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EP0101345B1 - Screw compressor - Google Patents

Screw compressor Download PDF

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Publication number
EP0101345B1
EP0101345B1 EP83401448A EP83401448A EP0101345B1 EP 0101345 B1 EP0101345 B1 EP 0101345B1 EP 83401448 A EP83401448 A EP 83401448A EP 83401448 A EP83401448 A EP 83401448A EP 0101345 B1 EP0101345 B1 EP 0101345B1
Authority
EP
European Patent Office
Prior art keywords
rotor
compressor
rotors
casing
coating material
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP83401448A
Other languages
German (de)
French (fr)
Other versions
EP0101345A1 (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
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 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 of the type comprising a male rotor and a female rotor disposed respectively in two parallel cylindrical intercommunicating chambers formed in a housing and delimited axially by a rear wall and a partition. front, each rotor being supported in the housing and driven in rotation by a shaft means disposed in a longitudinal recess passing through the rotor and comprising an outer end passing through the front bulkhead, these ends being provided with cooperating toothed wheels for synchronous drive rotors.
  • a compressor of this type is described in the document FR-A-1 243471, in which each rotor is fitted on a long shaft projecting on either side of the longitudinal ends of the rotor to rotate in bearings of the housing.
  • Rotor assemblies of this type impose significant axial dimensions on the compressor and have a significant 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 body, which performs most of the compression work.
  • the object of the present invention is to provide a screw compressor designed for the supply of low overpressures, less than 1 bar, of particularly compact structure, with low interturning rotary assemblies, providing good volumetric efficiency, especially at low speed, and allowing mass production, in particular for use in the area of volumetric supercharging of heat engines.
  • the shaft means of each rotor comprises a set of rear bearings received in sealed manner in the corresponding end of the '' recess and comprising a shaft element fixed on the rear wall of the housing, and a front shaft element, constituting said outer end of shaft means, having an inner end secured to the corresponding rotor and cooperating with an annular seal mounted in a tubular part of the front partition extending into the front part of the rotor recess.
  • Document FR-A-1 110 645 describes a compressor in which the female rotor is driven by the threads of the male rotor, each hollow rotor rotating on a fixed shaft mounted cantilevered in the housing.
  • Document DE-A-2 520 667 describes a central outlet pump with opposite helical double pitch rotors and of massive construction and each supported at one end by a bearing assembly partially integrated in a blind bore formed in the hub of the rotor .
  • each rotor is broken down into two distinct parts, thus making it possible to significantly reduce the inertia of each rotating assembly, the axial size of the compressor being able to be considerably reduced, in particular due to the integration of the rear bearing assembly into the through recess of the rotor.
  • 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 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 housing body 1 defining two chambers cylindrical parallels 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 for receive a rear bearing assembly 11 fixed on 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 through the head of a screw 15, the threaded end of which is screwed into the tubular axis 12 protrudes from the rear wall 2 to receive, in the embodiment shown, a nut 16 ensuring the blocking of the assembly rear bearing 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 disposed inside the latter, between the internal surface 9 and the axis element 12 which itself is mounted in 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 tank 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 end 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 comes the front end of the enlarged head 22 of the shaft elements 20 and 21.
  • the enlarged head 22 of the elements d 'shaft 20 or 21 is locked in the corresponding rotor 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 bearing 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 portion 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 bulkhead 26.
  • the ratio of the pitch diameters of the timing gears 34 and 32, 33 is the same as the ratio of the number of the helical threads of the rotors 5 and 6.
  • the entrance aging is effected by the female rotor 6, via the driving gear 34, there follows a 50% increase in the speed of rotation of the male rotor 5, namely, for an input rotation speed at the pulley 36 of 15,000 revolutions per minute, a rotation speed of the male rotor 5 of 22,500 revolutions per minute, which is authorized by the reduction of the inertia of the rotary assemblies.
  • this inertia as can be seen in FIG.
  • 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 striking with cold.
  • 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 housing zone 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 class of compressor considered, in rigid plastic material, for example in phenolic or polyamide resin 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 material. of erodible coating of the walls of the housing and, between them, the optimal cooperation between male and female threads for the automatic obtaining of 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 binder dissolved in a volatile solvent, particles of graphite and / or molybdenum disulfide and is applied by immersion, brushing or spraying.

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

Description

La présente invention concerne les compresseurs et, plus particulièrement, les compresseurs ou soufflantes volumétriques à vis du type comprenant un rotor mâle et un rotor femelle disposés respectivement dans deux chambres parallèle cylindriques intercommunicantes formées dans un boîtier et délimitées axialement par une paroi arrière et une cloison avant, chaque rotor étant supporté dans le boîtier et entraîné en rotation par un moyen d'arbre disposé dans un évidement longitudinal traversant du rotor et comportant une extrémité extérieure traversant la cloison avant, ces extrémités étant munies de roues dentées coopérantes pour l'entraînement synchrone des rotors. Un compresseur de ce type est décrit dans le document FR-A-1 243471, dans lequel chaque rotor est emmanché sur un arbre long faisant saillie de part et d'autre des extrémités longitudinales du rotor pour tourillonner dans des paliers du boîtier.The present invention relates to compressors and, more particularly, to volumetric screw compressors or blowers of the type comprising a male rotor and a female rotor disposed respectively in two parallel cylindrical intercommunicating chambers formed in a housing and delimited axially by a rear wall and a partition. front, each rotor being supported in the housing and driven in rotation by a shaft means disposed in a longitudinal recess passing through the rotor and comprising an outer end passing through the front bulkhead, these ends being provided with cooperating toothed wheels for synchronous drive rotors. A compressor of this type is described in the document FR-A-1 243471, in which each rotor is fitted on a long shaft projecting on either side of the longitudinal ends of the rotor to rotate in bearings of the housing.

Les équipages de rotors de ce type imposent au compresseur des dimensions axiales importantes et présentent une inertie notable, 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.Rotor assemblies of this type impose significant axial dimensions on the compressor and have a significant 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 body, which performs 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 intertie, 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 provide a screw compressor designed for the supply of low overpressures, less than 1 bar, of particularly compact structure, with low interturning rotary assemblies, providing good volumetric efficiency, especially at low speed, and allowing mass production, in particular for use in the area of volumetric supercharging of heat engines.

Pour ce faire, selon une caractéristique de l'invention, dans un compresseur à vis, du type défini ci-dessus, le moyen d'arbre de chaque rotor comprend un ensemble de palier arrière reçu de façon étanche dans l'extrémité correspondante de l'évidement et comprenant un élément d'axe fixé sur la paroi arrière du boîtier, et un élément d'arbre avant, constituant ladite extrémité extérieure de moyen d'arbre, ayant une extrémité intérieure solidarisée au rotor correspondant et coopérant avec un joint annulaire monté dans une partie tubulaire de la cloison avant s'étendant dans la partie avant de l'évidement du rotor.To do this, according to a characteristic of the invention, in a screw compressor, of the type defined above, the shaft means of each rotor comprises a set of rear bearings received in sealed manner in the corresponding end of the '' recess and comprising a shaft element fixed on the rear wall of the housing, and a front shaft element, constituting said outer end of shaft means, having an inner end secured to the corresponding rotor and cooperating with an annular seal mounted in a tubular part of the front partition extending into the front part of the rotor recess.

Le document FR-A-1 110 645 décrit un compresseur dans lequel le rotor femelle est entraîné par les filets du rotor mâle, chaque rotor creux tourillonnant sur un arbre fixe monté en porte à faux dans le boîtier.Document FR-A-1 110 645 describes a compressor in which the female rotor is driven by the threads of the male rotor, each hollow rotor rotating on a fixed shaft mounted cantilevered in the housing.

Le document DE-A-2 520 667 décrit une pompe à sortie centrale avec des rotors à double pas hélicoïdaux opposés et de construction massive et supportés chacun à une extrémité par un ensemble de palier partiellement intégré dans un alésage borgne formé dans le moyeu du rotor.Document DE-A-2 520 667 describes a central outlet pump with opposite helical double pitch rotors and of massive construction and each supported at one end by a bearing assembly partially integrated in a blind bore formed in the hub of the rotor .

Avec l'agencement selon l'invention, la ligne ou moyen d'arbre de chaque rotor est décomposée en deux parties 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 traversant du 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 the arrangement according to the invention, the line or shaft means of each rotor is broken down into two distinct parts, thus making it possible to significantly reduce the inertia of each rotating assembly, the axial size of the compressor being able to be considerably reduced, in particular due to the integration of the rear bearing assembly into the through recess of the rotor. 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, dans un tel compresseur à vis, au moins les parois internes des chambres - et avantageusement également les parois des filets des rotors - sont revêtues d'une couche en surépaisseur d'un matériau de revêtement érodable contenant des particules de lubrifiant sec, les roues dentées d'entraînement étant typiquement couplées mutuellement sans jeu angulaire.According to another characteristic of the invention, in such a screw compressor, 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 an erodible coating material containing particles of dry lubricant, the drive gear wheels typically being coupled to each other without angular play.

De cette façon, le montage du compresseur s'effectue très simplement et rapidement, en limitant les jeux résultant de variations de tolérances et sans poser, par la suite, de 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 is carried out very simply and quickly, limiting the clearances resulting from variations in tolerances and without subsequently posing any 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 I II-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 I II-III of Figure 2.

Comme représenté sur les dessins, le compresseur comprend un corps de boîtier 1, d'allure sensiblement parallélipédique, 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 intercom- muniquant 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 baque 19 vissée dans un taraudage de l'extrémité de la portée lisse interne 9.As shown in the drawings, 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 housing body 1 defining two chambers cylindrical parallels 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 for receive a rear bearing assembly 11 fixed on 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 through the head of a screw 15, the threaded end of which is screwed into the tubular axis 12 protrudes from the rear wall 2 to receive, in the embodiment shown, a nut 16 ensuring the blocking of the assembly rear bearing 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 disposed inside the latter, between the internal surface 9 and the axis element 12 which itself is mounted in 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 tank 19 screwed into an internal thread of the end of the internal smooth surface 9.

Les corps de rotor mâle 5 et rotor femelle 6 ont leur extrémité 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 rotor 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.The male rotor 5 and female rotor 6 bodies have their front end 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 comes 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 d 'shaft 20 or 21 is locked in the corresponding rotor 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 zone de portée du joint 39 étant au moins partiellement intégrée dans la partie 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 en relation avec le rotor mâle 5, que les joints avant 30 et 39 sont sensiblement intégrés dans l'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 bearing 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 portion 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 bulkhead 26. The ratio of the pitch diameters of the timing gears 34 and 32, 33 is the same as the ratio of the number of the helical threads of the rotors 5 and 6. In the arrangement according to the invention, the entrance aging is effected by the female rotor 6, via the driving gear 34, there follows a 50% increase in the speed of rotation of the male rotor 5, namely, for an input rotation speed at the pulley 36 of 15,000 revolutions per minute, a rotation speed of the male rotor 5 of 22,500 revolutions per minute, which is authorized by the reduction of the inertia of the rotary 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 striking with cold. 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 de 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 housing zone 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 class of compressor considered, in rigid plastic material, for example in phenolic or polyamide resin 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 dans un solvant volatile, de particules de graphite et/ou 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 material. of erodible coating of the walls of the housing and, between them, the optimal cooperation between male and female threads for the automatic obtaining of 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 coating material, of the clearances. necessary, the suitable angular setting between the rotors being ensured by mutual coupling without angular play 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 binder dissolved in a volatile solvent, particles of graphite and / or molybdenum disulfide and is applied by immersion, brushing or spraying.

Claims (10)

1. A screw type compressor comprising a male rotor (5) and a female rotor (6) disposed respectively within two interconnected cylindrical parallel chambers (3, 4) provided in a casing (1) and axially delimited by a rear wall (2) and a front cover (26), each rotor being supported in the casing and driven for rotary movement by a shaft hub disposed in a transverse longitudinal cavity (7, 8) of the rotor and comprising an exterior extremity (31, 35) traversing the front cover (26), said extremities being provided with gears (34; 32, 33) cooperating for synchronously driving the rotors, characterized in that the shaft hub of each rotor
(5, 6) comprises a rear bearing assembly (11) received in fluid tight manner within the corresponding extremity (9) of the cavity (7;8) and comprising an axis element (12) fixed to the rear wall (2) of the casing (1), and a front shaft element (20, 21 ) constituting said exterior extremity of the shaft hub, having an interior extremity (22) fixedly connected to the corresponding rotor and cooperating with an annular seal (30, 39) mounted in a tubular portion (28) of the front cover (26) extending into the front portion of the cavity (7;8) of the rotor (5;6).
2. The compressor of claim 1, characterized in that the front shaft hub (21) of the female rotor (6) comprises coupling means (36) for coupling to a motor device for driving the compressor.
3. The compressor of claim 2, characterized in that the front shaft element (20) of the male rotor (5) comprises a pair of coaxial gears (32, 33) for compensation of play with the gear (34) of the front shaft element (21 ) of the female rotor (6).
4. The compressor of any of claims 1 to 3, characterized in that the two rotors (5, 6) are made from rigid plastic material.
5. The compressor of claim 4, characterized in that each rotor (5, 6) is molded on its front shaft element (20, 21).
6. The compressor of any of claims 1 to 5, characterized in that the rear axis element (12) is fixed on the rear wall (2) by a central bolt (15).
7. The compressor of any of the preceding claims, characterized in that at least the internal walls of the chambers (3, 4) of the casing (1) are coated by a layer (50) of an erodable coating material containing particles of a dry lubricant.
8. The compressor of claim 7, characterized in that the surfaces of the threads of the rotors (5, 6) are also coated by a layer of such a erodable coating material.
9. The compressor of claim 7 or claim 8, characterized in that the erodable coating material contains graphite particles.
EP83401448A 1982-07-22 1983-07-13 Screw compressor Expired EP0101345B1 (en)

Applications Claiming Priority (2)

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

Publications (2)

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

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EP83401448A Expired EP0101345B1 (en) 1982-07-22 1983-07-13 Screw compressor

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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)
MX (1) MX156478A (en)
SU (1) SU1454263A3 (en)

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Also Published As

Publication number Publication date
JPS5932688A (en) 1984-02-22
HU186334B (en) 1985-07-29
FR2530742B1 (en) 1987-06-26
MX156478A (en) 1988-08-26
US4490102A (en) 1984-12-25
DE3366726D1 (en) 1986-11-13
BR8303973A (en) 1984-02-28
ES524343A0 (en) 1984-04-16
EP0101345A1 (en) 1984-02-22
FR2530742A1 (en) 1984-01-27
AU555160B2 (en) 1986-09-11
SU1454263A3 (en) 1989-01-23
ES8404473A1 (en) 1984-04-16
AU1711683A (en) 1984-01-26
JP2551233Y2 (en) 1997-10-22
JPH0647689U (en) 1994-06-28

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