EP3299630A1 - Système de compresseur - Google Patents

Système de compresseur Download PDF

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Publication number
EP3299630A1
EP3299630A1 EP16190726.6A EP16190726A EP3299630A1 EP 3299630 A1 EP3299630 A1 EP 3299630A1 EP 16190726 A EP16190726 A EP 16190726A EP 3299630 A1 EP3299630 A1 EP 3299630A1
Authority
EP
European Patent Office
Prior art keywords
compressor
transmission
drive
gvt
cmp
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.)
Withdrawn
Application number
EP16190726.6A
Other languages
German (de)
English (en)
Inventor
Joachim NISSLER
Hans Schulz
Daniel Seiler
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Priority to EP16190726.6A priority Critical patent/EP3299630A1/fr
Priority to PCT/EP2017/071740 priority patent/WO2018059863A1/fr
Publication of EP3299630A1 publication Critical patent/EP3299630A1/fr
Withdrawn legal-status Critical Current

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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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement

Definitions

  • the invention relates to an arrangement for compressing a process fluid with a drive and a multi-stage gear compressor, wherein the drive is mechanically drivingly connected by means of a first clutch with the gear compressor.
  • the known gear compressor are used for the compression of large volume flows, in particular for the air compression.
  • the space required for the radial fluid energy machines or the compressor stages-arranged on the transmission housing of the transmission compressor- also increases. This results in collision problems of the housing of the radial fluid energy machines, which are also referred to as spiral housing.
  • the distance of the arranged on the gearbox volute casing is limited due to internal gear design conditions. With reasonable constructive effort this distance can hardly be increased.
  • the usually used in the transmission Large wheel is chosen so large in diameter that the distance between the pinion shafts to drive the radial turbofan energy machines is sufficient.
  • the enlargement of the large wheel has limits, because the outer peripheral speed can not be increased without limit.
  • the speed of the radial fluid power machines or the drive speed can not be increased without limit. Accordingly, results for a given gear design in the gearbox of the gear compressor, an upper size barrier, which can not be broken with previous means.
  • the invention has the object to develop an arrangement of the type defined in such a way that even larger volume flows of process gas can be compressed.
  • a preferred embodiment of the transmission compressor of the arrangement according to the invention provides that the transmission comprises a large wheel, wherein the large gear and the drive shaft have a common first axis of rotation, wherein an external toothing of the large wheel drives directly or indirectly pinion shafts of the radial fluid energy machines. Furthermore, it is expedient according to the invention if the radial fluid power machines are compressor stages.
  • a preferred field of application for the arrangement according to the invention is the air separation.
  • the efficiency of the compression has a high priority in the air separation.
  • the mechanical losses in gearbox compressors are mainly ventilation losses in the gearboxes.
  • the gas volume trapped in the gears is swirled by the intermeshing gears and heats up significantly in this lossy flow. Accordingly, it is desirable to design the smallest possible transmission with a small pitch circle speed.
  • the gear size of the gear compressor can be reduced as a result of the outsourcing of the first compression stage, without causing collisions of the spiral housing. In this way, there are improvements in efficiency of the transmission compressor as a result of the invention.
  • the invention results in a further degree of freedom of design because the gear compressor can on the one hand be designed as a standard component and the separate individual compressor can be adapted to the prevailing ambient pressure of the installation site.
  • the adaptation of the upstream of the gear compressor arranged single compressor is less expensive.
  • the final pressure of the compressor is highly dependent on the ambient pressure, so that the simple possibility of adaptation by means of the arrangement according to the invention is desirable.
  • An advantageous development of the invention provides that the process fluid from the separate single compressor completely is forwarded to the first stage of the transmission compressor by means of the connecting line.
  • a complete redirection is to be understood as forwarding minus any losses (eg leaks).
  • the separate single compressor can be suitably designed as a large blower, as axial compressor or as a radial compressor.
  • the gear compressor has a drive shaft to which at one end of the shaft, the first clutch and at the other end of the shaft, the second clutch are arranged so that the drive shaft is formed as a drive through the gear compressor.
  • through drive means that a shaft of the gear compressor driven by the drive extends through the gearbox of the gear compressor, so that a direct or indirect coupling of the separate single compressor can take place by means of the second clutch.
  • An indirect coupling of the separate single compressor is conceivable, for example, by providing an intermediate gear.
  • the separate single compressor may be coupled directly or indirectly to a pinion shaft of the gear compressor.
  • An alternative to a drive through the gearbox of the gear compressor is the ability to provide the drive between the separate single compressor and the gear compressor, so that a motor shaft extends through the drive and is coupled to a shaft end by means of a first clutch of the gear compressor and on the other shaft end of the motor shaft is coupled to transmit power by means of a second clutch of the separate single compressor.
  • the separate individual compressor particularly preferably has a pressure ratio of between 2 and 3.
  • the entire arrangement has a pressure ratio between 4 and 600.
  • the transmission compressor may expediently have a pressure ratio between 2-200.
  • the gear compressor is designed with up to 8 stages.
  • the gear compressor may each have an intermediate cooling between the individual compression stages. It is particularly advantageous to provide intermediate cooling between the individual compressor and the transmission compressor.
  • An advantageous development provides that the individual compressor has only a single stage or a single impeller of a centrifugal compressor.
  • the individual compressor can be structurally given an adapted speed by means of a variation of the number of teeth of a first gear, which can be advantageously assigned to the individual compressor for the transformation of the drive speed to the compressor speed.
  • the individual compressor has adjustable bearing points, so that the speed adaptation does not require a complicated adaptation design.
  • FIGS. 1 . 2 and 3 each show an inventive arrangement A in a schematic plan view.
  • the entire arrangement is driven by means of a drive DR, which is preferably designed as a four-pole or six-pole electric motor.
  • the drive DR is mechanically drivingly connected to the transmission compressor GVT by means of a first clutch CP1.
  • a second clutch CP2 By means of a second clutch CP2, the drive DR is indirectly or directly mechanically connected to a separate single compressor CMP.
  • the separate single compressor CMP is arranged upstream of the transmission compressor GVT such that the process fluid PF is forwarded downstream to the first stage SG1 of the transmission compressor via a connection line CD1.
  • a first intermediate cooling IC1 may be provided in the connecting line CD1 for removing a first heat flow Q1 ( FIG. 1 ).
  • the first stage SG1 of the transmission compressor GVT is at the same time the second stage ST2 of the entire compression process.
  • the gear compressor GVT itself has four compression stages and, based on the overall process, these stages include the second compression stage ST2, the third compression stage ST3, the fourth compression stage ST4 and the fifth compression stage ST5.
  • an intermediate cooling can be provided between each compression stage of the transmission compressor GVT, in which FIG. 1
  • a second, third and fourth intermediate cooling IC2, IC3, IC4 provided for discharging a second, third and fourth heat flow Q2, Q3, Q4.
  • FIG. 1 the special embodiment of a drive through the drive DR is shown, in which a motor shaft MSH carries the first clutch CP1 with a first end and the second clutch CP2 with a second end. Accordingly, the separate single compressor CMP is arranged at the first end of the motor shaft MSH and the gear compressor GVT is connected to the second clutch CP2.
  • the motor shaft MSH extends through the drive DR in the sense of a through drive, wherein the drive DR between the transmission compressor GVT and the separate single compressor CMP is arranged.
  • the single compressor CMP has a first transmission GE1.
  • the transmission compressor has a second transmission GE2.
  • the first transmission 1 may also be formed integrated into the second transmission GE2.
  • the individual compressor can constructively by means of a variation of the number of teeth of the first transmission GE1, which is advantageously assigned to the individual compressor CMP for the transformation of the input speed to the compressor speed, an adapted speed can be awarded.
  • the gear compressor GVT in this case has a drive shaft DRS, at which at one end of the shaft, the first clutch CP1 and at the other end of the shaft, the second clutch CP2 are arranged. Accordingly drives the drive shaft DRS of the gear compressor GVT as a through drive the separate single compressor CMP.
  • FIG. 3 An advantageous development of this shows the FIG. 3 , in which the gear compressor GVT is also arranged as a through drive between the separate single compressor CMP and the drive DR.
  • the transmission of the gear compressor GVT is not only provided for the translation of the speed of the drive for the stages two to five, but it is in the gear compressor GVT also a translation of the rotational speed of the drive DR to a speed the separate single compressor CMP provided.
  • an intermediate gear between the drive DR and the separate single compressor CMP is installed as an integrated component in the gear box of the gear compressor GVT.
  • This intermediate gear can also be provided as a separate module between the gear compressor GVT and the separate single compressor CMP or as an integrated transmission component of the separate single compressor CMP, as in the FIG. 1 shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP16190726.6A 2016-09-27 2016-09-27 Système de compresseur Withdrawn EP3299630A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP16190726.6A EP3299630A1 (fr) 2016-09-27 2016-09-27 Système de compresseur
PCT/EP2017/071740 WO2018059863A1 (fr) 2016-09-27 2017-08-30 Système de compression

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16190726.6A EP3299630A1 (fr) 2016-09-27 2016-09-27 Système de compresseur

Publications (1)

Publication Number Publication Date
EP3299630A1 true EP3299630A1 (fr) 2018-03-28

Family

ID=57137821

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16190726.6A Withdrawn EP3299630A1 (fr) 2016-09-27 2016-09-27 Système de compresseur

Country Status (2)

Country Link
EP (1) EP3299630A1 (fr)
WO (1) WO2018059863A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026801A (zh) * 2018-07-20 2018-12-18 西安陕鼓动力股份有限公司 一种单轴离心压缩机组及低能耗操作方法
EP3705725A1 (fr) 2019-03-05 2020-09-09 Siemens Aktiengesellschaft Agencement pourvu de composants de l'engrenage

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0620363A1 (fr) * 1993-03-12 1994-10-19 Praxair Technology, Inc. Intégration d'unités de chambre de combustion-turbine et processeurs à pression
JP3457828B2 (ja) * 1997-03-05 2003-10-20 三菱重工業株式会社 コンプレッサ及びガスエキスパンダ装置
DE102009015862A1 (de) 2009-04-01 2010-10-07 Siemens Aktiengesellschaft Getriebeverdichterrotor für Kaltgasanwendungen
DE102010020145A1 (de) 2010-05-11 2011-11-17 Siemens Aktiengesellschaft Mehrstufiger Getriebeverdichter
DE102014225136A1 (de) 2014-12-08 2016-06-09 Siemens Aktiengesellschaft Getriebeverdichter, Anordnung mit einem Antrieb und einem Getriebeverdichter
DE102015200439A1 (de) 2015-01-14 2016-07-14 Siemens Aktiengesellschaft Anordnung, Getriebeverdichter
DE102015203287A1 (de) 2015-02-24 2016-08-25 Siemens Aktiengesellschaft Getriebeverdichtergehäuse, Getriebeverdichter

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0620363A1 (fr) * 1993-03-12 1994-10-19 Praxair Technology, Inc. Intégration d'unités de chambre de combustion-turbine et processeurs à pression
JP3457828B2 (ja) * 1997-03-05 2003-10-20 三菱重工業株式会社 コンプレッサ及びガスエキスパンダ装置
DE102009015862A1 (de) 2009-04-01 2010-10-07 Siemens Aktiengesellschaft Getriebeverdichterrotor für Kaltgasanwendungen
DE102010020145A1 (de) 2010-05-11 2011-11-17 Siemens Aktiengesellschaft Mehrstufiger Getriebeverdichter
DE102014225136A1 (de) 2014-12-08 2016-06-09 Siemens Aktiengesellschaft Getriebeverdichter, Anordnung mit einem Antrieb und einem Getriebeverdichter
DE102015200439A1 (de) 2015-01-14 2016-07-14 Siemens Aktiengesellschaft Anordnung, Getriebeverdichter
DE102015203287A1 (de) 2015-02-24 2016-08-25 Siemens Aktiengesellschaft Getriebeverdichtergehäuse, Getriebeverdichter

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026801A (zh) * 2018-07-20 2018-12-18 西安陕鼓动力股份有限公司 一种单轴离心压缩机组及低能耗操作方法
CN109026801B (zh) * 2018-07-20 2020-01-10 西安陕鼓动力股份有限公司 一种单轴离心压缩机组及低能耗操作方法
EP3705725A1 (fr) 2019-03-05 2020-09-09 Siemens Aktiengesellschaft Agencement pourvu de composants de l'engrenage

Also Published As

Publication number Publication date
WO2018059863A1 (fr) 2018-04-05

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