US20140377083A1 - Compressor system for natural gas, method of compressing natural gas and plant using them - Google Patents

Compressor system for natural gas, method of compressing natural gas and plant using them Download PDF

Info

Publication number
US20140377083A1
US20140377083A1 US14/374,590 US201314374590A US2014377083A1 US 20140377083 A1 US20140377083 A1 US 20140377083A1 US 201314374590 A US201314374590 A US 201314374590A US 2014377083 A1 US2014377083 A1 US 2014377083A1
Authority
US
United States
Prior art keywords
rotary member
epicyclic gearbox
compressor
centrifugal compressor
driver machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/374,590
Other languages
English (en)
Inventor
Remo Tacconelli
Shankar Chandrasekaran
Murali Krishna Reddy
Tivon sing lezin Ah Karm
Sandilya Vadapalli
Denis Guillaume Guenard
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.)
Nuovo Pignone SRL
Original Assignee
Nuovo Pignone SRL
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nuovo Pignone SRL filed Critical Nuovo Pignone SRL
Assigned to NUOVO PIGNONE SRL reassignment NUOVO PIGNONE SRL ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TACCONELLI, REMO, VADAPALLI, Sandilya, GUENARD, Denis Guillaume, REDDY, Murali Krishna, CHANDRASEKARAN, SHANKAR, AH KARM, Tivon Sing Lezin
Publication of US20140377083A1 publication Critical patent/US20140377083A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0261—Surge control by varying driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/028—Units comprising pumps and their driving means the driving means being a planetary gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • Embodiments of the subject matter disclosed herein generally relate to a compressor system for natural gas, a method of compressing natural gas and a plant using such a compressor and/or method.
  • process gas This happens, for example, in downstream plants wherein the gas comes typically from a pipeline or from another plant (so called “process gas”).
  • FIG. 1 there is shown a general block diagram of this known solution: a traditional centrifugal compressor TCC is connected to the output of a traditional parallel-axes gearbox PAGB that is connected to the output of a traditional driver machine TDR; gearbox PAGB increases the rotation speed from input to output and this is schematically represented by the different number of arcs at its input and at its output.
  • FIG. 1 highlights that the axes of the input shaft and the output shaft of the gearbox are parallel and at a distance from each other.
  • FIG. 2 there is shown a general block diagram of this known solution: a traditional electric power generator TEPG is connected to the output of a traditional epicyclic gearbox TEGB that is connected to the output of a traditional turbine TTB; gearbox TEGB decreases the rotation speed from input to output and this is schematically represented by the different number of arcs at its input and at its output; FIG. 2 highlights that the axes of the input shaft and the output shaft of the gearbox are coincident.
  • a first aspect of the present invention is a compressor system for natural gas.
  • a compressor system for natural gas comprises: a driver machine comprising an output rotary member, an epicyclic gearbox comprising an input rotary member and an output rotary member, and having a gear ratio greater than one thus increasing the rotation speed from input to output, and a centrifugal compressor for compressing natural gas comprising an input rotary member; the output rotary member of said driver machine is coupled to the input rotary member of said epicyclic gearbox, and the output rotary member of said epicyclic gearbox is coupled to the input rotary member of said centrifugal compressor.
  • Said epicyclic gearbox may be multi-stage and more particularly two-stage.
  • Said epicyclic gearbox may comprise at least two (more particularly at least three) intermediate shafts transmitting rotation from said input rotary member to said output rotary member, and integrating or mounting one toothed member or two toothed members of different diameters.
  • the axes of said at least two intermediate shafts may be arranged to rotate around the axis of the input rotary member of the epicyclic gearbox.
  • Said driver machine may be an electric motor.
  • Said driver machine may be a gas turbine.
  • Said driver machine may be a steam turbine.
  • Said gearbox may be mounted on the driver machine.
  • Said gearbox may be mounted on foot.
  • Said gearbox may be mounted both on the driver machine and on foot.
  • the compressor system may comprise further a single baseplate; in this case, said driver machine and said centrifugal compressor are mounted on said single baseplate.
  • Said centrifugal compressor may have a rated power in the range from 2 MW to 40 MW.
  • Said driver machine may comprise two output rotary members; in this case, the compressor system comprises an epicyclic gearbox and a centrifugal compressor for each of said two output rotary members.
  • the compressor system may comprise at least one centrifugal compressor in addition to the one already considered; different arrangements are possible.
  • the compressor system may comprise further a variable-speed drive system coupled to said driver machine and arranged to vary the rotation speed of said centrifugal compressor.
  • Said centrifugal compressor may be operated at a maximum rotation speed in the range from 14000 rpm to 28000 rpm.
  • Said centrifugal compressor may be operated at a pressure ratio in the range from 1.5 to 40.
  • Said centrifugal compressor may be operated so to provide an maximum output gas pressure in the range from 30 bar to 600 bar.
  • Said centrifugal compressor may be operated so to treat a maximum gas flow in the range from 1500 m3/hr to 100000 m3/hr.
  • said output rotary member may be used for driving two or more centrifugal compressors at different rotation speeds.
  • Said driver machine may be operated at variable rotation speed.
  • a third aspect of the present invention is a plant, i.e. an upstream or a downstream plant.
  • a plant comprises a compressor system for gas and this compressor system comprises: a driver machine comprising an output rotary member, an epicyclic gearbox comprising an input rotary member and an output rotary member, and having a gear ratio greater than one thus increasing the rotation speed from input to output, and a centrifugal compressor for compressing gas comprising an input rotary member; wherein the output rotary member of said driver machine is coupled to the input rotary member of said epicyclic gearbox, and wherein the output rotary member of said epicyclic gearbox is coupled to the input rotary member of said centrifugal compressor.
  • the plant may be of the upstream type, in particular of the offshore upstream type.
  • the plant may be of the downstream type.
  • FIG. 1 shows schematically a prior art solution for compressing natural gas using a parallel-axes gearbox
  • FIG. 2 shows schematically a prior art solution for generating electric power using an epicyclic gearbox
  • FIG. 4 shows schematically a first embodiment of the present invention of a compressor system
  • FIG. 5 shows schematically a second embodiment of the present invention of a compressor system
  • FIG. 6 shows schematically a third embodiment of the present invention of a compressor system
  • FIG. 7 shows a schematic side view of a fourth embodiment of the present invention of a compressor system
  • FIG. 8 shows a schematic side view of a fifth embodiment of the present invention of a compressor system
  • FIG. 9 shows a schematic side view of a sixth embodiment of the present invention of a compressor system
  • FIG. 10 shows schematically a seventh embodiment of the present invention of a compressor system
  • FIG. 11 shows schematically a eighth embodiment of the present invention of a compressor system
  • FIG. 12 shows schematically a ninth embodiment of the present invention of a compressor system
  • FIG. 13 shows a graph corresponding to a reasonable limit for using parallel-axes gearboxes in combination with gas turbines in accordance with an embodiment of the present invention in accordance with the present invention
  • FIG. 14 shows two graphs corresponding to a reasonable limit for using respectively parallel-axes gearboxes and epicyclic gearboxes in combination with electric motors in accordance with an embodiment of the present invention
  • FIG. 15 shows a conceptual flowchart of a method for compressing natural gas in accordance with an embodiment of the present invention
  • FIG. 16 shows schematically an offshore platform in accordance with an embodiment of the present invention.
  • FIG. 3 shows schematically the principle of the compressor systems disclosed herein.
  • This compressor system comprises: a driver machine DR, an epicyclic gearbox EGB, and a centrifugal compressor CC for compressing natural gas.
  • Driver machine DR comprises a output rotary member DO; the epicyclic gearbox EGB comprises an input rotary member GI and an output rotary member GO; the centrifugal compressor CC comprises an input rotary member CI.
  • the output rotary member DO of the driver machine DR is coupled to the input rotary member GI of the epicyclic gearbox EGB; the output rotary member GO of the epicyclic gearbox EGB is coupled to the input rotary member CI of the centrifugal compressor CC.
  • the gear ratio of the epicyclic gearbox EGB is greater than one (typically much greater than one) thus increasing the rotation speed from input to output; this is schematically represented by the different number of arcs at its input, i.e. the member GI, and at its output, i.e. the member GO; specifically, next to the input rotary member GI there is one arc, meaning low rotation speed, and next to the output rotary member GO there are three arcs, meaning high rotation speed.
  • centrifugal compressors to be considered for the present patent application in the field of Oil & Gas such as those labeled CC, CC 1 , CC 2 , CC 3 , CCA, CCB, CCC in the figures, have typically a rated power in the range from 2 MW to 40 MW.
  • the centrifugal compressor rotates at high rotation speed; this is achieved by an epicyclic gearbox with a (relatively) high gear ratio.
  • the gear ratio of the epicyclic gearbox is in the range from 5 to 20.
  • multi-stage epicyclic gearing may be used. Two-stage epicyclic gearing may be a good compromise in terms of radial size, axial size, weight and gear ratio of the gearbox.
  • the epicyclic gearbox comprises at least two intermediate shafts transmitting rotation from the input rotary member to the output rotary member of the gearbox; each of these intermediate shafts may integrate or mount two toothed members of different diameters located at opposite sides of the intermediate shaft so that gear ratio is increased in a limited space; these intermediate shafts may be arranged to rotate around the axis of the input rotary member of the epicyclic gearbox; more particularly, three or five intermediate shafts, symmetrically located around the input rotary member, are used.
  • the solution of gearbox just described may be considered a specific type of two-stage epicyclic gearbox, the two stages being integrated in a single arrangement, and is called “compound gearing”.
  • an electric motor EM is used as a driver machine; using electric motor for compressing natural gas is typical of upstream applications particularly for offshore platforms.
  • the compressor system of FIG. 4 comprises the electric motor EM, an epicyclic gearbox EGB 1 and a centrifugal compressor CC 1 connected in train configuration.
  • a gas turbine GT is used as a driver machine.
  • the compressor system of FIG. 5 comprises the gas turbine GT, an epicyclic gearbox EGB 2 and a centrifugal compressor CC 2 connected in train configuration.
  • a steam turbine ST is used as a driver machine.
  • the compressor system of FIG. 6 comprises the steam turbine ST, an epicyclic gearbox EGB 3 and a centrifugal compressor CC 3 connected in train configuration.
  • the choice of the driver machine is influenced by many factors.
  • FIG. 7 and FIG. 8 and FIG. 9 emphasizes the construction of the compressor system even if in a very schematic way. These figures do not specify the kind of driver machine used, and they show simply a driver machine DR, an epicyclic gearbox EGB and a centrifugal compressor CC connected in train configuration.
  • FIG. 7 and FIG. 8 and FIG. 9 comprises a single baseplate BP and provide that the driver machine DR and the centrifugal compressor CC are mounted on the baseplate BP.
  • the epicyclic gearbox EGB is mounted only on the baseplate BP.
  • the epicyclic gearbox EGB is mounted only on the driver machine DR.
  • the epicyclic gearbox EGB is mounted partially on the baseplate BP and partially on the driver machine DR.
  • FIG. 7 and FIG. 8 and FIG. 9 mounting directly the epicyclic gearbox on the driver machine (typically on an electric motor) leads to a very compact arrangement, i.e. with a small footprint.
  • a double mounting may be a compromise between size of the footprint and mechanical complication of the design of the flanges of the driver machine and the gearbox.
  • the choice of the mounting of the epicyclic gearbox is influenced by many factors.
  • the driver machine DR comprises two output rotary members, in particular on opposite sides, and there is an epicyclic gearbox (EGBA and EGBB) and a centrifugal compressor (CCA and CCB) for each of the two output rotary members; this may be considered a double-train configuration.
  • EGBA and EGBB epicyclic gearbox
  • CCA and CCB centrifugal compressor
  • the compressor system comprises, in addition to the centrifugal compressor CC, another centrifugal compressor CCC; in this case, the compressor CC has an output rotary member (not shown in the figure).
  • Another gearbox GB is provided so that the two compressors CC and CCC may rotate at different rotation speeds.
  • the mechanical connection is a single-train configuration; the rotary members of the machines are not shown in the figure.
  • the output rotary member of the driver machine DR is connected to the input rotary member of the epicyclic gearbox EGB, the output rotary member of the epicyclic gearbox EGB is connected to the input rotary member of the compressor CC, the output rotary member of the compressor CC is connected to the input rotary member of the gearbox GB; the output rotary member of the gearbox GB is connected to the input rotary member of the compressor CCC. Comparing FIG. 11 with FIG. 1 , one can realize that other machines are mechanically connected downstream to compressor CC, and as part of the same train.
  • the fluid connection in the embodiment of FIG. 11 provides that the gas compressed by compressor CC is further compressed by compressor CCC; therefore, in general there is no need that the rotation speed of compressor CCC is much higher than the rotation speed of compressor CC; therefore, gearbox GB does not need to be an epicyclic gearbox (having a high gear ratio), although it might be.
  • the compressor system comprises, in addition to the centrifugal compressor CC, another centrifugal compressor CCC.
  • Another gearbox GB might also be provided.
  • the mechanical connection is a single-train configuration; the rotary members of the machines are not shown in the figure.
  • the output rotary member of the driver machine DR is connected to the input rotary member of the gearbox GB
  • the output rotary member of the gearbox GB is connected to the input rotary member of the compressor CCC
  • the output rotary member of the compressor CCC is connected to the input rotary member of the epicyclic gearbox EGB
  • the output rotary member of the epicyclic gearbox EGB is connected to the input rotary member of the compressor CC. Comparing FIG. 12 with FIG. 1 , one can realize that other machines are mechanically connected between the epicyclic gearbox EGB and the driver machine DR, and as part of the same train.
  • the fluid connection in the embodiment of FIG. 12 provides that the gas compressed by compressor CCC is further compressed by compressor CC.
  • the rotation speed of compressor CC is much higher than the rotation speed of compressor CCC due to the presence of the epicyclic gearbox EGB; therefore, gearbox GB may also be omitted or, if present (as in FIG. 12 ), gearbox GB does not need to be an epicyclic gearbox (having a high gear ratio), although it might be.
  • VSD variable-speed drive
  • a reliable four-poles AC induction electric motor operating at a frequency of 50 Hz may be combined with a reliable VSD system able to vary the frequency from 0 Hz up to 75 Hz; this result in a rotation speed from 0 rpm to 2250 rpm.
  • the Rated power is expressed in MWatts and the Gear ratio is expressed as a pure number.
  • the graph of FIG. 13 labeled PAGB, has been derived by the Inventors and corresponds to a reasonable limit for using parallel-axes gearboxes in combination with gas turbines; this graph assumes a rotation speed of the gas turbine acting as a driver machine of about 6000 rpm; above this limit, parallel-axes gearboxes can not be used and epicyclic gearboxes have to be contemplated.
  • a similar graph may be provided for steam turbines.
  • the graphs of FIG. 14 labeled PAGB and EGB, have been derived by the Inventors and correspond to a reasonable limit for using respectively parallel-axes gearboxes and epicyclic gearboxes in combination with electric motors; these graphs assume a rotation speed of the electric motor acting as a driver machine of about 1500 rpm (50 Hz operation); very similar graphs may be provided for a rotation speed of about 1800 rpm (60 Hz operation); the best area of application (according to the current technologies) of the combination of a four-poles AC induction electric motor and an epicyclic gearbox is comprised between these two graphs; it is to be considered that four-poles AC induction electric motors are certified to be used for very high power applications (for example 2-40 MW) even in environments with risks of explosions due to a specific gas mixture being compressed.
  • FIG. 14 refers to use of four-poles motors, the present invention does not exclude the use of two-poles motors.
  • the compression of gas in the above described embodiments is carried out, at least partially, by means of a centrifugal compressor driven by a driver machine through an epicyclic gearbox having a gear ratio greater then one.
  • the epicyclic gearbox is used for reaching a high rotation speed of the compressor; therefore, in an embodiment, the gear ratio of said epicyclic gearbox is in the range from 5 to 20, depending on the application; the epicyclic gearbox is designed accordingly.
  • a high rotation speed (achieved through epicyclic gearing) allows to use more compact and more efficient centrifugal compressors.
  • the centrifugal compressor is operated at a pressure ratio in the range from 1.5 to 40, depending on the application.
  • a pressure ratio in the range from 1.5 to 40, depending on the application.
  • the mixture of the gas influence the choice of the pressure ratio: for example, if a natural gas is rich of hydrogen, the lower part of the above mentioned range is preferable due to the risk of explosions.
  • the centrifugal compressor is operated so to provide an maximum output gas pressure in the range from 30 bar to 600 bar, depending on the application.
  • the centrifugal compressor is operated so to treat a maximum gas flow in the range from 1500 m3/hr to 100000 m3/hr, depending on the application.
  • the rotation speed is often constant during stable operation, i.e. regime.
  • the rotation speed is varied, for example during start-up or if different regimes are contemplated; for this purpose a VSD system is used.
  • FIG. 16 shows an offshore platform OP comprising a compressor system CS feeding compressed natural gas to a pipeline PL; this is an example of an “upstream” application.
  • the compressor system CS may be used at an offshore platform to produce compressed gas, to be injected into a well.
  • centrifugal compressor of the compressor system according to embodiments of the present invention are the following: reduction in the size, improvement in efficiency, reduction in weight, and reduction in footprint.
  • driver machine of the compressor system includes: possibility to use lower power driver machines, possibility to use lower speed driver machines, reduction in weight, and reduction in footprint.
  • baseplate of the compressor system according to embodiments of the present invention are the following: lower size, and lower weight.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US14/374,590 2012-01-27 2013-01-24 Compressor system for natural gas, method of compressing natural gas and plant using them Abandoned US20140377083A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
IT000002A ITCO20120002A1 (it) 2012-01-27 2012-01-27 Sistema compressore per gas naturale, metodo per comprimere gas naturale ed impianto che li utilizza
ITCO2012A000002 2012-01-27
PCT/EP2013/051384 WO2013110733A1 (en) 2012-01-27 2013-01-24 Compressor system for natural gas, method of compressing natural gas and plant using them

Publications (1)

Publication Number Publication Date
US20140377083A1 true US20140377083A1 (en) 2014-12-25

Family

ID=45992730

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/374,590 Abandoned US20140377083A1 (en) 2012-01-27 2013-01-24 Compressor system for natural gas, method of compressing natural gas and plant using them

Country Status (14)

Country Link
US (1) US20140377083A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
EP (1) EP2807379B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
JP (1) JP6405241B2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
KR (1) KR102051047B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CN (1) CN104487710A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
AU (3) AU2013213569A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
BR (1) BR112014017629B8 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CA (1) CA2861960C (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
ES (1) ES2895980T3 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
IT (1) ITCO20120002A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
MX (1) MX2014008601A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
PL (1) PL2807379T3 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
RU (1) RU2631578C9 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
WO (1) WO2013110733A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109185182A (zh) * 2018-09-11 2019-01-11 重庆冲能动力机械有限公司 一种能快速响应变速的离心叶轮机械

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109751513B (zh) * 2018-12-03 2022-05-10 国家管网集团重庆天然气管道有限责任公司 一种天然气长输管道离心压缩机组智能保护系统
CN110080831A (zh) * 2019-05-31 2019-08-02 西安热工研究院有限公司 超临界二氧化碳热力循环发电系统压缩机的驱动调速布局结构及方法

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2194054A (en) * 1939-03-30 1940-03-19 Laval Steam Turbine Co Pumping system
US3214990A (en) * 1962-12-27 1965-11-02 Worthington Corp Geared turbine
US3589836A (en) * 1968-11-04 1971-06-29 Trw Inc Unitized pump system
US3736074A (en) * 1972-04-20 1973-05-29 Worthington Cei Inlet, filter and noise suppressor enclosure for compressing apparatus
US3802795A (en) * 1972-04-19 1974-04-09 Worthington Cei Multi-stage centrifugal compressor
US3809493A (en) * 1970-06-08 1974-05-07 Carrier Corp Interchangeable compressor drive
US4047848A (en) * 1974-01-31 1977-09-13 Compair Industrial Limited Centrifugal compressors
US4105372A (en) * 1975-01-31 1978-08-08 Hitachi, Ltd. Fluid rotary machine
US20070060442A1 (en) * 2005-09-14 2007-03-15 Ransbarger Weldon L Rotation coupling employing torque converter and synchronization motor
US20070134111A1 (en) * 2005-12-14 2007-06-14 Eybergen William N Fuel cell compressor system
DE102010020145A1 (de) * 2010-05-11 2011-11-17 Siemens Aktiengesellschaft Mehrstufiger Getriebeverdichter
WO2011146231A1 (en) * 2010-05-21 2011-11-24 Exxonmobil Upstream Research Company Parallel dynamic compressor apparatus and methods related thereto

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1000877A (en) * 1962-06-30 1965-08-11 Ckd Praha Improvements in or relating to rotary blowers or compressors
JPS5119305U (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) * 1974-07-31 1976-02-12
SU740976A1 (ru) * 1977-02-18 1980-06-15 Производственное Объединение "Невский Завод" Им. В.И.Ленина Противопомпажна система турбокомпрессора
JPS5975597U (ja) * 1982-10-28 1984-05-22 株式会社荏原製作所 タ−ボ圧縮機
JPS61218793A (ja) * 1985-03-25 1986-09-29 Ebara Corp 遠心式圧縮機
DE4234739C1 (de) * 1992-10-15 1993-11-25 Gutehoffnungshuette Man Getriebe-Mehrwellenturbokompressor mit Rückführstufen
JP2000104698A (ja) * 1998-09-28 2000-04-11 Kobe Steel Ltd 圧縮装置
CN2924090Y (zh) * 2006-03-20 2007-07-18 陕西鼓风机（集团）有限公司 煤气透平机与电动机同轴驱动的高炉鼓风机组
JP4906925B2 (ja) * 2006-12-19 2012-03-28 ルノー・トラックス 自動車車両用パワーユニットおよび該パワーユニットを備えた車両
US8047809B2 (en) * 2007-04-30 2011-11-01 General Electric Company Modular air compression apparatus with separate platform arrangement
EP2083172A1 (en) * 2008-01-22 2009-07-29 Siemens Aktiengesellschaft Multi-body compressor train
CN201235747Y (zh) * 2008-06-20 2009-05-13 浙江大学 一种汽车空调混合驱动装置
EP2414748B1 (en) * 2009-03-30 2019-11-27 TMEIC Corporation Compressor surge control system and method
RU95762U1 (ru) * 2010-03-17 2010-07-10 Леонид Григорьевич Кузнецов Установка для подготовки и подачи буферного газа

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2194054A (en) * 1939-03-30 1940-03-19 Laval Steam Turbine Co Pumping system
US3214990A (en) * 1962-12-27 1965-11-02 Worthington Corp Geared turbine
US3589836A (en) * 1968-11-04 1971-06-29 Trw Inc Unitized pump system
US3809493A (en) * 1970-06-08 1974-05-07 Carrier Corp Interchangeable compressor drive
US3802795A (en) * 1972-04-19 1974-04-09 Worthington Cei Multi-stage centrifugal compressor
US3736074A (en) * 1972-04-20 1973-05-29 Worthington Cei Inlet, filter and noise suppressor enclosure for compressing apparatus
US4047848A (en) * 1974-01-31 1977-09-13 Compair Industrial Limited Centrifugal compressors
US4105372A (en) * 1975-01-31 1978-08-08 Hitachi, Ltd. Fluid rotary machine
US20070060442A1 (en) * 2005-09-14 2007-03-15 Ransbarger Weldon L Rotation coupling employing torque converter and synchronization motor
US20070134111A1 (en) * 2005-12-14 2007-06-14 Eybergen William N Fuel cell compressor system
DE102010020145A1 (de) * 2010-05-11 2011-11-17 Siemens Aktiengesellschaft Mehrstufiger Getriebeverdichter
WO2011146231A1 (en) * 2010-05-21 2011-11-24 Exxonmobil Upstream Research Company Parallel dynamic compressor apparatus and methods related thereto

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109185182A (zh) * 2018-09-11 2019-01-11 重庆冲能动力机械有限公司 一种能快速响应变速的离心叶轮机械

Also Published As

Publication number Publication date
CA2861960C (en) 2021-01-19
BR112014017629A8 (pt) 2017-07-11
AU2019203084A1 (en) 2019-05-23
KR102051047B1 (ko) 2019-12-02
RU2631578C9 (ru) 2017-11-15
PL2807379T3 (pl) 2022-01-31
ES2895980T3 (es) 2022-02-23
RU2014129396A (ru) 2016-03-20
AU2013213569A1 (en) 2014-08-14
BR112014017629B8 (pt) 2022-02-22
BR112014017629B1 (pt) 2021-12-14
JP2015505010A (ja) 2015-02-16
MX2014008601A (es) 2014-08-27
EP2807379A1 (en) 2014-12-03
AU2017201857A1 (en) 2017-04-06
AU2019203084B2 (en) 2020-06-25
RU2631578C2 (ru) 2017-09-25
EP2807379B1 (en) 2021-09-15
JP6405241B2 (ja) 2018-10-17
KR20140126716A (ko) 2014-10-31
CA2861960A1 (en) 2013-08-01
BR112014017629A2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 2017-06-20
ITCO20120002A1 (it) 2013-07-28
CN104487710A (zh) 2015-04-01
WO2013110733A1 (en) 2013-08-01

Similar Documents

Publication Publication Date Title
AU2019203084B2 (en) Compressor system for natural gas, method of compressing natural gas and plant using them
US8814502B2 (en) Dual input drive AGB for gas turbine engines
CN102893032B (zh) 多级齿轮式压缩机
RU2014103719A (ru) Газотурбинный двигатель (варианты) и способ повышения производительности газотурбинного двигателя
JP2016145636A (ja) 伝動ターボ機械
US20150152783A1 (en) Combination of two gas turbines to drive a load
RU2734984C2 (ru) Линия по производству азотной кислоты
CN105276145B (zh) 一种燃气发电机齿轮箱
EP3464905B1 (en) Compression train including two centrifugal compressors and lng plant including two centrifugal compressors
JP2019502046A (ja) 軸流圧縮機および遠心圧縮機を含むｌｎｇプラント
JP2008208959A (ja) 増速機およびそれを用いた風力発電装置
JP5535713B2 (ja) ガス化複合発電システム
CN208885884U (zh) 一种齿轮架传动行星轮减速机
Fuenfer Where Compact & Simple Solutions Count-Variable Speed Planetary Gears
CN108019465A (zh) 一种多级齿轮减速机

Legal Events

Date Code Title Description
AS Assignment

Owner name: NUOVO PIGNONE SRL, ITALY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TACCONELLI, REMO;CHANDRASEKARAN, SHANKAR;REDDY, MURALI KRISHNA;AND OTHERS;SIGNING DATES FROM 20140702 TO 20140723;REEL/FRAME:033404/0360

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: ADVISORY ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION