US3717418A - Compressor barrel assembly - Google Patents

Compressor barrel assembly Download PDF

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Publication number
US3717418A
US3717418A US00044446A US3717418DA US3717418A US 3717418 A US3717418 A US 3717418A US 00044446 A US00044446 A US 00044446A US 3717418D A US3717418D A US 3717418DA US 3717418 A US3717418 A US 3717418A
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United States
Prior art keywords
diaphragms
casing
axial
shrouds
axially
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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 - Lifetime
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US00044446A
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English (en)
Inventor
K Pilarczyk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Elliott Turbomachinery Co Inc
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Carrier Corp
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Publication of US3717418A publication Critical patent/US3717418A/en
Assigned to ELLIOTT TURBOMACHINERY CO., INC. reassignment ELLIOTT TURBOMACHINERY CO., INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CARRIER CORPORATION, A CORP OF DEL.
Assigned to FIRST NATIONAL BANK OF CHICAGO, THE reassignment FIRST NATIONAL BANK OF CHICAGO, THE LICENSE (SEE DOCUMENT FOR DETAILS). Assignors: ELLIOT TURBOMACHINERY CO., INC.
Assigned to CONTINENTAL BANK N.A. reassignment CONTINENTAL BANK N.A. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ELLIOTT TURBOMACHINERY CO., INC.
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger

Definitions

  • the three stage centrifugal compressor of the present invention employs a one-piece cast casing having a cylindrical bore containing therein a removable barrel assembly, which assembly comprises three directly engaging diaphragms, three ditfusors, three shrouds and a rotor having three impellers, all in axially stacked relationship. Only the three diaphragms are axially clamped directly to each other by means of tension bolts.
  • the diffusers and shrouds are held by the diaphragms for axial free play and biased in one axial direction by axially compressed sealing O-rings and effective piston surfaces under the inuence of the Huid being pumped.
  • the end closure containing the bearings and drive for the overhung rotor has a cylindrical surface ush with the cylindrical bore of the casing, which surface is overlapped by the outer cylindrical surface of one of the diaphragms to provide for axial alignment.
  • Four engaging cylindrical surfaces on the diaphragms further assure axial alignment.
  • Fluid passages are provided integrally cast in the diaphragms and casing for conducting the fluid through intercoolers, between stages.
  • the axial limitations with respect to length are of considerable advantage in providing a minimum length to the cantilevered portion of an overhung rotor so that high speed operation may be possible,
  • the piping connections between stages are cast into removable diaphragme and one piece casing.
  • the removable barrel assembly includes a diaphragm, a shroud, a diffuser, and an impeller for each stage, with only the diaphragms being directly clamped to each other and the casing so that tolerance accumulation in the axial direction will be held to a minimum.
  • the shrouds and diffusers are stationarily mounted between the diaphragms, with axial free play so that their tolerances in the axial direction will not pass from one stage to another andl their considerable thermal expansion will not be an accumulating problem.
  • Means are provided to bias the shrouds and diffusers in one axial direction, and include sealing O-rings compressed in the axial direction and piston surfaces on the shrouds and ditfusers that will produce a net axial force in response to the pressure of the fluid being pumped.
  • the barrel assembly has the advantages of a rigid construction, separate pieces for each barrel element and only three elements axially clamped together that would produce a tolerance accumulation for the entire length of the assembly.
  • FIG. l is a perspective view of a complete compressor employing the features of the present invention.
  • FIG. 2 is a schematic flow sheet showing the path of the fluid as it moves between stages and through the intercoolers
  • FIG. 3 is a partial cross-sectional view taken on a vertical plane passing substantially through the axis of rotation of the compressor of FIG. l;
  • FIG. 4 is a partial perspective exploded view, with portions cut-away, of the one piece compressor casing and its relationship with the top wall of the intercooler chambers;
  • FIG. 5 is an enlarged cross-sectional view of the barrel assembly and its relationship to the compressor casing and drive, taken substantially in the same plane as FIG. 3;
  • FIG. 6 is a cross-sectional View taken along line 6-6 in FIG. 4;
  • FIG. 7 is a cross-sectional View of the casing taken along line 7-7 of FIG. 4;
  • FIG. 8 is a cross-sectional view of the casing taken along line 3-8 in FIG. 4;
  • FIG. 9 is a cross-sectional view of the casing taken along line 9-9 in FIG. 4 and FIG. 5;
  • FIG. ll is a cross-sectional view of the casing taken along line 11--11 of FIGS. 4 and 5;
  • FIG. 12 is a cross-sectional View of the casing taken along line 12-12 of FIGS. 4 and 5.
  • the compressor base 1 securely mounts an electric drive motor 2, which has an output shaft 3 for driving the rotor 4 through gear train 5.
  • the gear train 5 is mounted within a separate casing 6 that forms the end closure for the compressor casing 7.
  • the casings 6 and 7 are each cast in one piece from iron, and the base 1 is Welded sheet steel fabrication.
  • Inlet uid is provided for the compressor through an inlet housing S having mounted therein an inlet valve 9 controlled by a suitable mechanism 10.
  • intercooler chambers 11 and 12 for cooling the fluid between the first and second stages and between the second and third stages, respectively.
  • these intercooler chambers may be of any construction and include any type of conventional intercooling equipment, such as a parallel tube waterdluid heat exchanger.
  • inlet fluid passes through the first stage impeller 13, the intercooler chamber 11, the second stage impeller 14, the intercooler chamber 12, and the third stage impeller 15.
  • the cast iron casing 7 is provided with an axial cylindrical bore 16 and a planar surface 17, with a plurality of integrally cast passages therebetween for conducting the tiuid between stages and the intercoolers.
  • passage 18 conducts fluid from the first stage output to the intercooler chamber 11
  • passage 19 conducts fluid from the intercooler chamber 11 to the second stage
  • passage 20 conducts fluid from the second stage to the intercooler chamber 12
  • passage 21 conducts Huid from the intercooler chamber 12 to the third stage.
  • the passages in the top of the intercooler chambers have been given numbers corresponding to those used with respect to the casing 7, but with the addition of primes.
  • passages 18', 20' extend directly through the top plate of the base for discharge directly into the chambers 11 and 12, while the return fiuid from the chamber 11, 12 is conducted respectively, in passages 19', 21 which extend for substantially the full height of the base 1 between the intercooler chambers 11 and 12.
  • a three stage removable barrel assembly is shown within the cylindrical bore of the casing 7.
  • the first stage includes a diaphragm 22, a shroud 23, a diffuser 24 and the impeller 13; the second stage includes diaphragm 25, shroud 26, diffuser 27, and impeller 14; and the third stage includes diaphragm 28, shroud 29, diffuser 30, and impeller 1S.
  • Each of the diaphragms is a one piece iron casting, and each of the diffusers and shrouds is a one piece aluminum casting.
  • Each of the diaphragms 22, 25, 28 has an outer cylindrical surface in direct engagement with the inner cylindrical bore 16 of the casing 7.
  • the end closure formed by the gear casing 6 has an adjacent inner cylindrical surface 31 that is flush with the cylindrical surface 16 of the compressor casing 7, with the outer cylindrical surface of the diaphragm overlapping these ush inner cylindrical surfaces to accurately align the gear casing 6 with the barrel assembly for proper positioning of the rotor 4.
  • the gear casing 6 determines the positioning of the rotor 4, by means of the radial bearing 32 and the combination radial-thrust bearing 33 that rotatably mount the rotor 4 in an overhung position. These bearings provide the sole rotational support for the cantilever-ed rotor.
  • the rotor may be of any rigid type construction, but preferably the impellers 13, 14, 1S are integrally secured to the rotor shaft, with the interposition of suitable labyrinth seals as shown.
  • the various components are assembled outside the casing and slid from left to right, as viewed in FIG. 5, into the casings 6 and 7. Thereafter, the diaphragms 22, 25, 2S are rigidly secured to the gear casing 6 by means of a plurality of tension bolts 34.
  • the gear casing 6 forms the main axial reference element, with the thrust bearing 33 forming the axial fixed reference point for the rotor 4 and the end face 35 forming the axial reference point for the diaphragms; since the gear casing 6 is of a one piece cast construction, the axial distance between points 33 and 35 is fixed and may be accurately determined.
  • tolerance accumulation in the axial direction will occur only from point 35 to the left, as viewed in FIG. 5, and then only with respect to the three diaphragms 22, 25, 28 that are directly clamped to each other.
  • the shrouds 23, 26, 29 and diffusers 24, 27, 30 radially engage the diaphragms to fix their radial position and axially engage, in only one direction, the diaphragms to fix their axial position while allowing free axial play or clearance movement in the opposite axial direction with respect to the diaphragms.
  • biasing means including the axially compressed sealing O-rings 36, 37 and the piston action of the surface exposed to the pumped fluid on the diffusers and shrouds. More particularly, the O-ring 36 will exert an axial force to the right, as viewed in FIG.
  • the shroud 23 has a considerable surface area facing to the left that is exposed to the high pressure diffuser outlet of the first stage, which will produce an axial force to the right greater than the axial force to the left produced by the rightwardly facing area exposed to the high speed low pressure gas moving through the impeller 13 and blades of the diffuser 24; the diffuser 24 has substantially only a left-hand surface exposed to the pressurized gases to produce a net force in the righthand direction; analysis of the shroud 29 would be similar to that of the shroud 23, but with considerable affects obtained by the left-hand exposure of the shroud 29 t0 the gases within the first stage, to produce a net rightwardly oriented axial force; together, the diffusers Z, 30 have opposed surfaces exposed respectively to the outlet gases of the second and third stages, with the higher pressure gases of the third stage predominating to produce a net axial force in the right-hand direction; due to the c011- struction of the diaphragm 25, the shroud 26 has
  • additional O-rings are provided between adjacent surfaces, with many of these O-rings not being shown since they are conventional, but it being understood that these additional sealing O-rings do not contribute to the above-mentioned axial biasing of the shrouds and diffusers.
  • the axial biasing of the piston effects and the axially compressed O-rings 36, 37 are in the same righthand direction to complement each other.
  • annular chambers 38, 39, 40, 41 are sealed with respect to each other by any appropriate means, for example, O-rings (not shown).
  • the diaphragms 22, 25, 28 are provided with integrally cast passages or externally congurated surfaces cooperating with surfaces of adjacent diaphragms to form passages for conducting air between the annular chambers 38-41 and respective ones of the shrouds inputs and diffuser outputs.
  • the output from the last stage diffuser 30 is connected by the diaphragms into the annular chamber 42 formed by opposed annular channels in the diaphragm 25 and casing 7.
  • the high pressure compressor output may pass upwardly, as shown in FIG. 11, through an outlet 43 to the point of use, storage tank, conventional blow-off device, or the like.
  • the compressor output may be conducted from the annular chamber 42 downwardly through outlet 44 into the compressor base 1 to be connected to piping to the point of use and/ or be connected to various pressure responsive control and monitoring devices, which for example may have meters, warning lights or the like on the control panel 45 as shown in FIG. 1. Also, in FIG.
  • the outlet 43 is shown with a sealing plug or cap that is used when an excess pressure blow-off device is not employed and the compressor output is directed downwardly into the compressor base for connection with piping to the point of use.
  • the compressor output from annular chamber 42 is conducted by means of a generally axially extending passage 46 (FIG. 1l) that is cast into the casing 7, but not in communication with any of the previously described passages of the casing 7 except for those shown in FIG. 1l.
  • the passage 46 conducts a portion of the compressor output to annular chamber 47, which is shown in FIG. 5 as being formed by opposed annular channels respectively in the casing 7 and diffuser 22.
  • the high pressure compressor output is directed into an annular chamber 48 formed between the shroud 23 and diaphragm 22.
  • a nozzle may be inserted through the shroud 23 to direct the gases from chamber 48 against the blade tips of impeller 13 to produce a power recovery turbine action to take care of excess pressure on partial load. The structure and function of this power recovery will not be described in detail, because it forms the subject matter of one of the previously mentioned co-pending applications.
  • this capacity is built into the structure so that the chamber exists and if desired, appropriate pressure responsive valving may be incorporated into the passage 46 for dumping excess pressure into the annular chamber 48, and the shroud 23 may be drilled for reception of one or more nozzles to complete the turbine. This capacity is built in whether used or not.
  • the compressor barrel assembly of the present invention may be removed from the one-piece cast casing for inspection, repair and replacement of the various individual uid guide elements, particularly, the diaphragms, shrouds and diffusers.
  • the construction of these elements as individual pieces greatly facilitates the casting of the internal piping, a reduction in manufacturing cost, ease of replacement, and ease of modifying for power recovery.
  • the piston effects heretofore mentioned will predominate to hold the diffusers and shrouds tightly and sealingly in their proper positions.
  • the piston effects will increase proportionately with increased compressor pressures, to produce a desired corresponding increase in sealing effect.
  • Accurate alignment is obtained by means of telescopically engaging annular surfaces between the casing, diaphragms, diffusers and shrouds.
  • the cylindrical bore of the one piece casing forms the primary radial reference point, by providing engagement With the diaphragms and one piece impeller mounting housing.
  • the impeller has a thermal expansion reference point at its furtherest end provided by a thrust bearing, to provide additional length for thermal expansion of the rotor assembly, which additional length will have a greater thermal expansion than the corresponding relatively cool and massive casing 6, to compensate for the rather high thermal expansion to be encountered with the aluminum diaphragms, shrouds, and diflusers.
  • interstage piping being integrally cast into the casing and diaphragms, the size, complexity and cost of the compressor is greatly reduced. Correspondingly, setup time, sealing problems and maintenance are greatly reduced.
  • a pumping device comprising: a casing; a rotor rotatably mounted in said casing and having a plurality of centrifugal impellers; a plurality of annular diaphragms axially stacked Within said casing corresponding in number and respectively surrounding said impellers; means clamping said diaphragms axially directly to each other; a plurality of separate stationary diffusers correspondingly associated with and corresponding in number to said impellers, means mounting said difusers to said diaphragms about their respective irnpellers with axial free play with respect to said diaphragms; and resilient means axially biasing each of said diffusers relative to said diaphragms whereby axial expansion of said diffuser relative to said diaphragms will be absorbed.
  • said axially biasing means include a plurality of sealing G-rings.
  • said axially biasing means including separate piston means for each diffuser having at least one axial face subjected to the iluid being pumped for producing a net axial force biasing its associated diffuser toward an adjacent diaphragm.
  • said axially biasing means include a plurality of sealing O-rings.
  • the device of claim 1 constituting a multi-stage centrifugal compressor wherein said casing is a one piece casting having an inner cylindrical bore provided with a plurality of annular inwardly opening channels in fluid communication with respective impellers; and said dia-V phragms and casing having a plurality of integral passage means for conducting fluid out of the casing from each impeller and into said casing for at least some of said impellers.
  • the device of claim 1 including an end closure for one axial end of said casing; bearing means providing the sole rotational support of said rotor and being located solely on the side of said rotor with said end closure; and means providing removal of said rotor, said diaphragms and said diifusers axially from said casing in the direction opposite from said end closure.
  • the device of claim 6, constituting a multi-stage centrifugal compressor wherein there are three impellers on said rotor, with the first stage impeller having an inlet facing axially away from said end closure, the second stage impeller having an inlet facing said end closure, and the third stage impeller being located axially intermediate said first and second stage impellers and having an inlet facing away from said end closure.
  • the device of claim 1 including means for holding said diaphragms concentric with respect to each other in said casing, including cylindrical outer surfaces on said diaphragms in engagement with said casing, and telescopically interengaging cylindrical surfaces.
  • said means clamping include an end closure rigidly secured to said casing and a plurality of tension bolts axially extending through said diaphragms and into said end closure.
  • a pumping device comprising: a casing; a rotor rotatably mounted in said casing and having a plurality of open centrifugal impellers; a plurality of annular diaphragms axially stacked Within said casing corresponding in number and respectively surrounding said impellers; means clamping said diaphragms axially directly to each other; a plurality of stationary shrouds corresponding in number and respectively associated with said impellers; at least one shroud and one diaphragm being provided with confronting surfaces arranged in spaced relation one to another to define an axial clearance space and resilient means in said clearance space biasing said shroud relative to said diaphragm whereby engagement of parts in an axial direction is assured.
  • said axial biasing means include a plurality of O-rings compressed in the axial direction between at least some of said shrouds and some of said diaphragms.
  • shrouds are piston means for producing a net axial force, in the same direction as the force produced by said Oerings, from the pressurized -fluid during operation.
  • the second stage impeller having its inlet opening in they.
  • second stage diffuser and the second stage shroud being axially mounted, in order, between the third stage diaphragm and the second stage diaphragm.
  • a multi-stage pumping device for fluids comprising: a cast one piece casing having an inner cylindrical bore; a plurality of diaphragms corresponding in number to the number of stages being received within and engaging said bore in axial stacked relationship, each of said diaphragms being of a one piece casting; each of said diaphragms having integrally cast non-communicating passage means extending radially completely therethrough and corresponding to at least a first stage Outlet passage, a second stage inlet passage, and a second stage outlet passage; and said casing having integrally cast non-com'- municating passage means extending radially therethrough respectively in -uid alignment with each of said diaphragm passage means.
  • a centrifugal pumping device comprising: an open centrifugal impeller mounted for rotation about an axis; a separate stationary shroud and a separate stationary diffuser operatively mounted about said impeller to form a single pumping stage; a first axial abutment; a second axial abutment; at least one of said axial abutments being provided with a surface confronting a surface on at least one of said stationary parts in spaced relation thereto to define an axial clearance space; and an Oring sealingly and axially compressed between said one axial abutment and said one stationary part to provide means for axially biasing said diffuser and shroud axially toward said other axial abutment.
  • the device of claim 18, including piston means responsive to the pumped iluid to' produce a net axial force on said diffuser and shroud complementary to the axial force produced by said O-ring.
  • the device of claim 18, including a second open centrifugal impeller drivingly secured to said first mentioned centrifugal impeller; a second shroud and a second diffuser operatively associated with said second impeller and mounted in axial stacked relationship between one of said axial abutrnents and said first mentioned shroud and diffuser; and said O-ring clamping all of said diffusers and shrouds in the axial direction.
  • the device of claim 22, including an overhung rotor rigidly carrying said impellers and having bearing means only at its axial end opposite from said O-ring.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00044446A 1970-06-08 1970-06-08 Compressor barrel assembly Expired - Lifetime US3717418A (en)

Applications Claiming Priority (1)

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US4444670A 1970-06-08 1970-06-08

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US3717418A true US3717418A (en) 1973-02-20

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US00044446A Expired - Lifetime US3717418A (en) 1970-06-08 1970-06-08 Compressor barrel assembly

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US (1) US3717418A (de)
CA (1) CA955570A (de)
CH (1) CH523432A (de)
DE (1) DE2128233B2 (de)
FR (1) FR2096063A5 (de)
GB (1) GB1357183A (de)
NL (1) NL7107688A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3802795A (en) * 1972-04-19 1974-04-09 Worthington Cei Multi-stage centrifugal compressor
US3909154A (en) * 1974-09-05 1975-09-30 Carrier Corp Centrifugal compressor
US4277223A (en) * 1979-11-29 1981-07-07 Guy F. Atkinson Company Case construction for multi-stage pump
US4309144A (en) * 1978-08-04 1982-01-05 Bbc Brown, Boveri & Company, Ltd. Axial thrust bearing
US4533294A (en) * 1980-09-25 1985-08-06 Dresser Industries, Inc. High speed centrifugal pump and method for operating same at reduced noise levels
US20100296916A1 (en) * 2007-10-30 2010-11-25 Richard Julius Gozdawa Gas compressor
ITCO20120030A1 (it) * 2012-06-06 2013-12-07 Nuovo Pignone Srl Compressori ad alto rapporto di pressione con intercooler multiplo e relativi metodi

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5413108A (en) * 1977-06-29 1979-01-31 Sumitomo Rubber Ind Bead structure of steel tire
EP0704624B1 (de) * 1994-09-28 2003-01-08 Ishikawajima-Harima Heavy Industries Co., Ltd. Turboverdichter

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3802795A (en) * 1972-04-19 1974-04-09 Worthington Cei Multi-stage centrifugal compressor
US3909154A (en) * 1974-09-05 1975-09-30 Carrier Corp Centrifugal compressor
US4309144A (en) * 1978-08-04 1982-01-05 Bbc Brown, Boveri & Company, Ltd. Axial thrust bearing
US4277223A (en) * 1979-11-29 1981-07-07 Guy F. Atkinson Company Case construction for multi-stage pump
US4533294A (en) * 1980-09-25 1985-08-06 Dresser Industries, Inc. High speed centrifugal pump and method for operating same at reduced noise levels
US20100296916A1 (en) * 2007-10-30 2010-11-25 Richard Julius Gozdawa Gas compressor
US8573924B2 (en) * 2007-10-30 2013-11-05 Yorlan Holdings Limited Gas compressor
WO2013182492A1 (en) * 2012-06-06 2013-12-12 Nuovo Pignone Srl High pressure ratio compressors with multiple intercooling and related methods
ITCO20120030A1 (it) * 2012-06-06 2013-12-07 Nuovo Pignone Srl Compressori ad alto rapporto di pressione con intercooler multiplo e relativi metodi
KR20150027198A (ko) * 2012-06-06 2015-03-11 누보 피그노네 에스알엘 다수의 중간 냉각을 갖는 고압력비 압축기 및 관련 방법
CN104471214A (zh) * 2012-06-06 2015-03-25 诺沃皮尼奥内股份有限公司 具有多重中间冷却的高压力比压缩机和相关方法
US20150152884A1 (en) * 2012-06-06 2015-06-04 Nuovo Pignone Srl High pressure ratio compressors with multiple intercooling and related methods
JP2015518941A (ja) * 2012-06-06 2015-07-06 ヌオーヴォ ピニォーネ ソチエタ レスポンサビリタ リミタータＮｕｏｖｏ Ｐｉｇｎｏｎｅ Ｓ．Ｒ．Ｌ． 複数の中間冷却を有する高圧比圧縮機および関連する方法
AU2013270787B2 (en) * 2012-06-06 2016-12-08 Nuovo Pignone Srl High pressure ratio compressors with multiple intercooling and related methods
RU2616682C2 (ru) * 2012-06-06 2017-04-18 Нуово Пиньоне СРЛ Компрессор с высокой степенью сжатия и с более чем одним промежуточным охлаждением и связанный с ним способ
CN109944810A (zh) * 2012-06-06 2019-06-28 诺沃皮尼奥内技术股份有限公司 具有多重中间冷却的高压力比压缩机和相关方法

Also Published As

Publication number Publication date
FR2096063A5 (de) 1972-02-11
DE2128233B2 (de) 1976-11-04
NL7107688A (de) 1971-12-10
CA955570A (en) 1974-10-01
CH523432A (de) 1972-05-31
GB1357183A (en) 1974-06-19
DE2128233A1 (de) 1971-12-16

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Owner name: ELLIOTT TURBOMACHINERY CO., INC., A CORP OF DELAWA

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Effective date: 19851220

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Owner name: FIRST NATIONAL BANK OF CHICAGO, THE,ILLINOIS

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Effective date: 19871109

Owner name: FIRST NATIONAL BANK OF CHICAGO, THE, ONE FIRST NAT

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Effective date: 19891212