CA2101711C - Control system for supplying a gas flow to a gas consumption apparatus - Google Patents
Control system for supplying a gas flow to a gas consumption apparatus Download PDFInfo
- Publication number
- CA2101711C CA2101711C CA002101711A CA2101711A CA2101711C CA 2101711 C CA2101711 C CA 2101711C CA 002101711 A CA002101711 A CA 002101711A CA 2101711 A CA2101711 A CA 2101711A CA 2101711 C CA2101711 C CA 2101711C
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- Prior art keywords
- gas
- valve
- flow
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- signal
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/023—Valves; Pressure or flow regulators in the fuel supply or return system
- F02M21/0239—Pressure or flow regulators therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
- F02D19/021—Control of components of the fuel supply system
- F02D19/023—Control of components of the fuel supply system to adjust the fuel mass or volume flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
- F02D19/026—Measuring or estimating parameters related to the fuel supply system
- F02D19/027—Determining the fuel pressure, temperature or volume flow, the fuel tank fill level or a valve position
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
- F02D19/026—Measuring or estimating parameters related to the fuel supply system
- F02D19/027—Determining the fuel pressure, temperature or volume flow, the fuel tank fill level or a valve position
- F02D19/028—Determining the fuel pressure, temperature or volume flow, the fuel tank fill level or a valve position by estimation, i.e. without using direct measured parameter of a corresponding sensor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/023—Valves; Pressure or flow regulators in the fuel supply or return system
- F02M21/0233—Details of actuators therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N1/00—Regulating fuel supply
- F23N1/005—Regulating fuel supply using electrical or electromechanical means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N5/00—Systems for controlling combustion
- F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel
- F23N5/184—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel using electronic means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/04—Gas-air mixing apparatus
- F02M21/047—Venturi mixer
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N2225/00—Measuring
- F23N2225/04—Measuring pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N2235/00—Valves, nozzles or pumps
- F23N2235/12—Fuel valves
- F23N2235/16—Fuel valves variable flow or proportional valves
-
- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S251/00—Valves and valve actuation
- Y10S251/905—Movable coil electrical actuator, e.g. voice coil
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/2496—Self-proportioning or correlating systems
- Y10T137/2499—Mixture condition maintaining or sensing
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7758—Pilot or servo controlled
- Y10T137/7759—Responsive to change in rate of fluid flow
- Y10T137/776—Control by pressures across flow line valve
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7758—Pilot or servo controlled
- Y10T137/7761—Electrically actuated valve
Abstract
A control system for supplying a gas flow to a gas consumption apparatus, comprising a gas supply pipe which can be connected to the apparatus and which has an electrically controlled gas control valve, and an electronic control unit. The control unit comprises a mathematical module, model-related to the control valve, for adjusting the valve position, and the gas control valve has in-built sensors for gas variables and valve position, the control system adjusting the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit. The mathematical module comprises a flow submodule, a mechanical submodule and a valve-position submodule, and the flow submodule receives, at its inputs, the desired gas-flow signal and gas variables originating from the valve sensors and supplies, at its output, a signal relating to the through-flow area of the valve, to the mechanical submodule. Said mechanical submodule contains mechanical valve parameters processed therein and supplies, at its output, a valve-position signal to the valve-position submodule, which receives a position signal originating from the valve-position sensor. The valve sensors for the gas variables comprise a sensor for the gas inlet pressure, a sensor for the gas inlet temperature and a sensor for the gas pressure difference across the valve. The gas control valve is designed as a cylindrical hollow slide valve having central gas feed and lateral gas outlet with exponential flow profile, and is provided with an electromagnetic actuator having a wire coil wound on the valve slide in a permanent magnetic field.
Description
CONTROL SYSTEM FOR SUPPLYING A G.T~.~ FLOln7 TO ~?. GAS CONSUMP'L"ION
APPARATUS
TECHNICAL FTELD
J The invention relates to a contrc>1 system for supplying a gas flow to a gas consumption apparatus, comprising ~~ c~as supply pipe which can 'be connected to the apparatus and which has an e~.ectrioall.y contx°c'l.led gas cont:rol valve, and an electronic control unit. Suckz a control system. i.s disclosed in EP 0 077 286 published April 20, 1983.
1 ~ EiACI~GROUND AR'T
In a first embodiment of thi:~ known sy:~tem, use is made of an electronic control regulation which adjusts the control valve on the basis of a signal representing the desired gas flow, and of a flow-x°ate or throughput sensor whose output signal is fed back as a corx-action to the E~lect.ronic: control system, which 15 then readjusts the control valve. F~part from the fact: that suc?~
throughput sensors are inaccurate and unre-liabl.e, this systenc is much too slow i.f fast response times are desirr~d. In a sfcorxd embodiment. of this known system, use is made of a simple valve-positioning .loo>x> whickG ~aperates the motcar of the control valve on the basis of a composite input signal. The composite :input signal 2~ essentially comprises a K.~ombinatiox: c}f :i.n:l.et_ g;~s ~~ressure a.nd :rot,ary speed of a gas engine. Corrections ~~an be made tlxex°eto h~y means of a few :Less important variables, such as atmospheric pressure air temperature and gas temperature.
This last embodiment is less cumbersome and also operates more vapidly than the first embodiment but is insufficiently accux°at.e. fhe ox~je~t of the invention is 25 therefore to eliminate the abovementi.oned problems.
Furthermore, in an application of such control systems, namely in gas injection systems for gas combustic7n e~rGgines, thc- :homogeneity cof the gas/air mixture in the cylinders is of great i.mportraz3.cc~ ire achievin.g a:> low as possible an emission of harmful substances. A reduirement related thereto is a very 3fl accurate gas metering with rapid response to alterations in load and rotary speed. In practice, it is of except:ic:~na7. i.mpork:azice to regulates the gas/air ratio extremely accurately in accordance with any desired curve during alteration from starting rotary speed to fuli load at maximum rotary speed. This should also be achieved with varying gay; inlets pressuve°s arol k:emperature:s . Then known systems do not meet these requirements. The object of the invention is al.f>o to fulfil the latter.
SUMMARY OF THE TNVELJT'I'STE FEAT'IJRES
This is achieved, ~c.cordi.ng t~a the i.n~~~nr:ion, with a control -2 ~-system of the type mentioned in the z.nt.raduction in that the control unit comprises a mathematical module, modal-related to the control valve, for adjusting the valve position and in that the gas ~antro~. valve has in-built sensors fox gas variables and valve position, the control system adjusting the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit.
The mathematical module nnent.ianed comprises a flow submodule, a mechanical submodule and a valve-position submodule, whe:cein the flow submodule receives, at its inputs, the desired gas-f7.ow si~~ra.al and. gwis variables originating from the valve sensors and supplies, at its output a s~.gnal, relating to the through-flow area of the valve, to the mechanical submodule, and wherein the mechanical submodule contains mechanical valve paxamete.r;v pr«cessed therein and supplies, at its output, a valve-position signal to the valve-position submodule, which receives a position signal originating from tkae valve-position sensor.
The desired gau-flow signal ment;ianed ma.y origp.nate from a main control system, such as the management system of a ga:~ engine. The valve sensors, built into the gas control valve, far gas parameters comprise a sensor for the gas inlet pressure, a sensor° for the gas :i~ilet terrrperature, and a sensor for the gas pressure difference across the valve.
With this system according t~: the invention, it is .possible to correct automatically for varying gas inlet pressures and temperatures. The system carries out. this correction in an extremely rapid response even during alterations in loading of the consumption apparat7.as, and i:E the latter is a combustion device, during alteratic>ns :in the x°otax-y speed r_.hereof . This is of importance as regards low fuel consumption and low emission of harmful substances.
BRIEF DESCRIPTION OF THE T)RAWINGS
The invention will be explained in greater detail on the basis of an exemplary embodiment, with reference to the drawings, wherein:
Figure 1 shows a diagrammatic representation of the c:ontr.-ol system according to the invention;
Figure 2 shows a block diagram for explaining the representation of Figure 1;
Figure 3 shows an embodiment of the control valve; and Figure 4 shows an application of the ~antrol system of figure 2 in a combustion device, such as a gas eng:i.ne.
DETAILED SUMMARY OF THE INVENTION
Figure 1 gives a very diagrammatic representation of the control system according to the invention, in which Qgn :ind::cat:.e::~ a signal representing the desired gas flow, 2 indicates a mathematical module related to the control valve in terms of a model, 3 indicates an actuator associated with the control valve and 4 indicates diagrammatically the control valve. A gas flow, which is regulated by means of the valve to a gas flow Qh (Q prevailing) at the outlet aide, is fed to the inlet side of the valve 4. A number of gas variables measured at the control valve, such as the gas inlet pressure P1, the gas inlet temperature T1, the gas pressure difference across the valve DP and the valve position Sh, are fed to the module 2. A number of gas parameters, such as standard gas density Gn, standard pressure Pn, standard temperature Tn, gas resistance coefficient ~. and mechanical valve constants b and k are also fed to the module 2. Via the output of the module, a certain control signal is fed to the electromechanical actuator 3 which, finally, exerts a force F on the slide of the control valve 4.
The gas flow in the outlet of the control valve can be adjusted in linear proportion to the desired gas-flow signal fed to the input with the aid of the abovementioned mathematical model-related module. In said module, an accurate mathematical model is implemented which describes the static and dynamic behaviour of the gas flow and the valve. After production, the model is matched once only to the physical model with the aid of a number of parameters which are determined separately in a measurement arrangement. With such a module, gas flows can then be adjusted in a control range of, for example. 0-75 nm3/h with a resolution of 0.02 nm3/h, with an automatic correction of fluctuations in gas inlet pressure and temperature. In this connection, the control valve has three functions. The main function is the control mentioned of the outgoing gas flow. A further function is the complete or 100x shut-off during standstill of the consumption apparatus, such as a gas engine, if the latter is not using any gas. A further Function is the shut-off of the gas flow during deceleration of the gas engine. Under these conditions, a minimum leakage of the gas flow is permissible.
Figure 2 shows the control system according to the invention in greater detail. The module 2 comprises a flow submodule 2.1, a mechanical submodule 2.2 and a position submodule 2.3. A signal representing the desired standard gas flow Qgn is fed to the submodule 2.1. This may originate from any main control system associated with the gas consumption apparatus. If a consumption apparatus which functions as a combustion device, such as a gas engine, is used, this is the signal representing the desired gas flow originating from the engine management ~1 system. The submodule 2.1 incorporates a flow model with which the through-flow area A of the gas control valve is determined in accordance with a certain function.
For applications involving fairly low gas pressures and flow velocities (so-called nonsonic}, the starting point is an adiabatic behaviour of the gas flow and the fa~a that: the gas velocity and the pressure differences are small, as a result of which the Bernoulli energy conservation law for liquids can also be applied to gases: namely P1 + ~,p,vl2 + p,g,hl = p2 + ~,p~K~ + p.g.h~. Here P1 and P2 are static pressures, p is the gas density, v is the gas velocity, g is the acceleration due t;o gravity and h is the height:. Since the process proceeds at constant height, hl = h2. This germ is therefore eliminated.
The equation mentioned must be expanded since t::he through-faow from the inlet side to the outlet sides is acc_~ompana.ed by energy loss in the form of friction. This energy loss can be determined in accordance with DP = ~.~.p.v2, where d~F' = static. plus dynamic pressure difference and ~ = coefficient of resistance.
After substituting v :- Qi'A, where A is the through-flow area of the valve, and after some calcu:lat:i.an, an expression for the gas flow results : Qgn = A .,I ( 2L1P/p~} . Ove:c~ a broad t:e~per°ature range , the gas density p is given by pn.(Pl.Tn/Pn.'f:1), where pn is the specific mass, Tn is the standard temperature and Pn is the standard pressure. After substitution, this gives for A:
~ = ~?9'n . ~'n . T1 .,~.n °..
F'? . Tn 2 L1 P
For applications involving higher gas pressures and flow velocities (so-called sonic} in wtx:ich, far example, the Bernoulli iaw no longer holds true, other laws apply and anathex~ relationship can be derived for A.
The mechanical submodule 2.2 contains a mathematical mechanical model of the valve, with actuator arad sensors. Since the through-flow ports of the control valve have an expaner~tial behaviour, in order to obtain a constant relative error ovex° the entire range, the through-flow aperture of the valve slide becomes a function of the valve position S in accordance with the following equation:
A(s) = k.e.b~s. This then gives ~y=(1/b}.ln(A/k}, where k and b are mechanical constants which are dependent an the valve shape., ~~~7~~~~
The module 2.2 supplies a signal S representing the valve position to the position submodule 2.3. This module, which also receives a signal Sh from the valve-position sensor which is proportional to the position of the valve slide, supplies, at its output, a control signal to 5 the actuator.
The valve comprises a cylindrical hollow slide valve having a central gas inlet and lateral gas outlet with exponential flow profile.
This gas control valve incorporates an electromagnetic actuator with a wire coil in a permanent magnetic field. The position regulation of this electromechanical actuator, which operates the stroke of the valve slide.
is a second-order mechanical mass-spring system. In order to obtain a force F generated by the actuator, the coil must be controlled by a current or voltage signal. For current control, we can write F~oi~
constant.I for the latter.
In Figure 3, an embodiment is given as an example of the gas control valve. In this figure, 11 indicates the valve housing, 12 the profiled sleeve, 13 the valve slide, 14 the wira-wound coil and 14.1 the connections thereof, 15 the permanent magnet, 16 a spring, 17 a number of field conductors, 18 the magnetic casing, 19 the coil form, 20 the position sensor and 20.1 the connections thereof, 21 the sensor for the gas inlet pressure P1, 22 the sensor for the gas inlet temperature T1 and 23 the sensor for the gas differential pressure DP.
As stated, the actuator incorporated in the abovementioned gas control valve comprises a wire coil 14 and a permanent magnet 15. The coil is partly in a narrow air gap 24 in which very high magnetic flux density prevails. This is achieved by guiding the magnetic field of the magnet with the aid of iron conductors 17 and concentrating it in the air gap. If the coil is energized with a current, said coil will experience a (Lorentz) force which is linearly proportional to the magnitude of the current, the flux density and the length of the coil which is situated in the field. The wire coil is wound round a thin plastic form 19 which is attached to the valve slide 13 to which the movement is transferred.
Under these circumstances, said valve slide slides over both through-flow ports. As a result of reversing the current direction, the direction of the force will also reverse. When the coil moves inwards, towards the magnet in the drawing, the gas which is situated in that space will have to make room for the volume of the coil. The gas flow produced in this way may possibly be used partly to cool the wire coil. The gas flow entering on the left-hand side flows via two through-flow ports (not :~. ~ :~. 'a ~.
shown) situated opposite one another and parallel to the plane of the drawing into a circumferentially situated space 25 and passes to the outside via the outlet port 26. The two through-flow ports have, as stated, an exponential flow profile which is indicated as a dashed line by 27.
The diagrammatically indicated gas differential pressure sensor 23 measures the pressure difference across the valve. The response time of this sensor must be shorter than the full-stroke time of the valve slide. This is not more than 30 ms. The diagrammatically indicated temperature sensor 22 measures the absolute temperature of the gas, and the diagrammatically indicated pressure sensor measures the absolute pressure of the gas. The position sensor 20 accurately measures, in a way not indicated further, the position of the valve slide and converts it into an electrical signal Sh. This output signal must be linearly proportional to the position of the valve slide.
Figure 4 gives an example of an application of the gas control valve according to the invention for a gas/air mixer of a combustion device, such as a gas engine. In Figure 4, the same components as those from Figures 1 to 3 are indicated by the same reference numerals.
30 indicates a gas/air mixer, such as a venturi mixing tube.
Air supplied via an air filter 31 is fed to the inlet side thereof. From the outlet side of the mixer 30, an amount of gas/air mixture is fed via a throttle or mixing valve 32 to the gas engine 33~
From the gas engine, a number of variables such as, for example, rotary speed n, absolute inlet mixture temperature (MAT), absolute inlet mixture pressure (MAP), ignition data, are fed to the abovementioned main control or management system 34 of the engine. Such a system is able to determine a certain gas/air ratio for any loading and speed of the engine and supply for the latter a signal Qgn representing the desired gas flow. This signal Qgn, varying for example between 0 and 5 volts, will then be converted in the gas control system according to the invention in direct proportion into a gas flow of, for example, 0 to 75 nm3/h.
The abovementioned so-called open-loop or forward control of the management system can also operate in a closed-loop design. That is to say the desired gas flow signal to the gas contral system will be corrected in such a way that the measured gas/air ratio is equal to the gas/sir ratio of the engine map. The said engine map is a characteristics diagram of the engine and indicates the desired gas/sir ratio (expressed ~10~~~~
as lambda) at a particular engine speed and a particular engine loading.
With the aid of a special sensor, the so-called lambda sensor, in the outlet channel 35 of the engine, the prevailing gas/air ratio is detected. The open-loop control is used, for example, if no lambda sensor is used or if the lambda sensor is heating up or is defective.
APPARATUS
TECHNICAL FTELD
J The invention relates to a contrc>1 system for supplying a gas flow to a gas consumption apparatus, comprising ~~ c~as supply pipe which can 'be connected to the apparatus and which has an e~.ectrioall.y contx°c'l.led gas cont:rol valve, and an electronic control unit. Suckz a control system. i.s disclosed in EP 0 077 286 published April 20, 1983.
1 ~ EiACI~GROUND AR'T
In a first embodiment of thi:~ known sy:~tem, use is made of an electronic control regulation which adjusts the control valve on the basis of a signal representing the desired gas flow, and of a flow-x°ate or throughput sensor whose output signal is fed back as a corx-action to the E~lect.ronic: control system, which 15 then readjusts the control valve. F~part from the fact: that suc?~
throughput sensors are inaccurate and unre-liabl.e, this systenc is much too slow i.f fast response times are desirr~d. In a sfcorxd embodiment. of this known system, use is made of a simple valve-positioning .loo>x> whickG ~aperates the motcar of the control valve on the basis of a composite input signal. The composite :input signal 2~ essentially comprises a K.~ombinatiox: c}f :i.n:l.et_ g;~s ~~ressure a.nd :rot,ary speed of a gas engine. Corrections ~~an be made tlxex°eto h~y means of a few :Less important variables, such as atmospheric pressure air temperature and gas temperature.
This last embodiment is less cumbersome and also operates more vapidly than the first embodiment but is insufficiently accux°at.e. fhe ox~je~t of the invention is 25 therefore to eliminate the abovementi.oned problems.
Furthermore, in an application of such control systems, namely in gas injection systems for gas combustic7n e~rGgines, thc- :homogeneity cof the gas/air mixture in the cylinders is of great i.mportraz3.cc~ ire achievin.g a:> low as possible an emission of harmful substances. A reduirement related thereto is a very 3fl accurate gas metering with rapid response to alterations in load and rotary speed. In practice, it is of except:ic:~na7. i.mpork:azice to regulates the gas/air ratio extremely accurately in accordance with any desired curve during alteration from starting rotary speed to fuli load at maximum rotary speed. This should also be achieved with varying gay; inlets pressuve°s arol k:emperature:s . Then known systems do not meet these requirements. The object of the invention is al.f>o to fulfil the latter.
SUMMARY OF THE TNVELJT'I'STE FEAT'IJRES
This is achieved, ~c.cordi.ng t~a the i.n~~~nr:ion, with a control -2 ~-system of the type mentioned in the z.nt.raduction in that the control unit comprises a mathematical module, modal-related to the control valve, for adjusting the valve position and in that the gas ~antro~. valve has in-built sensors fox gas variables and valve position, the control system adjusting the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit.
The mathematical module nnent.ianed comprises a flow submodule, a mechanical submodule and a valve-position submodule, whe:cein the flow submodule receives, at its inputs, the desired gas-f7.ow si~~ra.al and. gwis variables originating from the valve sensors and supplies, at its output a s~.gnal, relating to the through-flow area of the valve, to the mechanical submodule, and wherein the mechanical submodule contains mechanical valve paxamete.r;v pr«cessed therein and supplies, at its output, a valve-position signal to the valve-position submodule, which receives a position signal originating from tkae valve-position sensor.
The desired gau-flow signal ment;ianed ma.y origp.nate from a main control system, such as the management system of a ga:~ engine. The valve sensors, built into the gas control valve, far gas parameters comprise a sensor for the gas inlet pressure, a sensor° for the gas :i~ilet terrrperature, and a sensor for the gas pressure difference across the valve.
With this system according t~: the invention, it is .possible to correct automatically for varying gas inlet pressures and temperatures. The system carries out. this correction in an extremely rapid response even during alterations in loading of the consumption apparat7.as, and i:E the latter is a combustion device, during alteratic>ns :in the x°otax-y speed r_.hereof . This is of importance as regards low fuel consumption and low emission of harmful substances.
BRIEF DESCRIPTION OF THE T)RAWINGS
The invention will be explained in greater detail on the basis of an exemplary embodiment, with reference to the drawings, wherein:
Figure 1 shows a diagrammatic representation of the c:ontr.-ol system according to the invention;
Figure 2 shows a block diagram for explaining the representation of Figure 1;
Figure 3 shows an embodiment of the control valve; and Figure 4 shows an application of the ~antrol system of figure 2 in a combustion device, such as a gas eng:i.ne.
DETAILED SUMMARY OF THE INVENTION
Figure 1 gives a very diagrammatic representation of the control system according to the invention, in which Qgn :ind::cat:.e::~ a signal representing the desired gas flow, 2 indicates a mathematical module related to the control valve in terms of a model, 3 indicates an actuator associated with the control valve and 4 indicates diagrammatically the control valve. A gas flow, which is regulated by means of the valve to a gas flow Qh (Q prevailing) at the outlet aide, is fed to the inlet side of the valve 4. A number of gas variables measured at the control valve, such as the gas inlet pressure P1, the gas inlet temperature T1, the gas pressure difference across the valve DP and the valve position Sh, are fed to the module 2. A number of gas parameters, such as standard gas density Gn, standard pressure Pn, standard temperature Tn, gas resistance coefficient ~. and mechanical valve constants b and k are also fed to the module 2. Via the output of the module, a certain control signal is fed to the electromechanical actuator 3 which, finally, exerts a force F on the slide of the control valve 4.
The gas flow in the outlet of the control valve can be adjusted in linear proportion to the desired gas-flow signal fed to the input with the aid of the abovementioned mathematical model-related module. In said module, an accurate mathematical model is implemented which describes the static and dynamic behaviour of the gas flow and the valve. After production, the model is matched once only to the physical model with the aid of a number of parameters which are determined separately in a measurement arrangement. With such a module, gas flows can then be adjusted in a control range of, for example. 0-75 nm3/h with a resolution of 0.02 nm3/h, with an automatic correction of fluctuations in gas inlet pressure and temperature. In this connection, the control valve has three functions. The main function is the control mentioned of the outgoing gas flow. A further function is the complete or 100x shut-off during standstill of the consumption apparatus, such as a gas engine, if the latter is not using any gas. A further Function is the shut-off of the gas flow during deceleration of the gas engine. Under these conditions, a minimum leakage of the gas flow is permissible.
Figure 2 shows the control system according to the invention in greater detail. The module 2 comprises a flow submodule 2.1, a mechanical submodule 2.2 and a position submodule 2.3. A signal representing the desired standard gas flow Qgn is fed to the submodule 2.1. This may originate from any main control system associated with the gas consumption apparatus. If a consumption apparatus which functions as a combustion device, such as a gas engine, is used, this is the signal representing the desired gas flow originating from the engine management ~1 system. The submodule 2.1 incorporates a flow model with which the through-flow area A of the gas control valve is determined in accordance with a certain function.
For applications involving fairly low gas pressures and flow velocities (so-called nonsonic}, the starting point is an adiabatic behaviour of the gas flow and the fa~a that: the gas velocity and the pressure differences are small, as a result of which the Bernoulli energy conservation law for liquids can also be applied to gases: namely P1 + ~,p,vl2 + p,g,hl = p2 + ~,p~K~ + p.g.h~. Here P1 and P2 are static pressures, p is the gas density, v is the gas velocity, g is the acceleration due t;o gravity and h is the height:. Since the process proceeds at constant height, hl = h2. This germ is therefore eliminated.
The equation mentioned must be expanded since t::he through-faow from the inlet side to the outlet sides is acc_~ompana.ed by energy loss in the form of friction. This energy loss can be determined in accordance with DP = ~.~.p.v2, where d~F' = static. plus dynamic pressure difference and ~ = coefficient of resistance.
After substituting v :- Qi'A, where A is the through-flow area of the valve, and after some calcu:lat:i.an, an expression for the gas flow results : Qgn = A .,I ( 2L1P/p~} . Ove:c~ a broad t:e~per°ature range , the gas density p is given by pn.(Pl.Tn/Pn.'f:1), where pn is the specific mass, Tn is the standard temperature and Pn is the standard pressure. After substitution, this gives for A:
~ = ~?9'n . ~'n . T1 .,~.n °..
F'? . Tn 2 L1 P
For applications involving higher gas pressures and flow velocities (so-called sonic} in wtx:ich, far example, the Bernoulli iaw no longer holds true, other laws apply and anathex~ relationship can be derived for A.
The mechanical submodule 2.2 contains a mathematical mechanical model of the valve, with actuator arad sensors. Since the through-flow ports of the control valve have an expaner~tial behaviour, in order to obtain a constant relative error ovex° the entire range, the through-flow aperture of the valve slide becomes a function of the valve position S in accordance with the following equation:
A(s) = k.e.b~s. This then gives ~y=(1/b}.ln(A/k}, where k and b are mechanical constants which are dependent an the valve shape., ~~~7~~~~
The module 2.2 supplies a signal S representing the valve position to the position submodule 2.3. This module, which also receives a signal Sh from the valve-position sensor which is proportional to the position of the valve slide, supplies, at its output, a control signal to 5 the actuator.
The valve comprises a cylindrical hollow slide valve having a central gas inlet and lateral gas outlet with exponential flow profile.
This gas control valve incorporates an electromagnetic actuator with a wire coil in a permanent magnetic field. The position regulation of this electromechanical actuator, which operates the stroke of the valve slide.
is a second-order mechanical mass-spring system. In order to obtain a force F generated by the actuator, the coil must be controlled by a current or voltage signal. For current control, we can write F~oi~
constant.I for the latter.
In Figure 3, an embodiment is given as an example of the gas control valve. In this figure, 11 indicates the valve housing, 12 the profiled sleeve, 13 the valve slide, 14 the wira-wound coil and 14.1 the connections thereof, 15 the permanent magnet, 16 a spring, 17 a number of field conductors, 18 the magnetic casing, 19 the coil form, 20 the position sensor and 20.1 the connections thereof, 21 the sensor for the gas inlet pressure P1, 22 the sensor for the gas inlet temperature T1 and 23 the sensor for the gas differential pressure DP.
As stated, the actuator incorporated in the abovementioned gas control valve comprises a wire coil 14 and a permanent magnet 15. The coil is partly in a narrow air gap 24 in which very high magnetic flux density prevails. This is achieved by guiding the magnetic field of the magnet with the aid of iron conductors 17 and concentrating it in the air gap. If the coil is energized with a current, said coil will experience a (Lorentz) force which is linearly proportional to the magnitude of the current, the flux density and the length of the coil which is situated in the field. The wire coil is wound round a thin plastic form 19 which is attached to the valve slide 13 to which the movement is transferred.
Under these circumstances, said valve slide slides over both through-flow ports. As a result of reversing the current direction, the direction of the force will also reverse. When the coil moves inwards, towards the magnet in the drawing, the gas which is situated in that space will have to make room for the volume of the coil. The gas flow produced in this way may possibly be used partly to cool the wire coil. The gas flow entering on the left-hand side flows via two through-flow ports (not :~. ~ :~. 'a ~.
shown) situated opposite one another and parallel to the plane of the drawing into a circumferentially situated space 25 and passes to the outside via the outlet port 26. The two through-flow ports have, as stated, an exponential flow profile which is indicated as a dashed line by 27.
The diagrammatically indicated gas differential pressure sensor 23 measures the pressure difference across the valve. The response time of this sensor must be shorter than the full-stroke time of the valve slide. This is not more than 30 ms. The diagrammatically indicated temperature sensor 22 measures the absolute temperature of the gas, and the diagrammatically indicated pressure sensor measures the absolute pressure of the gas. The position sensor 20 accurately measures, in a way not indicated further, the position of the valve slide and converts it into an electrical signal Sh. This output signal must be linearly proportional to the position of the valve slide.
Figure 4 gives an example of an application of the gas control valve according to the invention for a gas/air mixer of a combustion device, such as a gas engine. In Figure 4, the same components as those from Figures 1 to 3 are indicated by the same reference numerals.
30 indicates a gas/air mixer, such as a venturi mixing tube.
Air supplied via an air filter 31 is fed to the inlet side thereof. From the outlet side of the mixer 30, an amount of gas/air mixture is fed via a throttle or mixing valve 32 to the gas engine 33~
From the gas engine, a number of variables such as, for example, rotary speed n, absolute inlet mixture temperature (MAT), absolute inlet mixture pressure (MAP), ignition data, are fed to the abovementioned main control or management system 34 of the engine. Such a system is able to determine a certain gas/air ratio for any loading and speed of the engine and supply for the latter a signal Qgn representing the desired gas flow. This signal Qgn, varying for example between 0 and 5 volts, will then be converted in the gas control system according to the invention in direct proportion into a gas flow of, for example, 0 to 75 nm3/h.
The abovementioned so-called open-loop or forward control of the management system can also operate in a closed-loop design. That is to say the desired gas flow signal to the gas contral system will be corrected in such a way that the measured gas/air ratio is equal to the gas/sir ratio of the engine map. The said engine map is a characteristics diagram of the engine and indicates the desired gas/sir ratio (expressed ~10~~~~
as lambda) at a particular engine speed and a particular engine loading.
With the aid of a special sensor, the so-called lambda sensor, in the outlet channel 35 of the engine, the prevailing gas/air ratio is detected. The open-loop control is used, for example, if no lambda sensor is used or if the lambda sensor is heating up or is defective.
Claims (7)
1. A control system for supplying a gas tow to a gas consumption apparatus, comprising:
a gas supply pipe adapted to be connected to the apparatus having an electrically controlled gas control valve;
the gas control valve comprising in-built valve sensor means for sensing gas variables and valve position, a cylindrical hollow slide valve having a valve slide and including a central gas feed and a lateral gas outlet with an exponential flow profile and an electromagnetic actuator having a wire coil which is wound on the valve slide in a permanent magnetic field; and an electronic control unit comprising a mathematical module, model-related to the control valve, for adjusting the position of the control valve;
wherein the control system is adapted to adjust the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit.
a gas supply pipe adapted to be connected to the apparatus having an electrically controlled gas control valve;
the gas control valve comprising in-built valve sensor means for sensing gas variables and valve position, a cylindrical hollow slide valve having a valve slide and including a central gas feed and a lateral gas outlet with an exponential flow profile and an electromagnetic actuator having a wire coil which is wound on the valve slide in a permanent magnetic field; and an electronic control unit comprising a mathematical module, model-related to the control valve, for adjusting the position of the control valve;
wherein the control system is adapted to adjust the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit.
2. The control system according to claim 1, wherein the mathematical module comprises a flow submodule, a mechanical submodule and a valve-position submodule each having inputs and outputs, the flow submodule adapted to receive the desired gas-flow signal and gas variables originating from the valve sensor means at its inputs and the flow submodule adapted to supply a signal relating to a through-flow area of the valve at its output, wherein the through-flow area signal is directed to the mechanical submodule and the mechanical submodule is adapted to process mechanical valve parameters and supply a valve-position signal at its output which is adapted to be directed to the valve-position submodule which receives a position signal originating from the valve sensor means.
3. The control system according to claim 2, wherein the valve sensor means for sensing the gas variables comprise a sensor means for sensing gas inlet pressure, a sensor means for sensing gas inlet temperature and a sensor means for sensing gas pressure difference across the valve.
4. The control system according to claim 3, wherein the flow submodule is provided with calculation means in communication with and adapted to receive an inlet pressure signal from the sensor means for sensing the gas inlet pressure, the flow submodule being in communication with and adapted to receive an inlet temperature signal from the sensor means for sensing the gas inlet temperature, and the flow submodule being in communication with and adapted to receive a gas pressure difference signal from the sensor means for sensing the gas pressure difference across the valve, the calculation means adapted to generate a through-flow area signal for transmission to the mechanical submodule, wherein the through-flow area signal is determined in accordance with the following equation:
where A=through-flow area, Qgn=desired gas flow, P1=inlet pressure of the gas, T1=inlet temperature of the gas, .DELTA.P=differential gas pressure across the valve, Pn=standard pressure of the gas, Tn=standard temperature of the gas, .RHO.=specific mass, .zeta.=coefficient of gas resistance.
where A=through-flow area, Qgn=desired gas flow, P1=inlet pressure of the gas, T1=inlet temperature of the gas, .DELTA.P=differential gas pressure across the valve, Pn=standard pressure of the gas, Tn=standard temperature of the gas, .RHO.=specific mass, .zeta.=coefficient of gas resistance.
5. A control system according to claim 4, wherein the mechanical submodule is provided with further calculation means for receiving the through-flow area signal from the flow submodule and for generating the valve position signal in accordance with the following equation:
S=(1/b).cndot.ln (A/k), where S=valve position, b=mechanical parameter, k=mechanical parameter.
S=(1/b).cndot.ln (A/k), where S=valve position, b=mechanical parameter, k=mechanical parameter.
6. A gas control assembly for use with a gas combustion engine, comprising:
a control system including a gas supply pipe adapted to be connected to the engine having an electrically controlled gas control valve, the gas control valve comprising in-built valve sensor means for sensing gas variables and valve position, a cylindrical hollow slide valve having a valve slide and including a central gas feed and a lateral gas outlet with an exponential flow profile and an electromagnetic actuator having a wire coil wound on the valve slide in a permanent magnetic field, an electronic control unit comprising a mathematical module, model-related to the control valve, for adjusting the position of the control valve wherein the control system is adapted to adjust the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit;
a gas/air mixer, wherein the lateral gas outlet of the gas control valve is connected to the gas/air mixer and the gas/air mixer is connected to an air inlet conduit means for supplying a gas/air mixture to the gas combustion engine;
sensor means for detecting a rotary speed of the gas combustion engine;
a sensor means for detecting an inlet temperature of the gas/air mixture to the gas combustion engine;
a sensor means for detecting an inlet pressure of the gas/air mixture to the gas combustion engine; and the assembly including at least one input for receiving the desired gas flow signals including the sensed rotary speed, inlet temperature and pressure and at least one output for providing the desired gas flow signal to the control system.
a control system including a gas supply pipe adapted to be connected to the engine having an electrically controlled gas control valve, the gas control valve comprising in-built valve sensor means for sensing gas variables and valve position, a cylindrical hollow slide valve having a valve slide and including a central gas feed and a lateral gas outlet with an exponential flow profile and an electromagnetic actuator having a wire coil wound on the valve slide in a permanent magnetic field, an electronic control unit comprising a mathematical module, model-related to the control valve, for adjusting the position of the control valve wherein the control system is adapted to adjust the control valve in linear proportion to a desired gas-flow signal to be supplied to the control unit;
a gas/air mixer, wherein the lateral gas outlet of the gas control valve is connected to the gas/air mixer and the gas/air mixer is connected to an air inlet conduit means for supplying a gas/air mixture to the gas combustion engine;
sensor means for detecting a rotary speed of the gas combustion engine;
a sensor means for detecting an inlet temperature of the gas/air mixture to the gas combustion engine;
a sensor means for detecting an inlet pressure of the gas/air mixture to the gas combustion engine; and the assembly including at least one input for receiving the desired gas flow signals including the sensed rotary speed, inlet temperature and pressure and at least one output for providing the desired gas flow signal to the control system.
7. The control assembly according to claim 6, further comprising a sensor means for detecting a prevailing gas/air ratio at an output side of the gas combustion engine and for generating a prevailing gas/air ratio signal to be supplied to the assembly.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NL9201391A NL9201391A (en) | 1992-07-31 | 1992-07-31 | Control system for supplying a gas flow to a gas appliance. |
NL9201391 | 1992-07-31 |
Publications (2)
Publication Number | Publication Date |
---|---|
CA2101711A1 CA2101711A1 (en) | 1994-02-01 |
CA2101711C true CA2101711C (en) | 2004-04-27 |
Family
ID=19861139
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CA002101711A Expired - Fee Related CA2101711C (en) | 1992-07-31 | 1993-07-30 | Control system for supplying a gas flow to a gas consumption apparatus |
Country Status (10)
Country | Link |
---|---|
US (1) | US5388607A (en) |
EP (1) | EP0581391B1 (en) |
JP (1) | JPH06173725A (en) |
AT (1) | ATE145449T1 (en) |
AU (1) | AU669185B2 (en) |
CA (1) | CA2101711C (en) |
DE (1) | DE69306056T2 (en) |
DK (1) | DK0581391T3 (en) |
ES (1) | ES2096848T3 (en) |
NL (1) | NL9201391A (en) |
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-
1992
- 1992-07-31 NL NL9201391A patent/NL9201391A/en not_active Application Discontinuation
-
1993
- 1993-07-30 JP JP5206931A patent/JPH06173725A/en active Pending
- 1993-07-30 CA CA002101711A patent/CA2101711C/en not_active Expired - Fee Related
- 1993-07-30 AU AU44323/93A patent/AU669185B2/en not_active Ceased
- 1993-07-30 US US08/100,561 patent/US5388607A/en not_active Expired - Lifetime
- 1993-08-02 DK DK93202284.1T patent/DK0581391T3/en active
- 1993-08-02 ES ES93202284T patent/ES2096848T3/en not_active Expired - Lifetime
- 1993-08-02 AT AT93202284T patent/ATE145449T1/en not_active IP Right Cessation
- 1993-08-02 EP EP93202284A patent/EP0581391B1/en not_active Expired - Lifetime
- 1993-08-02 DE DE69306056T patent/DE69306056T2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE69306056D1 (en) | 1997-01-02 |
JPH06173725A (en) | 1994-06-21 |
EP0581391A1 (en) | 1994-02-02 |
CA2101711A1 (en) | 1994-02-01 |
ES2096848T3 (en) | 1997-03-16 |
AU669185B2 (en) | 1996-05-30 |
DK0581391T3 (en) | 1996-12-09 |
US5388607A (en) | 1995-02-14 |
EP0581391B1 (en) | 1996-11-20 |
ATE145449T1 (en) | 1996-12-15 |
NL9201391A (en) | 1994-02-16 |
DE69306056T2 (en) | 1997-03-13 |
AU4432393A (en) | 1994-02-03 |
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Effective date: 20050801 |