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Publication numberUS3129877 A
Publication typeGrant
Publication dateApr 21, 1964
Filing dateDec 22, 1961
Priority dateMay 17, 1956
Publication numberUS 3129877 A, US 3129877A, US-A-3129877, US3129877 A, US3129877A
InventorsBertil Wahlsten Bengt, Robert Nilsson Hans
Original AssigneeSvenska Rotor Maskiner Ab
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Rotary piston, positive displacement compressor
US 3129877 A
Abstract  available in
Images(1)
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Claims  available in
Description  (OCR text may contain errors)

April 2l 1964 H. R. NlLssoN ETAL ROTARY PISTON, POSITIVE DISPLACEMENT COMPRESSOR Original Filed April 29. 1957 TTORN EY 'l Il United States Patent O 3,129,877 ROTARY PISTGN, POSlTlVE DEPLACEMENT CGMIPRESSUR Hans Robert Nilsson, Ektorp, and Bengt Bertii Wahisten,

Stockhoim, Sweden, assignors to Svenska Rotor Maskiner Aktiebolag, Nacka, Sweden, a corporation of Sweden Continuation of application Ser. No. 655,843, Apr. 29, 1957. This application Dec. 22, 1961, Ser. No. 161,576 Claims priority, application Sweden May 17, 1956 4 Claims. (Cl. 23d-143) 'Ihis application is a continuation of our prior application Serial No. 655,843, filed April 29, 1957, and now abandoned, 'and relates back thereto for all dates and rights incident to the ling thereof and of our corresponding Swedish application Serial No. 4,723/56, filed May 17, 1956, and from which priority is claimed.

The present invention relates to rotary piston, positive displacement compressors of the kind in which at least two dissimilar rotors, male and female (as hereinafter defined) and provided with helical lands and grooves, are mounted to rotate in intermeshing relation about coplanar axes in intersecting bores in a casing structure the walls of which cooperate with portions of the rotor grooves to form compression chambers diminishing in volume as the rotors revolve to compress an elastic fluid contained therein.

This general type of compressor is well known in the ait, the first practical design of which, embodying an inbuilt or internal compression ratio, is disclosed in U.S. Patent No. 2,243,874, granted to Alf Lfyshol-m June 3, 1941, the original Lysholm design being modified to provide an improved form of rotor by the invention disclosed in U.S. Patent No. 2,622,787, granted December 23, 1952, to Hans Nilsson, the latter form of rotor being employed in the present disclosure, by way of example bu-t without limitation, to illustrate the principles and advantages of tbe present invention.

Compressors of the kind here under discussion have attained a considerable measure of commercial success, but heretofore have without exception been operated as dry compressors, that is, without lubricant or other liquid being introduced into the working spaces of the machine and with the rotors being maintained out of contact with the casing walls by suitable clearance and out of Contact with each other by appropriate clearance through the use of timing or synchronizing gears. In the case of dry compressors, leakage from the working chambers is retarded only by the space packing afforded by the relatively close clearances obtained through veryl accurate manufacture, but even with the maintenance of very close clearances, acceptable efficiencies are obtainable with dry compressors only by operating them at relatively high speeds so that the volumes of fluid handled are very large in relation to the size of the machine and consequently of the dimensions of the chambers from which the leakage occurs through the space packing.

With such compressors, the tip speed of the male rotor may be as high as of the order of from 150 to 200 meters per second, as noted in the aforesaid Nilsson patent, which may entail rotor yspeeds of as much as 10,000 to 12,000 r.p.m. for compressors of the sizes usually driven by electric motor-s or internal combustion engines. Such speeds necessitate the use of stepup gears between the 3,129,877 Patented Apr. 21, 1964 "ice prime mover and the compressor which are undesirable from the standpoint of weight bulk and service as well as cost.

A further practical 4disadvantage of the high speed of operation of the dry compressor is the relatively high noise level resulting from the high frequency pulsating admission to and discharge from the Working chambers of the gaseous medium being compressed, which requires in most installation the added cost, Iweight and bulk of silencing equipment.

Still more important are the practical limitations posed on dry compressors by the factor of the heat generated by the work of compression. Such heat obviously and unavoidably creates dimensional changes due to expansion and contraction of the casing, rotor and other parts controlling the clearances, which are probably the most important as well yas the most sensitive factor determinative of the performance of the dry compressor. To keep `such changes to an acceptable minimum, req-uires as a practical matter that at least the casings of dry compressors be liquid cooled if any substantial inbuilt compression ratio, say three to one or better, is incorporated in a single stage of compression from atmospheric inlet pressure, and even with liquid cooling, practical experience has demonstrated that Ia ratio of five to one represents the desirable upper limitV for single stage compression.

Thus while dry compressors of the kind under discussion have proved to be of practical commercial value and have gone into extensive use, they are 'subject to several important limitations, particularly in the very large field requiring so-called shop air, that is, air at about one hundred pounds gage pressure, and moreover requiring that such air be provided by portable compressors desirably driven directly by internal combustion engines and effecting compression in a single stage without an intercooler.

It is therefore the primary object of the present invention to provide a new and improved compressor of the general type under consideration which will eliminate .the above noted and other limitations and deficiencies of such compressors as heretofore employed.

To this end the invention contemplates the injection of liquid into the working chambers of the compressor to effect two major purposes, the `first being to provide a liquid seal instead of dry space packing for the clearance spaces between the rotors and the casing and between the intermeshing portions of the rotors and the second being to effect direct cooling of the gaseous fluid While it is being compressed, so that the compression cycle ydeviates from the adiabatic to more nearly approach the isothermal. Preferably such injection is confined to or substantially' to the compression phase of the cycle for reasons hereinafter more fully appearing, and =for la better understanding of other and more detailed objects of the invention together with the preferred manner of carrying the invention into effect in order to obtain the maximum benefit therefrom, reference may best be had to the ensuing portion of this specification, .taken in conjunction with the accompanying drawings, in which:

FIG. l is a longitudinal section, partly in broken away elevation, taken 'along the lines 1-1 and liz-1a of FIG. 2;

FG. 2 is a partial section taken along line 2-.2 of FIG. 1;

FIG. 3 is a fragmentary elevation, in part broken away and on much larger scale, of portions of the rotors shown in FIG-S. l and 2; and

FIG. 4 is a section similar `to FiG. 2 showing a modified form of construction.

The compressor shown in FIGS. l and 2 consists of two co-operating rotors 1Z0-and 22 of which one, the male rotor 20, is provided with convex lands 24 and intervening grooves 26 and cro-operates with the other or female rotor Z2 which is provided With concave lands 23 and intervening grooves 30. As ywill be obvious from the drawings, the rotors are not only dissimilar in form, but also embody the basically characteristic feature of oompressors of the kind to which the invention is directed, that the major portion of the lands and intervening grooves of the male rotor lie outside the pitch circle of the rotor while the major portion of the lands and grooves of the -female rotor lie inside the pitch circle of the female rotor. In fact yas in usually the preferred case, the outer circumference or envelope of the female rotor substantially coincides with its pitch circle while the lands of the male rotor lie substantially entirely outside its pitch circle. Also as lwill be evident from FIG. 2, the convex profile of the lands of the male rotor provide an outer or crest portion that is substantially circular in cross section, being of the form disclosed in the aforesaid Nilsson patent, which in connection with the use of the present invention has certain definite advantages as Will `hereinafter more fully appear. The rotors are provided with end shafts 32 and 34 which are located in end walls 36 and 38 of ldie compressor casing 40' which tiurther includes a jacketed barrel portion 42 enclosing the rotors. The end Wall 36 comprises a separate element whilst the end wall 38 is made integral with the barrel portion 42.

The casing is provided with an inlet 44 and an outlet 46 for the gas, for example air, which is to be compressed in the machine. In the example shown inlet 44 is located at the bottom and outlet 46 at the top, each being within or adjacent to the corresponding end Wall of the casing, respectively. However, the invention is not restricted to this placing or design of inlet and outlet which may be varied according to well-known principles.

The barrel portion 42 and the end walls 36 and 3S are double-walled to provide jacket spaces 48 to which liquid under pressure is supplied from a source thereof (not shown) from which said liquid is injected vvia supply openings into the working chambers of the machine.

As previously noted, the proliie of the rotors shown is that disclosed in the Nilsson patent aforesaid, characterized by male rotor lands the crest portion of the prolile of which are circular in outline. This specific form of profile is particularly advantageously employed in a compressor into which liquid is introduced in substantial quantity for the purpose of obtaining appreciable cooling effect as Well as for sealing purposes, and conversely, injection of liquid in the preferred manner cooperates, as hereinafter explained, in a particularly advantageous way to enhance the effectiveness of operation of rotors having the circular form of profile.

The particular advantage of the use of rotors characterized by the circular profile, in a compressor into which liquid is introduced, is perhaps best understood from a consideration of the Nilsson patent, which for the purpose of giving a detailed explanation of the nature and advantages of the circular profile, may be considered as incorporated herein by reference and further may be considered in conjunction with FIG. 3 of the disclosure. As explained in the Nilsson patent, the early forms of devices of the character under consideration employed male rotors, one or both of the flanks of the lands of which were generated curves, usually generated by a point on or closely adjacent to the pitch circle of the cooperating female rotor. The

purpose of this construction was to insure continuity of the sealing line defining the perimeter of each Working charnber at the point of entry of the crest of a male land into a female groove to create the chamber. This was accomplished by such construction, but it was also accompanied by the unavoidable and inherently disadvantageous formation of closed or trapped pockets in the interspace between fully meshed lands, which trapped pockets run out to zero volume as the rotors revolve to cause the compression chambers also to run out to zero volume as they deliver their contents to the outlet of the compressor. The creation of these trapped pockets, their disadvantages, the necessity for venting them if excessive pressures and undesirable losses are to be avoided, and different expediente for venting them, are recognized and discussed in Lysholm Patent No. 2,243,874, granted June 3, i941, and Whitield Patent No. 2,287,716, granted .Tune 23, 1942. One of the major advantages achieved by the circular proiile disclosed in the aforesaid Niisson patent is the elimination of the trapped pockets characteristically produced by generated profiles and while this advantage is of importance in the field of dry compressors, it will be evident that it is of even greater importance for compressors into the compression spaces of which liquid is introduced, particularly if the quantity introduced is substantial, as must be the case if a material cooling effect is to be secured. With an incompressible liquid present in the chambers, it is self evident that effective venting means must be provided for venting the trapped pockets if destructive pressures are to be avoided, and experience has shown that the required venting of the trapped pockets, through the medium either of excessively large clearance spaces or the provision of venting Spaces or passages, can be effected only at the expense of undesirable loss in the overall eiciency of operation of the machine.

With dry compressors, experience has demonstrated that timing gears for maintaining the intermeshing rotors in properly spaced phase relation to insure clearance between them are a practical necessity. It is to be noted, however, that in the case of generated profiles the necessity for timing gears is more pronounced than in the case of circular profiles since in the former case the trapped pockets produce torque forces tending to make one rotor overrun or underrun its mating rotor while in the latter case such torque forces are not produced. In any case it is highly desirable if not essential to use timing gears with dry compressors, Whereas with compressors into which liquid is introduced, such gears may be dispensed with, particularly when the liquid used is a lubricant such as ordinary lubricating oil, which is quite suitable for the purpose. This is particularly true in the case where the preferred form of circular profile herein disclosed is employed and no fluid pressure generated torques are developed tending to make the rotors turn at different speeds. Thus it will be evident that compressors constructed in accordance with the present concept afford the additional advantage of enabling the extra bulk, weight and cost of timing gears to be eliminated.

While as previously pointed out, the introduction of liquid into the compression chambers results in obtaining important advantages, such as improved sealing, direct cooling of the uid being compressed, elimination of gearing and the like, such introduction involves other factors of a less favorable nature that must be taken into consideration and which the present invention operates to greatly ameliorate if not entirely eliminate.

In the first place there is the matter of dynamic losses due to agitation of the fluid in the compressor resulting from the movement of the rotors. These losses have heretofore commonly been referred to as ventilation losses, engendered by the turbulence of the elastic fluid constituting the sole content of the compression chambers, and the gaseous fluid friction developed as a result of the flow through the space packed clearance spaces. These losses have been of substantial magnitude, particularly in View of the high peripheral or tip speeds required for acceptable operation of a dry compressor.

The introduction of liquid, by providing a solid fluid closure instead of the space packed clearances of a dry compressor, reduces the rate of leakage loss from the compression chambers to such an extent that the tip speeds of the rotors can be reduced, while still maintaining acceptable ethciency, to a minor fraction of the speed necessary for operation of a dry compressor. Such reduction is in fact of such magnitude that it is possible to reduce the speed to a value such that compressors of a type and size heretofore requiring step-up gears when operated dry by normal speed electric motors or by internal combustion engines, may be and are normally operated directly connected to such power plants when operated with liquid introduced, thus achieving one of the major objects of the invention.

Not only is major reduction in speed of operation made possible by the introduction of liquid, but experience has shown it to be necessary if undue losses are to be avoided. Basically, of course, the reason for this is that the very much greater density and viscosity of even the thinnest liquids (water or very light hydrocarbons could be used if desired), as compared with that of the gaseous fluids usually compressed, results in what may be termed churning losses developed by the liquid (as distinguished from turbulence or ventilation losses developed by a gas) of such magnitude that the high speeds characteristic of dry operation could not be tolerated.

In spite of major reduction in speed as compared with dry operation, wet operation, that is, operation with the introduction of liquid, entails substantial churning losses, and in one of its more specific aspects the present invention contemplates introduction of the liquid into the compression chambers in a particular fashion the effect of which is to minimize churning losses as well as other losses of a nature to be dealt with later.

In order best to understand this, it is appropriate first to briey review the fundamental nature of the operation of compressors of the kind disclosed. When operating as a compressor, the rotors are turned in the directions indicated by the arrows appearing in FIGS. 2 and 4, this action serving to draw air into the rotor grooves through the inlet 44 and to discharge the compressed air through the outlet 46, in the directions noted by the arrows in FIG. 1. AS will be noted from this gure, the helices of the lands and grooves of the rotors have a total wrap angle of less than 360, in accordance with standard practice for this type of compressor, so that the working .chambers are not delimited axially by successive intermeshes ofthe same lands and grooves, which would produce chambers moving axially at constant length and volume as transport chambers rather than as compression chambers decreasing in length and in volume as the rotors revolve. With the present construction the rotor grooves iirst till with fluid during the suction phase of the cycle as their right hand ends (as seen in FIG. 1) pass the port 44. Following the point of cutoff from this port, the grooves carry their fluid contents upwardly at constant volume in a so-called transport phase of the cycle until the right hand end of a male or female rotor land commences entry, respectively, into the right hand end of a cooperating female or male rotor groove. The place of such entry is at the line of intersection 56 between the two bores 5S and 6% in the barrel portion of the casing, and such entry commences the compression phase of the cycle. It is well to note at this point that the entry of a land into a groove to initiate compression may occur before the groove involved has moved to a position in which it has been cut off from the inlet, so that there is an overlap between the inlet and compression phases of the cycle and no intervening constant volume transport phase. All this, however, is well known in the art, as exemplied by Lysholm Patent No. 2,410,172, granted October 29, 1946.

At the time the compression phase commences each compression chamber is formed by two cooperating grooves, one male and one female, and is axially delimited at one end by the xed transverse plane of the delivery end wall 38 of the casing and at the other end by the place of intermesh of the rotors. This results in the formation of what may be termed chevron-shaped chambers extending between an axially ixed end plane, which remains fixed, and a moving place of intermesh which moves toward that plane as the rotors revolve, to shorten the chamber axially until it runs out to Zero volume. When the chamber comes into communication with the outlet port 46, the compression phase may technically be said to terminate, to be followed by the final delivery phase at .constant pressure. In practice, however, the latter phase may for practical purposes be considered as a final part or" the compression phase since the volume of the compression chamber is continuing to decrease and the final pressure may increase to a value above that existing when registration with the outlet port occurs. This is fully recognized and discussed in Lysholm Patent No. 2,519,913, granted August 22, 1950, and for the purposes of the present disclosure and specification, the term compression phase as hereinafter used is to be `considered as including the delivery phase. While for the sake of simplicity the present invention has been described and illustrated as applied to a compressor having rotors with helical lands and grooves of single hand, the invention is in no wise limited to such structures but is equally applicable to compressors having herringbone rotors of the kind shown in Lysholm Patent No. 2,289,371, granted Iuly 14, 1942, such compressors, insofar as the present invention is concerned, being the full equivalent of the example herein illustrated.

With the foregoing in mind, it will be apparent that, insofar as the factor of sealing the compression chambers is concerned, only the .compression phase of the cycle, and that portion of the cooperating parts defining the perimeter of a chamber in which a pressure differential above inlet pressure has been established, need be taken into account. The perimeters of the chambers in which elevated pressures are present deine areas very considerably less than the total internal area of the bores and casing ends enclosing the rotors, the total of what may be termed the area of the pressure surface or pressure area being in fact less than half, or the minor portion, of the total of the internal casing surface. It is only over this area of the surface that sealing against leakage from the compression chambers is required, and in accordance with one particular aspect of the invention, the churning losses incident to the use of a liquid sealant are minimized by conning the introduction of the liquid to, or substantially to, the pressure area of the casing. It will be understood, of course, that the liquid sealant will necessarily be eventually distributed over the entire internal surface of the casing, but it will equally be evident that if a sucient quantity is injected to provide a material cooling effect the relative concentration of liquid and the resultant churning loss will be greatest in the vicinity of the place of introduction which should therefore be held to a minimum area.

Furthermore from the standpoint of the desired cooling effect to be produced by the liquid, it is obvious that no such effect is required until the compression zone is reached, where heat is rst generated by the work of compression. On the other hand, it is highly desirable that compression be commenced Without preheating of the inlet air. Since the liquid used for sealing and cooling is heated in the process and must for reasons of economy be recirculated in the system after having been separated vfrom the air delivered by the compressor, its admission temperature to the compressor may well be above that of the incoming air unless additional and undesirable cooling equipment is provided. By confining the introduction of liquid to or approximately to the compression phase of the cycle, undesirable preheating of the inlet air by recirculated liquid at higher than inlet temperature is with certainty avoided.

Reverting again to the preferred form of rotor with lands of circular prole, the advantages to be derived from it are accompanied by one unfavorable characteristic which, however, in accordance with another of the more specific aspects of the present invention, is substantially eliminated as a practical consideration. This characteristic is the inherent formation of a gap or interruption in the sealing line of uniform clearance defining the perimeter of each compression chamber, due to the non-generated character of the male rotor lands at the crests thereof. The nature of this gap and the cause of its formation are disclosed and explained in detail in the aforesaid Lysholrn Patent No. 2,622,787, to which reference may be had for such detailed explanation, but for the purposes of this disclosure and an understanding of the special relationship between a rotor of circular prole, with its numerous advantages hereinbefore noted, and the particular preferred mode of introducing liquid in accordance with the present invention, reference to FIG. 3 hereof is suicient. As will be seen from this figure, the circular crest of the male rotor land 26 reaches the line of intersection 56 between the two rotor bores on the high pressure side of the plane of the rotor axes, at a place axially displaced from the adjacent edge of the female rotor land 2S. This inherently produces a small and substantially isosceles triangular gap indicated at x--y-z in the figure, resulting in a break in the sealing line between that portion formed between one casing bore and the crest of the female land and the contiguous portion formed between the other bore and the .crest portion of the cooperating male land. To effect compression the rotors revolve in the directions indicated by the arrows in the figure, and with such directions of rotation, the gaps travel axially along the line of intersections 56 from right to left as viewed in the ligure, from the position at the right hand end of the rotors where the gaps are formed as the cooperating lands come into mesh to establish the compression chambers, to the position where the gaps disappear by virtue of the fact that the place of intermesh of the rotors has come into communication with the outlet port of the compressor. These gaps constitute undesirable leakage or blow holes through which compressed working fluid can leak from any given compression chamber to the next succeeding chamber of the series, which is always at a lower pressure.

Obviously, anything that will tend to reduce the leakage through the blow holes is highly desirable and accordingly the injection of the liquid for the broad general purposes of the invention is availed of to provide a further improvement, in the preferred embodiment of apparatus, by effecting the injection through a series of orices or nozzles 545 distributed axially along the length of the line of intersection 56 between the casing bores, along which the gaps travel. Such injection, even though it is desirable to inject in the form of a spray to secure the maximum cooling effect from a given amount of liquid, obviously provides a concentration of liquid at the line along which the gaps travel sufficient to very materially reduce their size and the leakage rate of the fluid therethrough.

While for more or less self-evident reasons, it is preferable in order to secure the maximum benefit to inject along the line of intersection on the high pressure side, the beneficial eiects derived from this arrangement are not critical- 1y dependent upon this precise location. As will be apparent from the direction of rotation of the rotors as seen in FIGS. 2 and 4, liquid injected into the barrels at any place along the high pressure side of the plane of the rotor axes will be carried with relatively short paths of travel to the line of intersection where the gaps occur, tending to ll them. Also, under some circumstances it may be desirable to include a larger area on the high pressure side over which newly injected liquid is distributed to the chambers, and instead of injection exactly along the high 55 pressure line of intersection, injection may for example be made through series of orifices 62 opening through the walls of the respective barrels at places peripherally spaced from the high pressure line of intersection but still preferably on the hiffh pressure sides of the barrels, as shown in the modification illustrated in FIG. 4.

From the foregoing it will be apparent that the principles of the invention are applicable to a wide variety of specic compressor applications involving widely varying compression ratios, different gaseous fluids to be compressed, and different liquids to be utilized for sealing and cooling. The specific design and mode of operation will naturally be governed by the particular conditions to be met and may require other specific expedients than those herein illustrated and described by way of example, and the invention is accordingly to be considered as embracing all forms of structure falling Within the scope of the appended claims.

We claim:

l. A rotary piston, positive displacement, elastic iluid compressor comprising a casing structure providing a barrel portion having intersecting bores with co-planar axes and further providing spaced apart ports communicating with said bores and comprising a high pressure port at least the major portion of which is located to one side of the plane of said axes and a low pressure port at least a major portion of which is located on the opposite side of said plane, rotors provided with helical lands and grooves having an effective wrap angle of less than 360 rotatably mounted in said bores and comprising a male rotor having lands and intervening grooves the major portions of which lie outside the pitch circle of the male rotor and a female rotor having lands and intervening grooves the major portions of which lie inside the pitch circle of the female rotor, the lands and grooves of said rotors intermeshing to form with the confronting portion of the casing structure chevron-shaped working chambers each composed of communicating portions of a male rotor groove and a female rotor groove joining at the apex end of the chamber and said apex end moving axially towards said high pressure port as the rotors revolve to decrease the volume of the chamber and eflect compression of the uid contents thereof, the lands of said male rotor having convexly curved profiles the outer portions of which lie peripherally within the lines of a land having a root of the same peripheral width and flanks generated by points on the pitch circle of said female rotor and the profile of the grooves of said female rotor being the envelopes developed by the convex lands of said male rotor in passing into and out of mesh with said female rotor, whereby a series of gaps is created in the sealing lines of normal clearance between the cooperating parts dening the perimeters of said compression chambers, said gaps extending axially of the line of intersection between said bores on the high pressure side ofthe bores and said gaps traveling axially of said line of intersection toward said high pressure port as the rotors revolve, and means for sealing the clearance between the parts defining the perimeters of said chambers inclusive of said gaps and for cooling the uid being compressed therein comprising a plurality of openings in the barrel portion of said casing structure for injecting liquid into said chambers, said openings being distributed length- Wise of said barrel portion of the casing structure in the area thereof adjacent to and inclusive of said line of intersection.

2. A compressor as defined in claim 1, in which the convexly curved flanks of the lands of the male rotor have crest portions which are of generally circular profile and in which the grooves of the female rotor are generally circular and the proiiles of which are the envelopes developed by the convex lands of the male rotor in passing into and out ot' mesh with the female rotor.

3. A compressor as defined in claim l, in which said openings for injecting liquid into said chambers are located along said line of intersection.

4. A compressor as defined in claim 2 in which said openings for injecting liquid into said chambers are 1ocaed along said line of intersection.

References Cited in the le of this patent 5 UNITED STATES PATENTS 1,424,312 Leonard Aug. 1, 1922 1,439,628 Kien Dec. 19, 1922 1,634,023 Davison June 28, 1927 1,672,571 Leonard June 5, 192s 1 1,673,260 Meston et a1 June 12, 1928 10 Zajac July 3, 1928 Lysholm Oct. 3, 1939 Lysholm June 3, 1941 Whitfield June 23, 1942 Lysholm et al July 14, 1942 Lysholm Oct. 29, 1946 Lysholm Aug. 22, 1950 Nilsson Dec. 23, 1952 FOREIGN PATENTS Australia Feb. 25, 1959

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Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3265293 *Jan 10, 1966Aug 9, 1966Svenska Rotor Maskiner AbVacuum pump of the screw rotor type and method for operating the same
US3307453 *Feb 25, 1965Mar 7, 1967Svenska Rotor Maskiner AbScrew rotor machines for expanding a gaseous working medium of high temperature
US3484823 *Dec 15, 1967Dec 16, 1969Cornell Aeronautical Labor IncMultirecompression heater and/or high temperature compressor
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US3677664 *Jun 29, 1970Jul 18, 1972Edwards High Vacuum Int LtdRotary mechanical pumps of the screw type
US3795117 *Sep 1, 1972Mar 5, 1974Dunham Bush IncInjection cooling of screw compressors
US3931718 *Jul 17, 1973Jan 13, 1976Hall-Thermotank Products Ltd.Refrigerant screw compression with liquid refrigerant injection
US5895778 *Aug 25, 1997Apr 20, 1999Hatco CorporationPoly(neopentyl polyol) ester based coolants and improved additive package
US6273696 *Jun 9, 1998Aug 14, 2001Sterling Fluid Systems (Germany) GmbhScrew spindle vacuum pump and operating method
US6444626Aug 25, 1998Sep 3, 2002Hatco CorporationPoly(neopentyl polyol) ester based coolants and improved additive package
US6733258 *Oct 16, 2002May 11, 2004Denso CorporationGas compressor apparatus having a discharge pulsation reducing cooler
US6991440 *Sep 30, 2003Jan 31, 2006Ghh-Rand Schraubenkompressoren GmbhTwo-stage screw compressor
US8113183 *Jul 24, 2008Feb 14, 2012GM Global Technology Operations LLCEngine and supercharger with liquid cooled housings
USRE30499 *Nov 19, 1974Feb 3, 1981Dunham-Bush, Inc.Injection cooling of screw compressors
Classifications
U.S. Classification418/99, 418/83, 418/201.1
International ClassificationF04C18/16
Cooperative ClassificationF04C18/16
European ClassificationF04C18/16