CN103573400A - Pneumatic continuously-variable transmission comprising engine capable of outputting high-pressure gas directly - Google Patents
Pneumatic continuously-variable transmission comprising engine capable of outputting high-pressure gas directly Download PDFInfo
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- CN103573400A CN103573400A CN201210264988.3A CN201210264988A CN103573400A CN 103573400 A CN103573400 A CN 103573400A CN 201210264988 A CN201210264988 A CN 201210264988A CN 103573400 A CN103573400 A CN 103573400A
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Abstract
A pneumatic continuously-variable transmission is composed of an engine capable of outputting high-pressure gas directly and a pneumatic motor (11) connected with the engine. The engine capable of outputting high-pressure gas directly comprises an engine body (1) and further comprises a high-pressure pipe cavity (8), a pressure sensor (7) and a power matching controller (13); an intake valve, an exhaust valve and an output valve (6) are mounted on a cylinder head of the engine body (1); the high-pressure pipe cavity (8) is connected with the output valve (6), the pressure sensor (7) is mounted in the high-pressure pipe cavity (8), and the power matching controller (13) controls the output valve (6) to be switched on for a period of time when different crankshafts in power stroke of the engine are in location correspondence, the volume of gas delivered into the high-pressure pipe cavity (8) from a cylinder of the engine is then controlled through the output valve (6), and the gas is used for directly driving the pneumatic motor (11) that is connected with the high-pressure pipe cavity (8) to rotate. The pneumatic continuously-variable transmission without utilization of clutches has high output torque and high benefit.
Description
Affiliated technical field
The present invention relates to a kind of stepless speed variator, relate to more specifically a kind of for automobile, the stepless speed variator being formed by direct output high-pressure gas motor.
Background technique
Automatic transmission is for automatically changing torque and rotational speed, and on the whole, current automatic transmission has automatic transmission speed changer and multiple stepless speed variator to come into operation.The low transmitting torque of automatic transmission transmission efficiency is little, and speed change is level and smooth not.And general stepless speed variator (CVT), although the speed change of automobile is steady, but general stepless speed variator (CVT) is comprised of two groups of speed-changing wheel discs and driving belt, if the number of patent application of announcing is 01803818.2 patent, because the manufacturing technology difficulty of CVT speed changer is large, adopt and compress driving belt on speed-changing wheel disc, by frictional force carry-over moment, so transmitting torque is little.Above automatic transmission transmitting torque is little in sum, all will have automatic clutch, is only applicable to sedan car, inapplicable on the passenger-cargo carriage of high-power.
Therefore, the object of this invention is to provide a kind of stepless speed variator, output torque is greatly applicable to passenger-cargo carriage, without reduction gear, can direct drive of wheel axle, and efficiency is high, and without clutch, in manufacturing technology, maturation is easy to manufacture.
Summary of the invention
The pneumatic stepless speed variator that this object can consist of direct output high-pressure gas motor claimed in claim 1 is realized.The present invention by direct output high-pressure gas motor be connected pneumatic motor (11) with it and form, directly output high-pressure gas motor comprises motor (1), in motor (1) cylinder head, there are suction valve and outlet valve, it is characterized in that: at cylinder, cover delivery valve (6) is also installed, directly output high-pressure gas motor also comprises the high pressure tube chamber (8) being connected with delivery valve (6), and the pressure transducer (7) of installing in high pressure tube chamber (8), form with power match controller (13), by power match controller (13), control delivery valve (6), corresponding conducting a period of time constantly of different crank positions in motor (1) power stroke, by delivery valve (6) control engine gas gas in the jar, be input to the air inflow of high pressure tube chamber (8), for directly driving, be connected pneumatic motor (11) rotation with high pressure tube chamber (8), delivery valve during other stroke (6) cuts out, by the pressurized gas that are stored in high pressure tube chamber (8), to pneumatic motor, export energy.
One end of delivery valve of the present invention (6) is connected with delivery valve coil drive assembly (12), is controlled the keying of delivery valve (6) by the electromagnetic coil power on/off of delivery valve coil drive assembly (12) the inside.
Power match controller of the present invention (13) input end is connected to pressure transducer (7), crank position sensing (5), output terminal is connected to delivery valve drive circuit (14), the slippage of high-voltage tube cavity pressure when the rise of high pressure tube chamber (8) internal pressure and delivery valve are closed while detecting delivery valve (6) unlatching by pressure transducer (7), under the programming instruction of the inner CPU processor of power match controller (13) is controlled, compare computing and draw the corresponding crank position of delivery valve switching signal next time, this signal amplifies by delivery valve drive circuit (14), driver output valve coil drives the electromagnetic coil in assembly (12) to drive delivery valve (6) action.Power match controller (13) input end is connected with progress signal control end, astern signal control end and pneumatic motor output shaft position transducer (21), in inside, advance or retreat under instruction repertorie control, according to pneumatic motor position of output axle sensor (21), detect pneumatic motor piston (19) position, export corresponding switching signal to the transfer valve drive circuit (15) and the outlet valve drive circuit (26) that are connected with output terminal, drive transfer valve (18) and pneumatic motor outlet valve (24) action, pneumatic motor is rotated.
Power match controller of the present invention (13) output terminal is connected to Injection Pump drive circuit (10), according to crankshaft position sensor (5) power match controller (13), calculate speed of crankshaft and the position of delivery valve (6) start signal on bent axle next time, power match controller (13) calculates crank position corresponding when Injection Pump start signal arrives next time, output switching signal is to Injection Pump drive circuit (10), the action of control Injection Pump, makes the leading or synchronous delivery valve opening time of position, fuel combustion maximal pressure force.
Power match controller of the present invention (13) can be according to being assemblied in the pneumatic motor position of output axle sensor (21) on pneumatic motor output shaft (16), the rotating speed of pneumatic motor output shaft (16) detected, the opening angle scope that makes transfer valve (16) is the angular range on corresponding pneumatic motor position of output axle, rotating speed speed with pneumatic motor output shaft (16) changes, while making pneumatic motor output shaft (16) rotating speed fast, the opening angle scope of transfer valve (18) on pneumatic motor position of output axle is little, when pneumatic motor output shaft (16) rotating speed is slow, the opening angle scope of transfer valve (18) on pneumatic motor position of output axle is large, increase the slewing range of pneumatic motor.
The effect of power match controller (13) is: according to the variation of load, the output power that detects motor is input to the matching state of the power of pneumatic motor with it, control delivery valve switch triggering signal time, controlling delivery valve opens at different crank positions, the pressurized gas of output different pressures, reach and adjust the object that is input to pneumatic motor power; Advancement amount according to the opening time of delivery valve and speed of crankshaft auto-compensation Injection Pump start signal, makes the leading or synchronous delivery valve opening time of position, fuel combustion maximal pressure force.
Above motor (1) is to take diesel engine as example explanation, but its principle is equally applicable to petrol engine.
The invention has the beneficial effects as follows: the moment of torsion that power transmits by friction by air pressure transmission ratio of two term is large; Directly with output valve (6) switch, control turning of pneumatic motor output shaft (16) and stop, without clutch; Direct output engine high cylinder pressure gas-powered pneumatic motor, high efficiency; Adopt electronic signal to control automobile forward-reverse, be easy to control.
Accompanying drawing explanation
Fig. 1 is first embodiment of the invention schematic diagram.
Fig. 2 is second embodiment of the invention schematic diagram
Fig. 3 is crank position and high-voltage tube cavity pressure figure
1. motors in figure, 2. piston, 3. connecting rod, 4. bent axle, 5. crankshaft position sensor, 6. delivery valve, 7. pressure transducer, 8. high pressure tube chamber, 9. Injection Pump, 10. Injection Pump drive circuit, 11. pneumatic motors, 12. delivery valve coil drive assemblies, 13. power match controllers, 14. delivery valve drive circuits, 15. transfer valve drive circuits, 16. pneumatic motor output shafts, 17. transfer valve coil drive assemblies, 18. transfer valves, 19. pneumatic motor pistons, 20. pneumatic motor connecting rods, 21. pneumatic motor position of output axle sensors, 22. outlet valve drive circuits, 23. outlet pipes, 24. pneumatic motor outlet valves, 25. outlet valve coil drive assemblies.
Embodiment
Below in conjunction with accompanying drawing, the present invention is further described.
Delivery valve (6) and transfer valve (18) are made hollow shape inside and are passed into cooling liquid.Cylinder can have a plurality of, and Fig. 1 draws a cylinder in 4 cylinders.Pressure transducer (7) is that a piezoelectric pressure transducer is converted into electrical signal force value, and crankshaft position sensor (5) and pneumatic motor output shaft position transducer (21) are to adopt magnetic induction type position transducer.Fig. 1 pneumatic motor (11) is a kind of pneumatic motor that can clockwise and anticlockwise, Fig. 2 pneumatic motor (11) is a kind of piston type pneumatic motor, its cylinder number is more than two cylinders, Fig. 2 adopts in 4 cylinder figure and only makes one of them cylinder, and each cylinder reaches top dead center position and on pneumatic motor output shaft (16), differs 90 degree positions.Storage, CPU processor and delivery valve switching signal output terminal, Injection Pump switching signal output terminal are contained in Fig. 1 power match controller (13) inside, and Fig. 2 power match controller (13) is than many transfer valves of Fig. 1 switching signal output terminal, pneumatic motor outlet valve switch signal output part and astern signal control end.
Fig. 1 example work is as follows: direct output high-pressure gas engine working process is also the same with common four stroke engine, is divided into air-breathing, compression, work done, four strokes of exhaust.Wherein except power stroke difference, other stroke working procedure is identical.
The sinusoidal curve cb of Fig. 3 is engine crankshaft corner and piston position plotted curve, only draws the part curve relevant with power stroke in figure.When in figure, a point is for compression stroke, piston runs to top dead center position, by the bent axle 360 degree crank position when the top dead center that circles, it is 0 degree, the spatial volume of now cylinder sealing is minimum, intake valve, exhaust valve closing, fuel combustion increases cylinder pressure and promotes descent of piston, and along with descent of piston cylinder pressure reduces, during to lower dead center b point position, inner pressure of air cylinder is minimum, exhaust valve is opened, 180 degree that when a little, corresponding bent axle turns over.Curve cg is the adjustment range of controlling delivery valve (6) conducting, curve eh be delivery valve (6) ON time be delivery valve (6) in the conducting of e point, in h point position, close, e point and h point are the arbitrfary points on curve cg.The curve of Fig. 3 top is the change curve of the corresponding crankshaft angles of high-voltage tube cavity pressure, when delivery valve (6) when e point has just started conducting in high pressure tube chamber (8) gas pressure be Fe value, when delivery valve (6) cuts out to h point, pressure is elevated to Fh value.When delivery valve (6) conducting, pressurized gas enter in high pressure tube chamber, the interior gas pressure rising of high pressure tube chamber (8) output power of internal combustion engine, after delivery valve conducting a period of time, delivery valve cut-off when corresponding bent axle turns over an angle value arrival h point, now in tube chamber, gas pressure equates with inner pressure of air cylinder if do not considered conducting pressure loss.Delivery valve ON time is that bent axle forwards h point to during this period of time from e point, the cut-off of other times delivery valve, and pressurized gas, by pneumatic motor work done, are discharged from outlet pipe, and the interior gas pressure of high pressure tube chamber (8) reduces.Under cylinder injects with amount fuel operating mode same case, the corresponding e point of delivery valve conducting trigger signal place diverse location, tube chamber internal pressure after delivery valve conducting is also different, the conducting during the closer to lower dead center b point of e point position, the pressure reaching in tube chamber after delivery valve conducting is lower, the power capability that motor is externally exported is lower, the energy that pneumatic motor obtains is also lower, the speed of crankshaft of motor own is but faster, because the rotating speed that total power is stayed the many bent axles of internal energy once the power minimizing that regularly motor is externally exported is just faster; Otherwise e point position is the closer to d point, the pressure reaching is higher, externally capacity for work is strengthened, can the speed of crankshaft of motor own slower, but during maximum pressure, delivery valve conducting trigger signal corresponding points are not at top dead center a point, and at d point, now delivery valve just bent axle forward to d point be conducting bent axle while forwarding top dead center a point to delivery valve close.
Delivery valve during engine idle (6) cuts out and does not work, and pressurized gas do not enter high pressure tube chamber (8), pneumatic motor stall.When stepping on the throttle and power match controller (13) receives progress signal, under matching controller (13) internal program is controlled, when bent axle (4) forwards the g point position as Fig. 3 to, the pulse signal of delivery valve (6) is opened in output, pressurized gas enter high pressure tube chamber (8), promoting pneumatic motor (11) rotates, and under power match controller (13) is controlled, the slippage of high-voltage tube cavity pressure when the rise of high pressure tube chamber (8) internal pressure and delivery valve are closed while detecting delivery valve (6) unlatching by pressure transducer (7), through the inner CPU processor comparison operation of power match controller (13), draw rotating speed when engine output matches with the power that is input to pneumatic motor (11), pneumatic motor when opening the throttle (11) to enter the larger rotating speed of pressure also higher, reach the order of vehicles speed.
The power match working principle of power match controller (13) is as follows: some e, the h corresponding position moment intraluminal pressure Fe of high pressure and the Fh that before and after delivery valve switch, are Fig. 3.Measure in this high pressure tube chamber before conducting pressure Fe value and last pressure Fe value and remember that ' on Fe ' subtracts each other and obtain a difference and be designated as ' Fe is poor ', Fe poor=Fe-Fe on; The pressure Fh value in like manner reaching after conducting in high pressure tube chamber and last pressure Fh value remember ' on Fh ' subtract each other obtain a difference be designated as ' Fh is poor ' be Fh poor=Fh-Fh on.' Fe is poor ' that obtain and ' Fh is poor ' be added obtain a value be designated as F` be F`=Fe poor+Fh is poor; F` is the amount of reflection pressure matching direction, while reducing even stall because of the large output speed of pneumatic motor load change, cylinder outputs to the intraluminal power ratio pneumatic motor of high pressure and absorbs the power Fe of many times putting in place and be greater than ' on Fe ' Fh and be greater than ' on Fh ' and may show that F` is for just, contrary F`, for negative, is zero when both power match.In the situation that input fuel identical total output is identical, power matching circuit work is as follows: pneumatic motor resistance become large suction pressure become the large → external output power minimizings → engine speed of motor risings → power matching circuit calculate F` value become just becoming draw greatly next delivery valve ON time in advance → the external output power change of motor greatly → engine speed reduction → F` value is varied down to zero; Now that best power match point delivery valve ON time is constant.
The location point of fuel when perfect combustion reaches maximum pressure value in cylinder is relevant with the opening time of oil burning jet oil pump, crank position when Injection Pump (9) opening time, corresponding crank position can be controlled fuel combustion pressure maximum point by power match controller (13) control, appears on Fig. 3 curve df interval fuel combustion pressure maximum point.The general corresponding bent axle of d point is in-15 degree positions, and the corresponding bent axle of f point forwards 15 degree positions to.The scope of fuel combustion pressure maximum point is ahead of top dead center a point, and the adjustment range of delivery valve (6) is ahead of the conducting of top dead center a point, because when load when weight pneumatic motor approaches stall, the energy of cylinder work done can not finely be exported by pneumatic motor work done, and engine crankshaft rotating speed is accelerated, by making fuel combustion pressure maximum point be ahead of top dead center a point, and delivery valve (6) is ahead of the conducting of top dead center a point, it is the rotary inertia that is to utilize engine flywheel, when compression stroke, more flywheel energy is transferred to gas internal energy, improve the output of cylinder internal air pressure, suppress Speed of Reaction Wheels too fast.Power match controller (13) is controlled the opening time of Injection Pump, make when some e, h that delivery valve (6) opening time is Fig. 3 drop in curve df, fuel combustion pressure maximum point is neutral position, Fig. 3 mid point eh position in delivery valve (6) ON time, and other times section, when point e, the h that is Fig. 3 when delivery valve (6) opening time drops in curve fg, fuel combustion pressure maximum point is at f point invariant position.
In Fig. 1, reversing is to realize reversing by changing the airintake direction of clockwise and anticlockwise pneumatic motor (11), in Fig. 1, does not make.
Fig. 2 example is compared with Fig. 1 example, and different is pneumatic motor part and power match controller (13), and all the other are identical.Power match controller (13) can be according to being assemblied in the pneumatic motor position of output axle sensor (21) on pneumatic motor output shaft (16), the rotating speed of pneumatic motor output shaft (16) detected, make the opening angle of transfer valve (18), the angular range on pneumatic motor position of output axle changes with the rotating speed speed of pneumatic motor output shaft (16), while making pneumatic motor output shaft (16) rotating speed fast, the opening angle scope of transfer valve (18) on pneumatic motor position of output axle is little, when pneumatic motor output shaft (16) rotating speed is slow, the opening angle scope of transfer valve (18) on pneumatic motor position of output axle is large, increase the slewing range of pneumatic motor, in Fig. 2 example, automobile speed per hour is from being less than 5 kilometers while accelerating to 100 kilometers, under power match controller (13) is controlled, the angle of flow of transfer valve (18) is reduced to 20 degree from 150 degree.The clockwise and anticlockwise of pneumatic motor (11) is by power match controller (13), to detect the position of pneumatic motor position of output axle sensor (21), controls corresponding transfer valve and outlet valve action, reaches and controls the object that automobile advances or retreats.
Claims (6)
1. the pneumatic stepless speed variator that direct output high-pressure gas motor forms, by direct output high-pressure gas motor be connected pneumatic motor (11) with it and form, directly output high-pressure gas motor comprises motor (1), in motor (1) cylinder head, not only there are suction valve and outlet valve, it is characterized in that: motor (1) cylinder covers delivery valve (6) is also installed, directly output high-pressure gas motor also comprises the high pressure tube chamber (8) being connected with delivery valve (6), and the pressure transducer (7) of installing in high pressure tube chamber (8), form with power match controller (13), by power match controller (13), control delivery valve (6), corresponding conducting a period of time constantly of different crank positions in motor (1) power stroke, by delivery valve (6) control engine gas gas in the jar, be input to the air inflow of high pressure tube chamber (8), for directly driving, be connected pneumatic motor (11) rotation with high pressure tube chamber (8), delivery valve during other stroke (6) cuts out, by the pressurized gas that are stored in high pressure tube chamber (8), to pneumatic motor, export energy.
2. delivery valve according to claim 1 (6), described delivery valve (6) one end it is characterized in that is connected with delivery valve coil drive assembly (12), is controlled the keying of delivery valve (6) by the electromagnetic coil power on/off of delivery valve coil drive assembly (12) the inside.
3. power match controller according to claim 1 (13), it is characterized in that power match controller (13) input end is connected to pressure transducer (7), crank position sensing (5), output terminal is connected to delivery valve drive circuit (14), the slippage of high-voltage tube cavity pressure when the rise of high pressure tube chamber (8) internal pressure and delivery valve are closed while detecting delivery valve (6) unlatching by pressure transducer (7), under the programming instruction of the inner CPU processor of power match controller (13) is controlled, compare computing and draw the corresponding crank position of delivery valve switching signal next time, this signal amplifies by delivery valve drive circuit (14), driver output valve coil drives the electromagnetic coil in assembly (12) to drive delivery valve (6) action, pneumatic motor is rotated.
4. according to the power match controller (13) described in claim 1 or 3, it is characterized in that power match controller (13) output terminal is connected to Injection Pump drive circuit (10), according to crankshaft position sensor (5) power match controller (13), calculate speed of crankshaft and the position of delivery valve (6) start signal on bent axle next time, power match controller (13) calculates crank position corresponding when Injection Pump start signal arrives next time, output switching signal is to Injection Pump drive circuit (10), the action of control Injection Pump, make the leading or synchronous delivery valve opening time of position, fuel combustion maximal pressure force.
5. power match controller according to claim 1 (13), it is characterized in that power match controller (13) input end is connected with progress signal control end, astern signal control end and pneumatic motor output shaft position transducer (21), in inside, advance or retreat under instruction repertorie control, according to pneumatic motor position of output axle sensor (21), detect pneumatic motor piston (19) position, export corresponding switching signal to the transfer valve drive circuit (15) and the outlet valve drive circuit (26) that are connected with output terminal, drive transfer valve (18) and pneumatic motor outlet valve (24) action, pneumatic motor is rotated.
6. power match controller according to claim 5 (13), it is characterized in that power match controller (13) can be according to being assemblied in the pneumatic motor position of output axle sensor (21) on pneumatic motor output shaft (16), the rotating speed of pneumatic motor output shaft (16) detected, the opening angle scope that makes transfer valve (18) is the angular range on corresponding pneumatic motor position of output axle, rotating speed speed with pneumatic motor output shaft (16) changes, while making pneumatic motor output shaft (16) rotating speed fast, the opening angle scope of transfer valve (18) on pneumatic motor position of output axle is little, when pneumatic motor output shaft (16) rotating speed is slow, the opening angle scope of transfer valve (18) on pneumatic motor position of output axle is large, increase the slewing range of pneumatic motor.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210264988.3A CN103573400A (en) | 2012-07-30 | 2012-07-30 | Pneumatic continuously-variable transmission comprising engine capable of outputting high-pressure gas directly |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210264988.3A CN103573400A (en) | 2012-07-30 | 2012-07-30 | Pneumatic continuously-variable transmission comprising engine capable of outputting high-pressure gas directly |
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| CN103573400A true CN103573400A (en) | 2014-02-12 |
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| CN201210264988.3A Pending CN103573400A (en) | 2012-07-30 | 2012-07-30 | Pneumatic continuously-variable transmission comprising engine capable of outputting high-pressure gas directly |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106715904A (en) * | 2014-09-22 | 2017-05-24 | 惠而浦股份有限公司 | Improper opening detection method of multiple suction reciprocating compressor suction valve |
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| JPH1144227A (en) * | 1997-07-28 | 1999-02-16 | Isuzu Ceramics Kenkyusho:Kk | Structure of combustion chamber of engine |
| WO2002029216A1 (en) * | 2000-10-05 | 2002-04-11 | Renault Sport | Valve actuating device, and method for controlling same |
| CN2709660Y (en) * | 2004-05-19 | 2005-07-13 | 龚海舟 | Level chain operation stepless speed change IC engine |
| GB2464704A (en) * | 2008-10-23 | 2010-04-28 | Univ Brunel | Air motor |
| CN202866989U (en) * | 2012-07-30 | 2013-04-10 | 刘增兴 | Pneumatic continuously variable transmission composed of direct output high-pressure gas engine |
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2012
- 2012-07-30 CN CN201210264988.3A patent/CN103573400A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1144227A (en) * | 1997-07-28 | 1999-02-16 | Isuzu Ceramics Kenkyusho:Kk | Structure of combustion chamber of engine |
| WO2002029216A1 (en) * | 2000-10-05 | 2002-04-11 | Renault Sport | Valve actuating device, and method for controlling same |
| CN2709660Y (en) * | 2004-05-19 | 2005-07-13 | 龚海舟 | Level chain operation stepless speed change IC engine |
| GB2464704A (en) * | 2008-10-23 | 2010-04-28 | Univ Brunel | Air motor |
| CN202866989U (en) * | 2012-07-30 | 2013-04-10 | 刘增兴 | Pneumatic continuously variable transmission composed of direct output high-pressure gas engine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106715904A (en) * | 2014-09-22 | 2017-05-24 | 惠而浦股份有限公司 | Improper opening detection method of multiple suction reciprocating compressor suction valve |
| CN106715904B (en) * | 2014-09-22 | 2020-01-03 | 恩布拉科压缩机工业和制冷解决方案有限公司 | Method for detecting incorrect opening of suction valve of multi-suction reciprocating compressor |
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Application publication date: 20140212 |