US3180565A - Worm rotary compressors with liquid joints - Google Patents

Worm rotary compressors with liquid joints Download PDF

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Publication number
US3180565A
US3180565A US278125A US27812563A US3180565A US 3180565 A US3180565 A US 3180565A US 278125 A US278125 A US 278125A US 27812563 A US27812563 A US 27812563A US 3180565 A US3180565 A US 3180565A
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worm
threads
casing
compressor
pinion
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Zimmern Bernard
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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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members 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

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  • the present invention concerns various improvements relating to rotary compressors utilizing hour-glass worms as drive members and in which the tightness between the worm threads and the pinion teeth is ensured by liquid joints, the said improvements making it possible, in particular, to' produce compressors having an appreciable eitective volume corresponding to a reduced number of Worm threads and aifording nevertheless a high compression rate per stage, whilst using hour-glass worms and pinions made in one piece.
  • the inventor has noticed in fact that in order to obtain an important effective volume between the threads of such of a screw, without having to split either the screw or the pinions into several pieces and assemble thosetwo types of components by successive segments, it'becomes necessary to resort to worms having but four to six threads, and capable of cooperating with unitary pinions having preferably seven or eleven teeth respectively.
  • Another improvement within the'scope of the present invention concerns the relative forms to be given to the worm extension on the high pressure side, as well as to the surrounding casing, in order to eliminate all axial thrusts on the worm and make it possible'for the compressor bearings to rotate at a high speed, so as to obtain the highest possible power to weight ratio.
  • the inventor advocates, as a means of avoiding said breaks in continuity and simplitying the construction of compressors, the use of casings having a linear profile in cross-section, i.e. conical casings producing a compression rate which increases in proportion to the angle of opening of the cone, 'thesaid casings becoming at the extreme limit, for an angle of opening of 180,plarie-shaped casings cooperating with discs carrying spirally shaped threads, and placed at right angles to the casing axis.
  • FIGURE 1 shows diagrammatically a diametral cross section .of an ordinary hour-glass worm mounting, indicating the shape ordinarily given to the teeth of a unitary pinion in order to enable them to be inserted between the threads of a unitary 'globoid worm, the delivery rate of compressed gas being very low with this type of mounting.
  • FIGURE 2 shows one half of a diametral cross section of a compressor having a higher rate of delivery, with a unitary six thread hour-glass worm cooperating with a truncated cone shaped casing together with two unitary pinions having eleven teeth.
  • FIGURE 3 shows one half of a cross section similar to FIGURE 2, but relates to a compressor with a unitary four thread hour-glass worm cooperating with two unitary pinions of seven teeth.
  • FIGURE 1 shows hour-glass worm 1, truncated at its upper and lower portions according to conical profiles 2 and 3, and cooperating with a pinion 4 having fifteen teeth adapted to engage 'with the threads of said worm.
  • Worm 1 has a circular outer profile, corresponding to chain dotted circle 5, the latter being concentric with circle 6 which corresponds to the bottom of the threads in worm 1.
  • the required result is obtained by reason of the fact that the faces '14 and 15- in threads worm and'pinion s can be either made in one piece or formed by assembling several segments into'one piece prior to inserting the pinion teeth within the worm threads.
  • FIGURE 2 shows the hour-glass worm .10, whose top portion is truncated according to conical profileindicated in 2a, and whose eifective outer profile is also conical as may be seen in 5a, on said figure.
  • Theroots of the threads define a concave portion of the worm surface which is part circular when seen in axial section.
  • Theworm extends in 2%, beyond said effective part
  • said extension corresponding in shape to the profile of the conical casing which surrounds it.
  • Median tooth 24 in the eifective sector of said pinion can therefore penetrate easily between threads 18 and 23, owing to the fact that sides 25 and 26 respectively associated to threads 23 and 18, adapted to cooperate on chambers contained by the casings and the worm, as a result of the reduced number of threads.
  • the sides of adjacent worm threads may be made to converge outwardly, since it becomes possible to place pinion 29 in a position wherein, as in the case shown in cross section on -FIGURE 3, there ison worm 1b but one thread 30 requiring to be engaged with two adjacent teeth 31 and 32 on pinion 29 ,said thread beingevenable to have in cross section any convex shape capable of being-easily inserted between said teeth 31 and 32 on pinion 29.
  • FIGURE 4 concerns a compressor in which worm 1c, having a cylindrical profile on the major part'of its height, is truncated in'Zb, at its top portion, for suction.
  • This figure shows how it is possible to avoidthe production by the: compressed gases of an upward. axial thrust on the, lower face of a vertically placed worm having a cylindrical outer profile, and consequently to relieve the bearings, so as to make it possible to increase the rotational speed and thepower to weight ratio of the compressor, taking into account the fact that the worm isnot subjected toradial thrusts, since the compressor is provided with pinions mounted in pairs.
  • The-worm 1c in FIGURE 4 comprises beyond its effective portion, i.e..beyond point 191:, a cylindrical extension 29a.
  • liquid in the joints can penetrate between the. worm and the casings below point 1%, and accumulate within exhaust groove. 34, which makes it necessary to provide, below worm 10, a circular segment 37, forming a plane joint, said segment resting on at least onespring 38 in order to protect the roller bearings carrying the spindle 8 of worm 1c.
  • the compressor shown on FIGURE 5 includes worm 10 having a cylindrical outer profile, as well as an exhaust groove 34 communicating with the suction side by means of a duct 35, asin the case of FIGURE 4.
  • the roots of the threads define a concave portion of the worm surface which is part circular when seen in axial section.
  • the worm has six threads, and it will be seen that both pinions 39 and 40 are provided with eleven teeth having two parallel sides and similar in type to those shown on FIGURE 2.
  • the effective compression rate in a compressor of this kind is in fact slightly higher than the theoretical rate. It may range from 5.5 to 6, whereas its theoretical value is between 4 and 5, which makes it possible to produce compressed air at a 7 kg./cm. pressure, with a good efficiency factor.
  • the figure shows in 41 an exhaust port, outlined in.
  • the position in height of worm 10 can be adjusted by means of threaded plug 42.
  • worm 1c is mounted between casing 43 and cap 44, by means of lower bearing 45 and upper bearing 46, lower bearing 45 resting on a spring washer 47 and both bearings being protected from all contact with the liquid in the joints by means of circumferential gaskets 48 and 49 respectively.
  • Pinion 39 made in a plastic substance, is mountedon a steel support.
  • the assembly-of said drive member includes in the lower part a washer 47a and a tightening screw 69.
  • This assembly includes in the upper part two screws 42a.
  • a lubricator cap 70 is provided for lubricating bearing 46a.
  • the compressed air outlet duct 60 is made up in fact by bringing together two ducts '71 and 72 which receive respectively the compressed air in the vicinity of upper pinions 62 and 63.
  • the lower duct 61 is made up of two ducts 73 and 74 brought together. A portion of duct 73 has been taken away in order to show that the said duct receives compressed air at the level of the lower left pinion, not
  • duct 74 receives compressed air at the level of pinion 64.
  • FIGURE 6 shows in cross section one of the effective portions of the compressor, indicated by 51, wherein the threads are spiral shaped, and not helix shaped as usual, the depth of said threads increasing gradually from point 52 up to the median portion corresponding substantially to the position of thread 51, and decreasing beyond that position towards the periphery of the disc, i.e.
  • the disc includes. two spiral threads symmetrically placed relatively to the median plane of the compressor and situated respectively one on the top of the disc/the other on the bottom.
  • the decrease in diameter of the compressor from the inlet of gases to their outlet in the vicinity of the spindle acting in combination With the gradual reduction in the depth of threads provided immediately beyond the position shown in FIGURE 6, and with the gradual reduction in the length of compression chambers, is operative in producing a high compression rate of about 5.
  • the compressor in FIGURE 6 has four pinions, three of which are indicated on the drawing by the numerals 62, 63 and 64.
  • a grease box a is also provided in the lower portion of spindle 59 for lubricating bearing 45a.
  • the edge in the sectionedpart 58 of cover 55 corresponds to one of the millings provided to secure a clearance for the various pinions.
  • the casing on which bear the two covers 54 and 55 can be seen on the drawing, in particular at76. This casing whose outer shape is formed by a surface of revolution has an internal dissymmetry and forms a suction volute before joining up with the suction in the straight portion of the drawing.
  • pinion 62 can also be seen in FIG- URE 7, with its steel support indicated under the numeral Said pinion and support are mounted on one of the shafts 78 by means of a spring'washer 79 and a screw 80a which fulfils the same function as screw 80 seen in FIGURE 5.
  • the truncated ridges of three out of the four threads in disc 12 are indicated respectively by numerals 81, 82 and 83, the sides of said threads being indicated respectively by numerals 81a, 82a, 82b and 83b, and the truncated peripheral portions of said'threads being indicated by numeral 2d.
  • the dotted line indicated by numeral 84 shows the shape given to a compressed air exhaust port leading through'cover 54 and opening into duct 71 by means of outlet 85.
  • a compressor comprising a casing having a central axis, a disc rotatably and coaxially mounted in said casing, atleast one face of said disc being formed with a coaxial annular depression therein, said depression being partcircular in section, a plurality of spirally extending threads projecting upwardly from said depression to the level of the remainder of said disc surface, the inner surface of said casing comprising a portion positioned to be swept by side carries four threads, with not less than two nor more than three of said threads meshing with each pinion at.
  • a compressor as claimed in claim 4 in which said threads mesh with said pinions over an arc of about 102".
  • a compressor comprising a casing having a central axis, a one-piece drive member rotatably and coaxially mounted in said casing, said'drive member having at least one concave surface portion which defines a pair of circular arcs in those planes containing said axis, a group of screw threads positioned on said concave surface, the crests of said threads lying in the locus generated by a straight line rotated about a point on said axis, at least part of the inner surface of said casing being positioned to be swept by said crests and define therewith a plurality of pressure chambers extending from one end'of said group of screw threads to the other, a plurality of toothed pinions mounted to turn about axes perpendicular to the axis of said drive/member and projecting through said casing to mesh with said threads, each thread traversing.
  • a compressor as claimed in claim 6 in which said drive member terminates near the inlet end of the thread group in a surface transverse to said locus, and said transverse surface terminates where it meets said locusinia chamfer defining one wall of a passageway communicate ing withsaid inlet.
  • a compressor as claimed in claim 7 in which said drive member carries six discrete threads and there are two of said pinions, the two flanks of each tooth on said pinions being parallel to each other.
  • a compressor as claimed in claim 8 in which each pinion has eleven teeth.
  • a compressor as claimed in claim 7 in which said drive member carries four discrete threads and there are two of said pinions, and in which the two flanks of each pinion tooth converge as they approach the center of the.
  • A-compressor as claimed in claim 10 in which each .2 taining said axis and provided with a group of said threads having their crests in a plane which constitutes the locus generated by said straight line, said disc being formed with a peripheral edge transverse tosaid one face positioned near the inlet end of 'saidthread group, and. said edge terminating whereit meets said one face in a chamfer defining one wall of'a passage which communicates with said inlet.
  • a compressor as claimed'in claim 13 comprising a single drive member having two oppositely facing concave surface portions, eachofwhich defines a circular arc in those planes containing said axis, and is provided with a group of said threads with the crests of, the threads posi tioned onsaid two concave surface portions lying in the loci generated by twoparailel lines perpendicular to said axis which are rotated thereabout, and a pair of pinions engaging the threads on each ofcsaid. concave surface portions.
  • a compressor. as claimed 'in'claim 14 in' which there are four discrete threads on each concave surface portion and the two fianks of each pinion tooth converge as they approach the center of the pinion on which that tooth is carried.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US278125A 1962-05-08 1963-05-06 Worm rotary compressors with liquid joints Expired - Lifetime US3180565A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR896859A FR1331998A (fr) 1962-05-08 1962-05-08 Perfectionnements aux compresseurs rotatifs à vis globique et à joints liquides

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US3180565A true US3180565A (en) 1965-04-27

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DE (1) DE1503667C3 (de)
FR (1) FR1331998A (de)
GB (1) GB1046465A (de)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3632239A (en) * 1968-12-27 1972-01-04 Bernard Zimmern Rotatable worm fluid compression-expansion machine
US3841806A (en) * 1973-04-05 1974-10-15 Rudy S Compressors and expansion machines of the worm and pinion type
US3905731A (en) * 1974-10-04 1975-09-16 Bernard Zimmern Baffle structure for rotary worm compression-expansion machines
US3932077A (en) * 1973-03-13 1976-01-13 Bernard Zimmern Rotary interengaging worm and worm wheel with specific tooth shape
JPS5128849B1 (de) * 1970-07-23 1976-08-21
USRE30400E (en) * 1968-02-08 1980-09-09 Globoid-worm compressors
US4470781A (en) * 1982-09-29 1984-09-11 Bernard Zimmern Positive displacement meshing screw machine
US4569640A (en) * 1982-05-13 1986-02-11 Bernard Zimmern Device for high pressure compression
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
US4890461A (en) * 1987-07-21 1990-01-02 Bernard Zimmern Hermetic or semi-hermetic refrigeration motor-compressor unit
US5080568A (en) * 1990-09-20 1992-01-14 Bernard Zimmern Positive displacement rotary machine
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
US5087182A (en) * 1989-09-12 1992-02-11 Bernard Zimmern Casing construction for screw compression/expansion machines
US20100003153A1 (en) * 2006-11-02 2010-01-07 Daikin Industries, Ltd. Compressor
US20100158737A1 (en) * 2007-05-23 2010-06-24 Daikin Industries, Ltd. Screw compressor
CN101832267A (zh) * 2010-04-28 2010-09-15 北京力通高科技发展有限公司 节能单螺杆压缩机
US20100278677A1 (en) * 2007-12-28 2010-11-04 Daikin Industries, Ltd. Single-screw compressor
CN103114999A (zh) * 2012-09-29 2013-05-22 苏州利森空调制冷有限公司 一种单螺杆压缩机的节能压缩组件
CN103541896A (zh) * 2013-11-11 2014-01-29 阜新金昊空压机有限公司 单螺杆双星轮水泵
CN106593859A (zh) * 2017-01-10 2017-04-26 黄山工业泵制造有限公司 一种盘轮式容积式泵
CN110446858A (zh) * 2017-03-21 2019-11-12 大金工业株式会社 单螺杆压缩机

Families Citing this family (12)

* 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
GB1548390A (en) * 1975-08-18 1979-07-11 Hall Thermotank Prod Ltd Sealing arrangement in a rotary fluid machine
FR2352182A1 (fr) * 1976-05-17 1977-12-16 Rylewski Eugeniusz Machine tournante a fluide
FR2505415B1 (fr) * 1981-05-11 1985-06-21 Zimmern Bernard Pompe monovis equilibree a forte puissance massique
FR2508113A1 (fr) * 1981-06-17 1982-12-24 Zimmern Bernard Machine volumetrique a vis et pignons
FR2541367B1 (fr) * 1982-01-14 1986-01-03 Zimmern Bernard Anneau d'etancheite pour machine volumetrique a vis et pignon
FR2519712A1 (fr) * 1982-01-14 1983-07-18 Omphale Sa Vis cylindro-conique pour machine volumetrique a vis et pignon
FR2541437B1 (fr) * 1982-05-13 1985-08-23 Zimmern Bernard Economiseur centrifuge pour refrigeration
FR2611000B1 (fr) * 1987-02-12 1991-08-16 Zimmern Bernard Pignon flottant avec ressort pour machine volumetrique
FR2620205A1 (fr) * 1987-09-04 1989-03-10 Zimmern Bernard Compresseur hermetique pour refrigeration avec moteur refroidi par gaz d'economiseur
FR2624215B1 (fr) * 1987-12-03 1990-05-11 Zimmern Bernard Pignons flottants pour machine a vis haute pression
US4968231A (en) * 1988-02-23 1990-11-06 Bernard Zimmern Oil-free rotary compressor with injected water and dissolved borate

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US265381A (en) * 1882-10-03 Water motor
US1367801A (en) * 1919-12-23 1921-02-08 Daniel N Clark Rotary engine
US1654048A (en) * 1924-11-19 1927-12-27 Westinghouse Electric & Mfg Co Gear pump
US1735477A (en) * 1922-06-16 1929-11-12 Stuart Res Engineering Corp Method of and apparatus for compressing and expanding elastic fluids
DE494168C (de) * 1927-12-03 1930-03-19 Motor Pumpen G M B H Einrichtung zur Selbstansaugung von Schraubenkolbenpumpen mit Widerlagerzahnscheiben
US1989552A (en) * 1934-01-03 1935-01-29 Paul E Good Rotary compressor
US2158933A (en) * 1937-07-26 1939-05-16 Paul E Good Rotary compressor
US2500143A (en) * 1946-09-26 1950-03-07 Arnold E Biermann Rotary abutment compressor
US2603412A (en) * 1947-01-23 1952-07-15 Curtiss Wright Corp Fluid motor or compressor
US2716861A (en) * 1948-05-19 1955-09-06 Goodyear James Wallis Pressure energy translating and like devices
FR1259874A (fr) * 1960-06-16 1961-04-28 Compresseur ou pompe à fluide

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US265381A (en) * 1882-10-03 Water motor
US1367801A (en) * 1919-12-23 1921-02-08 Daniel N Clark Rotary engine
US1735477A (en) * 1922-06-16 1929-11-12 Stuart Res Engineering Corp Method of and apparatus for compressing and expanding elastic fluids
US1654048A (en) * 1924-11-19 1927-12-27 Westinghouse Electric & Mfg Co Gear pump
DE494168C (de) * 1927-12-03 1930-03-19 Motor Pumpen G M B H Einrichtung zur Selbstansaugung von Schraubenkolbenpumpen mit Widerlagerzahnscheiben
US1989552A (en) * 1934-01-03 1935-01-29 Paul E Good Rotary compressor
US2158933A (en) * 1937-07-26 1939-05-16 Paul E Good Rotary compressor
US2500143A (en) * 1946-09-26 1950-03-07 Arnold E Biermann Rotary abutment compressor
US2603412A (en) * 1947-01-23 1952-07-15 Curtiss Wright Corp Fluid motor or compressor
US2716861A (en) * 1948-05-19 1955-09-06 Goodyear James Wallis Pressure energy translating and like devices
FR1259874A (fr) * 1960-06-16 1961-04-28 Compresseur ou pompe à fluide

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE30400E (en) * 1968-02-08 1980-09-09 Globoid-worm compressors
US3632239A (en) * 1968-12-27 1972-01-04 Bernard Zimmern Rotatable worm fluid compression-expansion machine
JPS5128849B1 (de) * 1970-07-23 1976-08-21
US3932077A (en) * 1973-03-13 1976-01-13 Bernard Zimmern Rotary interengaging worm and worm wheel with specific tooth shape
US3841806A (en) * 1973-04-05 1974-10-15 Rudy S Compressors and expansion machines of the worm and pinion type
US3905731A (en) * 1974-10-04 1975-09-16 Bernard Zimmern Baffle structure for rotary worm compression-expansion machines
US4569640A (en) * 1982-05-13 1986-02-11 Bernard Zimmern Device for high pressure compression
US4470781A (en) * 1982-09-29 1984-09-11 Bernard Zimmern Positive displacement meshing screw machine
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
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
US4890461A (en) * 1987-07-21 1990-01-02 Bernard Zimmern Hermetic or semi-hermetic refrigeration motor-compressor unit
US5087182A (en) * 1989-09-12 1992-02-11 Bernard Zimmern Casing construction for screw compression/expansion machines
US5080568A (en) * 1990-09-20 1992-01-14 Bernard Zimmern Positive displacement rotary machine
US8192187B2 (en) * 2006-11-02 2012-06-05 Daikin Industries, Ltd. Compressor with screw rotor and gate rotor
US20100003153A1 (en) * 2006-11-02 2010-01-07 Daikin Industries, Ltd. Compressor
US20100158737A1 (en) * 2007-05-23 2010-06-24 Daikin Industries, Ltd. Screw compressor
US8419397B2 (en) 2007-05-23 2013-04-16 Daikin Industries, Ltd. Screw compressor
CN101668951B (zh) * 2007-05-23 2011-06-08 大金工业株式会社 螺杆压缩机
US8523548B2 (en) * 2007-12-28 2013-09-03 Daikin Industries, Ltd. Screw compressor having a gate rotor assembly with pressure introduction channels
US20100278677A1 (en) * 2007-12-28 2010-11-04 Daikin Industries, Ltd. Single-screw compressor
CN101832267A (zh) * 2010-04-28 2010-09-15 北京力通高科技发展有限公司 节能单螺杆压缩机
CN103114999A (zh) * 2012-09-29 2013-05-22 苏州利森空调制冷有限公司 一种单螺杆压缩机的节能压缩组件
CN103541896A (zh) * 2013-11-11 2014-01-29 阜新金昊空压机有限公司 单螺杆双星轮水泵
CN106593859A (zh) * 2017-01-10 2017-04-26 黄山工业泵制造有限公司 一种盘轮式容积式泵
CN110446858A (zh) * 2017-03-21 2019-11-12 大金工业株式会社 单螺杆压缩机
CN110446858B (zh) * 2017-03-21 2021-08-03 大金工业株式会社 单螺杆压缩机
US11300124B2 (en) 2017-03-21 2022-04-12 Daikin Industries, Ltd. Single-screw compressor with a gap adjuster mechanism

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Publication number Publication date
DE1503667C3 (de) 1974-01-24
GB1046465A (en) 1966-10-26
DE1503667B2 (de) 1973-06-20
FR1331998A (fr) 1963-07-12
DE1503667A1 (de) 1970-07-16

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