EP0135256B1 - Assemblage d'un compresseur à suralimentation et fixation de phase de rotors - Google Patents

Assemblage d'un compresseur à suralimentation et fixation de phase de rotors Download PDF

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Publication number
EP0135256B1
EP0135256B1 EP84304078A EP84304078A EP0135256B1 EP 0135256 B1 EP0135256 B1 EP 0135256B1 EP 84304078 A EP84304078 A EP 84304078A EP 84304078 A EP84304078 A EP 84304078A EP 0135256 B1 EP0135256 B1 EP 0135256B1
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EP
European Patent Office
Prior art keywords
rotors
shaft
shafts
gear
lobes
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
EP84304078A
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German (de)
English (en)
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EP0135256A1 (fr
Inventor
Raymond Adrian Soeters, Jr.
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Eaton Corp
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Eaton Corp
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Publication date
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Priority to AT84304078T priority Critical patent/ATE34602T1/de
Publication of EP0135256A1 publication Critical patent/EP0135256A1/fr
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Publication of EP0135256B1 publication Critical patent/EP0135256B1/fr
Expired legal-status Critical Current

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    • 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
    • F04C18/126—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 radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions

Definitions

  • This invention relates to rotary compressors or blowers, particularly to blowers of the Roots-type. More specifically, the present invention relates to a method of assembling such blowers and to a fixture for timing the rotors and gears of such a blower.
  • Rotary blowers particularly Roots-type blowers employed as superchargers for internal combustion engines are well-known in the prior art. However, they have not been widely used, particularly in passenger cars for several reasons since they, in general, have been characterized by several problems such as noisy operation, relatively high manufacturing and assembly costs, low efficiency and/or poor durability. Quite often, all or many of these problems are related to the basic design of a few components in such blowers since these basic designs often dictate machining costs and/or assembly methods which in turn may lead to one or more other problems such as noise, efficiency, and/or durability.
  • a rotary blower or supercharger designed to negate or substantially reduce all of the above-stated problems.
  • the rotors, shafts, and timing gears of the supercharger disclosed herein require no premachining or machining during assembly to effect proper timing.
  • the shafts may be pressed into the rotors without concern of phase relation or timing.
  • the supercharger may be partially assembled and one of the timing gears installed without concern of phase relation or timing.
  • the supercharger disclosed herein is designed to be accurately and quickly timed during assembly by a specially designed fixture.
  • United States Patent 3,192,639 discloses a machine for angularly relating (timing) the rotors, shafts and timing gears of a rotary blower in accordance with the precharacterized portions of Claims 1 and 9 herein.
  • the invention is characterized alternatively by the machine according to Claim 1 or the method according to Claim 9:
  • Figure 1 illustrates a Roots-type blower or compressor 10 including a housing assembly 12 having a main or center housing section 14 and end sections 16, 18, a pair of rotors 20, 22 mounted on parallel shafts 24, 26 to define rotor assemblies, bearing assemblies 28, 30 disposed at adjacent end faces 20a, 22a of the rotors, bearing assemblies 32, 34 disposed at the other adjacent end faces 20b, 22b of the rotors, and timing gears 36, 38 secured to the shafts 24, 26.
  • Shaft 24 and gear 36 are driven elements and shaft 26 and gear 38 are drive or driving elements with respect to the driven elements.
  • Bearings 28, 30, 32, 34 are by definition antifriction bearings, i.e., rolling contact bearings.
  • Housing assembly 10 is preferably a lightweight material such as aluminum.
  • the assembly includes or defines a pair of generally cylindrical working chambers 42, 44 defined circumferentially by cylindrical wall portions 14a, 14b and end wall portions 14c, 18a defining end surfaces normal to the cylindrical wall portions.
  • the chambers transversely overlap each other and the end walls of both chambers are disposed in common planes.
  • the housing assembly further includes a chamber 46 separated from chambers 42, 44 by end wall portion 14c, an annular axially extending side wall portion 14d having a plurality of threaded bores 48 for securing end section 16 thereto by bolts 50, a plurality of threaded bores 52 for securing end section 18 to the other end of the housing by bolts 54, a plurality of cooling and reinforcing ribs 14e, an outlet or discharge port 56 seen only in Figure 2, and an unshown inlet or suction port.
  • the inlet port has its entrance defined by end section 18; the port extends axially into chambers 42, 44 with a decreasing cross-sectional area that terminates just short of a cusp 14f defined by the intersection of cylindrical wall portions 14a, 14b as seen in Figure 2.
  • End wall portion 14c includes through bores 58, 60 having major diameters 58a, 60a and shoulders 58b, 60b for supporting and positioning bearing assemblies 28, 30 in the housing; intermediate diameters provide support for radial seals 62, 64.
  • End section 16 includes a bore 66 having a ball or antifriction bearing 68 disposed therein for supporting the drive end of driving shaft 26 and a seal 70 for sealing chamber 46 from the ambient or the exterior of the housing assembly.
  • Chamber 46 contains oil for lubricating ball bearings 28,30, 68 and gears 36, 38.
  • Rotors 20, 22 are preferably formed of a lightweight material such as aluminum.
  • the rotors are shown fragmentally in Figure 1.
  • Each rotor includes three helical teeth or lobes 20c, 22c of modified involute profile, as shown in Figure 2, an axially extending bore 20d, 22d having an axis concentric to the lobes, and alignment or phasing holes 20e, 22e extending axially into end faces 20b, 22b of each lobe.
  • the lobes pump or transport a fluid, such as air, from the housing inlet to the housing outlet.
  • the bores are identical and each includes, as viewed from left-to-right in Figure 1, a first diameter bore portion 20f, 22f extending from a shoulder defined by the end face of a small hub portion 20g, 22g projecting axially from end face 20a, 22a to a shoulder 20h, 22h defined by the difference in diameter between the first bore portion and a second bore portion 20i, 22i of reduced diameter.
  • the cylindrical walls of the first and second bore portions are machined smooth and the axial distances between the end faces of hub portions 20g, 22g and shoulders 20h, 22h are closely controlled for reasons discussed hereinafter.
  • Rotors 20, 22 are disclosed herein in Figure 2 with three circumferentially disposed lobes extending helically about the axis of their respective shafts or bores. and with modified involute profiles. However, other well-known rotor forms may be employed, such as two lobe with or without involute lobes, straight lobes extending parallel to the rotor axis, etc.
  • any clearance provided to prevent such touching should be held to an absolute minimum. This minimum clearance is determined by several factors, such as, machining tolerances of individual parts, stack-up tolerances during assembly, backlash in the timing gears 36, 38, radial and axial growth of parts relative to each other due mainly to nonuniform temperature changes and differences in coefficient of expansion of parts, and radial and axial bearing play.
  • driven shaft 24 and driving shaft 26 respectively include bosses 24a, 24b and 26a, 26b for rotationally supporting the rotor and shaft assemblies in bearing assemblies 28, 30, 32, 34.
  • Shafts 24, 26 are identical between these bosses.
  • a description of portions of shaft 24 between bosses 24a, 24b will suffice for both shafts and will require further detailed description only with respect to shaft portions to the left of bosses 24a, 26a for both shafts as viewed in Figure 1.
  • Portions of shaft 26 between bosses 26a, 26b are not given reference characters to avoid undue clutter of the drawings.
  • shaft 24 includes a boss 24c having radial seal 62 running thereon, a shoulder 24d which abuts the end face of hub portion 20g to define the axial position of the shaft in the rotor bore, a rolled spline portion 24e, and smooth surface portions 24f, 24g which respectively form interference fits with bore portions 20f, 20i, when shaft is pressed into place.
  • Shoulder 24d ensures that growth difference between the shaft and rotor are to the right of the shoulder or are a minimum at the splines.
  • Smooth surface portions 24f, 24g are axially separated by a shaft portion 24h and a conical or chamfered portion 24i.
  • the right end of smooth surface portion 24g also includes a conical or chamfered portion 24j.
  • Shaft 24 is preferably formed from steel.
  • Splines 24e extend parallel to the axis of shaft 24 and function similar to a broach when shaft 24 is pressed into bore 20, i.e., splines 24e form mating splines in the bore.
  • the self-broaching function of splines 24e ma; be improved by application of a hardening process to the splines.
  • the left end of shaft 24 is similar to the portions of the shaft between seal boss 24c and bearing boss 24b, i.e., the left end includes smooth surface portions 24k, 24m which form interference fits with stepped bore portions 36a, 36b in gear 36 and a rolled spline portion 24n having axially extending splines which function similar to a broach when gear 36 is pressed on the shaft.
  • Gear 36 is preferably of variable hardness, i.e, the tooth portion of the gear is hardened and the hub portion is relatively soft to allow the self-broaching by the shaft splines 24n.
  • gear 36 may be of uniform hardness and have internal splines in which case the steps at the shaft end would be smooth and relatively soft.
  • the left end of shaft 26, as shown in Figure 1, includes an annular recess 26k having a snap ring 71 disposed therein for positioning a shim 73, a tapered or conical portion 26m for receiving a mating conical bore 38a in gear 38, a threaded portion having a nut 72 threaded thereon for securing or seating the gear on the tapered portion, a boss 26n having the inner race of bearing 68 lightly pressed thereon, a boss 26p having radial seal 70 running thereon, and a drive end 26q having a key slot 26r for keying a V-pulley or the like to the shaft.
  • the modified form includes a shaft 74 and a gear 76 which respectively replace shaft 26 and gear 38.
  • Shaft 74 and gear 76 are configured to be joined together in the same manner as shaft 24 and gear 36, all other parts of 74 and gear 76 are the same as described for shaft 26 and gear 38.
  • the axial position of gear 76 on shaft 74 is set during assembly by an annular shim 77.
  • Ball-bearing assembly 28 includes inner and outer races 78, 80 and a plurality of balls or rolling contact means 82 which interconnect the races with a limited amount of radial and axial bearing play between the races.
  • the outer race is snugly pressed into the major diameter portion 58a of bore 58 and seated against shoulder 58b which fixes the axial position of the bearing assembly with respect to end wall portion 14c of chamber 42.
  • the inner race is snugly pressed on boss 24a and is axially positioned on the boss by an annular shim 84 whose thickness is determined during assembly of the supercharger as explained hereinafter.
  • Bearing assembly 32 includes a steel or wear resistant sleeve 86 snugly pressed into a stepped bore 88 in end section 18, outer and inner races 90, 92, a plurality of balls or rolling contact means 94, a seal 96, a spring assembly 98 having two Belleville or cone-disk springs reacting between outer race 90 and a steel washer 100, a snap ring 102, and a cap or plug 104 for sealing the bearing from the ambient or the exterior of the housing assembly and thereby defining in combination with seal 96 a cavity containing a lubricant such as grease.
  • Outer race 90 forms a close tolerance, sliding fit with steel sleeve 86 and the inner race forms a snug press fit with boss 24b.
  • Steel sleeve 86 prevents fretting of the aluminum structure of end section 18.
  • Spring assembly 98 biases shaft 24 and rotor 20 to the right and hence biases inner race 92 and shaft 24 to the right.
  • Snap ring 102 ensures retention of the inner race on boss 24b.
  • Balls 94 of bearings 32, 34, like balls 82 of bearings 28, 30, interconnect the outer and inner races with a limited amount of radial and axial bearing play therebetween.
  • Inner race 92 is preferably pressed on boss 24b; alternatively the inner race may form a close tolerance sliding fit with boss 24b, in which case snap ring 102 then prevents axial movement of the race in one direction.
  • bearings designed to react radial and axial forces are manufactured such that the balls interconnect their outer and inner races with limited amounts of radial and axial bearing play therebetween.
  • Some of the bearing play is intentionally built into the bearing during manufacture to allow for shrinkage of the outer race when it is pressed into a bore, expansion of the inner race when it is pressed on a shaft, and thermal growth when the bearing reaches operating temperature during use. Additionally, some of the bearing play is due to manufacturing tolerances of the bearing and some is due to manufacturing tolerances of the bores and shafts that receive the races. These manufacturing tolerances may vary over a rather wide range and, in general, decrease with increasing manufacturing costs. In a Roots blower wherein the bearings are subjected to fluctuating loads, the tolerance affects bearing noise, bearing life, and the running clearances between the rotors and blower housing and between the meshed lobes of the rotors.
  • the rotor and shaft assemblies are readily positioned with respect to each other and with respect to their cylindrical and end wall surfaces without meticulous adjustments during assembly even when axial and radial play in the ball bearing assemblies varies over rather wide ranges. Further, the bearing play is effectively reduced to zero without fear of bearing overload, thereby reducing bearing noise, improving bearing life, and facilitating the use of minimum running clearances between the meshed lobes of the rotors and the housing surfaces defining chambers 42, 44.
  • the rotors and/or the housing surfaces may be coated with an abradable graphite material such as 2ES which is obtainable from Superior Graphite Company, 20 North Wacker Drive, Chicago, II 60606.
  • abradable graphite material such as 2ES which is obtainable from Superior Graphite Company, 20 North Wacker Drive, Chicago, II 60606.
  • the material which may be sprayed on, readily wears or abrades in response to contact with relatively moveable surfaces until substantially zero clearance exists therebetween.
  • Supercharger 10 is designed to be readily and accurately assembled in mass production.
  • the rotors and their associated shafts are assembled first. Since the aluminum of the rotors has a greater coefficient of expansion than the steel of the shafts, the amount of interference fit between the smooth surface shaft portions and their associated bore portions is calculated to ensure an interference fit when the rotors are operating at their maximum design temperature. To prevent metal deformation such as galling of the rotor bores and bending of the shafts while the shafts are being pressed into the bores, the rotors are preheated to their maximum calculated design temperature.
  • the shafts When the shafts are first place into their respective bores, they freely enter until their chamfered portions seat against the shoulders defined by the hub portions 20g, 22g and portions 20h, 22h defined by the difference in diameter of the bore portions.
  • the axially spaced apart chamfers ensure axial alignment of the shafts in the bores as the shafts are pressed into the bores.
  • the broach shaped splines on the shafts cut mating splines in the smoothly machined surfaces of the bore portions 20f, 22f.
  • This self-broaching feature reduces machining costs of the rotors, since the relatively expensive process of forming internal splines or keyways in a small diameter bore is avoided, reduces assembly costs since the shafts may be pressed into the rotor bores without concern of angular phasing or timing between the shafts and their associated rotors as is necessary when both the shafts and rotor bores have previously machined splines or keyways, and the self-broaching ensures substantially perfect concentricity between the shaft and rotor axes since any lack of concentricity of the self-boaching splines and the shaft axis will not effect shaft-rotor concentricity.
  • the shaft-rotor assemblies are then placed on a phasing and assembly fixture or machine 200 illustrated in Figures 5 and 6 to facilitate positioning the rotors in housing 14 and installation of bearings 28, 30.
  • This part of the assembly may be accomplished prior to use of fixture 200.
  • the fixture includes a rectangular base 202 having longitudinally extending sides 202a, 202b, transversely extending ends 202c, 202d, a flat upper surface 202e, a first raised surface 202f of somewhat crescent shape, first and second stepped through bores 204, 206, a stepped annular recess 208, a through bore 210 extending longitudinally between ends 202c, 202d, a stepped bore 212 extending transversely between sides 202a, 202b and intersecting recess 208 and bore 210, a stepped bore 214 extending between end 202c and stepped bore 204, a stepped bore 216 extending between end 202d and stepped recess 208 and a bore
  • End plates 220, 222 are fixed to the base by a plurality of bolts 224.
  • the fixture may be moved about by handle 221, 223 fixed to the end plates.
  • Bores 210, 218 are closed at end 202d by end plate 222.
  • Bore 212 is closed at side 202a by a cover 226 fixed to the base by a plurality of cap screws 228 and is closed at side 202b by a dial indicator mount 230 fixed to the base by a plurality of cap screws 232.
  • Stepped bore 204 includes a reduced diameter portion 204a machined to close tolerance for sliding receipt of boss 26b of supercharger shaft 26.
  • Bore 214 includes a portion 214a threadably receiving a lock screw 234 fixed to a knob 236 via a shaft 238 for selectively locking shaft 26 and rotor 22 against rotation relative to surface 202f.
  • Stepped annular recess 208 includes an inner wall surface or hub 208a and a shoulder or support surface 208b both machined to close tolerance for radially and vertically positioning an annular member 240 in the recess for close tolerance rotation about the axis of bore 206.
  • Annular member 240 includes a second or upper surface portion 240a disposed in a plane common to the plane of surface 202f, a stepped through bore 242 having a dowel 244 pressed therein and projecting upward beyond surface 240a for forming a close tolerance sliding fit with one of the phasing holes 20e in rotor 20, and an annular gear or pinion 246 having external spur gear teeth 246a with a pitch diameter or circle equal to the pitch diameter or circle of lobes 20c of rotor 20.
  • a snap ring 248 retains the annular member in recess 208 and a plurality of screws 250 fixing the pinion to the annular member with the pitch circle concentric with the axis of bore 206.
  • Bore 206 includes a reduced diameter portion 206a machined to close tolerance for receiving boss 24b of rotor shaft 24.
  • the transverse spacing of bore portions 204a, 206a is the same as the transverse spacing of bores 58, 60 in end wall portion 14c of the supercharger housing 14. Accordingly, when the partially assembled supercharger is placed on fixture 200, as shown in Figure 6, the axes of shafts 24, 26 assume the same parallel relation to each other they will have after final assembly of the supercharger.
  • Bore 216 includes a portion 216a threadably receiving a lock screw 252 fixed to a knob 254 via a shaft 256 for selectively locking annular member 240 against rotation in recess 208 and accordingly preventing rotation of shaft 24 and rotor 20.
  • Stepped bore 212 includes a bore portion 212a forming a close tolerance sliding fit with a member 258 having a bifurcated end 258a slidably receiving one end of a rack gear 260 having teeth 260a in mesh with pinion teeth 246a. End 258a is partially sectioned and shows only the bottom tine projecting beyond the rack.
  • the other end of member 258 includes an annular flange or head 258b which limits movement of the member into the bore and which contacts a dial indicator link 262.
  • Rack gear 260 is loosely connected to member 258 by a pin 264 pressed into transverse bores in the tines at the bifurcated end. The pin is loosely received in or extends through a bore 266 in the rack end.
  • the rack is biased in its longitudinal direction by a spring 268 seated at one end in a recess 270 in member 258 and pushing at the other end against rack 260.
  • the rack is biased in its transverse direction by a spring 272 disposed in bore 218 and reacting at one end against end plate 222 and at the other end against a ball 274 slidably disposed the bore.
  • Springs 268 and 272 resiliently remove all back lash in one direction between the meshed teeth of pinion 246 and rack 260.
  • Bore 210 forms a rather close tolerance sliding fit with a release rod 276 having at one end a buttonlike portion 276a extending through end plate 220 and at the other end a bifurcated portion transversely extending across bore 212.
  • the bifurcated end is partially sectioned to show the bottom tine 276b which slidably supports be adjacent end of rack 260.
  • a rounded abutment 276c contacts the rack and a pin 278, pressed into a transverse bore in the tines maintains rod 276 in bore 210.
  • a bolt 280 threaded into end plate 222, limits travel of the rod.
  • a partially shown dial indicator 282 of conventional construction is positioned on mount 230 and is actuated by link 262 in response to longitudinal movement of rack 260.
  • bosses 24b, 26b are placed in bores 206, 204 to orient the axes of the rotor assemblies with respect to each other.
  • Center housing section 14, with seals 62, 64 pressed into bores 58, 60 is then placed on the assemblies with removeable shims positioned between end faces 20a, 22a and end wall 14c.
  • Bearings 28, 30 are then pressed into position with the outer races seated against shoulders 58b, 60b and the inner races axially positioned on bosses 24a, 26a such that any bearing play between the races and the balls is taken up in the direction of the bearing assemblies 32, 34.
  • Backlash or clearance between the meshed lobes of rotors 20, 22 is then determined using the following procedure.
  • Rotor 22 is locked or fixed against rotation relative to surface 202f by lock screw 234 and rotor 20 is turned through the total clearance between the then meshed lobes.
  • the clearance is shown on dial indicator 282.
  • Rotor 22 is then unlocked, button 276 is depressed to release rack 260 and disengage the dial indicator from gear 246, and rotors 20, 22 are rotated to new positions to determine the clearance between a different set of meshed lobes to find the set of meshed lobes having the minimum backlash or clearance.
  • the clearance between the set of lobes having the minimum clearance is then set to provide a minimum backlash in each direction.
  • Rotor 20 is then locked or fixed against rotation relative to rotor 22 by lock screw 252.
  • Timing gear 38 is then loosely positioned on tapered portion 26m of shaft 26 and meshed with gear 36 to effect proper timing therebetween.
  • An axial force is applied to seat gear 38 on the tapered surface and gear 38 is then locked on the tapered surface by threading nut 72 into abutment with the gear.
  • gear 76 freely telescopes on shaft 74 far enough to allow meshing engagement with gear 36; the adjusted backlash is locked by pressing gear 76 on shaft 74 in a manner analogous to pressing gear 36 on shaft 24.
  • the partially assembled supercharger is then removed from the fixture to allow installation of end section 18 and bearing assemblies 32, 34.
  • the springs in the bearing assemblies preload the rotor and shaft assembly to the right, as viewed in Figure 1, thereby removing all axial and radial bearing play and allowing the rotors and shafts to thermally expand or contract axially due to temperature changes.
  • the axial expansion and contraction will always occur relative to bearing assemblies 28, 30 since their inner and outer races are respectively fixed relative to the shafts and housing and since the spring assemblies always bias the shaft and rotor assemblies to the right. Further, the axial expansions and contractions will not appreciably change preload of the bearings since the spring assemblies maintain the preload substantially constant.
  • End section 16 with seal 70 and bearing 68 positioned in bore 66 may then be attached to center housing section 14 via bolts 50.

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

Claims (16)

  1. 3. La machine selon la revendication 2, dans laquelle ledit moyen d'indication (292) comprend en outre:
    un moyen mobile (246) avec et fixé sur ledit élément (240) et en alignement axial avec un point du cercle primitif des lobes (20c) du rotor (20) supporté sur la surface (240a) citée en premier; et
    un moyen (260) agissant en réponse à un mouvement dudit moyen mobile (246) pour fournir une indication directe du jeu entre les lobes en prise à l'intersection des cercles primitifs des lobes.
  2. 4. La machine selon la revendication 1, comprenant en outre:
    un pignon (246) fixé sur ledit élément (240) et comportant des dents externes (246a) ayant un diamètre de cercle primitif sensiblement égal au diamètre de cercle primitif des lobes du rotor supporté par ladite surface (240a) définie par ledit élément (240) et concentrique à l'axe de rotation dudit élément;
    une crémaillère (260) comportant des dents (260a) en prise avec les dents (246a) dudit pignon et déplaçable par glissement en réponse à une rotation dudit élément (240); et
    ledit moyen indicateur (282) étant relié à ladite crémaillère pour enregistrer, en lecture directe les indications du jeu entre lesdits lobes.
  3. 5. La machine selon la revendication 4, comprenant en outre:
    un moyen (276a) pour déplacer par pivotement ladite crémaillère en la désaccouplant dudit pignon (246) pour permettre une rotation dudit élément (240b) sans un mouvement de glissement de ladite crémaillère (260).
  4. 6. La machine selon la revendication 5, comprenant en outre:
    des moyens élastiques (268, 272) sollicitant lesdites dents de crémaillère (260a) pour les amener en prise avec les dents (246a) du pignon.
    7. La machine selon la revendication 6, dans laquelle lesdits moyens élastiques (268,272) comprennent:
    un moyen (272) pour solliciter ladite crémaillère transversalement à la direction dudit mouvement de glissement de ladite crémaillère (260).
  5. 8. La machine selon la revendication 7, dans laquelle lesdits moyens élastiques (268,272) comprennent en outre:
    un moyen (268) sollicitant ladite crémaillère dans la direction dudit mouvement de glissement de cette dernière.
  6. 9. Un procédé d'assemblage partiel d'un compresseur rotatif (10) et de synchronisation du compresseur partiellement assemblé sur une machine (200) conformément à une des revendications 1 à 8; le compresseur, lorsqu'il est partiellement assemblé, comportant des lobes en prise sans contact (20c, 22c) formés sur un premier et un second rotors (20, 22) respectivement fixés sur un prmier et un second arbres parallèles (24, 26 ou 74) espacés transversalement d'une distance prédéterminée l'un de l'autre et entraînés dans une relation angulaire fixée par un premier et un second engrenages de synchronisation en prise (36, 38 ou 76) respectivement adaptés pour être fixés sur des parties (24n, 26m ou 74) des arbres s'étendant axialement au delà de faces extrêmes adjacentes (20a, 22a) des rotors tandis que les arbres sont supportés au niveau desdites faces extrêmes adjacentes dans des ensembles de paliers (28, 30) portés par une partie (14c) d'un carter de compresseur et avant le montage en prise des premier et second engrenages de synchronisation;
    le procédé étant caractérisé en ce qu'il consiste à:
    supporter les parties d'arbres (24m, 26m ou 74) dans les ensembles de pamiers (28, 30) avec les lobes de rotors en prise,
    supporter les autres faces extrêmes adjacentes (20b, 22b) sur les première et seconde surface (202f, 240a) disposées dans un plan commun et définies par la monture (200), et avec ladite seconde surface (240a) montée de façon tournante;
    empêcher une rotation des rotors (20, 22) par rapport à leurs surfaces de support (202f, 240a), déterminer un jeu entre les lobes en prise (20c, 22c),
    régler un jeu entre les lobes en prise (20c, 22c), empêcher une rotation des surfaces de support (202f, 240a) l'une par rapport à l'autre; et
    fixer les premier et second pignons de synchronisation (36, 38 ou 76) respectivement sur les première et seconde parties d'arbres (24m, 26m ou 74) et en prise l'un avec l'autre.
  7. 10. Le procédé selon la revendication 9, comportant la fixation des premier et second arbres (24, 26 ou 74) respectivement sur les premier et second rotors (20, 22) de façon que les parties d'arbres (24, 26m, ou 74) s'étendent au delà des premières surfaces extrêmes (20a, 22a) et sans tenir compte de la relation de phase angulaire entre les axes des arbres et des rotors.
  8. 11. Le procédé selon la revendication 9 ou 10, dans lequel le premier pignon de synchronisation (36) comprend un moyen formant surface d'alésage cylindrique (36b), la première partie d'arbre (24m) comprend un moyen formant surface d'arbre cylindrique (24m) de plus grand diamètre que le moyen formant surface d'alésage (36b) et une série de cannelures espacées circonférentielle- ment (24n), formées dans l'un (24m) des moyens formant surfaces précités et constituées d'un matériau agissant de façon à déformer une partie de l'autre moyen formant surface (36b), et le procédé de fixation dudit premier pignon (36) sur ladite première partie d'arbre (24) consiste à:
    pousser ladite première partie d'arbre (24m) partiellement dans ledit moyen formant surface d'alésage (36b) pour produire au moins un assemblage avec emmanchement partiel entre ledit moyen formant surface d'arbre et ledit moyen formant surface d'alésage; et
    pousser ladite première partie d'arbre (24m) plus loin dans ledit moyen formant surface d'alésage (36b) pour produire une déformation dudit autre moyen formant surface (36b) par lesdites cannelures, en formant ainsi des cannelures correspondantes dans ledit autre moyen formant surface (24m).
  9. 12. Le procédé selon la revendication 11, dans lequel ledit pignon de synchronisation (76) et ledit second arbre (74) comprennent respectivement des surfaces d'alésage et d'arbre ainsi que des cannelures qui sont respectivement sensiblement identiques aux moyens formant surfaces d'alésage et d'arbre (36b, 24m) et aux cannelures (24n); et le procédé de fixation du second pignon (76) sur le second arbre (76) inclut le fait que l'on effectue les deux opérations précitées de poussée simultanément pour les deux engrenages et arbres.
  10. 13. Le procédé selon la revendication 11 ou 12, consistant en outre à:
    former lesdites cannelures (24n) en produisant une déformation de ladite partie d'arbre (24m).
  11. 14. Le procédé selon la revendication 11 ou 12, dans lequel l'étape de support mentionnée en premier est effectuée avant l'étape de support mentionnée en second.
  12. 15. Le procédé selon la revendication 10,11,12 ou 13, dans lequel l'étape de fixation mentionnée en premier est effectuée avant l'étape de support mentionnée en second.
EP84304078A 1983-06-20 1984-06-18 Assemblage d'un compresseur à suralimentation et fixation de phase de rotors Expired EP0135256B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84304078T ATE34602T1 (de) 1983-06-20 1984-06-18 Aufladeverdichteranlage und phaseneinstellung der rotoren.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US50607583A 1983-06-20 1983-06-20
US506075 1983-06-20

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EP0135256A1 EP0135256A1 (fr) 1985-03-27
EP0135256B1 true EP0135256B1 (fr) 1988-05-25

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JP (1) JPS6011694A (fr)
AT (1) ATE34602T1 (fr)
DE (1) DE3471505D1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0218623U (fr) * 1988-07-19 1990-02-07
US5910001A (en) * 1996-07-03 1999-06-08 Hitachi Techno Engineering Co., Ltd. Method for adjusting engaged clearance between rotors of screw compressor and apparatus therefor
JP4505704B2 (ja) * 2001-03-09 2010-07-21 株式会社Ｉｈｉ 二軸機械式過給機用ケーシング
CN101929830B (zh) * 2009-06-19 2012-02-29 宝山钢铁股份有限公司 一种夹送辊辊轴轴承间隙测量方法
CN104405643B (zh) * 2014-09-29 2017-09-05 任丘市本溪石油设备有限公司 立式防冻自吸活塞泵
EP4103841A1 (fr) * 2020-02-12 2022-12-21 Nova Rotors Srl Pompe à déplacement positif
CN114183343A (zh) * 2021-11-16 2022-03-15 北京卫星制造厂有限公司 一种循环泵及循环泵间隙控制方法

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2444773A (en) * 1944-05-18 1948-07-06 Northern Pump Company Adjustable gearing
AT185925B (de) * 1952-12-13 1956-06-25 Aerzener Maschinenfabrik Ges M Vorrichtung zum Einstellen der Drehkolben von Drehkolbenmaschinen
US3192639A (en) * 1960-01-20 1965-07-06 Waterous Co Apparatus for angularly relating members on a shaft
US3915026A (en) * 1974-07-29 1975-10-28 Wallace Murray Corp Lobe type pump adjustment

Also Published As

Publication number Publication date
JPH0511230B2 (fr) 1993-02-12
EP0135256A1 (fr) 1985-03-27
ATE34602T1 (de) 1988-06-15
JPS6011694A (ja) 1985-01-21
DE3471505D1 (en) 1988-06-30

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