CN105649764A - Maintenance device with optimized control system for hydroelectric power station - Google Patents
Maintenance device with optimized control system for hydroelectric power station Download PDFInfo
- Publication number
- CN105649764A CN105649764A CN201610041631.7A CN201610041631A CN105649764A CN 105649764 A CN105649764 A CN 105649764A CN 201610041631 A CN201610041631 A CN 201610041631A CN 105649764 A CN105649764 A CN 105649764A
- Authority
- CN
- China
- Prior art keywords
- oil
- engine
- pressure
- control valve
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 238000012423 maintenance Methods 0.000 title claims abstract description 30
- 238000007906 compression Methods 0.000 claims abstract description 112
- 230000006835 compression Effects 0.000 claims abstract description 110
- 238000002347 injection Methods 0.000 claims abstract description 78
- 239000007924 injection Substances 0.000 claims abstract description 78
- 238000001514 detection method Methods 0.000 claims abstract description 20
- 230000002000 scavenging effect Effects 0.000 claims abstract description 8
- 239000003921 oil Substances 0.000 claims description 268
- 238000004146 energy storage Methods 0.000 claims description 74
- 239000000446 fuel Substances 0.000 claims description 56
- 230000000694 effects Effects 0.000 claims description 39
- 238000000034 method Methods 0.000 claims description 37
- 230000008569 process Effects 0.000 claims description 36
- 230000008859 change Effects 0.000 claims description 28
- 239000007788 liquid Substances 0.000 claims description 19
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 17
- 238000002485 combustion reaction Methods 0.000 claims description 15
- 238000006073 displacement reaction Methods 0.000 claims description 15
- 230000010349 pulsation Effects 0.000 claims description 8
- 238000004458 analytical method Methods 0.000 claims description 7
- 239000002283 diesel fuel Substances 0.000 claims description 7
- 239000000295 fuel oil Substances 0.000 claims description 7
- 230000001960 triggered effect Effects 0.000 claims description 7
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 230000004044 response Effects 0.000 description 10
- 230000009467 reduction Effects 0.000 description 6
- 238000010521 absorption reaction Methods 0.000 description 5
- 230000001133 acceleration Effects 0.000 description 5
- 230000003247 decreasing effect Effects 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 5
- 230000001739 rebound effect Effects 0.000 description 5
- 230000000630 rising effect Effects 0.000 description 5
- 230000035939 shock Effects 0.000 description 5
- 230000003068 static effect Effects 0.000 description 5
- 230000004304 visual acuity Effects 0.000 description 5
- 238000005381 potential energy Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/02—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving cycles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B77/00—Component parts, details or accessories, not otherwise provided for
- F02B77/08—Safety, indicating, or supervising devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/02—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving vehicles; peculiar to engines driving variable pitch propellers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
- F02N7/06—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of reciprocating-piston type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N2200/00—Parameters used for control of starting apparatus
- F02N2200/02—Parameters used for control of starting apparatus said parameters being related to the engine
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Fuel-Injection Apparatus (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
The invention discloses a maintenance device with an optimized control system for a hydroelectric power station. The maintenance device for the hydroelectric power station comprises a maintenance vehicle and an engine connected with the maintenance vehicle, wherein the engine is used for driving the maintenance vehicle; the engine comprises a power part, an oil injection system and a hydraulic part; the hydraulic part comprises a compression cavity, a pump cavity, a return cavity and a hydraulic circuit; the compression cavity is arranged in the rear part of the engine, and a first oil port and a second oil port are arranged in the compression cavity; the first oil port and the second oil port are connected with a compression energy accumulator through a first control valve and a second control valve respectively; the pump cavity is connected with a low-pressure oil path and a high-pressure oil path through a one-way valve respectively; a return control valve and a low-pressure energy accumulator are arranged on the low-pressure oil path; a pressure reducing valve is arranged on an oil pipeline from a high-pressure energy accumulator to a cylinder body; and a start valve is arranged on an oil pipeline between the compression energy accumulator and the high-pressure energy accumulator. The maintenance device for the hydroelectric power station, which is disclosed by the invention, is simple in structure, convenient to manufacture, high in scavenging efficiency, stable in performance, and high in output torque; and complete control system and position detection system are designed.
Description
Technical field
The present invention relates to hydroelectric field, it is specifically related to a kind of water generating station attending device with optimal control system.
Background technology
Water power system utilize river, lake etc. to be positioned at water that eminence has potential energy flow to lower, wherein contained potential energy converting and energy will become the kinetic energy of water turbine, then borrow water turbine to be prime mover, pushing generator produces electric energy. Utilizing waterpower to promote hydraulicefficiency machinery to rotate, water can be changed into mechanical energy, just can send along with water turbine rotates electric next if connecting another kind of machinery on water turbine, at this moment mechanical energy is changed into again electric energy.
At hydroelectric field, owing to power station is vast in territory, hydropower station attending device, especially maintenance cart becomes important hydropower station attending device. How to reduce the work energy consumption of hydropower station attending device further and raise the efficiency, be the problem that people are concerned about always. Present maintenance cart, substantially it is all with engine-driven, and existing engine generally exists the problems such as structure is too complicated, control is accurate not, output torque is not enough, therefore we can set about improving the performance of hydropower station attending device from this aspect.
Summary of the invention
For the problems referred to above, the present invention provide a kind of compact construction, control accurately, stable performance and the big hydropower station attending device of output torque.
The object of the present invention realizes by the following technical solutions:
A kind of water generating station attending device with optimal control system, the engine comprising maintenance cart and be connected with maintenance cart, engine is for driving maintenance cart, it is characterized in that, engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve, power piston, combustion chamber, oil thrower, scavenging port, hydraulic part comprises compression chamber, pump chamber, return chamber, position and hydraulic circuit, described compression chamber is arranged at the rear portion of engine, it is provided with the first oil mouth thereon, 2nd oil mouth, described first oil mouth, 2nd oil mouth is connected with compress energy storage device with the 2nd control valve by the first control valve respectively, described pump chamber is connected with high-pressure oil passage with low pressure oil way respectively by check valve, high-pressure oil passage is used for engine loading fuel feeding, low pressure oil way is provided with back level control valve and low pressure accumulator, return bypass on level control valve and it is provided with oil return check valve, chamber, described time position is directly connected with high pressure accumulator, is provided with reducing valve on the oil line of described high pressure accumulator to cylinder body, starting duty and catch fire operating mode time reducing valve be held open, during nominal situation reducing valve close, described compress energy storage device is connected by oil line with high pressure accumulator, and is provided with starting valve on oil line between described compress energy storage device and high pressure accumulator, and for improving the compression ratio of engine during start operating performance, during nominal situation, starting valve cuts out, described high-pressure oil passage is connected with a load energy storage, leads to a road and be connected with described compress energy storage device after reducing valve, the end of engine is provided with hydraulic pressure sacculus, is full of the pressure oil injected in advance, is connected with low pressure accumulator by oil line, is also provided with spring safety valve between hydraulic pressure sacculus and low pressure accumulator bottom it in hydraulic pressure sacculus, the upper left side of described hydraulic pressure sacculus is provided with the dead band You Kou of inclination, its place straight line and hydraulic pressure sacculus are tangent, dead band oil mouth and compress energy storage device return a magnetic valve be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead zone location being in when the end of piston component between the 2nd oil mouth and hydraulic pressure sacculus, return a magnetic valve make piston component return to the ideally stop region between the 2nd oil mouth and the first oil mouth to start next stroke by opening dead band, described injection system is high-pressure co-rail electric-controlling injection system, comprise injection pump, common rail pipe, electric-controlled fuel injector, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump, fuel oil enters injection pump through purifier, after the compression of injection pump, low pressure oil turns into high-pressure oil, and inputted common rail pipe by injection pump, in common rail pipe, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently high-pressure oil is inputted in electric-controlled fuel injector, wait the oil spout instruction of electronically controlled unit,
Described engine also comprises position detecting system, position detecting system is detected by linear displacement sensor and location triggered sensor and sends signal when piston component arrives top dead center position, bottom dead center position and feed forward position, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve, feed forward position is determined according to the speed value cooperation position detection system of piston; Described engine also comprises constant-voltage driving system, and described constant-voltage driving system comprises engine and hydraulic variable motor, keeps exporting the constant of oil liquid pressure by motor driving moment and load resistance square; By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure;
Described engine also comprises start control system, normal operation Controlling System and fire controll system:
Start control system, the control for engine starting duty: after start signal sends, opens starting valve and reducing valve, and compress energy storage device is owing to being connected with high pressure accumulator and pressure raises, and the compression ratio of engine is improved, the signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve and the 2nd control valve are opened, piston component is under the effect of compress energy storage device, start compression stroke, if piston component being detected not in lower dead center, first level control valve is opened back, hydraulic efficiency oil in pump chamber and compression chamber is released by low pressure oil way, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator pressure, close back level control valve, then start compression stroke, when piston arrives feed forward position, 2nd control valve is closed, when piston arrives after top dead center, first control valve is closed, return level control valve to open, piston component returns to after bottom dead center again, close back level control valve, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when frequency valve start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature do not meet ignition condition, then repeat above-described working process, until after pressure and temperature meets ignition condition, start to enter the control process of normal operation,
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve and reducing valve, first control valve keeps normal open state, after start signal sends, 2nd control valve is opened, first hydraulic efficiency oil in compress energy storage device enter compression chamber by the 2nd control valve, piston component is promoted to move to top dead center, after the first oil mouth is opened, 2nd control valve is closed, it is connected by the first oil mouth between compression chamber and compress energy storage device, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve is opened again,
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve, and open reducing valve and return level control valve, piston component is made to be returned to bottom dead center position, then the first control valve is opened, wait next starting impulse signal, engine moves according to normal operating cycle again.
The useful effect of the present invention is: 1, hydraulic efficiency system all can to load fuel feeding in compression and expansion process, and the string pressure string oil phenomenon that should not be able to occur between effectively anti-locking system; Coordinate each energy storage to reduce output flow pulsation, sound reduction; For the operation characteristic of each operating mode engine, devise new Controlling System, can more precisely, effectively control the operation of engine; 2, between top dead center and lower dead center, feed forward position is added, frequency valve is just closed when piston component arrives feed forward position under start operating performance, switch-valve is closed again in arrival after top dead center, so both ensure that the speed of compression stroke, turn reduce the resistance of expansion stroke, improve the working efficiency of engine on the whole and reduce journey time; 3, by the starting valve between control high pressure accumulator and compress energy storage device, increase the compression ratio of engine, and output oil pressure can not be impacted generation hydro pulse, starting valve is closed after nominal situation, replace the method that traditional petrol station system heightens compression ratio, there is the simple feature of economical and practical structure; 4, in order to avoid back opening by mistake and improving the accurate degree caught fire and judge of level control valve, take the position of cylinder temperature cylinder pressure and piston component as the main basis for estimation caught fire, consider the retardance that cylinder temperature declines simultaneously, add frequency and the front feedback signal of frequency variation rate (or change in displacement rate), namely first determination frequency and frequency change rate are less than set(ting)value, and then judge that whether piston is at bottom dead center position, if do not existed, then open back level control valve; 5, devise new hydraulic pressure sacculus formula snubber assembly and attached superpressure preventing device thereof, while playing buffering and superpressure preventing function, the hydraulic efficiency loss of engine can also be played certain supplementary function; 6, the setting of a magnetic valve is returned by dead band oil mouth and dead band, can effectively solve piston component to be difficult to return to the problem that lower dead center starts next stroke in dead zone location, arranged by tangent oily mouth simultaneously reduce piston component enter dead band after the wriggling time, improve further the whole efficiency of engine.
Accompanying drawing explanation
The invention will be further described to utilize accompanying drawing, but the embodiment in accompanying drawing does not form any limitation of the invention, for the those of ordinary skill of this area, under the prerequisite not paying creative work, it is also possible to obtain other accompanying drawing according to the following drawings.
Fig. 1 is the structural representation of this hydropower station attending device engine;
Fig. 2 is the structural representation of injection system;
Fig. 3 is the position view in ideally stop region and dead band.
Reference numeral: 1-compression chamber; 2-the 2nd control valve; 3-first control valve; 4-compress energy storage device; 5-first oil mouth; 6-the 2nd oil mouth; 7-pump chamber; 8-high pressure accumulator; 9-air inlet check valve; 10-power piston; 11-combustion chamber; 12-oil thrower; 13-scavenging port; 14-goes back to a chamber; 15-resetting piston; 17-returns level control valve; 18-low pressure accumulator; 19-compression piston; 21-oil return check valve; 22-reducing valve; 23-starting valve; 24-load energy storage; 25-high-pressure oil passage; 26-low pressure oil way; 27-hydraulic pressure sacculus; 28-mechanical safety valve; 29-transfer pump; 30-purifier; 31-injection pump; 32-common rail pipe; 33-electric-controlled fuel injector; 34-dead band You Kou; 35-returns in dead band a magnetic valve; A-is stop region ideally; B-dead band.
Embodiment
The invention will be further described with the following Examples.
Embodiment 1: a kind of water generating station attending device with optimal control system as Figure 1-3, the engine comprising maintenance cart and being connected with maintenance cart, engine is for driving maintenance cart, and engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve 9, power piston 10, combustion chamber 11, oil thrower 12, scavenging port 13, resetting piston 15, compression piston 19, hydraulic part comprises compression chamber 1, pump chamber 7, returning chamber, position 14 and hydraulic circuit, described compression chamber 1 is arranged at the rear portion of engine, is provided with the first oil mouth 5 thereon, 2nd oil mouth 6, described first oil mouth 5, 2nd oil mouth 6 is connected with compress energy storage device 4 with the 2nd control valve 2 by the first control valve 3 respectively, described pump chamber 7 is connected with high-pressure oil passage 25 with low pressure oil way 26 respectively by check valve 9, high-pressure oil passage 25 is for engine loading fuel feeding, being provided with back level control valve 17 and low pressure accumulator 18 on low pressure oil way 26, on time level control valve 17, also bypass is provided with oil return check valve 21, chamber, described time position 14 is directly connected with high pressure accumulator 8, is provided with reducing valve 22 at described high pressure accumulator 8 to the oil line of cylinder body, described compress energy storage device 4 is connected by oil line with described high pressure accumulator 8, and the oil line between described compress energy storage device 4 and described high pressure accumulator 8 is also provided with starting valve 23, described high-pressure oil passage 25 is connected with a load energy storage 24, leads to a road and be connected with described compress energy storage device 4 after described reducing valve 22, described injection system is high-pressure co-rail electric-controlling injection system.
The end of engine is provided with hydraulic pressure sacculus 27, the pressure oil of the certain pressure injected in advance it is full of in hydraulic pressure sacculus 27, it is connected with low pressure accumulator 18 by oil line bottom it, when load pressure reduces suddenly or fuel charge overshoot causes piston to cross the 2nd oil mouth 6 with bigger speed, hydraulic pressure sacculus 27 can play good shock absorption, and substantially can not produce rebound effect; Simultaneously in order to prevent hydraulic pressure sacculus 27 overpressure failure, spring safety valve 28 also it is provided with between hydraulic pressure sacculus 27 and low pressure accumulator 18, once hydraulic pressure sacculus 27 superpressure spring safety valve 28 will be opened automatically, and by low pressure accumulator 18 compensator or trimmer pressure, at this moment the hydraulic efficiency system of engine can be played certain supplementary function by hydraulic pressure sacculus 27. The upper left side of described hydraulic pressure sacculus 27 is provided with the dead band oil mouth 34 of inclination, its place straight line and hydraulic pressure sacculus 27 are tangent, dead band oil mouth 34 and compress energy storage device 4 return a magnetic valve 35 be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead band B being in when the end of piston component between the 2nd oil mouth 6 and hydraulic pressure sacculus 27, return a magnetic valve 35 make piston component return to the ideally stop region A between the 2nd oil mouth 6 and the first oil mouth 5 to start next stroke by opening dead band.
The effect of high pressure accumulator 8 is: one is ensure that when engine shutdown, and piston component can stop at bottom dead center position, reduces and wriggles; When two is under engine starting duty and situation of catching fire occurs, promote piston component to be returned to bottom dead center position, enable engine continue to start next circulation.
This engine also comprises position detecting system, signal when described position detecting system arrives top dead center position, bottom dead center position and feed forward position by linear displacement sensor and location triggered sensor detection piston component, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve 3, feed forward position is determined according to the speed value cooperation position detection system of piston.
Described injection system comprises injection pump 31, common rail pipe 32, electric-controlled fuel injector 33, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump 29, fuel oil enters injection pump 31 through purifier 30, after the compression of injection pump 31, low pressure oil turns into high-pressure oil, and inputted common rail pipe 32 by injection pump 31, in common rail pipe 32, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently by relatively stable and have certain pressure high-pressure oil input electric-controlled fuel injector 33 in, wait the oil spout instruction of electronically controlled unit.
This engine is also provided with constant-voltage driving system, and described constant-voltage driving system mainly comprises engine and hydraulic variable motor, by motor driving moment and load resistance square, maintains and exports the constant of oil liquid pressure. By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure. Hydraulic variable motor is connected with load machinery, and both rotating speeds are equal; In steady operation situation, motor driving moment is equal with load resistance square size, and direction is contrary, and when resistance becomes big, motor driving moment is less than load resistance square, and motor rotary speed is reduced. Owing to the flow of output hydraulic pressure oil is constant, the situation current downflow resistance that output hydraulic pressure oil increases in back pressure increases, thus causes the rising of pressure in system. Now, the variable mechanism of oil motor receives the feedback of this pressure raises signal and regulates, and self discharge capacity is increased, increases the flow of motor when rotating speed reduces, thus reduce oil stream dynamic resistance, maintain engine and export the constant of oil liquid pressure. Meanwhile, owing to discharge capacity increases, motor driving moment also increases thereupon, and balances each other with load resistance square gradually, and system realizes reaching steady-working state again. Equally, when load resistance reduces, when fluid motor-driven moment is greater than load resistance square, motor rotary speed raises, and causes the reduction of pressure in hydraulic efficiency system. Now, hydraulic variable motor discharge capacity regulates to the direction reduced, and driving moment and load resistance square are balanced each other, pressure constant in keeping system while realizing system stability work.
Described engine also comprises start control system, normal operation Controlling System and fire controll system:
Start control system, the control for engine starting duty: after start signal sends, opens starting valve 23 and reducing valve 22, and compress energy storage device 4 is owing to being connected with high pressure accumulator 8 and pressure raises, and the compression ratio of engine is improved; The signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve 3 and the 2nd control valve 2 are opened, piston component is under the effect of compress energy storage device 4, start compression stroke, if piston component being detected not in lower dead center, first level control valve 17 is opened back, hydraulic efficiency oil in pump chamber 7 and compression chamber 1 is released by low pressure oil way 26, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator 8 pressure, close back level control valve 17, then start compression stroke; When the speed of piston is decreased to a certain set(ting)value, think that it arrives feed forward position, now the 2nd control valve 2 is closed, when piston arrives after top dead center, first control valve 3 is closed, and returns level control valve 17 and opens, the control mode that the first control valve 3 and the 2nd control valve 2 substep are closed by this kind, both ensure that the speed of compression stroke, turn reduce the resistance of expansion stroke; Piston component returns to after bottom dead center again, close back level control valve 17, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when the 2nd control valve 2 start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature are all lower, then repeat above-described working process, until after pressure and temperature meets ignition condition, starting to enter the control process of normal operation.
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve 23 and reducing valve 22, first control valve 3 keeps normal open state, after start signal sends, 2nd control valve 2 is opened, first hydraulic efficiency oil in compress energy storage device 4 enter compression chamber 1 by the 2nd control valve 2, piston component is promoted to move to top dead center, after the first oil mouth 5 is opened, 2nd control valve 2 is closed, it is connected by the first oil mouth 5 between compression chamber 1 and compress energy storage device 4, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is substantially equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve 2 is opened again.
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve 3, and open reducing valve 22 and return level control valve 17, piston component is made to be returned to bottom dead center position, then the first control valve 3 is opened, wait next starting impulse signal, engine moves according to normal operating cycle again.
Described 2nd control valve 2 adopts peak flow to be 250L/min, opens the high-frequency electrohydraulic servo-valve that pulsewidth is 10ms, electrohydraulic servo valve is that one accepts analog quantity electric control signal, export with the hydrauliccontrol valve of electric control signal size and change in polarity and response fast, there is dynamic response and good static characteristics fast, as: resolving power height, stagnant ring are little, the linear lag is good. The peak flow of the 2nd control valve 2, when use peak flow be 250L/min, open pulsewidth be 10ms electrohydraulic servo valve time, about the acceleration segment length of piston component can be increased to original 5 times, the compression stroke time used obviously reduces, thus make the motion cycle reduce 7ms nearly than originally, improve the maximum functional frequency of engine significantly, achieve unexpected effect.
Embodiment 2: a kind of water generating station attending device with optimal control system as Figure 1-3, the engine comprising maintenance cart and being connected with maintenance cart, engine is for driving maintenance cart, and engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve 9, power piston 10, combustion chamber 11, oil thrower 12, scavenging port 13, resetting piston 15, compression piston 19, hydraulic part comprises compression chamber 1, pump chamber 7, returning chamber, position 14 and hydraulic circuit, described compression chamber 1 is arranged at the rear portion of engine, is provided with the first oil mouth 5 thereon, 2nd oil mouth 6, described first oil mouth 5, 2nd oil mouth 6 is connected with compress energy storage device 4 with the 2nd control valve 2 by the first control valve 3 respectively, described pump chamber 7 is connected with high-pressure oil passage 25 with low pressure oil way 26 respectively by check valve 9, high-pressure oil passage 25 is for engine loading fuel feeding, being provided with back level control valve 17 and low pressure accumulator 18 on low pressure oil way 26, on time level control valve 17, also bypass is provided with oil return check valve 21, chamber, described time position 14 is directly connected with high pressure accumulator 8, is provided with reducing valve 22 at described high pressure accumulator 8 to the oil line of cylinder body, described compress energy storage device 4 is connected by oil line with described high pressure accumulator 8, and the oil line between described compress energy storage device 4 and described high pressure accumulator 8 is also provided with starting valve 23, described high-pressure oil passage 25 is connected with a load energy storage 24, leads to a road and be connected with described compress energy storage device 4 after described reducing valve 22, described injection system is high-pressure co-rail electric-controlling injection system.
The end of engine is provided with hydraulic pressure sacculus 27, the pressure oil of the certain pressure injected in advance it is full of in hydraulic pressure sacculus 27, it is connected with low pressure accumulator 18 by oil line bottom it, when load pressure reduces suddenly or fuel charge overshoot causes piston to cross the 2nd oil mouth 6 with bigger speed, hydraulic pressure sacculus 27 can play good shock absorption, and substantially can not produce rebound effect; Simultaneously in order to prevent hydraulic pressure sacculus 27 overpressure failure, spring safety valve 28 also it is provided with between hydraulic pressure sacculus 27 and low pressure accumulator 18, once hydraulic pressure sacculus 27 superpressure spring safety valve 28 will be opened automatically, and by low pressure accumulator 18 compensator or trimmer pressure, at this moment the hydraulic efficiency system of engine can be played certain supplementary function by hydraulic pressure sacculus 27. The upper left side of described hydraulic pressure sacculus 27 is provided with the dead band oil mouth 34 of inclination, its place straight line and hydraulic pressure sacculus 27 are tangent, dead band oil mouth 34 and compress energy storage device 4 return a magnetic valve 35 be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead band B being in when the end of piston component between the 2nd oil mouth 6 and hydraulic pressure sacculus 27, return a magnetic valve 35 make piston component return to the ideally stop region A between the 2nd oil mouth 6 and the first oil mouth 5 to start next stroke by opening dead band.
The effect of high pressure accumulator 8 is: one is ensure that when engine shutdown, and piston component can stop at bottom dead center position, reduces and wriggles; When two is under engine starting duty and situation of catching fire occurs, promote piston component to be returned to bottom dead center position, enable engine continue to start next circulation.
This engine also comprises position detecting system, signal when described position detecting system arrives top dead center position, bottom dead center position and feed forward position by linear displacement sensor and location triggered sensor detection piston component, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve 3, feed forward position is determined according to the speed value cooperation position detection system of piston.
Described injection system comprises injection pump 31, common rail pipe 32, electric-controlled fuel injector 33, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump 29, fuel oil enters injection pump 31 through purifier 30, after the compression of injection pump 31, low pressure oil turns into high-pressure oil, and inputted common rail pipe 32 by injection pump 31, in common rail pipe 32, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently by relatively stable and have certain pressure high-pressure oil input electric-controlled fuel injector 33 in, wait the oil spout instruction of electronically controlled unit.
This engine is also provided with constant-voltage driving system, and described constant-voltage driving system mainly comprises engine and hydraulic variable motor, by motor driving moment and load resistance square, maintains and exports the constant of oil liquid pressure. By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure. Hydraulic variable motor is connected with load machinery, and both rotating speeds are equal; In steady operation situation, motor driving moment is equal with load resistance square size, and direction is contrary, and when resistance becomes big, motor driving moment is less than load resistance square, and motor rotary speed is reduced. Owing to the flow of output hydraulic pressure oil is constant, the situation current downflow resistance that output hydraulic pressure oil increases in back pressure increases, thus causes the rising of pressure in system. Now, the variable mechanism of oil motor receives the feedback of this pressure raises signal and regulates, and self discharge capacity is increased, increases the flow of motor when rotating speed reduces, thus reduce oil stream dynamic resistance, maintain engine and export the constant of oil liquid pressure. Meanwhile, owing to discharge capacity increases, motor driving moment also increases thereupon, and balances each other with load resistance square gradually, and system realizes reaching steady-working state again. Equally, when load resistance reduces, when fluid motor-driven moment is greater than load resistance square, motor rotary speed raises, and causes the reduction of pressure in hydraulic efficiency system. Now, hydraulic variable motor discharge capacity regulates to the direction reduced, and driving moment and load resistance square are balanced each other, pressure constant in keeping system while realizing system stability work.
Described engine also comprises start control system, normal operation Controlling System and fire controll system:
Start control system, the control for engine starting duty: after start signal sends, opens starting valve 23 and reducing valve 22, and compress energy storage device 4 is owing to being connected with high pressure accumulator 8 and pressure raises, and the compression ratio of engine is improved; The signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve 3 and the 2nd control valve 2 are opened, piston component is under the effect of compress energy storage device 4, start compression stroke, if piston component being detected not in lower dead center, first level control valve 17 is opened back, hydraulic efficiency oil in pump chamber 7 and compression chamber 1 is released by low pressure oil way 26, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator 8 pressure, close back level control valve 17, then start compression stroke; When the speed of piston is decreased to a certain set(ting)value, think that it arrives feed forward position, now the 2nd control valve 2 is closed, when piston arrives after top dead center, first control valve 3 is closed, and returns level control valve 17 and opens, the control mode that the first control valve 3 and the 2nd control valve 2 substep are closed by this kind, both ensure that the speed of compression stroke, turn reduce the resistance of expansion stroke; Piston component returns to after bottom dead center again, close back level control valve 17, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when the 2nd control valve 2 start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature are all lower, then repeat above-described working process, until after pressure and temperature meets ignition condition, starting to enter the control process of normal operation.
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve 23 and reducing valve 22, first control valve 3 keeps normal open state, after start signal sends, 2nd control valve 2 is opened, first hydraulic efficiency oil in compress energy storage device 4 enter compression chamber 1 by the 2nd control valve 2, piston component is promoted to move to top dead center, after the first oil mouth 5 is opened, 2nd control valve 2 is closed, it is connected by the first oil mouth 5 between compression chamber 1 and compress energy storage device 4, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is substantially equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve 2 is opened again.
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve 3, and open reducing valve 22 and return level control valve 17, piston component is made to be returned to bottom dead center position, then the first control valve 3 is opened, wait next starting impulse signal, engine moves according to normal operating cycle again.
Described 2nd control valve 2 adopts peak flow to be 200L/min, opens the high-frequency electrohydraulic servo-valve that pulsewidth is 15ms, electrohydraulic servo valve is that one accepts analog quantity electric control signal, export with the hydrauliccontrol valve of electric control signal size and change in polarity and response fast, there is dynamic response and good static characteristics fast, as: resolving power height, stagnant ring are little, the linear lag is good. The peak flow of the 2nd control valve 2, when use peak flow be 200L/min, open pulsewidth be 15ms electrohydraulic servo valve time, about the acceleration segment length of piston component can be increased to original 6 times, the compression stroke time used obviously reduces, thus make the motion cycle reduce 10ms nearly than originally, improve the maximum functional frequency of engine significantly, achieve unexpected effect.
Embodiment 3: a kind of water generating station attending device with optimal control system as Figure 1-3, the engine comprising maintenance cart and being connected with maintenance cart, engine is for driving maintenance cart, and engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve 9, power piston 10, combustion chamber 11, oil thrower 12, scavenging port 13, resetting piston 15, compression piston 19, hydraulic part comprises compression chamber 1, pump chamber 7, returning chamber, position 14 and hydraulic circuit, described compression chamber 1 is arranged at the rear portion of engine, is provided with the first oil mouth 5 thereon, 2nd oil mouth 6, described first oil mouth 5, 2nd oil mouth 6 is connected with compress energy storage device 4 with the 2nd control valve 2 by the first control valve 3 respectively, described pump chamber 7 is connected with high-pressure oil passage 25 with low pressure oil way 26 respectively by check valve 9, high-pressure oil passage 25 is for engine loading fuel feeding, being provided with back level control valve 17 and low pressure accumulator 18 on low pressure oil way 26, on time level control valve 17, also bypass is provided with oil return check valve 21, chamber, described time position 14 is directly connected with high pressure accumulator 8, is provided with reducing valve 22 at described high pressure accumulator 8 to the oil line of cylinder body, described compress energy storage device 4 is connected by oil line with described high pressure accumulator 8, and the oil line between described compress energy storage device 4 and described high pressure accumulator 8 is also provided with starting valve 23, described high-pressure oil passage 25 is connected with a load energy storage 24, leads to a road and be connected with described compress energy storage device 4 after described reducing valve 22, described injection system is high-pressure co-rail electric-controlling injection system.
The end of engine is provided with hydraulic pressure sacculus 27, the pressure oil of the certain pressure injected in advance it is full of in hydraulic pressure sacculus 27, it is connected with low pressure accumulator 18 by oil line bottom it, when load pressure reduces suddenly or fuel charge overshoot causes piston to cross the 2nd oil mouth 6 with bigger speed, hydraulic pressure sacculus 27 can play good shock absorption, and substantially can not produce rebound effect; Simultaneously in order to prevent hydraulic pressure sacculus 27 overpressure failure, spring safety valve 28 also it is provided with between hydraulic pressure sacculus 27 and low pressure accumulator 18, once hydraulic pressure sacculus 27 superpressure spring safety valve 28 will be opened automatically, and by low pressure accumulator 18 compensator or trimmer pressure, at this moment the hydraulic efficiency system of engine can be played certain supplementary function by hydraulic pressure sacculus 27. The upper left side of described hydraulic pressure sacculus 27 is provided with the dead band oil mouth 34 of inclination, its place straight line and hydraulic pressure sacculus 27 are tangent, dead band oil mouth 34 and compress energy storage device 4 return a magnetic valve 35 be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead band B being in when the end of piston component between the 2nd oil mouth 6 and hydraulic pressure sacculus 27, return a magnetic valve 35 make piston component return to the ideally stop region A between the 2nd oil mouth 6 and the first oil mouth 5 to start next stroke by opening dead band.
The effect of high pressure accumulator 8 is: one is ensure that when engine shutdown, and piston component can stop at bottom dead center position, reduces and wriggles; When two is under engine starting duty and situation of catching fire occurs, promote piston component to be returned to bottom dead center position, enable engine continue to start next circulation.
This engine also comprises position detecting system, signal when described position detecting system arrives top dead center position, bottom dead center position and feed forward position by linear displacement sensor and location triggered sensor detection piston component, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve 3, feed forward position is determined according to the speed value cooperation position detection system of piston.
Described injection system comprises injection pump 31, common rail pipe 32, electric-controlled fuel injector 33, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump 29, fuel oil enters injection pump 31 through purifier 30, after the compression of injection pump 31, low pressure oil turns into high-pressure oil, and inputted common rail pipe 32 by injection pump 31, in common rail pipe 32, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently by relatively stable and have certain pressure high-pressure oil input electric-controlled fuel injector 33 in, wait the oil spout instruction of electronically controlled unit.
This engine is also provided with constant-voltage driving system, and described constant-voltage driving system mainly comprises engine and hydraulic variable motor, by motor driving moment and load resistance square, maintains and exports the constant of oil liquid pressure. By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure. Hydraulic variable motor is connected with load machinery, and both rotating speeds are equal; In steady operation situation, motor driving moment is equal with load resistance square size, and direction is contrary, and when resistance becomes big, motor driving moment is less than load resistance square, and motor rotary speed is reduced. Owing to the flow of output hydraulic pressure oil is constant, the situation current downflow resistance that output hydraulic pressure oil increases in back pressure increases, thus causes the rising of pressure in system. Now, the variable mechanism of oil motor receives the feedback of this pressure raises signal and regulates, and self discharge capacity is increased, increases the flow of motor when rotating speed reduces, thus reduce oil stream dynamic resistance, maintain engine and export the constant of oil liquid pressure. Meanwhile, owing to discharge capacity increases, motor driving moment also increases thereupon, and balances each other with load resistance square gradually, and system realizes reaching steady-working state again. Equally, when load resistance reduces, when fluid motor-driven moment is greater than load resistance square, motor rotary speed raises, and causes the reduction of pressure in hydraulic efficiency system. Now, hydraulic variable motor discharge capacity regulates to the direction reduced, and driving moment and load resistance square are balanced each other, pressure constant in keeping system while realizing system stability work.
Described engine also comprises start control system, normal operation Controlling System and fire controll system:
Start control system, the control for engine starting duty: after start signal sends, opens starting valve 23 and reducing valve 22, and compress energy storage device 4 is owing to being connected with high pressure accumulator 8 and pressure raises, and the compression ratio of engine is improved; The signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve 3 and the 2nd control valve 2 are opened, piston component is under the effect of compress energy storage device 4, start compression stroke, if piston component being detected not in lower dead center, first level control valve 17 is opened back, hydraulic efficiency oil in pump chamber 7 and compression chamber 1 is released by low pressure oil way 26, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator 8 pressure, close back level control valve 17, then start compression stroke; When the speed of piston is decreased to a certain set(ting)value, think that it arrives feed forward position, now the 2nd control valve 2 is closed, when piston arrives after top dead center, first control valve 3 is closed, and returns level control valve 17 and opens, the control mode that the first control valve 3 and the 2nd control valve 2 substep are closed by this kind, both ensure that the speed of compression stroke, turn reduce the resistance of expansion stroke; Piston component returns to after bottom dead center again, close back level control valve 17, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when the 2nd control valve 2 start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature are all lower, then repeat above-described working process, until after pressure and temperature meets ignition condition, starting to enter the control process of normal operation.
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve 23 and reducing valve 22, first control valve 3 keeps normal open state, after start signal sends, 2nd control valve 2 is opened, first hydraulic efficiency oil in compress energy storage device 4 enter compression chamber 1 by the 2nd control valve 2, piston component is promoted to move to top dead center, after the first oil mouth 5 is opened, 2nd control valve 2 is closed, it is connected by the first oil mouth 5 between compression chamber 1 and compress energy storage device 4, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is substantially equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve 2 is opened again.
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve 3, and open reducing valve 22 and return level control valve 17, piston component is made to be returned to bottom dead center position, then the first control valve 3 is opened, wait next starting impulse signal, engine moves according to normal operating cycle again.
Described 2nd control valve 2 adopts peak flow to be 220L/min, opens the high-frequency electrohydraulic servo-valve that pulsewidth is 20ms, electrohydraulic servo valve is that one accepts analog quantity electric control signal, export with the hydrauliccontrol valve of electric control signal size and change in polarity and response fast, there is dynamic response and good static characteristics fast, as: resolving power height, stagnant ring are little, the linear lag is good. The peak flow of the 2nd control valve 2, when use peak flow be 220L/min, open pulsewidth be 20ms electrohydraulic servo valve time, about the acceleration segment length of piston component can be increased to original 7 times, the compression stroke time used obviously reduces, thus make the motion cycle reduce 12ms nearly than originally, improve the maximum functional frequency of engine significantly, achieve unexpected effect.
Embodiment 4: a kind of water generating station attending device with optimal control system as Figure 1-3, the engine comprising maintenance cart and being connected with maintenance cart, engine is for driving maintenance cart, and engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve 9, power piston 10, combustion chamber 11, oil thrower 12, scavenging port 13, resetting piston 15, compression piston 19, hydraulic part comprises compression chamber 1, pump chamber 7, returning chamber, position 14 and hydraulic circuit, described compression chamber 1 is arranged at the rear portion of engine, is provided with the first oil mouth 5 thereon, 2nd oil mouth 6, described first oil mouth 5, 2nd oil mouth 6 is connected with compress energy storage device 4 with the 2nd control valve 2 by the first control valve 3 respectively, described pump chamber 7 is connected with high-pressure oil passage 25 with low pressure oil way 26 respectively by check valve 9, high-pressure oil passage 25 is for engine loading fuel feeding, being provided with back level control valve 17 and low pressure accumulator 18 on low pressure oil way 26, on time level control valve 17, also bypass is provided with oil return check valve 21, chamber, described time position 14 is directly connected with high pressure accumulator 8, is provided with reducing valve 22 at described high pressure accumulator 8 to the oil line of cylinder body, described compress energy storage device 4 is connected by oil line with described high pressure accumulator 8, and the oil line between described compress energy storage device 4 and described high pressure accumulator 8 is also provided with starting valve 23, described high-pressure oil passage 25 is connected with a load energy storage 24, leads to a road and be connected with described compress energy storage device 4 after described reducing valve 22, described injection system is high-pressure co-rail electric-controlling injection system.
The end of engine is provided with hydraulic pressure sacculus 27, the pressure oil of the certain pressure injected in advance it is full of in hydraulic pressure sacculus 27, it is connected with low pressure accumulator 18 by oil line bottom it, when load pressure reduces suddenly or fuel charge overshoot causes piston to cross the 2nd oil mouth 6 with bigger speed, hydraulic pressure sacculus 27 can play good shock absorption, and substantially can not produce rebound effect; Simultaneously in order to prevent hydraulic pressure sacculus 27 overpressure failure, spring safety valve 28 also it is provided with between hydraulic pressure sacculus 27 and low pressure accumulator 18, once hydraulic pressure sacculus 27 superpressure spring safety valve 28 will be opened automatically, and by low pressure accumulator 18 compensator or trimmer pressure, at this moment the hydraulic efficiency system of engine can be played certain supplementary function by hydraulic pressure sacculus 27. The upper left side of described hydraulic pressure sacculus 27 is provided with the dead band oil mouth 34 of inclination, its place straight line and hydraulic pressure sacculus 27 are tangent, dead band oil mouth 34 and compress energy storage device 4 return a magnetic valve 35 be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead band B being in when the end of piston component between the 2nd oil mouth 6 and hydraulic pressure sacculus 27, return a magnetic valve 35 make piston component return to the ideally stop region A between the 2nd oil mouth 6 and the first oil mouth 5 to start next stroke by opening dead band.
The effect of high pressure accumulator 8 is: one is ensure that when engine shutdown, and piston component can stop at bottom dead center position, reduces and wriggles; When two is under engine starting duty and situation of catching fire occurs, promote piston component to be returned to bottom dead center position, enable engine continue to start next circulation.
This engine also comprises position detecting system, signal when described position detecting system arrives top dead center position, bottom dead center position and feed forward position by linear displacement sensor and location triggered sensor detection piston component, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve 3, feed forward position is determined according to the speed value cooperation position detection system of piston.
Described injection system comprises injection pump 31, common rail pipe 32, electric-controlled fuel injector 33, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump 29, fuel oil enters injection pump 31 through purifier 30, after the compression of injection pump 31, low pressure oil turns into high-pressure oil, and inputted common rail pipe 32 by injection pump 31, in common rail pipe 32, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently by relatively stable and have certain pressure high-pressure oil input electric-controlled fuel injector 33 in, wait the oil spout instruction of electronically controlled unit.
This engine is also provided with constant-voltage driving system, and described constant-voltage driving system mainly comprises engine and hydraulic variable motor, by motor driving moment and load resistance square, maintains and exports the constant of oil liquid pressure. By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure. Hydraulic variable motor is connected with load machinery, and both rotating speeds are equal; In steady operation situation, motor driving moment is equal with load resistance square size, and direction is contrary, and when resistance becomes big, motor driving moment is less than load resistance square, and motor rotary speed is reduced. Owing to the flow of output hydraulic pressure oil is constant, the situation current downflow resistance that output hydraulic pressure oil increases in back pressure increases, thus causes the rising of pressure in system. Now, the variable mechanism of oil motor receives the feedback of this pressure raises signal and regulates, and self discharge capacity is increased, increases the flow of motor when rotating speed reduces, thus reduce oil stream dynamic resistance, maintain engine and export the constant of oil liquid pressure. Meanwhile, owing to discharge capacity increases, motor driving moment also increases thereupon, and balances each other with load resistance square gradually, and system realizes reaching steady-working state again. Equally, when load resistance reduces, when fluid motor-driven moment is greater than load resistance square, motor rotary speed raises, and causes the reduction of pressure in hydraulic efficiency system. Now, hydraulic variable motor discharge capacity regulates to the direction reduced, and driving moment and load resistance square are balanced each other, pressure constant in keeping system while realizing system stability work.
Described engine also comprises start control system, normal operation Controlling System and fire controll system:
Start control system, the control for engine starting duty: after start signal sends, opens starting valve 23 and reducing valve 22, and compress energy storage device 4 is owing to being connected with high pressure accumulator 8 and pressure raises, and the compression ratio of engine is improved; The signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve 3 and the 2nd control valve 2 are opened, piston component is under the effect of compress energy storage device 4, start compression stroke, if piston component being detected not in lower dead center, first level control valve 17 is opened back, hydraulic efficiency oil in pump chamber 7 and compression chamber 1 is released by low pressure oil way 26, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator 8 pressure, close back level control valve 17, then start compression stroke; When the speed of piston is decreased to a certain set(ting)value, think that it arrives feed forward position, now the 2nd control valve 2 is closed, when piston arrives after top dead center, first control valve 3 is closed, and returns level control valve 17 and opens, the control mode that the first control valve 3 and the 2nd control valve 2 substep are closed by this kind, both ensure that the speed of compression stroke, turn reduce the resistance of expansion stroke; Piston component returns to after bottom dead center again, close back level control valve 17, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when the 2nd control valve 2 start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature are all lower, then repeat above-described working process, until after pressure and temperature meets ignition condition, starting to enter the control process of normal operation.
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve 23 and reducing valve 22, first control valve 3 keeps normal open state, after start signal sends, 2nd control valve 2 is opened, first hydraulic efficiency oil in compress energy storage device 4 enter compression chamber 1 by the 2nd control valve 2, piston component is promoted to move to top dead center, after the first oil mouth 5 is opened, 2nd control valve 2 is closed, it is connected by the first oil mouth 5 between compression chamber 1 and compress energy storage device 4, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is substantially equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve 2 is opened again.
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve 3, and open reducing valve 22 and return level control valve 17, piston component is made to be returned to bottom dead center position, then the first control valve 3 is opened, wait next starting impulse signal, engine moves according to normal operating cycle again.
Described 2nd control valve 2 adopts peak flow to be 270L/min, opens the high-frequency electrohydraulic servo-valve that pulsewidth is 25ms, electrohydraulic servo valve is that one accepts analog quantity electric control signal, export with the hydrauliccontrol valve of electric control signal size and change in polarity and response fast, there is dynamic response and good static characteristics fast, as: resolving power height, stagnant ring are little, the linear lag is good. The peak flow of the 2nd control valve 2, when use peak flow be 270L/min, open pulsewidth be 25ms electrohydraulic servo valve time, about the acceleration segment length of piston component can be increased to original 7.5 times, the compression stroke time used obviously reduces, thus make the motion cycle reduce 12ms nearly than originally, improve the maximum functional frequency of engine significantly, achieve unexpected effect.
Embodiment 5: a kind of water generating station attending device with optimal control system as Figure 1-3, the engine comprising maintenance cart and being connected with maintenance cart, engine is for driving maintenance cart, and engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve 9, power piston 10, combustion chamber 11, oil thrower 12, scavenging port 13, resetting piston 15, compression piston 19, hydraulic part comprises compression chamber 1, pump chamber 7, returning chamber, position 14 and hydraulic circuit, described compression chamber 1 is arranged at the rear portion of engine, is provided with the first oil mouth 5 thereon, 2nd oil mouth 6, described first oil mouth 5, 2nd oil mouth 6 is connected with compress energy storage device 4 with the 2nd control valve 2 by the first control valve 3 respectively, described pump chamber 7 is connected with high-pressure oil passage 25 with low pressure oil way 26 respectively by check valve 9, high-pressure oil passage 25 is for engine loading fuel feeding, being provided with back level control valve 17 and low pressure accumulator 18 on low pressure oil way 26, on time level control valve 17, also bypass is provided with oil return check valve 21, chamber, described time position 14 is directly connected with high pressure accumulator 8, is provided with reducing valve 22 at described high pressure accumulator 8 to the oil line of cylinder body, described compress energy storage device 4 is connected by oil line with described high pressure accumulator 8, and the oil line between described compress energy storage device 4 and described high pressure accumulator 8 is also provided with starting valve 23, described high-pressure oil passage 25 is connected with a load energy storage 24, leads to a road and be connected with described compress energy storage device 4 after described reducing valve 22, described injection system is high-pressure co-rail electric-controlling injection system.
The end of engine is provided with hydraulic pressure sacculus 27, the pressure oil of the certain pressure injected in advance it is full of in hydraulic pressure sacculus 27, it is connected with low pressure accumulator 18 by oil line bottom it, when load pressure reduces suddenly or fuel charge overshoot causes piston to cross the 2nd oil mouth 6 with bigger speed, hydraulic pressure sacculus 27 can play good shock absorption, and substantially can not produce rebound effect; Simultaneously in order to prevent hydraulic pressure sacculus 27 overpressure failure, spring safety valve 28 also it is provided with between hydraulic pressure sacculus 27 and low pressure accumulator 18, once hydraulic pressure sacculus 27 superpressure spring safety valve 28 will be opened automatically, and by low pressure accumulator 18 compensator or trimmer pressure, at this moment the hydraulic efficiency system of engine can be played certain supplementary function by hydraulic pressure sacculus 27. The upper left side of described hydraulic pressure sacculus 27 is provided with the dead band oil mouth 34 of inclination, its place straight line and hydraulic pressure sacculus 27 are tangent, dead band oil mouth 34 and compress energy storage device 4 return a magnetic valve 35 be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead band B being in when the end of piston component between the 2nd oil mouth 6 and hydraulic pressure sacculus 27, return a magnetic valve 35 make piston component return to the ideally stop region A between the 2nd oil mouth 6 and the first oil mouth 5 to start next stroke by opening dead band.
The effect of high pressure accumulator 8 is: one is ensure that when engine shutdown, and piston component can stop at bottom dead center position, reduces and wriggles; When two is under engine starting duty and situation of catching fire occurs, promote piston component to be returned to bottom dead center position, enable engine continue to start next circulation.
This engine also comprises position detecting system, signal when described position detecting system arrives top dead center position, bottom dead center position and feed forward position by linear displacement sensor and location triggered sensor detection piston component, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve 3, feed forward position is determined according to the speed value cooperation position detection system of piston.
Described injection system comprises injection pump 31, common rail pipe 32, electric-controlled fuel injector 33, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump 29, fuel oil enters injection pump 31 through purifier 30, after the compression of injection pump 31, low pressure oil turns into high-pressure oil, and inputted common rail pipe 32 by injection pump 31, in common rail pipe 32, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently by relatively stable and have certain pressure high-pressure oil input electric-controlled fuel injector 33 in, wait the oil spout instruction of electronically controlled unit.
This engine is also provided with constant-voltage driving system, and described constant-voltage driving system mainly comprises engine and hydraulic variable motor, by motor driving moment and load resistance square, maintains and exports the constant of oil liquid pressure. By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure. Hydraulic variable motor is connected with load machinery, and both rotating speeds are equal; In steady operation situation, motor driving moment is equal with load resistance square size, and direction is contrary, and when resistance becomes big, motor driving moment is less than load resistance square, and motor rotary speed is reduced. Owing to the flow of output hydraulic pressure oil is constant, the situation current downflow resistance that output hydraulic pressure oil increases in back pressure increases, thus causes the rising of pressure in system. Now, the variable mechanism of oil motor receives the feedback of this pressure raises signal and regulates, and self discharge capacity is increased, increases the flow of motor when rotating speed reduces, thus reduce oil stream dynamic resistance, maintain engine and export the constant of oil liquid pressure. Meanwhile, owing to discharge capacity increases, motor driving moment also increases thereupon, and balances each other with load resistance square gradually, and system realizes reaching steady-working state again. Equally, when load resistance reduces, when fluid motor-driven moment is greater than load resistance square, motor rotary speed raises, and causes the reduction of pressure in hydraulic efficiency system. Now, hydraulic variable motor discharge capacity regulates to the direction reduced, and driving moment and load resistance square are balanced each other, pressure constant in keeping system while realizing system stability work.
Described engine also comprises start control system, normal operation Controlling System and fire controll system:
Start control system, the control for engine starting duty: after start signal sends, opens starting valve 23 and reducing valve 22, and compress energy storage device 4 is owing to being connected with high pressure accumulator 8 and pressure raises, and the compression ratio of engine is improved; The signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve 3 and the 2nd control valve 2 are opened, piston component is under the effect of compress energy storage device 4, start compression stroke, if piston component being detected not in lower dead center, first level control valve 17 is opened back, hydraulic efficiency oil in pump chamber 7 and compression chamber 1 is released by low pressure oil way 26, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator 8 pressure, close back level control valve 17, then start compression stroke; When the speed of piston is decreased to a certain set(ting)value, think that it arrives feed forward position, now the 2nd control valve 2 is closed, when piston arrives after top dead center, first control valve 3 is closed, and returns level control valve 17 and opens, the control mode that the first control valve 3 and the 2nd control valve 2 substep are closed by this kind, both ensure that the speed of compression stroke, turn reduce the resistance of expansion stroke; Piston component returns to after bottom dead center again, close back level control valve 17, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when the 2nd control valve 2 start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature are all lower, then repeat above-described working process, until after pressure and temperature meets ignition condition, starting to enter the control process of normal operation.
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve 23 and reducing valve 22, first control valve 3 keeps normal open state, after start signal sends, 2nd control valve 2 is opened, first hydraulic efficiency oil in compress energy storage device 4 enter compression chamber 1 by the 2nd control valve 2, piston component is promoted to move to top dead center, after the first oil mouth 5 is opened, 2nd control valve 2 is closed, it is connected by the first oil mouth 5 between compression chamber 1 and compress energy storage device 4, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is substantially equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve 2 is opened again.
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve 3, and open reducing valve 22 and return level control valve 17, piston component is made to be returned to bottom dead center position, then the first control valve 3 is opened, wait next starting impulse signal, engine moves according to normal operating cycle again.
Described 2nd control valve 2 adopts peak flow to be 230L/min, opens the high-frequency electrohydraulic servo-valve that pulsewidth is 30ms, electrohydraulic servo valve is that one accepts analog quantity electric control signal, export with the hydrauliccontrol valve of electric control signal size and change in polarity and response fast, there is dynamic response and good static characteristics fast, as: resolving power height, stagnant ring are little, the linear lag is good. The peak flow of the 2nd control valve 2, when use peak flow be 230L/min, open pulsewidth be 30ms electrohydraulic servo valve time, about the acceleration segment length of piston component can be increased to original 8 times, the compression stroke time used obviously reduces, thus make the motion cycle reduce 14ms nearly than originally, improve the maximum functional frequency of engine significantly, achieve unexpected effect.
Finally should be noted that; above embodiment is only in order to illustrate the technical scheme of the present invention; but not limiting the scope of the invention; although having done to explain to the present invention with reference to better embodiment; it will be understood by those within the art that; the technical scheme of the present invention can be modified or equivalent replacement, and not depart from essence and the scope of technical solution of the present invention.
Claims (2)
1. one kind has the water generating station attending device of optimal control system, the engine comprising maintenance cart and be connected with maintenance cart, engine is for driving maintenance cart, it is characterized in that, engine comprises power section, injection system and hydraulic part, described power section comprises air inlet check valve, power piston, combustion chamber, oil thrower, scavenging port, hydraulic part comprises compression chamber, pump chamber, return chamber, position and hydraulic circuit, described compression chamber is arranged at the rear portion of engine, it is provided with the first oil mouth thereon, 2nd oil mouth, described first oil mouth, 2nd oil mouth is connected with compress energy storage device with the 2nd control valve by the first control valve respectively, described pump chamber is connected with high-pressure oil passage with low pressure oil way respectively by check valve, high-pressure oil passage is used for engine loading fuel feeding, low pressure oil way is provided with back level control valve and low pressure accumulator, return bypass on level control valve and it is provided with oil return check valve, chamber, described time position is directly connected with high pressure accumulator, is provided with reducing valve on the oil line of described high pressure accumulator to cylinder body, starting duty and catch fire operating mode time reducing valve be held open, during nominal situation reducing valve close, described compress energy storage device is connected by oil line with high pressure accumulator, and is provided with starting valve on oil line between described compress energy storage device and high pressure accumulator, and for improving the compression ratio of engine during start operating performance, during nominal situation, starting valve cuts out, described high-pressure oil passage is connected with a load energy storage, leads to a road and be connected with described compress energy storage device after reducing valve, the end of engine is provided with hydraulic pressure sacculus, is full of the pressure oil injected in advance, is connected with low pressure accumulator by oil line, is also provided with spring safety valve between hydraulic pressure sacculus and low pressure accumulator bottom it in hydraulic pressure sacculus, the upper left side of described hydraulic pressure sacculus is provided with the dead band You Kou of inclination, its place straight line and hydraulic pressure sacculus are tangent, dead band oil mouth and compress energy storage device return a magnetic valve be connected by being arranged on dead band between the two, in operating mode of catching fire, during the dead zone location being in when the end of piston component between the 2nd oil mouth and hydraulic pressure sacculus, return a magnetic valve make piston component return to the ideally stop region between the 2nd oil mouth and the first oil mouth to start next stroke by opening dead band, described injection system is high-pressure co-rail electric-controlling injection system, comprise injection pump, common rail pipe, electric-controlled fuel injector, pressure transmitter and electronically controlled unit, during engine operation, under the effect of transfer pump, fuel oil enters injection pump through purifier, after the compression of injection pump, low pressure oil turns into high-pressure oil, and inputted common rail pipe by injection pump, in common rail pipe, electronically controlled unit receives the feedback of pressure transmitter and controls pressure limiting valve, to regulate force value in rail and to make it keep constant, subsequently high-pressure oil is inputted in electric-controlled fuel injector, wait the oil spout instruction of electronically controlled unit,
Described engine also comprises position detecting system, position detecting system is detected by linear displacement sensor and location triggered sensor and sends signal when piston component arrives top dead center position, bottom dead center position and feed forward position, the side of feed forward position close top dead center position between top dead center position and bottom dead center position, for the closedown of start operating performance piston compression stroke control first control valve, feed forward position is determined according to the speed value cooperation position detection system of piston; Described engine also comprises constant-voltage driving system, and described constant-voltage driving system comprises engine and hydraulic variable motor, keeps exporting the constant of oil liquid pressure by motor driving moment and load resistance square; By exporting, high-voltage oil liquid drives hydraulic variable motor, and is connected with load by deceleration device, and its discharge capacity regulates automatically with the change of operating pressure;
Described engine also comprises normal operation Controlling System and fire controll system:
Normal operation Controlling System, control for engine nominal situation: after entering nominal situation, close starting valve and reducing valve, first control valve keeps normal open state, after start signal sends, 2nd control valve is opened, first hydraulic efficiency oil in compress energy storage device enter compression chamber by the 2nd control valve, piston component is promoted to move to top dead center, after the first oil mouth is opened, 2nd control valve is closed, it is connected by the first oil mouth between compression chamber and compress energy storage device, when piston component arrives oil spout position, trigger sensor, produce fuel injection signal, and control fuel charge and make the ratio of compression time and Bulking Time equal the ratio of volume change of hydro-pump two strokes, so that expansion flow is equal with compression flow, to reduce the pulsation of engine output flow, fuel injection process is completed by injection system, at near top dead center, fuel combustion heat release, piston component returns to lower dead center under the effect of cylinder pressure, and it is stabilized in lower dead center before the 2nd control valve is opened again,
Fire controll system, control for engine fire operating mode: in engine working process, after start signal sends, all piston component position is carried out one-time detection, if engine frequency and frequency change rate are all less than set(ting)value, then detect the position of piston component, if piston component is not at bottom dead center position, and cylinder temperature cylinder pressure is less than value of catching fire, then think that engine catches fire in a upper circulation, now first close the first control valve, and open reducing valve and return level control valve, piston component is made to be returned to bottom dead center position, then the first control valve is opened, wait next starting impulse signal, engine moves according to normal operating cycle again,
Described 2nd control valve employing peak flow is the high-frequency electrohydraulic servo-valve of 250L/min, and it opens pulsewidth is 10ms.
2. a kind of water generating station attending device with optimal control system according to claim 1, it is characterized in that, also comprise start control system, control for engine starting duty: after start signal sends, open starting valve and reducing valve, compress energy storage device is owing to being connected with high pressure accumulator and pressure raises, and the compression ratio of engine is improved, the signal of displacement sensor is detected by control unit of engine, if detected result display piston component is in lower dead center, then the first control valve and the 2nd control valve are opened, piston component is under the effect of compress energy storage device, start compression stroke, if piston component being detected not in lower dead center, first level control valve is opened back, hydraulic efficiency oil in pump chamber and compression chamber is released by low pressure oil way, piston component is made to be returned to bottom dead center position under the effect of high pressure accumulator pressure, close back level control valve, then start compression stroke, when piston arrives feed forward position, 2nd control valve is closed, when piston arrives after top dead center, first control valve is closed, return level control valve to open, piston component returns to after bottom dead center again, close back level control valve, piston component completes a working cycle, pressure and temperature value in cylinder when recording and analyses assembly arrives top dead center in this process, when frequency valve start signal sends again, judge whether cylinder pressure and the temperature of a upper circulation record meet diesel-fuel ignition condition, if in-cylinder pressure and temperature do not meet ignition condition, then repeat above-described working process, until after pressure and temperature meets ignition condition, start to enter the control process of normal operation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610041631.7A CN105649764A (en) | 2016-01-21 | 2016-01-21 | Maintenance device with optimized control system for hydroelectric power station |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610041631.7A CN105649764A (en) | 2016-01-21 | 2016-01-21 | Maintenance device with optimized control system for hydroelectric power station |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105649764A true CN105649764A (en) | 2016-06-08 |
Family
ID=56487738
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610041631.7A Withdrawn CN105649764A (en) | 2016-01-21 | 2016-01-21 | Maintenance device with optimized control system for hydroelectric power station |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105649764A (en) |
-
2016
- 2016-01-21 CN CN201610041631.7A patent/CN105649764A/en not_active Withdrawn
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6470677B2 (en) | Free piston engine system with direct drive hydraulic output | |
| US20120137667A1 (en) | Regenerative Hydraulic Pump | |
| CN102305222B (en) | Electro-hydraulic variable valve device with energy accumulator buffer function and energy storage method thereof | |
| CN114458663B (en) | Energy control method based on hydraulic pile hammer | |
| CN104806354A (en) | Free piston internal combustion generation power system with adjustable compression ratio | |
| CN105649764A (en) | Maintenance device with optimized control system for hydroelectric power station | |
| CN105649767A (en) | Rubbish classifying and collecting device with fast starting function | |
| CN105507318A (en) | Novel efficient pile driving device | |
| CN105604691B (en) | High-efficient road watering device | |
| CN105649762A (en) | Maintenance device with quick start function for solar power generation field | |
| CN105649763A (en) | Mountain cross-country device with high output torque and low noise | |
| CN105649768A (en) | Mobile maintenance station with high output torque and low noise | |
| CN105649766A (en) | Geological sampling device with high output torque and low noise | |
| CN105626246A (en) | Ramming device provided with optimized control system and used for construction | |
| CN105649769A (en) | Fruit collecting and transporting device with high output torque and low noise | |
| CN105626245A (en) | River pollution treatment device with quick start function | |
| JP2630931B2 (en) | Fuel injection control device for internal combustion engine | |
| CN105649765A (en) | Sewage treatment device with optimized control system | |
| CN105625146B (en) | A kind of path formation device of height output moment of torsion low noise | |
| CN105715390A (en) | Novel and efficient material transportation device | |
| CN105604122A (en) | Digging device with rapid start function | |
| CN105673196A (en) | Scenic patrol device with optimized control system | |
| CN105715365A (en) | Novel efficient transformer substation maintaining device | |
| CN105706618A (en) | Landscaping device with rapid starting function | |
| CN105626249B (en) | High-output-torque low-noise petroleum transportation device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WW01 | Invention patent application withdrawn after publication | ||
| WW01 | Invention patent application withdrawn after publication |
Application publication date: 20160608 |