mutual coupling without angular clearance between the toothed wheels 34 and 32, 33. The erodible coating material contains particles of dry lubricant ensuring flexible operation and without significant heating of the compressor . The erodible coating material consists for example of a combination of a resin, a dissolved graphite binder and / or of in a volatile solvent, of molybdenum / disulphide particles and is applied by immersion, brushing or spraying.

Quoique la présente invention ait été décrite en relation avec des modes de réalisation particulier, elle ne s'en trouve pas limitée mais est au contraire susceptible de modifications et de variantes qui apparaîtront à l'homme de l'art.Although the present invention has been described in relation to particular embodiments, it is not limited thereto but is on the contrary subject to modifications and variants which will appear to those skilled in the art.

Claims (13)

1. Compresseur à vis, comprenant un rotor mâle (5) et un rotor femelle (6) disposés respectivement dans deux chambres parallèles cylindriques intercommunicantes (3, 4) formées dans un boîtier (1) et fermées, à leurs extrémités axialement opposées, par une cloison frontale arrière (2) et une cloison frontale avant (26), chaque rotor étant supporté et entraîné en rotation par un moyen d'arbre comportant une première extrémité (31, 35) traversant la cloison avant (26), ces premières extrémités étant munies de roues dentées (34 ; 32, 33) coopérantes pour l'entraînement synchrone des rotors, chaque première extrémité de moyen d'arbre s'étendant dans un évidement formé dans le moyeu du rotor correspondant et étant couplée en rotation à ce dernier dans ledit évidement, caractérisé en ce que chaque rotor (5, 6) comprend un évidement longitudinal traversant (7, 8), le moyen d'arbre comprenant un ensemble de palier arrière (11) reçu dans l'extrémité correspondante (9) de cet évidement et monté de façon étanche sur un élément d'axe (12) fixé sur la cloison frontale arrière (2) du boîtier, et un élément d'arbre avant (20, 21), constituant ladite première extrémité de moyen d'arbre, solidarisé au rotor correspondant et coopérant avec un joint annulaire (30, 39) monté dans une partie tubulaire (28) de la cloison avant (26) s'étendant dans la partie avant de l'évidement traversant (7, 8) du rotor (5, 6).1. Screw compressor, comprising a male rotor (5) and a female rotor (6) respectively disposed in two parallel cylindrical intercommunicating chambers (3, 4) formed in a housing (1) and closed, at their axially opposite ends, by a rear front partition (2) and a front front partition (26), each rotor being supported and driven in rotation by a shaft means comprising a first end (31, 35) passing through the front partition (26), these first ends being provided with cooperating toothed wheels (34; 32, 33) for the synchronous drive of the rotors, each first end of the shaft means extending in a recess formed in the hub of the corresponding rotor and being coupled in rotation to the latter in said recess, characterized in that each rotor (5, 6) comprises a through longitudinal recess (7, 8), the shaft means comprising a rear bearing assembly (11) received in the corresponding end (9) of this recess and mounted d e in a sealed manner on an axis element (12) fixed on the rear front partition (2) of the housing, and a front shaft element (20, 21), constituting said first end of shaft means, secured to the rotor corresponding and cooperating with an annular seal (30, 39) mounted in a tubular part (28) of the front partition (26) extending in the front part of the through recess (7, 8) of the rotor (5, 6 ). 2. Compresseur selon la revendication 1, caractérisé en ce que l'élément d'arbre avant (21) du rotor femelle (6) comporte des moyens de couplage (36) à un dispositif moteur d'entraînement de compresseur.2. Compressor according to claim 1, characterized in that the front shaft element (21) of the female rotor (6) comprises coupling means (36) to a compressor drive motor device. 3a Compresseur selon la revendication 2, caractérisé en ce que l'élément d'arbre avant (20) du rotor mâle (5) comporte deux roues dentées coaxiales (32, 33) de rattrapage de jeu avec la roue dentée (34) de l'élément d'arbre avant (21) du rotor femelle (6).3a compressor according to claim 2, characterized in that the front shaft element (20) of the male rotor (5) comprises two coaxial toothed wheels (32, 33) for taking up play with the toothed wheel (34) of the 'front shaft element (21) of the female rotor (6). 4. Compresseur selon l'une des revendications 1 à 3, caractérisé en ce que les deux rotors (5, 6) sont réalisés en matériau plastique rigide.4. Compressor according to one of claims 1 to 3, characterized in that the two rotors (5, 6) are made of rigid plastic material. 5. Compresseur selon la revendication 4, caractérisé en ce que chaque rotor (5, 6) est surmoulé sur son élément d'arbre avant (20, 21). '5. Compressor according to claim 4, characterized in that each rotor (5, 6) is molded onto its front shaft element (20, 21). '' 6. Compresseur selon l'une des revendications 1 à 5, caractérisé en ce que l'élément d'axe arrière (12) est fixé sur la paroi frontale arrière (2) par une vis centrale (15).6. Compressor according to one of claims 1 to 5, characterized in that the rear axle element (12) is fixed to the rear front wall (2) by a central screw (15). 7. Compresseur selon l'une des revendications précédentes, caractérisé en ce qu'au moins les parois internes des chambres (3, 4) du boîtier (1) sont revêtues d'une couche en surépaisseur (50) d'un matériau de revêtement érodable contenant des particules de lubrifiant sec.7. Compressor according to one of the preceding claims, characterized in that at least the internal walls of the chambers (3, 4) of the housing (1) are coated with an extra layer (50) of a coating material erodible containing particles of dry lubricant. 8. Compresseur à vis, du type comprenant un rotor mâle (5) et un rotor femelle (6) disposés dans deux chambres parallèles intercommunicantes (3, 4) formées dans un boîtier (1) et fermées, à leurs extrémités axialement opposées, par une cloison frontale arrière (2) et une cloison frontale avant (26), respectivement, chaque rotor étant supporté et entraîné en rotation par un moyen d'arbre comportant une première extrémité (31, 35) traversant la cloison avant (26), ces premières extrémités étant munies de roues dentées coopérantes (34, 32, 33) pour l'entraînement synchrone des rotors, caractérisé en ce qu'au moins les parois internes des chambres (3, 4) sont revêtues d'une couche en surépaisseur (50) d'un matériau de revêtement érodable contenant des particules de lubrifiant sec, les roues dentées d'entraînement (34; 32, 33) étant couplées mutuellement sans jeu angulaire.8. Screw compressor, of the type comprising a male rotor (5) and a female rotor (6) arranged in two parallel intercommunicating chambers (3, 4) formed in a housing (1) and closed, at their axially opposite ends, by a rear front partition (2) and a front front partition (26), respectively, each rotor being supported and driven in rotation by a shaft means comprising a first end (31, 35) passing through the front partition (26), these first ends being provided with cooperating toothed wheels (34, 32, 33) for the synchronous drive of the rotors, characterized in that at least the internal walls of the chambers (3, 4) are coated with an extra layer (50 ) an erodible coating material containing particles of dry lubricant, the drive gear wheels (34; 32, 33) being mutually coupled without angular play. 9. Compresseur selon la revendication 8, caractérisé en ce que les surfaces des filets--des rotors (5, 6) sont revêtues d'une couche en sur¢paisseur dudit matériau de revêtement érodable.9. Compressor according to claim 8, characterized in that the surfaces of the threads - of the rotors (5, 6) are coated with a layer in excess thickness of said erodible coating material. 10. Compresseur selon la revendication 8 ou la revendication 9, caractérisé en ce que la première extrémité (31) du moyen d'arbre d'un (5) des rotors comporte deux roues dentées coaxiales (32, 33) de rattrapage de jeu avec la roue dentée (34) de la première extrémité (35) du moyen d'arbre de l'autre rotor (6).10. Compressor according to claim 8 or claim 9, characterized in that the first end (31) of the shaft means of one (5) of the rotors comprises two coaxial toothed wheels (32, 33) for taking up play with the toothed wheel (34) of the first end (35) of the shaft means of the other rotor (6). 11. Compresseur selon l'une des revendications 8 à 10, caractérisé en ce que le matériau de revêtement érodable (50) contient des particules de graphite.11. Compressor according to one of claims 8 to 10, characterized in that the erodible coating material (50) contains graphite particles. 12. Compresseur selon l'une des revendications 8 à 11, caractérisé en ce que le moyen d'arbre de chaque rotor comporte un élément d'arbre avant (20, 21) tourillonnant par rapport à la cloison avant (26) et fixé par son extrémité intérieure (22) dans un évidement axial (23) du rotor.12. Compressor according to one of claims 8 to 11, characterized in that the shaft means of each rotor comprises a front shaft element (20, 21) journalled relative to the front partition (26) and fixed by its inner end (22) in an axial recess (23) of the rotor. 13. Compresseur selon la revendication 12, caractérisé en ce que l'élément d'arbre avant (21) du rotor femelle (6) comporte des moyens de couplage (36) à un moteur d'entraînement du compresseur.13. Compressor according to claim 12, characterized in that the front shaft element (21) of the female rotor (6) comprises coupling means (36) to a motor for driving the compressor.
EP83401448A 1982-07-22 1983-07-13 Screw compressor Expired EP0101345B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8212803A FR2530742B1 (en) 1982-07-22 1982-07-22 VOLUMETRIC SCREW COMPRESSOR
FR8212803 1982-07-22

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EP0101345A1 true EP0101345A1 (en) 1984-02-22
EP0101345B1 EP0101345B1 (en) 1986-10-08

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US (1) US4490102A (en)
EP (1) EP0101345B1 (en)
JP (2) JPS5932688A (en)
AU (1) AU555160B2 (en)
BR (1) BR8303973A (en)
DE (1) DE3366726D1 (en)
ES (1) ES8404473A1 (en)
FR (1) FR2530742B1 (en)
HU (1) HU186334B (en)
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DE102005015685A1 (en) * 2005-04-06 2006-10-12 Leybold Vacuum Gmbh Rotor for a vacuum pump has a single-piece positive displacer held by two shaft journals on both ends of the positive displacer
JP4702639B2 (en) * 2005-10-31 2011-06-15 株式会社前川製作所 Liquid jet screw compressor
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WO2009029855A1 (en) 2007-08-30 2009-03-05 Micropump.Inc. Methods for manufacturing pump-heads having a desired internal clearance for rotary member
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CN108799113A (en) * 2018-08-03 2018-11-13 天津商业大学 Oil-free lubrication Spiral Lobe Refrigeration Compressor
AU2020452724A1 (en) * 2020-06-10 2023-02-02 Mehmet Bora KUZUCAN Compressor

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WO1986004639A1 (en) * 1983-01-18 1986-08-14 Delta Screw Nederland B.V. Screw compressor or motor with specific rotor profiles
EP0225070A1 (en) * 1985-11-18 1987-06-10 Eaton Corporation Port arrangement for rotary positive displacement blower
EP0290664A1 (en) * 1987-05-15 1988-11-17 Leybold Aktiengesellschaft Two-shaft pump
EP0348591A2 (en) * 1988-06-29 1990-01-03 KABUSHIKI KAISHA KOBE SEIKO SHO also known as Kobe Steel Ltd. Screw type mechanical supercharger
EP0348591A3 (en) * 1988-06-29 1990-05-23 KABUSHIKI KAISHA KOBE SEIKO SHO also known as Kobe Steel Ltd. Screw type mechanical supercharger
EP0493315A1 (en) * 1990-12-28 1992-07-01 TES WANKEL, TECHNISCHE FORSCHUNGS- UND ENTWICKLUNGSSTELLE LINDAU GmbH Sealing
EP0666422A1 (en) * 1994-02-05 1995-08-09 MAN Gutehoffnungshütte Aktiengesellschaft Bearings and drive connection for the rotors of a screw compressor
US5620044A (en) * 1994-10-07 1997-04-15 Ford Motor Company Gravity precision sand casting of aluminum and equivalent metals
EP0705979A1 (en) * 1994-10-07 1996-04-10 Ford Motor Company Limited Efficiency enhanced fluid pump or compressor
EP0736692A1 (en) * 1995-04-08 1996-10-09 MAN Gutehoffnungshütte Aktiengesellschaft Sealing, bearing support and driving of the rotors of a dry running screw compressor
CN1112515C (en) * 1996-03-27 2003-06-25 北越工业株式会社 Shaft structure of screw rotor for screw fluid machinery
EP1857680A2 (en) * 2006-05-18 2007-11-21 Grundfos Management A/S pump rotor
EP1857680A3 (en) * 2006-05-18 2008-02-20 Grundfos Management A/S pump rotor
FR2964163A1 (en) * 2010-10-12 2012-03-02 Alcatel Lucent Dry type vacuum pump e.g. spiral type vacuum pump, has rolling bearing interposed between rolling bearing support axle and axial wall of central housing of rotor shaft that is supported in rotation in main bearing
IT202100025589A1 (en) * 2021-10-07 2023-04-07 Tm I C S R L Termomeccanica Ind Compressors SCREW COMPRESSOR.
EP4163495A1 (en) * 2021-10-07 2023-04-12 TM.I.C. S.r.l. Termomeccanica Industrial Compressors Screw compressor

Also Published As

Publication number Publication date
AU1711683A (en) 1984-01-26
FR2530742A1 (en) 1984-01-27
AU555160B2 (en) 1986-09-11
JP2551233Y2 (en) 1997-10-22
HU186334B (en) 1985-07-29
ES524343A0 (en) 1984-04-16
DE3366726D1 (en) 1986-11-13
JPH0647689U (en) 1994-06-28
US4490102A (en) 1984-12-25
SU1454263A3 (en) 1989-01-23
JPS5932688A (en) 1984-02-22
BR8303973A (en) 1984-02-28
ES8404473A1 (en) 1984-04-16
MX156478A (en) 1988-08-26
EP0101345B1 (en) 1986-10-08
FR2530742B1 (en) 1987-06-26

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