US3632239A - Rotatable worm fluid compression-expansion machine - Google Patents

Rotatable worm fluid compression-expansion machine Download PDF

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US3632239A
US3632239A US884606A US3632239DA US3632239A US 3632239 A US3632239 A US 3632239A US 884606 A US884606 A US 884606A US 3632239D A US3632239D A US 3632239DA US 3632239 A US3632239 A US 3632239A
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worm
pinion
teeth
threads
axis
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Bernard Zimmern
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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/02—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees
    • F04C3/04—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49236—Fluid pump or compressor making
    • Y10T29/49242—Screw or gear type, e.g., Moineau type

Definitions

  • a fluid compression-expansion machine comprising a worm rotatable inside a casing and at least one toothed pinion meshing with the worm and rotatable about an axis transversal to the axis of the worm, wherein the dimensions and relative positions of the worm and the pinion are so selected that there exists at least one axis of insertion for the pinion which satisfies the equation:
  • h is the algebraic distance from this point M,- of the perpendicular dropped from the center of the pinion onto the tangent at point M, to the flank of the tooth.
  • r,- is the absolute value of the distance from point M to the projection of the axis of the worm on the plane of contact between the worm and the pinion,
  • dj, hj, r,- are analogous quantities relating to a point Mj of contact between a flank of a tooth and a thread, this flank being on the same side of the tooth as the axis.
  • This invention relates to a machine of the kind comprising a worm rotatable about a first axis with respect to a casing, and at least one toothed pinion meshing with the worm and rotatable about an axis, with respect to said casing, which is transverse to said first axis, the crests of the worm threads lying on a common surface of revolution about said first axis, the casing having a portion making sealing engagement with a least a portion of said common surface of revolution, extending between circumferentially adjacent sides of two circumferentially adjacent said pinions, or between opposite sides of said pinion where a single pinion is used, the casing sealingly engaging said pinion sides.
  • the form of the worm and of the or each pinion is such that the portions of the pinion teeth within said common surface of revolution make fluidtight contact with the worm teeth so that fluidtight chambers are defined between the worm teeth, the casing and the pinion teeth, the casing having an inlet and an outlet and the arrangement being such that as the worm and pinion rotate in mesh one such chamber communicating with the outlet increases in volume to draw fluid into the chamber, is subsequently sealed off from the inlet by a pinion tooth, is transferred between pinion teeth to the outlet, is communicated with the outlet and has its volume decreased to discharge its fluid through the outlet.
  • a machine of the above kind is hereinafter referred to as being of the kind specified.
  • a worrn having the form necessary to fulfill the conditions set out above is hereinafter referred to as a globoid worm".
  • a machine of the kind specified may be used as a compressor or as a pressure reducer.
  • the pressure variation ratio (compression or expansion ratio) of a machine of the kind specified depends on the number of worm threads meshing simultaneously with the teeth of the pinion, The higher this number is, the lower is the residual volume of the compression or expansion chambers at the moment at which they are connected to the high-pressure orifice, (i.e., the outlet in the case of a compressor, or the inlet in the case of a pressure reducer) and the higher, therefore, is the pressure variation ratio.
  • French patent specification No. 1,331,998 also describes compressors in which the outer profile of the worm, (i.e., the envelope of the thread crests) is cylindrical, and by means of which fairly high compression ratios can be obtained without splitting the worm or pinion.
  • the number of pinion teeth simultaneously in engagement with the worm cannot exceed three, and in certain angular positions of the worm only a single tooth of the pinion has both of its flanks in contact with adjacent thread flanks of the worm.
  • the compression ratio is thereby limited to a value of the order of six, so that when such a compressor is used to compress air, compressed air at the standard pressure of 7 bars can be obtained. This compression ratio is too low for some purposes, for example for refrigerator compressors.
  • d is the algebraic distance between the straight line and a point M, of contact between one flank of a pinion tooth and a worm thread; this distance being measured from the M, along the tangent at this point the flank of the tooth, the flank in question being on the opposite side of the tooth from the straight line;
  • h is the algebraic distance from this point M, to the perpendicular dropped from the center of the pinion onto the said tangent, this distance being measured from the point r, is the absolute value for the distance from the point M,- to
  • d,, h,, r are analogous quantities relating to a point M,- of contact between a flank of a tooth and a thread, this flank being situated on the same side of the tooth as the straight line.
  • the worm and pinion can be assembled by making the latter carry out a composite displacement combining translation and rotation about said straight line which will hereafter be termed insertion axis.
  • the worm and pinion are formed so that insertion axis exists only in a number of ranges of relative angular positions of the worm and pinion said number being equal to the number of worm threads, these zones being each of only a few degrees extent and being obtained by appropriate truncation of the worm on the low-pressure side.
  • the worm and pinion may be formed so that insertion axis exist only in a single range of relative angular position of the worm and pinion, said range being of only a few degrees extent and being obtained by truncation of a single thread on the low-pressure side.
  • FIG. 1 is an elevation view partly in section and partly cutaway, of a first embodiment of the invention, with a globoid worm having a conical outer surface;
  • FIG. 2 is an elevation view, partly in section, of a globoid worm having a cylindrical outer surface a pinion adapted to cooperate with this worm, before it is assembled with the worm in a machine according to the invention;
  • FIGS. 3 and 4 are elevation views illustrating respectively the initial and final phases in assembly of the pinion and worm of FIG. 2;
  • FIG. 5 is a diagram illustrating the geometrical relationships between a worm and pinion of a machine according to the invention.
  • FIG. 6 is a diagram illustrating a method of obtaining the relative dimensions of a worm and pinion for a machine according to the invention
  • FIG. 7 is a diagrammatic section illustrating one embodiment of worm and pinion for a machine according to the invention.
  • FIG. 8 is a diagrammatic section illustrating another embodiment of a worm and pinion for a machine according to the invention.
  • FIG. 9 is a perspective view illustrating yet another embodiment of a worm for a machine according to the invention.
  • FIG. 1 A pump according to the invention for use as a compressor or pressure reducer is illustrated in FIG. 1.
  • This machine has a globoid worm 1, the crests of whose threads define a conical surface of revolution about the rotary axis of the worm.
  • the worm 1 is mounted so that it is rotatable about its axis 2 and is supported by ball bearing 3 in a casing 4.
  • Two symmetrically disposed toothed pinions 5 are rotatable about their axes 6 and mesh with the worm 1.
  • the casing 4 has a series of lowpressure orifices 7, which are spaced around its periphery and form the fluid intake in the case of a compressor or the fluid outlet in the case of a pressure reducer.
  • the casing 4 contains two orifices of triangular cross section, forming an outlet for the discharge of compressed fluid in the case of a compressor or an inlet for the intake of fluid for expansion in the case of a pressure reducer.
  • One if these orifices is indicated by broken lines at 8 in FIG. 1, this orifice being in fact situated in front of the plane of section.
  • Fluidtightness of the compression or expansion chambers is ensured in a conventional manner by liquid seals. Sealing liquid is injected into the machine on the intake side for the fluid being compressed or expanded, near the pinions 5. Injectors 9 are provided on the low-pressure side of the intake of this sealing fiuid if the machine is operating as a compressor. If the machine is being used as a pressure reducer, these injectors are housed in the fluid intake orifice 8.
  • the worm 1 turns in the direction of the arrow f if the machine is operating as a compressor and in the opposite direction if it is operating as a pressure reducer.
  • a worm having a cylindrical surface such as the worm 11 shown in FIG. 2, may be substituted for the conical worm I.
  • the conical worm 1 and the cylindrical worm 11 there are, for all angular positions of the worm, at least two teeth on the pinion 5 which are simultaneously in contact along both their flanks with the threads on the worm. It is therefore impossible to insert the pinion in the worm merely by means of translation, unless, as indicated above, the teeth and threads are tapered, which considerably reduces the delivery and power-to-weight ratio of the machine. If the worm and pinion are brought together by mere translation it will be seen from FIG.
  • one-piece worms and pinions are used for which, in any angular position of the worm, at least two teeth on the pinion are simultaneously in contact along both their flanks with the threads on the worm.
  • FIGS. 3 and 4 The manner of assembly is illustrated in FIGS. 3 and 4 for a I cylindrical worm l2 and a pinion 13.
  • the pinion 13 (FIG. 3) is inclined so that its plane forms an angle a with the axis of the worm l2, and the ends 14, 15 of the teeth 16, 17 which must ultimately be in contact along both their flanks with the threads 18, 19 and 21 of the worm, are brought into contact with the two end threads 18, 21 respectively.
  • the pinion 13 is then inserted along an axis 22, which will be defined below, while subjecting this pinion to rotation about this axis 22 in such a way as to reduce the angle of inclination a progressively, until the pinion 13 is in position (FIG. 4).
  • an axis such as 22 will be termed an insertion axis.
  • the plane of FIG. 5 is the plane containing the lines of contact of the pinion 24 with the worm 23 when the pinion is in its operating position.
  • This plane does not necessarily contain the axis of the worm 23. However, it is assumed that the distance from this axis to the plane of the Figure does not exceed 20 percent of the external diameter d of the worm 23 in the center of the sector of cooperation between the worm and pinion, or that the angle formed by the worm axis with the plane of the Figure does not exceed 20.
  • the projection of the axis of the worm 23 onto the plane of the Figure is indicated at 25.
  • each tooth 26 has a flank 27 situated on the opposite side of the tooth from the axis 22 and a flank 28 situated on the same side of the tooth as the axis 22.
  • flanks such as 27 will be termed “remote flanks and flanks such as 28 adjacent flanks”.
  • the tangent 29 to the flank 27 at a point M has been traced from the point M, on a remote flank 27, the point M, being a point of contact between the tooth 26 and a thread 31 on the worm.
  • This tangent intersects the axis 22 at a point A,.
  • a perpendicular OH is dropped from the center 0 of the pinion 24 onto the tangent 29.
  • the distances MA, and MJ-l, measured algebraically along the tangent 29 from the point M, will be designated d, and h, respectively.
  • the absolute value for the distance from the point M, to the projection 25 of the worm axis will be termed n.
  • the axis 22 is an insertion axis in the sense defined above if the following condition is satisfied for every pair of points such as M, and M,:
  • the pinion has four teeth 36 to 39 which are in contact with three threads 34, 41 and 35 on the worm.
  • the intermediate teeth 37, 38 are in contactwith the threads along both their flanks simultaneously whereas the extreme teeth 36, 39 come into contact with the threads along one of their flanks only.
  • the condition (1) must be verified for the following two pairs of points.
  • the first pair is formed by two points 42, 43 on the extreme thread 34, point 42 being situated on the tooth 37 at the periphery of the worm, on that flank remote from the axis 22, and point 43 being situated on the adjacent flank of the tooth 36 at the periphery of the pinion.
  • the second pair is formed by points 44, 45 homologous to the points 42, 43 and situated on the other extreme thread 35.
  • the possible insertion axes must comprehend this perpendicular, which forms an axis of symmetry.
  • condition (I) imposes certain limits on the dimensions of the worm and pinion and on their relative positions.
  • FIG. 6, therefore, illustrates how to determine, by means of the condition (1), the maximum diameter of the pinion such that at least one insertion axis exists.
  • the generatrix of the conical outer surface of the worm is assumed to have an inclination of 35 relative to the wonn axis.
  • the pinion has 11 teeth, each 16 millimeters wide.
  • the distance from the center of the pinion to the worm axis is 80 millimeters and the distance between this center and the generatrix of the cone is 30 millimeters.
  • the maximum diameter of the pinion for which at least one insertion axis exists may be determined graphically as follows, proceeding by means of successive approximations:
  • the position of the axis 22 is then modified so that, with the above-mentioned equation still satisfied, the quantity dh/r, relating to the point 44 and the point 45 defined above, has a value respectively greater than and lower than the common value relating to points 42 and 43.
  • this determination of the maximum diameter may be carried out in other ways.
  • an electronic computer could be used.
  • the width of teeth 16 mm.
  • the maximum diameter for the pinion is of the order of 94 mm.
  • the only insertion axis is then the axis of symmetry, i.e. the perpendicular dropped from the center of the pinion onto the worm axis.
  • width of teeth I 1 mm.
  • the worm and pinion cannot be assembled without splitting one or other of these elements.
  • the pinion diameter must be reduced to 84 mm.
  • the pinion has five teeth in engagement with the worm, three of which are, in the insertion position, in contact with the worm threads along both their flanks.
  • this condition (I) need only be satisfied over at least 70 percent of the effective height of the tooth, in the case of teeth having parallel flanks.
  • the effective height of a tooth is defined as that length of the flank of the tooth which is in contact with the threads of the worm when the pinion is fully inserted.
  • This effective height of the teeth can be further increased if the flanks are not parallel over the entire height of the tooth.
  • FIG. 7 shows a cylindrical worm 48 with a diameter of I00 mm. cooperating with a pinion 49 having 15 teeth.
  • the width of the teeth is 11 mm., and the center-to-center distance between the worm and pinion is 80 mm. It has been demonstrated above that, with these characteristics, there is no insertion axis for a pinion diameter greater than 84 mm. if the teeth have parallel flanks. In the embodiment in FIG. 7, the flanks of the teeth are parallel over a height of 15 mm. from the base of the teeth, and then have a convergent portion 51 forming an angle of the order of 30 with the tooth axis. Under these conditions, the pinion diameter may be up to 100 mm. There is then an insertion axis 22, which is the axis of symmetry.
  • the worm and pinion can be assembled in all angular positions of the worm.
  • the worm and pinion may have profiles and dimensions such that assembly is only possible in a limited number of angular positions of the worm, possibly even only one of these positions.
  • FIG. 8 therefore, shows a cylindrical worm 52, having an external diameter of 100 mm. and cooperating with a pinion 53 having 13 teeth with parallel flanks.
  • the centertocenter distance between the worm and pinion is 80 mm., and the effective height of the teeth is 20 mm.
  • the pinion 53 has three teeth simultaneously in engagement along both their flanks with the worm threads whatever the angular position of the worm. It is found that, for this etfective tooth height, no insertion axis which fulfills the condition (1) exists. Either the tooth height must be reduced, or the worm or pinion must be split.
  • the worm 52 may be truncated on the low-pressure side by means of a conical surface 54, which is coaxial with the worm.
  • a conical surface 54 which is coaxial with the worm.
  • the length of engagement of the worm with the pinion extends substantially over a whole number of teeth.
  • the number of positions of the worm which permit assembly of the worm and pinion is equal to the number of worm threads.
  • a single thread may be truncated, as indicated in FIG. 9.
  • only thread 62 is truncated at 63 on the low-pressure side.
  • machines may be constructed in which the pinion has only two teeth in contact with the worm along both of their flanks in at least one angular position of the worm, and at most four teeth in engagement with the threads in all positions of the worm.
  • machines may be built in which the pinion has, in at least one angular position of the worm, only three teeth in engagement along both their flanks with the worm threads, the number of teeth in engagement being at most five for all positions of the worm.
  • condition (1) is independent of the number of threads on the worm. This number can therefore be selected in such a way that each thread extends, in a known fashion, over an angular sector of the worm substantially equal to the angular interval separating two successive pinions. This last condition, of course, permits optimum use of the volume between two adjacent threads.
  • the exact angular extent of each thread may be determined while taking wellknown considerations into account, for example the fact that the number of worm threads and the number of teeth on the pinions are preferably incommensurable.
  • Machines according to the invention can give high deliveries and compression ratios, while using one-piece worms and pinions which do not deform during operation and which ensure long service.
  • the solution provided by means of the invention makes it possible to make machines of the kind specified having cylindrical worms with compression or expansion ratios greater than 10.
  • such high compression ratios can be obtained only with conical worms, which, as already stated, have the disadvantage of producing considerable axial thrust, or with worms or pinions made in a plurality of parts, which deteriorate rapidly.
  • These high compression ratios are particularly desirable in the refrigeration industry.
  • a fluid compression or expansion machine comprising a casing, a worm rotatable in said casing about a first axis, at least one toothed pinion rotatable in said casing about a second axis which is transverse to said first axis, said worm having a plurality of threads in meshing engagement with the teeth of said pinion, said casing having passageways for the fluid at lower and higher pressure respectively and having a portion in sealing engagement with the crests of the worm threads and defining fluidtight chambers between the casing and the threads of the worm, said chambers coming successively into communication with the higher pressure passageway on the high-pressure side of the worm and being successively sealed off from the lower pressure passageway by a pinion tooth, the number of the teeth of one pinion which simultaneously mesh with threads of the worm being greater than three for at least one angular position of the worm about said first axis, the first of said simultaneously meshing teeth having at least part of its flanks inclined at an angle with respect
  • M is a point of contact between a v vorm thread and one flank of a pinion tooth, said flank being on the opposite side of said tooth from said straight line,
  • M is a point of contact between a worm thread and one flank of a pinion tooth, said flank being on the same side of the tooth as said straight line,
  • d is the distance between point M, andsaid straight line, said distance being algebraically meastired from point M, along the tangent at point M, to said flank of the tooth,
  • h is the distance from point M, to the perpendicular dropped from the center of the pinion to said tangent, said distance being algebraically measured from point M, along said tangent,
  • r is the absolute value of the distance from point M, to the projection of said first axis on the plane of contact between the worm and the pinion,
  • d,, h,, r, are the same as d,, h,, r, but relative to point M,.
  • each tooth of the pinion has parallel flanks, and in which said condition is satisfied over at least 70 percent of that portion of the teeth which is in contact with the threads of the worm.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)
  • Transmission Devices (AREA)
US884606A 1968-12-27 1969-12-12 Rotatable worm fluid compression-expansion machine Expired - Lifetime US3632239A (en)

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FR181008 1968-12-27

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JP (1) JPS5131363B1 (enrdf_load_stackoverflow)
FR (1) FR1601531A (enrdf_load_stackoverflow)
NL (1) NL166096C (enrdf_load_stackoverflow)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4227867A (en) * 1978-03-06 1980-10-14 Chicago Pneumatic Tool Company Globoid-worm compressor with single piece housing
US4484872A (en) * 1982-01-14 1984-11-27 Omphale S.A. Globoid-worm machine with tapered screw clearance near high pressure end seal
US4775304A (en) * 1986-07-03 1988-10-04 The United States Of America As Represented By The Secretary Of The Navy Centrifugal scavenging system for single screw compressors
US4981424A (en) * 1988-12-21 1991-01-01 The United States Of America As Represented By The Secretary Of The Navy High pressure single screw compressors
US5082431A (en) * 1986-07-03 1992-01-21 The United States Of America As Represented By The Secretary Of The Navy Mechanical scavenging system for single screw compressors
US5255205A (en) * 1990-03-02 1993-10-19 Hewlett-Packard Company Method and apparatus for regulating fluid flow
US6122824A (en) * 1995-11-01 2000-09-26 Jensen; David L. Method for manufacturing fluid compression/compressor rotor
GB2356021A (en) * 1999-10-26 2001-05-09 Shiliang Zha Screw and pinion teeth profiles in a single screw compressor
US6547545B1 (en) * 1998-12-09 2003-04-15 Joensson John Holger Rotary machine for a compression or an expansion of a gaseous working fluid
US20040037730A1 (en) * 2001-01-05 2004-02-26 Hiromichi Ueno Single-screw compressor
GB2402974A (en) * 2003-06-17 2004-12-22 Richard See Rotary device in which rotor has sectors of different radii
WO2006043024A1 (en) * 2004-10-21 2006-04-27 Turnstile Technology Limited Rotary device
US20100074785A1 (en) * 2006-11-24 2010-03-25 Daikin Industries, Ltd. Compressor
US20100183468A1 (en) * 2007-06-22 2010-07-22 Daikin Industries, Ltd. Single screw compressor structure and method of assembling single screw compressor including the same
US20100247364A1 (en) * 2007-05-14 2010-09-30 Daikin Industries, Ltd. Single screw compressor structure
CN108131167A (zh) * 2017-12-06 2018-06-08 西安交通大学 一种离心式单螺杆压缩机或膨胀机
CN108150416A (zh) * 2017-12-13 2018-06-12 西安交通大学 一种单螺杆压缩机轴的悬臂式布置结构

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2315503C2 (de) * 1973-03-28 1983-03-31 Omphale S.A., Puteaux, Hauts-de-Seine Außenachsige Rotationskolben-Verdichtungs-oder Expansionsmaschine
JP5074511B2 (ja) * 2007-09-28 2012-11-14 大資 鳥越 容積形ガス圧縮機
JP5125524B2 (ja) * 2008-01-11 2013-01-23 ダイキン工業株式会社 スクリュー圧縮機
JP2011021574A (ja) * 2009-07-17 2011-02-03 Mitsui Seiki Kogyo Co Ltd 単一のゲートロータを有するスクリューコンプレッサにおける圧縮室構造

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US711083A (en) * 1898-11-14 1902-10-14 Charles Havelock Taylor Rotary engine.
DE334636C (de) * 1921-03-18 Wilhelm H Eyermann Anordnung an Schneckenradmaschinen
US2279414A (en) * 1940-10-24 1942-04-14 George R Scott Worm for use in double enveloping worm gearing
US2603412A (en) * 1947-01-23 1952-07-15 Curtiss Wright Corp Fluid motor or compressor
US3180565A (en) * 1962-05-08 1965-04-27 Zimmern Bernard Worm rotary compressors with liquid joints
US3181296A (en) * 1962-01-31 1965-05-04 Zimmern Fernand Gas engine with continuous fuel injection

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE334636C (de) * 1921-03-18 Wilhelm H Eyermann Anordnung an Schneckenradmaschinen
US711083A (en) * 1898-11-14 1902-10-14 Charles Havelock Taylor Rotary engine.
US2279414A (en) * 1940-10-24 1942-04-14 George R Scott Worm for use in double enveloping worm gearing
US2603412A (en) * 1947-01-23 1952-07-15 Curtiss Wright Corp Fluid motor or compressor
US3181296A (en) * 1962-01-31 1965-05-04 Zimmern Fernand Gas engine with continuous fuel injection
US3180565A (en) * 1962-05-08 1965-04-27 Zimmern Bernard Worm rotary compressors with liquid joints

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4227867A (en) * 1978-03-06 1980-10-14 Chicago Pneumatic Tool Company Globoid-worm compressor with single piece housing
US4484872A (en) * 1982-01-14 1984-11-27 Omphale S.A. Globoid-worm machine with tapered screw clearance near high pressure end seal
US4775304A (en) * 1986-07-03 1988-10-04 The United States Of America As Represented By The Secretary Of The Navy Centrifugal scavenging system for single screw compressors
US5082431A (en) * 1986-07-03 1992-01-21 The United States Of America As Represented By The Secretary Of The Navy Mechanical scavenging system for single screw compressors
US4981424A (en) * 1988-12-21 1991-01-01 The United States Of America As Represented By The Secretary Of The Navy High pressure single screw compressors
US5255205A (en) * 1990-03-02 1993-10-19 Hewlett-Packard Company Method and apparatus for regulating fluid flow
US6122824A (en) * 1995-11-01 2000-09-26 Jensen; David L. Method for manufacturing fluid compression/compressor rotor
US6547545B1 (en) * 1998-12-09 2003-04-15 Joensson John Holger Rotary machine for a compression or an expansion of a gaseous working fluid
GB2356021A (en) * 1999-10-26 2001-05-09 Shiliang Zha Screw and pinion teeth profiles in a single screw compressor
GB2356021B (en) * 1999-10-26 2003-12-17 Shiliang Zha Single screw compressor
US20040037730A1 (en) * 2001-01-05 2004-02-26 Hiromichi Ueno Single-screw compressor
EP1357292A4 (en) * 2001-01-05 2004-03-17 Daikin Ind Ltd EINSCHRAUBENVERDICHTER
US6896501B2 (en) 2001-01-05 2005-05-24 Daikin Industries, Ltd. Single-screw compressor
GB2402974A (en) * 2003-06-17 2004-12-22 Richard See Rotary device in which rotor has sectors of different radii
US20070175435A1 (en) * 2003-06-17 2007-08-02 See Richard J Rotary compressor and expander, and rotary engine using the same
US7650871B2 (en) 2003-06-17 2010-01-26 Turnstile Technology Limited Rotary compressor and expander, and rotary engine using the same
WO2006043024A1 (en) * 2004-10-21 2006-04-27 Turnstile Technology Limited Rotary device
US20100074785A1 (en) * 2006-11-24 2010-03-25 Daikin Industries, Ltd. Compressor
US8105059B2 (en) * 2006-11-24 2012-01-31 Daikin Industries, Ltd. Compressor with screw rotor and gate rotor with inclined gate rotor center axis
US20100247364A1 (en) * 2007-05-14 2010-09-30 Daikin Industries, Ltd. Single screw compressor structure
US8337184B2 (en) 2007-05-14 2012-12-25 Daikin Industries, Ltd. Single screw compressor structure
US20100183468A1 (en) * 2007-06-22 2010-07-22 Daikin Industries, Ltd. Single screw compressor structure and method of assembling single screw compressor including the same
US8485804B2 (en) 2007-06-22 2013-07-16 Daikin Industries, Ltd. Single screw compressor structure and method of assembling single screw compressor including the same
CN108131167A (zh) * 2017-12-06 2018-06-08 西安交通大学 一种离心式单螺杆压缩机或膨胀机
CN108150416A (zh) * 2017-12-13 2018-06-12 西安交通大学 一种单螺杆压缩机轴的悬臂式布置结构

Also Published As

Publication number Publication date
NL166096B (nl) 1981-01-15
DE1964387A1 (de) 1970-08-27
FR1601531A (enrdf_load_stackoverflow) 1970-08-24
DE1964387B2 (de) 1976-09-30
JPS5131363B1 (enrdf_load_stackoverflow) 1976-09-06
NL166096C (nl) 1981-06-15
NL6919475A (enrdf_load_stackoverflow) 1970-06-30

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