EP0161130A1 - Volumetric screw compressor - Google Patents

Volumetric screw compressor Download PDF

Info

Publication number
EP0161130A1
EP0161130A1 EP85400531A EP85400531A EP0161130A1 EP 0161130 A1 EP0161130 A1 EP 0161130A1 EP 85400531 A EP85400531 A EP 85400531A EP 85400531 A EP85400531 A EP 85400531A EP 0161130 A1 EP0161130 A1 EP 0161130A1
Authority
EP
European Patent Office
Prior art keywords
chambers
compressor according
rotor
opening
pair
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
EP85400531A
Other languages
German (de)
French (fr)
Other versions
EP0161130B1 (en
Inventor
Jean-Jacques Carré
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 EP0161130A1 publication Critical patent/EP0161130A1/en
Application granted granted Critical
Publication of EP0161130B1 publication Critical patent/EP0161130B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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

Definitions

  • the present invention relates to screw compressors, and more particularly to volumetric compressors or blowers intended for supercharging or scanning thermal engines of motor vehicles.
  • the present invention relates more specifically to the screw compressors with front intake, of the type comprising a male rotor and a cooperating female rotor, respectively disposed in a pair of interconnected parallel cylindrical chambers formed in a housing, an intake passage communicating with one end. of the pair of chambers by an entry opening delimited, at this end of the pair of chambers, by a wall partially obscuring adjacent portions of each chamber, and an outlet passage communicating with the other end of this pair of chambers .
  • a compressor of this type is described in document FR-A-1216086.
  • the inlet opening is formed by the other open front end of the boltier and is partially obscured by a small cover plate obscuring the interpenetration area of two veins each belonging to one of the rotors to avoid direct communication between the inlet opening and the outlet opening, which axially covers more than the half the length of the rotors and partially radially the end portions of the rotors opposite the inlet opening.
  • the subject of the present invention is improvements to this type of compressor and to propose a new arrangement of inlet and outlet openings for the production of a compact positive displacement compressor, with low inertia, with rapid rotation and with high efficiency, by permanently providing, in each rotor, a buffer flow between the inlet and outlet openings, along which there prevails an intermediate pressure varying between atmospheric pressure at the inlet and the discharge overpressure at the exhaust.
  • the inlet opening consists, for each chamber, of an annular sector with an opening angle less than 200 °, the two annular sectors being substantially symmetrical with respect to at the intersection plane of the chambers and separated from each other by a central portion of the wall.
  • the outlet passage communicates with the chambers by an outlet opening formed in a peripheral wall of the bolt bowl, this outlet opening having a general V shape substantially centered on the plane of intersection of the chambers. and the edges of which converging towards each other are, in projection, substantially parallel to the threads of the respective rotors.
  • the screw compressor according to the invention comprises a male rotor (1) and a female rotor (2) each comprising helical threads arranged, so that the threads of each rotor cooperate with those of the 'other rotor in slight mutual contact, in a pair of parallel cylindrical chambers (3) and (4), respectively, intercommunicating longitudinally along a plane of intersection parallel to the axes Z and Z' common to the male rotor (1) and to the chamber (3), on the one hand, and to the female rotor (2) and to the chamber (4) on the other.
  • the rotors (1) and (2) are coupled at one of their ends, in the example shown, to a pair of gears (6) and (7) cooperating mutually without play to synchronously drive the rotors (1) and (2).
  • the gears (6) and (7) are arranged in an interior cavity of the housing (5) sealed from the chambers (3) and (4) by a front partition in which the rotors (1) and ( 2), the latter comprising, at their ends opposite the gears (6) and (7), bearings supported on a front end wall (B) attached to the housing (5).
  • the axis (9) of the gear (7) and of the female rotor (2) is coupled to a drive device of the compressor, the gear (7) of the female rotor (2) therefore being the drive gear of the gear (6) of the male rotor (1), according to a general arrangement which is the subject of document EP-0101345 the content of which is assumed to be incorporated here for reference.
  • each annular sector (11) or (12) has an external profile centered on the corresponding axis Z or Z 'and of radius corresponding to that of the associated chamber (3) or (4), and an internal profile in the form of arc of a circle, also centered on the corresponding axis Z or Z 'and of radius corresponding to the radius of the hub of the corresponding rotor (1) or (2).
  • the mixed rotor comprises 4 lobes or threads and the female rotor comprises 6 threads, the threads being of symmetrical or slightly asymmetrical profile. As can be seen in FIG.
  • the two sectors (11) and (12) are substantially symmetrical with respect to the plane of intersection of the chambers (3) and (4) and are separated, at the level of their closest zones. one from the other, by a central portion (13) of the wall (8).
  • the adjacent edges (14) and (15) of the sectors (11) and (12) extend radially towards the respective axes Z and Z ', forming between them an angle less than 90 °, typically about 80 °.
  • the annular sector (11) of the male screw has an opening angle ⁇ less than 180 °, typically around 165 ° .
  • the annular sector (12) of the female screw (2) has an opening angle ⁇ greater than 180 ° but less than 200 °, typically around 190 °.
  • the top of the triangle is truncated, the outlet opening (16) consequently having a small transverse edge (19) opposite the base and parallel to the latter.
  • the base has a central projecting portion (20) of transverse extension corresponding substantially to that of the short side (19).
  • the outlet opening (16) is substantially centered on the plane of intersection of the chambers (3) and (4) but has a slight asymmetry to take account of the number of different threads on the male (1) and female (2) rotors.
  • the maximum axial height of the opening (16) (between the large base and the short side (19)) is less than twice the axial distance between two adjacent rotor threads, typically of the order of 1.25 times the axial distance between adjacent rotor threads.
  • the overall length of the rotors corresponds substantially to half the pitch of the threads of each rotor.
  • vein B of the male screw (1) and the vein B 'of the female screw (2) enter into communication or interpenetration with one another being isolated, on the side of their intake end, from the inlet openings (11) and (12). It is the same for the veins C and C 'which will cease to be confused to enter on the other hand in communication with the corresponding inlet openings (11) and (12). Furthermore the vein A, also concealed by the wall (8) is in communication with the vein D 'of the female screw (2) which it communicates with the inlet opening (12). On the other hand, the vein A ′, in the configuration shown, is it completely closed.
  • veins B and B ' remain closed for a half rotation of each rotor, these veins thus playing the role of buffer veins between the intake (11,12) and the exhaust (16), the pressure of the 'air in these veins B and B' increasing by a value equal to atmospheric pressure up to a nominal compression pressure, of the order of 1.6 bar absolute, at the limit of the exhaust.
  • a nominal compression pressure of the order of 1.6 bar absolute

Landscapes

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

Abstract

Le compresseur comporte une ouverture d'entrée frontale constituée de deux secteurs annuiaires (11,12) avant chacun un angle d'ouverture inférieur à 200 degrés, les deux secteurs annulaires étant sensiblement symétriques par rapport au plan d'intersection des chambres des rotors et séparés l'un de l'autre par une portion centrale d'une paroi d'extrémité du boitier définissant lesdits secteurs annulaires. L'ouverture de sortie (16) est formée dans une paroi périphérique du boiter et présente une forme générale en V dont les bords convergents sont parallèles, en projection, aux filets des rotors respectifs et dont la hauteur axiale est inférieure au double de la distance axiale entre deux filets de rotors adjacents.The compressor has a front inlet opening consisting of two annular sectors (11,12) each before an opening angle less than 200 degrees, the two annular sectors being substantially symmetrical with respect to the plane of intersection of the chambers of the rotors and separated from each other by a central portion of an end wall of the housing defining said annular sectors. The outlet opening (16) is formed in a peripheral wall of the housing and has a general V shape whose converging edges are parallel, in projection, to the threads of the respective rotors and whose axial height is less than twice the distance axial between two adjacent rotor threads.

Description

La présente invention concerne les compresseurs à vis, et plus particulièrement les compresseurs ou soufflantes volumétriques destinés à la suralimentation ou au balayage de moteurs thermiques de véhicules automobiles.The present invention relates to screw compressors, and more particularly to volumetric compressors or blowers intended for supercharging or scanning thermal engines of motor vehicles.

La présente invention concerne plus spécifiquement les compresseurs à vis à admission frontale, du type comprenant un rotor mâle et un rotor femelle coopérante, disposés respectivement dans une paire de chambres cylindriques parallèles intercommuniquantes formées dans un boitier, un passage d'admission communiquant avec une extrémité de la paire de chambres par une ouverture d'entrée délimitée, à cette extrémité de la paire de chambres, par une paroi occultant partiellement des portions adjacentes de chaque chambre, et un passage de sortie communiquant avec l'autre extrémité de cette paire de chambres.The present invention relates more specifically to the screw compressors with front intake, of the type comprising a male rotor and a cooperating female rotor, respectively disposed in a pair of interconnected parallel cylindrical chambers formed in a housing, an intake passage communicating with one end. of the pair of chambers by an entry opening delimited, at this end of the pair of chambers, by a wall partially obscuring adjacent portions of each chamber, and an outlet passage communicating with the other end of this pair of chambers .

Un compresseur de ce type est décrit dans le document FR-A-1216086. Dans ce document, où les rotors sont montés en porte à faux dans une extrémité du boîtier et le rotor femelle est entrainé par contact avec le rotor mâle, l'ouverture d'entrée est constituée par l'autre extrémité frontale ouverte du boltier et est partiellement occultée par une plaque de couverture de petites dimensions occultant la zone d'interpénétration de deux veines appartenant chacune à un des rotors pour éviter une communication directe entre l'ouverture d'entrée et l'ouverture de sortie, laquelle couvre axialement plus de la moitié de la longueur des rotors et partiellement radialement les portions d'extrémité des rotors opposées à l'ouverture d'entrée.A compressor of this type is described in document FR-A-1216086. In this document, where the rotors are cantilevered in one end of the housing and the female rotor is driven by contact with the male rotor, the inlet opening is formed by the other open front end of the boltier and is partially obscured by a small cover plate obscuring the interpenetration area of two veins each belonging to one of the rotors to avoid direct communication between the inlet opening and the outlet opening, which axially covers more than the half the length of the rotors and partially radially the end portions of the rotors opposite the inlet opening.

La présente invention a pour objet des perfectionnements à ce type de compresseur et de proposer un nouvel agencement d'ouvertures d'entrée et de sortie pour la réalisation d'un compresseur volumétrique compact, à faible inertie, à rotation rapide et à rendement élevé, en ménageant en permanence, dans chaque rotor, une veine tampon entre les ouvertures d'entrée et de sortie, le long de laquelle règne une pression intermédiaire évoluant entre la pression atmosphérique à l'admission et la surpression de refoulement à l'échappement.The subject of the present invention is improvements to this type of compressor and to propose a new arrangement of inlet and outlet openings for the production of a compact positive displacement compressor, with low inertia, with rapid rotation and with high efficiency, by permanently providing, in each rotor, a buffer flow between the inlet and outlet openings, along which there prevails an intermediate pressure varying between atmospheric pressure at the inlet and the discharge overpressure at the exhaust.

Pour ce faire, selon une caractéristique de l'invention ,l'ouverture d'entrée est constituée,pour chaque chambre, d'un secteur annulaire d'angle d'ouverture inférieur à 200°, les deux secteurs annulaires étant sensiblement symétriques par rapport au plan d'intersection des chambres et séparés l'un de de l'autre par une portion centrale de la paroi.To do this, according to a characteristic of the invention, the inlet opening consists, for each chamber, of an annular sector with an opening angle less than 200 °, the two annular sectors being substantially symmetrical with respect to at the intersection plane of the chambers and separated from each other by a central portion of the wall.

Selon une autre caractéristique de l'invention, le passage de sortie communique avec les chambres par une ouverture de sortie formée dans une paroi périphérique du boltier, cette ouverture de sortie ayant une forme générale en V sensiblement centrée sur le plan d'intersection des chambres et dont les bords convergeant l'un vers l'autre sont, en projection, sensiblement parallèles eux filets des rotors respectifs.According to another characteristic of the invention, the outlet passage communicates with the chambers by an outlet opening formed in a peripheral wall of the bolt bowl, this outlet opening having a general V shape substantially centered on the plane of intersection of the chambers. and the edges of which converging towards each other are, in projection, substantially parallel to the threads of the respective rotors.

D'autres caractéristiques et avantages de le présente invention ressortiront de le description suivante d'un mode de réalisation, donné à titre illustratif et nullement limitatif, faite en relation avec des dessine annexés, sur lesquels :

  • - la figure 1 est une vue frontale d'un compresseur selon l'invention, montrant l'agencement relatif des sections annulaires constituant l'ouverture d'entrée d'air
  • - la figure 2 est une vue schématique du dessus du compresseur de la figure 1 montrant la disposition de l'ouverture de sortie ; et
  • la figure 3 est une vue schématique en perspective du compresseur des figures 1 et 2.
Other characteristics and advantages of the present invention will emerge from the following description of an embodiment, given by way of illustration and in no way limiting, made in relation to the accompanying drawings, in which:
  • - Figure 1 is a front view of a compressor according to the invention, showing the relative arrangement of the annular sections constituting the air inlet opening
  • - Figure 2 is a schematic top view of the compressor of Figure 1 showing the arrangement of the outlet opening; and
  • FIG. 3 is a schematic perspective view of the compressor of FIGS. 1 and 2.

Comme on le voit sur les figures, le compresseur à vis selon l'invention comprend un rotor mâle (1) et un rotor femelle (2) comportant chacun des filets hélicoideux disposés, de façon que les filets de chaque rotor coopèrent avec ceux de l'autre rotor en léger contact mutuel, dans une paire de chambres cylindriques parallèles (3) et (4), respectivement, intercommuniquant longitudinalement suivant un plan d'intersection parallèle aux axes Z et Z' communs au rotor mâle (1) et à la chambre (3), d'une part, et au rotor femelle (2) et à la chambre (4) d'autre part. Les rotors (1) et (2) sont couplés à une de leurs extrémités, dans l'exemple représenté,à une paire d'engrenanes (6) et (7) coopérant mutuellement sans jeu pour entraîner en synchronisme les rotors (1) et (2). Les engrenages (6) et (7) sont disposés dans une cavité intérieure du boîtier (5) séparée de façon étanche des chambres (3) et (4) par une cloison frontale dans lesquelles sont supportés à tourillonnement les rotors (1) et (2), ces derniers comprenant, à leurs extrémités opposées aux engrenages (6) et (7), des paliers supportés sur une paroi frontale d'extrémité (B) rapportée sur le boîtier (5). De préférence, l'axe (9) de l'engrenage (7) et du rotor femelle (2) est couplé a un dispositif d'entrainement du compresseur, l'engrenage (7) du rotor femelle (2) étant donc l'engrenage d'entrainement de l'engrenage (6) du rotor mâle (1), suivant un agencement général faisant l'objet du document EP-0101345 dont le contenu est supposé intégré ici pour référence.As can be seen in the figures, the screw compressor according to the invention comprises a male rotor (1) and a female rotor (2) each comprising helical threads arranged, so that the threads of each rotor cooperate with those of the 'other rotor in slight mutual contact, in a pair of parallel cylindrical chambers (3) and (4), respectively, intercommunicating longitudinally along a plane of intersection parallel to the axes Z and Z' common to the male rotor (1) and to the chamber (3), on the one hand, and to the female rotor (2) and to the chamber (4) on the other. The rotors (1) and (2) are coupled at one of their ends, in the example shown, to a pair of gears (6) and (7) cooperating mutually without play to synchronously drive the rotors (1) and (2). The gears (6) and (7) are arranged in an interior cavity of the housing (5) sealed from the chambers (3) and (4) by a front partition in which the rotors (1) and ( 2), the latter comprising, at their ends opposite the gears (6) and (7), bearings supported on a front end wall (B) attached to the housing (5). Preferably, the axis (9) of the gear (7) and of the female rotor (2) is coupled to a drive device of the compressor, the gear (7) of the female rotor (2) therefore being the drive gear of the gear (6) of the male rotor (1), according to a general arrangement which is the subject of document EP-0101345 the content of which is assumed to be incorporated here for reference.

Conformément à un aspect de l'invention, dans la paroi frontale d'extrémité (8) sont formées deux découpes traversantes en forme de secteurs annulaires (11) et (12) constituant l'ouverture d'entrée du compresseur. Chaque secteur annulaire (11) ou (12) a un profil extérieur centré sur l'axe correspondant Z ou Z' et de rayon correspondant à celui de la chambre associée (3) ou (4), et un profil intérieur en forme d'arc de cercle, également centré sur l'axe correspondant Z ou Z' et de rayon correspondant au rayon du moyeu du rotor correspondant (1) ou (2). Avantageusement, le rotor mêle comprend 4 lobes ou filets et le rotor femelle comprend 6 filets, les filets étant à profil symétrique ou légèrement assymétrique. Comme on le voit sur la figure 1, les deux secteurs (11) et (12) sont sensiblement symétriques par rapport au plan d'intersection des chambres (3) et (4) et sont séparés, au niveau de leurs zones les plus proches l'une de l'autre, par une portion centrale (13) de la paroi (8). Les bords adjacents (14) et (15) des secteurs (11) et (12) s'étendent radialement vers les axes respectifs Z et Z' en formant entre eux un angle inférieur à 90°, typiquement d'environ 80°. Le secteur annulaire (11) de la vis mâle présente un angle d'ouverture α inférieur à 180°, typiquement d'environ 1650. Par contre, le secteur annulaire (12) de la vis femelle (2) présente un angle d'ouverture β supérieur à 180° mais inférieur à 200°, typiquement d'environ 190°.According to one aspect of the invention, in the front end wall (8) are formed two through cutouts in the form of annular sectors (11) and (12) constituting the inlet opening of the compressor. Each annular sector (11) or (12) has an external profile centered on the corresponding axis Z or Z 'and of radius corresponding to that of the associated chamber (3) or (4), and an internal profile in the form of arc of a circle, also centered on the corresponding axis Z or Z 'and of radius corresponding to the radius of the hub of the corresponding rotor (1) or (2). Advantageously, the mixed rotor comprises 4 lobes or threads and the female rotor comprises 6 threads, the threads being of symmetrical or slightly asymmetrical profile. As can be seen in FIG. 1, the two sectors (11) and (12) are substantially symmetrical with respect to the plane of intersection of the chambers (3) and (4) and are separated, at the level of their closest zones. one from the other, by a central portion (13) of the wall (8). The adjacent edges (14) and (15) of the sectors (11) and (12) extend radially towards the respective axes Z and Z ', forming between them an angle less than 90 °, typically about 80 °. The annular sector (11) of the male screw has an opening angle α less than 180 °, typically around 165 ° . On the other hand, the annular sector (12) of the female screw (2) has an opening angle β greater than 180 ° but less than 200 °, typically around 190 °.

Comme on le voit sur les figures 2 et 3, dans une paroi latérale du boîtier (5) opposée,par rapport au plan des axes Z et Z', à la portion centrale de séparation (13) de la paroi (8), est formée une ouverture de sortie en V (16) de profil général sensiblement triangulaire avec une base perpendiculaire aux axes Z et Z', à légère distance de l'extrémité des rotors (1) et (2) opposée à la paroi (8), et des bords convergents (17) et (18) s'étendant, en projection dans un plan parallèle au plan des axes Z et Z', sensiblement parallèlement aux filets des rotors respectifs (1) et (2), comme on le voit bien sur la figure 2. De préférence, le sommet du triangle est tronqué, l'ouverture de sortie (16) présentant en conséquence un petit bord transversal (19) opposé à la base et parallèle à cette dernière. Corrélativement, la base présente centralement une partie en saillie (20) d'extension transversale correspondant sensiblement à celle du petit côté (19). Comme on le voit sur la figure 2, l'ouverture de sortie (16) est sensiblement centrée sur le plan d'intersection des chambres (3) et (4) mais présente une légère dissymétrie pour tenir compte du nombre de filets différents sur les rotors mâle (1) et femelle (2). Conformément à un aspect de l'invention, le hauteur axiale maximale de l'ouverture (16) (entre as grande base et le petit côté (19))est inférieure au double de la distance axiale entre deux filets de rotors adjacente, typiquement de l'ordre de 1,25 fois le distance axiale entre filets de rotors adjacents. Dans l'exemple représenté sur la figure 3, on notera que la longueur hors-tout des rotors correspond sensiblement à la moitié du pas des filets de chaque rotor.As seen in Figures 2 and 3, in a side wall of the housing (5) opposite, relative to the plane of the axes Z and Z ', to the central separation portion (13) of the wall (8), is formed a V-shaped outlet opening (16) of generally triangular profile with a base perpendicular to the axes Z and Z ', at a slight distance from the end of the rotors (1) and (2) opposite the wall (8), and converging edges (17) and (18) extending, in projection in a plane parallel to the plane of the axes Z and Z ', substantially parallel to the threads of the respective rotors (1) and (2), as can be seen in FIG. 2. Preferably, the top of the triangle is truncated, the outlet opening (16) consequently having a small transverse edge (19) opposite the base and parallel to the latter. Correspondingly, the base has a central projecting portion (20) of transverse extension corresponding substantially to that of the short side (19). As seen in Figure 2, the outlet opening (16) is substantially centered on the plane of intersection of the chambers (3) and (4) but has a slight asymmetry to take account of the number of different threads on the male (1) and female (2) rotors. In accordance with one aspect of the invention, the maximum axial height of the opening (16) (between the large base and the short side (19)) is less than twice the axial distance between two adjacent rotor threads, typically of the order of 1.25 times the axial distance between adjacent rotor threads. In the example shown in FIG. 3, it will be noted that the overall length of the rotors corresponds substantially to half the pitch of the threads of each rotor.

Avec l'agencement ainsi décrit, et en se référant à la configuration représentée sur les dessins, on note, compte tenu des sens de rotation figurés par les flèches, que la veine B de la vis mâle (1) et la veine B' de la vis femelle (2) entrent en communication ou en interpénétration l'une avec l'autre en étant isolées, du côté de leur extrémité d'admission, des ouvertures d'entrée (11) et (12). Il en est de même pour les veines C et C' qui vont cesser, elles, d'être confondues pour entrer par contre en communication avec les ouvertures d'entrée correspondantes (11) et (12). Par ailleurs la veine A, également occultée par la paroi (8) est en communication avec la veine D' de la vis femelle (2) qui elle communique avec l'ouverture d'entrée (12). Par contre, la veine A', dans la configuration représentée, est elle totalement fermée. On comprendra donc que les veines B et B' demeurent fermées pour une demi rotation de chaque rotor, ces veines jouant ainsi le rôle de veines tampons entre l'admission (11,12) et l'échappement (16), la pression de l'air dans ces veines B et B' croissant d'une valeur égale à la pression atmosphérique jusqu'à une pression nominale de compression, de l'ordre de 1,6 bar absolu , à la limite de l'échappement. On réalise donc ainsi, dans un agencement particulièrement compact et à pas important, une isolation parfaite entre l'admission et l'échappement grâce aux veines tampons où la pression croit progressivement au fur et à mesure de la rotation, jusqu'à la pression nominale de compression, à la limite de l'échappement, fournissant ainsi une pression de refoulement sensiblement constante et présentant des battements fortement atténués.With the arrangement thus described, and with reference to the configuration shown in the drawings, it is noted, taking into account the directions of rotation shown by the arrows, that the vein B of the male screw (1) and the vein B 'of the female screw (2) enter into communication or interpenetration with one another being isolated, on the side of their intake end, from the inlet openings (11) and (12). It is the same for the veins C and C 'which will cease to be confused to enter on the other hand in communication with the corresponding inlet openings (11) and (12). Furthermore the vein A, also concealed by the wall (8) is in communication with the vein D 'of the female screw (2) which it communicates with the inlet opening (12). On the other hand, the vein A ′, in the configuration shown, is it completely closed. It will therefore be understood that the veins B and B 'remain closed for a half rotation of each rotor, these veins thus playing the role of buffer veins between the intake (11,12) and the exhaust (16), the pressure of the 'air in these veins B and B' increasing by a value equal to atmospheric pressure up to a nominal compression pressure, of the order of 1.6 bar absolute, at the limit of the exhaust. Thus, in a particularly compact and large pitch arrangement, a perfect isolation between the intake and the exhaust is achieved thanks to the buffer veins where the pressure gradually increases as the rotation proceeds, up to the nominal pressure. compression, at the limit of the exhaust, thus providing a substantially constant discharge pressure and having greatly attenuated beats.

Quoique la présente invention ait été décrite en relation avec des modes de réalisation particuliers, elle ne s'en trouve pas limitée mais est au contraire susceptible de modifications et de variantes qui apparaîtront à l'home 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 (10)

1. Compresseur à vie, comprenant un rotor mâle (1) et un rotor femelle (2) coopérante, disposés dans une paire de chambres cylindriques intercommuniquantes (3,4) formées dans un boiter (5), un passage d'admission (11,12) communiquant avec une extrémité de la paire de chambres (3,4) par une ouverture d'entrée (11,12) délimitée, à cette extrémité de la paire de chambres,par une paroi (8) occultant partiellement des portions adjacentes de chaque chambre (3,4),et un passage de sortie communiquant avec l'autre extrémité de cette paire de chambres, caractérisé en ce que l'ouverture d'entrée est constituée, pour chaque chambre (3,4), d'un secteur annulaire (11,12) d'angle d'ouverture (α,β) inférieur à 200 degrés, les deux secteurs annulaires étant sensiblement symétriques par rapport au plan d'intersection des chambres (3,4) et séparés l'un de l'autre par une portion centrale (13) de la paroi (8).1. Lifetime compressor, comprising a cooperating male rotor (1) and a cooperating female rotor (2), arranged in a pair of intercommunicating cylindrical chambers (3,4) formed in a housing (5), an intake passage (11 , 12) communicating with one end of the pair of chambers (3,4) by an inlet opening (11,12) delimited, at this end of the pair of chambers, by a wall (8) partially obscuring adjacent portions of each chamber (3,4), and an outlet passage communicating with the other end of this pair of chambers, characterized in that the inlet opening consists, for each chamber (3,4), of an annular sector (11,12) with an opening angle (α, β) less than 200 degrees, the two annular sectors being substantially symmetrical with respect to the plane of intersection of the chambers (3,4) and separated one on the other by a central portion (13) of the wall (8). 2. Compresseur selon la revendication 1, caractérisé en ce que le passage de sortie communique avec les chambres (3,4) par une ouverture de sortie (16) formée dans une paroi périphérique du boîtier (5). cette ouverture de sortie (16) ayant une forme générale en V sensiblement centré sur le plan d'intersection des chambres (3,4) et dont les bords conver- geants (17,18) sont,en projection, parallèles aux filets des rotors respectifs (1,2).2. Compressor according to claim 1, characterized in that the outlet passage communicates with the chambers (3,4) by an outlet opening (16) formed in a peripheral wall of the housing (5). this outlet opening (16) having a general V shape substantially centered on the plane of intersection of the chambers (3, 4) and whose converging edges (17, 18) are, in projection, parallel to the threads of the rotors respective (1,2). 3. Compresseur selon la revendication 1 ou la revendication 2, caractérisé en ce que la hauteur axiale du V de l'ouverture de sortie (16) est inférieure au double de la distance axiale entre deux filets de rotors adjacents.3. Compressor according to claim 1 or claim 2, characterized in that the axial height of the V of the outlet opening (16) is less than twice the axial distance between two adjacent rotor threads. 4. Compresseur selon la revendication 3, caractérisé en ce que la hauteur axiale du V de l'ouverture de sortie (16) est sensibelemnt égale à 1,25 fois la distance axiale entre deux filets de rotors adjacents.4. Compressor according to claim 3, characterized in that the axial height of the V of the outlet opening (16) is sensitelemnt equal to 1.25 times the axial distance between two adjacent rotor threads. 5. Compresseur selon l'une des revendications précédentes, caractérisé en ce qu'il comprend au moins une paire d'engrenages (6,7) d'entraînement en synchronisme des rotors (1,2) supportés'dans le boîtier (5) au voisinage de ladite autre extrémité de la paire de chambres (3,4).5. Compressor according to one of the preceding claims, characterized in that it comprises at least one pair of gears (6,7) for synchronous drive of the rotors (1,2) supported in the housing (5) in the vicinity of said other end of the pair of chambers (3,4). 6. Compresseur selon la revendication 5, caractérisé en ce que ladite paroi (8) délimitant l'ouverture d'entrée est une paroi frontale rapportée sur l'extrémité du boîtier (5) opposée aux engrenages (6,7) et supportant des paliers pour les rotors (1,2).6. Compressor according to claim 5, characterized in that said wall (8) delimiting the inlet opening is a front wall attached to the end of the housing (5) opposite the gears (6,7) and supporting bearings for rotors (1,2). 7. Compresseur selon l'une des revendications précédentes, caractérisé en ce que le rotor mâle (1) comporte quatre filets et le rotor femelle (2) six filets.7. Compressor according to one of the preceding claims, characterized in that the male rotor (1) has four threads and the rotor female (2) six fillets. 8. Compresseur selon la revendication 7, caractérisé en ce que le secteur annulaire d'entrée (11) pour le rotor mâle (1) a un angle d'ouverture (α) inférieur à 180 degrés.8. Compressor according to claim 7, characterized in that the annular inlet sector (11) for the male rotor (1) has an opening angle (α) less than 180 degrees. 9. Compresseur selon la revendication 7 ou le revendication 8, caractérisé en ce que le secteur annulaire d'entrée (12) pour le rotor fe- melle(2) a un angle d'ouverture (β) supérieur à 180 degrés.9. Compressor according to claim 7 or claim 8, characterized in that the annular inlet sector (12) for the female rotor (2) has an opening angle (β) greater than 180 degrees. 10. Compresseur selon l'une des revendications précédentes caractérisé en ce que les extrémités radiales adjacentes (14,15) des secteurs annulaires d'entrée (11,12) forment entre elles un angle d'environ 80 degrés.10. Compressor according to one of the preceding claims, characterized in that the adjacent radial ends (14,15) of the annular inlet sectors (11,12) form between them an angle of approximately 80 degrees.
EP85400531A 1984-03-28 1985-03-20 Volumetric screw compressor Expired EP0161130B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8404841 1984-03-28
FR8404841A FR2562166B1 (en) 1984-03-28 1984-03-28 VOLUMETRIC SCREW COMPRESSOR

Publications (2)

Publication Number Publication Date
EP0161130A1 true EP0161130A1 (en) 1985-11-13
EP0161130B1 EP0161130B1 (en) 1988-03-02

Family

ID=9302560

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85400531A Expired EP0161130B1 (en) 1984-03-28 1985-03-20 Volumetric screw compressor

Country Status (9)

Country Link
US (1) US4588363A (en)
EP (1) EP0161130B1 (en)
JP (1) JP2589972B2 (en)
AU (1) AU566579B2 (en)
DE (1) DE3561761D1 (en)
ES (1) ES295665Y (en)
FR (1) FR2562166B1 (en)
MX (1) MX158277A (en)
SU (1) SU1378790A3 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2501966Y2 (en) * 1989-09-14 1996-06-19 小川精機株式会社 Supercharger
US6599112B2 (en) 2001-10-19 2003-07-29 Imperial Research Llc Offset thread screw rotor device
US6786710B2 (en) * 2002-08-27 2004-09-07 Carrier Corporation Discharge porting for screw compressor with tangential flow guide cusp
JP2005315149A (en) * 2004-04-28 2005-11-10 Toyota Industries Corp Screw type fluid machine
CN100417816C (en) * 2005-09-30 2008-09-10 浙江大学 Screw profile for high-flow high-pressure three-screw pump
CN100360808C (en) * 2005-09-30 2008-01-09 陈行 Unequal-tooth-number screw profile for high-flow high-pressure three-screw pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2287716A (en) * 1941-04-22 1942-06-23 Joseph E Whitfield Fluid device
US2410172A (en) * 1941-05-31 1946-10-29 Jarvis C Marble Rotary screw wheel apparatus
CH325597A (en) * 1953-04-06 1957-11-15 Dresser Ind Volumetric rotary machine
GB959833A (en) * 1959-06-04 1964-06-03 Svenska Rotor Maskiner Ab Improvements in or relating to screw rotor machines
DE1949175A1 (en) * 1969-09-29 1971-04-01 Borisoglebskij Aleksandr I Rotary piston machine with helical wheels

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3073514A (en) * 1956-11-14 1963-01-15 Svenska Rotor Maskiner Ab Rotary compressors
US3108740A (en) * 1960-06-17 1963-10-29 Svenska Rotor Maskiner Ab Regulating means for rotary piston compressors
US3414189A (en) * 1966-06-22 1968-12-03 Atlas Copco Ab Screw rotor machines and profiles
GB1248031A (en) * 1967-09-21 1971-09-29 Edwards High Vacuum Int Ltd Two-stage rotary vacuum pumps
GB1548663A (en) * 1975-06-24 1979-07-18 Maekawa Seisakusho Kk Refrigerating apparatus
JPS5430520A (en) * 1977-08-12 1979-03-07 Hitachi Ltd Screw compressor
JPS5996494A (en) * 1982-11-25 1984-06-02 Hitachi Ltd Screw hydraulic machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2287716A (en) * 1941-04-22 1942-06-23 Joseph E Whitfield Fluid device
US2410172A (en) * 1941-05-31 1946-10-29 Jarvis C Marble Rotary screw wheel apparatus
CH325597A (en) * 1953-04-06 1957-11-15 Dresser Ind Volumetric rotary machine
GB959833A (en) * 1959-06-04 1964-06-03 Svenska Rotor Maskiner Ab Improvements in or relating to screw rotor machines
DE1949175A1 (en) * 1969-09-29 1971-04-01 Borisoglebskij Aleksandr I Rotary piston machine with helical wheels

Also Published As

Publication number Publication date
MX158277A (en) 1989-01-18
AU566579B2 (en) 1987-10-22
FR2562166B1 (en) 1986-07-18
ES295665U (en) 1987-03-16
ES295665Y (en) 1987-11-01
EP0161130B1 (en) 1988-03-02
DE3561761D1 (en) 1988-04-07
AU4005085A (en) 1985-10-03
JP2589972B2 (en) 1997-03-12
US4588363A (en) 1986-05-13
JPS60219486A (en) 1985-11-02
SU1378790A3 (en) 1988-02-28
FR2562166A1 (en) 1985-10-04

Similar Documents

Publication Publication Date Title
EP0161130B1 (en) Volumetric screw compressor
FR2572470A1 (en) REVERSIBLE FLOW PALLET PUMP.
FR2570444A1 (en) VANE PUMP
BE1005290A3 (en) IMPROVEMENTS OF COMPRESSOR REGENERATIVE TYPE A toroidal chamber.
FR2580441A1 (en) IMPROVEMENTS IN THE INDUCED ROTORS OF ELECTROMAGNETIC RETARDERS
FR2611377A1 (en) SIDE CHANNEL PUMP
CH667697A5 (en) ROTARY INTERNAL COMBUSTION ENGINE.
FR2567971A1 (en) COMPRESSOR FOR THERMAL MOTORS OF VEHICLES
FR2687728A1 (en) VOLUMETRIC MACHINE WITH LOUVOYING PISTONS, IN PARTICULAR A FOUR-STROKE ENGINE.
EP0751297A1 (en) Turbo molecular pump
FR2509802A1 (en) PUMPS AND MOTORS
FR2588322A1 (en) Hydraulic machine of modular structure
FR2740274A1 (en) ALTERNATOR HAVING IMPROVED INTERNAL VENTILATION MEANS
FR2469581A1 (en) Rotary compressor with seal strips slidable in rotor slots - has slots widened at outer ends to prevent jamming of deformed strip tips
EP0350408A2 (en) Suction device for kitchen extractor, air cleaner and extractor containing such a device
FR2611818A1 (en) Molecular rotary vacuum pump of the Gaëde channel type
EP1012479B1 (en) Turbine pump with improved efficiency for motor vehicle fuel tank
FR2497881A1 (en) Positive displacement hydraulic gear pump - has male and female interlocking rotors with one or two engaging teeth
FR2684417A1 (en) Vacuum pump of the screw type
FR3005106A1 (en) ROTARY VOLUMIC MACHINE WITH THREE PISTONS
EP0115228A1 (en) Volumetric machine with conical screws
EP0851980B1 (en) Rotary vane pump
JPH01234655A (en) Plastic gear
WO1988005118A1 (en) Profiles of screw-type rotors for rotary machines conveying a gaseous fluid
FR2605685A1 (en) Casing for an axial fan of the flat type

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19850329

AK Designated contracting states

Designated state(s): CH DE GB IT LI SE

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BENDIX FRANCE

17Q First examination report despatched

Effective date: 19860825

ITF It: translation for a ep patent filed

Owner name: ING. ZINI MARANESI & C. S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE GB IT LI SE

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

Ref document number: 3561761

Country of ref document: DE

Date of ref document: 19880407

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

26N No opposition filed
ITTA It: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 85400531.1

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: GB

Payment date: 20040205

Year of fee payment: 20

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

Ref country code: SE

Payment date: 20040303

Year of fee payment: 20

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

Ref country code: CH

Payment date: 20040319

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20040331

Year of fee payment: 20

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

Ref country code: LI

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20050319

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20050319

Ref country code: CH

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20050319

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

EUG Se: european patent has lapsed