CN203404355U - Numerical control speed changer control mechanism - Google Patents

Numerical control speed changer control mechanism Download PDF

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Publication number
CN203404355U
CN203404355U CN201320515466.6U CN201320515466U CN203404355U CN 203404355 U CN203404355 U CN 203404355U CN 201320515466 U CN201320515466 U CN 201320515466U CN 203404355 U CN203404355 U CN 203404355U
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double acting
cylinder
piston
length
slippage
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王建军
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王建军
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Abstract

The utility model provides a numerical control speed changer control mechanism. The numerical control speed changer control mechanism is characterized by comprising an electronic control command signal unit, a command executing unit and a command executing terminal. The numerical control speed changer control mechanism is characterized in that that the electronic control command signal unit comprises a gear control handle, gear selecting switches and gear changing switches, and the gear selecting switches and the gear changing switches are located on the corresponding gears and are connected with the command executing unit which is connected with the command executing terminal. An original automotive speed changer control lever is replaced by the numerical control speed changer control mechanism. Compared with the prior art, the numerical control speed changer control mechanism has the advantages that the universality is strong, modular and integrated production can be achieved, the design of the speed changer control mechanism does not need to be taken into consideration when an automobile is updated, and the numerical control speed changer control mechanism is easy and convenient to install and adjust, and due to the fact that after the gear is engaged, the pressure exerted by a gear selecting multidigit cylinder and a gear changing multidigit cylinder exists continuously, gear falling cannot happen.

Description

Numerical control transmission control
Technical field
The present invention relates to shifting vehicle gearbox technical field, be specifically related to a kind of gearshift based on forced maneuver formula speed changer automobile.
Background technique
The transmission control of domestic heavy card automobile generally adopts single lever-type, flexible axle boom guy type and many bars by changing three kinds of operating handle structures of power support reversable at present.They when Installation and Debugging more complicated, require great effort time-consuming.In using process, also there is interim problem: when new car dispatches from the factory, each position is in order to guarantee durability, fit tolerance is as far as possible few, it is generally heavy that this just causes new car to put into gear, with reaching after a period of time normal running moment, feel pleasant, but simultaneously problem also starts to come out, especially poor in road conditions or occur off-gear phenomenon while shaking suddenly.Off-gear reason has two: one, and each coordinates link to lose damping function, the power producing in the displacement process of motor and operator cabin has surpassed the coupling mechanism force of gear, gear is taken off naturally, when the power of mechanical pull bar is delivered to shift of transmission arm, realize after gearshift, in normal running process, as there is the at this moment weight of mechanical pull bar itself of suddenly vibrations of road conditions as liftable reducing bank, the inertial force of generation is easy to the coupling mechanism force over gear, at this moment also can off-gear; The 2nd, while dispatching from the factory due to new car, gear locking spring and the coupling mechanism force of speed changer inside there are certain requirements, and substantially can meet usage requirement, and with after a period of time, block selecting moment and the moment of putting into gear of speed changer have very large change.For the problem of off-gear, at present automobile factory is difficult to take out a unified standard to vehicle product after sale, use client also all to represent to give tacit consent to, but this problem is very important.In some developing countries, there is too above problem.
How do external colleagues address these problems now? some developed countries in Europe adopt automatic transmission.China's economic development is now rapid, do you why not use for reference the colleague of European countries? there are two reasons: the one, 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, not as good as the external value that speed changer produces, is a huge exploitation for automobile factory and terminal client.200,000 yuan of left and right of heavy truck price in the field of business, automatic transmission is in 100,000 left and right; The 2nd, due to China's actual conditions, there is the overload imagination in various degree in heavy truck, in addition road conditions are complicated, need to go up a hill, lower weir, long-distance raid, should Duola hurry up, oil consumption is few again, and automatic transmission just can not brought into play its performance, and in this meaning, forced maneuver formula speed changer is that manual-type transmission still exists comparative advantages.
And no matter be the speed-changing lever that single lever-type, flexible axle boom guy type or many bars change power support switching structure, when automobile is retrofited the replacement, need to redesign specification and the size of 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 mechanism gear clear directly perceived, especially vehicle more than 8 gears, need to rely on driver's feel and the wrong gear of just unlikely extensions of experience completely, do not resemble automatic transmission by keeping off with N gear, P etc. and mark clearly position retaining disk and limit.
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 am engaged in the industry 12 years, resolve to research and develop a kind of electronic controlled transmission operating mechanism and am connected the gap in external colleague, meet product suitable for China, that own compatriot likes, make to enjoy in driving procedure the enjoyment that same family car is the same.In 2010, start to do feasible analysis and scheme and determine, technological scheme completes now.
Summary of the invention
The object of the invention is to solve automotive transmission Installation and Debugging inconvenience that prior art exists, easily fall gear, cannot realize the technical problems such as integrated, modularization, a kind of numerical control transmission control is provided.
For realizing this object, technological scheme disclosed by the invention is:
This numerical control transmission control, comprises automatically controlled command signal unit 10, instruction execution unit 20, and terminal is carried out in instruction; It is characterized in that automatically controlled command signal unit comprises block selecting switch 10-2 and the shift switch 10-3 on gear Joystick 10-1 and corresponding gear, block selecting switch 10-2 and shift switch 10-3 and instruction performance element 20 are connected, and instruction execution unit 20 and instructions are carried out terminal and are connected.
Further, instruction is carried out terminal and is comprised gearshift positional cylinder 30, block selecting positional cylinder 40 and plug into 50, described gearshift positional cylinder 30 is arranged vertically with described block selecting positional cylinder 40 and the piston rod of the two 50 is connected with the gear arm of speed changer by described plugging into, and gearshift positional cylinder 30 is hinged on vehicle frame respectively with the rodless side end cap of block selecting positional cylinder 40.
Further, gearshift positional cylinder 30 and block 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 arranges respectively gas/liquid mouth, 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 hole is set on piston, n width is set on piston rod and is 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 being mated, piston can be in slippage section and piston rod relative translation.
Further, gearshift positional cylinder 30 has the two ends that first piston 111, the first double acting cylinder be set in the first double acting cylinder 121 of two linear array and the second double acting cylinder 122, the first double acting cylinders the first gas/liquid mouth 101 and the second gas/liquid mouth 102 is set respectively; The two ends that the second piston 112, the second double acting cylinders are set in the second double acting cylinder arrange respectively the 3rd gas/liquid mouth 103 and the 4th gas/liquid mouth 104; On gearshift positional cylinder piston rod, the first slippage section 131 and the second slippage section 132 that width is greater than piston thickness is set, gearshift positional cylinder piston rod is divided into the first block resistance section 141, the second block resistance section 142 and the 3rd block resistance section 143 by the first described slippage section and the second slippage section; It is characterized in that: the difference of the thickness of the length of the first slippage section 131 and the second piston 112 equals the poor of the length of the second slippage section 132 and the thickness of first piston 111.
Block selecting positional cylinder 40 has the 3rd double acting cylinder 221, the 4th double acting cylinder 222 and the 5th double acting cylinder 223 of three linear array, the two ends that the 3rd piston 211, the three double acting cylinders are set in the 3rd double acting cylinder arrange respectively the 5th gas/liquid mouth 201 and the 6th gas/liquid mouth 202; The interior two ends that the 4th piston 212, the four double acting cylinders are set of the 4th double acting cylinder 222 arrange respectively the 7th gas/liquid mouth 203 and the 8th gas/liquid mouth 204; The interior two ends that the 5th piston 213, the five double acting cylinders are set of the 5th double acting cylinder 223 arrange respectively the 9th gas/liquid mouth 205 and the tenth gas/liquid mouth 206; The 4th slippage section 232 and the 5th slippage section 233 that the 3rd slippage section 231, width that width equals the 3rd piston 211 thickness are greater than respective pistons thickness are set on block selecting positional cylinder piston rod, and block selecting positional cylinder piston rod is divided into the 4th block resistance section 241, the 5th block resistance section 242, the 6th block 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 the length+four slippage section 232 of the length≤five block resistance section 242 in hole between length+three double acting cylinder 221 of the 3rd double acting cylinder 221 inner chambers and the cylinder between the 4th double acting cylinder 222; The length of length-five slippage sections 233 of length >=five double acting cylinder 223 inner chambers of length-tetra-slippage sections 232 of the 4th double acting cylinder 222 inner chambers.
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 chambers of the first double acting cylinder 121 inner chambers, 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 stop bit of positional cylinder piston rod of shifting gears when first to fourth gas/liquid mouth enters gas/liquid respectively if define is respectively H1, H2, H 3 and H 4, and H1=H 4, H1-H2=H3-H4=20mm.
Length=the 50mm of length=five double acting cylinder 223 inner chambers of length=four double acting cylinder 222 inner chambers of the 3rd described double acting cylinder 221 inner chambers; Thickness=the 18mm of thickness=five piston 213 of the thickness of the 3rd piston 211=four piston 212; Length=the 67mm in hole between length=four double acting cylinder 222 in hole and the cylinder between the 5th double acting cylinder 223 between the cylinder between the 3rd double acting cylinder 221 and the 4th double acting cylinder 222; Length=the 92mm of the length of the 5th block resistance section 242=six block resistance section 243; Length=the 32mm of the length of the 4th slippage section 232=five slippage section 233; If when defining the 5th to the 9th gas/liquid mouth and entering gas/liquid respectively, the stop bit of block selecting positional cylinder piston rod is respectively L1, L2, L3, L4 and L5: L2-L4=L5-L3=L3-L1=7mm, L2-L5=11mm.
Described block selecting switch 10-2 and shift switch 10-3 are approach switch, and described instruction execution unit 20 comprises some groups of solenoid valves.
Compared with prior art, the present invention replaces original automotive transmission control lever with numerical control transmission control, and universality is strong, can realize modularization, integrated production, when car replacement is regenerated, without the design of considering transmission control, Installation and Debugging are simple and convenient; After having put into gear, block selecting positional cylinder and gearshift positional cylinder institute applied pressure sustainable existence, can not fall the phenomenon of gear.
Accompanying drawing explanation
Fig. 1 is structure principle chart of the present invention.
Fig. 2 is the structural representation of gearshift positional cylinder.
Fig. 3 is the structural representation of block selecting positional cylinder.
Stroke schematic diagram when Fig. 4 enters gas/liquid for the different gas/liquid mouths of gearshift positional cylinder.
Fig. 5 is the stroke schematic diagram of the different gas/liquid mouths of block selecting positional cylinder while entering gas/liquid.
Fig. 6 is existing ten gear automotive transmission gear spacing schematic diagram.
Embodiment
With reference to Fig. 1-Fig. 6.
Take ten gear trucies as example illustrates this numerical control transmission control, mainly comprise automatically controlled command signal unit 10, instruction execution unit 20, terminal is carried out in instruction; Described automatically controlled command signal unit comprises block selecting switch 10-2 and the shift switch 10-3 on gear Joystick 10-1 and corresponding gear; Described instruction execution unit 20 comprises 8 groups of solenoid valves, the required power supply of solenoid valve is from storage battery and the generator of automobile, the required pressurized air of solenoid valve shares source of the gas from compressor and the brake system of automobile, instruction is carried out terminal and is comprised gearshift positional cylinder 30 and block selecting positional cylinder 40, gearshift positional cylinder 30 is arranged vertically with block selecting positional cylinder 40 and the piston rod of the two 50 is connected with the gear arm of speed changer by plugging into, and the rodless side end cap of gearshift positional cylinder 30 and block selecting positional cylinder 40 is hinged on vehicle frame respectively.
Gearshift positional cylinder there are two linear array with the second double acting cylinder 122, the first double acting cylinders in first piston 111, the first double acting cylinder be set two ends the first gas/liquid mouth 101 and the second gas/liquid mouth 102 are set respectively; The two ends that the second piston 112, the second double acting cylinders are set in the second double acting cylinder arrange respectively the 3rd gas/liquid mouth 103 and the 4th gas/liquid mouth 104; On gearshift positional cylinder piston rod, the first slippage section 131 and the second slippage section 132 that width is greater than piston thickness is set, gearshift positional cylinder piston rod is divided into the first block resistance section 141, the second block resistance section 142 and the 3rd block 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 chambers of the first double acting cylinder 121 inner chambers, 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:
When the first gas/liquid mouth 101 air inlets or oil-feed, when first piston 111 place's the first slippage sections 131 are when interior, first piston 111 is the downward translation of inwall with respect to the first double acting cylinder 121 along gearshift positional cylinder piston rod, when first piston 111 contacts with the second block resistance section 142, first piston 111 promotes the downward translation of gearshift positional cylinder piston rod, and gearshift positional cylinder piston rod terminates in range H1 place;
When the second gas/liquid mouth 102 air inlets or oil-feed, when first piston 111 place's the first slippage sections 131 are when interior, first piston 111 along gearshift positional cylinder piston rod with respect to the translation that makes progress of the inwall of the first double acting cylinder 121, when first piston 111 contacts with the first block resistance section 141, first piston 111 promotes the translation that makes progress of gearshift positional cylinder piston rods, and gearshift 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=the second slippage section 132.
The working procedure of the second double acting cylinder 122:
When the 3rd gas/liquid mouth 103 air inlets or oil-feed, when second piston 112 place's the second slippage sections 132 are when interior, the second piston 112 is the downward translation of inwall with respect to the second double acting cylinder 122 along gearshift positional cylinder piston rod, when the second piston 112 contacts with the 3rd block resistance section 143, the second piston 112 promotes the downward translation of gearshift positional cylinder piston rod, and gearshift positional cylinder piston rod terminates in range H3 place;
When the 4th gas/liquid mouth 104 air inlets or oil-feed, when second piston 112 place's the first slippage sections 132 are when interior, the second piston 112 along gearshift positional cylinder piston rod with respect to the translation that makes progress of the inwall of the second double acting cylinder 122, when the second piston 112 contacts with the second block resistance section 142, the second piston 112 promotes the translation that makes progress of gearshift positional cylinder piston rods, and gearshift 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=the first slippage section 131.
Four strokes to sum up, minimum stroke H2=40mm during the work of range H3-the 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, minimum stroke H4 overlaps during the work of range H1 and the second double acting cylinder 122.
Block selecting positional cylinder has the 3rd double acting cylinder 221, the 4th double acting cylinder 222 and the 5th double acting cylinder 223 of three linear array, the two ends that the 3rd piston 211, the three double acting cylinders are set in the 3rd double acting cylinder arrange respectively the 5th gas/liquid mouth 201 and the 6th gas/liquid mouth 202; The interior two ends that the 4th piston 212, the four double acting cylinders are set of the 4th double acting cylinder 222 arrange respectively the 7th gas/liquid mouth 203 and the 8th gas/liquid mouth 204; The interior two ends that the 5th piston 213, the five double acting cylinders are set of the 5th double acting cylinder 223 arrange respectively the 9th gas/liquid mouth 205 and the tenth gas/liquid mouth 206; The 4th slippage section 232 and the 5th slippage section 233 that the 3rd slippage section 231, width that width equals the 3rd piston 211 thickness are greater than respective pistons thickness are set on block selecting positional cylinder piston rod, and block selecting positional cylinder piston rod is divided into the 4th block resistance section 241, the 5th block resistance section 242, the 6th block resistance section 243 and the 7th block resistance section 244 by the 3rd slippage section, the 4th slippage section and the 5th slippage section; As preferred version, the length=50mm of length=five double acting cylinder 223 inner chambers of length=four double acting cylinder 222 inner chambers of the 3rd double acting cylinder 221 inner chambers; Thickness=the 18mm of thickness=five piston 213 of the thickness of the 3rd piston 211=four piston 212; Length=the 67mm in hole between length=four double acting cylinder 222 in hole and the cylinder between the 5th double acting cylinder 223 between the cylinder between the 3rd double acting cylinder 221 and the 4th double acting cylinder 222; Length=the 92mm of the length of the 5th block resistance section 242=six block resistance section 243; Length=the 32mm of the length of the 4th slippage section 232=five slippage section 233.
The working procedure of the 3rd double acting cylinder 221:
Equal in length due to the 3rd piston 211 thickness and the 3rd slippage section 231, therefore the 3rd piston 211 is equivalent to be fixed on block selecting positional cylinder piston rod, when the 5th gas/liquid mouth 201 air inlets or oil-feed, the 3rd piston 211 promotes block selecting positional cylinder piston rod to right translation, and block selecting positional cylinder piston rod terminates in minimum stroke L1 place;
When the 6th gas/liquid mouth 202 air inlets or oil-feed, the 3rd piston 211 promotes block selecting positional cylinder piston rod to left, and block 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-tri-pistons 112 of reciprocating stroke=range L2-minimum stroke L1=the 3rd double acting cylinder 221 inner chambers.
The working procedure of the 4th double acting cylinder 222:
When the 7th gas/liquid mouth 203 air inlets or oil-feed, when the 4th piston 212 is in the 4th slippage section 232 when interior, the 4th piston 212 along block selecting positional cylinder piston rod with respect to the inwall of the 4th double acting cylinder 222 to right translation, when the 4th piston 212 contacts with the 6th block resistance section 243, the 4th piston 212 promotes block selecting positional cylinder piston rod to right translation, and block selecting positional cylinder piston rod terminates in minimum stroke L3 place;
When the 8th gas/liquid mouth 204 air inlets or oil-feed, when the 4th piston 212 is in the 4th slippage section 232 when interior, the 4th piston 212 along block selecting positional cylinder piston rod with respect to the inwall of the 4th double acting cylinder 222 to left, when the 4th piston 212 contacts with the 5th block resistance section 242, the 4th piston 212 promotes block selecting positional cylinder piston rod to left, and block 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 length-tetra-slippage sections 232 of reciprocating stroke=range L4-minimum stroke L3=the 4th double acting cylinder 222 inner chambers.
The working procedure of the 5th double acting cylinder 223:
When the 9th gas/liquid mouth 205 air inlets or oil-feed, when the 5th piston 213 is in the 5th slippage section 233 when interior, the 5th piston 213 along block selecting positional cylinder piston rod with respect 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, the 5th piston 213 promotes block selecting positional cylinder piston rod to right translation, and block selecting positional cylinder piston rod terminates in minimum stroke L5 place;
When the tenth gas/liquid mouth 206 air inlets or oil-feed, when the 5th piston 213 is in the 5th slippage section 233 when interior, the 5th piston 213 along block selecting positional cylinder piston rod with respect to the inwall of the 5th double acting cylinder 223 to left, when the 5th piston 213 contacts with the 6th block resistance section 243, the 5th piston 213 promotes block selecting positional cylinder piston rod to left, and block 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 length-five slippage sections 233 of reciprocating stroke=range L6-minimum stroke L5=the 5th double acting cylinder 223 inner chambers.
Six strokes to sum up:
L2-L1=32mm;
Length=the 92-67+32-50=7mm of length-tetra-double acting cylinder 222 inner chambers of the length+four slippage section 232 in hole between length-tetra-double acting cylinders 222 of L2-L4=the 6th block resistance section 243 and the cylinder between the 5th double acting cylinder 223;
Length=the 92+32-67-50=7mm of length-tetra-double acting cylinder 222 inner chambers in hole between length-tri-double acting cylinders 221 of the length+four slippage section 232 of L3-L1=the 5th block resistance section 242 and the cylinder between the 4th double acting cylinder 222;
Mm-50, mm+32, mm-67, the length=92 mm=7mm of length-five double acting cylinder 223 inner chambers of the length+five slippage section 233 in hole between length-tetra-double acting cylinders 222 of L5-L 3=the 6th block resistance section 243 and the cylinder between the 5th double acting cylinder 223;
L2-L6=0
L4-L5=L2-L1-L2-L4-L5-L3-L3-L1=32-7-7-7=11mm。
The gear of known current ten gear vehicle transmissions distributes as shown in Figure 6, and the block selecting between five adjacent two gears of selector fork is respectively 7mm, 11mm, 7mm, 7mm apart from a, b, c, d, and the gearshift stroke X of selector fork is 40mm.
Wherein the 4th gas/liquid mouth 104 and the tenth gas/liquid mouth 206 are given it up.L2 is corresponding to R-1 gear, and L1 is corresponding to 8-9 gears, and L4 is corresponding to 2-3 gear, and L3 is corresponding to 6-7 gear, and L5 is corresponding to 4-5 gear; L2-L4=gearshift=7mm; L4-L5=block selecting=11mm; L5-L 3=c=7mm; L3-L1=d=7mm.H3-H2=X=40mm。
According to above-mentioned corresponding relation, three gas/liquid mouths on positional cylinder 30 of 8 solenoid valves in instruction execution unit 20 and block selecting switch 10-2, shift switch 10-3 in automatically controlled command signal unit 10, gearshift and the annexation of 5 gas/liquid mouths on block selecting positional cylinder 40 are:
The first gas/liquid mouth 101 is connected with sebific duct with the air outlet of the first solenoid valve 20-1, and in automatically controlled command signal unit 10,5 shift switch 10-3 placed in the middle are connected with the first solenoid valve 20-1 after connecting for gear neutral electrical signal is provided back;
The second gas/liquid mouth 102 is connected with sebific duct with the air outlet of the second solenoid valve 20-2, in automatically controlled command signal unit 10, after 5 shift switch 10-3 series connection of below, is connected for lower block electrical signal is provided with the second solenoid valve 20-2;
The 3rd gas/liquid mouth 103 is connected with sebific duct with the air outlet of the 3rd solenoid valve 20-3, in automatically controlled command signal unit 10, after 5 shift switch 10-3 series connection of top, is connected for upper gear electrical signal is provided with the 3rd solenoid valve 20-3;
The 5th gas/liquid mouth 201 is connected with sebific duct with the air outlet of the 4th solenoid valve 20-4, in automatically controlled command signal unit 10, after two block selecting switch 10-2 series connection up and down of position, R-1, is connected for R-1 gear electrical signal is provided with the 4th solenoid valve 20-4;
The 6th gas/liquid mouth 202 is connected with sebific duct with the air outlet of the 5th solenoid valve 20-5, in automatically controlled command signal unit 10, after two block selecting switch 10-2 series connection up and down of 8-9 positions, is connected for 8-9 gear electrical signal are provided with the 5th solenoid valve 20-4;
The 7th gas/liquid mouth 203 is connected with sebific duct with the air outlet of the 6th solenoid valve 20-6, in automatically controlled command signal unit 10, after two block selecting switch 10-2 series connection up and down of 6-7 positions, is connected for 6-7 gear electrical signal are provided with the 6th solenoid valve 20-6;
The 8th gas/liquid mouth 204 is connected with sebific duct with the air outlet of the 7th solenoid valve 20-7, in automatically controlled command signal unit 10, after two block selecting switch 10-2 series connection up and down of 2-3 positions, is connected for 2-3 gear electrical signal are provided with the 7th solenoid valve 20-7;
The 9th gas/liquid mouth 205 is connected with sebific duct with the air outlet of the 8th solenoid valve 20-8, in automatically controlled command signal unit 10, after two block selecting switch 10-2 series connection up and down of 4-5 positions, is connected for 4-5 gear electrical signal are provided with the 8th solenoid valve 20-7;
Control route is as follows:
First: when Joystick 10-1 arrives except the position, somewhere of middle part neutral, corresponding block selecting switch 10-2 or shift switch 10-3 send block selecting or shifting commands;
Second: in instruction execution unit, except the first solenoid valve 20-1, corresponding solenoid valve is opened;
The the 3rd: block selecting positional cylinder or gearshift positional cylinder that instruction is carried out in terminal are made displacement by instruction;
The the 4th: power transmission is in shift of transmission arm;
The the 5th: gear arm drives transmission gear to put in place;
The the 6th: when Joystick 10-1 arrives middle part neutral gear position, one of them sends five block selecting switch 10-3 placed in the middle and pluck gear instruction;
The the 7th: the solenoid valve 20-1 in instruction execution unit closes and exhaust;
The the 8th: reset displacement is made in the work of the first double acting cylinder 121 in gearshift positional cylinder;
The 9th: recovering state neutral position state, put into gear to pluck to keep off and circulated.
Take below and hang a gear and real work flow process is once described as example:
Joystick 10-1 chooses 1 gear and puts, Joystick 10-1 successively approaches with block selecting switch 102 and shift switch 103 that 1 gear is put, first block selecting switch 102 sends command signal and controls the 4th solenoid valve 20-4 unlatching, the 5th gas/liquid mouth 201 enters gas/liquid, and block selecting positional cylinder piston rod retracts to minimum stroke position; Then shift switch 103 sends command signal and controls the second solenoid valve 20-2 and open, and the second gas/liquid mouth 102 enters gas/liquid, and gearshift positional cylinder piston rod retracts to minimum stroke position, and moment is transmitted to shift of transmission arm and completes and put into gear, and vehicle starts normally to travel.Pluck gear operation: on Joystick 10-1, move on to while reaching center, R-1 neutral, block selecting switch 102 sends command signal control the 4th solenoid valve 20-4 and cuts out, the 5th gas/liquid mouth 201 enters gas/liquid and connects atmosphere, make command terminal stop displacement and accomplish quick condition simultaneously, make it can not affect next instruction and carry out; Joystick 10-1 and high order end that shift switch 10-3 placed in the middle approach, shift switch 10-3 sends command signal and controls the first solenoid valve 20-1 unlatching, the first gas/liquid mouth 101 enters gas/liquid, gearshift positional cylinder piston rod stretches out 20mm compared with origin-location, moment is transmitted to shift of transmission arm and completes and pluck gear, vehicle is in neutral position state, and from hanging a gear to plucking to neutral, circulation completes.Other gear operation by that analogy.
Above-described embodiment is only explanation technical conceive of the present invention and feature, and its object is to allow person skilled in the art can understand content of the present invention and implement according to this, can not limit the scope of the invention with this.For example the numerical control speed-changer operation device of seven gears and 12 gear automobiles can be derived from above-mentioned principle.All equivalences that Spirit Essence is done according to the present invention change or modify, within all should being encompassed in protection scope of the present invention.

Claims (9)

1. numerical control transmission control, comprises automatically controlled command signal unit (10), instruction execution unit (20), and terminal is carried out in instruction; It is characterized in that automatically controlled command signal unit comprises block selecting switch (10-2) and the shift switch (10-3) on gear Joystick (10-1) and corresponding gear, block selecting switch (10-2) and shift switch (10-3) and instruction performance element (20) are connected, and instruction execution unit (20) and instruction is carried out terminal and is connected.
2. the numerical control transmission control of claim 1, it is characterized in that instruction execution terminal comprises gearshift positional cylinder (30), block selecting positional cylinder (40) and plug into (50), described gearshift positional cylinder (30) is arranged vertically with described block selecting positional cylinder (40) and the piston rod of the two is connected with the gear arm of speed changer by described plugging into (50), and gearshift positional cylinder (30) is hinged on vehicle frame respectively with the rodless side end cap of block selecting positional cylinder (40).
3. the numerical control transmission control of claim 2, it is characterized in that described gearshift positional cylinder (30) and block 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 arranges respectively gas/liquid mouth, 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 hole is set on piston, n width is set on piston rod and is 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 being mated, piston can be in slippage section and piston rod relative translation.
4. the numerical control transmission control of claim 3, it is characterized in that described gearshift positional cylinder (30) has the first double acting cylinder (121) and second double acting cylinder (122) of two linear array, the two ends that first piston (111), the first double acting cylinder are set in the first double acting cylinder arrange respectively the first gas/liquid mouth (101) and the second gas/liquid mouth (102); The second piston (112) is set in the second double acting cylinder, and the two ends of the second double acting cylinder arrange respectively the 3rd gas/liquid mouth (103) and the 4th gas/liquid mouth (104); On gearshift positional cylinder piston rod, the first slippage section (131) and the second slippage section (132) that width is greater than piston thickness is set, gearshift positional cylinder piston rod is divided into the first block resistance section (141), the second block resistance section (142) and the 3rd block resistance section (143) by the first described slippage section and the second slippage section; The difference of the thickness of the length of the first slippage section (131) and the second piston (112) equals the poor of the length of the second slippage section (132) and the thickness of first piston (111).
5. the numerical control transmission control of claim 3, it is characterized in that described block selecting positional cylinder (40) has the 3rd double acting cylinder (221), the 4th double acting cylinder (222) and the 5th double acting cylinder (223) of three linear array, the 3rd piston (211) is set in the 3rd double acting cylinder, and the two ends of the 3rd double acting cylinder arrange respectively the 5th gas/liquid mouth (201) and the 6th gas/liquid mouth (202); The 4th piston (212) is set in the 4th double acting cylinder (222), and the two ends of the 4th double acting cylinder arrange respectively the 7th gas/liquid mouth (203) and the 8th gas/liquid mouth (204); The 5th piston (213) is set in the 5th double acting cylinder (223), and the two ends of the 5th double acting cylinder arrange respectively the 9th gas/liquid mouth (205) and the tenth gas/liquid mouth (206); The 4th slippage section (232) and the 5th slippage section (233) that the 3rd slippage section (231), width that width equals the 3rd piston (211) thickness are greater than respective pistons thickness are set on block selecting positional cylinder piston rod, and block selecting positional cylinder piston rod is divided into the 4th block resistance section (241), the 5th block resistance section (242), the 6th block 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+four slippage section (232) of the length≤five block resistance section (242) in hole between the cylinder between length+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 sections (233) of length >=five double acting cylinder (223) inner chamber of length-tetra-slippage sections (232) of the 4th double acting cylinder (222) inner chamber.
6. the numerical control transmission control of claim 4, 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 length=the first double acting cylinder (121) of the second block resistance section (142) and the cylinder between the second double acting cylinder (122); The stop bit of positional cylinder piston rod of shifting gears when first to fourth gas/liquid mouth enters gas/liquid respectively if define is respectively H1, H2, H 3 and H 4, and H1=H 4, H1-H2=H3-H4=20mm.
7. the numerical control transmission control of claim 5, is characterized in that the length=50mm of length=five double acting cylinder (223) inner chamber of length=four double acting cylinder (222) inner chamber of the 3rd described double acting cylinder (221) inner chamber; Thickness=the 18mm of thickness=five piston (213) of thickness=four piston (212) of the 3rd piston (211); Length=the 67mm in hole between length=four double acting cylinder (222) in hole and the cylinder between the 5th double acting cylinder (223) between the cylinder between the 3rd double acting cylinder (221) and the 4th double acting cylinder (222); Length=the 92mm of the length=six block resistance section (243) of the 5th block resistance section (242); Length=the 32mm of the length=five slippage section (233) of the 4th slippage section (232); If when defining the 5th to the 9th gas/liquid mouth and entering gas/liquid respectively, the stop bit of block selecting positional cylinder piston rod is respectively L1, L2, L3, L4 and L5: L2-L4=L5-L3=L3-L1=7mm, L2-L5=11mm.
8. the numerical control transmission control of claim 1, is characterized in that described block selecting switch (10-2) and shift switch (10-3) are approach switch.
9. the numerical control transmission control of claim 1, is characterized in that described instruction execution unit (20) comprises 8 groups of solenoid valve (20-1; 20-2; 20-8).
CN201320515466.6U 2013-08-22 2013-08-22 Numerical control speed changer control mechanism Expired - Fee Related CN203404355U (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103453132A (en) * 2013-08-22 2013-12-18 王建军 Control mechanism of numerically-controlled transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103453132A (en) * 2013-08-22 2013-12-18 王建军 Control mechanism of numerically-controlled transmission
CN103453132B (en) * 2013-08-22 2015-08-26 王建军 Control mechanism of numerically-controlltransmission transmission

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