CN110939506A - Split type large expansion ratio engine - Google Patents
Split type large expansion ratio engine Download PDFInfo
- Publication number
- CN110939506A CN110939506A CN201911367056.XA CN201911367056A CN110939506A CN 110939506 A CN110939506 A CN 110939506A CN 201911367056 A CN201911367056 A CN 201911367056A CN 110939506 A CN110939506 A CN 110939506A
- Authority
- CN
- China
- Prior art keywords
- air
- gas
- working
- expansion
- rotor
- 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.)
- Pending
Links
Images
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
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
- F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
- F02B33/22—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with pumping cylinder situated at side of working cylinder, e.g. the cylinders being parallel
-
- 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
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/06—Engines with prolonged expansion in compound cylinders
- F02B41/08—Two-stroke compound engines
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The invention discloses a split type large expansion ratio engine and a regulation and control method, belonging to the field of engines and comprising a gas compression device, a high-pressure pipeline, a high-pressure gas tank, an expansion acting device and a control unit; the gas compression device provides high-pressure gas to the high-pressure gas tank through the high-pressure pipeline, the high-pressure gas tank can keep constant pressure, reduce air pressure pulsation and provide the high-pressure gas to the expansion acting device, the radiating unit can be connected in series on the pipeline to control the temperature of the compressed gas, the control unit can control the temperature of the compressed gas, the pump air quantity and the air quantity needed by the expansion acting device can be balanced, the air pressure and the compression ratio in the tank are kept constant at preset values, the engine can use different fuels by changing the compression ratio and the temperature of the compressed gas, and the compression ratio can be improved. Through a certain technical scheme and a regulation and control method, the expansion ratio of the engine can be easily realized to be larger than the compression ratio at low cost under various working conditions, and the super-large expansion ratio is realized especially under the working condition of a small accelerator, so that the oil consumption is greatly reduced.
Description
Technical Field
The invention relates to the field of engines, in particular to a split type large expansion ratio engine.
Background
In a conventional otto-cycle internal combustion engine, four strokes are used in each cycle: the intake stroke, the compression stroke, the power stroke and the exhaust stroke are all completed in one cylinder, the compression stroke and the power stroke of the piston are equal and less than the length of the cylinder, and the compression ratio and the expansion ratio are equal and fixed. As a result, 1, when the working stroke of the piston is finished, the gas in the cylinder still has higher residual air pressure, and the high-temperature gas cannot be fully expanded to work, so that energy waste is caused, which is particularly shown under the working condition of a large throttle; in the common characteristic curve chart of the ordinary four-stroke engine, the larger the torque (accelerator) is, the more the fuel efficiency is sharply reduced when the torque (accelerator) is higher than a medium-high value at the same rotating speed. As a result, under the working condition of a small accelerator, the opening of a throttle valve of the gasoline engine is reduced, the air inflow per cycle is obviously reduced, but the air volume is consistent with that of a large accelerator at the end of compression, but the density is reduced, so that the temperature, the density and the air pressure of gas in a cylinder are greatly reduced during ignition combustion, and further the fuel efficiency is low; it can be seen in the universal characteristic curve chart of the common four-stroke engine that the torque (accelerator) is below a medium-high value under the same rotating speed, and the smaller the torque (accelerator), the lower the fuel efficiency; this is also true of diesel engines, because the air-fuel ratio changes. As a result 3, because the compression process is also carried out in the working cylinder, the high temperature generated in the compression process can not be effectively reduced, so that the compression ratio of the gasoline engine can only adopt a lower value, otherwise, knocking damage can be caused, and the low compression ratio means low fuel efficiency. As a result, at the end of the exhaust stroke, there is still a residual volume, the volume utilization rate is low, and exhaust gas is difficult to evacuate, which causes a series of problems. As a result 5, two internal combustion cylinders are required to complete one power stroke for one crankshaft revolution.
In fact, automobile engines on the market belong to an otto cycle internal combustion engine, gasoline engines are more, most of the engines run under the working condition of non-medium and high torque (accelerator) in most of time periods, so that the comprehensive fuel efficiency is very low, and particularly, the gasoline engines even reach less than 15%. If the fuel efficiency of the existing engine can be obviously improved, especially the fuel efficiency under the working condition of a medium-small accelerator is improved, the fuel efficiency control method has great significance for realizing energy conservation and emission reduction.
Other similar prior art
Atkinson cycle engine: similar to an otto cycle engine, the four-stroke engine belongs to a four-stroke engine, can realize that the expansion ratio is larger than the compression ratio, but reduces the air suction and compression strokes, sacrifices certain power performance, has a complex mechanical structure, poor reliability, unchangeable compression ratio, and can not effectively cool compressed gas, when the four-stroke engine is used for a gasoline engine, the compression ratio is lower, and the fuel efficiency is improved to a limit;
miller cycle engine: the expansion ratio is larger than the compression ratio, but the valve is closed early, and the valve is closed early before the end of the intake stroke. The defects are that the power of the engine is insufficient under high load, the compression ratio is reduced more under the working condition of a low accelerator, a complex gas distribution mechanism is needed, the compressed gas cannot be effectively cooled, the compression ratio is lower when the gas distribution mechanism is used for a gasoline engine, and the improvement of the fuel efficiency is limited;
chinese patent CN 102472152 a discloses a split-cycle air-hybrid engine with ignition and charging modes: the device belongs to a split type, namely compression and work are generated in different cylinders; the air distribution mechanism and the air distribution regulation are quite complex, the compression ratio is not fixed and is not stable, the normal work of the engine is not facilitated, and the improvement of the fuel efficiency is limited;
chinese patent CN107407190A discloses a split-cycle engine: the fuel-saving device belongs to a split type, the whole structure is complex, the air distribution mechanism and the air distribution regulation are quite complex, the compression ratio is not fixed and stable, the normal work of an engine is not facilitated, and the fuel efficiency is not improved much.
Chinese patent CN101608569A discloses an out-of-cylinder compression variable stroke engine which belongs to a split type, can output different powers in various stroke states by working, has a constant and pre-set compression ratio, can use different fuels, but has troublesome power output adjustment, can not obviously realize that the expansion ratio is larger than the compression ratio, and has limited improvement of fuel efficiency.
Chinese patent CN208153149U discloses an eccentric rotor engine, which belongs to a split rotor engine, and has the advantages of simple structure, convenient processing, assembly and combination, and reduced production cost. However, the circular arc-shaped air suction compression movable sheet is not reasonable, the reliability and the sealing performance are difficult to guarantee, the overall design is not reasonable and clear, the expansion ratio larger than the compression ratio cannot be obviously realized, and the improvement of the fuel efficiency is limited.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to solve the technical problem of providing a split type large-expansion-ratio engine, which separately performs compression and expansion work, and can realize that the expansion ratio is larger than the compression ratio at low cost under various working conditions by a certain technical means, particularly can realize that the compression ratio is not changed and the expansion ratio is far larger than the compression ratio under the working condition of a small accelerator, thereby greatly reducing the oil consumption.
In order to achieve the purpose, the invention adopts the following technical scheme:
the invention provides a split type large expansion ratio engine which comprises a gas compression device, a high-pressure gas tank and an expansion acting device, wherein the high-pressure gas tank is connected with the expansion acting device; the gas compression device provides compressed gas for the high-pressure gas tank, the high-pressure gas tank can store the compressed gas, has constant pressure and reduces pressure pulsation and provides the compressed gas for the expansion work-doing device, and the high-pressure gas tank also comprises a pipeline gas cavity or other gas cavities with the same function; the expansion working device comprises a stator, a rotor, an air inlet mechanism, an exhaust mechanism and an oil supply mechanism; the rotor is arranged in the stator, a closed working air cavity is formed between the stator and the rotor, the stator is provided with an air inlet mechanism and an air outlet mechanism for periodic air inlet and air outlet, and the oil supply mechanism and the air inlet mechanism synchronously supply fuel; the stator is cylindrical and consists of a cylinder body, an upper cylinder cover and a lower cylinder cover, the rotor is circular and is arranged in the stator, one or more movable scraping blades are arranged on the rotor, the diameter of the rotor is smaller than the inner diameter of the cylinder body, the circle center of the rotor is not coincident with the circle center of the stator, the circle center of the rotor is taken as a rotating shaft, the outer circle of the rotor is always in close contact with the inner wall of the cylinder body of the stator when the rotor rotates, two or a plurality of closed working air cavities are formed between the contact surface and the scraping blades and between the scraping blades and the scraping blades, the air inlet mechanism is a phase-control air inlet valve and is arranged on the cylinder body of the stator close to the contact surface, the exhaust mechanism, namely an exhaust hole is arranged on the other side close to the contact surface, the air inlet mechanism and the oil supply mechanism work together, a certain amount of compressed gas is injected when the working, exhaust gas is discharged from the exhaust hole when the working air cavity contracts; an air cavity communicating groove is formed between the contact surface and the maximum working air cavity on the inner wall of the stator, so that the working air cavity can smoothly exhaust air to the exhaust hole when being contracted, and the negative work of gas can be prevented.
The invention has the preferable technical scheme that the expansion acting device comprises a stator, a rotor, an air inlet mechanism, an air exhaust mechanism and an oil supply mechanism; the rotor is arranged in the stator, a closed working air cavity is formed between the stator and the rotor, the stator is provided with an air inlet mechanism and an air outlet mechanism for periodic air inlet and air outlet, and the oil supply mechanism and the air inlet mechanism synchronously supply fuel; the stator is cylindrical and consists of a cylinder body, an upper cylinder cover and a lower cylinder cover, a movable scraping blade is arranged on the cylinder body, the diameter of the rotor is smaller than the inner diameter of the cylinder body, the rotor is arranged in the stator, the center of the rotor is taken as the axis of a rotating shaft, the center of the rotor is not coincident with the axis, the far center point of the rotor is always in close contact with the inner wall of the cylinder body during rotation, and two closed working air cavities are formed between the contact surface and the scraping blade; the movable scraper is arranged in the scraper groove box and can freely extend out, the air inlet mechanism is a phase control air inlet valve and is arranged on the cylinder body close to the scraper, the exhaust mechanism, namely an exhaust hole, is arranged on the other side close to the scraper, the air inlet mechanism and the oil supply mechanism work together, a certain amount of compressed gas is injected when the working air cavity begins to grow, fuel with a certain proportion is sprayed, high-pressure fuel gas expands after ignition to push the rotor to do work outwards, the exhaust hole is communicated with the contracted working air cavity all the time, and waste gas is discharged from the exhaust hole when the working air cavity contracts.
The invention preferably adopts the technical scheme that the device also comprises a control unit; the control unit can balance the pumping capacity of the gas compression device and the gas demand of the expansion acting device, and make the gas pressure and the compression ratio in the tank constant in preset ranges; the expansion work-doing device comprises a cylinder body, a cylinder cover, a piston, a connecting rod, a crankshaft, a phase-controlled intake valve, an exhaust valve and an oil supply mechanism, and belongs to a piston type; the crankshaft rotates to drive the piston to reciprocate in the cylinder through the connecting rod, the phase control air inlet valve and the exhaust valve are arranged on the cylinder cover, the phase control air inlet valve and the oil supply mechanism work together, a certain amount of compressed gas is injected when a working air cavity begins to grow, a certain proportion of fuel is injected, high-pressure fuel gas expands after ignition to push the piston to work outwards, and the exhaust valve is opened to exhaust waste gas when the working air cavity contracts; the closing angle of the phase-control air inlet valve is variable, so that the air inflow per week is adjustable, compressed air is injected when a working air cavity is just started to be enlarged, the torsion and power output are changed by changing the air inflow per week of the expansion working device, the minimum volume of the working air cavity is set to be minimum as much as possible, the expansion working device can operate with small air inflow when the throttle is small, and finally the compression ratio is far greater than the compression ratio without basically changing under the working condition of the throttle; the minimum volume of the working air cavity refers to the volume sum of the working air cavity when the piston reaches the top dead center; the small air inflow refers to that the air inflow per week is small, and the natural state volume of the small air inflow per week is far smaller than the maximum volume of the working air cavity, so that the super-large expansion ratio is obtained; the natural state volume refers to the volume of compressed gas entering the cylinder in an uncompressed state; the closing angle refers to the angle of rotation of the air inlet valve from opening to closing of the crankshaft; the week refers to the time interval between two adjacent air intakes of the expansion work device.
The invention preferably adopts the technical scheme that the device also comprises a control unit; the control unit can balance the pumping capacity of the gas compression device and the gas demand of the expansion acting device, and make the gas pressure and the compression ratio in the tank constant in preset ranges; the phase-controlled air inlet valve closing angle of the expansion acting device is variable, so that the air inflow per week is adjustable, the torsion and power output are changed by changing the air inflow per week of the expansion acting device, the minimum ignition volume of a working air cavity is set to be minimum as far as possible, the expansion acting device can operate with small air inflow when a small accelerator is used, and finally the compression ratio under the working condition of the small accelerator is basically unchanged, and the expansion ratio is far larger than the compression ratio; the minimum ignition volume of the working air cavity refers to the minimum working air cavity volume capable of normally igniting; the week refers to the time interval between two adjacent air inlets of the expansion work-doing device; the small air inflow refers to that the air inflow per week is small, and the volume of the air inflow per week is far smaller than the maximum volume of the working air cavity in a natural state, so that the super-large expansion ratio is obtained; the natural state volume refers to the volume of compressed gas entering the cylinder in an uncompressed state; the closing angle refers to the angle of rotation of the air inlet valve from opening to closing of the rotating shaft.
The invention has the preferable technical scheme that the natural state volume of the maximum pumping air quantity per week of the gas compression device or the maximum air input per week of the expansion work-doing device is smaller than the maximum volume of the working air cavity, so that the expansion ratio is still larger than the compression ratio under the working condition of a large throttle; the natural state volume refers to the volume of the compressed gas entering the working air cavity in an uncompressed state, and the period of each week refers to the time interval between two adjacent air inlets of the expansion working device.
The invention has the preferable technical scheme that the phase-controlled air inlet valve of the expansion working device comprises a driving mechanism, a valve and a secondary valve; the valve is in a normally closed state under the action of the spring force, and the valve is opened towards the working air cavity and can resist the high pressure of the fuel gas in the cylinder so as to prevent the high pressure fuel gas in the cylinder from flowing backwards; the driving mechanism consists of a cam, a feeler lever linkage mechanism and the like, wherein the cam is arranged on a cam shaft and synchronously rotates along with a rotating shaft of the engine or rotates according to a certain rotation ratio, and the head of the feeler lever is tightly contacted with the cam and can drive various valves through the linkage mechanism; the auxiliary valve is in a normally closed state under the action of a spring force, and can resist the high pressure of compressed gas to prevent gas leakage into the cylinder when being arranged in front of the valve; the cam is a variable cross-section cam, and the closing angle of the air inlet valve is changed by swinging the contact rod head back and forth along the direction of the camshaft or by moving the camshaft back and forth along the axial direction, so that the weekly air inflow of the expansion acting device is adjustable.
The invention has the preferable technical scheme that components such as a special energy storage gas tank and the like are additionally arranged between a gas compression device and an expansion acting device, and a certain control method is adopted to realize the recovery and utilization of energy such as automobile braking and the like.
The invention preferably adopts the technical scheme that the device also comprises a heat dissipation unit; the heat dissipation unit is connected in series on the passage of the compressed gas and can dissipate the heat of the compressed gas, so that the compression ratio of the engine is improved.
The invention has the beneficial effects that:
1. expansion ratio is larger than compression ratio under various working conditions
To understand the advantages and benefits of the present invention, the expansion ratio versus compression ratio of the device of the present invention was carded as follows:
the following reasons: expansion ratio is cylinder volume/intake volume; compression ratio is intake natural volume/intake volume
Therefore, the method comprises the following steps: expansion ratio/compression ratio (cylinder volume/natural volume of intake air)
The following reasons: maximum pumping natural volume (or maximum intake natural volume) < cylinder volume (characteristic of the invention)
Therefore, the method comprises the following steps: expansion ratio/compression ratio > maximum pumping natural volume/intake natural volume
The following reasons: maximum natural intake volume/natural intake volume is maximum pumping capacity per week/intake air per week
Therefore, the method comprises the following steps: expansion ratio/compression ratio > maximum amount of gas pumped per week/amount of gas taken per week (formula 1)
The reason is that: maximum weekly air pumping quantity is maximum weekly air intake quantity
Therefore, the method comprises the following steps: expansion ratio/compression ratio > maximum amount of intake air per week/amount of intake air per week (formula 2)
As can be seen from equations 1 and 2: when the air intake amount per week approaches to the maximum air pumping amount per week or the maximum air intake amount per week, the expansion ratio can still be larger than the compression ratio; when the weekly intake air amount is smaller than the maximum weekly intake air amount or the maximum weekly pump air amount, the expansion ratio is much larger than the compression ratio, and the smaller the weekly intake air amount, the larger the expansion ratio.
Note:
the volume of the cylinder is equal to the total volume of the maximum air cavity capable of accommodating working gas in the expansion acting device
The natural intake volume is the volume of gas entering the expansion work-doing device every week in a natural state before entering the engine compression device;
the natural volume of the pumping gas is the volume of the gas pumped out by the gas compression device every week in the natural state before entering the engine compression device;
each work cycle of the expansion work-doing device.
2. The engine has the advantages that under the working condition of a small throttle, the air inflow of the working cylinder per week is reduced, but the air pressure, the air-fuel ratio, the equivalent compression ratio and the density of compressed gas entering the working cylinder are not changed, and during ignition and combustion, the temperature, the density and the air pressure of gas in the cylinder are not reduced (compared with the working condition of a large throttle), so that the fuel efficiency is not reduced, and the fuel efficiency is improved on the contrary because the expansion ratio is extremely large and the expansion ratio is far greater than the compression ratio, and the gas can fully expand to work, so that the heat efficiency under the working conditions of medium and. Under the working condition of a large throttle, the expansion ratio is still larger than the compression ratio, and the thermal efficiency is also improved.
3. The invention reduces the temperature of the compressed gas by additionally arranging the heat radiation unit, so that the equivalent compression ratio of non-compression ignition engines such as gasoline engines can be improved, and the integral fuel efficiency of the gasoline engines is improved. Because the temperature is controllable, the device can adapt to various fuels with different burning points, including green energy sources such as hydrogen, natural gas and the like, and has better applicability.
4. In order to realize that a crankshaft rotates for one circle to complete one power stroke, the common Otto cycle engine requires two internal combustion cylinders. In order to realize that the crankshaft rotates for one circle to complete one power stroke, the engine needs to be provided with an internal combustion cylinder and an air compression cylinder, but the air compression cylinder does not need to work under the extreme working conditions of high temperature and high pressure, and the wall thickness, the material strength, the heat dissipation difficulty, the weight, the manufacturing difficulty and the like are small, so the overall manufacturing cost is low.
5. The solution of the invention is also advantageous in that the compression ratio is relatively fixed and the preset value is adjustable. The compression ratio is relatively fixed, which is beneficial to stable work, accurate regulation and control and stable performance of the engine, for example, the compression ratio can not be reduced under the working condition of a small accelerator, and the thermal efficiency can not be reduced. The adjustable preset value is beneficial to the engine to work in the best state and improve the adaptability of the engine, for example, different preset values can be selected to adapt to various fuels with different burning points, and for example, the more matched preset value is selected timely according to different rotating speeds of the engine so as to exert the best performance of the engine.
6. The invention also provides a two-rotor type structure scheme, which has the advantages of simpler structure and higher power density
Drawings
FIG. 1 is a schematic structural diagram of a first embodiment provided in the detailed description of the invention;
FIG. 2 is a schematic control diagram of a first embodiment of the present invention;
FIG. 3 is a schematic structural diagram of a second embodiment of the present invention;
FIG. 4 is a simplified schematic diagram of the structure of a fourth embodiment of the present invention;
FIG. 5 is a simplified schematic diagram of an expansion work device according to a fifth embodiment of the present invention;
fig. 6 is a schematic diagram of a structure of a phased intake valve according to a sixth embodiment of the present invention.
In the figure:
11. an electronic damper; 12. a one-way intake valve; 13. a compressor cylinder; 14. a one-way exhaust valve; 15. a compressor piston; 16. fixing the connecting rod; 17. a connecting rod; 21. a high pressure pipeline; 22. a buffer high pressure gas tank; 23. a high pressure gas tank; 24. an air pressure sensor; 25. a temperature sensor; 26. a heat dissipation temperature control unit; 31. a phase-controlled intake valve; 32. a working cylinder; 33. an exhaust valve; 34. a working piston; 35. a connecting rod; 36. a spark plug; 41. an air source inlet; 42. gas filtering; 43. a tail gas oxygen sensor; 5. a crankshaft; 61. a control center; 62 an accelerator pedal sensor; 71. a rotor type compressor; 72. a high pressure gas tank; 73. a rotor; 74. a movable scraper; 75. a phase-controlled intake valve; 76. the air cavity is communicated with the groove; 77. an exhaust hole; 81. a movable scraper (arranged on the stator); 82. a stator cylinder; 83. an eccentric rotor; 91. a secondary valve; 92. an air valve; 93. a variable cross-section cam; 94. a feeler lever; 95. a connecting rod; 96. an air inlet; 97. a cylinder wall.
Detailed Description
The technical scheme of the invention is further explained by the specific implementation mode in combination with the attached drawings.
Noun interpretation
To fully understand the inventive concept, the same may be applied to engines disclosed in the prior art and in the present application
The terms involved provide the explanation and definition as follows:
working medium: i.e. the working medium of the engine, here air.
Working conditions are as follows: the working conditions of the engine mainly refer to torque (accelerator), rotating speed and the like.
Compression ratio: the compression ratio is the ratio of the maximum volume in the cylinder when the piston of the Otto cycle engine is at the bottom dead center to the minimum volume in the cylinder when the piston is at the top dead center, and is the compression ratio which can express the degree of gas compression. The equivalent compression ratio herein refers to the density ratio of the compressed air to the compressed air (the density of the outside air), which is mainly determined by the pressure and temperature of the air in the high-pressure air tank, and is a relatively fixed preset value.
Expansion ratio: the expansion ratio is the ratio of the cylinder volume at the end of the power stroke and the cylinder volume at the beginning of the power stroke of the internal combustion engine, and the expansion ratio and the compression ratio of the general internal combustion engine (otto cycle) are equal and are fixed values. The expansion ratio is the cylinder volume at the end of work/the intake volume of the work cylinder, and is a variable value which gradually increases with the decrease of the accelerator and gradually decreases with the increase of the accelerator.
An air inlet stroke: the travel distance of the piston of the working cylinder, the size of the air inlet stroke, the closing angle of the air inlet valve, the weekly air inlet amount of the working cylinder and the engine torque are positively correlated and are variable values during the air inlet period from the opening to the closing of the air inlet valve of the working cylinder.
The working stroke is as follows: the travel distance of the piston of the working cylinder is indicated from the beginning of the work of the fire to the end of the work of the gas and from the piston to the bottom dead center. The power stroke is a total stroke (fixed value) -intake stroke (variable value) which is a variable value that is inversely related to the closing angle of the intake valve, the weekly intake air amount of the power cylinder, and the engine torque.
Phase angle: the phase angle of a crankshaft is defined to be 0 degree when a piston in a working cylinder is at a top dead center, the phase angle is defined to be 180 degree when the working piston runs to the bottom dead center, the phase angle corresponding to the intake stroke of the working cylinder is defined to be 0 degree to a closing angle, the phase angle corresponding to the working stroke of the working cylinder is defined to be 180 degrees to 360 degrees, and the closing angle refers to the phase angle of the crankshaft when the phase-controlled intake valve 31 is closed and is a controlled variable value.
The preset value is as follows: the preset value is the best reasonable value obtained by the control center microcomputer according to a certain algorithm according to the prestored experimental data, the intention and the demand of the user, signals transmitted by various sensors, the working condition of the engine and the like, and the value can be a dynamic value.
Example one
As shown in fig. 1 and 2, the present embodiment provides a split type large expansion ratio engine technical solution, which is mainly applicable to a compression ignition engine of diesel type, and belongs to the piston type
Compression and storage of air
The crankshaft 5 rotates, the piston 15 in the air cylinder 13 is driven by the connecting rods 16 and 17 to reciprocate up and down, the piston 15 divides the air cylinder 13 into two halves, and the upper cavity compresses air and the lower cavity sucks air, and vice versa.
Under the reverse stopping action of the one- way valves 12 and 14, compressed air firstly enters the buffer air tank 22 for buffering through the high-pressure pipeline 21 and then is guided into the high-pressure air tank 23 for temporary storage, and meanwhile, outside air is smoothly sucked into the compressor cylinder 13 through the air supply pipeline. The buffer tank 22 functions to buffer, dampen, and reduce unwanted vibrations.
The preferable scheme of the embodiment also lies in that the residual volumes of the upper cavity and the lower cavity are close to zero when the piston 15 reaches the upper dead point and the lower dead point, so that the exhaust is complete, the volume in the cylinder is fully utilized, and the volume power of the whole machine can be effectively improved because the crankshaft 5 rotates for a circle to pump air twice, which is equivalent to doubling the working volume and doubling the efficiency.
Control of the amount of gas pumped per week
When the opening degree of the electronic throttle valve 11 is reduced, the vacuum degree of the gas sucked into the compression cylinder 13 is increased, the density is reduced, the mass is reduced, the gas pumping amount per week (which means one rotation of the crankshaft, the same is true) is reduced, on the contrary, the gas pumping amount per week is increased, therefore, the gas pumping amount per week of the gas compression device can be controlled by changing the opening degree of the throttle valve 11.
Air pressure and compression ratio control
The total volume of the high- pressure air tanks 22 and 23 is large enough to buffer and temporarily store the incoming flow, effectively reduce the pulsation of the air pressure, provide a stable high-pressure air source for the working cylinder 32, continuously obtain the supplement of the compressed air delivered by the air cylinder 13, maintain the dynamic balance, maintain the stability of the compression ratio and the pressure intensity, and ensure the normal and stable operation of the engine. The tank 23 is provided with an air pressure sensor, when the air outlet amount and the air inlet amount of the high-pressure air tank 23 are unbalanced, the air pressure of the tank 23 can rise and fall slightly, and the air pressure sensor 24 in the tank feeds the change back to the control center 61.
The control center 61 synchronously changes the opening of the electronic throttle valve 11 according to the change of the closing angle of the working cylinder air inlet valve 31, so that the weekly pumping capacity of the air cylinder 13 and the weekly air inflow of the working cylinder 32 are maintained to be basically equal, meanwhile, the air pressure in the tank 23 is compared with a preset value, the weekly pumping capacity is further controlled, when the pressure intensity is greater than the preset value, the weekly pumping capacity is reduced, otherwise, the weekly pumping capacity is increased, and finally, the pressure intensity of the compressed gas is stabilized at the preset value, and because the gas pressure intensity is in direct proportion to the compression ratio, the compression ratio is also stabilized at a relatively fixed preset.
Air intake and air intake control for working cylinder
The crankshaft 5 rotates and drives the piston 34 in the working cylinder to reciprocate up and down through the connecting rod 35, when the piston 34 reaches the top dead center, the exhaust valve 33 is closed, the phase control intake valve 31 is opened, the piston 34 starts to move downwards, and the compressed air from the high-pressure air tank 23 is injected into the working cylinder 32, so that air intake starts.
Weekly air intake and power output control: the control center 61 controls the closing angle of the phase-controlled intake valve 31 in accordance with a signal from the accelerator pedal 62, and when the rotational phase angle of the crankshaft 5 reaches the closing angle, the phase-controlled intake valve 31 is closed, the intake stroke ends, and the intake stops, and since the closing angle of the intake valve 31 and the intake stroke are positively correlated, the intake stroke and the intake volume are positively correlated, and the intake air amount is intake volume × gas density, the control of the intake air amount per week can be realized by changing the closing angle of the phase-controlled intake valve 31. Since the air-fuel mixture ratio in this embodiment is a relatively fixed preset value, and the energy is proportional to the weekly intake air, the weekly intake air for controlling the working cylinder is equal to the torque output of the engine.
Maximum weekly air intake control: when the maximum weekly air inflow of the expansion working device is larger than the maximum weekly pump air flow of the gas compression device, the pressure intensity and the compression ratio of the compressed gas are greatly reduced, and the engine cannot normally work, so that the maximum weekly air inflow of the expansion working device needs to be regulated and limited, and the specific control method comprises the following steps: the control center 61 detects the opening of the electronic throttle valve 11, when detecting that the opening of the electronic throttle valve 11 reaches the maximum and can not be increased any more, the increase of the closing angle of the controllable air inlet valve 31 is stopped immediately, namely the air intake amount per week is not increased any more, meanwhile, the pressure value of the compressed gas is compared with a preset value, the air intake amount per week of the working cylinder 32 is further controlled, when the pressure is smaller than the preset value, the air intake amount per week is reduced, otherwise, the air intake amount per week is increased, and finally, the pressure and the compression ratio of the compressed gas entering the working cylinder 32 are stabilized at the preset value, so that the maximum air intake amount per week does not exceed the maximum air pumping amount.
Mixing and ignition of fuel
The oil nozzle should be installed at the air inlet of the acting cylinder and other turbulent air parts to mix oil and gas fast with high speed, high pressure and high temperature air inlet flow. In the present embodiment, since low ignition point fuel such as diesel oil is used, only in-cylinder direct injection is used, and the fuel is directly ignited and combusted by high temperature of compressed air after the intake valve 31 is closed and the intake is finished by rapid injection.
The weekly fuel injection quantity is accurately controlled by a microcomputer control center 61 according to the weekly air inflow of the working cylinder 32, the signal of the tail gas oxygen sensor 43, the user intention and the like and by combining various working conditions and requirements, the fuel injection quantity is reduced if energy is required to be saved, the air-fuel ratio is stabilized in an economic operation range, the fuel injection quantity is increased if high performance is required, and the air-fuel ratio is stabilized in an operation range meeting the high performance requirement.
In the present invention, the compressed air flows into the working cylinder 32 at a very high speed in a very short time, and a very strong vortex is formed in the cylinder, which is beneficial to fuel mixing and rapid flame propagation, and accelerates the combustion speed. And the higher the combustion speed, the higher the thermal efficiency.
Gas expansion work
After ignition, the piston 34 continues to move downward and the gas power stroke begins. The mixed oil gas is rapidly combusted, the temperature and the air pressure in the working cylinder 32 are rapidly increased, and the high-temperature and high-pressure fuel gas expands to push the piston 34 to do work. The piston pushes the crankshaft 6 to rotate continuously through the crankshaft connecting rod 35, and the energy is converted into shaft power to be output outwards. And ending the power stroke until the piston 35 moves to the bottom dead center.
Under the working condition of large throttle, the air inflow per week is large, and because the natural volume of the maximum air inflow per week or the maximum air pumping quantity per week is smaller than the volume of 32 cylinders of the working cylinder (the characteristic of the invention), even if the air inflow per week is maximum and the power output reaches the maximum, the expansion ratio is still larger than the equivalent compression ratio, the fuel gas can fully expand to work, so the fuel efficiency can be improved (compared with the common engine). Under the working condition of a small throttle, the air inflow of the working cylinder per week is reduced, but the air pressure, the air-fuel ratio, the equivalent compression ratio and the density of compressed gas entering the working cylinder are not changed, and the temperature, the density and the air pressure of the gas in the working cylinder are not reduced (compared with the working condition of a large throttle) during ignition combustion, so that the fuel efficiency is not reduced.
Exhaust gas
The piston 34 moves to the bottom dead center, and after the working stroke is finished, the exhaust valve 33 of the working cylinder 32 is immediately opened, and the exhaust stroke starts. When the piston 34 starts to move upward and the exhaust gas is discharged out of the cylinder by the inertial rotation force of the crankshaft 5 until the piston moves to the top dead center, the exhaust valve 33 is closed, the exhaust gas is completely discharged out of the cylinder, and the exhaust stroke is finished. Subsequently, the working cylinder enters the next working cycle.
The preferable scheme of the embodiment is that when the piston 34 of the power cylinder runs to the top dead center, the volume of the cylinder is close to zero, so that the waste gas can be completely discharged out of the cylinder, a series of problems caused by the difficulty in completely discharging the waste gas of the common otto cycle engine are solved, and the volume utilization rate is improved.
Example two
The technical scheme of the engine provided by the embodiment is mainly suitable for gasoline non-compression ignition engines or gasoline and diesel dual-mode engines, and belongs to the piston type.
As shown in fig. 3, the present embodiment is substantially the same as the first embodiment, and the differences mainly lie in: the high-pressure pipeline 21 is connected in series with a heat dissipation temperature control unit 26, a temperature sensor 25 is additionally arranged in the high-pressure gas tank 23 close to the gas outlet, and a spark plug 36 is additionally arranged in the working cylinder.
The difference is also the control of the compressed air temperature: a temperature sensor 25 is further arranged in the high-pressure gas tank 32 close to the gas outlet for detecting the temperature of the gas flowing into the working cylinder 32 and feeding the detected temperature back to the control center 61, the control center 61 compares the feedback value with a preset value and then controls the heat dissipation speed of the heat dissipation temperature control unit 26, when the temperature is higher than the preset value, the heat dissipation speed of the heat dissipation unit is increased, otherwise, the heat dissipation speed is reduced, so that the temperature of the gas flowing in the pipe is changed, and finally, the temperature of the compressed gas is stabilized at the preset value meeting the requirements. The high temperature is favorable for quick mixing of oil and gas and accelerating the combustion speed, thereby saving oil, and the low temperature can prevent the gasoline engine from knocking and knocking the cylinder, so that the optimal balance point needs to be found according to experiments. In addition, the microcomputer control center 61 is used for controlling the preset temperature of the compressed air, so that the device can adapt to various fuels with different burning points, and has better applicability. When the engine is operating in the diesel mode, the heat sink temperature control unit 26 is bypassed and rendered inoperative.
The difference is also the injection and ignition: when gasoline fuel is used, the oil injection mode can be in or out of a cylinder, or a mode combining pre-injection outside the cylinder and direct injection inside the cylinder, so that oil and gas mixing is facilitated, an oil injection nozzle is required to be arranged at an air flow turbulence position such as an air inlet of an acting cylinder, and the oil and gas are quickly mixed by utilizing high-speed, high-pressure and high-temperature intake air flow. When the air intake of the power cylinder is started, the oil injection is started, and when the air intake stroke is finished, the oil injection is stopped. The ignition timing is controlled by the microcomputer control center 61, when the air inlet valve 31 is closed and the air inlet stroke is finished, the spark plug 36 is ignited, if the abnormal condition of explosion and knock occurs, the ignition timing can be delayed properly to solve the problem quickly.
EXAMPLE III
The scheme provided by the embodiment is mainly used for improving the pumping loss of the engines in the first embodiment and the second embodiment, and the specific scheme is as follows: a late-closing one-way valve is adopted to replace the one-way air inlet valve 12 of the medium pressure air cylinder in the first embodiment and the second embodiment, and the corresponding electronic throttle valve 11 is eliminated.
Under the working condition of a small accelerator, the opening degree of the electronic throttle valve 11 is smaller, and the air resistance is larger, so that the pumping loss is larger. If the energy loss is reduced, the intake valve late closing one-way valve is adopted to replace the one-way intake valve 12 of the air pressing cylinder, and the corresponding electronic throttle valve 11 is eliminated. The working principle of the intake valve late-closing one-way valve is as follows: the late-closing one-way valve is controlled to delay closing of a certain phase angle, a certain amount of air is spitted back to the air inlet pipeline in the air compression stroke, and the air pumping is reduced by a certain volume every time, so that the air pumping quantity per week is controlled. The elimination of the electronic throttle 1 greatly reduces the pumping losses.
The disadvantage of this solution is that the valve train is relatively complex and the manufacturing costs will increase.
In addition, only the special components such as the energy storage gas tank and the like are added between the gas compression device and the expansion acting device and a certain control method is adopted, and the recovery and the utilization of the automobile braking energy can be realized.
Example four
The principle and the control method of the gas compression device and the expansion working device are basically the same as those of the first embodiment and the second embodiment, and the difference is that the gas compression device and the expansion working device adopt a rotor structure, preferably a double-blade configuration, the structure is simpler, the power density is high, and a complex exhaust structure is not needed. The structure diagram is shown in figure 4, and the scheme is characterized in that: the gas compression is completed by the rotor compressor 71, the gas can be compressed twice after rotating for one circle, and the compression efficiency is high; in the expansion acting device, the rotor 73 uses the self circle center as a rotating shaft, the outer circle of the rotor is always in close contact with the inner wall of the cylinder body when the rotor rotates, a plurality of closed working air cavities are formed between the contact surface and the scraping blade 74 and between the scraping blade 74 and the scraping blade 74, when the working air cavities just become large, a certain amount of compressed gas meeting the requirements is injected into the air control valve 75, a certain amount of fuel is sprayed by the fuel supply mechanism, high-pressure fuel gas expands after ignition to push the rotor 73 to rotate to do work outwards, when the working air cavities reach the maximum, waste gas in the cavities begins to be discharged from the exhaust hole 77 through the air cavity communicating groove 76; the rotor 73 continues to rotate, the working air cavity begins to shrink, the air cavity communicating groove 76 enables the exhaust hole to be communicated with the shrunk working air cavity all the time, waste gas is exhausted from the exhaust hole 77 when the working air cavity shrinks, until the working air cavity shrinks to zero, the waste gas is completely exhausted, and the working cycle is finished; the rotor 73 rotates for a circle and can do work twice, and the power density of the engine is high due to the fact that the working air cavity occupies a large proportion relative to the volume of the total working air cavity when the working air cavity reaches the maximum and the expansion capacity is high; in addition, the moving part is a rotor, complex vibrating parts such as a crankshaft, a piston, a connecting rod and the like are not arranged, and a complex exhaust mechanism is not arranged, so that the cost is low, the reliability and the smoothness are good, the rotating speed and the power density are favorably improved, and the inner walls of the rotor and the stator are circular and are easy to machine and manufacture.
EXAMPLE five
The present embodiment is substantially the same as the fourth embodiment, except that the expansion work-doing device adopts another rotor structure. The structure sketch of the expansion work-doing device is shown in figure 5, and the scheme is characterized in that: in the expansion acting device, a movable scraping blade 81 is arranged on a stator 82, a rotor 83 uses the circle center of the stator 82 as the axis of a rotating shaft, the circle center of the rotor 83 is not coincident with the axis, the far center point of the rotor is always in close contact with the inner wall of a cylinder body of the stator 82 during rotation, two closed working air cavities are formed between the contact surface and the scraping blade, one working air cavity is used for air intake while the other working air cavity is used for air exhaust, and the rotor rotates for one circle to act once. The special advantages are that: the piston type air-conditioning engine works once per week like a piston type air-conditioning engine, but can do expansion work in a full cycle, air exhaust is performed while air is admitted in the next cycle, and the piston type air-conditioning engine only does expansion work in the first half cycle, so that the combustion and expansion period is long, sufficient time is provided for combustion, the thermal efficiency and the rotating speed are favorably improved, and the power density is improved; because the volume of the working air cavity is the sum of the volumes of the working air cavities when the working air cavity reaches the maximum, the expansion capacity of the working air cavity is higher than that of the working air cavity in the fourth embodiment, the thermal efficiency is higher, but the power density is slightly poor.
EXAMPLE six
The embodiment provides an implementation scheme for the key component phase-controlled intake valve in the invention, the structure of the phase-controlled intake valve is similar to that of an air intake mechanism of a common otto cycle engine on the market, and the phase-controlled intake valve is composed of a valve and a valve driving mechanism, and the main difference is that the closing angle of the intake valve is variable, so that the weekly air intake quantity of an expansion acting device is adjustable. The structural principle of the phase control air inlet valve is shown in figure 6, and the scheme is characterized in that: the normally closed auxiliary valve 91 which is opened towards the outside of the cylinder is additionally arranged, the high pressure of compressed gas can be resisted, the gas leakage is prevented, the driving mechanism drives the auxiliary valve 91 to be opened, the compressed gas flowing through the auxiliary valve 92 indirectly drives the valve to be opened, and the valve 92 is closed under the action of spring force when the auxiliary valve 91 is closed; the present invention has been described in terms of a preferred embodiment in which the weekly intake air amount of an expansion work device is adjustable by changing the cam to a variable cross-section cam 93 by oscillating a contact rod head 94 back and forth in the direction of the camshaft or by moving the camshaft back and forth in the axial direction to change the phased intake valve closing angle, and it will be appreciated by those skilled in the art that various changes or equivalent substitutions may be made in these features and embodiments without departing from the spirit and scope of the present invention. The present invention is not to be limited by the specific embodiments disclosed herein, and other embodiments that fall within the scope of the claims of the present application are intended to be within the scope of the present invention.
Claims (8)
1. A split type large expansion ratio engine is characterized by comprising a gas compression device, a high-pressure gas tank and an expansion work-doing device; the gas compression device provides compressed gas for the high-pressure gas tank, the high-pressure gas tank is used for storing the compressed gas, keeping constant pressure, reducing air pressure pulsation and providing the compressed gas for the expansion work-doing device, and the high-pressure gas tank also comprises a pipeline gas cavity or other gas cavities with the same function;
the expansion working device comprises a stator, a rotor, an air inlet mechanism, an exhaust mechanism and an oil supply mechanism; the rotor is arranged in the stator, a closed working air cavity is formed between the stator and the rotor, the stator is provided with an air inlet mechanism and an air outlet mechanism for periodic air inlet and air outlet, and the oil supply mechanism and the air inlet mechanism synchronously supply fuel;
the stator comprises a cylinder, a cylinder body, an upper cylinder cover and a lower cylinder cover, the rotor is circular and is arranged in the stator, one or more movable scraping blades are arranged on the rotor, the diameter of the rotor is smaller than the inner diameter of the cylinder, the circle center of the rotor is not coincident with the circle center of the stator, the circle center of the rotor is taken as a rotating shaft, the outer circle of the rotor is always in close contact with the inner wall of the stator cylinder body when the rotor rotates, two or a plurality of closed working air cavities are formed between the contact surface and the scraping blades and between the scraping blades and the scraping blades, the air inlet mechanism is a phase-control air inlet valve and is arranged on the stator cylinder body close to the contact surface, the exhaust mechanism, namely an exhaust hole is arranged on the other side close to the contact surface, the air inlet mechanism and the oil supply mechanism work together, a certain amount of compressed gas is injected when the working air cavities are, exhaust gas is discharged from the exhaust hole when the working air cavity contracts;
an air cavity communicating groove is formed between the contact surface and the maximum working air cavity on the inner wall of the stator, so that the working air cavity can smoothly exhaust air to the exhaust hole when being contracted.
2. The split large expansion ratio engine according to claim 1, wherein:
the expansion working device comprises a stator, a rotor, an air inlet mechanism, an exhaust mechanism and an oil supply mechanism; the rotor is arranged in the stator, a closed working air cavity is formed between the stator and the rotor, the stator is provided with an air inlet mechanism and an air outlet mechanism for periodic air inlet and air outlet, and the oil supply mechanism and the air inlet mechanism synchronously supply fuel;
the stator comprises a cylinder body, an upper cylinder cover and a lower cylinder cover, a movable scraping blade is arranged on the cylinder body, the diameter of the rotor is smaller than the inner diameter of the cylinder body, the rotor is arranged in the stator, the center of the rotor is taken as the axis of a rotating shaft, the center of the rotor is not coincident with the axis, the far center point of the rotor is always in close contact with the inner wall of the cylinder body during rotation, and two closed working air cavities are formed between the contact surface and the scraping blade;
the movable scraper is arranged in the scraper groove box and can freely extend out, the air inlet mechanism is a phase control air inlet valve and is arranged on the cylinder body close to the scraper, the exhaust mechanism, namely an exhaust hole, is arranged on the other side close to the scraper, the air inlet mechanism and the oil supply mechanism work together, a certain amount of compressed gas is injected when the working air cavity begins to grow, fuel with a certain proportion is sprayed, high-pressure fuel gas expands after ignition to push the rotor to do work outwards, the exhaust hole is communicated with the contracted working air cavity all the time, and waste gas is discharged from the exhaust hole when the working air cavity contracts.
3. The split large expansion ratio engine according to claim 1, wherein:
also includes a control unit; so as to balance the pumping capacity of the gas compression device and the gas demand of the expansion acting device, and ensure that the gas pressure and the compression ratio in the tank are constant in a preset range;
the expansion work-doing device comprises a cylinder body, a cylinder cover, a piston, a connecting rod, a crankshaft, a phase-controlled air inlet valve, an exhaust valve and an oil supply mechanism; the crankshaft rotates to drive the piston to reciprocate in the cylinder through the connecting rod, the phase control air inlet valve and the exhaust valve are arranged on the cylinder cover, the phase control air inlet valve and the oil supply mechanism work together, a certain amount of compressed gas is injected when a working air cavity begins to grow, a certain proportion of fuel is injected, high-pressure fuel gas expands after ignition to push the piston to work outwards, and the exhaust valve is opened to exhaust waste gas when the working air cavity contracts;
the closing angle of the phase-control air inlet valve is variable, so that the air inflow per week is adjustable, compressed air is injected when a working air cavity is just started to be enlarged, the torsion and power output are changed by changing the air inflow per week of the expansion working device, the minimum volume of the working air cavity is set to be minimum as much as possible, the expansion working device can operate with small air inflow when the throttle is small, and finally the compression ratio is far greater than the compression ratio without basically changing under the working condition of the throttle;
the minimum volume of the working air cavity refers to the volume sum of the working air cavity when the piston reaches the top dead center; the small air inflow refers to that the air inflow per week is small, and the natural state volume of the small air inflow per week is far smaller than the maximum volume of the working air cavity, so that the super-large expansion ratio is obtained; the natural state volume refers to the volume of compressed gas entering the cylinder in an uncompressed state; the closing angle refers to the angle of rotation of the air inlet valve from opening to closing of the crankshaft; the week refers to the time interval between two adjacent air intakes of the expansion work device.
4. The split large expansion ratio engine according to claim 1 or 2, characterized in that:
also includes a control unit; the control unit can balance the pumping capacity of the gas compression device and the gas demand of the expansion acting device, and make the gas pressure and the compression ratio in the tank constant in preset ranges;
the phase-controlled air inlet valve closing angle of the expansion acting device is variable, so that the air inflow per week is adjustable, the torsion and power output are changed by changing the air inflow per week of the expansion acting device, the minimum ignition volume of a working air cavity is set to be minimum as far as possible, the expansion acting device can operate with small air inflow when a small accelerator is used, and finally the compression ratio under the working condition of the small accelerator is basically unchanged, and the expansion ratio is far larger than the compression ratio;
the minimum ignition volume of the working air cavity refers to the minimum working air cavity volume capable of normally igniting; the week refers to the time interval between two adjacent air inlets of the expansion work-doing device; the small air inflow refers to that the air inflow per week is small, and the volume of the air inflow per week is far smaller than the maximum volume of the working air cavity in a natural state, so that the super-large expansion ratio is obtained; the natural state volume refers to the volume of compressed gas entering the cylinder in an uncompressed state; the closing angle refers to the angle of rotation of the air inlet valve from opening to closing of the rotating shaft.
5. The split large expansion ratio engine according to any one of claims 1 to 3, wherein:
the natural state volume of the maximum pumping air quantity per week of the gas compression device or the maximum air inflow per week of the expansion working device is smaller than the maximum volume of the working air cavity, so that the expansion ratio is still larger than the compression ratio under the working condition of a large throttle;
the natural state volume refers to the volume of the compressed gas entering the working air cavity in an uncompressed state, and the period of each week refers to the time interval between two adjacent air inlets of the expansion working device.
6. The split large expansion ratio engine according to any one of claims 1 to 3, wherein:
the phase-controlled air inlet valve of the expansion working device comprises a driving mechanism, an air valve and an auxiliary air valve; the valve is in a normally closed state under the action of the spring force, and the valve is opened towards the working air cavity and can resist the high pressure of the fuel gas in the cylinder so as to prevent the high pressure fuel gas in the cylinder from flowing backwards; the driving mechanism comprises a cam, a feeler lever and a feeler lever linkage mechanism, the cam is arranged on a cam shaft and synchronously rotates along with a rotating shaft of the engine or rotates according to a certain rotation ratio, the head of the feeler lever is tightly contacted with the cam, and various valves can be driven through the linkage mechanism;
the auxiliary valve is in a normally closed state under the action of a spring force, and can resist the high pressure of compressed gas to prevent gas leakage into the cylinder when being arranged in front of the valve; the cam is a variable cross-section cam, and the closing angle of the air inlet valve is changed by swinging the contact rod head back and forth along the direction of the camshaft or by moving the camshaft back and forth along the axial direction, so that the weekly air inflow of the expansion acting device is adjustable.
7. The split large expansion ratio engine according to any one of claims 1 to 3, wherein:
a special energy storage gas tank is additionally arranged between the gas compression device and the expansion acting device so as to recycle and utilize energy of automobile braking and the like.
8. The split large expansion ratio engine according to any one of claims 1 to 3, wherein:
the device also comprises a heat dissipation unit; the heat dissipation unit is connected in series on a passage of the compressed gas to dissipate heat of the compressed gas, so that the compression ratio of the engine is improved.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910060639.1A CN109519273A (en) | 2019-01-23 | 2019-01-23 | A kind of separated type super large expansion ratio engine and regulation method |
| CN2019100606391 | 2019-01-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110939506A true CN110939506A (en) | 2020-03-31 |
Family
ID=65799351
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910060639.1A Withdrawn CN109519273A (en) | 2019-01-23 | 2019-01-23 | A kind of separated type super large expansion ratio engine and regulation method |
| CN201911367056.XA Pending CN110939506A (en) | 2019-01-23 | 2019-12-26 | Split type large expansion ratio engine |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910060639.1A Withdrawn CN109519273A (en) | 2019-01-23 | 2019-01-23 | A kind of separated type super large expansion ratio engine and regulation method |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN109519273A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113530668A (en) * | 2021-08-18 | 2021-10-22 | 蒙毓江 | Circumferential air passage engine |
| US20220154652A1 (en) * | 2020-11-17 | 2022-05-19 | Volvo Truck Corporation | Internal combustion engine system |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109519273A (en) * | 2019-01-23 | 2019-03-26 | 谢炳炎 | A kind of separated type super large expansion ratio engine and regulation method |
| BR202022021251U2 (en) * | 2022-10-19 | 2024-04-30 | Gabriel Fernando Carrão Macedo | TWO-STROKE ENGINE WITH DIRECT INJECTION WITHOUT ADDING LUBRICANT TO THE FUEL |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2440114Y (en) * | 2000-07-18 | 2001-07-25 | 夏立刚 | Slidine-vane rotor engine |
| CN102428259A (en) * | 2009-05-06 | 2012-04-25 | 奇德钟 | Separate-type rotary engine |
| WO2012159637A2 (en) * | 2011-05-20 | 2012-11-29 | Bacolla Carlos Ruben Carlos | Split-cycle engine |
| CN204253168U (en) * | 2014-11-24 | 2015-04-08 | 梁华羽 | A kind of supercharging integrative-structure of four stroke engine |
| CN105102785A (en) * | 2013-02-07 | 2015-11-25 | 法雷奥电机控制系统公司 | Discharge valve and associated device |
| CN105275586A (en) * | 2015-10-30 | 2016-01-27 | 赖宽 | Two-stroke double-cylinder engine |
| CN106304839A (en) * | 2014-03-07 | 2017-01-04 | 菲利普·克瑞斯坦尼 | Two-stroke internal combustion engine with pre-cold compression |
| CN109519273A (en) * | 2019-01-23 | 2019-03-26 | 谢炳炎 | A kind of separated type super large expansion ratio engine and regulation method |
| CN110500178A (en) * | 2019-09-04 | 2019-11-26 | 秦子涵 | A kind of rotor blade engine |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1928333A (en) * | 2006-10-01 | 2007-03-14 | 袁辉 | Internal-combustion engine |
| CN101608569A (en) * | 2008-06-19 | 2009-12-23 | 刘永红 | Changeable-stroke engine with cylinder outside compression |
| WO2009155620A1 (en) * | 2008-06-26 | 2009-12-30 | Sl Ingconsult Gmbh | Principle of a four-stroke reciprocating engine with spatial separation of the intake and compression strokes from the power and exhaust stroke |
| CN101832176B (en) * | 2009-03-09 | 2012-12-26 | 大连理工大学 | Engine |
| US8443769B1 (en) * | 2012-05-18 | 2013-05-21 | Raymond F. Lippitt | Internal combustion engines |
| CN105201642B (en) * | 2015-09-15 | 2017-12-15 | 麦镇荣 | Six-stroke progressively adding type burning gasoline and diesel engine |
-
2019
- 2019-01-23 CN CN201910060639.1A patent/CN109519273A/en not_active Withdrawn
- 2019-12-26 CN CN201911367056.XA patent/CN110939506A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2440114Y (en) * | 2000-07-18 | 2001-07-25 | 夏立刚 | Slidine-vane rotor engine |
| CN102428259A (en) * | 2009-05-06 | 2012-04-25 | 奇德钟 | Separate-type rotary engine |
| WO2012159637A2 (en) * | 2011-05-20 | 2012-11-29 | Bacolla Carlos Ruben Carlos | Split-cycle engine |
| CN105102785A (en) * | 2013-02-07 | 2015-11-25 | 法雷奥电机控制系统公司 | Discharge valve and associated device |
| CN106304839A (en) * | 2014-03-07 | 2017-01-04 | 菲利普·克瑞斯坦尼 | Two-stroke internal combustion engine with pre-cold compression |
| CN204253168U (en) * | 2014-11-24 | 2015-04-08 | 梁华羽 | A kind of supercharging integrative-structure of four stroke engine |
| CN105275586A (en) * | 2015-10-30 | 2016-01-27 | 赖宽 | Two-stroke double-cylinder engine |
| CN109519273A (en) * | 2019-01-23 | 2019-03-26 | 谢炳炎 | A kind of separated type super large expansion ratio engine and regulation method |
| CN110500178A (en) * | 2019-09-04 | 2019-11-26 | 秦子涵 | A kind of rotor blade engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20220154652A1 (en) * | 2020-11-17 | 2022-05-19 | Volvo Truck Corporation | Internal combustion engine system |
| US11598248B2 (en) * | 2020-11-17 | 2023-03-07 | Volvo Truck Corporation | Internal combustion engine system |
| CN113530668A (en) * | 2021-08-18 | 2021-10-22 | 蒙毓江 | Circumferential air passage engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109519273A (en) | 2019-03-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110939506A (en) | Split type large expansion ratio engine | |
| US7418929B2 (en) | Internal combustion engine and method | |
| US9458741B2 (en) | Split cycle phase variable reciprocating piston spark ignition engine | |
| US9074526B2 (en) | Split cycle engine and method with increased power density | |
| US7434551B2 (en) | Constant temperature internal combustion engine and method | |
| US20100229806A1 (en) | Internal combustion engines with surcharging and supraignition systems | |
| KR20080059344A (en) | Four-stroke internal combustion engine | |
| US8844496B2 (en) | Internal combustion engine with separate combustion chamber and a method to achieve modified and controlled autoignition in said chamber | |
| KR20200130832A (en) | All working conditions Channel division Time division Supercharged intake variable compression ratio technology of internal combustion engine | |
| KR102207883B1 (en) | Exhaust gas recirculation system and ship including the same | |
| Sen et al. | Performance analysis of supercharging process in SI engine & CI engine and application of supercharger | |
| EP1497541B1 (en) | Four-stroke rotary internal-combustion engine | |
| KR20170035333A (en) | 2 Stroke 1 Cycle Engine with External Compressed Air Supplying System | |
| CN104005846A (en) | Fuel-selectable piston type two-travel engine | |
| Sen et al. | ANALYSIS OF CHARGING PROCESS IN SI ENGINE & CI ENGINE AND APPLICATION OF SUPERCHARGER | |
| Joseph | Small Diesel Engines | |
| JP2000234536A (en) | Energy reserving cycle engine | |
| JPH01318725A (en) | Control device for engine | |
| JPH0547372U (en) | Two-cycle engine scavenging pump controller |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200331 |
|
| RJ01 | Rejection of invention patent application after publication |