EP3375990B1 - Modellbasierte überwachung des betriebszustandes einer expansionsmaschine - Google Patents

Modellbasierte überwachung des betriebszustandes einer expansionsmaschine Download PDF

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Publication number
EP3375990B1
EP3375990B1 EP17161565.1A EP17161565A EP3375990B1 EP 3375990 B1 EP3375990 B1 EP 3375990B1 EP 17161565 A EP17161565 A EP 17161565A EP 3375990 B1 EP3375990 B1 EP 3375990B1
Authority
EP
European Patent Office
Prior art keywords
expansion machine
steam pressure
thermodynamic cycle
live steam
feed pump
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.)
Active
Application number
EP17161565.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3375990A1 (de
Inventor
Andreas Schuster
Roy Langer
Jens-Patrick Springer
Fabian Weigand
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.)
Orcan Energy AG
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Orcan Energy 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 Orcan Energy AG filed Critical Orcan Energy AG
Priority to EP17161565.1A priority Critical patent/EP3375990B1/de
Priority to PCT/EP2017/080029 priority patent/WO2018166642A1/de
Priority to RU2019129133A priority patent/RU2724806C1/ru
Priority to CN201780090816.XA priority patent/CN110730855B/zh
Priority to US16/495,088 priority patent/US11035258B2/en
Priority to BR112019018768-5A priority patent/BR112019018768B1/pt
Publication of EP3375990A1 publication Critical patent/EP3375990A1/de
Application granted granted Critical
Publication of EP3375990B1 publication Critical patent/EP3375990B1/de
Active legal-status Critical Current
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Classifications

    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits

Definitions

  • the invention relates to a method for operating a thermodynamic cycle device, in particular an organic rankine cycle device (ORC device) with an expansion machine, and a thermodynamic cycle device that can be operated with the method according to the invention.
  • a thermodynamic cycle device in particular an organic rankine cycle device (ORC device) with an expansion machine
  • ORC device organic rankine cycle device
  • thermodynamic cycle device for example an Organic Rankine Cycle device
  • a generator or a motor / generator unit in order to feed energy into a power grid
  • the expansion machine is subjected to rotational speeds due to the grid frequency.
  • another external device such as a device with an internal combustion engine, in order to support it.
  • the object of the invention is to avoid the disadvantages mentioned.
  • the invention describes the solution to the above problem by adding model-based control and / or monitoring to the operation (starting process, normal operation, shutdown process) of the thermodynamic cycle device with the expansion machine.
  • thermodynamic cycle device in particular an ORC device
  • the thermodynamic cycle device comprises an evaporator, an expansion machine, a condenser and a feed pump and the expansion machine is coupled to an external device in normal operation
  • the method comprises the steps of: measuring an exhaust pressure downstream of the expansion machine; and setting a volume flow of the feed pump according to a computer-implemented control model of the thermodynamic cycle device as a function of the measured evaporation pressure and a target speed of the expansion machine as input variables of the control model and with the volume flow of the feed pump as output variable of the control model.
  • the evaporation pressure downstream of the expansion machine can be measured between the expansion machine and the feed pump, in particular between the expansion machine and the condenser or between the condenser and the feed pump.
  • the pressure loss of the condenser can either be neglected or it is known and is taken into account in the regulation.
  • the volume flow of the working medium pumped by the feed pump can be regulated in various ways. Setting the speed of the feed pump is one way of adjusting the volume flow of the feed pump, other options would be a throttle (throttle valve) or a 3-way valve after the pump or an adjustment of the delivery characteristics of the feed pump by adjusting a stator or a piston stroke.
  • a throttle throttle valve
  • a 3-way valve after the pump or an adjustment of the delivery characteristics of the feed pump by adjusting a stator or a piston stroke.
  • the method according to the invention has the advantage that the measuring point required for the speed measurement according to the prior art can be avoided with the aid of the model-based control within the scope of the present invention.
  • thermodynamic cycle device can include the following steps: regulating the expansion machine into a state in which the target speed of the expansion machine is greater than or equal to a predetermined speed of the external device to be coupled to the expansion machine, wherein the external device to be coupled comprises in particular a generator, a generator / motor unit or a device operated with a separate motor; and then coupling the expansion machine to the external device. If the speeds are the same, there is a power-neutral coupling. If the speed of the expansion device during coupling is (somewhat) greater than a synchronous speed, then the effective performance of the expansion machine is positive and therefore does not damage the bearing.
  • Another further development is that the following further steps can be carried out: measuring the live steam pressure upstream of the expansion machine; Comparison of the measured live steam pressure with a current model live steam pressure according to the control model; and initiating a shutdown process and / or aborting the starting process if the measured live steam pressure is more than a predetermined amount or more than a predetermined fraction below the model live steam pressure, which depends on the measured exhaust steam pressure.
  • the live steam pressure upstream of the expansion machine can be measured between the feed pump and the expansion machine, in particular between the evaporator and the expansion machine or between the feed pump and the evaporator.
  • the live steam pressure could, for example, be measured at the outlet of the feed pump / inlet of the evaporator and corrected for the pressure loss of the evaporator and / or the pipelines up to the inlet into the expansion machine.
  • the following further steps can be carried out: measuring a heat source temperature of a heat source which supplies the thermodynamic cycle device via the evaporator; and performing the starting process only if the measured heat source temperature is greater than or equal to a current model heat source temperature according to the control model.
  • thermodynamic cycle device can include the following steps: decoupling the expansion machine from the external device if the live steam pressure and / or the heat source temperature is below a respective one predetermined threshold fall; and opening a bypass line to bypass the expansion machine.
  • control model according to the invention can include analytical and / or numerical and / or tabular relationships of the input and output variables.
  • thermodynamic cycle device according to claim 10.
  • thermodynamic cycle device (in particular an ORC device) according to the invention comprises an evaporator, an expansion machine, a condenser, and a feed pump, the expansion machine being coupled to an external device in normal operation; wherein the thermodynamic cycle device further comprises: an exhaust pressure measurement device for measuring an exhaust pressure downstream of the expansion machine; and a control device for setting a volume flow of the feed pump according to a control model of the thermodynamic cycle device, which is stored in a memory of the control device, as a function of the measured evaporation pressure and a setpoint speed of the expansion machine as input variables of the control model and with the volume flow of the feed pump as output variable of the control model. Measuring the evaporation pressure downstream of the Expansion machine can take place at the points mentioned above in connection with the method according to the invention.
  • thermodynamic cycle device can be further developed in such a way that the control device is designed to carry out the following steps during a starting process of the thermodynamic cycle device: regulating the expansion machine into a state in which the desired speed of the expansion machine is greater than or equal to a predetermined speed of that of the expansion machine to be coupled external device, the external device to be coupled comprising in particular a generator, a generator / motor unit or a device operated with a separate motor; and then coupling the expansion machine to the external device.
  • thermodynamic cycle device further comprises a live steam pressure measuring device for measuring a live steam pressure upstream of the expansion machine; wherein the control device is designed to compare the measured live steam pressure with a current model live steam pressure according to the control model, and to initiate a shutdown process and / or to abort a start-up process if the measured live steam pressure is increased by more than a predetermined amount or by more than a predetermined fraction is below the model live steam pressure.
  • the live steam pressure upstream of the expansion machine can be measured at the points already mentioned above in connection with the method according to the invention.
  • thermodynamic cycle device further comprises: a heat source temperature measuring device for measuring a heat source temperature of a heat source that supplies the thermodynamic cycle device with heat via the evaporator; wherein the control device is designed to carry out the starting process only when the measured heat source temperature is greater than or equal to a current model heat source temperature according to the control model.
  • thermodynamic cycle device further comprises a bypass line as a direct connection between the evaporator and the condenser to bypass the expansion machine; wherein the control device is designed to carry out the following steps during a shutdown process of the thermodynamic cycle device: decoupling the expansion machine from the external device if the live steam pressure and / or the heat source temperature fall below a respective predetermined threshold value; and opening the bypass line by means of a valve in the bypass line.
  • thermodynamic cycle device further comprises: a coupling for coupling the expansion device to the external device; and / or a transmission for setting a speed ratio from the expansion device to the external device.
  • FIG. 1 shows an embodiment 100 of the thermodynamic cycle device according to the invention.
  • the ORC cycle comprises a feed pump 40 for increasing the pressure, an evaporator 10 for preheating, evaporation and overheating of a working medium, an expansion machine 20 for power-generating expansion of the working medium, which with or without clutch 27 is connected to a generator 25 (or a motor / generator Unit) or an external process 26 is connected, a possible bypass 50 for bypassing the expansion machine 20 and a condenser 30 for deheating, condensation and subcooling of the working medium.
  • the cycle process device 100 comprises an evaporation pressure measuring device 61 for measuring an evaporation pressure downstream of the expansion machine 20.
  • the evaporation pressure measuring device 61 is provided here between the expansion machine 20 and the condenser 30.
  • a control device 80 for setting a volume flow of the working medium pumped by the feed pump 40 (for example by setting a rotational speed of the feed pump 40) according to a control model of the thermodynamic cycle device 100 stored in a memory 81 of the control device 80 only as a function of the measured exhaust steam pressure (if necessary corrected by the mentioned correction value) and a target speed of the expansion machine 20 as input variables of the control model and with the Volume flow of the feed pump 40 (eg in the form of the speed of the feed pump 40) as the output variable of the control model.
  • a coupling switch 28 can also be provided, which couples the generator 25 (or the motor / generator unit) to or disconnects from a power supply system.
  • the invention is based on the following problem. If the expansion machine 20 is operated by a motor, ie power is entered, for example, by the generator 25 in motor operation based on a fixed speed setting or by the external process 26, there is a risk of damage since the power flow does not correspond to the design point ("defective operation").
  • the direction of force on the rotor of the expansion machine (as in Figure 2 ), is based on the force effect of the pressure position of live steam and exhaust steam (depending on the pressure difference across the expansion machine) and the forces due to the power output or power consumption ("transmission force", depending on the pressure quotient via the expansion machine, see also Figure 4 ) certainly. At the operating and thus design point of the expansion machine, these are designed so that the resulting force acts in the direction of the force absorption capacity of the bearing.
  • the expansion machine 20 is a screw expander.
  • Damage is caused, for example, by abrasion or chip formation from the contact of rotating bodies with the housing, since the force effect is not supported by the bearing ( Figure 2 ). This can also result in a shift in the axial direction and possibly a rotation of the bearing ring due to the relief, which can lead to damage to the bearing.
  • connection point b connection speed
  • connection point c connection point
  • the expansion machine 20 is brought to a defined starting point (speed), which prevents damage to the expansion machine when it is switched on.
  • the necessary measurement values of flow and speed of the expansion machine which can be determined by expensive measuring technology, are avoided by model-based control.
  • the state of the expansion machine 20 (in particular its speed) can thus be clearly determined by knowing the live steam pressure, exhaust steam pressure and live steam volume flow (depending on the desired connection speed).
  • the equation above to determine the expansion engine speed initially represents the simplest form and can be further improved in accuracy, for example, by correction using a variable-speed leakage volume flow.
  • the electrical power and thus, for example, a state of the thermodynamic cycle can be derived from the expansion machine speed and the other thermodynamic variables.
  • the live steam mass flow can also be determined relatively easily from the live steam volume flow, which could also be measured in the liquid phase between the feed pump 40 and the evaporator 10.
  • the necessary measuring devices e.g. Coriolis
  • the live steam density also depends on the position of the evaporation pressure, since it is a function of the live steam pressure (and the live steam temperature).
  • the live steam pressure itself is a function of the exhaust steam pressure in this case of the power-free expansion machine operation.
  • This circumstance (p FD and V ⁇ SP vary) also leads to a static starting behavior with fixed speed specification of the feed pump depending on the evaporation pressure, which depends on the condensation conditions such as heat sink temperature depends on starting with a motor drive (high evaporation pressure p AD ; under-synchronous until the expansion machine comes to a standstill) or accelerating the expander beyond the permissible speed (low p AD ).
  • the problems under 1) + 2) can be avoided by additionally monitoring the achieved process variable of the live steam pressure before the connection process. If the pump and the bypass behave regularly, this must correspond to the value determined in the modeling. If it deviates downwards, the start can be terminated without damaging the expansion machine 20.
  • T HW necessary heat source temperature
  • the temperature on the heat input side of the system is reduced in the desired manner in order to achieve a safe standstill of the system at moderate temperatures.
  • this lowering reduces the fresh steam pressure p FD and thus the pressure quotient ⁇ .
  • Damaged operation can also occur here during the downhill run.
  • T HW hot water temperature
  • p FD live steam pressure
  • control device 80 of the feed pump 40 which works without measured values of the expander speed or the flow and contains the low pressure (exhaust pressure) as an input variable in order to regulate to a desired speed of the expansion device 20.
  • the Live steam pressure and the hot water temperature from the model formation are used as a monitoring variable (falling below the model value means deviation in the system with damage potential).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Feedback Control In General (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP17161565.1A 2017-03-17 2017-03-17 Modellbasierte überwachung des betriebszustandes einer expansionsmaschine Active EP3375990B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP17161565.1A EP3375990B1 (de) 2017-03-17 2017-03-17 Modellbasierte überwachung des betriebszustandes einer expansionsmaschine
PCT/EP2017/080029 WO2018166642A1 (de) 2017-03-17 2017-11-22 Modellbasierte überwachung des betriebszustandes einer expansionsmaschine
RU2019129133A RU2724806C1 (ru) 2017-03-17 2017-11-22 Основанный на модели контроль рабочего состояния расширительной машины
CN201780090816.XA CN110730855B (zh) 2017-03-17 2017-11-22 对膨胀机运行状态的基于模型的监视
US16/495,088 US11035258B2 (en) 2017-03-17 2017-11-22 Model-based monitoring of the operating state of an expansion machine
BR112019018768-5A BR112019018768B1 (pt) 2017-03-17 2017-11-22 Método para controlar um aparelho de processo de ciclo termodinâmico, e aparelho de processo de ciclo termodinâmico

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17161565.1A EP3375990B1 (de) 2017-03-17 2017-03-17 Modellbasierte überwachung des betriebszustandes einer expansionsmaschine

Publications (2)

Publication Number Publication Date
EP3375990A1 EP3375990A1 (de) 2018-09-19
EP3375990B1 true EP3375990B1 (de) 2019-12-25

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US (1) US11035258B2 (zh)
EP (1) EP3375990B1 (zh)
CN (1) CN110730855B (zh)
BR (1) BR112019018768B1 (zh)
RU (1) RU2724806C1 (zh)
WO (1) WO2018166642A1 (zh)

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Publication number Priority date Publication date Assignee Title
CN111794820B (zh) * 2020-06-09 2021-09-03 同济大学 一种有机朗肯循环系统
CN112377270B (zh) * 2020-11-11 2022-05-17 贵州电网有限责任公司 一种膨胀发电机组冲转过程中快速稳定转速的方法

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Also Published As

Publication number Publication date
RU2724806C1 (ru) 2020-06-25
BR112019018768A2 (pt) 2020-04-07
BR112019018768A8 (pt) 2023-01-24
BR112019018768B1 (pt) 2023-12-05
CN110730855B (zh) 2022-05-13
US11035258B2 (en) 2021-06-15
WO2018166642A1 (de) 2018-09-20
CN110730855A (zh) 2020-01-24
US20200095897A1 (en) 2020-03-26
EP3375990A1 (de) 2018-09-19

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