CN1331021A - Hydraulic engageing or preshifting of clutch and hydraulic engagement type speed variator of clutch - Google Patents

Abstract

A speed variator with hydraulic engaging and pre-shafting of clutch for vehicles and its manually hydraulic control system are disclosed. Then one model of said speed variator has 4-5 advancing shifts and ordinary gears for drive and user one of the clutches to control relative shift. The another model of the said speed variator has more than 4-5 advancing shifts and ordinary gears for drive, and uses three of the clutches for direct shifting by pre-shifting. The said manually hydraulic control system for features no need of padel for clutch.

Description

Clutch hydraulic pressure engages or gear changes in advance, clutch hydraulic pressure engagement type change-speed box

The present invention relates to that a kind of clutch hydraulic pressure that is used for self-propelled vehicle engages or gear changes in advance, clutch hydraulic pressure engagement type change-speed box.The invention still further relates to the hand-hydraulic control system that is used for this change-speed box.

The used transmission system of modern automotive has automatic transmission with hydraulic torque converter, manual gear shift transmission and a kind of automatically controlled hand-operated transmission that grows up usually on the manual gear shift transmission basis.In above-mentioned change-speed box, structure more complicated, the part processing difficulty of automatic transmission with hydraulic torque converter are bigger, the multi-disc wet clutch that is adopted is when being in released state, though have certain endplay between the friction lining, but owing to still exist certain work fluid between each friction lining, make the power-transfer clutch of idle running produce certain fluid loss due to friction, this makes the efficient of automatic transmission with hydraulic torque converter not enough very high.In addition, when automatic transmission with hydraulic torque converter adopted planetary gear apparatus, gear of every conversion will be controlled two to three gear shift power elements that are made of power-transfer clutch and drg, control four to five required gear shift power elements of gear and reached eight to ten, increasing more gear again has bigger difficulty.Hand-operated transmission because of simple in structure, efficient is higher is widely used at present.The gear-change operation process of this change-speed box is too loaded down with trivial details, has increased motorist's working strength, is unfavorable for safe driving.Though some vehicle has adopted automatically controlled hand-operated transmission now, the cut time of power was than deficiencies such as length when still there was gear shift in this change-speed box.And,, also increased the probability of et out of order because of having set up extra electronic control system.

The objective of the invention is provides a kind of clutch hydraulic pressure engagement type change-speed box that utilizes ordinary gear to carry out transmission for self-propelled vehicle, the respective clutch of each gear is not only separated when disconnecting fully in the clutch pack of this change-speed box, and each gear makes control become simpler only by a corresponding power-transfer clutch direct control.The present invention is for second kind of gear that self-propelled vehicle provides changes in advance, clutch hydraulic pressure engagement type change-speed box also is to adopt ordinary gear to carry out transmission, this change-speed box utilizes the gear mode of changing in advance just can further realize more gear is carried out direct gear shift control at three power-transfer clutchs that keep only passing through on the higher driving efficiency basis clutch pack.Another object of the present invention is for above-mentioned change-speed box provides corresponding hand-hydraulic control system, thereby makes the gear-change operation process simpler easily.

Be fully to realize above-mentioned purpose, engage or gear changes in advance, in two kinds of dissimilar change-speed boxs of clutch hydraulic pressure engagement type, each type has all been carried out multiple variation combination at the employing clutch hydraulic pressure that the present invention provides.Simultaneously, also provided corresponding hand-hydraulic control system for this change-speed box of two types.

Have in the diaxon clutch hydraulic pressure engagement type change-speed box of four D Drives first kind of the first kind that the present invention provides, it has the imput shaft that links to each other with engine crankshaft, on imput shaft, be fixed with the driving gear of four D Drives and a reverse gear, be set with second, third and the 4th driven axle sleeve on the driven shaft that is arranged in parallel with imput shaft versatilely, these driven shafts put and are fixed with the driven gear that is meshed with two, three and four retaining driving gears on the imput shaft respectively.The driven gear movable set that is meshed with one grade and reverse driving gear on the imput shaft is on driven shaft, and driven shaft links to each other with one grade or the engagement of reverse gear driven gear by the synchromesh cover on it.Set driven shaft and each the driven axle sleeve outer end on it put in the clutch pack that has four power-transfer clutchs on the output shaft, clutch pack is fixed on the output shaft by the master of clutch-bell cover, four power-transfer clutchs of clutch pack be located in the clutch-bell cover by master, middle two that spacer ring and outer shroud constituted every in the air, make the spacer ring both sides respectively have two power-transfer clutchs.Be provided with the binary pressure ring between master and spacer ring, first and second friction linings are arranged in its both sides, are provided with another binary pressure ring between spacer ring and outer shroud, arrange third and fourth friction lining for its two.Putting in the driven shaft of clutch pack links to each other with first friction lining in the clutch pack, and the end of driven shaft also with the coaxial movable set of the master of clutch pack, second, third with the 4th driven axle sleeve then respectively with clutch pack in second, third link to each other with the 4th friction lining.The binary pressure ring is that the side ring body by both sides constitutes with the intermediate sleeve that links to each other, between the ring body of the both sides of binary pressure ring, be provided with the inner split ring that is fixed on the clutch-bell cover inwall, pass through the sealing member slipper seal between the side ring body of binary pressure ring and the clutch-bell cover inwall, also by the sealing member slipper seal, make inner split ring both sides formation hydraulic cavities separately between intermediate sleeve and the inner split ring.Hydraulic cavities separately on the two binary pressure rings is led to the oil circuit joint that is enclosed within on the output shaft by corresponding oil circuit respectively.

Have in the diaxon clutch hydraulic pressure engagement type change-speed box of five D Drives second kind of the first kind that the present invention provides, it has the power-transfer clutch that links to each other with engine crankshaft through self connection minor axis, this clutch pack comprises five power-transfer clutchs, utilizes bearing installation by a side master of clutch-bell cover by the connection minor axis that links to each other.In five power-transfer clutchs of clutch pack, four power-transfer clutchs be located in the clutch-bell cover by master, middle two that spacer ring and outer shroud constituted every in the air, make the spacer ring both sides respectively have two power-transfer clutchs.Be provided with the binary pressure ring between master and spacer ring, its both sides are provided with first and second friction linings, and another binary pressure ring is set between spacer ring and outer shroud, and its both sides are provided with third and fourth friction lining.The outer shroud outside at clutch-bell cover is provided with unsteady pressure ring, it between outer shroud and the unsteady pressure ring the 5th friction lining of the 5th power-transfer clutch, the pressure ring that floats links to each other by the piston on the outer side cylinder of attaching parts and master, oil cylinder is made of with the outer ring cowling that links to each other the inner sleeve on the master, the outer sleeve of its upper piston surrounds oil cylinder, the piston ring flat-plate that picks out from outer sleeve puts in oil cylinder, pass through the sealing member slipper seal between the outer sleeve of piston and the master of oil cylinder and the outer ring cowling, also by the sealing member slipper seal, make piston ring flat-plate both sides form hydraulic cavities and counter balance pocket between the inner sleeve of piston ring flat-plate and oil cylinder.Every side on the two binary pressure rings hydraulic cavities of hydraulic cavities and piston ring flat-plate both sides and counter balance pocket is separately led to through corresponding oil circuit respectively and is enclosed within the oil circuit joint that is connected on the minor axis.On set first imput shaft that matches with clutch pack and its second, third, the 4th and the 5th driving axle housing put in the clutch pack, the inner of first imput shaft links to each other with first friction lining of inboard power-transfer clutch, and its inner and the coaxial movable set of master, the inner of second to the 5th driving axle housing then links to each other with second to the 5th friction lining of power-transfer clutch respectively.In first imput shaft outside, be fixed with one grade and reverse driving gear, be fixed with the driving gear of two to five grades of corresponding gears respectively in the outer end of second to the 5th driving axle housing.On the output shaft that is arranged in parallel with first imput shaft, be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, wherein, one grade, second gear link to each other with output shaft by the roller of unidirectional fee engine clutch respectively with the third gear driven gear, and, first speed driven gear is also to be sleeved on the output shaft through connecting bushing behind the roller of unidirectional fee engine clutch, and output shaft links to each other with the reverse gear driven gear engagement of connecting bushing or movable set by the synchromesh cover on it again.Corresponding side at one grade, second gear and third gear driven gear, be respectively equipped with clutch engagement face with anti-skidding ripple, match with it, on output shaft, be respectively equipped with corresponding hydraulic ram, on the piston of oil cylinder, also be provided with face of joint with anti-skidding ripple, the corresponding hydraulic ram of on the output shaft each leads to the oil circuit joint that is enclosed within on the output shaft through separately oil circuit respectively, and corresponding with this grade of control clutch group again oil circuit is communicated with.Fourth gear and five grades of driven gears are fixed on the output shaft.

Have in the coaxial clutch hydraulic pressure engagement type change-speed box of five D Drives at the third of the first kind that the present invention provides, the structure of the clutch pack that is adopted is identical with change-speed box in above-mentioned second kind of scheme, for no other reason than that adopted coaxial layout type, the friction lining of five power-transfer clutchs in the clutch pack by the inboard laterally ordering to be changed at first be the 4th direct speed friction lining, be first friction lining, second friction lining, the 3rd friction lining and the 5th friction lining then successively.The set direct speed imput shaft that matches with clutch pack and on the first, second, third and the 4th driving axle housing put in the clutch pack, the inner of direct speed imput shaft links to each other with the 4th direct speed friction lining of clutch pack inboard, and its inner also with the coaxial movable set of master, first, second, third then links to each other with the 5th friction lining with first, second, third of clutch pack respectively with the inner of the 4th driving axle housing.The outer end of direct speed imput shaft directly links to each other with output shaft, in the outside of first driving axle housing, is fixed with one grade and reverse driving gear, is fixed with two, three and five grades driving gear respectively in the outer end of second, third and the 4th driving axle housing.On the transmission shaft that is arranged in parallel with the direct speed imput shaft, be respectively equipped with and above-mentioned one, two, three and five grade of driven gear that driving gear is meshed, transmission shaft drives output shaft by a pair of transmission gear.On transmission shaft in the set corresponding driven gear, as for one, two with the third gear driven gear frame mode that links to each other with transmission shaft of the roller by unidirectional fee engine clutch respectively, be with above-mentioned second kind of scheme change-speed box in one, two and the layout of third gear driven gear on output shaft be identical.The 5th grade of driven gear is fixed on the transmission shaft.

Any one clutch hydraulic pressure engagement type change-speed box for the above-mentioned first kind, the present invention has provided corresponding hand-hydraulic control system, in this control system, the fuel-displaced pipeline that picks out from oil pump had both led to the oil discharge outlet of unloader valve, led to oil feed line through check valve again.Oil feed line not only is communicated with the oil inlet of selector valve, also be provided with three on it to the oil circuit that picks out, wherein, article one, be communicated with the logical hydraulic fluid port of pressure of unloader valve, another joint locking shutoff valve through being in normally open engages flow regulating valve with the starting that is in series and is communicated with oil return line, and the 3rd the separation shutoff valve through being in normally off also leads to oil return line.In above-mentioned each valve, selector valve links to each other with gear-shift lever, separating shutoff valve links to each other with brake pedal, starting engages flow regulating valve and links to each other with Das Gaspedal through spring, engaging the locking shutoff valve can be by locking control action of the joint of gear-shift lever or set locking controls control, and the control mechanism that can be closed by manipulation, be established in addition when surpassing second gear during one grade on this valve is closed, Be Controlled is opened during neutral gear.Selector valve comprises valve body and spool wherein, on the inwall of valve body, be provided with layout reverse gear hydraulic fluid port far away, neutral gear hydraulic fluid port and corresponding hydraulic fluid port successively from one grade of hydraulic fluid port to four to five grades, wherein, the reverse gear hydraulic fluid port is communicated with through the oil circuit of check valve with one grade of hydraulic fluid port, the neutral gear hydraulic fluid port is communicated with oil return line, one grade to four to five grades corresponding hydraulic fluid port on the valve body leads to oil circuit joint on the change-speed box through separately oil circuit respectively, is communicated with the fluid chamber of corresponding power-transfer clutch respectively by the corresponding hydraulic fluid port on the oil circuit joint again.Spool in the valve body comprises base portion, zerk and one grade of sprue, and zerk is communicated with oil inlet on the valve body, when spool is handled by gear-shift lever, the zerk on it can be respectively with valve interior wall on each grade hydraulic fluid port connect successively.When zerk and the connection of reverse gear hydraulic fluid port, one grade of sprue is just sheltering from one grade of hydraulic fluid port, and this moment, gear-shift lever also is out of gear one grade in advance by the synchromesh cover of reverse gear control mechanism, and engages with reverse gearwheel subsequently.When zerk and other gear hydraulic fluid port are connected, one grade of sprue be parked in other gear hydraulic fluid port every empty or do not hide the position of stifled each grade hydraulic fluid port.

Above the present invention has provided the clutch hydraulic pressure engagement type change-speed box and the hand-hydraulic control system thereof of the first kind.In the change-speed box of this type, each gear is all controlled by corresponding power-transfer clutch, and in order to use the more gear of clutch control of lesser amt, the gear that the present invention has provided second type changes in advance, clutch hydraulic pressure engagement type change-speed box.

First kind of diaxon gear in second type that the present invention provides changes in advance, in the clutch hydraulic pressure engagement type change-speed box, it has the clutch pack that links to each other with engine crankshaft through self connection minor axis, this clutch pack comprises three power-transfer clutchs, utilizes bearing installation by a side master of clutch-bell cover by the connection minor axis that links to each other.Be provided with the binary pressure ring between master in clutch-bell cover and the spacer ring, its both sides are provided with first and second friction linings of two power-transfer clutchs, are provided with another binary pressure ring in the spacer ring outside, and the 3rd friction lining of three-clutch is set between the two.The binary pressure ring is that the side ring body by both sides constitutes with the intermediate sleeve that links to each other, between the ring body of the both sides of binary pressure ring, be provided with the inner split ring that is fixed on the clutch-bell cover inwall, pass through the sealing member slipper seal between the side ring body of binary pressure ring and the clutch-bell cover inwall, pass through another sealing member slipper seal between intermediate sleeve and the inner split ring, make the inner split ring both sides form hydraulic cavities, hydraulic cavities separately on the two binary pressure rings and counter balance pocket are led to the oil circuit joint that is enclosed within on the connection minor axis by corresponding oil circuit respectively.Set first imput shaft that matches with clutch pack and on the second and the 3rd driving axle housing put in the clutch pack, first imput shaft links to each other with first friction lining of clutch pack inboard, and its inner also with the coaxial movable set of master, second links to each other with the 3rd friction lining with second respectively with the inner of the 3rd driving axle housing.Be provided with fixing one grade in the outside of first imput shaft, the driving gear of reverse driving gear and other gear, the outside at the second and the 3rd driving axle housing, be respectively equipped with fixing second gear, the driving gear of third speed drive gear and other gear, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first imput shaft, second driving axle housing and the 3rd driving axle housing cocycle are provided with, and make two gears of being separated by between the driving gear of the variant gear on each imput shaft or the driving axle housing.On the output shaft that is arranged in parallel with first imput shaft, be respectively equipped with the driven gear that is meshed with each grade driving gear on above-mentioned imput shaft and the driving axle housing, these driven gears are sleeved on the output shaft versatilely, output shaft is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set, bi-directional synchronization shift sleeve control between the driven gear of two gears is arranged at interval, independent driven gear is by the control of unidirectional synchromesh cover.

Second kind of change-speed box of second type that the present invention provides improves on above-mentioned first kind of change-speed box basis, and this change-speed box has saved the connection minor axis of clutch pack, and the oil circuit joint is located on the oil-guiding shaft of establishing in addition that picks out from clutch pack.This change-speed box improves by following mode, clutch pack is directly captiveed joint with bent axle through master, on master, establish the oil-guiding shaft that passes hollow first imput shaft that picks out in addition, the hydraulic cavities separately of the binary pressure ring in the clutch pack and the continuous oil circuit of counter balance pocket lead to the outer end of oil-guiding shaft respectively through oil-guiding shaft, be connected with cover oil circuit joint thereon again.One grade, reverse driving gear are arranged on the other low-grade axle of avoiding the oil circuit joint, this beam warp transmission gear is established gear driven on first imput shaft in addition, the first speed driven gear of one grade of driving gear on a breast wheel drive output shaft, the reverse gear driving wheel directly drives the reverse gear driven gear.

The third gear of second type that the present invention provides changes in advance, clutch hydraulic pressure engagement type change-speed box also is the dual-shaft variable device, in this change-speed box, it has the clutch pack that links to each other with engine crankshaft through self connection minor axis, this clutch pack comprises three power-transfer clutchs, utilizes bearing installation by a side master of clutch-bell cover by the connection minor axis that links to each other.Be provided with the binary pressure ring between the master of clutch-bell cover and outer shroud, its both sides are provided with first friction lining and second friction lining of two power-transfer clutchs.Be provided with unsteady pressure ring in the outer shroud of the clutch-bell cover outside, the 3rd friction lining of three-clutch is set between outer shroud and the unsteady pressure ring, the pressure ring that floats links to each other by the piston on the oil cylinder outside attaching parts and the master.Oil cylinder is made of with the outer ring cowling that links to each other the inner sleeve on the master, piston jacket tube on it surrounds oil cylinder, the piston ring flat-plate that picks out from outer sleeve puts in oil cylinder, pass through the sealing member slipper seal between the outer sleeve of piston and the master of oil cylinder and the outer ring cowling, also by the sealing member slipper seal, make piston ring flat-plate both sides form hydraulic cavities and counter balance pocket between the inner sleeve of piston ring flat-plate and oil cylinder.Hydraulic cavities separately on the binary pressure ring and the hydraulic cavities of piston both sides and counter balance pocket are led to through corresponding oil circuit respectively and are enclosed within the oil circuit joint that is connected on the minor axis.As for the first set imput shaft and on the second and the 3rd driving axle housing put in remainders such as clutch pack, with above-mentioned this type of first kind of change-speed box be essentially identical.

The 4th kind of coaxial gear in second type that the present invention provides changes in advance, in the clutch hydraulic pressure engagement type change-speed box, for clutch pack and on imput shaft and second, third driving axle housing on it arrangement etc. of set each grade driving gear, adopted and above-mentioned this type of first kind of structure that change-speed box is identical.After this change-speed box coaxial arrangement, the outer end of first imput shaft and the coaxial movable set of set output shaft, with transmission shaft that first imput shaft is arranged in parallel on be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, transmission shaft drives output shaft through a pair of transmission gear.Be located at each grade driven gear movable set on the transmission shaft on transmission shaft, transmission shaft is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism control of gear accordingly by set.First imput shaft is also by being linked to each other with output shaft by the synchromesh cover of the pre-converting mechanism control of gear on it.Usually, last gear on first imput shaft is a direct speed, does not establish the driving gear of this gear on first imput shaft.

Change in advance at the 5th kind of coaxial gear of second type of the present invention, in the clutch hydraulic pressure engagement type change-speed box, the structure of its clutch pack and above-mentioned this type of the third change-speed box are basic identical, all adopted the structural arrangement mode that helps reducing the power-transfer clutch axial length, by the synchromesh cover effect of the pre-converting mechanism control of gear etc., is identical with above-mentioned this type of the 4th kind of coaxial speed variator as for the layout of the transmission shaft of this change-speed box and output shaft, driven gear on it all.

Change in advance at the 6th kind of coaxial gear of second type that the present invention provides, in the clutch hydraulic pressure engagement type change-speed box, it has the clutch pack that links to each other with engine crankshaft through self connection minor axis, and this clutch pack is utilized bearing installation by a side master of clutch-bell cover by the connection minor axis that links to each other.Clutch pack comprises four power-transfer clutchs, two power-transfer clutchs of every side be in respectively in the clutch-bell cover by master, middle two that spacer ring and outer shroud constituted every in the air, make two power-transfer clutchs of each tool of spacer ring both sides.Be provided with the binary pressure ring between master and the spacer ring, the direct speed friction lining and first friction lining are set in its both sides, be provided with another binary pressure ring between spacer ring and outer shroud, its both sides are the second and the 3rd friction linings.Hydraulic cavities separately on the two binary pressure rings is led to the oil circuit joint that is enclosed within on the output shaft by corresponding oil circuit respectively.Set direct speed imput shaft that matches with clutch pack and first, second and third driving axle housing on it put in the clutch pack, the inner of direct speed imput shaft links to each other with the direct speed friction lining of inboard, its inner also with the coaxial movable set of master, the inner of first, second and the 3rd driving axle housing then links to each other respectively with the 3rd friction lining with first, second.Outer end in the direct speed imput shaft is provided with output shaft, diaxon directly is fixedly connected together, be provided with fixing one grade in the outside of first driving axle housing, the driving gear of reverse driving gear and other gears, be respectively equipped with the driving gear of fixing second gear and third speed drive gear and other gear in the outside of the second and the 3rd driving axle housing, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first driving axle housing, second driving axle housing and the circulation of the 3rd driving axle housing are provided with, make two gears of being separated by between the driving gear of the variant gear on each driving axle housing, on the transmission shaft that is arranged in parallel with the direct speed imput shaft, be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, transmission shaft drives output shaft through a pair of transmission gear.Be located at each grade driven gear movable set on the transmission shaft on transmission shaft, transmission shaft is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism control of gear accordingly by set.On corresponding driving axle housing, do not establish the driving gear of direct speed imput shaft institute respective notch.

Any one gear for above-mentioned second type changes in advance, clutch hydraulic pressure engagement type change-speed box, and the present invention has provided and set up the hand-hydraulic control system that gear changes control mechanism etc. in advance.In this hydraulic control system, the fuel-displaced pipeline that picks out from oil pump is divided into two strands, a stock-traders' know-how check valve, is provided with the oil circuit that holds oil cylinder, the oil-break shutoff valve that is in normally open and auxiliary oil circuit and communicates with the oil inlet that the gear of the pre-converting mechanism of gear changes valve in advance; The oil cut-off valve that holds that another stock-traders' know-how is held oil cylinder control leads to the fuel feeding Qi Lu with many shunt with total check valve, hold in the oil cylinder by spring-actuated piston and control it when holding oil pressure and hold oil cut-off valve and open reaching, hold oil cut-off valve and the total oil circuit between the check valve and also be communicated with the oil discharge outlet of unloader valve.In set fuel feeding qi road, article one, through check valve with have the oil circuit that holds oil cylinder and be communicated with, second is closed shutoff valve through neutral gear and is communicated with auxiliary oil circuit, article three, through being in the drain the oil shutoff valve and the oil return line connection of normally off, article four, also be communicated with the 5th oil inlet that leads to delayed-opening valve with oil return pipe through by pass valve.Delayed-opening valve comprises the spool in valve body and its valve opening, the exocoel of valve opening is communicated with oil inlet, the valve opening inwall is provided with oil outlet, spool shelters from oil outlet when being in off position by action of the spring, the valve opening inner chamber at spool back is communicated with oil return line through cutoff port, and oil return line leads to back the valve opening inner chamber through check valve again.The oil outlet of delayed-opening valve leads to the oil inlet of selector valve through oil feed line, on oil feed line, have and be provided with three oil circuits that pick out, article one, oil circuit is communicated with the logical hydraulic fluid port of pressure of unloader valve, the joint locking shutoff valve of another oil circuit through being in normally open engages flow regulating valve with the starting that is in series and is communicated with oil return line, and the 3rd the separation shutoff valve through being in normally off also is communicated with oil return line.In above-mentioned each valve, oil-break shutoff valve, the shutoff valve of draining the oil link to each other by being connected control piece with the separation shutoff valve, and can be braked pedal and more shelves increase the oil resistance cylinder and control respectively, starting engages flow regulating valve and links to each other with Das Gaspedal through spring, joint locking shutoff valve and neutral gear are closed shutoff valve and are controlled jointly by attaching parts, engaging the locking shutoff valve can be by locking control action of the joint of gear-shift lever or set locking controls control, can be closed by manipulation during one grade on this valve, the control mechanism of being established in addition when surpassing second gear is closed, Be Controlled is opened during neutral gear.Gear changes valve in advance and links to each other with selector valve, and is controlled jointly by gear level and centrifugal ascending, descending shift controlling mechanism.Selector valve comprises valve body and spool, on valve interior wall, be provided with the reverse gear hydraulic fluid port of being in that links to each other with the reverse gear oil circuit successively than distant positions, the neutral gear hydraulic fluid port that links to each other with oil return line, the one grade of hydraulic fluid port that links to each other with first oil circuit, the second gear hydraulic fluid port that links to each other with second oil circuit, the third gear hydraulic fluid port that links to each other with the 3rd oil circuit and by the corresponding hydraulic fluid port of tactic other gear that upgrades, from the fourth speed hydraulic fluid port, the continuous oil circuit of other set gear hydraulic fluid port is an oil circuit group by per three gears of order that upgrade also, the oil circuit group of three gears of less than comes at last, the corresponding oil circuit of each oil circuit group is repeated and first through check valve respectively in order, the second and the 3rd oil circuit is connected, and allows first, two gears are spaced between the gear that is had on every oil circuit of the second and the 3rd oil circuit.The reverse gear oil circuit of reverse gear hydraulic fluid port also is communicated with first oil circuit through check valve.First, second and the 3rd oil circuit lead to the oil circuit joint of change-speed box respectively, lead to the respective clutch hydraulic cavities of clutch pack again by the corresponding hydraulic fluid port on the oil circuit joint.The spool of selector valve comprises base portion, one grade of sprue, zerk and according to required at least one of establishing of oil circuit group number sprue at interval, zerk and at interval between the sprue and the two hydraulic fluid port distances that are spaced two gears at interval between the sprues, zerk communicates with oil inlet on the valve body.When spool is handled by gear-shift lever, the zerk on it can be successively with valve interior wall on each grade hydraulic fluid port link up respectively, when zerk and reverse gear hydraulic fluid port were linked up, one grade of sprue sheltered from one grade of oil day; Zerk move past one, two and the third gear hydraulic fluid port after, when connecting respectively with the gear hydraulic fluid port more than the fourth gear, set one and the interval sprue set up can shelter from corresponding one, two or the third gear hydraulic fluid port all the time respectively.Gear changes the spool that valve comprises valve body and Qi Nei in advance, be provided with layout reverse gear hydraulic fluid port far away on the valve interior wall and more than one grade by upgrading tactic and corresponding each grade hydraulic fluid port of selector valve hydraulic fluid port, the hydraulic fluid port of each gear leads to the corresponding control oil cylinder of the pre-converting mechanism of gear on the change-speed box respectively by oil circuit separately, further drive the corresponding synchronous shift sleeve by in-oil cylinder piston and shift fork; The spool that gear changes valve in advance comprises base portion and three mouthfuls of zerks, and three mouthfuls of zerks are communicated with oil inlet on the valve body, and the width of its zerk can be simultaneously linked up with the hydraulic fluid port of adjacent three gears that advance, but can not link up reverse gear hydraulic fluid port and one grade of hydraulic fluid port simultaneously.The spool that the spool of selector valve and gear the change valve in advance same moved further that directly links to each other, and the zerk of spool aligns mutually with the midway location of three mouthfuls of zerks.

When gear of the present invention is changed in advance, clutch hydraulic pressure engagement type change-speed box is used for diesel locomotive and during through vehicle that the express highway of being everlasting travels, because vehicle can often be in the stable motoring condition with the long period, for the transmission gear that makes other gear of N/R stops idle running, the present invention changes valve in advance to the gear in the hand-hydraulic control system and has carried out corresponding improvement in the following manner.Change in the valve in advance at this improved gear, the broad hydraulic fluid port that gear is changed in advance three mouthfuls of zerks of valve has three independent hydraulic fluid ports instead, middle hydraulic fluid port in these three hydraulic fluid ports directly oil inlet on valve body is communicated with auxiliary oil circuit, after the side hydraulic fluid port on both sides is communicated with together, oil circuit and the change-over valve established through other are communicated with auxiliary oil circuit again, when the needs fuel-economizing moved, change-over valve cut off the fuel feeding to the both sides hydraulic fluid port, and it is communicated with oil return line.

In the above-described two types corresponding hand-hydraulic control system that change-speed box adopted, have certain automatic operating function for making this control system, adopted this mode that allows selector valve also be controlled by centrifugal lifting shift controlling mechanism.In this mode, the control stalk of lifting shift controlling mechanism links to each other with the spool of selector valve by transmission connection piece, the connection head of the control stalk other end is between the ascending, descending shelves spring that actuating spindle puts, this control axle sleeve is installed on the speed shaft that links to each other with the output shaft of change-speed box, and through Transmission by centrifugal control on the speed shaft.During the speed shaft stall, the control axle sleeve is back into reference position by set spring, and the spool of corresponding selector valve also is in Neutral Position.On control stalk, be provided with and the corresponding setback castellated plates of each P PARK Position P, pressed on the setback castellated plates by the prevention wheel load of two actions of the spring, wherein, back at a bigger spring of elastic force, set is linked to each other with brake pedal by Transmission by the spring perch of bottom action of the spring, and it can be pulled away from the bigger spring of this elastic force.

Owing to can handle the gear-shift lever of hand-hydraulic control system easily, for preventing that gear-shift lever is by the operation of shelves more of mistake, gear-shift lever is also got over shelves and is increased the effect of oil resistance cylinder, stopper on this in-oil cylinder servo-actuated damping piston links to each other with gear-shift lever through attaching parts, stopper is in the middle of the servo-actuated damping piston, kept meta by the meta spring of both sides, the clearance space of stopper both sides can allow it move freely a gear to high or low shelves.A both sides oil pocket that increases the oil resistance cylinder at shelves more is respectively equipped with two oil circuits that pick out, the oil circuit that is provided with damping hole and normally closed cut-off valve by parallel connection between two oil circuits links to each other, this normally closed cut-off valve is braked pedal control, then, two oil circuits link to each other with the both sides oil pocket of control oil cylinder respectively again, in the control oil cylinder, be provided with by the control plunger of meta action of the spring, the piston rod of this piston by both sides can act on the two opposed rocking arms in the outside, can be linked to each other with the shutoff valve that separates of hand-hydraulic control system by the Transmission that two rocking arms drive respectively.

In two kinds of hand-hydraulic control system of the invention described above, adopted a kind of comparatively simple and reliable unloader valve, in the valve body of this unloader valve, be provided with control cylinder and valve opening, both link to each other by two oil circuits of band check valve, the outside of control cylinder is communicated with oil feed line through the logical hydraulic fluid port of pressure, on the inwall of control cylinder, be provided with logical oil ring groove and oil-feed annular groove, the inside of control cylinder is communicated with oil return line, in control cylinder, be equipped with by the valve plug of action of the spring, when this valve plug is pushed up the logical hydraulic fluid port side of pressure by spring, valve plug outwards moves past logical oil ring groove, allow logical oil ring groove communicate with oil return line, when plug valve is inwardly moved past logical oil ring groove and allows the oil-feed annular groove expose by the pressure oil effect, can allow two annular grooves all communicate with the logical hydraulic fluid port of pressure.Control cylinder is communicated with the valve pocket of valve opening inboard by the oil circuit of oil-feed annular groove through being provided with cutoff port and check valve on it, this valve pocket is communicated with the logical oil ring groove of control cylinder through the oil circuit of band plunger, unidirectional integrated valve and throttling check valve again simultaneously, the diameter of plunger of plunger, unidirectional integrated valve is smaller, and outer face is to oil return line.In valve opening, be equipped with by the spool of draining the oil of action of the spring, spool is provided with oil return slots or the oil discharge outlet that is communicated with oil return line, after hydraulic oil ejects the valve pocket of valve opening to spool, oil extraction annular groove on oil return slots on it or oil discharge outlet and the valve opening inwall is linked up, and makes the fuel-displaced pipeline connection of oil extraction annular groove through oil discharge outlet and oil pump.

In above-described first kind clutch hydraulic pressure engagement type change-speed box, though each gear is all by a respective clutch direct control of clutch pack, but because clutch pack has adopted binary pressure ring and globality structure, when this change-speed box has four to five D Drives, clutch pack and transmission gear still can constitute the arrangement form of compact conformation, volume than common manual change-speed box increases seldom, compares structurally also relative simple with present automatic transmission with hydraulic torque converter.

Gear in described second type changes in advance, in the clutch hydraulic pressure engagement type speed change, owing to adopted the pre-converting mechanism of gear, no matter how much gear quantity is increased to, and all can utilize the clutch pack with three power-transfer clutchs that the corresponding gear that is engaged is in advance carried out direct gear shift.Because the pre-converting mechanism of gear always following the selected corresponding gear of gear-shift lever, allow this gear and adjacent high and low shelves gear cluster thereof be in engagement state all the time, like this, can by gear-shift lever at any time the respective clutch of control clutch group change to high or low shelves.Because adjacent high and low shelves transmission gear is engaged in advance, just can carry out gear shift by control clutch during gear-change operation, the cut time of gearshift procedure medium power is very short.

In above-mentioned two kinds of dissimilar change-speed boxs, because the one chip friction disk clutch that most employing can be separated fully, this makes the friction lining of power-transfer clutch make loss due to friction very little because of thoroughly separating, and the driving efficiency of change-speed box is improved.

For the required hand-hydraulic control system of above-mentioned change-speed box, its manipulation process is very simple, by the push-and-pull gear-shift lever, and just can be to high or low shelves conversion.One grade of driveaway operation of this change-speed box also meets motorist's operating habit very much, because Das Gaspedal is also being controlled the starting of hydraulic control system simultaneously and is being engaged flow regulating valve, changing to one grade when starting to walk, as long as the control Das Gaspedal, can finish refuel and make one grade of power-transfer clutch gradually engage this operation.In addition, set up simple and effective centrifugal ascending, descending shift controlling mechanism for the hand-hydraulic control system after, also can allow this change-speed box have certain automatic ascending, descending shelves controllable function, so that more favourable light steering vehicle.

Below in conjunction with accompanying drawing and each specific embodiment to further detailed explanation of the present invention.

Fig. 1. the cutaway view of first kind of diaxon clutch hydraulic pressure of the first kind of the present invention engagement type change-speed box.

Fig. 2. the binary pressure ring amplification view of power-transfer clutch among Fig. 1.

Fig. 3. the structure principle chart of the hand-hydraulic control system that matches with first kind change-speed box.The zerk of selector valve is parked in neutral position among the figure.

Fig. 4. the unloader valve structure cutaway view of hand-hydraulic control system among Fig. 3.

Fig. 5. the cutaway view of second kind of diaxon clutch hydraulic pressure of the first kind of the present invention engagement type change-speed box.

Fig. 6. among Fig. 5, the oil cylinder of the 5th grade of power-transfer clutch and piston amplification view.

Fig. 7. grade different driven gears of each among Fig. 5 on the output shaft are by unidirectional fee engine clutch etc. or the amplification view that directly is connected with output shaft.

Fig. 8. the cutaway view of the third coaxial clutch hydraulic pressure engagement type change-speed box of the first kind of the present invention.

Fig. 9. first kind of diaxon gear of second type of the present invention changes in advance, the cutaway view of clutch hydraulic pressure engagement type change-speed box.

Figure 10. second kind of diaxon gear of second type of the present invention changes in advance, the cutaway view of clutch hydraulic pressure engagement type change-speed box.

Figure 11. the third diaxon gear of second type of the present invention changes in advance, the cutaway view of clutch hydraulic pressure engagement type change-speed box.

Figure 12. the 4th kind of coaxial gear of second type of the present invention changes in advance, the cutaway view of clutch hydraulic pressure engagement type change-speed box.

Figure 13. the 5th kind of coaxial gear of second type of the present invention changes in advance, the cutaway view of clutch hydraulic pressure engagement type change-speed box.

Figure 14. the 6th kind of coaxial gear of second type of the present invention changes in advance, the cutaway view of clutch hydraulic pressure engagement type change-speed box.

Figure 15. the hand-hydraulic control system structure principle chart that change in advance with the gear of second type, clutch hydraulic pressure engagement type change-speed box matches.Selector valve and gear change valve in advance and are in the second gear position among the figure.

Figure 16. have the selector valve structural representation of ten gears that advance.

Figure 17. the gear with three independent oil-feed ports changes the valve arrangement scheme drawing in advance.

First kind of diaxon clutch hydraulic pressure of the first kind of the present invention engagement type change-speed box is shown in Fig. 1 and 2 embodiment, this change-speed box has four D Drives and a reverse gear, it has the imput shaft 70 that links to each other with engine shaft 1, is fixed with the driving gear 81,82,83,84 and 97 of four D Drives and a reverse gear on imput shaft.Be set with second, third and the 4th driven axle sleeve 92,93 and 94 on the driven shaft 96 that is arranged in parallel with imput shaft 70 versatilely, these driven shafts put and are fixed with the driven gear 102,103 and 104 that is meshed with two, three and fourth gear driving gear on the imput shaft 70 respectively.Be meshed with one grade and reverse driving gear on the imput shaft one grade, reverse gear driven gear 101,110 are sleeved on the driven shaft 96 versatilely, and driven shaft links to each other with one grade or reverse gear driven gear by the cover of the synchromesh on it 99.Set driven shaft and each the driven axle sleeve outer end on it put in the clutch pack 5 that has four power-transfer clutchs on the output shaft 76, this clutch pack is fixed on the output shaft 76 by the master 14 of clutch-bell cover 12, four power-transfer clutchs of clutch pack are located in the clutch-bell cover be made of master 14, middle spacer ring 19 and outer shroud 20 two every in the air, make 19 two of spacer rings respectively have two power-transfer clutchs.Be provided with binary pressure ring 46 between master 14 and spacer ring 19, first and second friction linings 61,62 are arranged in its both sides, are provided with binary pressure ring 47 between spacer ring 19 and outer shroud 20, and third and fourth friction lining 63,64 is arranged in its both sides.Put in the driven shaft 96 of clutch pack and link to each other with first friction lining 61 in the clutch pack, and, the end of driven shaft also with the master 14 coaxial movable sets of clutch pack.Since first friction lining 61 transmits be after slowing down than high pulling torque, be provided with being installed on the inner walls of clutch pack by keyway etc. between two one grade friction lining 61, two friction linings on the driven shaft 96 every dish 25.Second, third with the 4th driven axle sleeve 92,93 with 94 respectively with clutch pack in second, third link to each other with 64 with the 4th friction lining 62,63.Binary pressure ring the 46, the 47th is made of with the intermediate sleeve 49 that links to each other the side ring body 48 of both sides, referring to Fig. 2, between the both sides of binary pressure ring ring body 48, be provided with the inner split ring 21 that is fixed on the clutch-bell cover inwall 13, pass through sealing member 55 slipper seals between the side ring body 48 of binary pressure ring and the clutch-bell cover inwall 13, by sealing member 56 slipper seals, make inner split ring both sides formation hydraulic cavities 53 separately between intermediate sleeve 49 and the inner split ring 21.When clutch-bell cover 12 adopted unitized constructions with master 14, hydraulic cavities 53 was through oil pipe 26 communicate with oil circuit 15 on the master (referring to Fig. 2).Hydraulic cavities separately 53 on the two binary pressure rings 46,47 is led to the oil circuit joint 44 that is enclosed within on the output shaft 76 by corresponding oil circuit respectively, so that clutch pack can be controlled by the hand-hydraulic control system.

Because of the power-transfer clutch in the clutch pack 5 often all is in from state, only when needed, just make the power-transfer clutch Be Controlled joint of corresponding gear.For allowing not controlled power-transfer clutch get back to released state voluntarily, each side ring body 48 of binary pressure ring all is by 52 effects of meta spring, as shown in Figure 2 through several spacing top covers 50.Simultaneously, the binary pressure ring also utilizes the locating dowel pin 51 on the side ring body to transmit the moment of torsion that friction lining transmits by spacing top cover 50.Match therewith, each friction lining of installing by spline is also by pull back spring effect (drawing among the figure), makes it does not made time spent return voluntarily by the binary pressure ring.Since one, the moment of torsion that transmitted of second gear power-transfer clutch than three, the fourth gear power-transfer clutch is big, not only one grade of power-transfer clutch has adopted two friction linings, and the oil pressure active area of corresponding binary pressure ring 46 also than three, the binary pressure ring 47 of fourth gear power-transfer clutch is big.The power of driving engine is passed to imput shaft 70 through antitorque damper spring 3 among the figure, when the power of driving engine when the turbine transformer of setting up is passed to imput shaft, will make this change-speed box have bigger power comformability.

What Fig. 3 provided is the hand-hydraulic control system that is used for the clutch hydraulic pressure engagement type change-speed box of the first kind.As seen from the figure, the fuel-displaced pipeline 265 that picks out from the oil pump 158 of this system promptly leads to the oil discharge outlet 372 of unloader valve 358, leads to oil feed line 271 through check valve 269 again.The oil feed line 271 that comes through check valve 269 not only is communicated with the oil inlet 164 of selector valve 161, also be provided with three on it to the oil circuit that picks out, wherein, oil circuit 277 is communicated with the logical hydraulic fluid port 362 of pressure of unloader valve 358, the joint locking shutoff valve 273 of oil circuit 272 through being in normally open engages flow regulating valve 274 with the starting that is in series and is communicated with oil return line 286, and the separation shutoff valve 276 of oil circuit 275 through being in normally off also leads to oil return line 286; In above-mentioned each valve, selector valve 161 links to each other with gear-shift lever 288, separating shutoff valve 276 links to each other with brake pedal 302, starting engages flow regulating valve 274 and links to each other with Das Gaspedal 298 through spring 299, and engaging locking shutoff valve 273 can be by locking control action of the joint of gear-shift lever 288 or set locking controls 289 control.When joint locking shutoff valve 273 was designed to by the joint of gear-shift lever 288 locking control action control, gear-shift lever can be arranged in by the side of bearing circle, and the push-and-pull gear-shift lever is a gear-change operation, presses down gear-shift lever then for controlling the control action that engages the locking shutoff valve.When engaging locking shutoff valve 273 and be designed to by 289 controls of set locking controls, this controls can be made into push button and is contained on the gear-shift lever 288 of driver's seat side (as gear-shift lever state among Fig. 3).Can be closed by manipulation when engaging one grade of locking shutoff valve, the control mechanism of being established in addition when surpassing second gear 291 is closed, and Be Controlled is opened during neutral gear.When gear-shift lever 288 quilts were handled above second gear, the swing arm 292 on the gear-shift lever can be allowed joint locking shutoff valve close by 293 effects of set protuberance among Fig. 3.And gear-shift lever is when getting back to Neutral Position, and a protuberance 294 of this position is also controlled the locking controls 289 that swing arm 292 allows fastener 295 unclamp to be locked, and shown in state among the figure, allows engage the locking shutoff valve and open.

Selector valve 161 comprises valve body 163 and spool wherein 192, is provided with layout reverse gear hydraulic fluid port 166 far away, neutral gear hydraulic fluid port 169 successively and from the corresponding hydraulic fluid port of 171 to four to five grades of one grade of hydraulic fluid ports on the inwall 165 of valve body.Because of change-speed box 155 has four D Drives, set D Drive hydraulic fluid port comprises from one grade to four hydraulic fluid ports of four-speed 171,172,173 and 174 on valve interior wall among Fig. 3.In above-mentioned each hydraulic fluid port, reverse gear hydraulic fluid port 166 is communicated with the oil circuit 181 of one grade of hydraulic fluid port 171 through check valve 167, neutral gear hydraulic fluid port 169 is communicated with oil return line 286, lead to oil circuit joint 44 on the change-speed box 155 through separately oil circuit 170 respectively from one to four-speed D Drive hydraulic fluid port on the valve body 163, be communicated with the fluid chamber of respective clutch respectively again by the corresponding hydraulic fluid port on the oil circuit joint.Spools 192 in the valve body 163 comprise base portion 194, zerk 195 and one grade of sprue 196, and zerk 195 communicates with oil inlet 164 on the valve body.Spool 192 among the figure also can become spool design by the push-pull fashion action by the work of rotary valve mode.When spool 192 is handled by gear-shift lever 288, the zerk 195 on it can be respectively with valve interior wall on each grade hydraulic fluid port connect successively.

After zerk 195 and reverse gear hydraulic fluid port 166 were connected, one grade of sprue 196 positive shield was lived one grade of hydraulic fluid port 171.In hand-hydraulic control system shown in Figure 3, when control gear-shift lever 288 changes to reverse gear, when the zerk 195 of selector valve is connected with reverse gear hydraulic fluid port 166, gear-shift lever is also thrown off first speed driven gear 101 in advance by the synchromesh cover 99 of reverse gear control mechanism, and engages with reverse gear driven gear 110 subsequently.When changing to reverse gear, the reverse gear control mechanism is in the following manner, control piece 307 on the gear-shift lever 288 is closed the shutoff valve 309 on the fuel-displaced pipeline of oil pump 158 earlier by rocking arm 308, the pressure oil that allows oil pump discharge is forced to from by-pass to reverse gear control cylinder 310, promote piston 312 after spring and shift fork 314 drive 99 and one grades in synchromeshs cover earlier and be out of gear at pressure oil, allow the synchromesh cover engage again with reverse gearwheel 110, then, this part pressure oil just oil ring groove 311 that goes out through being got out of the way by piston flows to check valve 269, enters selector valve 161 along oil feed line 271.After the reverse gear free wheel gear shift, because of shutoff valve 309 is opened, the oil effect that no longer is stressed of piston 312 in the reverse gear control cylinder, spring 315 promotes piston 312 returns, makes synchromesh cover 99 and reverse gearwheel throw off also engage with one grade of gear 101 immediately (i.e. state shown in the figure) by shift fork 314 simultaneously.In the reality, should set up corresponding Locking Device, when synchromesh is overlapped not with reverse gear or one grade of gear full engagement, stop gear-shift lever control selector valve to enter a reverse gear or a P PARK Position P.At the zerk 195 of selector valve 161 when the hydraulic fluid port of gear is connected in addition, one grade of sprue 196 be parked in other gear hydraulic fluid port every empty or do not hide the position of stifled each grade hydraulic fluid port.

For the zerk hydraulic oil when linking up with each grade hydraulic fluid port that reduces selector valve is provided with damping liquid compressing cylinder 243 to the joint impact of respective clutch on the corresponding oil circuit 170 of each gear hydraulic fluid port.

In the given hand-hydraulic control system of Fig. 3, though when gear-change operation, just can finish by simple push pull maneuver, but for further alleviating motorist's working strength, make this manually operated hydraulic control system have certain automatic guidance ability, selector valve 161 is also by centrifugal lifting shift controlling mechanism 318 controls.As seen from the figure, the control stalk 319 of this mechanism links to each other with the spool 192 of selector valve 161 by transmission connection piece, the connection head 320 of the control stalk other end is between the ascending, descending shelves spring of controlling on the axle sleeve 321 323,324, this control axle sleeve is installed on the speed shaft 325 that links to each other with the output shaft of change-speed box, and through Transmission 326 by centrifugal 328 on the speed shaft 325 control.During the speed shaft stall, control axle sleeve 321 is back into reference position by set spring 322, the spool 192 of corresponding selector valve 161 also is in Neutral Position (shown in state among the figure), when speed shaft 325 is rotated with different rotating speeds, centrifugal 328 on it just can drive control axle sleeve 321 compression springs 322, allow the control axle sleeve be in corresponding position.Can be parked on the corresponding gear positions for making, on control stalk, be provided with and the corresponding setback castellated plates 329 of each P PARK Position P, be pressed on the setback castellated plates by the prevention wheel 335 of two springs, 330,334 effects by the centrifugal control stalk of being controlled 319.Wherein, at the back of the bigger spring 330 of elastic force, the set spring perch 331 by 332 effects of bottom spring links to each other with brake pedal 302 by Transmission 333, and it can be pulled away from spring 330.

For after selector valve 161 is provided with centrifugal lifting shift controlling mechanism, when speed shaft 325 its rotation speed change amplitudes that driven by change-speed box hour, upgrade or lower category spring 323 or 324 that 321 compressions of the axially movable control axle sleeve of controlled making link to each other with control stalk, and the setback castellated plates 329 of control stalk 319 can be prevented from taking turns 335 and pushes down and can not move, and prevents that control stalk from driving selector valve and doing unnecessary reaction.When the variation of the speed of a motor vehicle goes beyond the limit, control axle sleeve 321 is rising or after the length of spring compressed that lowers category puts in place, the connection head 320 on just can push lever, and drive selector valve 161 upgrades or lowers category after overcoming the elastic force that stops wheel.Stop wheel 335 owing to the bigger spring of elastic force 330 is no longer acted on by brake pedal 302, therefore, utilizing brake pedal to carry out in the brake deceleration process, selector valve 161 is easier along with the reduction of the speed of a motor vehicle to be dropped to corresponding gear automatically by centrifugal lifting shift controlling mechanism.In the reality, also can not establish the spring 323 that upgrades in the centrifugal lifting shift controlling mechanism, and allow this mechanism only have the function that lowers category automatically.

Owing to just can be easy to carry out gear-change operation by the push-and-pull gear-shift lever, for avoiding firmly crossing greatly required gear, gear-shift lever 288 is also got over shelves and is increased 338 effects of oil resistance cylinder, this device as shown in Figure 3, stopper 342 in the oil cylinder 344 on the servo-actuated damping piston 339 links to each other with gear-shift lever 288 through attaching parts 343, stopper is in the middle of the servo-actuated damping piston 339, meta spring 341 by both sides keeps meta, and the clearance space 340 of stoping block both sides can allow it move freely a gear to high or low shelves.A both sides oil pocket 345 that increases oil resistance cylinder 338 at shelves more is respectively equipped with that the oil circuit that is provided with damping hole 348 and normally closed cut-off valve 349 by parallel connection links to each other between two oil circuits, 346, two oil circuits that pick out, and normally closed cut-off valve is braked pedal 302 and controls.Then, two oil circuits 346 link to each other with the both sides oil pocket 351 of control oil cylinder 350 respectively again, in the control oil cylinder, be provided with by the control plunger 352 of meta action of the spring, the piston rod 354 of this piston by both sides can act on the two opposed rocking arms 355 in the outside, can be linked to each other with the shutoff valve 276 that separates of hand-hydraulic control system by the Transmission 356 that two rocking arms drive respectively.Handling that gear-shift lever 288 raises or when reducing a gear, Dong stopper 342 clearance space 340 that just moves past a corresponding side is parked in a side of servo-actuated damping piston 339 thereupon, and the meta spring of this side is compressed.In the time of firmly will crossing selected gear greatly as handling gear-shift lever this moment, Fu stopper 342 will withstand on a side of servo-actuated damping piston, owing to only can't allow servo-actuated damping piston quick travel through two oil pockets of damping hole 348 logical oil, therefore the big resistance that is produced just feeds back to the driver, allows it stop to handle gear-shift lever.After gear-shift lever 288 was parked in a selected gear, meta spring 341 just can promote servo-actuated damping piston 339 and leave stopper 342 gradually, allowed stopper be in the midway location of servo-actuated damping piston 339 again.When in driving, needing shelves operation more, the motorist will firmly handle gear-shift lever, after drive servo-actuated damping piston 339 overcomes spring 353 elastic force of control oil cylinder 350 inner carriers 352, answered the piston rod 354 of a side and separation shutoff valve 276 unlatchings that rocking arm 355 drives the hand-hydraulic control system by piston 352 green phases that hydraulic oil promotes, allow the oil that comes of oil pump return oil return line, the gear of being crossed can not engaged, only after gear-shift lever is parked in corresponding gear, the piston 352 of control in the oil cylinder 350 be return gradually, allow separation shutoff valve 276 get back to off position, the power-transfer clutch that makes hydraulic oil control corresponding gear through selector valve engages.Because normally closed cut-off valve 349 also is braked pedal 302 controls, when stepping on the brake pedal brake, normally closed cut-off valve when being driven unlatching can be eliminated the moving resistance that servo-actuated damping piston 339 is applied, and allows the lifting shift controlling mechanism can drive selector valve 161 smoothly and carries out gear shift.

The selector valve 161 of hand-hydraulic control system is in Neutral Position among Fig. 3, and at this moment the next oil of oil pump 158 is to return oil return line 286 from joint locking shutoff valve 273, starting joint flow regulating valve 274 and the neutral gear hydraulic fluid port of opening 169 along oil feed line 271.Change to one grade of zerk 195 that makes selector valve with 171 connections of one grade of hydraulic fluid port during the ready to start vehicle when handling gear-shift lever 288, at this moment as long as light accelerator pedal 298, when driving engine is quickened, also engaging flow regulating valve 274 by backguy control starting closes gradually, so that stop hydraulic oil flow to oil return line, make the activating pressure of its increase, allow power-transfer clutch engage gradually, make vehicle start one grade of power-transfer clutch.Usually, Das Gaspedal is to be adjusted to the starting driving states that adapts under the normal road conditions to the controller characteristic curve of driving engine and power-transfer clutch, and when under disavantage such as upward slope, starting, for playing walking vehicle smoothly, special incremental adjustments mechanism can be set when starting, suitably increase the power output of driving engine in advance.Simultaneously, also can be this incremental adjustments mechanism and set up the controlled ratchet device that a cover matches with one grade of gear (among the figure picture) simultaneously again.When starting to walk on the upward slope road surface like this, as long as press the control knob of incremental adjustments mechanism earlier, ratchet device will work, stop one grade of transmission gear backward rotation, at this moment unclamp hand brake lever, vehicle can not slide to direction of fall yet, and is changing to one grade also by after handling Das Gaspedal, and vehicle is started to walk on the upward slope road surface.When vehicle start and after reaching certain speed, set incremental adjustments mechanism will get back to original state voluntarily, and ratchet device is also got back to out-of-action position simultaneously.

After vehicle changes to one grade of starting, as be in the traffic congestion state of going slowly that loiters, at this moment can not close and engage locking shutoff valve 273, under this state, as the need ramp to stop, as long as unclamp Das Gaspedal 298, just can allow one grade of power-transfer clutch get back to released state; Quicken as need, as long as gently step on Das Gaspedal, its operation of driving is very easy to.Travel under first gear speed as needing behind the vehicle start, may command engages the locking shutoff valve and closes by it, also can not separate even at this moment unclamp 298, one grades of power-transfer clutchs of Das Gaspedal.Behind the vehicle start, enter second gear, engage locking shutoff valve 273 and can be closed (if one grade time this valve be not closed) voluntarily, allow starting engage flow regulating valve 274 and no longer work by set control mechanism effect as handling gear-shift lever 288.

After selector valve 161 is in the driving shelves and engages locking shutoff valve 273 and also is closed, oily can the making very soon of coming of oil pump reaches rated pressure in the oil feed line, the hydraulic oil that reaches pressure just enters the logical hydraulic fluid port of pressure of unloader valve 358, allow the spool 382 of draining the oil of unloader valve move on to opening (referring to Fig. 4), make coming oil no longer to enter oil feed line and flowing to oil return line 286 of oil pump, allow oil pump be in complete unloading condition.In the hydraulic efficiency pressure system of Fig. 3, set up a low discharge pressure holding pump 159, so that the pressure oil that is leaked away to oil feed line compensation.The unnecessary hydraulic oil that enters oil feed line 271 can return fuel tank 160 through by pass valve 283.

The unloader valve detailed structure that the hand-hydraulic control system is adopted among Fig. 3 is provided with control cylinder 360 and valve opening 368 as shown in Figure 4 in the valve body 359 of unloader valve 358, both link to each other by two oil circuits 374,377 of band check valve.The outside of control cylinder 360 is communicated with oil feed line 271 through the logical hydraulic fluid port 362 of pressure, is provided with logical oil ring groove 363 and oil-feed annular groove 364 on the inwall 361 of control cylinder, and the inside of control cylinder is communicated with oil return line 286.The valve plug 365 that is acted on by spring 366 is housed in control cylinder 360, when this valve plug is pushed up logical hydraulic fluid port 362 sides of pressure by spring, valve plug outwards moves past logical oil ring groove 363 and allows its communicate with oil return line 286 (mode of operation shown in the unloader valve among Fig. 3), when valve plug 365 is inwardly moved past logical oil ring groove 362 and allows oil-feed annular groove 364 expose by the pressure oil effect (state shown in Fig. 4), can allow two annular grooves all communicate with the logical hydraulic fluid port 362 of pressure.Control cylinder 360 is communicated with the valve pocket 370 of valve opening 368 inboards by the oil circuit 374 of the oil-feed annular groove 364 on it through being provided with cutoff port 375 and check valve 376, and this valve pocket is communicated with the logical oil ring groove 363 of control cylinder through the oil circuit 377 of band plunger, unidirectional integrated valve 378 and throttling check valve 381 again simultaneously.Plunger 379 diameters of plunger, unidirectional integrated valve are smaller, and outer end 380 is towards oil return line 286.Be equipped with in valve opening 368 by the spool 382 of draining the oil of action of the spring, spool is provided with oil return slots or the oil discharge outlet 383 that is communicated with oil return line 286.After hydraulic oil ejected the valve pocket 370 of valve opening to spool 382, oil return slots on it or oil discharge outlet 383 were linked up with the oil extraction annular groove 371 on the valve opening inwall 369, and this oil extraction annular groove is communicated on the fuel-displaced pipeline 265 of oil pump 158 through oil discharge outlet 372.When the hydraulic fluid pressure in the oil feed line 271 increased, promotes valve plug 365 in the unloader valve and inwardly moves past logical oil ring groove, because of plunger, unidirectional integrated valve 378 still can not be opened by the oil pressure effect, at this moment hydraulic oil can't enter valve opening 368 and remove the control spool of draining the oil.When the valve plug 365 that is pushed moves past oil-feed annular groove 364, the hydraulic oil of washing valve plug open is just through oil-feed annular groove 364, cutoff port 375 and check valve 376 enter the valve pocket 370 of valve opening, go to promote to drain the oil spool 382 unlatchings, also make simultaneously plunger, unidirectional continuous cropping valve 378 is opened, in spool 382 opening processes of draining the oil, because of also can being pressed into valve pocket 370 to part fluid under action of the spring, valve plug 365 closes oil-feed annular groove 364, but the plunger that this moment, hydraulic oil can be through being opened by oil pressure, unidirectional continuous cropping valve 378 continues the spool 382 of draining the oil is pushed to the complete opening state, shown in Fig. 4 state.Because of the hydraulic oil that enters valve pocket 370 all is the deceleration of process cutoff port, can not make the spool 382 of draining the oil in opening process, produce impact.When the hydraulic oil in the oil feed line reduces because of reason pressure such as neutral gears, valve plug 365 can be shifted to the logical hydraulic fluid port 362 of pressure immediately under action of the spring, logical oil ring groove 363 on the control cylinder inwall is communicated with oil return line 286, shown in unloader valve state among Fig. 3, allow drain the oil spool 382 can be under action of the spring, fluid in the valve pocket is arranged to oil return line rapidly through plunger, unidirectional integrated valve etc., made the spool of draining the oil get back to off position, the oil that comes of oil pump 158 is just arranged to oil feed line again.

First kind of clutch hydraulic pressure engagement type change-speed box of the first kind and the hand-hydraulic control system that matches with this type of variator more than have been described, have gone on to say other different embodiment of this type of variator below with reference to the accompanying drawings.

What Fig. 5, Fig. 6 and Fig. 7 embodiment provided is the diaxon clutch hydraulic pressure engagement type change-speed box that second kind of the first kind of the present invention has five gears that advance, as shown in the figure, this change-speed box has the clutch pack 6 that links to each other with engine crankshaft 1 through self connection minor axis 16, this clutch pack comprises five power-transfer clutchs, utilizes bearing 41 to install by a side master 14 of clutch-bell cover 12 by the connection minor axis 16 that links to each other.In five power-transfer clutchs of clutch pack, four power-transfer clutchs are located in the clutch-bell cover be made of master 14, middle spacer ring 19 and outer shroud 20 two every in the air, make two power-transfer clutchs of each tool of spacer ring 19 both sides.Be provided with binary pressure ring 46 between master 14 and spacer ring 19, its both sides are provided with first and second friction linings 61,62, between spacer ring 19 and outer shroud 20 binary pressure ring 47 are set, and its both sides are provided with third and fourth friction lining 63,64.Being provided with the pressure ring 23 that floats in outer shroud 20 outsides of clutch-bell cover 12, is the 5th friction lining 65 of the 5th power-transfer clutch between outer shroud and the unsteady pressure ring.The pressure ring 23 that floats links to each other with piston 32 on the master 14 outer side cylinders 28 by attaching parts 24, the structure of oil cylinder 28 as shown in Figure 6, this oil cylinder is made of with the outer ring cowling 30 that links to each other the inner sleeve on the master 29, the outer sleeve 33 of its upper piston 32 surrounds oil cylinder 28, and the piston ring flat-plate 34 that picks out from outer sleeve puts in oil cylinder 28.Pass through sealing member 37 slipper seals between the outer sleeve 33 of piston 32 and the master 14 of oil cylinder 28 and the outer ring cowling 30, by sealing member 38 slipper seals, make piston ring flat-plate 34 both sides form hydraulic cavities 35 and counter balance pocket 36 between the inner sleeve 29 of piston ring flat-plate 34 and oil cylinder 28.Hydraulic oil not during apply piston 32 for making its return voluntarily, the piston in counter balance pocket and outside be provided with pull back spring 39 between the ring cowling.Can be controlled by hydraulic oil for making the power-transfer clutch on the clutch pack, every side on the two binary pressure rings 46,47 hydraulic cavities 35 of hydraulic cavities 53 and piston ring flat-plate both sides and counter balance pocket 36 is separately led to through corresponding oil circuit respectively and is enclosed within the oil circuit joint 44 that is connected on the minor axis 16, is controlled by the hand-hydraulic control system by the oil circuit joint again.

Set first imput shaft 70 that matches with clutch pack 6 and on it second, third, the 4th and the 5th driving axle housing 72,73,74 and 75 puts in the above-mentioned clutch pack 6, the inner of first imput shaft 70 links to each other with the power-transfer clutch of inboard first friction lining 61, and its inner and master 14 coaxial movable sets, the inner of second to the 5th driving axle housing then respectively with power-transfer clutch in second to the 5th friction lining 62,63,64 link to each other with 65.In first imput shaft, 70 outsides, be fixed with one grade and reverse driving gear 81,97, be fixed with two to five grades corresponding driving gear 82,83,84 and 85 respectively in the outer end of second to the 5th driving axle housing.On the output shaft 76 that is arranged in parallel with first imput shaft 70, be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear.The layout of these driven gears on output shaft 76 as shown in Figure 7, wherein, one grade, second gear and third gear driven gear 101,102 with 103 respectively the roller 114 by unidirectional fee engine clutch link to each other with output shaft 76, when preventing four, five grades, low-grade driven gear drags the driving gear high speed revolution.And, for first speed driven gear 101, it is behind the roller 114 of unidirectional fee engine clutch, also be sleeved on the output shaft 76 through connecting bushing 115, output shaft links to each other with the reverse gear driven gear 110 of connecting bushing 115 or unsteady suit by the cover of the synchromesh on it 99 again, when preventing reverse gear, first speed driven gear is locked mutually through free-wheel clutch and output shaft.

Link to each other with output shaft through free-wheel clutch with the third gear driven gear owing to one, two, when changing to these gears, can make vehicle can not utilize driving engine to brake.For overcoming this situation, corresponding side (referring to Fig. 7) in one grade, second gear and third gear driven gear 101,102 and 103, be respectively equipped with clutch engagement face 116 with anti-skidding ripple, match with it, on output shaft 76, be respectively equipped with corresponding hydraulic ram 117 and 118, on the piston 120,121 of oil cylinder, also be provided with face of joint 122 accordingly with anti-skidding ripple.The piston 120 of one grade of gear of control is unidirectional action among the figure, and is in disengaged position (not drawing among the figure) by the pull back spring effect, and the piston 121 of control two, 3rd gear is a beidirectional, and (not drawing among the figure) mediated by the meta action of the spring.The corresponding hydraulic ram 117 of on the output shaft 76 each and 118 leads to the oil circuit joint 123 that is enclosed within on the output shaft 76 through separately oil circuit 119 respectively, and then corresponding oil circuit with this grade of control clutch group 6 is communicated with (drawing among the figure).Like this, changing to one, two or during third gear, the power of driving engine can be passed to output shaft through corresponding driven gear and unidirectional fee engine clutch, be subjected to the corresponding oil cylinder of this grade hydraulic oil effect then to promote piston on it, utilization engages with the driven gear of this grade with the face of joint of anti-skidding ripple, so that when output shaft transmits lock torque, can utilize driving engine to brake.Fourth gear and five grades of driven gears 104,105 are fixed on the output shaft 76.

What Fig. 8 embodiment provided is the third coaxial clutch hydraulic pressure engagement type change-speed box of the first kind of the present invention, this change-speed box has five D Drives and a reverse gear, its clutch pack 6 structures and Fig. 5 embodiment are identical, for no other reason than that adopted coaxial layout type, the friction lining of five power-transfer clutchs in the clutch pack by the inboard laterally ordering to be changed at first be the 4th direct speed friction lining 64, be first friction lining 61, second friction lining 62, the 3rd friction lining 63 and the 5th friction lining 65 successively then.The set direct speed imput shaft 69 that matches with clutch pack and on the first, second, third and the 4th driving axle housing 71,72,73 and 74 put in the clutch pack 6, the inner of direct speed imput shaft 69 links to each other with the fourth speed direct speed friction lining 64 of clutch pack inboard, and its inner and master 14 coaxial movable sets, first, second, third then links to each other with 65 with the 5th friction lining 61,62,63 with first, second, third of power-transfer clutch respectively with the inner of the 4th driving axle housing.The outer end of direct speed imput shaft 69 and output shaft 76 directly are fixedly linked, the outside at first driving axle housing 71, be fixed with one grade and reverse driving gear 81,97, in second, third outer end, be fixed with two, three and five grades driving gear 82,83 and 85 respectively with the 4th driving axle housing 72,73 and 74.On the transmission shaft 78 that is arranged in parallel with direct speed imput shaft 69, be respectively equipped with and above-mentioned one, two, three and five grade of driven gear that driving gear is meshed, transmission shaft 78 drives output shafts 76 by a pair of transmission gear 79,80.On transmission shaft 78 in the set corresponding driven gear, as for one, two with third gear driven gear 101,102 and 103 frame modes of linking to each other with transmission shaft of the roller 114 by unidirectional fee engine clutch etc. respectively, be with second kind of change-speed box of above-mentioned Fig. 5 in one, two and the layout of third gear driven gear on output shaft be identical.The 5th grade of driven gear 105 is fixed on the transmission shaft 78.In this coaxial speed variator, fourth speed is directly to drive output shaft 76 by direct speed imput shaft 69, and all the other gears are to drive transmission shaft 78 respectively by each grade transmission gear, and transmission shaft drives output shaft 76 through transmission gear 79,80 again.

As the change-speed box that has five D Drives among Fig. 5 and Fig. 8 is made into four D Drives,, can make the structure of change-speed box more simple like this as long as save the parts and the transmission gear thereof of the 5th grade of power-transfer clutch.

Three kinds of different embodiment of first kind change-speed box more than have been described, the hand-hydraulic control system that matches with this type of variator also has been described simultaneously.The principal feature of this type of variator is that each gear all needs to control with a corresponding power-transfer clutch, and, in described second and third kind change-speed box, one, two and the third gear driven gear also to drive corresponding output shaft or transmission shaft by unidirectional fee engine clutch etc.

Fig. 9 to Figure 14 provides is that the gear of second type changes in advance, the different embodiment of clutch hydraulic pressure engagement type change-speed box, the clutch pack that such change-speed box utilization has three power-transfer clutchs by gear in advance the mode of changing can carry out direct gear conversion to more gear.Change in advance at first kind of diaxon gear of second type that Fig. 9 provides, in the clutch hydraulic pressure engagement type change-speed box, this change-speed box has six D Drives and a reverse gear, it has the clutch pack 7 that links to each other with engine crankshaft 1 through self connection minor axis 16, this clutch pack comprises three power-transfer clutchs, utilizes bearing 41 to install by a side master 14 of clutch-bell cover 12 by the connection minor axis 16 that links to each other.Be provided with binary pressure ring 46 between master 14 in clutch-bell cover 12 and the spacer ring 19, its both sides are provided with first and second friction linings 61,62 of two power-transfer clutchs, be provided with binary pressure ring 47 in spacer ring 19 outsides, the 3rd friction lining 63 of three-clutch is set between the two.The inner split ring both sides of binary pressure ring 46 have each self-hydraulic control 53 of formation, the inner split ring both sides of binary pressure ring 47 have hydraulic cavities separately 53 on counter balance pocket 54, the two binary pressure rings of hydraulic cavities 53 of formation and counter balance pocket 54 and lead to by corresponding oil circuit respectively and be enclosed within the oil circuit joint 44 that connects on the minor axis 16.Set first imput shaft 70 that matches with clutch pack 7 and on the second and the 3rd driving axle housing 72,73 put in the clutch pack, first imput shaft 70 links to each other with first friction lining 61 of clutch pack inboard, and its inner also with master 14 coaxial movable sets, second links to each other with the 3rd friction lining 62,63 with second respectively with the inner of the 3rd driving axle housing 72,73.

Each driving gear on first imput shaft and the second and the 3rd driving axle housing is arranged in the following manner, is provided with the driving gear of fixing a grade, reverse driving gear 81,97 and other gear in first imput shaft, 70 outsides.In the outside of the second and the 3rd driving axle housing 72,73, be respectively equipped with the driving gear of fixing second gear, third speed drive gear 82,83 and other gear.From fourth speed, the driving gear of other set gear is a gear cluster (gear cluster of three gears of less than comes at last) by per three gears of order that upgrade, the driving gear of each gear cluster repeats respectively in order toward first imput shaft 70, second driving axle housing 72 and the 73 cocycle settings of the 3rd driving axle housing make two gears of being separated by between the driving gear of the variant gear on each imput shaft or the driving axle housing.Because of the change-speed box among Fig. 9 has only six D Drives, only constituted a gear cluster by four, five and six grades driving gears, in the more change-speed box of gear, corresponding gear group quantity also can increase.The driving gear of other gear on the imput shaft is that the driving gear of other gear on fourth gear driving gear 84, the second and the 3rd driving axle housing is respectively five grades, six grades driving gears 85,86.

On the output shaft 76 that is arranged in parallel with first imput shaft 70, be respectively equipped with the driven gear that is meshed with each grade driving gear on above-mentioned imput shaft and the driving axle housing, these driven gears are sleeved on the output shaft versatilely, and output shaft 76 is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set.Bi-directional synchronization shift sleeve 126 controls between the driven gear of two gears is arranged at interval, independent driven gear is by unidirectional synchromesh cover 127 controls.Reverse gear driven gear 110 is independent driven gear in the present embodiment, for it is provided with unidirectional synchromesh cover 127, and be located at two gears at interval one, 126 in synchromesh cover between the fourth gear driven gear 101,104, five, 105,102 and three, six grades of driven gears 103,106 of second gear driven gear is two-way function.Set synchromesh cover is controlled by the hydraulic ram of the corresponding shift fork 125 quilts pre-converting mechanism of gear separately respectively.Bi-directional synchronization shift sleeve 126 is by two-way cylinder 128 controls, and one-way synchronization shift sleeve 127 is by single acting oil cylinder 129 controls.

The gear 136 that the gear 77 of the output shaft 76 of change-speed box through its end drives on the transmission shaft 135 among Fig. 9, the bevel gear 137 that passes through the transmission shaft front end again drives the bevel gear 138 of front wheel differential gears, and this layout is applicable to the vehicle of f-w-d.

Second kind of change-speed box of second type that Figure 10 provides improves on the change-speed box basis in Fig. 9, the characteristics of this change-speed box are to have saved the connection minor axis of clutch pack, hydraulic oil by the oil-guiding shaft transmitting control clutch pack of setting up, simultaneously, to one grade of also corresponding resetting of layout with reverse gear active, driven gear.The improvement of this change-speed box as shown in figure 10, clutch pack 7 is directly captiveed joint with bent axle 1 through master 14, on master 14, establish the oil-guiding shaft 42 that passes hollow first imput shaft 70 that picks out in addition, the continuous oil circuit of the hydraulic cavities separately of binary pressure ring 46,47 and counter balance pocket leads to oil-guiding shaft 42 outer ends through oil-guiding shaft respectively in the clutch pack, is connected with cover oil circuit joint 44 thereon again.One grade, reverse driving gear 81,97 are arranged on the other low-grade axle 139 of avoiding oil circuit joint 44, this beam warp transmission gear 140 is driven by the gear 141 of establishing in addition on first imput shaft 70, one grade of first speed driven gear 101 that driving gear 81 drives on the output shaft 76 through a breast wheel 112, reverse driving gear 97 directly drives reverse gear driven gear 110.This improved change-speed box principal feature is that clutch pack 7 can directly be fixed on the bent axle 1 of driving engine, reduced the axial dimension of clutch pack, simultaneously because of oil-guiding shaft not transfer torque can make its diameter less, help the sealing between oil circuit joint and the oil-guiding shaft like this.

What Figure 11 provided is that the third diaxon gear of second type changes in advance, clutch hydraulic pressure engagement type change-speed box, and the clutch pack of this change-speed box has adopted the structural arrangement mode that helps reducing axial dimension.The structure of this change-speed box as shown in Figure 11, it has the clutch pack 8 that links to each other with engine crankshaft 1 through self connection minor axis 16, this clutch pack comprises three power-transfer clutchs, utilizes bearing 41 to install by a side master 14 of clutch-bell cover 12 by the connection minor axis 16 that links to each other.Be provided with binary pressure ring 46 between the master 14 of clutch-bell cover 12 and outer shroud 20, its both sides are provided with first friction lining 61 and second friction lining 62 of two power-transfer clutchs.Be provided with the pressure ring 23 that floats in outer shroud 20 outsides of clutch-bell cover 12, the 3rd friction lining 63 of three-clutch is set between outer shroud and the unsteady pressure ring, the piston 32 that the pressure ring 23 that floats passes through on the oil cylinder 28 in attaching parts 24 and master 14 outsides links to each other.Among the structure of oil cylinder 28 and its upper piston 32 and Fig. 6 in second kind of change-speed box of the first kind oil cylinder and the piston structure of the 5th power-transfer clutch identical.The hydraulic cavities 35 of hydraulic cavities separately 53 on the binary pressure ring 46 and piston 32 both sides and counter balance pocket 36 are led to through corresponding oil circuit respectively and are enclosed within the oil circuit joint 44 that is connected on the minor axis 16.Put in the remainder of clutch pack etc. as for set first imput shaft 70 and second, third driving axle housing 72,73 on it, can be identical with the first kind of change-speed box of second type among above-mentioned Fig. 9.

Usually, one grade of transmitting ratio of twin-shaft transmission can be very not big, in the dual-shaft variable device in Figure 11, for increasing by one grade transmitting ratio, originally set one grade, reverse driving gear are changed to and only establish a driven wheel 111 on first imput shaft 70, drive the reducing gear 147 on the slow-speed shaft of establishing in addition 146 by this driven wheel, one grade, reverse driving gear 81,97 are arranged on the slow-speed shaft 146, one grade of first speed driven gear 101 that driving gear 81 drives on the output shaft 76 through intermediate gear 112, reverse driving gear 97 directly drives reverse gear driven gear 110.Though one of change-speed box grade, reverse gear transmission gear also are to adopt this arrangement among Figure 10, because of after oil-guiding shaft passes first imput shaft, make two, the corresponding increase of three-speed driving gear diameter, two, the three-speed transmitting ratio still is less than normal.

What Figure 12 provided is that the 4th kind of coaxial gear of second type changes in advance, clutch hydraulic pressure engagement type change-speed box, in this change-speed box, to clutch pack 7 and on imput shaft 70 and second, third driving axle housing 72,73 on it arrangement etc. of set each grade driving gear, adopted with above-mentioned Fig. 9 in this type of first kind of structure that change-speed box is identical.After this change-speed box coaxial arrangement among Figure 12, the outer end of first imput shaft 70 and set output shaft 76 coaxial movable sets, with transmission shaft 78 that first imput shaft is arranged in parallel on be respectively equipped with the driven gear that is meshed with each grade driving gear on first imput shaft 70, the second and the 3rd driving axle housing 72,73, transmission shaft 78 drives output shafts 76 through a pair of transmission gear 79,80.Be located at each grade driven gear movable set on the transmission shaft 78 on transmission shaft, transmission shaft 78 is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set, bi-directional synchronization shift sleeve 126 controls between the driven gear of two gears is arranged at interval, independent driven gear is by unidirectional synchromesh cover 127 controls.Because coaxial arrangement, first imput shaft 70 also goes up by it is overlapped 127 by the synchromesh of the pre-converting mechanism control of gear and links to each other with output shaft 76.Last gear on cause first imput shaft 70 is direct speed normally, on first imput shaft, do not establish the driving gear of this gear, because having institute on five D Drive change-speed boxs among Figure 12, to ranked fourth shelves are direct speeds, therefore, on first imput shaft 70, have only the driving gear 81,97 of a grade and reverse gear, and do not establish the driving gear of fourth speed.

Figure 13 provides is that the 5th kind of coaxial gear in second type changes in advance, clutch hydraulic pressure engagement type change-speed box, as seen from the figure, what the clutch pack 8 of this change-speed box adopted is the structure identical with the clutch pack of this type of the third change-speed box among Figure 11, simultaneously, first imput shaft, second with the 3rd driving axle housing 70,72 and 73 on the arrangement of each grade driving gear also this type of change-speed box with above-mentioned is identical.Because of the change-speed box among Figure 13 also is coaxial layout, transmission shaft 78 drives output shafts 76 through a pair of transmission gear 79,80, the mounting means of grade driven gear of each on the transmission shaft and corresponding synchronous shift sleeve etc. all with Figure 12 in the 4th kind of change-speed box be identical.But in this change-speed box of Figure 13, owing to be provided with eight D Drives, for the driving gear 86,88 that makes six grades and eight grades (seven grades are direct speed) can be passed to output shaft 76 to power with suitable transmitting ratio, established a high-grade transmission shaft 148 in this change-speed box in the drawings in addition, six grades and eight grades of driven gears 106,108 are located on the high-grade transmission shaft 148, and this transmission shaft drives output shafts 76 through a pair of transmission gear of setting up 149,150 again.Owing to be separated by less than two gears between six grades and eight grades, therefore be that two grades driven gear 106,108 is provided with respectively by the one-way synchronization shift sleeve 127 of the pre-converting mechanism control of gear.In this change-speed box of Figure 13, the driving gear 85,83 on second, third driving axle housing 72,73 is two grades of shared wheels, not only transmits five grades and three-speed power, also transmits the power of eight grades and six grades.Because of the last step on first imput shaft 70 is the 7th direct speed, on first imput shaft except that establishing one grade, reverse gear shared driving gear 81 and fourth gear driving gear 84, do not establish the 7th grade of driving gear, the 7th grade is overlapped 127 by first imput shaft 70 by synchromesh and passes to output shaft.

Figure 14 provides is that the 6th kind of coaxial gear in second type changes in advance, clutch hydraulic pressure engagement type change-speed box, in this change-speed box, it has the clutch pack 9 that links to each other with engine crankshaft 1 through self connection minor axis 16, and this clutch pack utilizes bearing 41 to install by a side master 14 of clutch-bell cover 12 by the connection minor axis 16 that links to each other.Clutch pack comprises four power-transfer clutchs, and two power-transfer clutchs of every side are in the clutch-bell cover 12 be made of master 14, middle spacer ring 19 and outer shroud 20 two respectively every in the air, make two power-transfer clutchs of each tool of spacer ring 19 both sides.Be provided with binary pressure ring 46 between master 14 and the spacer ring 19, the direct speed friction lining 60 and first friction lining 61 are set in its both sides, be provided with binary pressure ring 47 between spacer ring 19 and outer shroud 20, its both sides are the second and the 3rd friction linings 62,63.Hydraulic cavities separately 53 on the two binary pressure rings 46,47 is led to the oil circuit joint 44 that is enclosed within on the output shaft 76 by corresponding oil circuit respectively, and the power-transfer clutch in the clutch pack can be controlled by the hydraulic oil of hand-hydraulic control system.Set direct speed imput shaft that matches with clutch pack 9 69 and first, second and third driving axle housing 71,72 and 73 on it put in the clutch pack 9, the inner of direct speed imput shaft 69 links to each other with the direct speed friction lining 60 of clutch pack inboard, its the inner also with master 14 coaxial movable sets, the inner of first, second and the 3rd driving axle housing then links to each other with 63 with the 3rd friction lining 61,62 with first, second respectively.Be provided with output shaft 76 in the outer end of direct speed imput shaft 69, diaxon directly is fixedly connected together.Each grade driving gear on each driving axle housing is arranged in the following manner, the outside of first driving axle housing 71 is provided with the driving gear of fixing a grade, reverse driving gear 81,97 and other gear, is respectively equipped with the driving gear of fixing two and third speed drive gear 82,83 and other gear in the outside of the second and the 3rd driving axle housing 72,73.From fourth speed.The driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first, second and the 3rd driving axle housing 71,72 and 73 cocycle settings, makes two gears of being separated by between the driving gear of the variant gear on each driving axle housing.Change-speed box among Figure 14 has nine D Drives, and from fourth gear, four, five and six grades driving gear is a gear cluster, and seven, eight and nine grades driving gear comes second gear cluster, but seven grades are provided with in addition for direct speed.On first driving axle housing 71, only establish one and four-speed driving gear 81 and 84 accordingly, seven grades by 69 transmissions of direct speed imput shaft, on second driving axle housing 72, be provided with two, five and eight grades driving gear 82,85 and 88, on the 3rd driving axle housing 73, be provided with three, six and nine grades driving gear 83,86 and 89.

On the transmission shaft 78 that is arranged in parallel with direct speed imput shaft 69, be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, transmission shaft drives output shafts 76 through a pair of transmission gear 79,80.Being linked to each other with driven gear engagement on it etc. by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set as for transmission shaft 78, is identical with above-mentioned this type of given change-speed box.

Because the change-speed box among Figure 14 also is to have nine more gears, for making one, two and third gear have bigger transmitting ratio, in this change-speed box, be provided with low-grade axle 139 separately for these three gears, as seen from the figure, first, the the 3rd and the 3rd driving axle housing 71, on 72 and 73 one, two and third speed drive gear 81,82 and 83 respectively through separately a pair of reducing gear 142,143 and 144 drive corresponding one on the low-grade axle 139, two and third gear driven gear 101,102 and 103, the gear 80 that low-grade axle drives on the output shaft 76 through intermediate gear 112 by the gear 140 on it again.Low-grade axle 139 is set also is because be difficult to make the diameter of, two and third speed drive gear on first, second and the 3rd driving axle housing further to reduce again, after adopting this arrangement, to be two on low-grade axle, three-speed driven gear 102,103 is provided with unidirectional synchromesh cover 127 respectively, between one grade and these two opposite driven gears 101,110 of reverse gear a bi-directional synchronization shift sleeve 126 is set.

Figure 15 provides is and the gear of above-mentioned second type changes in advance, clutch hydraulic pressure engagement type change-speed box matches hand-hydraulic control system.Compare with the hydraulic control system among Fig. 3, this control system has been set up gear and has been changed valve, delayed-opening valve in advance and hold parts such as oil cylinder, the integral layout of this system and the structural principle of each parts are as shown in figure 15, the fuel-displaced pipeline 265 that picks out from oil pump 158 is divided into two strands, a stock-traders' know-how check valve 269, is provided with the oil circuit 259 that holds oil cylinder 258, the oil-break shutoff valve 285 that is in normally open and auxiliary oil circuit 284 and communicates with the oil inlet 232 that the gear of the pre-converting mechanism of gear changes valve 198 in advance; The oil cut-off valve 260 that holds that another stock-traders' know-how is held oil cylinder 258 controls leads to the fuel feeding qi road 278 with many shunt with total check valve 270.Hold in the oil cylinder 258 by spring-actuated piston 262 and can control it when holding oil pressure and hold oil cut-off valve 260 and open reaching, hold between oil cut-off valve 260 and the total check valve 270 oil circuit 261 and also and the oil discharge outlet 372 of unloader valve 358 be communicated with.In set fuel feeding qi road, article one, through check valve 280 with have the oil circuit 259 that holds oil cylinder 258 and be communicated with, second is closed shutoff valve 281 through neutral gear and is communicated with auxiliary oil circuit 284, article three, the shutoff valve 282 of draining the oil through being in normally off is communicated with oil return line 286, article four, also be communicated with the 5th oil inlet 249 that leads to delayed-opening valve 245 with oil return line through by pass valve 283.

Delayed-opening valve comprises the spool 254 in valve body 246 and its valve opening 249, and the exocoel of valve opening is communicated with oil inlet 249, and valve opening inwall 248 is provided with oil outlet 250, when spool is in off position by action of the spring, shelters from oil outlet 250.The valve opening inner chamber 251 at spool back is communicated with oil return line 286 through cutoff port 252, and oil return line leads to back the valve opening inner chamber through check valve 253 again.

The oil outlet 250 of delayed-opening valve leads to the oil inlet 164 of selector valve 162 through oil feed line 271, on oil feed line 271, be provided with three oil circuits that pick out, article one, oil circuit is communicated with the logical hydraulic fluid port 362 of pressure of unloader valve 358, the joint locking shutoff valve 273 of second oil circuit through being in normally open engages flow regulating valve 274 with the starting that is in series and is communicated with oil return line 286, and the separation shutoff valve 276 of the 3rd oil circuit through being in normally off also is communicated with oil return line 286.

In above-mentioned each valve, oil-break shutoff valve 285, drain the oil shutoff valve 282 with separate shutoff valve 276 and link to each other by being connected control piece 304, and can be braked pedal 302 and get over and grade increase oil resistance cylinder 338 and control respectively.Starting engages flow regulating valve 274 and links to each other with Das Gaspedal 298 through spring 299, and joint locking shutoff valve 273 is closed shutoff valve 281 with neutral gear and controlled jointly by attaching parts 290.Engaging locking shutoff valve 273 can be by locking control action of the joint of gear-shift lever 288 or set locking controls 289 control, and the control mechanism that can be closed by manipulation, be established in addition when surpassing second gear during one grade on this valve is closed, and Be Controlled is opened during neutral gear.The manipulation control that engages locking shutoff valve Be Controlled mechanism is referring to the hydraulic control system among Fig. 3.Gear changes valve 198 in advance and links to each other with selector valve 162, and is controlled jointly by gear-shift lever 288 and centrifugal lifting shift controlling mechanism 318.

Selector valve 162 comprises valve body 163 and spool 193, on valve interior wall 165, be provided with the reverse gear hydraulic fluid port 166 of being in that links to each other with reverse gear oil circuit 168 successively than distant positions, the neutral gear hydraulic fluid port 169 that links to each other with oil return line 286, the one grade of hydraulic fluid port 171 that links to each other with first oil circuit 181, the second gear hydraulic fluid port 172 that links to each other with second oil circuit 182, the third gear hydraulic fluid port 173 that links to each other with the 3rd oil circuit 183 and by the corresponding hydraulic fluid port of tactic other gear that upgrades, from fourth speed hydraulic fluid port 174, the continuous oil circuit of other set gear hydraulic fluid port is an oil circuit group by per three gears of order that upgrade, the oil circuit group of three gears of less than comes at last, the corresponding oil circuit of each oil circuit group is repeated and first through check valve 191 respectively in order, the second and the 3rd oil circuit 181,182 and 183 are connected, and allow first, two gears are spaced between the gear that is had on every oil circuit of the second and the 3rd oil circuit.The reverse gear oil circuit 168 of reverse gear hydraulic fluid port 166 also is communicated with first oil circuit 181 through check valve 167.First, second and the 3rd oil circuit 181,182 and 183 lead to the oil circuit joint 44 of change-speed box 156 respectively, lead to the respective clutch hydraulic cavities 53 (referring to each change-speed box of second type) of clutch pack again by the corresponding hydraulic fluid port on the oil circuit joint.Because the change-speed box among Figure 15 has six D Drives, therefore on valve interior wall 165, be provided with six hydraulic fluid ports of one grade to six grades, only formed an oil circuit group from the hydraulic fluid port of six grades of fourth speeds to the.With four, five oil circuits that link to each other with 176 with six grades of hydraulic fluid ports 174,175 respectively through check valve 191 be communicated to one, two and first, second and the 3rd oil circuit 181,182 and 183 of third gear hydraulic fluid port on.The binary pressure ring counter balance pocket of clutch pack also is communicated with oil return line 286 through oil circuit 287 by behind the oil circuit joint.The spool 193 of selector valve 162 comprises base portion 194, one grade of sprue 196, zerk 195 and according to required at least one of establishing of oil circuit group number sprue 197 at interval.Because of valve body 163 has only an oil circuit group of fourth gear to six grade hydraulic fluid port, a sprue 197 is at interval arranged accordingly on spool 193.Zerk and at interval between the sprue and the hydraulic fluid port distance of two two gears that are spaced between the sprue (when two above oil circuit groups are arranged, plural interval sprue being arranged also) at interval, zerk 195 communicates with oil inlet 164 on the valve body 163.When spool 193 is handled by gear-shift lever 288, the zerk 195 on it can be successively with valve interior wall 165 on each grade hydraulic fluid port link up respectively.When zerk 195 is linked up with reverse gear hydraulic fluid port 166, one grade of sprue 196 shelters from one grade of hydraulic fluid port 171, zerk 195 move past one, two and the third gear hydraulic fluid port after when connecting respectively with the gear hydraulic fluid port more than the fourth gear, set one and the interval sprue 197 set up can shelter from corresponding one, two or third gear hydraulic fluid port 171,172 or 173 all the time respectively so that the hydraulic oil that enters from the above hydraulic fluid port of fourth gear not can from corresponding one, two or the third gear hydraulic fluid port moving to refluxing.

Gear changes the spool 235 that valve 198 comprises valve body 199 and Qi Nei in advance, on valve interior wall 200, be provided with layout reverse gear hydraulic fluid port 231 far away and one grade of hydraulic fluid port more than 201 by upgrading tactic and corresponding each grade hydraulic fluid port of selector valve hydraulic fluid port, owing to be to match, on valve interior wall 200, have six hydraulic fluid ports 201,202,203,204,205 and 206 of one to six grade with change-speed box with six D Drives.The hydraulic fluid port of each gear leads to the corresponding double acting and the single-acting control oil cylinder 128,129 of the pre-converting mechanism of gear on the change-speed box respectively by oil circuit 234 separately, further drive output shafts (or transmission shaft) with in-oil cylinder piston by shift fork 125 and go up corresponding two-way and one-way synchronization shift sleeves 126,127, link to each other with corresponding driven gear engagement on it.The change-speed box of hydraulic control system has six D Drives among Figure 15, one, fourth gear, two, the driven gear of five grades and three, six grades is controlled respectively by three bi-directional synchronization shift sleeves 126, three synchromeshs are applied mechanically three double actings control oil cylinders 128 and are driven, remaining reverse gear driven gear by the one-way synchronization shift sleeve by 129 controls of single-acting oil cylinder.The spool 235 that gear changes valve in advance comprises base portion 236 and three mouthfuls of zerks 237, three mouthfuls of zerks are communicated with oil inlet 232 on the valve body, the width energy while of its zerk links up with the hydraulic fluid port of three adjacent gears that advance, but can not link up reverse gear hydraulic fluid port 166 and one grade of hydraulic fluid port 171 simultaneously.The spool 235 that the spool 193 of selector valve and gear the change valve in advance same moved further that directly links to each other, and the midway location of three mouthfuls of zerks 237 aligns mutually in the zerk 195 of spool 193 and the spool 235.When hydraulic control system being used for Figure 14 and being provided with the coaxial speed variator of direct speed imput shaft 69, change in advance in each set on the valve interior wall 200 of valve D Drive hydraulic fluid port at gear, the direct speed imput shaft relatively the position of gear do not establish this grade hydraulic fluid port.

At the unstart driving engine, (the position when zerk and neutral gear hydraulic fluid port are connected when selector valve also is in Neutral Position, do not draw this state among the figure), the piston 262 that holds in the oil cylinder 258 is pushed to logical hydraulic fluid port 264 by spring, the continuous oil cut-off valve 260 that holds cuts out, neutral gear is closed shutoff valve 281 and at this moment also is in closed condition, and the joint locking shutoff valve 273 that links to each other then is unlocked.After driving engine is started, drive oil pump 158 runnings, hydraulic oil is arranged to oil outlet pipe 265, also be in closed condition because of holding oil cut-off valve 260, this part hydraulic oil just enters through check valve 269 and holds oil cylinder 258, promoting piston 262 moves to the inside, during neutral gear, three mouthfuls of zerks 237 and one grade of hydraulic fluid port 171 of changing valve because of gear in advance are in on-state in advance, one grade of hydraulic fluid port 201 that hydraulic oil also changes valve in advance through auxiliary oil circuit 284 and gear removes to control the control oil cylinder 128 on the change-speed box 156, corresponding synchronous shift sleeve 126 is engaged in advance with first speed driven gear 101, allow clutch pack can change to one grade at any time.Be pushed and make when holding oil cut-off valve 260 and opening when holding in-oil cylinder piston 262, the hydraulic oil of being discharged by oil pump just flows to total check valve 270 through this valve, behind total check valve, enter the oil inlet 249 of delayed-opening valve 245, the spool 254 that promotes in it allows oil outlet 250 expose, this part hydraulic oil joint locking shutoff valve 273 of flowing to the oil inlet 164 of selector valve 162 respectively and open through oil feed line 271 then, the neutral gear hydraulic fluid port 169 through being connected respectively again by the selector valve zerk, engage locking shutoff valve 273 and series connected starting joint flow regulating valve 274 and turn back to oil return line 286.In this hydraulic efficiency pressure system, as long as driving engine started, the oil extraction of oil pump makes just that to hold oil cylinder 258 oil-filled, and transference is held the oil circuit 259 that oil cylinder communicates and is in the operation pressure state all the time, and making gear change valve 198 in advance can be at first by the hydraulic oil effect.

When needs play walking vehicle, handle gear-shift lever 288 earlier and enter a P PARK Position P, allow selector valve interior zerk 195 and one grade of hydraulic fluid port 171 connect, simultaneously, three mouthfuls of zerks 237 that gear changes valve in advance also connect second gear hydraulic fluid port 202 when connecting one grade of hydraulic fluid port 201 in advance.At this moment as long as light accelerator pedal 298, allow starting engage flow regulating valve 274 and turn down gradually, hydraulic oil is carried out throttling, engage, allow vehicle start with regard to the first clutch of may command clutch pack.As needing ramp to stop this moment, as long as unclamp Das Gaspedal, just power-transfer clutch can separate because of losing the oil pressure effect.As at this moment will under one grade of state, travelling, can allow joint locking shutoff valve 273 forward off position to by control, neutral gear is closed then Be Controlled unlatching of shutoff valve 281, and under this state, even unclamp Das Gaspedal 298, corresponding power-transfer clutch can not separate yet.Further quicken as needing behind the vehicle start, can handle gear-shift lever 288 and enter two P PARK Position Ps, allow the zerk 195 of selector valve connect with second gear hydraulic fluid port 172, i.e. position shown in Figure 15, and three mouthfuls of zerks 237 that gear changes in the valve in advance move on to the position of also connecting third gear hydraulic fluid port 203 thereupon.As seen from the figure, though three mouthfuls of zerks 237 that this moment, gear changed valve in advance one on the valve body, two and the third gear hydraulic fluid port connect, allow one, two and third gear driven gear of change-speed box engage, but 195 of the zerks of selector valve 162 are connected with the second gear hydraulic fluid port 172 on the valve body, the second clutch of control clutch group is in engagement state, and allows adjacent first to be in the idling conditions that separates with the third gear power-transfer clutch.At this moment as need to quicken or slow down, can pass through gear-shift lever at any time, control first or three-clutch carry out combination, change to adjacent high or low grade, and in this gearshift procedure, the interrupted time of the power of driving engine is very short.Because selector valve changes valve by being connected control piece by synchro control in advance with gear, no matter selector valve is in any gear that advances, gear changes valve in advance also can follow these shelves, height adjacent with this grade and low-grade driven gear are just engaged when gear shift in advance, so as can by selector valve at any time the control clutch group change to adjacent high or low shelves.

When prominent when meeting bigger sloping Lu Erxu shelves changing to corresponding gear more in the driving, be parked in selected gear after can firmly handling the gear of gear-shift lever 288 in the middle of crossing.When handle gear-shift lever begin to cross in the middle of during gear, shelves increase oil resistance cylinder 338 and allow earlier and separate shutoff valve 276 and the shutoff valve 282 of draining the oil is opened through connecting control piece 343 more, allow oil-break shutoff valve 285 close simultaneously, to prevent to hold institute's hydraulic oil that stored up loss in the oil cylinder 258.After the above-mentioned separation shutoff valve and the shutoff valve of draining the oil were opened, just earial drainage was to oil return line 286 for the pressure oil in its pipeline, and the synchromesh that makes the respective clutch of middle the gear of being crossed and control driven gear is overlapped can Be Controlled because of at this moment can not get pressure oil.After losing oil pressure in the pipeline, at this moment the spool 254 in the delayed-opening valve 245 is also moved on to the position of closing oil outlet 250 by action of the spring, cuts off the oil circuit that flows to selector valve 162.When the manipulation gear-shift lever is parked in selected gear, increase the 338 get out of hand effects of oil resistance cylinder because of getting over shelves, separate shutoff valve 276 and just get back to off position voluntarily with the shutoff valve 282 of draining the oil, also allow simultaneously oil-break shutoff valve 285 open, the hydraulic oil that oil pump is discharged just flows to gear immediately and changes valve 198 and delayed-opening valve 245 in advance, at this moment in delayed-opening valve, because of the hydraulic oil at spool 254 backs can only outwards flow out through cutoff port 252 delayed-opening valve is also opened, the hydraulic oil that oil pump comes just at first changes the synchromesh cover that valve goes to control corresponding gear in advance through gear and engages with driven gear, so that clutch pack can be carried out power joint subsequently.Along with engaging of synchromesh cover and driven gear, as superpressure in the fuel feeding qi road 278, hydraulic oil can release to oil return line 286 through by pass valve 283.After synchromesh cover and corresponding driven gear full engagement, the spool 254 of delayed-opening valve 245 is also promoted to open by hydraulic oil, this part hydraulic oil just goes the respective clutch of control clutch group through selector valve 162 then, make it to engage and transferring power, allow through getting over the motoring condition that the selected gear of shelves adapts to vehicle.State and required time when getting over gear shift are identical with the mode of operation of common manual shift transmission, also are that synchronous earlier back engages.

When brake activation pedal 302 carries out braking brake, be identical when the control that separates the shutoff valve and the shutoff valve of draining the oil etc. is got over gear shift with the manipulation gear-shift lever.But this moment, brake pedal can act on centrifugal lifting shift controlling mechanism (referring to Fig. 3) simultaneously, made this mechanism's easier drive selector valve of energy and gear change valve in advance and slided to corresponding low grade.Behind the loosen the brake, the hydraulic oil that oil pump is discharged can change valve in advance through gear earlier and engage with driven gear by the corresponding synchronous shift sleeve, and delayed-opening valve just allows hydraulic oil remove to control corresponding clutch engagement through selector valve then.

Change to corresponding gear at selector valve 162, when joint locking shutoff valve 273 also is closed, the hydraulic oil that oil pump 158 is discharged makes soon behind the oil cylinder needs that satisfy power-transfer clutch and control synchromesh cover and reaches rated pressure in the pipeline, the hydraulic oil that reaches pressure just enters the logical hydraulic fluid port 362 of pressure of unloader valve 358, allow the interior draining valve of unloader valve move (referring to Fig. 4), make the oil extraction of oil pump flow to oil return line 286 through unloader valve.As long as the oil pressure in the pipeline is reduced to a certain degree because of gear shift etc., unloader valve is just closed the oil circuit that leads to oil return line, and the hydraulic oil that allows oil pump discharge continues to replenish into oil feed line.In the control system of Figure 15, the pressure holding pump 159 that is provided with low discharge replenishes the pressure oil that leaks away, to reduce the action frequency of unloader valve.

What Figure 16 provided is the selector valve that is used to have ten D Drive change-speed boxs, owing to have ten D Drives, is provided with ten hydraulic fluid ports from a grade to ten grades on the valve body 163 of selector valve.From fourth speed, the hydraulic fluid port of other set gear has been divided into three oil circuit groups, and wherein, four to six grades is one group, and seven to nine grades is second group, and last the 3rd group is had only ten grades of hydraulic fluid ports.Every oil circuit in these three oil circuit groups all is communicated with first, second and the 3rd oil circuit 181,182 and 183 respectively successively through check valve 191.Because of three oil circuit groups are arranged, correspondingly on the spool 193 be provided with three at interval sprues 197, the zerk 195 of spool is in the position that communicates with eight grades of hydraulic fluid ports 178 among the figure, the interval sprue of corresponding midway location is just hiding blocks second gear hydraulic fluid port 172, and the hydraulic oil that enters from eight grades of hydraulic fluid ports can not flowed out from the second gear hydraulic fluid port.On first, second and the 3rd oil circuit, be respectively equipped with vibration reduction and cushioning oil cylinder 243, impact, make engaging process more soft to slow down hydraulic fluid pressure suffered in the clutch's jointing process.Selector valve among Figure 15 and Figure 16 and gear change in advance that valve all adopts with rotation mode work, during practical application, also can make valve by the guiding valve mode of push-and-pull and work.

In the reality, gear is many more, and the required transmission gear of change-speed box also can be many more, and these variable gears that are in the constant-mesh state have only one group to carry out transmission of power, and the gear of remainder only can dally and increase loss due to friction.For a change this state, this change-speed box is being used for diesel locomotive and during through vehicle that the express highway of being everlasting travels, adopted Figure 17 given change valve in advance through improved gear, this valve as shown in the figure, it has three independent hydraulic fluid ports 238,239 and 240 to the broad hydraulic fluid port of three mouthfuls of zerks 237 in the valve body 199 instead, the middle hydraulic fluid port 239 directly oil inlet 232 on valve body is communicated with auxiliary oil circuit 284, after the side hydraulic fluid port 238,240 on both sides was communicated with together, oil circuit 241 and the change-over valve 242 established through other were communicated with auxiliary oil circuit 284 again.When vehicle with the long period when a static stall moves, be the fuel-economizing operation, but the fuel feeding that manipulation transforms valve 242 cuts off to both sides hydraulic fluid port 238,240 and makes it be communicated with oil return line 286.After handling like this, the height of adjacent gear and low-grade synchromesh cover are just got back to and the driven gear phase-separated state because of the effect that can not get pressure oil, allow two parts transmission gear of 2/3rds of adjacent gear no longer be stopped operating by drive, the loss due to friction of change-speed box is reduced, also allow these gears not frayed simultaneously.In this state as adopt when being provided with the change-speed box of direct speed imput shaft among Figure 14, as just utilizing direct speed imput shaft transferring power this moment, then all the transmission gear of gears all will stop operating.When road condition change need change to other gear, shift to an earlier date the manipulation transforms valve, allow the height of adjacent gear and low-grade respective synchronization shift sleeve with after driven gear engages, just can handle gear-shift lever at any time and change to high or low grade.Certainly, owing to the transmission gear that makes stall, driving axle housing etc. reach synchronous speed, need to prolong certain synchronous engagement time, this just requires to strengthen the resistance to abrasion of synchromesh cover, perhaps sets up special mechanism such as automatically controlled and makes the transmission gear of stall reach synchronous speed.

The first and second two kinds of each change-speed box and corresponding manual hydraulic control systems in dissimilar have been described in above embodiment.In above-mentioned change-speed box of the present invention, given hydraulic control system is the mechanical type mechanism that a kind of energy satisfies basic operation needs, in the reality, in order to make change-speed box can more adapt to the rotating speed of driving engine and different road conditions, can set up modern electronic control package for it fully, also can set up automatically controlled best gear suggestion device, make the motorist change to best gear by signal prompt.

Change in advance at the second type gear of the present invention, in the clutch engagement formula change-speed box, owing to increase the suffered less-restrictive of its gear quantity, have the easiest gear-change operation mode simultaneously again, therefore this change-speed box can be applicable to most of vehicles.This change-speed box with after turbine transformer matches, because of having had better low speed starting ability, more be applicable to heavy goods vehicle, the higher power-driven gear of cost that also can replace in the diesel locomotive being adopted.

Claims (15)

1. the clutch hydraulic pressure engagement type change-speed box that is used for self-propelled vehicle, feature of the present invention is: it has the imput shaft (70) that links to each other with engine crankshaft (1), on imput shaft, be fixed with the driving gear of four D Drives and a reverse gear, on the driven shaft (96) that is arranged in parallel with imput shaft (70), be set with second, third and the 4th driven axle sleeve (92), (93) and (94) versatilely, put at these driven shafts and be fixed with the driven gear that is meshed with two, three and fourth gear driving gear on the imput shaft (70) respectively; The driven gear (101) that is meshed with one grade and reverse driving gear (81), (97) on the imput shaft, (110) movable set are on driven shaft (96), and driven shaft links to each other with one grade or the engagement of reverse gear driven gear by the synchromesh cover (99) on it; Set driven shaft and each the driven axle sleeve outer end on it put in the clutch pack (5) that has four power-transfer clutchs on the output shaft (76), clutch pack is fixed on the output shaft by the master (14) of clutch-bell cover (12), four power-transfer clutchs of clutch pack are located in the clutch-bell cover be made of master (14), middle spacer ring (19) and outer shroud (20) two every in the air, make spacer ring (19) both sides respectively have two power-transfer clutchs; Between master (14) and spacer ring (19), be provided with binary pressure ring (46), first and second friction linings (61), (62) are arranged in its both sides, be provided with another binary pressure ring (47) between spacer ring (19) and outer shroud (20), third and fourth friction lining (63), (64) are arranged in its both sides; The driven shaft (96) that puts in clutch pack links to each other with first friction lining (61) in the clutch pack, and, the end of driven shaft also with the coaxial movable set of master (14) of clutch pack, second, third with the 4th driven axle sleeve (92), (93) and (94) then respectively with clutch pack in second, third link to each other with (64) with the 4th friction lining (62), (63); Binary pressure ring (46), (47) be that side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), pass through sealing member (56) slipper seal between intermediate sleeve (49) and the inner split ring (21), make inner split ring both sides formation hydraulic cavities (53) separately, the hydraulic cavities separately (53) on the two binary pressure rings is led to the oil circuit joint (44) that is enclosed within on the output shaft (76) by corresponding oil circuit respectively.

2. the clutch hydraulic pressure engagement type change-speed box that is used for self-propelled vehicle, feature of the present invention is: it has the clutch pack (6) that links to each other with engine crankshaft (1) through self connection minor axis (16), this clutch pack comprises five power-transfer clutchs, utilizes bearing (41) to install by a side master (14) of clutch-bell cover (12) by the connection minor axis (16) that links to each other; In five power-transfer clutchs of clutch pack, four power-transfer clutchs are located in the clutch-bell cover be made of master (14), middle spacer ring (19) and outer shroud (20) two every in the air, make spacer ring (19) both sides respectively have two power-transfer clutchs; Be provided with binary pressure ring (46) between master (14) and spacer ring (19), its both sides are provided with first and second friction linings (61), 62); Between spacer ring (19) and outer shroud (20) binary pressure ring (47) is set, its both sides are provided with third and fourth friction lining (63), (64); Binary pressure ring (46), (47) are that the side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), by sealing member (56) slipper seal, make the inner split ring both sides form hydraulic cavities (53) between intermediate sleeve (49) and the inner split ring (21); Outer shroud (20) outside at clutch-bell cover is provided with unsteady pressure ring (23), it between outer shroud and the unsteady pressure ring the 5th friction lining (65) of the 5th power-transfer clutch, the pressure ring (23) that floats links to each other with piston (32) on the outer side cylinder of master (14) (28) by attaching parts (24), oil cylinder (28) is made of with the outer ring cowling (30) that links to each other the inner sleeve on the master (29), the outer sleeve of its upper piston (32) surrounds oil cylinder (28), the piston ring flat-plate (34) that picks out from outer sleeve puts in oil cylinder (28), pass through sealing member (37) slipper seal between the outer sleeve (33) of piston (32) and the master (14) of oil cylinder (28) and the outer ring cowling (30), by sealing member (38) slipper seal, make piston ring flat-plate (34) both sides form hydraulic cavities (35) and counter balance pocket (36) between the inner sleeve (29) of piston ring flat-plate (34) and oil cylinder (28); Every side on two binary pressure rings (46), (47) hydraulic cavities (35) of hydraulic cavities (53) and piston ring flat-plate (34) both sides and counter balance pocket (36) is separately led to through corresponding oil circuit respectively and is enclosed within the oil circuit joint (44) that is connected on the minor axis (16); Set first imput shaft (70) that matches with clutch pack (6) and on second, third, the 4th and the 5th driving axle housing (72), (73), (74) and (75) put in the clutch pack, the inner of first imput shaft (70) links to each other with first friction lining (61) of inboard power-transfer clutch, and its inner and the coaxial movable set of master (14), the inner of second to the 5th driving axle housing then links to each other with (65) with second to the 5th friction lining (62), (63), (64) of power-transfer clutch respectively; In first imput shaft (70) outside, be fixed with one grade and reverse driving gear (81), (97), be fixed with two to five grades corresponding driving gear (82), (83), (84) and (85) respectively in the outer end of second to the 5th driving axle housing; On the output shaft (76) that is arranged in parallel with first imput shaft (70), be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, wherein, one grade, second gear and third gear driven gear (81), (82) link to each other with output shaft (76) by the roller (114) of unidirectional fee engine clutch respectively with (83), and, first speed driven gear (101) is behind the roller (114) of unidirectional fee engine clutch, also be sleeved on the output shaft (76) through connecting bushing (115), output shaft links to each other with reverse gear driven gear (110) engagement of connecting bushing (115) or movable set by the synchromesh cover (99) on it again; At one grade, second gear and third gear driven gear (101), (102) and a corresponding side of (103), be respectively equipped with clutch engagement face (116) with anti-skidding ripple, match with it, on output shaft (76), be respectively equipped with corresponding hydraulic ram (117), (118), also be provided with face of joint (122) on the piston in oil cylinder (120) (121) with anti-skidding ripple, the corresponding hydraulic ram of on the output shaft each (117), (118) lead to the oil circuit joint (123) that is enclosed within on the output shaft (76) through corresponding oil circuit (119) respectively, be communicated with the corresponding oil circuit of this grade of control clutch group (6) again; Fourth gear and five grades of driven gears (104), (105) are fixed on the output shaft (76).

3. the clutch hydraulic pressure engagement type change-speed box that is used for self-propelled vehicle, feature of the present invention is: it has the clutch pack (6) that links to each other with engine crankshaft (1) through self connection minor axis (16), this clutch pack comprises five power-transfer clutchs, utilizes bearing (41) to install by a side master (14) of clutch-bell cover (12) by the connection minor axis (16) that links to each other; In five power-transfer clutchs of clutch pack, four power-transfer clutchs are located in the clutch-bell cover be made of master (14), middle spacer ring (19) and outer shroud (20) two every in the air, make spacer ring (25) both sides respectively have two power-transfer clutchs; Be provided with binary pressure ring (46) between master (14) and spacer ring (19), its both sides are provided with the 4th direct speed friction lining (64) and first friction lining (61); Be provided with binary pressure ring (47) between spacer ring (19) and outer shroud (20), its both sides are provided with the second and the 3rd friction lining (62), (63); Binary pressure ring (46), (47) are that the side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), by sealing member (56) slipper seal, make the inner split ring both sides form hydraulic cavities (53) between intermediate sleeve (49) and the inner split ring (21); Outer shroud (20) outside at clutch-bell cover is provided with unsteady pressure ring (23), it between outer shroud and the unsteady pressure ring the 5th friction lining (65) of the 5th power-transfer clutch, the pressure ring (23) that floats links to each other with piston (32) on the outer side cylinder of master (14) (28) by attaching parts (24), oil cylinder (28) is made of with the outer ring cowling (30) that links to each other the inner sleeve on the master (29), the outer sleeve of its upper piston (32) surrounds oil cylinder (28), the piston ring flat-plate (34) that picks out from outer sleeve puts in oil cylinder (38), pass through sealing member (37) slipper seal between the outer sleeve (33) of piston (32) and the master (14) of oil cylinder (28) and the outer ring cowling (30), by sealing member (38) slipper seal, make piston ring flat-plate (34) both sides form hydraulic cavities (35) and counter balance pocket (36) between the inner sleeve (29) of piston ring flat-plate (34) and oil cylinder (28); Every side on two binary pressure rings (46), (47) hydraulic cavities (35) of hydraulic cavities (53) and piston ring flat-plate (34) both sides and counter balance pocket (36) is separately led to through corresponding oil circuit respectively and is enclosed within the oil circuit joint (44) that is connected on the minor axis (16); The set direct speed imput shaft (69) that matches with clutch pack (6) and on the first, second, third and the 4th driving axle housing (71), (72), (73) and (74) put in the clutch pack, the inner of direct speed imput shaft (69) links to each other with the 4th direct speed friction lining (64) of clutch pack inboard, and its inner and coaxial movable set of master (14), first, second, third then links to each other with (65) with the 5th friction lining (61), (62), (63) with first, second, third of power-transfer clutch respectively with the inner of the 4th driving axle housing; The outer end of direct speed imput shaft (69) and output shaft (76) directly are fixedly linked, the outside in first driving axle housing (71), be fixed with one grade and reverse driving gear (81), (97), in second, third outer end, be fixed with two, three and five grades driving gear (82), (83) and (85) respectively with the 4th driving axle housing (72), (73) and (74); On the transmission shaft (78) that is arranged in parallel with direct speed imput shaft (69), be respectively equipped with and above-mentioned one, two, three and five grades of driven gears that driving gear is meshed, transmission shaft (78) is by a pair of transmission gear (79), (80) drive output shaft (76), go up in set each grade driven gear at transmission shaft (78), one, two and third gear driven gear (101), (102) link to each other with transmission shaft (78) by the roller (114) of unidirectional fee engine clutch respectively with (103), and, first speed driven gear (101) also is sleeved on the transmission shaft (78) through connecting bushing (115) behind the roller (114) of unidirectional fee engine clutch, and transmission shaft links to each other with reverse gear driven gear (110) engagement of connecting bushing (115) or movable set by the synchromesh cover (99) on it again; At one grade, second gear and third gear driven gear (101), (102) and a corresponding side of (103), be respectively equipped with clutch engagement face (116) with anti-skidding ripple, match with it, on transmission shaft (78), be respectively equipped with corresponding hydraulic ram (117), (118), piston (120) at hydraulic ram, (121) also be provided with face of joint (122) on accordingly with anti-skidding ripple, control one, two and the corresponding hydraulic ram of third gear driven gear lead to the oil circuit joint (123) that is enclosed within on the transmission shaft (78) through separately oil circuit (119) respectively, be communicated with the corresponding oil circuit of this grade of control clutch group (6) again; Five grades of driven gears (105) are fixed on the transmission shaft (78).

4. hand-hydraulic control system that is used for any one described change-speed box of claim 1 to 3, the fuel-displaced pipeline (265) that picks out from the oil pump (158) of this system had both led to the oil discharge outlet (372) of unloader valve (358), lead to oil feed line (271) through check valve (269) again, feature of the present invention is: the oil feed line (271) that comes from check valve (269) not only is communicated with the oil inlet (164) of selector valve (161), also be provided with three on it to the oil circuit that picks out, wherein, oil circuit (277) is communicated with the logical hydraulic fluid port (362) of pressure of unloader valve (358), oil circuit (272) through being in normally open joint locking shutoff valve (273) and the starting joint flow regulating valve (274) that is in series be communicated with oil return line (286), the separation shutoff valve (276) of oil circuit (275) through being in normally off also leads to oil return line (286); In above-mentioned each valve, selector valve (161) links to each other with gear-shift lever (288), separating shutoff valve (276) links to each other with brake pedal (302), starting engages flow regulating valve (274) and links to each other with Das Gaspedal (298) through spring (299), engaging locking shutoff valve (273) can be by locking control action of the joint of gear-shift lever (288) or set locking controls (289) control, and the control mechanism (291) that can be closed by manipulation, be established in addition when surpassing second gear during one grade on this valve is closed, Be Controlled is opened during neutral gear; Selector valve (161) comprises valve body (163) and spool wherein (192), on the inwall (165) of valve body, be provided with layout reverse gear hydraulic fluid port (166) far away successively, neutral gear hydraulic fluid port (169) and from the corresponding hydraulic fluid port of to four to five grades of one grade of hydraulic fluid ports (171), wherein, reverse gear hydraulic fluid port (166) is communicated with the oil circuit (181) of one grade of hydraulic fluid port (171) through check valve (167), neutral gear hydraulic fluid port (169) is communicated with oil return line (286), one grade to four to five grades corresponding hydraulic fluid port on the valve body (163) leads to oil circuit joint (44) on the change-speed box (155) through separately oil circuit respectively, be communicated with the fluid chamber of respective clutch respectively again by the corresponding hydraulic fluid port on the oil circuit joint, spool (192) in the valve body (163) comprises base portion (194), zerk (195) and one grade of sprue (196), zerk (195) is communicated with oil inlet (164) on the valve body, when spool (192) is handled by gear-shift lever (288), zerk on it (195) can be respectively with valve interior wall on each grade hydraulic fluid port connect successively, when zerk (195) is connected with reverse gear hydraulic fluid port (166), one grade of sprue (196) is just sheltering from one grade of hydraulic fluid port (171), and this moment, gear-shift lever (288) is also thrown off first speed driven gear in advance by the synchromesh cover (99) of reverse gear control mechanism, and engage with the reverse gear driven gear subsequently, zerk (195) when in addition the hydraulic fluid port of gear is connected, one grade of sprue (196) be parked in other gear hydraulic fluid port every empty or do not hide the position of stifled each grade hydraulic fluid port.

5. the gear that is used for self-propelled vehicle changes in advance, clutch hydraulic pressure engagement type change-speed box, feature of the present invention is: it has the clutch pack (7) that links to each other with engine crankshaft (1) through self connection minor axis (16), this clutch pack comprises three power-transfer clutchs, side master (14) by clutch-bell cover (12) utilizes bearing (41) to install by the connection minor axis (16) that links to each other, be provided with binary pressure ring (46) between master (14) in clutch-bell cover (12) and the spacer ring (19), its both sides are provided with first and second friction linings (61) of two power-transfer clutchs, (62), be provided with binary pressure ring (47) in spacer ring (19) outside, the 3rd friction lining (63) of three-clutch is set between the two; Binary pressure ring (46), (47) be that side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), pass through sealing member (56) slipper seal between intermediate sleeve (49) and the inner split ring (21), make the inner split ring both sides of binary pressure ring (46) form hydraulic cavities (53) separately, the inner split ring both sides of binary pressure ring (47) form hydraulic cavities (53) and counter balance pocket (54), and hydraulic cavities separately (53) on the two binary pressure rings and counter balance pocket (54) are led to the oil circuit joint (44) that is enclosed within on the connection minor axis (16) by corresponding oil circuit respectively; Set first imput shaft (70) that matches with clutch pack (7) and on the second and the 3rd driving axle housing (72), (73) put in the clutch pack, first imput shaft (70) links to each other with first friction lining (61) of clutch pack inboard, and its inner also with the coaxial movable set of master (14), second links to each other with the 3rd friction lining (62) (63) with second respectively with the inner of the 3rd driving axle housing (72), (73); Be provided with fixing one grade in first imput shaft (70) outside, reverse driving gear (81), (97) and the driving gear of other gear, at the second and the 3rd driving axle housing (72), (73) the outside, be respectively equipped with fixing second gear, third speed drive gear (82), (83) and the driving gear of other gear, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first imput shaft (70), second driving axle housing (72) and the 3rd driving axle housing (73) cocycle setting make two gears of being separated by between the driving gear of the variant gear on each imput shaft or the driving axle housing; On the output shaft (76) that is arranged in parallel with first imput shaft (70), be respectively equipped with the driven gear that is meshed with each grade driving gear on above-mentioned imput shaft and the driving axle housing, these driven gears are sleeved on the output shaft versatilely; Output shaft (76) is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set, bi-directional synchronization shift sleeve (126) control between the driven gear of two gears is arranged at interval, independent driven gear is controlled by unidirectional synchromesh cover (127).

6. change-speed box according to claim 5, it is characterized in that: clutch pack (7) is directly captiveed joint with bent axle (1) through master (14), on master (14), establish the oil-guiding shaft (42) that passes hollow first imput shaft (70) that picks out in addition, binary pressure ring (46) in the clutch pack, (47) the hydraulic cavities separately and the continuous oil circuit of counter balance pocket lead to the oil-guiding shaft outer end through oil-guiding shaft respectively, be connected with cover oil circuit joint (44) thereon again, one grade, reverse driving gear (81), (97) be arranged on the other low-grade axle (139) of avoiding the oil circuit joint, this beam warp transmission gear (140) is driven by the gear (141) of establishing in addition on first imput shaft (70), the first speed driven gear (101) of one grade of driving gear (81) on a breast wheel (112) drive output shaft, reverse driving gear (97) directly drives reverse gear driven gear (110).

7. the gear that is used for self-propelled vehicle changes in advance, clutch hydraulic pressure engagement type change-speed box, feature of the present invention is: it has the clutch pack (8) that links to each other with engine crankshaft (1) through self connection minor axis (16), this clutch pack comprises three power-transfer clutchs, side master (14) by clutch-bell cover (12) utilizes bearing (41) to install by the connection minor axis (16) that links to each other, between the master (14) of clutch-bell cover (12) and outer shroud (20), be provided with binary pressure ring (46), its both sides are provided with first friction lining (61) and second friction lining (62) of two power-transfer clutchs, binary pressure ring (46) is that the side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), by sealing member (56) slipper seal, make the inner split ring both sides form hydraulic cavities (53) separately between intermediate sleeve (49) and the inner split ring (21); Outer shroud (20) outside at clutch-bell cover is provided with unsteady pressure ring (23), the 3rd friction lining (63) of three-clutch is set between outer shroud and the unsteady pressure ring, the pressure ring (23) that floats links to each other by the piston (32) on the oil cylinder (28) outside attaching parts (24) and the master (14), oil cylinder (28) is made of with the outer ring cowling (30) that links to each other the inner sleeve on the master (29), the outer sleeve (33) of its upper piston (32) surrounds oil cylinder (28), the piston ring flat-plate (34) that picks out from outer sleeve puts in oil cylinder (28), pass through sealing member (37) slipper seal between the outer sleeve (33) of piston (32) and the master (14) of oil cylinder (28) and the outer ring cowling (30), by sealing member (38) slipper seal, make piston ring flat-plate (34) both sides form hydraulic cavities (35) and counter balance pocket (36) between the inner sleeve (29) of piston ring flat-plate (34) and oil cylinder (28); The hydraulic cavities separately (53) on the binary pressure ring (46) and the hydraulic cavities (35) of piston both sides and counter balance pocket (36) are led to through corresponding oil circuit respectively and are enclosed within the oil circuit joint (44) that is connected on the minor axis (16); Set first imput shaft (70) that matches with clutch pack (8) and on the second and the 3rd driving axle housing (72), (73) put in the clutch pack, first imput shaft (70) links to each other with first friction lining (61) of clutch pack inboard, and its inner also with the coaxial movable set of master (14), second links to each other with the 3rd friction lining (62), (63) with second respectively with the inner of the 3rd driving axle housing (72), (73); Be provided with fixing one grade in first imput shaft (70) outside, reverse driving gear (81), (97) and the driving gear of other gear, at the second and the 3rd driving axle housing (72), (73) the outside, be respectively equipped with fixing second gear, third speed drive gear (82), (83) and the driving gear of other gear, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first imput shaft (70), the circulation of second driving axle housing (72) and the 3rd driving axle housing (73) is provided with, and makes two gears of being separated by between the driving gear of the variant gear on each imput shaft or the driving axle housing; On the output shaft (76) that is arranged in parallel with first imput shaft (70), be respectively equipped with the driven gear that is meshed with each grade driving gear on above-mentioned imput shaft and the driving axle housing, these driven gears are sleeved on the output shaft versatilely; Output shaft (76) is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set, bi-directional synchronization shift sleeve (126) control between the driven gear of two gears is arranged at interval, independent driven gear is controlled by unidirectional synchromesh cover (127).

8. the gear that is used for self-propelled vehicle changes in advance, clutch hydraulic pressure engagement type change-speed box, and feature of the present invention is; It has the clutch pack (7) that links to each other with engine crankshaft (1) through self connection minor axis (16), this clutch pack comprises three power-transfer clutchs, side master (14) by clutch-bell cover (12) utilizes bearing (41) to install by the connection minor axis (16) that links to each other, between master (14) on the clutch-bell cover (7) and spacer ring (19), be provided with binary pressure ring (46), its both sides are provided with first and second friction linings (61) of two power-transfer clutchs, (62), be provided with binary pressure ring (47) in spacer ring (19) outside, the 3rd friction lining (63) of three-clutch is set between the two; Binary pressure ring (46), (47) be that side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), pass through sealing member (56) slipper seal between intermediate sleeve (49) and the inner split ring (21), make the inner split ring both sides of binary pressure ring (46) form hydraulic cavities (53) separately, the inner split ring both sides of binary pressure ring (47) form hydraulic cavities (53) and counter balance pocket (54), and hydraulic cavities separately (53) on the two binary pressure rings and counter balance pocket (54) are led to the oil circuit joint (44) that is enclosed within on the connection minor axis (16) by corresponding oil circuit respectively; Set first imput shaft (70) that matches with clutch pack (7) and on the second and the 3rd driving axle housing (72), (73) put in the clutch pack, first imput shaft (70) links to each other with first friction lining (61) of clutch pack inboard, and its inner also with the coaxial movable set of master (14), second links to each other with the 3rd friction lining (62), (63) with second respectively with the inner of the 3rd driving axle housing (72), (73); Be provided with fixing one grade in first imput shaft (70) outside, reverse driving gear (81), (97) and the driving gear of other gear, at the second and the 3rd driving axle housing (72), (73) the outside, be respectively equipped with fixing second gear, third speed drive gear (82), (83) and the driving gear of other gear, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first imput shaft (70), the circulation of second driving axle housing (72) and the 3rd driving axle housing (73) is provided with, and makes two gears of being separated by between the driving gear of the variant gear on each imput shaft or the driving axle housing; The outer end of first imput shaft (70) and the set coaxial movable set of output shaft (76), with transmission shaft (78) that first imput shaft is arranged in parallel on be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, transmission shaft (78) drives output shaft (76) through a pair of transmission gear (79), (80); Be located at each grade driven gear movable set on the transmission shaft (78) on transmission shaft, transmission shaft (78) is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set, bi-directional synchronization shift sleeve (126) control between the driven gear of two gears is arranged at interval, independent driven gear is controlled by unidirectional synchromesh cover (127); First imput shaft (70) is also by being linked to each other with output shaft (76) engagement by the synchromesh cover (127) of the pre-converting mechanism control of gear on it, usually, last gear on first imput shaft (70) is a direct speed, does not establish the driving gear of this gear on first imput shaft.

9. the gear that is used for self-propelled vehicle changes in advance, clutch hydraulic pressure engagement type change-speed box, feature of the present invention is: it has the clutch pack (8) that links to each other with engine crankshaft (1) through self connection minor axis (16), this clutch pack comprises three power-transfer clutchs, side master (14) by clutch-bell cover (12) utilizes bearing (41) to install by the connection minor axis (16) that links to each other, between the master (14) of clutch-bell cover (12) and outer shroud (20), be provided with binary pressure ring (46), its both sides are provided with first friction lining (61) and second friction lining (62) of two power-transfer clutchs, binary pressure ring (46) is that the side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), by sealing member (56) slipper seal, make the inner split ring both sides form hydraulic cavities (53) separately between intermediate sleeve (49) and the inner split ring (21); Outer shroud (20) outside at clutch-bell cover is provided with unsteady pressure ring (23), the 3rd friction lining (63) of three-clutch is set between outer shroud and the unsteady pressure ring, the pressure ring (23) that floats links to each other with piston (32) on the outer side cylinder of master (14) (28) by attaching parts (24), oil cylinder (28) is made of with the outer ring cowling (30) that links to each other the inner sleeve on the master (29), the outer sleeve (33) of its upper piston (32) surrounds oil cylinder (28), the piston ring flat-plate (34) that picks out from outer sleeve puts in oil cylinder (28), pass through sealing member (37) slipper seal between the outer sleeve (33) of piston (32) and the master (14) of oil cylinder (28) and the outer ring cowling (30), by sealing member (38) slipper seal, make piston ring flat-plate (34) both sides form hydraulic cavities (35) and counter balance pocket (36) between the inner sleeve (29) of piston ring flat-plate (34) and oil cylinder (28); Two hydraulic cavities (53) on the binary pressure ring (46) and the hydraulic cavities (35) of piston ring flat-plate both sides and counter balance pocket (36) are led to through separately oil circuit respectively and are enclosed within the oil circuit joint (44) that is connected on the minor axis (16); Set first imput shaft (70) that matches with clutch pack (8) and on the second and the 3rd driving axle housing (72), (73) put in the clutch pack, first imput shaft (70) links to each other with first friction lining (61) of clutch pack inboard, and its inner also with the coaxial movable set of master (14), second links to each other with the 3rd friction lining (62), (63) with second respectively with the inner of the 3rd driving axle housing (72), (73); Be provided with fixing one grade in first imput shaft (70) outside, reverse driving gear (81), (97) and the driving gear of other gear, at the second and the 3rd driving axle housing (72), (73) the outside, be respectively equipped with fixing second gear, third speed drive gear (82), (83) and the driving gear of other gear, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first imput shaft (70), the circulation of second driving axle housing (72) and the 3rd driving axle housing (73) is provided with, and makes two gears of being separated by between the driving gear of the variant gear on each imput shaft or the driving axle housing; The outer end of first imput shaft (70) and the set coaxial movable set of output shaft (76), with transmission shaft (78) that first imput shaft is arranged in parallel on be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, transmission shaft (78) drives output shaft (76) through a pair of transmission gear (79), (80); Be located at each grade driven gear movable set on the transmission shaft (78) on transmission shaft, transmission shaft (78) is linked to each other with driven gear engagement on it by the synchromesh cover of the pre-converting mechanism of gear control accordingly by set, bi-directional synchronization shift sleeve (126) control between the driven gear of two gears is arranged at interval, independent driven gear is controlled by unidirectional synchromesh cover (127); First imput shaft (70) is also by being linked to each other with output shaft (76) engagement by the synchromesh cover (127) of the pre-converting mechanism control of gear on it, usually, last gear on first imput shaft (70) is a direct speed, does not establish the driving gear of this gear on first imput shaft.

10. the gear that is used for self-propelled vehicle changes in advance, clutch hydraulic pressure engagement type change-speed box, feature of the present invention is: it has the clutch pack (9) that links to each other with engine crankshaft (1) through self connection minor axis (16), and this clutch pack utilizes bearing (41) to install by a side master (14) of clutch-bell cover (12) by the connection minor axis (16) that links to each other; Clutch pack comprises four power-transfer clutchs, and two power-transfer clutchs of every side are in the clutch-bell cover (12) be made of master (14), middle spacer ring (19) and outer shroud (20) two respectively every in the air, make two power-transfer clutchs of each tool of spacer ring (19) both sides; Be provided with binary pressure ring (46) between master (14) and the spacer ring (19), direct speed friction lining (60) and first friction lining (61) are set in its both sides, be provided with binary pressure ring (47) between spacer ring (19) and outer shroud (20), its both sides are the second and the 3rd friction lining (62), (63); Binary pressure ring (46), (47) be that side ring body (48) by both sides constitutes with the intermediate sleeve that links to each other (49), be provided with the inner split ring (21) that is fixed on the clutch-bell cover inwall (13) between the both sides of the binary pressure ring ring bodies (48), pass through sealing member (55) slipper seal between the side ring body (48) of binary pressure ring and the clutch-bell cover inwall (13), pass through sealing member (56) slipper seal between intermediate sleeve (49) and the inner split ring (21), make inner split ring (21) both sides formation hydraulic cavities (53) separately, the hydraulic cavities separately (53) on the two binary pressure rings is led to the oil circuit joint (44) that is enclosed within on the connection minor axis (16) by corresponding oil circuit respectively; Set direct speed imput shaft (69) that matches with clutch pack (9) and first, second and third driving axle housing (71) on it, (72) and (73) put in the clutch pack, the inner of direct speed imput shaft (69) links to each other with inboard direct speed friction lining (60), its inner also with the coaxial movable set of master (14), the inner of first, second and the 3rd driving axle housing then links to each other with (63) with the 3rd friction lining (61), (62) with first, second respectively; Be provided with output shaft (76) in the outer end of direct speed imput shaft (69), diaxon directly is fixedly connected together, be provided with fixing one grade in the outside of first driving axle housing (71), reverse driving gear (81), (97) and the driving gear of other gear, at the second and the 3rd driving axle housing (72), (73) the outside is respectively equipped with fixing second gear and third speed drive gear (82), (83) and the driving gear of other gear, from fourth speed, the driving gear of other set gear is a gear cluster by per three gears of order that upgrade, the gear cluster of three gears of less than comes at last, the driving gear of each gear cluster repeats respectively in order toward first, the second and the 3rd driving axle housing (71), (72) and (73) cocycle setting, make two gears of being separated by between the driving gear of the variant gear on each driving axle housing; On the transmission shaft (78) that is arranged in parallel with direct speed imput shaft (69), be respectively equipped with the driven gear that is meshed with above-mentioned each grade driving gear, transmission shaft drives output shaft (76) through a pair of transmission gear (79), (80); Be located at each grade driven gear movable set on the transmission shaft (78) on transmission shaft, transmission shaft (78) is connected with a joggle by the synchromesh cover and the driven gear on it of the pre-converting mechanism control of gear accordingly by set, bi-directional synchronization shift sleeve (126) control between the driven gear of two gears is arranged at interval, independent driven gear is controlled by unidirectional synchromesh cover (127); On corresponding driving axle housing, do not establish the driving gear of direct speed imput shaft institute respective notch.

11. hand-hydraulic control system that is used for any one described change-speed box of claim 5 to 10, feature of the present invention is: the fuel-displaced pipeline (265) that picks out from the oil pump (158) of this system is divided into two strands, a stock-traders' know-how check valve (269), is provided with the oil circuit (259) that holds oil cylinder (258), the oil-break shutoff valve (285) that is in normally open and auxiliary oil circuit (284) and communicates with the oil inlet (232) that the gear of the pre-converting mechanism of gear changes valve (198) in advance; Another stock-traders' know-how held oil cylinder (258) control hold oil cut-off valve (260) and always check valve (270) lead to fuel feeding branch road (278) with many shunt, hold in the oil cylinder (258) by spring-actuated piston (262) and control it when holding oil pressure and hold oil cut-off valve (260) and open reaching, hold between oil cut-off valve (260) and the total check valve (270) oil circuit (261) and also and the oil discharge outlet (372) of unloader valve (358) be communicated with; In set fuel feeding branch road, article one, through check valve (280) with have the oil circuit (259) that holds oil cylinder (258) and be communicated with, second is closed shutoff valve (281) through neutral gear and is communicated with auxiliary oil circuit (284), article three, the shutoff valve of draining the oil (282) through being in normally off is connected with oil return line (286), article four, also be communicated with the 5th oil inlet (249) that leads to delayed-opening valve (245) with oil return line through by pass valve (283); Delayed-opening valve comprises the spool (254) in valve body (246) and its valve opening (249), the exocoel of valve opening is communicated with oil inlet (249), valve opening inwall (248) is provided with oil outlet (250), when spool is in off position by action of the spring, shelter from oil outlet (250), the valve opening inner chamber (251) at spool back is communicated with oil return line (286) through cutoff port (252), and oil return line leads to back the valve opening inner chamber through check valve (253) again; The oil outlet of delayed-opening valve (250) leads to the oil inlet (164) of selector valve (162) through oil feed line (271), on oil feed line (271), be provided with three oil circuits that pick out, article one, oil circuit is communicated with the logical hydraulic fluid port (362) of pressure of unloader valve (358), the second oil circuit through being in normally open joint locking shutoff valve (273) and the starting joint flow regulating valve (274) that is in series be communicated with oil return line (286), the separation shutoff valve (276) of the 3rd oil circuit through being in normally off also is communicated with oil return line (286); In above-mentioned each valve, oil-break shutoff valve (285), the shutoff valve (282) of draining the oil links to each other by being connected control piece with separation shutoff valve (276), and can be braked pedal (302) and more shelves increase oil resistance cylinder (338) and control respectively, starting engages flow regulating valve (274) and links to each other with Das Gaspedal (298) through spring (299), joint locking shutoff valve (273) is closed shutoff valve (281) with neutral gear and is controlled jointly by attaching parts, engaging locking shutoff valve (273) can be by locking control action of the joint of gear-shift lever (288) or set locking controls (289) control, can be closed by manipulation during one grade on this valve, the control mechanism of being established in addition when surpassing second gear is closed, Be Controlled is opened during neutral gear; Gear changes valve (198) in advance and links to each other with selector valve (162), and by gear-shift lever (288) and the common control of centrifugal lifting shift controlling mechanism (318); Selector valve (162) comprises valve body (163) and spool (193), on valve interior wall (165), be provided with the reverse gear hydraulic fluid port (166) of being in that links to each other with reverse gear oil circuit (168) successively than distant positions, the neutral gear hydraulic fluid port (169) that links to each other with oil return line (286), the one grade of hydraulic fluid port (171) that links to each other with first oil circuit (181), the second gear hydraulic fluid port (172) that links to each other with second oil circuit (182), the third gear hydraulic fluid port (173) that links to each other with the 3rd oil circuit (183) and by the corresponding hydraulic fluid port of tactic other gear that upgrades, from fourth speed hydraulic fluid port (174), the continuous oil circuit of other set gear hydraulic fluid port is an oil circuit group by per three gears of order that upgrade, the oil circuit group of three gears of less than comes at last, the corresponding oil circuit of each oil circuit group is repeated and first through check valve (191) respectively in order, the second and the 3rd oil circuit (181), (182) and (183) be connected, allow first, two gears that are spaced between the gear that is had on every oil circuit of the second and the 3rd oil circuit, the reverse gear oil circuit (168) of reverse gear hydraulic fluid port (166) also is communicated with first oil circuit (181) through check valve (167); First, second and the 3rd oil circuit (181), (182) and (183) are led to the oil circuit joint (44) of change-speed box respectively, lead to the respective clutch hydraulic cavities (53) of clutch pack again by the corresponding hydraulic fluid port on the oil circuit joint; The spool (193) of selector valve (162) comprises base portion (194), one grade of sprue (196), zerk (195) and according to required at least one of establishing of oil circuit group number sprue (197) at interval, zerk and at interval between the sprue and the two hydraulic fluid port distances that are spaced two gears at interval between the sprues, zerk (195) communicates with oil inlet (164) on the valve body (163); When spool (193) is handled by gear-shift lever, zerk on it (195) can be successively with valve interior wall (165) on each grade hydraulic fluid port link up respectively, when zerk (195) is linked up with reverse gear hydraulic fluid port (166), one grade of sprue (196) shelters from one grade of hydraulic fluid port (171), zerk (195) move past one, two and the third gear hydraulic fluid port after when connecting respectively with the gear hydraulic fluid port more than the fourth gear, set one and the interval sprue (197) set up can shelter from corresponding one, two or the third gear hydraulic fluid port all the time respectively; Gear changes valve (198) in advance and comprises valve body (199) and the spool (235) in it, be provided with layout reverse gear hydraulic fluid port (231) far away on the valve interior wall (200) and more than one grade of hydraulic fluid port (201) by upgrading tactic and corresponding each grade hydraulic fluid port of selector valve hydraulic fluid port, the hydraulic fluid port of each gear leads to the corresponding double acting and the single-acting control oil cylinder (128) of the pre-converting mechanism of gear on the change-speed box respectively by oil circuit separately, (129), further drive corresponding two-way and one-way synchronization shift sleeve (126) on output shaft or the transmission shaft with in-oil cylinder piston by shift fork (125), (127); The spool (235) that gear changes valve in advance comprises base portion (236) and three mouthfuls of zerks (237), three mouthfuls of zerks are communicated with oil inlet (232) on the valve body, the width energy while of its zerk links up with the hydraulic fluid port of three adjacent gears that advance, but can not link up reverse gear hydraulic fluid port (166) and one grade of hydraulic fluid port (171) simultaneously, the spool (235) that the spool of selector valve (193) and gear the change valve in advance same moved further that directly links to each other, and the midway location of three mouthfuls of zerks (237) is to align mutually in the zerk (195) of spool (193) and the spool (235).

12. hand-hydraulic control system according to claim 11, it is characterized in that: the broad hydraulic fluid port that gear is changed in advance three mouthfuls of zerks (237) of valve (198) has three independent hydraulic fluid ports (238) instead, (239) and (240), middle hydraulic fluid port (239) the directly oil inlet (232) on valve body is communicated with auxiliary oil circuit (284), the side hydraulic fluid port (238) on both sides, (240) after being communicated with together, oil circuit (241) and the change-over valve (242) established through other are communicated with auxiliary oil circuit (284) again, when the needs fuel-economizing moves, change-over valve (242) cuts off to both sides hydraulic fluid port (238), (240) fuel feeding, and it is communicated with oil return line (286).

13. centrifugal lifting shift controlling mechanism that is used for claim 4,11 or 12 described hand-hydraulic control system, it is characterized in that: the control stalk of this mechanism (319) links to each other with the spool of selector valve by transmission connection piece, the connection head (320) of the control stalk other end is between ascending, descending shelves spring (323) in control axle sleeve (321), (324), this control axle sleeve is installed on the speed shaft (325) that links to each other with the output shaft of change-speed box, and is controlled by centrifugal (328) on the speed shaft through Transmission (326); During speed shaft (325) stall, control axle sleeve (321) is back into reference position by set spring (322), and the spool of corresponding selector valve also is in Neutral Position; On control stalk (319), be provided with and the corresponding setback castellated plates of each P PARK Position P (329), be pressed on the setback castellated plates by the prevention of two actions of the spring wheel (335), wherein, back at the bigger spring (330) of elastic force, the set spring perch (331) by bottom spring (332) effect links to each other with brake pedal (302) by Transmission (333), and it can be pulled away from spring (330).

14. shelves more that are used for right demand 4,11 or 12 described hand-hydraulic control system increase the oil resistance cylinder, it is characterized in that: the stopper (342) on the interior servo-actuated damping piston of oil cylinder (344) (339) links to each other with gear-shift lever (288) through attaching parts, stopper is in the middle of the servo-actuated damping piston (339), kept meta by the meta spring (341) of both sides, the clearance space of stopper both sides (340) can allow it move freely a gear to high or low shelves; A both sides oil pocket (345) that increases oil resistance cylinder (338) at shelves more is respectively equipped with two oil circuits (346) that pick out, the oil circuit that is provided with damping hole (348) and normally closed cut-off valve (349) by parallel connection between two oil circuits links to each other, normally closed cut-off valve is braked pedal (302) control, then, two oil circuits (346) link to each other with the both sides oil pocket (351) of control oil cylinder (350) respectively again, in the control oil cylinder, be provided with by the control plunger of meta action of the spring (352), the piston rod (354) of this piston by both sides can act on the two opposed rocking arms (355) in the outside, can be linked to each other with the shutoff valve (276) that separates of hand-hydraulic control system by the Transmission (356) that two rocking arms drive respectively.

15. a unloader valve that is used for claim 4,11 or 12 described hand-hydraulic control system is characterized in that; In the valve body (359) of unloader valve (358), be provided with control cylinder (360) and valve opening (368), both link to each other by two oil circuits (374), (377) of band check valve, the outside of control cylinder (360) is communicated with oil feed line (271) through the logical hydraulic fluid port (362) of pressure, be provided with logical oil ring groove (363) and oil-feed annular groove (364) on the inwall (361) of control cylinder, the inside of control cylinder is communicated with oil return line (286); In control cylinder (360), be equipped with by the valve plug (365) of spring (366) effect, when this valve plug is pushed up logical hydraulic fluid port (362) side of pressure by spring, valve plug outwards moves past logical oil ring groove (363), allow logical oil ring groove communicate with oil return line, inwardly moved past logical oil ring groove (363) and allow oil-feed annular groove (364) when exposing by the pressure oil effect at valve plug (365), can allow two annular grooves all communicate with the logical hydraulic fluid port (362) of pressure; Control cylinder (360) is communicated with by the inboard valve pocket (370) of the oil circuit (374) of the oil-feed annular groove (364) on it through being provided with cutoff port (375) and check valve (376) and valve opening (368), this valve pocket is communicated with the logical oil ring groove (363) of control cylinder through the oil circuit (377) of band plunger, unidirectional integrated valve (378) and throttling check valve (381) again simultaneously, the plunger of plunger, unidirectional integrated valve (379) diameter is smaller, and outer end (384) are towards oil return line (286); In valve opening (368), be equipped with by the spool of draining the oil (382) of action of the spring, spool is provided with oil return slots or the oil discharge outlet (383) that is communicated with oil return line (286), after hydraulic oil ejects the valve pocket (370) of valve opening to spool (382), oil return slots on it or oil discharge outlet (383) are linked up with the oil extraction annular groove (371) on the valve opening inwall (369), and the oil extraction annular groove is communicated with the fuel-displaced pipeline (265) of oil pump (158) through oil discharge outlet (372).

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