WO2023148602A1 - Turbomachine à réducteur/multiplicateur de vitesse intégré - Google Patents

Turbomachine à réducteur/multiplicateur de vitesse intégré Download PDF

Info

Publication number
WO2023148602A1
WO2023148602A1 PCT/IB2023/050793 IB2023050793W WO2023148602A1 WO 2023148602 A1 WO2023148602 A1 WO 2023148602A1 IB 2023050793 W IB2023050793 W IB 2023050793W WO 2023148602 A1 WO2023148602 A1 WO 2023148602A1
Authority
WO
WIPO (PCT)
Prior art keywords
turbomachine
speed reducer
multiplier
shaft
pressure
Prior art date
Application number
PCT/IB2023/050793
Other languages
English (en)
Inventor
Roberto Bini
Mario Gaia
Davide Colombo
Original Assignee
Turboden S.p.A.
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 Turboden S.p.A. filed Critical Turboden S.p.A.
Publication of WO2023148602A1 publication Critical patent/WO2023148602A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/04—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/20—Lubricating arrangements using lubrication pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/005—Steam engine plants not otherwise provided for using mixtures of liquid and steam or evaporation of a liquid by expansion

Definitions

  • the present invention relates to a turbomachine, for example a turbine or a compressor, provided with an integrated speed reducer/multiplier.
  • the turbine is suitable for thermodynamic steam cycles and is particularly suitable for an organic Rankine cycle (hereinafter also ORC cycle).
  • the compressor may belong to a heat pump system.
  • the speed reducer/multiplier is used to reduce the turbine output speed or to increase the compressor input speed so that the solution is suitable for coupling with a generator or with an industrial electric motor, preferably with 4 poles.
  • thermodynamic cycle is defined as a finite succession of thermodynamic transformations (for example isotherms, isochores, isobars or adiabatic) at the end of which the system returns to its initial state.
  • This cycle can be direct, for example a direct Rankine cycle, in which a thermal source is used for the production of mechanical/electrical energy and heat at a lower temperature than that of the thermal source.
  • the thermodynamic cycle can also be of the inverse type, for example a heat pump cycle, in which a mechanical/electrical energy source is used together with a thermal source to produce heat at a higher temperature than that of the thermal source.
  • an ideal Rankine cycle in its simplest version is a thermodynamic cycle composed of two adiabatic transformations and two isobaric transformations, characterized by the fact that the working fluid undergoes changes of state, from liquid to gaseous and vice versa.
  • a direct cycle its purpose is to transform heat into work.
  • This cycle is generally adopted above all in thermoelectric plants for the production of electricity and uses water as the driving fluid, both in liquid form and in the form of steam, with the so-called steam turbine.
  • ORC organic Rankine cycles
  • the plant for an ORC cycle includes one or more pumps to feed the organic working fluid, one or more heat exchangers to carry out the preheating, vaporization and possible superheating or heating phases in supercritical conditions of the same working fluid, a vapor turbine for the expansion of the fluid, mechanically connected to an electric generator, a condenser which returns the organic working fluid to the liquid state and a possible regenerator to recover the heat downstream of the turbine and upstream of the condenser.
  • a speed reducer is normally placed between the turbine and the electric generator in order to reduce the speed of the turbine shaft to values suitable for operating the electric generator.
  • a heat pump cycle envisages a compressor which, by absorbing energy from an electric motor, raises the pressure of the working fluid; a condenser in which the working fluid condenses and transfers heat to the user, a throttling valve (or in any case an expander) in which the working fluid in the liquid phase expands to a lower pressure and an evaporator in which the working fluid vaporizes by absorbing heat from the low-temperature heat source.
  • a speed multiplier is normally placed between the electric generator and the compressor in order to increase the speed of the electric motor to values suitable for operating the compressor.
  • the critical component in the turbomachine-reducer/multiplier coupling is the rotary seal on the turbomachine shaft which must prevent the working fluid from escaping from inside the turbomachine itself. Furthermore, high rotation speeds of the turbomachine and high process temperatures make the proper functioning of this seal particularly critical.
  • the working fluid itself i.e., its vapor
  • the operation of the seal itself may not be acceptable, as it is designed to work with a very clean dry gas compared to a vapor which can leave deposits, such as carbon deposits, in presence of high temperatures.
  • the use of the working fluid vapor does not create problems for the system in the case of leakage towards the side of the turbomachine shaft where the organic working fluid is present, on the other hand the leakage towards the other side of the double seal then needs to manage this leakage of process fluid, with a solution similar to what was previously described;
  • a 'sealed' solution can also be used, i.e., in which there is in fact no outward rotating seal, since the support bearings of the shaft and the generator/electric motor, connected directly to the turbomachine, are immersed in the working fluid itself and the shaft itself rotates at a high rotation speed which does not allow the use of traditional industrial electric generators (for example, 2 or 4 poles) but high frequency generators, with special and expensive solutions to be adopted for the bearings themselves and for the coupling between the electrical network and the high frequency generator. In fact, this solution is not feasible especially for large turbomachine.
  • the proposed solution (which will preferably be applicable to turbomachine with a power higher than 100 kW) allows to overcome the limits and defects of what is currently available, providing for the use of a rotating seal towards the external environment of the traditional type, such as a so- called mechanical, installed on the slow shaft of a turbomachine. Therefore, this seal will operate under absolutely quiet speed and temperature conditions. Furthermore, the seal is easily replaceable because it is in fact external to the turbomachine itself.
  • a turbomachine is described provided with an integrated speed reducer/ multiplier and a seal downstream of the speed reducer/ multiplier, having the characteristics stated in the independent product claim annexed to the present description.
  • FIG. 1 illustrates a non-limiting embodiment of a turbine equipped with a speed reducer.
  • FIG. 1 illustrates a non-limiting embodiment of a turbine equipped with a speed reducer.
  • the reducer will be replaced by a speed multiplier which in fact performs the same function as the reducer but with an inverted power flow mechanics that pass through it.
  • the integrated turbine/reducer system 20 comprises an expansion turbine 1 connected to a speed reducer 2.
  • the speed reducer 2 reduces the rotation speed of the shaft 3 of the turbine to a value suitable for driving a preferably synchronous 4-pole electric generator 18 (of known type) connected to the electric net.
  • a 4-pole generator will rotate at 1500rpm (1800rpm on a 60Hz net) whereas the turbine typically requires a much higher rotational speed, such as 6000rpm (a compressor even higher speeds).
  • the turbine 1 operates in an organic Rankine cycle (ORC) plant.
  • ORC organic Rankine cycle
  • the turbine 1 is an axial turbine and even more preferably it is a multistage axial turbine with the rotor discs mounted cantilevered on the shaft 3 of the turbine 1.
  • the speed reducer 2 is preferably an epicyclic speed reducer in order to keep the input and output shafts of the gear reducer also co-axial.
  • the shaft 3 of the turbine 1 is physically separated from an input shaft 2' of the reducer 2 and is supported by oil-lubricated rolling bearings 4 installed inside the casing 5 of the turbine shaft.
  • the rolling bearings 4 of the shaft 3 of the turbine 1 provide both radial and axial support to the shaft itself.
  • a sealing device 6 is provided, such as for example a labyrinth seal, or in any case a device which does not have a perfect seal, preferably non-contacting seals.
  • This type of seal does not provide a completely hermetic separation of the shaft 3 from the process zone but is suitable for operating at much higher speeds and temperatures than a rotary contact seal. Since inside the turbine there is a slightly higher pressure than that present in the casing 5 (or rather the pressure in the casing 5 is maintained at a slightly lower level than that of the turbine), the environment inside of the casing 5 of the shaft 3 receives a small flow rate of working fluid which mixes with the lubricating oil.
  • the speed reducer 2 is designed to be pressure-tight and is connected to the casing 5 of the shaft 3 via a sealed connection pipe 7', preferably a bellows pipe, so that the pressure inside the speed reducer is equal to the pressure acting on the shaft 3 and there is no communication with the external environment.
  • the speed reducer 2 is also connected to the discharge side of the turbine (or to the suction side in the case of the compressor) via a pressure balancing line 8 in which a compressor 14 is installed, so that it is ensured that the pressure in the inside of the speed reducer 2 is slightly lower than that of the turbine discharge to achieve what was previously said, in order to avoid the entry of lubricating oil into the process area of the turbine 1. In this way lubricating oil infiltrations are avoided inside the process area, while, as already mentioned, there will be small infiltrations of organic working fluid inside the casing 5 of the shaft 3 and the speed reducer 2.
  • the balancing line 8 As an alternative to connecting the balancing line 8 to the discharge side of the turbine, it may be convenient to connect this line to a suitable point in the system (ORC cycle or heat pump) where the pressure is in any case lower than the turbine discharge pressure, to avoid the need for the compressor 14. It is also possible to maintain the pressure value inside the turbine 1 slightly higher than in the reducer 2 through suitable design measures in the turbine, for example with a suitable arrangement of the labyrinths inside the turbine 1 itself.
  • the output shaft 2" of the speed reducer 2 is provided with a double mechanical seal 9, which thus guarantees complete sealing against the external environment.
  • This double mechanical seal 9 works with rotation speeds and with temperatures which are much lower than those inside the turbomachine, thus resulting in a reliable and frequently used component in the industry, for example of rotary pumps, and will preferably be of the type with barrier fluid (typically the same lubricating oil as for bearings and gearbox). Furthermore, this double mechanical seal 9 is in such a position that it is not necessary to disassemble the shaft 3 of the turbine 1 in cases where the seal itself has to be repaired or replaced.
  • the lubricating oil by means of a suitable pump 16, is pumped into a cooler 13 and then into the lubrication circuit, having the function of both lubrication and cooling for the components of the speed reducer (gears, rolling bearings) and for the shaft 3 (and related rolling bearings 4) of the turbine 1.
  • the lubricating oil will be contaminated by the organic working fluid which emerges from the sealing device 6 of the turbine 1 on the basis of the mixing properties of the two fluids. Therefore, a separator 15 can advantageously be installed to separate the organic working fluid from the lubricating oil, thus allowing the lubricating properties of the oil to be kept under control.
  • the separator 15 can be heated to a controlled temperature by means of the coil 21 to improve the separation process.
  • the separated working fluid will be conveniently returned to the ORC (or heat pump) cycle circuit, for example by connecting it to balancing line 8 as in Fig. 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Système intégré (20) comprenant une turbomachine (1) reliée à un réducteur ou multiplicateur de vitesse (2) dans lequel : - un arbre (3) de la turbomachine (1) est séparé d'un arbre d'entrée (2') du réducteur ou multiplicateur de vitesse (2) et relié à celui-ci au moyen d'un dispositif d'accouplement (7), - entre une zone de traitement d'un fluide de travail de la turbomachine (1) et un carter (5) de l'arbre (3) de la turbomachine (1) est affecté un dispositif d'étanchéité à labyrinthe (6) qui sépare le fluide organique du travail de l'huile de lubrification du carter (5) et du réducteur ou multiplicateur (2), où la pression de fluide organique de travail est supérieure à la pression de l'huile de lubrification du carter (5) de l'arbre (3) de la turbomachine (1) et du réducteur ou multiplicateur de vitesse (2), - un arbre de sortie (2") du réducteur ou multiplicateur de vitesse (2) est pourvu d'un joint mécanique (9) ; - un séparateur (15) est prévu pour séparer l'huile lubrifiante du fluide de travail.
PCT/IB2023/050793 2022-02-02 2023-01-30 Turbomachine à réducteur/multiplicateur de vitesse intégré WO2023148602A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT202200001793 2022-02-02
IT102022000001793 2022-02-02

Publications (1)

Publication Number Publication Date
WO2023148602A1 true WO2023148602A1 (fr) 2023-08-10

Family

ID=81393001

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2023/050793 WO2023148602A1 (fr) 2022-02-02 2023-01-30 Turbomachine à réducteur/multiplicateur de vitesse intégré

Country Status (1)

Country Link
WO (1) WO2023148602A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2161417A1 (fr) * 2008-08-07 2010-03-10 General Electric Company Procédé de lubrification d'extenseur de vis et système de contrôle de la lubrification
WO2015091434A1 (fr) * 2013-12-18 2015-06-25 Nuovo Pignone Srl Appareil d'isolement d'un environnement interne d'une turbomachine
CN107355271A (zh) * 2017-07-25 2017-11-17 航天推进技术研究院 一种有机朗肯循环千瓦级发电装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2161417A1 (fr) * 2008-08-07 2010-03-10 General Electric Company Procédé de lubrification d'extenseur de vis et système de contrôle de la lubrification
WO2015091434A1 (fr) * 2013-12-18 2015-06-25 Nuovo Pignone Srl Appareil d'isolement d'un environnement interne d'une turbomachine
CN107355271A (zh) * 2017-07-25 2017-11-17 航天推进技术研究院 一种有机朗肯循环千瓦级发电装置

Similar Documents

Publication Publication Date Title
US11293309B2 (en) Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
EP3947922B1 (fr) Système de production d'énergie et procédé de production d'énergie par exploitation d'un tel système de production d'énergie
US8739538B2 (en) Generating energy from fluid expansion
Brasz et al. Power production from a moderate-temperature geothermal resource
KR102562570B1 (ko) 건조 가스 시일 냉각 장치 및 그 방법
CN111594283B (zh) 一种两级透平气悬浮orc发电系统及控制方法
WO2011058832A1 (fr) Système à turbocompresseur générateur de puissance de récupération de chaleur perdue de moteur et système de moteur alternatif pourvu de ce dernier
US20110283702A1 (en) Generating energy from fluid expansion
RU2453731C2 (ru) Винтовая машина, система преобразования энергии и способ преобразования энергии
KR101501852B1 (ko) 회전기 구동 시스템
US12044150B2 (en) Plant based upon combined Joule-Brayton and Rankine cycles working with directly coupled reciprocating machines
WO2023148602A1 (fr) Turbomachine à réducteur/multiplicateur de vitesse intégré
KR102649611B1 (ko) 오버행된 터보기계를 갖는 일체형 밀폐 밀봉된 터보팽창기-발생기
CN113661307B (zh) 发电系统和通过操作这种发电系统来发电的方法
JPH02252901A (ja) スクリュー膨張機の給油装置
WO2013042141A1 (fr) Détendeur à palette
CN103975134A (zh) 压缩和能量回收单元
JP7177835B2 (ja) 統合冷却を含む、特にランキンサイクルタイプの閉回路用の電気式ターボポンプアセンブリ
BRASZ Renewable Power Production of Moderate Temperature Geothermal Heat Using Air Conditioning Hardware

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23705655

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2023705655

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2023705655

Country of ref document: EP

Effective date: 20240902