CN103453132B - Control mechanism of numerically-controlltransmission transmission - Google Patents

Control mechanism of numerically-controlltransmission transmission Download PDF

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CN103453132B
CN103453132B CN201310370836.6A CN201310370836A CN103453132B CN 103453132 B CN103453132 B CN 103453132B CN 201310370836 A CN201310370836 A CN 201310370836A CN 103453132 B CN103453132 B CN 103453132B
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gear
double
cylinder
piston
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CN103453132A (en
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王建军
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王建军
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Abstract

The invention provides a kind of control mechanism of numerically-controlltransmission transmission, it is characterized in that comprising automatically controlled command signal unit, automatically controlled command signal unit comprises gear selecting switch on speed changer gear operation handle and corresponding gear and Gear-shift switch, gear selecting switch and Gear-shift switch and instruction performance element are connected, instruction execution unit is connected with gear selecting positional cylinder with gear shift positional cylinder respectively, gear shift positional cylinder is arranged vertically with gear selecting positional cylinder and the piston rod of the two to be connected with the gear shift arm of speed changer by plugging into, and the bar side end cap of gear shift positional cylinder and gear selecting positional cylinder is hinged on vehicle frame respectively.Compared with prior art, the present invention's control mechanism of numerically-controlltransmission transmission replaces original automotive transmission control lever, and universality is strong, can realize modularization, integrated production, without the need to considering the design of transmission control when car replacement is regenerated, Installation and Debugging are simple and convenient; After engage a gear completes, gear selecting positional cylinder and gear shift positional cylinder institute applied pressure sustainable existence, the phenomenon that can not lose rank.

Description

Control mechanism of numerically-controlltransmission transmission
Technical field
The present invention relates to automobile speed variator shift technical field, be specifically related to a kind of gearshift based on forced maneuver formula speed changer automobile.
Background technique
The transmission control of current domestic heavy card automobile generally adopts single lever-type, bowden cable formula and many bars by changing power support reversable three kinds of operating handle structures, they when Installation and Debugging more complicated, require great effort time-consuming.Interim problem is also there is: when new car dispatches from the factory, each position is in order to ensure durability in using process, fit tolerance is as far as possible few, this just causes new car engage a gear generally heavy, with reaching normal running moment after a period of time, feel pleasant, but problem also starts to come out simultaneously, especially there is phenomenon out of supply when road conditions difference or vibrations suddenly, reason out of supply has be each coordinate link lose damping function at two: one, the power produced in the displacement process of motor and operator cabin has exceeded the coupling mechanism force of gear, and gear is taken off naturally.After realizing gearshift when the power of mechanical pull bar is delivered to shifting of transmission arm, in normal running process, as occurred, road conditions shake suddenly the weight as liftable reducing bank at this moment mechanical pull bar itself, and the inertial force of generation can easily exceed the coupling mechanism force of gear, at this moment also can be out of supply.Two is because the gear locking spring of speed changer inside when new car dispatches from the factory and coupling mechanism force there are certain requirements, and substantially can meet usage requirement, with after a period of time, gear selecting moment and the engage a gear moment of speed changer have very large change.For problem out of supply, current automobile factory is difficult to take out a unified standard to production vehicles after sale, use client also all to represent acquiescence, but this problem is very important.Above problem is there is too in some developing countries.
How do now external colleagues address these problems? some developed countries in Europe adopt automatic transmission.China's economic development is now rapid, do you why not use for reference European countries colleague? there are two reasons, 1. due to technical reason, high the going against accepted conventions of price of import automatic transmission, the value of the profit that domestic production 5-8 platform automobile is created it would be better the value that an external speed changer produces, be the huge heavy truck of an exploitation price in the field of business about 200,000 yuan for automobile factory and terminal client, automatic transmission is about 100,000.2. due to China's actual conditions, there is the overload imagination in various degree in heavy truck, in addition road conditions are complicated, need go up a hill, lower weir, long-distance raid, should Duola hurry up, oil consumption is few again, and automatic transmission just can not play its performance, and forced maneuver formula speed changer and manual-type transmission still exist comparative advantages in this sense.
And no matter be single lever-type, bowden cable formula or many bars change the speed-changing lever of power support switching structure, when automobile carries out the remodeling replacement, need the specification and the size that redesign speed-changing lever, be unfavorable for integrated, the modularization development trend of industry.
Simultaneously, existing forced maneuver formula transmission control does not have automatic transmission control gears clear directly perceived, especially the vehicle more than 8 gears, need completely to rely on the feel of driver and experience just unlikely accidental shifting, do not resemble automatic transmission and limit by marking clearly gear dish with N shelves, P shelves etc.
To sum up reason, is badly in need of having a kind of Effector based on forced maneuver formula speed changer to change As-Is, has both met Domestic market needs, safe and reliable again, also retains original operating habit and has handling comfort.
I is engaged in the industry 12 years, resolve to research and develop a kind of electronic controlled transmission operating mechanism and be connected gap in external colleague, and meet suitable for China, the product that oneself compatriot likes, makes to enjoy the same enjoyment of same family car in driving procedure.Started in 2010 to do feasible analysis and scheme is determined, present technological scheme completes.
Summary of the invention
The object of the invention is to solve automotive transmission Installation and Debugging inconvenience that prior art exists, easily lose rank, the technical problems such as integrated, modularization cannot be realized, a kind of control mechanism of numerically-controlltransmission transmission is provided.
For realizing this object, technological scheme disclosed by the invention is:
This control mechanism of numerically-controlltransmission transmission, comprise automatically controlled command signal unit 10, automatically controlled command signal unit comprises gear selecting switch 10-2 on speed changer gear operation handle 10-1 and corresponding gear and Gear-shift switch 10-3, gear selecting switch 10-2 and Gear-shift switch 10-3 and instruction performance element 20 are connected, instruction execution unit 20 is connected with gear selecting positional cylinder 40 with gear shift positional cylinder 30 respectively, gear shift positional cylinder 30 is arranged vertically with gear selecting positional cylinder 40 and the piston rod of the two 50 to be connected with the gear shift arm of speed changer by plugging into, gear shift positional cylinder 30 and gear selecting positional cylinder 40 rodless side end cap are hinged on vehicle frame respectively.
Further, gear shift positional cylinder 30 and gear selecting positional cylinder 40 all have n linear array double-acting cylinder, n >=2, a piston is set in each double-acting cylinder, each double-acting cylinder two ends arrange gas port respectively, between two double-acting cylinders, hole between cylinder is set, between a piston rod and described cylinder, hole is sealed and matched and can axial translation, it is characterized in that: piston arranges piston hole, piston rod is arranged n width and be more than or equal to piston thickness, the slippage section of the narrow contracting of diameter, piston rod is divided into n+1 block resistance section by described slippage section, described piston hole and piston rod are sealed and matched in slippage section, when the length of slippage section is greater than the thickness of the piston be mated, piston can in slippage section with piston rod relative translation.
Further, gear shift positional cylinder 30 has the two ends arranging first piston 111, first double-acting cylinder in the first double-acting cylinder 121 of two linear array and the second double-acting cylinder 122, first double-acting cylinder and arranges the first gas port 101 and the second gas port 102 respectively; The two ends arranging the second piston 112, second double-acting cylinder in second double-acting cylinder arrange the 3rd gas port 103 and the 4th gas port 104 respectively; Gear shift positional cylinder piston rod is arranged the first slippage section 131 and the second slippage section 132 that width is greater than piston thickness, gear shift positional cylinder piston rod is divided into the first block resistance section 141, second block resistance section 142 and third gear resistance section 143 by the first described slippage section and the second slippage section; It is characterized in that: the difference of the length of the first slippage section 131 and the thickness of the second piston 112 equals the difference of the length of the second slippage section 132 and the thickness of first piston 111.
Gear selecting positional cylinder 40 has the 3rd double-acting cylinder 221 of three linear array, the 4th double-acting cylinder 222 and the 5th double-acting cylinder 223, the two ends arranging the 3rd piston the 211, three double-acting cylinder in 3rd double-acting cylinder arrange the 5th gas port 201 and the 6th gas port 202 respectively; The two ends arranging the 4th piston the 212, four double-acting cylinder in 4th double-acting cylinder 222 arrange the 7th gas port 203 and the 8th gas port 204 respectively; The two ends arranging the 5th piston the 213, five double-acting cylinder in 5th double-acting cylinder 223 arrange the 9th gas port 205 and the tenth gas port 206 respectively; Gear selecting positional cylinder piston rod is arranged width equals the 3rd slippage section 231 of the 3rd piston 211 thickness, width is greater than respective pistons thickness the 4th slippage section 232 and the 5th slippage section 233, gear selecting positional cylinder piston rod is divided into fourth gear to hinder section 241, fifth gear resistance section 242, sixth gear resistance section 243 and the 7th block resistance section 244 by the 3rd slippage section, the 4th slippage section and the 5th slippage section; It is characterized in that: the length of length+the four slippage section 232 of the length≤fifth gear resistance section 242 in hole between the cylinder between length+the three double-acting cylinder 221 of the 3rd double-acting cylinder 221 inner chamber and the 4th double-acting cylinder 222; The length of the length-five slippage section 233 of length >=the 5th double-acting cylinder 223 inner chamber of the length-four slippage section 232 of the 4th double-acting cylinder 222 inner chamber.
As preferably, the length=38mm of the length=the second slippage section 132 of the first described slippage section 131; Thickness=the 18mm of thickness=the second piston 112 of first piston 111; Length=the 58mm of length=the second double-acting cylinder 122 inner chamber of the first double-acting cylinder 121 inner chamber, the length in hole between the cylinder between length=the first double-acting cylinder 121 of the second block resistance section 142 and the second double-acting cylinder 122; If definition first to fourth gas port respectively air inlet time gear shift positional cylinder piston rod stop bit be respectively H1, H2, H 3 and H 4, then H1=H 4, H1-H2=H3-H4=20mm.
Length=the 50mm of length=the 5th double-acting cylinder 223 inner chamber of length=the 4th double-acting cylinder 222 inner chamber of the 3rd described double-acting cylinder 221 inner chamber; Thickness=the 18mm of thickness=the 5th piston 213 of thickness=the 4th piston 212 of the 3rd piston 211; Between the cylinder between the 3rd double-acting cylinder 221 and the 4th double-acting cylinder 222 length=between the 4th double-acting cylinder 222 and the 5th double-acting cylinder 223 in hole cylinder between the length=67mm in hole; Length=the 92mm of the length=sixth gear resistance section 243 of fifth gear resistance section 242; Length=the 32mm of length=the 5th slippage section 233 of the 4th slippage section 232; If definition the 5th to the 9th gas port respectively air inlet time gear selecting positional cylinder piston rod stop bit be respectively L1, L2, L3, L4 and L5, then: L2-L4=L5-L3=L3-L1=7mm, L2-L5=11mm.
Described gear selecting switch 10-2 and Gear-shift switch 10-3 is proximity switch, and described instruction execution unit 20 comprises some groups of solenoid valves.
Compared with prior art, the present invention's control mechanism of numerically-controlltransmission transmission replaces original automotive transmission control lever, and universality is strong, can realize modularization, integrated production, without the need to considering the design of transmission control when car replacement is regenerated, Installation and Debugging are simple and convenient; After engage a gear completes, gear selecting positional cylinder and gear shift positional cylinder institute applied pressure sustainable existence, the phenomenon that can not lose rank.
Accompanying drawing explanation
Fig. 1 is structure principle chart of the present invention;
Fig. 2 is the structural representation of gear shift positional cylinder;
Fig. 3 is the structural representation of gear selecting positional cylinder;
Stroke schematic diagram when Fig. 4 is the gas port air inlet of gear shift positional cylinder difference;
Stroke schematic diagram when Fig. 5 is the gas port air inlet of gear selecting positional cylinder difference;
Fig. 6 is existing ten gear car transmission gear spacing schematic diagram.
Embodiment
With reference to Fig. 1-Fig. 6
For ten gear trucies, this control mechanism of numerically-controlltransmission transmission is described, mainly comprises automatically controlled command signal unit 10, instruction execution unit 20, instruction performs terminal; Described automatically controlled command signal unit comprises gear selecting switch 10-2 on speed changer gear operation handle 10-1 and corresponding gear and Gear-shift switch 10-3; Described instruction execution unit 20 comprises 8 groups of solenoid valves, power supply needed for solenoid valve is from the storage battery of automobile and generator, pressurized air needed for solenoid valve is from the compressor (sharing source of the gas with brake system) of automobile, instruction performs terminal and comprises gear shift positional cylinder 30 and gear selecting positional cylinder 40, gear shift positional cylinder 30 is arranged vertically with gear selecting positional cylinder 40 and the piston rod of the two 50 to be connected with the gear shift arm of speed changer by plugging into, and gear shift positional cylinder 30 and gear selecting positional cylinder 40 rodless side end cap are hinged on vehicle frame respectively.
Gear shift positional cylinder there are two linear array with the second double-acting cylinder 122, first double-acting cylinder in first piston 111, first double-acting cylinder is set two ends the first gas port 101 and the second gas port 102 is set respectively; The two ends arranging the second piston 112, second double-acting cylinder in second double-acting cylinder arrange the 3rd gas port 103 and the 4th gas port 104 respectively; Gear shift positional cylinder piston rod is arranged the first slippage section 131 and the second slippage section 132 that width is greater than piston thickness, gear shift positional cylinder piston rod is divided into the first block resistance section 141, second block resistance section 142 and third gear resistance section 143 by the first described slippage section and the second slippage section; Length=the 38mm of the length=the second slippage section 132 of the first slippage section 131; Thickness=the 18mm of thickness=the second piston 112 of first piston 111; Length=the 58mm of length=the second double-acting cylinder 122 inner chamber of the first double-acting cylinder 121 inner chamber, the length in hole between the cylinder between length=the first double-acting cylinder 121 of the second block resistance section 142 and the second double-acting cylinder 122.
The working procedure of the first double-acting cylinder 121:
During the first gas port 101 air inlet, when in first piston 111 place first slippage section 131, first piston 111 is along the inwall downward translation of gear shift positional cylinder piston rod relative to the first double-acting cylinder 121, when first piston 111 contacts with the second block resistance section 142, first piston 111 promotes the downward translation of gear shift positional cylinder piston rod, and gear shift positional cylinder piston rod terminates in range H1 place;
During the second gas port 102 air inlet, when in first piston 111 place first slippage section 131, first piston 111 is along the inwall upwards translation of gear shift positional cylinder piston rod relative to the first double-acting cylinder 121, when first piston 111 contacts with the first block resistance section 141, first piston 111 promotes the upwards translation of gear shift positional cylinder piston rod, and gear shift positional cylinder piston rod terminates in minimum stroke H2 place;
During the work of the first double-acting cylinder 121, the thickness=38mm-18mm=20mm of length-the second piston 112 of reciprocating stroke=range H1-minimum stroke H2=second slippage section 132.
The working procedure of the second double-acting cylinder 122:
During the 3rd gas port 103 air inlet, when in the second piston 112 place second slippage section 132, second piston 112 is along the inwall downward translation of gear shift positional cylinder piston rod relative to the second double-acting cylinder 122, when the second piston 112 and third gear hinder section 143 contact time, second piston 112 promotes the downward translation of gear shift positional cylinder piston rod, and gear shift positional cylinder piston rod terminates in range H3 place;
During the 4th gas port 104 air inlet, when in the second piston 112 place first slippage section 132, second piston 112 is along the inwall upwards translation of gear shift positional cylinder piston rod relative to the second double-acting cylinder 122, when the second piston 112 contacts with the second block resistance section 142, second piston 112 promotes the upwards translation of gear shift positional cylinder piston rod, and gear shift positional cylinder piston rod terminates in minimum stroke H4 place;
During the work of the second double-acting cylinder 122, the thickness=38mm-18mm=20mm of the length-first piston 111 of reciprocating stroke=range H3-minimum stroke H4=first slippage section 131.
To sum up four strokes, minimum stroke H2=40mm during the work of range H3-first double-acting cylinder 121 during the work of the second double-acting cylinder 122, during the work of the first double-acting cylinder 121, during the work of range H1 with the second double-acting cylinder 122, minimum stroke H4 overlaps.
Gear selecting positional cylinder has the 3rd double-acting cylinder 221 of three linear array, the 4th double-acting cylinder 222 and the 5th double-acting cylinder 223, the two ends arranging the 3rd piston the 211, three double-acting cylinder in 3rd double-acting cylinder arrange the 5th gas port 201 and the 6th gas port 202 respectively; The two ends arranging the 4th piston the 212, four double-acting cylinder in 4th double-acting cylinder 222 arrange the 7th gas port 203 and the 8th gas port 204 respectively; The two ends arranging the 5th piston the 213, five double-acting cylinder in 5th double-acting cylinder 223 arrange the 9th gas port 205 and the tenth gas port 206 respectively; Gear selecting positional cylinder piston rod is arranged width equals the 3rd slippage section 231 of the 3rd piston 211 thickness, width is greater than respective pistons thickness the 4th slippage section 232 and the 5th slippage section 233, gear selecting positional cylinder piston rod is divided into fourth gear to hinder section 241, fifth gear resistance section 242, sixth gear resistance section 243 and the 7th block resistance section 244 by the 3rd slippage section, the 4th slippage section and the 5th slippage section; Preferably, the length=50mm of length=the 5th double-acting cylinder 223 inner chamber of length=the 4th double-acting cylinder 222 inner chamber of the 3rd double-acting cylinder 221 inner chamber; Thickness=the 18mm of thickness=the 5th piston 213 of thickness=the 4th piston 212 of the 3rd piston 211; Between the cylinder between the 3rd double-acting cylinder 221 and the 4th double-acting cylinder 222 length=between the 4th double-acting cylinder 222 and the 5th double-acting cylinder 223 in hole cylinder between the length=67mm in hole; Length=the 92mm of the length=sixth gear resistance section 243 of fifth gear resistance section 242; Length=the 32mm of length=the 5th slippage section 233 of the 4th slippage section 232.
The working procedure of the 3rd double-acting cylinder 221:
Because the 3rd piston 211 thickness is equal with the length of the 3rd slippage section 231, therefore the 3rd piston 211 is equivalent to be fixed on gear selecting positional cylinder piston rod, when the 5th gas port 201 air inlet, 3rd piston 211 promotes gear selecting positional cylinder piston rod to right translation, and gear selecting positional cylinder piston rod terminates in minimum stroke L1 place;
During the 6th gas port 202 air inlet, the 3rd piston 211 promotes gear selecting positional cylinder piston rod to left, and gear selecting positional cylinder piston rod terminates in range L2 place;
During the work of the 3rd double-acting cylinder 221, the thickness=50mm-18mm=32mm of length-three piston 112 of reciprocating stroke=range L2-minimum stroke L1=the 3rd double-acting cylinder 221 inner chamber.
The working procedure of the 4th double-acting cylinder 222:
During the 7th gas port 203 air inlet, when the 4th piston 212 is in the 4th slippage section 232,4th piston 212 along gear selecting positional cylinder piston rod relative to the inwall of the 4th double-acting cylinder 222 to right translation, when the 4th piston 212 and sixth gear hinder section 243 contact time, 4th piston 212 promotes gear selecting positional cylinder piston rod to right translation, and gear selecting positional cylinder piston rod terminates in minimum stroke L3 place;
During the 8th gas port 204 air inlet, when the 4th piston 212 is in the 4th slippage section 232,4th piston 212 along gear selecting positional cylinder piston rod relative to the inwall of the 4th double-acting cylinder 222 to left, when the 4th piston 212 and fifth gear hinder section 242 contact time, 4th piston 212 promotes gear selecting positional cylinder piston rod to left, and gear selecting positional cylinder piston rod terminates in range L4 place;
During the work of the 4th double-acting cylinder 222, the length=50mm-32mm=18mm of the length-four slippage section 232 of reciprocating stroke=range L4-minimum stroke L3=the 4th double-acting cylinder 222 inner chamber.
The working procedure of the 5th double-acting cylinder 223:
During the 9th gas port 205 air inlet, when the 5th piston 213 is in the 5th slippage section 233,5th piston 213 along gear selecting positional cylinder piston rod relative to the inwall of the 5th double-acting cylinder 223 to right translation, when the 5th piston 213 contacts with the 7th block resistance section 244,5th piston 213 promotes gear selecting positional cylinder piston rod to right translation, and gear selecting positional cylinder piston rod terminates in minimum stroke L5 place;
During the tenth gas port 206 air inlet, when the 5th piston 213 is in the 5th slippage section 233,5th piston 213 along gear selecting positional cylinder piston rod relative to the inwall of the 5th double-acting cylinder 223 to left, when the 5th piston 213 and sixth gear hinder section 243 contact time, 5th piston 213 promotes gear selecting positional cylinder piston rod to left, and gear selecting positional cylinder piston rod terminates in range L6 place;
During the work of the 5th double-acting cylinder 223, the length=50mm-32mm=18mm of the length-five slippage section 233 of reciprocating stroke=range L6-minimum stroke L5=the 5th double-acting cylinder 223 inner chamber.
To sum up six strokes:
L2-L1=32mm;
Length=the 92-67+32-50=7mm of length-four double-acting cylinder 222 inner chamber of length+the four slippage section 232 in hole between the cylinder between length-four double-acting cylinder 222 of L2-L4=sixth gear resistance section 243 and the 5th double-acting cylinder 223;
Length=the 92+32-67-50=7mm of length-four double-acting cylinder 222 inner chamber in hole between the cylinder between length-three double-acting cylinder 221 of length+the four slippage section 232 of L3-L1=fifth gear resistance section 242 and the 4th double-acting cylinder 222;
Length=92 mm-67 mm+32 mm-50 mm=7mm of length-five double-acting cylinder 223 inner chamber of length+the five slippage section 233 in hole between the cylinder between length-four double-acting cylinder 222 of L5-L 3=sixth gear resistance section 243 and the 5th double-acting cylinder 223;
L2-L6=0
L4-L5=(L2-L1)-(L2-L4)-(L5-L3)-(L3-L1)=32-7-7-7=11mm。
As shown in Figure 6, the gear selecting distance a between five adjacent two gears of range fork, b, c, d are respectively 7mm, 11mm, 7mm, 7mm, and the gear shift stroke X of range fork is 40mm in the gear distribution of known current ten gear vehicle speed changers.
Wherein the 4th gas port 104 and the tenth gas port 206 are given it up.L2 corresponds to R-1 gear, and L1 corresponds to 8-9 gears, and L4 corresponds to 2-3 gear, and L3 corresponds to 6-7 gear, and L5 corresponds to 4-5 gear; L2-L4=gear shift=7mm; L4-L5=gear selecting=11mm; L5-L 3=c=7mm; L3-L1=d=7mm.H3-H2=X=40mm。
According to above-mentioned corresponding relation, the annexation of 5 gas ports on 8 solenoid valves in instruction execution unit 20 and gear selecting switch 10-2, the Gear-shift switch 10-3 in automatically controlled command signal unit 10, three gas ports on gear shift positional cylinder 30 and gear selecting positional cylinder 40 is:
First gas port 101 is connected with sebific duct with the air outlet of the first solenoid valve 20-1, is connected for providing retrace (neutral) electrical signal after 5 Gear-shift switch 10-3 placed in the middle in automatically controlled command signal unit 10 connect with the first solenoid valve 20-1;
Second gas port 102 is connected with sebific duct with the air outlet of the second solenoid valve 20-2, and in automatically controlled command signal unit 10,5 Gear-shift switch 10-3 of below are connected for providing lower gear electrical signal with the second solenoid valve 20-2 after connecting;
3rd gas port 103 is connected with sebific duct with the air outlet of the 3rd solenoid valve 20-3, and in automatically controlled command signal unit 10,5 Gear-shift switch 10-3 of top are connected for providing the electrical signal that performs with the 3rd solenoid valve 20-3 after connecting;
5th gas port 201 is connected with sebific duct with the air outlet of the 4th solenoid valve 20-4, and in automatically controlled command signal unit 10, two gear selecting switch 10-2 up and down of position, R-1 are connected for providing R-1 grade electrical signal with the 4th solenoid valve 20-4 after connecting;
6th gas port 202 is connected with sebific duct with the air outlet of the 5th solenoid valve 20-5, and in automatically controlled command signal unit 10, two gear selecting switch 10-2 up and down of 8-9 positions are connected for providing 8-9 grades of electrical signal with the 5th solenoid valve 20-4 after connecting;
7th gas port 203 is connected with sebific duct with the air outlet of the 6th solenoid valve 20-6, and in automatically controlled command signal unit 10, two gear selecting switch 10-2 up and down of 6-7 positions are connected for providing 6-7 grades of electrical signal with the 6th solenoid valve 20-6 after connecting;
8th gas port 204 is connected with sebific duct with the air outlet of the 7th solenoid valve 20-7, and in automatically controlled command signal unit 10, two gear selecting switch 10-2 up and down of 2-3 positions are connected for providing 2-3 grades of electrical signal with the 7th solenoid valve 20-7 after connecting;
9th gas port 205 is connected with sebific duct with the air outlet of the 8th solenoid valve 20-8, and in automatically controlled command signal unit 10, two gear selecting switch 10-2 up and down of 4-5 positions are connected for providing 4-5 grades of electrical signal with the 8th solenoid valve 20-7 after connecting;
Control route is as follows:
When first: Joystick 10-1 arrival removes the position, somewhere of middle part neutral, corresponding gear selecting switch 10-2 or Gear-shift switch 10-3 sends gear selecting or shifting commands;
Second: in instruction execution unit, except the first solenoid valve 20-1, corresponding solenoid valve is opened;
3rd: the gear selecting positional cylinder in instruction execution terminal or gear shift positional cylinder make displacement by instruction;
4th: power transmission is in shift of transmission arm;
5th: gear arm drives transmission gear to put in place.
6th: Joystick 10-1 when arriving middle part neutral gear position, five gear selecting switch 10-3 placed in the middle one of them send and pluck a grade instruction;
7th: the solenoid valve 20-1 in instruction execution unit closes and is vented;
8th: reset displacement is made in the work of the first double-acting cylinder 121 in gear shift positional cylinder;
9th: recovering state neutral position state, engage a gear is plucked shelves and has been circulated.
Below to put in the first speed illustratively real work flow process:
Joystick 10-1 chooses 1 file location, Joystick 10-1 successively with the gear selecting switch 102 of 1 file location and Gear-shift switch 103 close, first gear selecting switch 102 sends command signal control the 4th solenoid valve 20-4 and opens, 5th gas port 201 air inlet, gear selecting positional cylinder piston rod retracts to minimum stroke position; Then Gear-shift switch 103 sends command signal and controls the second solenoid valve 20-2 and open, and the second gas port 102 air inlet, gear shift positional cylinder piston rod retracts to minimum stroke position, and moment is transmitted to shift of transmission arm and completes engage a gear, and vehicle starts normal traveling.Pluck shelves operation: Joystick 10-1 moves on to when reaching center, R-1 (neutral), gear selecting switch 102 sends command signal control the 4th solenoid valve 20-4 and cuts out, air is connected in 5th gas port 201 air inlet, make command terminal stop displacement and accomplish quick condition simultaneously, make it can not affect next instruction and perform; Joystick 10-1 and high order end that Gear-shift switch 10-3 placed in the middle is close, Gear-shift switch 10-3 sends command signal and controls the first solenoid valve 20-1 and open, first gas port 101 air inlet, gear shift positional cylinder piston rod comparatively stretches out 20mm in origin-location, moment is transmitted to shift of transmission arm and completes and pluck shelves, vehicle is in neutral position state, and pluck from putting in the first speed to neutral, circulation completes.Other gear position operation by that analogy.
Above-described embodiment, only for technical conceive of the present invention and feature are described, its object is to person skilled in the art can be understood content of the present invention and implement according to this, can not limit the scope of the invention with this.The numerical control speed-changer operation device of such as seven gears and 12 gear automobiles can be derived from above-mentioned principle.All equivalences done according to Spirit Essence of the present invention change or modify, and all should be encompassed within protection scope of the present invention.

Claims (7)

1. control mechanism of numerically-controlltransmission transmission, it is characterized in that comprising automatically controlled command signal unit (10), automatically controlled command signal unit comprises gear selecting switch (10-2) on speed changer gear operation handle (10-1) and corresponding gear and Gear-shift switch (10-3), gear selecting switch (10-2) and Gear-shift switch (10-3) and instruction performance element (20) are connected, instruction execution unit (20) is connected with gear selecting positional cylinder (40) with gear shift positional cylinder (30) respectively, gear shift positional cylinder (30) is arranged vertically with gear selecting positional cylinder (40) and the piston rod of the two is connected with the gear shift arm of speed changer by plug into (50), gear shift positional cylinder (30) and gear selecting positional cylinder (40) rodless side end cap are hinged on vehicle frame respectively, described gear shift positional cylinder (30) and gear selecting positional cylinder (40) all have n linear array double-acting cylinder, n >=2, a piston is set in each double-acting cylinder, each double-acting cylinder two ends arrange gas port respectively, between two double-acting cylinders, hole between cylinder is set, between a piston rod and described cylinder, hole is sealed and matched and can axial translation, piston arranges piston hole, piston rod is arranged n width and be more than or equal to piston thickness, the slippage section of the narrow contracting of diameter, piston rod is divided into n+1 block resistance section by described slippage section, described piston hole and piston rod are sealed and matched in slippage section, when the length of slippage section is greater than the thickness of the piston be mated, piston can in slippage section with piston rod relative translation.
2. control mechanism of numerically-controlltransmission transmission according to claim 1, it is characterized in that described gear shift positional cylinder (30) has the first double-acting cylinder (121) and second double-acting cylinder (122) of two linear array, first piston (111) is set in the first double-acting cylinder, the two ends of the first double-acting cylinder arrange the first gas port (101) respectively and the second gas port (102); Arrange the second piston (112) in second double-acting cylinder, the two ends of the second double-acting cylinder arrange the 3rd gas port (103) and the 4th gas port (104) respectively; Gear shift positional cylinder piston rod is arranged the first slippage section (131) and the second slippage section (132) that width is greater than piston thickness, gear shift positional cylinder piston rod is divided into the first block resistance section (141), the second block resistance section (142) and third gear to hinder section (143) by the first described slippage section and the second slippage section; The difference of the length of the first slippage section (131) and the thickness of the second piston (112) equals the difference of the length of the second slippage section (132) and the thickness of first piston (111).
3. control mechanism of numerically-controlltransmission transmission according to claim 1, it is characterized in that described gear selecting positional cylinder (40) has the 3rd double-acting cylinder (221) of three linear array, the 4th double-acting cylinder (222) and the 5th double-acting cylinder (223), arrange the 3rd piston (211) in 3rd double-acting cylinder, the two ends of the 3rd double-acting cylinder arrange the 5th gas port (201) and the 6th gas port (202) respectively; Arrange the 4th piston (212) in 4th double-acting cylinder (222), the two ends of the 4th double-acting cylinder arrange the 7th gas port (203) and the 8th gas port (204) respectively; Arrange the 5th piston (213) in 5th double-acting cylinder (223), the two ends of the 5th double-acting cylinder arrange the 9th gas port (205) and the tenth gas port (206) respectively; Gear selecting positional cylinder piston rod is arranged width equals the 3rd slippage section (231) of the 3rd piston (211) thickness, width is greater than respective pistons thickness the 4th slippage section (232) and the 5th slippage section (233), gear selecting positional cylinder piston rod is divided into fourth gear to hinder section (241), fifth gear resistance section (242), sixth gear resistance section (243) and the 7th block resistance section (244) by the 3rd slippage section, the 4th slippage section and the 5th slippage section; The length of the length+the four slippage section (232) of length≤fifth gear resistance section (242) in hole between the cylinder between the length+the three double-acting cylinder (221) of the 3rd double-acting cylinder (221) inner chamber and the 4th double-acting cylinder (222); The length of length-five slippage section (233) of length >=the 5th double-acting cylinder (223) inner chamber of length-four slippage section (232) of the 4th double-acting cylinder (222) inner chamber.
4. control mechanism of numerically-controlltransmission transmission according to claim 2, is characterized in that the length=38mm of the length=the second slippage section (132) of the first described slippage section (131); Thickness=the 18mm of thickness=the second piston (112) of first piston (111); Length=the 58mm of length=the second double-acting cylinder (122) inner chamber of the first double-acting cylinder (121) inner chamber, the length in hole between the cylinder between length=the first double-acting cylinder (121) of the second block resistance section (142) and the second double-acting cylinder (122); If definition first to fourth gas port respectively air inlet time gear shift positional cylinder piston rod stop bit be respectively H1, H2, H 3 and H 4, then H1=H 4, H1-H2=H3-H4=20mm.
5. control mechanism of numerically-controlltransmission transmission according to claim 3, is characterized in that the length=50mm of length=the 5th double-acting cylinder (223) inner chamber of length=the 4th double-acting cylinder (222) inner chamber of the 3rd described double-acting cylinder (221) inner chamber; Thickness=the 18mm of thickness=the 5th piston (213) of thickness=the 4th piston (212) of the 3rd piston (211); Between the cylinder between the 3rd double-acting cylinder (221) and the 4th double-acting cylinder (222) length=between the 4th double-acting cylinder (222) and the 5th double-acting cylinder (223) in hole cylinder between the length=67mm in hole; Length=the 92mm of length=sixth gear resistance section (243) of fifth gear resistance section (242); Length=the 32mm of length=the 5th slippage section (233) of the 4th slippage section (232); If definition the 5th to the 9th gas port respectively air inlet time gear selecting positional cylinder piston rod stop bit be respectively L1, L2, L3, L4 and L5, then: L2-L4=L5-L3=L3-L1=7mm, L2-L5=11mm.
6. control mechanism of numerically-controlltransmission transmission according to claim 1, is characterized in that described gear selecting switch (10-2) and Gear-shift switch (10-3) are proximity switch.
7. control mechanism of numerically-controlltransmission transmission according to claim 1, is characterized in that described instruction execution unit (20) comprises 8 groups of solenoid valve (20-1; 20-2; 20-8).
CN201310370836.6A 2013-08-22 2013-08-22 Control mechanism of numerically-controlltransmission transmission Active CN103453132B (en)

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CN111649129A (en) * 2020-05-29 2020-09-11 陕西法士特齿轮有限责任公司 Cylinder for realizing four gear selecting positions on actuating mechanism of AMT (automated mechanical transmission)

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CN203404355U (en) * 2013-08-22 2014-01-22 王建军 Numerical control speed changer control mechanism

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US5035113A (en) * 1988-05-19 1991-07-30 Csepel Autogyar Electropneumatic remote control for shifting the mechanical transmission of a motor vehicle
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