CN101133266B - Multi-ratio automatic transmission with independent rate of engagement and/or disengagement control of friction elements - Google Patents

Abstract

A multi-ratio automatic transmission (10) for a vehicle, the transmission (10) having at least one planetary gear set (16, 18), a plurality of friction elements (C1, C2, C3, B1, B2) for coupling components of the planetary gear set (16, 18) between an input and an output of the transmission in different configurations so as to achieve a plurality of drive ratios, and a control system (26) for selectively engaging/disengaging the friction elements (C1, C2, C3, B1, B2) in different combinations to effect selection of the ratios, wherein rate of engagement and/or disengagement of one or more of the friction elements (C1, C2, C3, B1, B2) is controlled independently of the or each of the other friction element(s) (C1, C2, C3, B1, B2).

Description

Have engage and/or throw off friction element control independent than the ratio of manying automatic transmission

Technical field

The present invention relates to a kind of transmission device, more specifically but not exclusively relate to a kind of many grades of automatic transmissions that are used for automobile.

Background technique

The automatic transmission that is used for automobile extensively is used in modern vehicle, because their conveniently and easily use and are approved.The development trend of this automatic transmission is to produce the ratio that more advances, so that better acceleration and fuel economy to be provided.Early stage automatic transmission has two ratios that advance, when the motor with transmission device coupling was forced to first grade of higher speed ground rotation, owing in order to realize acceptable top-speed capability, the spacing between the ratio was very wide, so acceleration and fuel economy are restricted.But in recent years, the automatic transmission that is used for automobile has developed into has 3,4,5 and 6 ratios that advance.Owing to have the ratio that more advances, ratio at interval must be tightr, still realized good top-speed capability simultaneously, and like this, motor can carry out work in narrower best effort district, so that improve fuel economy and/or performance.

But this many ratios automatic transmission relies on several friction elements usually, so that work between various ratios.Particularly, many ratios automatic transmission engages two friction elements at least at each ratio usually.Friction element is generally the form of clutch and clamping strap, because the frictional property of their work, clutch and clamping strap produce heat (wasting energy thus), and are worn and torn.

Specific many ratios automatic transmission has 6 ratios that advance, and it is worked by 5 friction elements of engagement/disengagement, and described 5 friction elements are made of 3 clutches and 2 clamping straps.Yet each ratio that advances need engage two in 5 friction elements.

The claimant determines that such transmission device upper frequency ground is used to be controlled at the friction element of operating between the ratio of transmission device, and its efficient is very low, and it is favourable therefore less using friction element for many ratios automatic transmission.

Summary of the invention

According to an aspect, a kind of many ratios automatic transmission that is used for vehicle is provided, this transmission device has: at least one planetary gear set; A plurality of friction elements, the parts of the planetary gear set under the different conditions that is used to be coupled between the input and output of transmission device are so that realize a plurality of velocity ratios; And control system, be used for different combinations engagement/disengagement friction element selectively, to implement the selection of velocity ratio, wherein, the control of the joint of one or more friction elements and/or the situation of disengagement is independent of each other friction element.

Advantageously, the independent control of the situation of this joint and/or disengagement can be controlled described one or more friction element adaptively.Self adaptive control, for example, can be the smooth transition that is used to realize between the drive gears state, be used to realize being fit to the shift feel (shift feel) and/or the shift property of coupling vehicle working condition and driver's input, be used to regulate wearing and tearing that the transmission device life period produces or leakage or the like.

Preferably, each ratio is corresponding at least one discrete shelves state of transmission device, at at least one grade state, drive kinetic current and be conducted through the overrunning clutch that is arranged to only transmit in one direction driving, like this, the rotation of overrunning clutch prevents that transmission device from providing from being input to the braking of output, at other grade state, this clutch is by bypass, to allow from being input to the braking of output.Preferably, overrunning clutch is the inclined wedge type overrunning clutch.Alternatively, overrunning clutch can be roller clutch, mechanical diode (mechanical diode) or the like.

More preferably, this transmission device has: give at least one grade state of fixed-ratio, wherein allow from being input to the braking of output; With another replacement shelves state of same ratio, wherein overrunning clutch can be operated and be used for preventing that transmission device is input to the braking of transmission device output.

Preferably, this transmission device has: automatic mode, the variation of selection ratio automatically under this pattern; And manual mode, the manually variation of selection ratio under this pattern, wherein, described shelves state is used for reaching the described fixed-ratio of giving at manual mode, and described replacement shelves state is used for reaching the described fixed-ratio of giving at automatic mode.In an alternative form, described shelves state is used for reaching the described fixed-ratio of giving at automatic mode, replaces the shelves state and is used for reaching to fixed-ratio at manual mode.

Preferably, transmission device has at least two planetary gear set, and the parts of the planetary gear set that a plurality of friction elements are connected between can being operated and being used for being coupling in input and exporting under different conditions are so that realize a plurality of velocity ratios.

In an example, transmission device has 6 ratios that advance, and whole 6 controls of advancing between the ratio are implemented by the engagement/disengagement of 5 friction elements.More preferably, 5 friction elements comprise 3 clutches and 2 clamping straps.Again more preferably, each clutch in 3 clutches all has substantially the apply piston of balance (apply piston) eccentrically.At least one clamping strap can have position transducer, is used to detect the position of clamping strap during the clamping strap engagement/disengagement, for use in control system.Preferably, when transmission device was positioned at the replacement shelves, transmission device only had a friction element to be engaged.

Preferably, transmission device has first, second and three-clutch (for example, C1, C2﹠amp; C3) and first and second clamping straps (for example, B1﹠amp; B2).More preferably, at first grade, second clutch is engaged, and second clamping strap is engaged, and other friction element is thrown off.Preferably, replacing first grade of state, second clutch is engaged, and other friction element is thrown off.Replacing first grade of state, adopt overrunning clutch, so that prevent that transmission device is from being input to the braking of output.Preferably, for second ratio of transmission device, second clutch is engaged, and first clamping strap is engaged, and other friction element is thrown off.Preferably, for the 3rd ratio of transmission device, second clutch is engaged, and three-clutch is engaged, and other friction element is thrown off.Preferably, for the 4th ratio of transmission device, second clutch is engaged, and first clutch is engaged, and other friction element is thrown off.Preferably, for the 5th ratio of transmission device, first and three-clutch be engaged, other friction element is thrown off.Preferably, for the 6th ratio of transmission device, first clutch is engaged, and first clamping strap is engaged, and other friction element is thrown off.Preferably, for the reverse gear ratio of transmission device, three-clutch is engaged, and second clamping strap is engaged, and other friction element is thrown off.

According to another aspect, a kind of many ratios automatic transmission that is used for vehicle is provided, this transmission device has: at least one planetary gear set; A plurality of friction elements, the parts of the planetary gear set under the different conditions that is used to be coupled between the input and output of transmission device are so that realize a plurality of velocity ratios; And control system, be used for different combinations engagement/disengagement friction element selectively, to implement the selection of velocity ratio, control system comprises the electrohydraulic system with a plurality of electromagnetic control valves, wherein, when vehicle predetermined than low speed or when being lower than it and advancing, by the selection operation electromagnetic control valve to throw off one or more friction elements, can implement the neutral state in the driving of transmission device automatically, thus, transmission device output is thrown off from the driving of transmission device input.

According to another aspect, a kind of many ratios automatic transmission that is used for vehicle is provided, transmission device has a plurality of ratios that advance, wherein, selection by engagement/disengagement friction element enforcement advancing ratio, described engagement/disengagement drives by the control system with at least one electromagnetic control valve, and when not using under the given state of electromagnetic control valve at transmission device, electromagnetic control valve is isolated in order to avoid be exposed to hydrodynamic pressure.

By reducing hydraulic leak by this way, can be under the situation that the oil hydraulic pump consumed energy reduces, the desirable hydraulic pressure in the realization system.

According to another aspect, a kind of many ratios automatic transmission that is used for vehicle is provided, this transmission device has: at least one planetary gear set; A plurality of friction elements, the parts of the planetary gear set under the different conditions that is used to be coupled between the input and output of transmission device are so that realize a plurality of velocity ratios; And overrunning clutch, wherein, each ratio is corresponding at least one discrete shelves state of transmission device, at at least one grade state, drive kinetic current and be conducted through the overrunning clutch that is arranged to only transmit in one direction driving, like this, the rotation of overrunning clutch prevents that transmission device from providing from being input to the braking of output, at other grade state, this clutch is by bypass, to allow from being input to the braking of output.

A kind of many ratios automatic transmission module, it has: first planetary gear set; The control gear group can be selected following arbitrary so that the friction element of a plurality of ratios that advance to be provided:

Be used for the control gear group so that another friction element of 4 ratios that advance to be provided; Or

Another planetary gear set of connecting with first planetary gear set, it is positioned at the downstream along actuating unit from direction first planetary gear set that is input to output; Be used to control second planetary gear set and move so that the device of at least 5 ratios that advance to be provided with first planetary gear set.

Can also use other parts to be used for special applications more velocity ratio to be provided and/or to revise transmission device, for example front-wheel drive application, mixed power drive to be used or the like.

According to another aspect, a kind of method of changing automatic transmission is provided, described automatic transmission has at least three friction elements, and this method comprises the following steps:

Remove a friction element;

Provide a planet gear train to replace this friction element; With

Provide a control system, to operate other friction element independently of one another.

According to another aspect, a kind of automatic transmission with 6 ratios that advance is provided, wherein, transmission device is constructed to be permeable to omit mechanical hardware, so that the automatic transmission with 4 ratios that advance is provided.

Description of drawings

With reference to accompanying drawing, by non-limitative example the present invention is illustrated, wherein:

Figure 1A is the concise and to the point cross sectional view of transmission device, has also shown the concise and to the point diagrammatic sketch of the electrohydraulic control system of transmission device;

Figure 1B is the concise and to the point cross sectional view of Figure 1A, has shown additional mark;

Fig. 1 C is the concise and to the point cross sectional view of Figure 1A and 1B, has shown additional mark;

Fig. 2 A is the sectional view of the transmission device of Fig. 1;

Fig. 2 B is the sectional view that is arranged to the transmission device of use in the front-wheel drive structure;

Fig. 3 is the tabulation that is used for the gear-changing component of the various gears that the transmission device of Fig. 1 and Fig. 2 has;

Fig. 4 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the neutral state of transmission device;

Fig. 5 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of first grade of state of transmission device;

Fig. 6 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of manual first grade of state of transmission device;

Fig. 7 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of second grade of state of transmission device;

Fig. 8 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of the third gear state of transmission device;

Fig. 9 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of the fourth speed state of transmission device;

Figure 10 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of the 5th grade of state of transmission device;

Figure 11 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of the 6th grade of state of transmission device;

Figure 12 is the power flow chart of the transmission device of Fig. 1 and Fig. 2, has shown the kinetic current of the reverse gear state of transmission device;

Figure 13 is the pressure-current curve diagram for normal high variable discharge (bleed) solenoid valve of electrohydraulic control system shown in Figure 1;

Figure 14 is the pressure-current curve diagram for the normal low variable discharge solenoid valve of electrohydraulic control system shown in Figure 1;

Figure 15 is the pressure-current curve diagram for the normal low O/I solenoid valve of electrohydraulic control system shown in Figure 1;

Figure 16 is to the applied force/moment of torsion of the damper of the lock-up clutch of the torque converter of Fig. 1 and Fig. 2 transmission device-damper displacement plotted curve; With

Figure 17 is the sectional view that is arranged to the transmission device of use in mixed power drives;

Embodiment

Foreword

With reference to Figure 1A, 1B, 1C and 2A, automatic transmission 10 in particular for rear wheel drive vehicle, have bell housing 12, lay torque converter 14, three friction clutch C1, C2 and C3, two clamping strap B1 and B2, the first simple planetary group 16, the 2nd Ravigneux formula planetary gear set 18 and overrunning clutch 20 in this bell housing 12.Because each clutch C1, C2 and C3 and clamping strap B1 and B2 all are friction element (that is, being used for keeping a part by friction selectively with respect to another part), so transmission device 10 has five friction elements altogether.Transmission device 10 utilizes these mechanical parts, power is passed to the output 24 of transmission device 10 from the input 22 of transmission device 10 with different ratios.Exemplary transmission device shown in the accompanying drawing provides six reverse gear ratio and the neutral states that are used for the forward gear ratio of pushing ahead of vehicle and are used for the reverse propulsion vehicle.

Fig. 2 B has shown the replacement structure of the similar transmission device 10 that is suitable for the front-wheel drive application form.The layout of the major character of transmission device itself is similar to the layout shown in Figure 1A, 1B, 1C and the 2A, and similarly signature is same reference character.Can see that main difference is, in Fig. 2 B, torque converter 14 and its bell housing are positioned at the side of transmission device, like this, torque converter is around rotating with the isolated axis of the axis of transmission device, so that suitably construct the spatial constraints that causes by typical front-wheel drive.

Except carrying out powerdriven these mechanical parts, transmission device 10 also comprises the electrohydraulic control system 26 that the bottom as Fig. 1 schematically illustrates.Electrohydraulic control system 26 has storage tank 28, and described storage tank keeps the storage of hydraulic fluid 30, and hydraulic fluid 30 passes filter 32 and sucks in the whole hydraulic pressure pipe network with reference character 34 expressions.Hydraulic pressure pipe network 34 has pump 36, be used for providing pressure to hydraulic fluid, like this, hydraulic fluid can flow through hydraulic pressure pipe network 34, is used for the cooler 38 of cooling liquid hydraulic fluid 30, manually operated valve 40 and the various valve and the solenoid valve of the driver's operation in response to the motion of the shelves mode selector of vehicle by vehicle, control the flow that hydraulic fluid flows through pipe network 34 by valve and solenoid valve, so that operated clutch C1, C2 and C3, clamping strap B1 and B2 and torque converter 14, and provide lubricating to transmission device 10.Solenoid valve is controlled via the electronic control system (not shown), electronic control system can form the part of CAN (control area net), in CAN, information and other electronic control unit (are for example shared, control unit of engine, the tractive force control unit, skid control brake system control unit, air bag controlled unit or the like).

The mechanical part general introduction

When transmission device 10 typical cases are installed in vehicle interior, to bolt anchoring spare 42, the engine bolt of vehicle is fixed on the torque converter 14 with bolt by the flywheel that makes motor.Thereby the rotation of flywheel is delivered to the shell 44 of torque converter 14.By being positioned at torque converter shell 44 inside, forming the hydraulic fluid 30 that fluid is coupled, power is passed to the turbine 46 of torque converter 14 via the fluid coupling from shell 44.More particularly, the fin that is positioned at shell 44 inboards of rotation makes hydraulic fluid enter the blade of turbine 46 in hydraulic fluid 30, thereby causes turbine 46 rotations.Power is delivered to input shaft 48 from turbine, and input shaft 48 passes to power the ring gear 50 of simple planetary group 16 again via wheel hub 52.

Ring gear 50 has the tooth of side formation within it, and the tooth of these tooth pinion mates 54, small gear 54 are mounted to around support 56 rotations.Small gear 54 also meshes sun gear 58.Support 56 is connected in parts 60, and gives parts 60 with transmission of power, and parts 60 also are formed up to the input end of clutch C2.

Input shaft 48 also is connected on the input end 62 of clutch C1 via wheel hub 52.Clutch C1 has five clutch plate 64, by means of by allowing that the hydraulic fluid that enters volume 70 overcomes the piston 66 that the effect of pressure spring 68 drives, can make clutch plate 64 form to drive and engage.When hydraulic fluid 30 entered volume 70, piston 66 left wheel hub 52, made volume 70 expand.This motion of piston 66 makes the outward edge 72 clamping clutch plate 64 of piston 66 form driving engagement.

Piston 66 is balanced by centrifugal action by the hydraulic fluid in the chamber 74, and this hydraulic fluid has prevented the self-acting (self-apply) that piston 66 is produced owing to hydraulic fluid 30 outwards drives when clutch C1 quickens rotation.Because chamber 74 has the outside degree similar with volume 70, offset so act on the centrifugal force that the effect of the centrifugal force of hydraulic fluid 30 is applied the hydraulic fluid in chamber 74 widely.Each other clutch C2 and C3 also have similar centrifugal balanced action piston.

Clutch plate 64 is attached to parts 76, and gives these parts 76 with transmission of power, and parts 76 pass to axle 78 with power via spline 80 again.Axle 78 passes to the short and small gear 84 that carries Ravigneux formula planetary gear set 18 and the support 82 of long small gear 86 via spline 88 with rotation.

Clutch C2 has six clutch plate 90, and piston 92 overcomes the motion of pressure spring 94 when allowing that hydraulic fluid 30 enters volume 96, can make clutch plate 90 form to drive and engage.Clutch plate 90 is attached to parts 98, and gives these parts 98 with transmission of power, and parts 98 pass to axle 99 with power via spline 100 again.Axle 99 is given transmission of power the sun gear 102 that advances of Ravigneux formula planetary gear set 18.

Parts 60 also are formed up to the input end of clutch C2, and are connected in five clutch plate 104 of C3, give this five clutch plate 104 with transmission of power.Under piston 108 is entering the effect of hydraulic fluid of volume 112, overcome the effect of pressure spring 110 and when mobile, can make clutch plate 104 under the power effect of piston 108, drive the output terminal 106 of engaging clutch C3.By means of clamping strap B1, the output terminal 106 of clutch C3 can be with respect to bell housing 12 transfixions.Output terminal 106 also is connected in the reverse gear sun gear 114 of Ravigneux formula planetary gear set 18 via spline 116.

Clamping strap B1 has the snap action piston 117 that is positioned at bigger power piston 119, and piston 117 has integral type position transducer 120, the position of push rod 122 during the position transducer 120 perception gear shift, and degree of accuracy is 0.1mm.

The reverse gear sun gear 114 and the sun gear 102 that advances all drive with long small gear 86 and engage, and the sun gear 102 that advances drives with long small gear 86 via short and small gear 84 and engages.Long small gear and ring gear 118 engagements, ring gear 118 is the output shaft 24 of drive transmission 10 again.Short and small gear 84 and long small gear 86 are kept by overrunning clutch 20 with respect to bell housing 12 around the support 82 of its rotation.Particularly, the inclined wedge type overrunning clutch only allows support 82 to rotate on a direction with respect to bell housing 12.By clamping strap B2, support 82 also can from respect to bell housing 12 on either direction rotation and keep motionless.

B2 clamping strap servomechanism 124 is connected in rear brake B2 via lever 126, and the piston 128 that lever 126 amplifies servomechanism 124 puts on the active force on the clamping strap B2.

Shown in the example of transmission device 10 in, overrunning clutch 20 is an inclined wedge type overrunning clutch 20.But in replacing example, inclined wedge type overrunning clutch 20 can be replaced by roller clutch, mechanical diode (mechanical diode) or the like.

The hydraulic part general introduction

Electrohydraulic control system 26 has suction line 200, and hydraulic fluid 30 is evacuated to the pump 36 by suction line 200, filter 32 from storage tank 28.Pump 36 is the Parachoidal type, and it is presented in the physical location between torque converter 14 and the simple planetary group 16 in the sectional view of transmission device 10.Pump 36 is driven by the shell 44 of torque converter 14, and pumping hydraulic fluid 30 is by the hydraulic line 202 to first order modulating valve 204, electromagnetism supply valve 206, pipeline safety valve 208 and manually operated valve 40 feeding pressurization hydraulic fluids.Change operation manually operated valve 40 in response to the position of shelves mode selector, this operation can be undertaken by the user of the vehicle that transmission device 10 is installed, for example by mobile T shape span mode selector, turn to pillar gear shift, lead drive controlling, push button selector or the like, just as the situation of concrete vehicle.

First order modulating valve 204 is regulated the pressure of the hydraulic fluid in the pipeline 202 by means of feedback line 210.When the pressure in the feedback line 210 increases, the piston 212 of first order modulating valve 204 overcomes by hydrodynamic pressure applied force in pressure spring 214 and the hydraulic line 202, (shown in Figure 1A) moves right, residual pressure is used for hydraulic fluid is fed into the controller of torque converter 14 along pipeline 216 like this, and is fed into the lubricating fitting of transmission device 10.If also there is residual pressure, then piston 212 is moved further, and makes residual pressure be dumped in the suction line 200.Feedback line 210 is provided with flow restriction restricting orifice or baffle plate 217, adjusts the size of restricting orifice or baffle plate 217, so that in response to the pressure of hydraulic fluid, first order modulating valve 204 is operated to desirable degree.

In whole hydraulic pressure pipe network 34, be provided with various discharge pipes 218, like this,, can discharge hydraulic fluid 30, get back to storage tank 28 with discharging by these discharge pipes 218.

Hydraulic fluid 30 is fed to action limit regulator 220 from first order modulating valve 204 by pipeline 222, and is fed to release limiting governor 224 by pipeline 216.Action limit regulator 220 has feedback line 226 (having flow restriction restricting orifice 227) and pressure spring 228, feedback line 226 is operated with the feedback system that is similar to aforementioned relevant first order modulating valve 204 with pressure spring 228, and the hydraulic fluid in the pipeline 230 is under the known pressure.Equally, discharge limiting governor 224 and have feedback line 232 (having flow restriction restricting orifice 233) and pressure spring 234, so that the hydraulic fluid in the pipeline 236 is under the known pressure.

Hydraulic fluid is fed to torque converter modulating valve 238 from action limit regulator 220 by pipeline 230.Hydraulic fluid is fed to torque converter modulating valve 238 (by pipeline tributary 240) from discharging limiting governor 224 by pipeline 236, also is fed to cooler/lubricant oil controlled adjuster 242 (by pipeline tributary 244).

Torque converter modulating valve 238 has piston 246, and piston 246 is operated in response to hydraulic fluid pressure in the hydraulic fluid pressure by pipeline 230 and 240 feedings, the power of hydraulic fluid pressure, pressure spring 252 by feedback line 248 and 250 feedings and the pipeline 254.Respond these inputs, hydraulic fluid with the ratio that changes along torque converter effect pipeline 256 and 258 feedings of torque converter discharge line.Hydraulic fluid by 256 feedings of torque converter effect pipeline makes hydraulic fluid flow through the inside of torque converter 14, this causes that torque converter enters lock state, at this lock state, the friction lock of turbine 46 locked clutches 47 (being arranged on torque converter shell 44 inside) on torque converter shell 44 antethecas 45.Otherwise, cause that by the hydraulic fluid of torque converter discharge line 258 feedings hydraulic fluid flows through the passage 260 between antetheca 45 and the lock-up clutch 47, to discharge lock-up clutch 47 from the frictional engagement on torque converter shell 44.

The hydraulic fluid that is fed to torque converter modulating valve 238 by pipeline 254 is supplied with by manually operated valve 40 from hydraulic line 202, along hydraulic driving pipeline 304, pass transducer shift valve 390, pipeline 264, be supplied to variable discharge solenoid valve (VBS) 262.Transducer shift valve 390 is via ON/OFF (O/I) solenoid valve 348 control, and ON/OFF (O/I) solenoid valve 348 provides flow of hydraulic fluid by solenoid valve supply valve 206.Solenoid valve supply valve 206 is provided with feedback line 284 (having flow limit restricting orifice 285) and pressure spring 286.Circuit 264 has the thimble filter 266 (for example being used for the filtering metal particle) that is used for hydraulic fluid, is used to reduce the flow restriction restricting orifice 268 of the pressure surge amplitude that is caused by pump 36 and further reduces pressure surge and prevent the storage tank 270 of liquid hammer.VBS262 is controlled by electronic control system, and in response to this electronic control system, VBS262 provides the control to the hydraulic fluid discharging, so that control the pressure of the hydraulic fluid in the pipeline 254 that is fed into torque converter modulating valve 238 as mentioned above.Thereby VBS262 is the lock pressure solenoid valve.VBS262 is normal low (NL) type, like this, does not supply at power under the situation of VBS262, and the output that is defaulted as hydraulic fluid is in the state of low pressure.Pressure-current curve diagram of NL VBS is provided in Figure 14.

Pipeline 202 is also along the pipeline 272 feeding hydraulic fluids that lead to VBS274, and VBS274 control hydraulic fluid is by the flow of pipeline 275.VBS274 is installed in series with thimble filter 276, flow restriction restricting orifice 278 and storage tank 280 to be similar to the layout of relevant VBS262 as mentioned above.Hydraulic fluid by pipeline 275 feedings is received by first order modulating valve 204, as further input, is used for the position of regulating piston 212.Thereby VBS274 is the line pressure control electromagnetic valve.VBS274 is normal high (NH) type, like this, does not supply at power under the situation of VBS274, and the output that is defaulted as hydraulic fluid is in the state of high pressure.Pressure-current curve diagram of NH VBS is provided in Figure 13.

The additional VBS282 that is provided shows with dotted line.Can expect that so additional VBS282 for example can be used for controlling the operation of the two ratio decoupling devices unit that uses with 6 ratio transmission combination of advancing, so that 7 ratios that advance altogether are provided.

Provide by pipeline 236 by cooler 38 and the flow of hydraulic fluid that is used for lubrication gear 10, perhaps by torque converter modulating valve 238 and pipeline 287, perhaps by pipeline tributary 244 and cooler/lubricant oil controlled adjuster 242.Pipeline 287 is provided with anti-discharging back valve 286, to allow hydraulic fluid along pipeline 287 one-way flow only.Pipeline 244 is divided into two pipeline tributaries 288 and 290, pipeline tributary 288 and 290 all feeding as the input of cooler/lubricant oil controlled adjuster 242.Hydraulic fluid pressure in these tributaries 288 and 290 and the hydraulic fluid pressure in the feedback line 296 are arranged the motion of the piston 294 of cooler/lubricant oil controlled adjuster 242 together, to determine the distribution by the hydraulic fluid of cooler pipeline 296 and cooler bypass line 298.Hydraulic fluid leaves cooler 38, pipe joint 300 again with cooler bypass line 298 in hydraulic fluid converge, from here, hydraulic fluid is given the parts of transmission device 10 as lubricant dispense along pipeline 302.

Each clutch C1, C2 and C3 are by the similar electrichydraulic control Equipment Control with ON/OFF (O/I) solenoid valve, and ON/OFF (O/I) solenoid valve is handled and is used to control the shift valve that hydraulic fluid flows to VBS.VBS control hydraulic fluid flows to clutch and regulating valve, and clutch and regulating valve is controlled hydraulic fluid again to the flowing of clutch plunger, with the engagement/disengagement clutch.

More particularly, the control of clutch C1 is by means of hydraulic fluid is fed into C1 shift valve 308 realizes along driving hydraulic line 304 and pipeline 306 by manually operated valve 40 (when manually operated valve 40 is in the drive pattern position) from hydraulic line 202.C1 shift valve 308 is by 310 operations of O/I solenoid valve, and O/I solenoid valve 310 receives 312 hydraulic fluids that flow into from electromagnetism supply valve 206 along pipeline.Pipeline 312 comprises the thimble filter 314 that just in time is positioned at O/I solenoid valve 310 upstreams.O/I solenoid valve 310 is normal low (NL) type, like this, does not supply with at power under the situation of O/I solenoid valve 310, is defaulted as low-pressure state, as shown in figure 15.The hydraulic fluid of C1 shift valve 308 control feeding VBS316, the output of VBS316 is fed into C1 modulating valve 318.The pipeline 320 that VBS316 is installed also is provided with thimble filter 322, storage tank 324 and is positioned at the restricting orifice 326,328 of VBS316 both sides.The piston 330 of C1 modulating valve 318 moves in response to the hydraulic fluid pressure in pipeline 320,332 and the feedback line 334.The output of C1 modulating valve 318 is fed into the volume 70 of clutch C1 by pipeline 336, so that mobile piston 66.VBS316 is the VBS of normal high type.

Clutch C2 is by the similar devices control that comprises O/I solenoid valve 338, C2 shift valve 340, VBS342 and C2 modulating valve 344, this Equipment Control hydraulic fluid via pipeline 346 to the flowing of volume 96, with the motion of control piston 92.VBS342 is the VBS of normal high type.

Clutch C3 is by the similar devices control that comprises O/I solenoid valve 348, C3 shift valve 350, VBS352 and C3 modulating valve 354, this Equipment Control hydraulic fluid via pipeline 356 to the flowing of volume 112, with the motion of control piston 108.VBS352 is the VBS of normal low type.

The preceding servomechanism 360 that is used for engage brake band B1 is also by being similar to the employed device control of clutch C1, C2 and C3.More particularly, this device comprises O/I solenoid valve 362, B1 shift valve 364, VBS366 and B1 modulating valve 368, this device control hydraulic fluid via pipeline 372 to the flowing of volume 370, with control piston 117 motion of (with push rod 122).VBS366 is the VBS of normal low type.

The back servomechanism 124 that is used for engage brake band B2 is also by being similar to the employed device control of clutch C1, C2, C3 and clamping strap B1.But the shared O/I solenoid valve 310 of B2 is with control B2 shift valve 392.In addition, B2 also utilizes VBS352, VBS352 control hydraulic fluid via pipeline 378 to the flowing of volume 128 and 394, with the motion of control piston 396.

When transmission device 10 was positioned at reverse gear, back servomechanism 124 was handled by means of the hydraulic fluid by reverse gear hydraulic line 374 and pipeline 376 and 378 feedings.One ball check valve 380 is arranged on the end of pipeline 376,382 the backflow that is used to prevent not expect from pipeline 376 to pipeline, or vice versa.

In an example shown, manually operated valve 40 has four valve motor pattern positions (that is, P (parking), R (reverse gear), N (neutral gear) and D (driving)).Manually operated valve also can be constructed with seven valve motor pattern positions (for example comprising shelves 4,2 and 1).Certainly, be to be further appreciated that manually operated valve can also have the valve motor pattern position of varying number (that is, except 4 or 7).

So, in described transmission device, hydraulic control system has four ON/OFF (O/I), 310,338,348,362 and six variable discharge solenoid valves of solenoid valve (VBS) 262,274,316,342,352,366 (adding the additional VBS282 that is advised).Should be appreciated that all these solenoid valves can replace with the solenoid valve type with identical functions, for example pulse duration modulation type (PWM), variable pressure/variable force type (VPS/VFS), discharge solenoid valve (bleed solenoids) or the like.

Each friction element in these transmission device 10 structures, can be clutch C1, C2 or C3 or clamping strap B1 or B2, during gear shift, can carry out electrichydraulic control individually, thereby for calibration/Application Engineer provides the full scale control of shift quality, and wearing and tearing or leakage that control system itself can be produced with the life period of transmission device 10 are regulated.Because control system all has full scale control to any friction element, so, when transmission device 10 is in driving or reverse gear, also can realize neutral state, for example, when vehicle stops at the traffic signals place, and/or when vehicle arrival is scheduled to than low speed (for example, when vehicle is about to stop).Because during long-time idle running, when for example congested in traffic, transmission device 10 loads motor and/or torque converter, so this has improved fuel economy.Should " neutral gear in the driving (Neutral-in-Drive) " feature under the ignorant situation of driver, occur.

Control system is made of key feature, when joint or holdback clutch C1, C2 and C3 and clamping strap B1 and B2, described key feature allows to adopt various controlling methods by means of the ability (not being exposed under the hydrodynamic pressure by making VBS) of untapped bypass VBS, control system can reduce the pressure leakage of hydraulic fluid, thereby can reduce fuel consumption.Line pressure can be controlled under any degree in the structural limits via VBS274, therefore also can be used as clutch/clamping strap Engagement Control or implement misuse protection.The line pressure system is the pipeline priority system, and it maintains line pressure under the low oil condition, sacrifices the demand as other loop of cooler flow, to keep this pressure.Though shown pump 36 is the Parachoidal type,, this pump 36 can replace with other any suitable pump, for example Gerotor pump (Cierotor), crescent pump (Crescent) or vane pump.

The torque converter locked loop that comprises action limit regulator 220, release limiting governor 224, torque converter modulating valve 238 and lock pressure adjuster solenoid valve 262 is designed to, realization is slided thereby allow lock-up clutch 47 to lean against on torque converter shell 44 antethecas 45 controllably to the control of the pressure of the both sides of lock-up clutch 47.

Torque converter modulating valve 238 has particular structure, and this structure has two feedback areas 248, one of 250-is used to exert pressure, and one is used for release pressure.Torque converter modulating valve 238 and size thereof design by this way, make valve 238 always can realize that between these two loops certain pressure is poor.In order successfully to control this two pressure, torque converter modulating valve 238 needs a kind of known supply pressure source.This by with two independent regulators, be action limit regulator 220 and discharge limiting governor 224 feeding torque converter modulating valve 238 and realize.These two regulators 220,224 are set to a fixation pressure, and this fixation pressure can be pre-conditioned to the source oil of torque converter modulating valve 238.According to the 3rd input that is input to torque converter modulating valve 238 from lock pressure adjuster VBS262, torque converter modulating valve 238 will act on or discharge lock-up clutch 47, keep the predetermined pressure difference on the lock-up clutch 47 simultaneously.

Lubricating loop is designed to, if get clogged at low temperature run duration cooler 38 very, is restricted if perhaps flow, and lubricant oil can bypass cooler 38, directly flows in the distribution of lubrication oil pipeline 302.

Transmission device 10 also is equipped with drive shaft speed sensor and output shaft speed sensor.Input speed sensor provides rate signal, and output speed sensor provides rate signal and sense of rotation signal.This sense of rotation is very important to some clutch and band effect strategy, especially in direction of vehicle movement to maximum under the very important situation that neutral gear drives or the neutral gear reverse gear is selected of effective gear shift control.The combination of these two velocity transducers can be slided to diagnose and be carried out closed loop or ADAPTIVE CONTROL with transmission device.

Oil hydraulic circuit 26 is arranged to, lose fully under the situation of electric power at transmission device solenoid valve (being O/I solenoid valve and VBS), transmission device 10 still can maintain parking, reverse gear, neutral gear and driving (the 4'sth) state, keeps cooler flow, largest tube linear pressure and lubrication flow simultaneously.

The operation of transmission device

The operation of transmission device under various shelves states (comprising first grade and manual first grade, reverse gear and neutral gear) is described below.

1. first grade

Aspect hydraulic pressure, operator's at first mobile T shape bar or pillar gear shift or other grade pattern direction instruction mechanism make first grade to be engaged to activation point.So this makes the manually operated valve 40 in the transmission device 10 move to activation point; This motion can utilize lever, cable, actuator or solenoid valve to carry out.In case be in activation point, manually operated valve 40 just allows oil to flow to the associated drives loop of valve body and pump cover, thus by hydraulic pressure to clutch and clamping strap shift valve energize.These shift valves are electrichydraulic control, and up to the instruction of receiving electronic control unit, these shift valves just allow oil pressure to enter clutch or clamping strap bond loop.In case these valves are pressurized, to stir (toggle) (utilizing O/I solenoid valve 338, VBS, PWM etc.), can carry out neutral gear-driving (N-D) gear shift by electric liquid instruction C2 shift valve 340 to allowing oil pressure and flow to be fed into the position in modulating valve loop by this C2 shift valve 340.Simultaneously, oil is fed into modulating valve electromagnetic pressure control valve (it can be PWM, VFS, VPS, VBS342 etc.).Now can be by utilizing modulating valve 344 and, carrying out clutch in conjunction with rising (ramp on) C2 clutch on the electromagnetic pressure control valve electricity liquid slope.Thereby the shift feel of N-D gear shift (shift feel) can be controlled by electronic controller, and can suitable/calibration import to mate various vehicle-states and to drive.If started misuse protection (abuseprotection) software algorithm, the misuse protection also can be supplied with the effect that protection drives pipeline of playing by the energy of cut-off clutch.When shift valve was handled, to each electromagnetic pressure control valve feeding oil, permission was used the limit leakage relevant with the solenoid valve of these types under the state of solenoid valve only needing by only.When not needing solenoid valve, oil can not be fed into solenoid valve, so, not requiring that oil hydraulic circuit has leakage, it is best that the pump size can reach, thereby bring maximum fuel Economy benefit.As the replacement controlling method that is used to engage the C2 clutch; clutch and regulating valve 344 can be set in maximum pressure during the N-D process; yet; this can cause ear-piercing shifting shock usually; for alleviating this problem; the slope changes line pressure or source oil (source oil) can to use line pressure control electromagnetic valve 274 to come lentamente, thereby forms smooth engagement.

First grade kinetic current (power flow) schematic representation is in Fig. 5.

Mechanically, produce input, and pass through the front reduction gear gear train of planetary gear set 16 forms from torque converter 14.Clutch C2 is engaged, and planetary gear set 18 provides input backward, and kinetic current leads to 1-2 inclined wedge type overrunning clutch 20, and like this, the support reaction torque is accepted by overrunning clutch 20.Vehicle do not have engine braking, so can slide.

More particularly, when quickening, have only overrunning clutch 20 to be used for support is upward kept static in opposite direction (promptly opposite with hand engine rotation).At sliding state, overrunning clutch 20 can not remain on postive direction with support, and therefore, kinetic current can not continue, can not brake engine.

In torque converter 14, do not provide mechanical caging by lock-up clutch 47, this just electrohydraulic control system 26 prevented.For this device, can find out that a friction element (C2) that only utilizes the hydraulic piston 66 by electrichydraulic control to engage just can be realized first grade.Although be called 1-2 inclined wedge type overrunning clutch, there is the people of relevant knowledge to determine, this same function can realize with similar device, roller clutch for example, mechanical diode or the like.

2. manual first grade

Manual first grade kinetic current schematic representation is in Fig. 6, and diagrammatic sketch has shown the kinetic current during sliding, and another diagrammatic sketch has shown the kinetic current during driving.

Manual first grade is similar to first grade, and difference is, has also used the B2 clamping strap, and like this, overrunning clutch 20 can not prevent that transmission device is input to the braking of transmission device output.Therefore, can implement engine braking at manual first grade.

More particularly, at manual first grade, use B2 clamping strap and overrunning clutch 20 to prevent that the support of planetary gear set is in (promptly opposite with hand engine rotation) rotation in the other direction.Because the B2 clamping strap does not have support is not remained on ability under the high-acceleration (promptly during the drive condition), overrunning clutch 20 and B2 clamping strap are shared the moment of torsion that applies jointly via support.On the contrary, during the sliding state, opposite situation takes place, its medium-height trestle attempt so compare with drive condition, applies moment of torsion in the postive direction spin in the opposite direction.According to qualification, overrunning clutch 20 can only prevent rotation in one direction, thereby support is only kept by the B2 clamping strap.Because support is static, kinetic current continues to flow to motor by gear train, like this, provides the braking to motor.

Particularly under drive condition, this is good, for example, if when the vehicle that transmission device is installed turns round and/or goes down the hill to advance, wish brake engine.The control of transmission device can be arranged to, and manually selects manual first grade by the automatic selection of control system and/or by the driver.For example, in one form, transmission device has can be at the selector that moves between (for example " driving ") pattern and the manual mode automatically.At automatic mode, when first ratio is suitable, select first grade automatically.At manual mode, the driver manually selects gear shift by the motion of selector, uses manual first grade when the driver selects first ratio.

At manual first grade, produce input from torque converter 14, and by front reduction gear gear train 16.Clutch C2 is switched on, and gear train 18 provides input backward.Therefore clamping strap B2 lock bracket assembly 82, and accept reaction, only utilizes the clutch and the B2 clamping strap that are bonded with each other that engine braking just is provided at manual first grade.Do not provide mechanical caging by lock-up clutch 47 in torque converter 14, electrohydraulic control system 26 has the check valve (override valve) that prevents to lock generation.

Aspect hydraulic pressure, the loop is identical with first grade, and difference is that the B2 clamping strap also is that electric liquid engages, and can rise or slope decline on the slope at joint or during throwing off.In case transmission device 10 shifts into second grade, first grade of bias valve 349 just touches and makes B2 loop (via pipeline 347) lose fuel feeding, thereby prevents that the B2 clamping strap from stopping (staying on) and causing tightening up (tie-up).

3. second grade

Second grade kinetic current schematic representation is in Fig. 7.

By keeping clutch C2 to be in the state of energy of first grade of state supply and, can realizing second grade by engage brake band B1.This locking reverse gear sun gear 102 and bracket component 82, thus make back planetary gear set 18 overspeed operation 1-2 machinery inclined wedge type overrunning clutch 20.In torque converter 14, provide mechanical caging by lock-up clutch 47.This lock-up clutch 47 is equipped with damper assembly usually, and with the vibration that buffering is caused by motor, lock-up clutch 47 can also adopt the slip of control pressure reduction, to alleviate torsional vibration further.Control by means of torque converter modulating valve 238 combination limiting governors 220 and 224 pairs of lock-up clutch 47 pressure at both sides of release limiting governor can realize controlling the slip of pressure reduction.This allows to control exactly the joint of lock-up clutch 47 on shell 44 antethecas 45 of torque converter 14.Compare with the legacy system that damper is only arranged, the engine speed when this causes introducing locking reduces, thereby makes the fuel economy benefit reach maximum.This is applicable to all grades state that locking is activated.

Can be installed in series together with the damper of different ratios by making lock-up clutch 47, multistage (for example three grades) damping is provided, like this, the displacement of damper is classified to resist applied force/moment of torsion, as shown in figure 16.This multistage damper can improve the inhibition to the vibration in the certain frequency scope.

Aspect hydraulic pressure, when gear shift began, line pressure was increased to and is higher than the required degree of gear shift.Then, relevant B1 shift valve 364 is driven by electric liquid, and up to the instruction of receiving electronic control unit, shift valve 364 just allows oil pressure to enter B1 clamping strap bond loop (promptly arriving B1 modulating valve 368).In case this valve 364 has been supplied to energy, oil promptly is fed into B1 modulating valve 368 and VBS366, and the pressure that can increase in the B1 band apply piston loop by electric liquid instruction B1 modulating valve electromagnetic pressure control valve 366 is carried out the 1-2 gear shift.Now can be by utilizing modulating valve 368 and, carrying out B1 and engage in conjunction with rising the B1 clamping strap on the electromagnetic pressure control valve electricity liquid slope.Thereby the shift feel of 1-2 gear shift can be controlled by electronic controller, and can adapt to/calibrate to mate various vehicle-states and to drive input.

As the additional input that inputs to electronic controller, band push rod position transducer 120 is included in preceding servomechanism push rod and the lid.This sensor 120 provides the engagement positio of clamping strap B1 to controller, so that can use different controlling methods.These controlling methods can comprise, carry out control action at a slow speed after fast Absorption (uptake) the clamping strap B1 gap, or throw off fast after moment of torsion reduces at a slow speed.If started misuse protection software algorithm, the misuse protection is also supplied with the effect that protection drives pipeline of playing by the energy that disconnects clamping strap.

4. third gear

The kinetic current schematic representation of third gear is in Fig. 8.

Third gear realizes by engaging clutch C2 and C3.This is locked in backgear group 18 1: 1 ratio.So total transmission output is than the ratio that equals nipper wheels 16.In torque converter 14, provide mechanical caging by lock-up clutch 47.

Aspect hydraulic pressure, when gear shift began, line pressure was increased to and is higher than the required degree of gear shift.Then, relevant C3 shift valve 350 is driven by electric liquid, and up to the instruction of receiving electronic control unit, shift valve 350 just allows oil pressure to enter the C3 bond loop.In case this valve 350 has been supplied to energy, oil promptly is supplied to C3 modulating valve 354 and VBS352, the pressure that can reduce in the B1 band apply piston loop by electric liquid instruction B1 modulating valve electromagnetic pressure control valve 366, and instruct C3 modulating valve electromagnetic pressure control valve 352 slope unlifting pressures simultaneously, be actually B1 loop and C3 loop are exchanged, carry out the 2-3 gear shift.In case the B1 loop has lost the moment of torsion bearing capacity, the C3 loop just can rise the C3 clutch and finishes gear shift by utilizing modulating valve 354 and finishing in conjunction with electromagnetic pressure control valve 352 electric liquid on the slope.Thereby the shift feel of 2-3 gear shift can be controlled by electronic controller, and can suitable/calibration import to mate various vehicle-states and to drive.

5. fourth speed

The kinetic current schematic representation of fourth speed is in Fig. 9.

Fourth speed is realized by making two inputs to backgear group 18.An input is from front reduction gear gear train 16 and clutch C2, and another is imported directly from input shaft 48 (via clutch C1).The C1 clutch is attached to the bracket component 82 of backgear group 18 on the input shaft 48, simultaneously, and sun gear 102 before the output of nipper wheels 16 drives by the C2 clutch.In torque converter 14, provide mechanical caging by lock-up clutch 47.

Aspect hydraulic pressure, the 3-4 gear shift is implemented in the mode identical with the 2-3 gear shift, and different is that slope, C3 loop descends, and rises on the slope, C1 loop.

6. the 5th grade

The 5th grade kinetic current schematic representation is in Figure 10.

The 5th grade by realizing two inputs to backgear group 18.An input is from front reduction gear gear train 16, and another is imported directly from input shaft 48 (via clutch C1).The C1 clutch is attached to the bracket component 82 of backgear group 18 on the input shaft 48, and simultaneously, the output of nipper wheels 16 drives reverse gear sun gear 114 by the C3 clutch.In torque converter 14, provide mechanical caging by lock-up clutch.

Aspect hydraulic pressure, the 4-5 gear shift is implemented in the mode identical with the 3-4 gear shift, and different is that slope, C2 loop descends, and rises on the slope, C3 loop.

7. the 6th grade

The 6th grade kinetic current schematic representation is in Figure 11.

By utilizing the B1 clamping strap that reverse gear sun gear 114 is locked onto on the gear mechanism housing 12, directly be urged to gear train bracket component 82 with the C1 clutch then from input shaft 48, realize the 6th grade.In torque converter 14, provide mechanical caging by lock-up clutch 47.

Aspect hydraulic pressure, the 5-6 gear shift is implemented in the mode identical with the 4-5 gear shift, and different is that slope, C3 loop descends, and rises on the slope, B1 loop.

8. reverse gear

Realize reverse gear, drive nipper wheels 16 by the C3 clutch, and by utilizing the B2 clamping strap that backgear pack support assembly 82 is locked onto on the gear mechanism housing 12.In torque converter, do not provide mechanical caging, but on hydraulic pressure, prevent mechanical caging via the electrichydraulic control loop by lock-up clutch 47.

Aspect hydraulic pressure, operator's at first mobile T shape bar or pillar gear shift or other grade pattern direction instruction mechanism engage reverse gear to car backing position.So this makes the manually operated valve 40 in the transmission device 10 move to car backing position; This motion can utilize lever, cable, actuator or solenoid valve to carry out.In case be positioned at car backing position, manually operated valve 40 just allows oil to flow to the relevant reversing loop of valve body and pump cover, thus with hydraulic pressure to clutch and clamping strap shift valve energize.Basically and then manually operated valve 40 is selected car backing position, just to B2 clamping strap energize.Its effect ratio can utilize line pressure to control, but the bias valve 349 that is used to drive purposes when reverse gear by bypass.In case the B2 clamping strap is connected, by electric liquid instruction C3 shift valve 350 to stir (utilizing O/I348, VBS, PWM etc.) to allowing oil pressure and flow to be fed into modulating valve loop (that is) position, to C3 modulating valve 354, engaging clutch C3 by it.Simultaneously, oil is fed into modulating valve electromagnetic pressure control valve (it can be PWM, VFS, VPS, VBS352 etc.).Now can be by utilizing modulating valve 354 and, carrying out clutch in conjunction with rising the C3 clutch on the electromagnetic pressure control valve 352 electric liquid slopes.Thereby the shift feel of N-R gear shift can be controlled by electronic controller, and can adapt to/calibrate to mate various vehicle-states and to drive input.If started misuse protection software algorithm, the misuse protection is also supplied with the effect that protection drives pipeline of playing by the energy of cut-off clutch.When shift valve was driven, to each electromagnetic pressure control valve feeding oil, permission was used the limit leakage relevant with the solenoid valve of these types under the state of solenoid valve only needing by only.When not needing solenoid valve 352, oil can not be fed into solenoid valve 352, so, not requiring that oil hydraulic circuit has leakage, it is best that the pump size can reach, thereby bring maximum fuel Economy benefit.As the replacement controlling method that is used to engage the C3 clutch, clutch and regulating valve 354 can be set in maximum pressure during the N-R process.Yet this can cause ear-piercing shifting shock usually, and for alleviating this problem, the slope changes line pressure or source oil can to use line pressure control electromagnetic valve 274 to come lentamente, thereby forms smooth engagement.

9. neutral gear

By throwing off whole three clutch C1, C2 and C3 and throwing off clamping strap B1 and B2, can realize the neutral state of transmission device 10.Therefore, neutral state is non-braking neutral gear, and wherein, the input and output of transmission device rotate freely with respect to drive housing.

Technological progress

Developed 6 ratios that advance (i.e. " 6 speed ") transmission device, it can utilize the existing production line that has been used to make 4 ratios that advance (i.e. " 4 speed ") transmission device to make, and can same production line simultaneously and 4 fast transmission devices make together.Original 4 fast transmission components and instrument above 70% also are used to 6 fast transmission devices, like this, can make 4 speed and the common basic modules of 6 fast modification.Basic module for example can comprise drive housing and/or be used for the inserting member of drive housing.Different parts can add in the basic module, make these modification in view of the above.

The design procedure that existing 4 fast automatic transmissions is converted to 6 ratio transmission devices that advance of coupling comprises: remove a friction element from the structure of 4 fast transmission devices; The friction element that provides planetary gear set to replace this to remove; With control system is provided, with operation residue friction element independently of one another.

6 fast automatic transmissions are configured to, and make mechanical hardware (comprising additional planetary gear set) to be omitted, so that the automatic transmission with 4 ratios that advance is provided.

Characteristics

The characteristics of the transmission device 10 in the above-mentioned example are as follows:

Single input shaft drive transmission;

Complete neutral gear function when neutral gear (not braking neutral gear);

Use 3 clutches, 2 clamping straps and 1 overrunning clutch to realize 6 ratios that advance;

Utilize 17 valves to realize whole electrichydraulic control of transmission device;

In torque converter, comprise lock-up clutch;

By only engaging a friction element, can realize first ratio;

Utilize each solenoid valve combination, can realize the control from the zero pressure to the maximum pressure respectively all friction clutches and clamping strap;

Utilized non-connection friction element (that is, not having common pressure or hydraulic pressure zone between the element);

Utilize drive shaft speed sensor to carry out control decision;

Utilize quadrature (quadrature) output speed sensor to carry out control decision;

Clamping strap push rod position transducer carries out control decision before utilizing simulation;

Utilize the control of direct clutch and clamping strap, can realize misuse protection the vehicle traction pipeline;

Utilize the control of direct clutch and clamping strap, can realize from neutral gear to the forward gears state and the smooth engagement of reverse gear state by electrichydraulic control;

Supportingly 6 ratio transmission device hardware that advance are installed in the former manufacturing bag space range by 4 ratio transmission devices that advance allowing;

Still utilize 6 ratio control gear that advance, mechanically be associated (hook up) allows and can carry out the manufacturing of 4 ratio transmission devices that advance by omitting mechanical hardware;

Utilize existing fabrication tool and facility, mechanically being associated allows to make 6 ratio transmission devices that advance;

Utilize the closed loop and the ADAPTIVE CONTROL of combination to guarantee smooth shifting control;

Utilization is to the pressure reduction electrichydraulic control of the lock-up clutch in the torque converter, allow to use the Sliding Control strategy, to realize lower locking engine speed and to reduce NVH (ear-piercing vibrating noise) when second grade, third gear, fourth speed, the 5th grade and the 6th grade;

Utilized the full scale variable pressure control that is independent of other transfer function;

Under the situation of electronic failure, hydraulic control system still can realize stopping, " soft returning (limp-home) " of reverse gear, neutral gear and driving fourth speed;

The torque converter locking takes place in hydraulic control system when preventing in parking, neutral gear, first grade of driving and reverse gear aspect the hydraulic pressure;

Hydraulic control system has the cooler that prevents transmission device and blocks or icing cooler bypass circulation;

Utilized metering pump;

In preceding brake-band piston assembly, utilized the snap action feature;

Utilized the preferential force feed of supplying with from pump of pipeline;

Utilize the combination of ON/OFF solenoid valve, variable discharge magnetic coil, shift valve and pressure regulator valve, realize the control of electric fluid clutch and clamping strap;

When not needing solenoid valve, control valve unit disconnects solenoid valve, and it is minimum that solenoid valve is leaked;

Modular design can comprise driving tube wire system modification, for example, and 4 speed, 5 speed, 6 speed, 7 speed, mixed drive and front-wheel drive.

Mix

It will be appreciated by those skilled in the art that according to transmission device of the present invention can be used for hybrid drive equally device for example shown in Figure 17.For example, transmission device can be provided with another upstream planetary gear group 401, and this upstream planetary gear group 401 is coupled in transmission device on internal-combustion engine (not shown) and the motor 400.

Under the situation that does not deviate from the spirit and scope of the present invention, can carry out many modifications and modification to transmission device.For example, transmission device can be provided with electric oil pump, described electric oil pump is independent of the input speed of transmission device and moves, so that oil pressure (i.e. " request pressure ") is provided as required, especially can not provide under the environment of sufficient pressurising force (for example, when the vehicle that this transmission device is installed is slowly advanced or stopped) at the mechanical oil pump of transmission device.

Claims (26)

1. many ratios automatic transmission that is used for vehicle, this transmission device has: at least one planetary gear set; A plurality of friction elements are used for the parts of the planetary gear set between the input and output of coupling transmission device under different conditions, so that realize a plurality of velocity ratios; And control system, be used for different combinations engagement/disengagement friction element selectively, to implement the selection of velocity ratio, wherein, the control of the joint of one or more friction elements and/or the situation of disengagement is independent of each other friction element;

It is characterized in that, each ratio is corresponding at least one discrete shelves state of transmission device, at at least one grade state, drive kinetic current and be conducted through the overrunning clutch that is arranged to only transmit in one direction driving, make the rotation of overrunning clutch prevent that transmission device from providing from being input to the braking of output, at other grade state, this clutch is by bypass, to allow from being input to the braking of output, and when transmission device was positioned at described at least one grade state, transmission device only had a friction element to be engaged.

2. transmission device as claimed in claim 1, wherein, described control system comprises the electrohydraulic system with a plurality of electromagnetic control valves.

3. transmission device as claimed in claim 2, wherein, one or more friction elements are controlled by special-purpose electromagnetic control valve.

4. transmission device as claimed in claim 2, wherein said control system carry out the full scale control separately of each friction element.

5. transmission device as claimed in claim 2, wherein, when vehicle predetermined than low speed or be lower than predetermined when advancing than low speed, by the selection operation electromagnetic control valve to throw off one or more friction elements, neutral state in the driving of automatic enforcement transmission device, thus, transmission device output is thrown off from the driving of transmission device input.

6. transmission device as claimed in claim 2, wherein said transmission device has isolation mounting, when not using under arbitrary given state of one or more electromagnetic control valves at transmission device, described isolation mounting is isolated one or more electromagnetic control valves makes described one or more electromagnetic control valve not be exposed to hydrodynamic pressure.

7. transmission device as claimed in claim 6, wherein control gear can be isolated described one or more electromagnetic control valve by isolation mounting.

8. transmission device as claimed in claim 5, wherein, the neutral state in the described driving is not for braking neutral state, and wherein, the input and output of transmission device all rotate freely with respect to drive housing.

9. transmission device as claimed in claim 1, wherein, at shelves state except described at least one grade state, overrunning clutch by bypass to allow from being input to the braking of output.

10. transmission device as claimed in claim 9, wherein, this transmission device has a shelves state to fixed-ratio, wherein allows from being input to the braking of output; And another that described at least one grade state is a same ratio replaced the shelves state, and wherein overrunning clutch can be operated the braking that is used for preventing to be input to from transmission device transmission device output.

11. transmission device as claimed in claim 10, wherein, described is the minimum ratio that advances that transmission device provides to fixed-ratio.

12. transmission device as claimed in claim 10, wherein, this transmission device has: automatic mode, the variation of selection ratio automatically under this automatic mode; And manual mode, the manually variation of selection ratio under this manual mode, wherein, described shelves state is used for reaching the described fixed-ratio of giving at manual mode, and described replacement shelves state is used for reaching the described fixed-ratio of giving at automatic mode.

13. transmission device as claimed in claim 1, wherein, overrunning clutch is the inclined wedge type overrunning clutch.

14. transmission device as claimed in claim 1, wherein, transmission device has at least two planetary gear set, and a plurality of friction elements are operated the parts with the planetary gear set of connecting between being coupling in input and exporting under different conditions, so that realize a plurality of velocity ratios.

15. transmission device as claimed in claim 1, wherein, each friction element all can be independent of other friction element operation.

16. the arbitrary described transmission device of claim as described above, wherein, transmission device has 6 ratios that advance, and whole 6 controls of advancing between the ratio are implemented by the engagement/disengagement of 5 friction elements.

17. transmission device as claimed in claim 16, wherein, described 5 friction elements comprise 3 friction clutches and 2 clamping straps.

18. transmission device as claimed in claim 17, wherein, transmission device has first, second and the three-clutch and first and second clamping straps, and wherein, when first grade of state at first ratio, second clutch is engaged, second clamping strap is engaged, other friction element, promptly first clutch, three-clutch and first clamping strap are thrown off.

19. transmission device as claimed in claim 18, wherein, at another replacement shelves state of first ratio, second clutch is engaged, other friction element, and promptly first clutch, three-clutch, first clamping strap and second clamping strap are thrown off.

20. transmission device as claimed in claim 19, wherein, for second ratio of transmission device, second clutch is engaged, and first clamping strap is engaged, other friction element, and promptly first clutch, three-clutch and second clamping strap are thrown off.

21. transmission device as claimed in claim 20, wherein, for the 3rd ratio of transmission device, second and three-clutch be engaged, other friction element, promptly first clutch, first clamping strap and second clamping strap are thrown off.

22. transmission device as claimed in claim 21, wherein, for the 4th ratio of transmission device, first and second clutches are engaged, other friction element, i.e. and three-clutch, first clamping strap and second clamping strap are thrown off.

23. transmission device as claimed in claim 22, wherein, for the 5th ratio of transmission device, first and three-clutch be engaged, other friction element, promptly second clutch, first clamping strap and second clamping strap are thrown off.

24. transmission device as claimed in claim 23, wherein, for the 6th ratio of transmission device, first clutch is engaged, and first clamping strap is engaged, other friction element, and promptly second clutch, three-clutch and second clamping strap are thrown off.

25. transmission device as claimed in claim 24, wherein, for the reverse gear ratio of transmission device, three-clutch is engaged, and second clamping strap is engaged, other friction element, and promptly first clutch, second clutch and first clamping strap are thrown off.

26. transmission device as claimed in claim 25, wherein, for the selected neutral state of transmission device, the neither one friction element is engaged.

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