CN101253351A

CN101253351A - Dual hydraulic machine transmission

Info

Publication number: CN101253351A
Application number: CNA2006800213105A
Authority: CN
Inventors: K·E·格利斯曼; M·R·弗罗纳
Original assignee: TOWICK CO
Current assignee: TOWICK CO; Torvec Inc
Priority date: 2005-06-15
Filing date: 2006-06-15
Publication date: 2008-08-27
Also published as: WO2006138474A3; JP2008546959A; EP1890898A2; KR20080016861A; AU2006259387B2; WO2006138474A2; BRPI0611951A2; AU2006259315A1; KR100943016B1; JP2008546958A; WO2006138447A3; EP1891356A2; CA2609901A1; WO2006138447A2; CA2609902A1; CA2609901C; MX2007015507A; MX2007015941A; KR20080016862A; EP1891356A4

Abstract

The modular transmission uses only a pair of small and light hydraulic machines of remarkably improved volumetric efficiency with pistons having body portions substantially as long as the axial length of the respective cylinders in which they reciprocate. The two hydraulic machines operate in a closed loop, one being used as a pump driven by the vehicle's engine, and the other used as a motor. Each machine has a fully articulatable swash plate. By computer control, the angles of the swash plates of the two machines are infinitely varied to provide an appropriate optimum ratio of engine/wheel speed for all conditions from start-up, city driving, hill climbing varied according to load and steepness, and over-drive for highway. This complete vehicle operation is attained while the vehicle's engine continues to operate at relatively constant speeds and relatively low RPM.

Description

Dual hydraulic machine transmission

Quoting of related application

The application require on June 15th, 2005 application, name is called the preference of co-pending 11/153, No. 111 U.S. Patent application of " DUALHYDRAULIC MACHINE TRANSMISSION ".11/153, No. 111 U.S. Patent application name that to be on January 10th, 2006 grant patent to Gleasman etc. is called the part continuity patent application of 6,983, No. 680 U. S. Patents of " LONG-PISTONHYDRAULIC MACHINES ".6,983, No. 680 U. S. Patents are in the part continuity application that on August 25th, 2003 applied for, existing resigned name is called 10/647, No. 557 U.S. Patent application of " LONG-PISTON HYDRAULIC MACHINE ".10/647, No. 557 U.S. Patent application is in the part continuity parent patent application that on August 28th, 2002 applied for, existing resigned name is called 10/229, No. 407 U.S.'s parent patent application of " LONG-PISTONHYDRAULIC MACHINES ".By reference above-mentioned patent and patent application are incorporated in herein.

The application also require on June 15th, 2005 application, name is called the preference of 11/153, No. 112 co-pending U.S. Patent application of " ORBITALTRANSMISSION WITH GEARED OVERDRIVE ".By reference this application is incorporated in herein.

Technical field

The present invention relates to be used for the hydraulic transformer of vehicle movement and relate to the employed fluid hydraulic pump/motor of the automobile machine that is suitable for relative " heavy duty ".More specifically, the present invention is suitable for being used for the full hydraulic speed changer of automobile.

Background technique

The full hydraulic speed changer is a prior art.The name that licenses to Anderson in August 10 nineteen sixty-five is called in 3,199, No. 286 U. S. Patents of " HYDROSTATIC DRIVE ", and the modularization hydraulic transmission is used single-stage pump to drive free-standing motor each in four wheels stepless acceleration is provided.Hydraulic transmission comprises the control valve of each wheel place and small amount of liquid filling.The name that licenses to Hancock etc. on February 15th, 1975 be called " HYDROSTATIC VEHICLE TRANSMISSION " 3,641, in No. 765 U. S. Patents, the four-wheel hydrostatic transmissions has the one-way valve of special setting and allows the restricted bindiny mechanism of difference, and tractive force control is provided between the wheel shaft of front and back.

In order to strengthen the petrol engine vehicle performance and to reduce vehicle weight and manufacture cost, there is a kind of transmission demand in related domain, and this transmission allows to use and turns back to motor certified but the reduced loss of machine of torque that speed is quite low.Also there is a kind of transmission demand in related domain, and motor was with more constant speed running when this transmission allowed automobile to change speed.Though the speed changer that uses on most of automobiles needs motor to circulate between low speed and ultra high speed in accelerating process at present, when the motor constant speed was moved, motor was higher to the utilization efficiency of fuel oil.

The full hydraulic speed changer has used effectively on the heavy machinery of low cruise such as tractor and the Lightweight Vehicles such as golf ball light roadster and ATV (ATV).Although attempted the full hydraulic speed changer is used for automobile, the efficient of the hydraulic transformer of prior art is too low, makes them to be applied in the automobile.The existing hydraulic transformer that uses in the automobile amplified in proportion will produce too huge, heaviness and the very big speed changer of noise, and this speed changer is bigger, heavier, more noisy than the speed changer that is used for automobile at present.

Although explosive motor is the industry standard that is used for american car, some main automakers are studying homogeneous charge compression-ignition (HCCI) motor.In traditional petrol engine, air-fuel oil mixture is by spark ignitor, thereby power is provided.In hcci engine, it is such to be similar to diesel engine, and a piston compresses air-fuel oil mixture, thereby increases its temperature till air-fuel oil mixture is lighted.According to estimates, hcci engine can improve 30% oil inflame efficient than normal benzine explosive motor.Yet, be to be difficult to control burning under low engine speed and two kinds of speed of high-engine rotating speed in the major obstacle that realizes the HCCI technology on the automobile.

Related domain needs a kind of like this speed changer: provide automobile runs necessary power, and allow its engine speed to remain in the narrow relatively low-medium speed scope simultaneously, the easier control of the burning of hcci engine like this.This speed changer allows to realize more having the hcci engine of fuel efficiency on the petrol power vehicle.

Oil hydraulic pump and motor also are well-known and widely used, and they are equipped with pistons reciprocating in corresponding cylinder, and each cylinder is formed in the cylinder block also circumferentially in about first radial distance of distance driving element rotatingshaft.Many this pump/motors have variable displacement capacity, and they are two kinds of basic designs commonly used.In the first basic design, piston is with respect to variable tilted but stationary swash plate, to-and-fro motion in the cylinder block of rotation.In the second basic design, piston is with respect to the swash plate of variable tilted and rotation, to-and-fro motion in fixing cylinder block, and swash plate usually is divided into and is included in " eccentric wheel " that do not rotate only nutating that slides on rotation and the nutating rotor surface.Although invention herein is suitable for this two kinds of designs, be more suitable in (and being described in this article) improvement a kind of type machine in back, in back one type machine, piston to-and-fro motion in the fixed air cylinder body.

The pump and the motor that use in the present invention and describe in this article are the fluid type hydraulic presses, and will be appreciated that employed term " fluid " and " pressurized fluid " are to be used for determining incompressible liquid rather than compressible gas herein in the whole text.Because liquid has incompressibility, so the pressure of these two kinds of dissimilar hydraulic presses is different fully with loading cycle, can't be used for the liquid-type machine to such an extent as to be used for the design of gas compression type machine, vice versa.Therefore, following note will all be interpreted as directly and be applicable to the fluid type hydraulic press, and mainly be applicable to those heavy-duty automotive application according to aforementioned content.

The hydraulic press that has a fixed air cylinder body can make than must support and protect the machine of heavy rotary cylinder body light, much smaller.Yet, these rotation of lighter machinery requirement and nutating swash plate assemblies, these assemblies are difficult to assembling and support.For the running of high pressure/high speed, the swash plate assembly must be supported, and its mode is that allow can relative movement between the matching surface of the head of rotary-piston not and rotation and nutating swash plate.This existing swash plate usually is divided into rotation/nutating rotor portion and nutating eccentric wheel part only, and the latter comprises by connecting " dog bone " the formula member and the close-fitting groove of head of rotary-piston not.

That is to say that this up to now fixed air cylinder body machine has used an end of " dog bone formula member " extension bar (that is the bar that, has two spheric ends) each piston that interconnects and nutating but non-rotary eccentric wheel.A spheric end of dog bone formula member pivotally is installed to the head of piston, but usually during whole relative movement between the groove of the head of rotary-piston not and nutating swash plate, another spheric end remains in the eccentric groove of swash plate always.Be well known in the art, these relative movement are moved along the non-circular path of continuous variation, and these paths produce in whole tilting position of the swash plate that leaves 0 degree.These dog bone formula members have greatly increased the complexity and the cost of the wobbler of making these light-duty machines.

The cylinder block of an end and rotation of each piston that dog bone formula member bar also is used for having (but and non-rotary) hydraulic press swash plate of inclination sometimes interconnects.Yet, more frequent situation is, the machine that the back is one type does not have this dog bone formula member, and has replaced using the piston of lengthening, and the piston of each lengthening at one end (the traditional hoof block element that is assembled by pivot usually covers once more) has the ballhead that effectively touches the nonrotational plane of swash plate.So design the piston of this lengthening, even so that also keep supporting the major component of the axial cylindrical body of each piston in the All Time during the piston maximum stroke by the respective cylinder wall of piston.The purpose of this additional support for lengthened piston is at piston during around their cylinder block rotation, guarantees to slip over inclination but the minimum lateral displacement of each spherical piston head during non-rotary swash plate when each spherical piston head.

Usually, these lengthened pistons mainly are lubricated by " seepage ", when promptly driving when pistons reciprocating driving high-pressure liquid or by high-pressure liquid, are forced to the high-pressure liquid part between the outer circumference of each cylinder wall and each piston body.Have only when allowable limit allows enough fluid between the elongated cylinder of cylinder wall and piston, it is lubricated that this seepage just provides, and the seepage of sufficient to guarantee good lubrication often has a negative impact to the volumetric efficiency of pump or motor machine.For example, 10 cubic inches machine can use similar 4 gallons fluid for the seepage per minute.When the littler allowable limit of frequent use reduced seepage, the demand of proper lubrication had limited and has reduced this allowable limit, has increased the pressure and the load size of machine.Undoubtedly, should be used for driven plunger or by the fluid of piston actuated in order to realize that this seepage has been used.Therefore, just in the above-mentioned example that provides, it is lubricated that 4 gallons of fluids of per minute are used for seepage, thereby reduced the volumetric efficiency of machine.

The content of following discloses of the present invention is to improve the volumetric efficiency of this lengthened piston machine, and guarantees suitable lubricated of piston simultaneously and simplify to be used to keep the device that contacts between piston and the swash plate.

Summary of the invention

Modular transmission only uses a pair of small and light hydraulic press that has piston to improve volumetric efficiency significantly, and the axial length of the respective cylinder that the length of these piston main bodies part moves back and forth with piston basically is identical.Two hydraulic press runnings are arranged in the closed-loop path, and one is used as the pump that is driven by vehicle motor, and another is as motor.Each machine has hinged swash plate fully.By computer control, the swash plate angle stepless change of two machines, thus the climbing that changes for startup, city driving, according to load and the gradient and the whole circumstances such as overdrive that are used for highway provide suitable optimal engine/vehicle wheel rotational speed ratio.Realized the operation of whole vehicle like this, vehicle motor remains in operation with constant relatively speed and relatively low RPM simultaneously.

Modular transmission is described to use the embodiment of various hydraulic presses, these embodiments have the combination to the novelty of simple structure feature, structure characteristic is included in reciprocating lengthened piston in the fixed air cylinder body, has the cylinder of unique lubrication groove and directly is attached to each and the hoof piece of the piston (not having dog bone formula member) of rotation and the sliding contact of nutating swash plate, or preferably with the hoof piece of the piston (not having dog bone formula member) of the only nutating eccentric wheel part sliding contact that separates swash plate.Test the remarkable enhancing that verified these simple structure features have caused volumetric efficiency synergistically, and when machine assembles fully, can manually change the mechanical efficiency (even the transmission shaft of machine has 12 cubic inches of volumes) of this enhancing easily.Every kind of disclosed machine can be used as pump and also can be used as motor running.

These fixed air cylinder hydraulic machines can be made more small and lightly than the traditional solid of rotation hydraulic press with similar specification.Along with lubricating of the lengthened piston that improves them, might use these littler lighter hydraulic presses to satisfy the required use high speed/high pressure technique of automobile and require to be used for electrodeless variable automatic transmission.

Each machine has hinged swash plate fully, and by means of computer program, the variation of the swash plate angle of two machines of electrodeless change, thereby provide the motor/rotating ratio of suitable the best to startup, city driving, the climbing and the whole circumstances such as overdrive on the highway that change according to heavy burden and steepness, thereby the electrodeless variable gear ratio that is equal to is provided.

Description of drawings

Fig. 1 shows the diagrammatic cross-section fragmentary of the hydraulic press that has variable swash plate angle;

Fig. 2 shows the hydraulic press partial sectional view along Fig. 1 plane 2-2 that omits part in order to know;

Fig. 3 A shows from the partial schematic diagram of the press table when swash plate inclination 25 is spent of the plane 3A-3A observation of Fig. 1;

Fig. 3 B shows from the swash plate of the plane 3B-3B observation of Fig. 3 A and the partial sectional view that piston presses down assembly;

Fig. 4 shows the sectional view of the single cylinder that has long spring;

Fig. 5 shows the diagrammatic cross-section fragmentary that has the hydraulic press that separates swash plate;

Fig. 6 shows the view that " closed-loop path " of two hydraulic presses that prior art is known arranged;

The pump of end-to-end embodiment's combination of the hydraulic module of Fig. 7 A demonstration speed changer of the present invention and the schematic representation of motor;

Fig. 7 B is presented at the same pump that makes up among the embodiment side by side and the motor explanatory view with another hydraulic module of forming speed changer of the present invention;

Fig. 8 A schematically and the hydraulic module of convergent-divergent ground displayed map 7A represents that it is the speed changer that is used for f-w-d vehicle;

Fig. 8 B schematically and the hydraulic module of convergent-divergent ground displayed map 7A represents that it is the speed changer that is used for rear wheel drive vehicle;

Fig. 9 A is schematically and the top view of the hydraulic module of convergent-divergent ground displayed map 7B, represents that it is the speed changer that is used for more traditional rear wheel drive vehicle;

Fig. 9 B is schematically and the end elevation of the hydraulic module of convergent-divergent ground displayed map 9A;

Figure 10 is the block diagram of the preferred input and output of computer control in the one embodiment of the invention.

Embodiment

At first, following key feature of the present invention is described:

In order to satisfy in the world needs to petroleum resources conservation; and can obviously not disturb fuel distribution on the our times at the same time, the invention provides and a kind ofly use known and through all-hydraulic, the gearless of the hydraulic pressure of checking and electronic unit, the speed changer of stepless variable.

Because hydraulic transformer of the present invention provides Operating torque with extremely low engine RPM, the petrol engine vehicle that replaces the original torque converter transmission of vehicle with the present invention is with much lower engine speed running.This feature comes from the efficient that the hydraulic press that uses the rotation swash plate that has the fixed air cylinder body and change in the angle continuum of states of broad (preferably spending+25 degree from-25) has been realized highly significant.

Speed changer of the present invention is being directly coupled on the motor of petrol power vehicle under the situation about not underspeeding.Speed changer of the present invention replaces the existing speed changer of this car fully, is installed in identical spatial position, but littler than original speed changer volume in fact, weight is lighter.Between the motor of vehicle and the present invention, need not clutch or torque converter, the present invention includes with " closed-loop path " flow of pressurized form connect respectively as two hydraulic presses of pump and motor operations.Pump is directly driven by motor car engine, produce the swash plate controlled flow of hydraulic fluid, and hydraulic fluid is sent to directly in the supporting motor.Motor is directly coupled on the wheel transmission shaft, by optionally locating the position of corresponding swash plate, produces the required moment of torsion of driver in the process that reacts on the driving wheel resistive torque.

That is to say that creative speed changer has fundamentally changed the mode of vehicle response in driver's input.In the automobile that has manual or automatic gear-shift transmission, when the driver steps on the throttle pedal requirement acceleration, power is increased on the wheel transmission shaft by increasing engine speed.In case quicken continuously, when motor reached a certain high speed, speed changer automatically or by the driver was imported through clutch, thereby changed higher gear into, and engine speed descends.Utilize creative gearless speed changer, when the driver steps on the throttle pedal requirement acceleration, increase power by in speed changer, changing the swash plate ratio, and engine speed still keeps relative fixed.In case quicken continuously, to have only when the swash plate ratio reaches a certain value, engine speed just is increased to new, high slightly level, thereby required extra power is provided.

The electronics control of speed changer is quite simple.Engine speed and take-off (propeller) shaft speed come under observation together with fuel consumption and driver's throttle valve and break index signal, and controlled variable only is the swash plate angle in hydraulic pump/motor, and controlled variable is an engine RPM under uncommon situation.

Utilize model machine of the present invention, hydraulic transformer provides enough power to the wheel transmission shaft of motion function vehicle car (weighing 5575 pounds), thereby on simulation dynamometer-simulation level road, automobile is accelerated to 30MPH rapidly, and keep the engine speed of 860RPM simultaneously.This preliminary test is restricted to vehicle and surpasses 0.67: 1 stepless change ratio from 25: 1 stepless change ratio.Because automobile accelerates to higher speed,, might make engine speed become big gently in order to make motor keep the time of constant speed to reach maximum and to improve fuel efficiency.The hydraulic transformer model machine can provide enough power so that automobile accelerates to the speed of road running, and can not make engine speed surpass 2200RPM simultaneously.In addition, this creationary speed changer can start and the speed of a motor vehicle of held stationary with 2RPM (that is, only the speed of 16 feet per minute clocks), and measure by positive displacement flowmeter this acceleration during, it has realized the rate of acceleration change peak value greater than 10MPH/ second, and reduces by 50% fuel consumption.Further, realized that with 20MPH/ gratifying deceleration, this deceleration stop vehicle fully and need not to use break second.

Speed changer of the present invention can utilize the minimum change to engine speed to change shaft speed.Therefore, the present invention allow engine speed remain on relative narrower in the low scope, the wherein easier control of burning in the hcci engine that proposes recently.Speed changer of the present invention is highly suitable for being used in the hcci engine that has more fuel efficiency on the petrol power car.

Further, the invention enables automotive industry might return to the motor of certified more low speed/higher moment of torsion, allow to utilize motor lighter, that cost is lower to realize even more high efficiency improvement.

Although it is known can be used for creating the operation of the hydraulic press of transmission pressure part of the present invention, it is right hereinafter will to describe preferred this hydraulic press in detail.As mentioned above, suppose that each disclosed machine is connected in " closed-loop path " hydraulic system of known pump that has a suitable pairing or motor.Two hydraulic presses in the speed changer of the present invention are structurally identical as far as possible, one as pump and another as motor.

In a preferred embodiment, speed changer of the present invention and storage battery use together, thereby improve fuel economy.

Long-piston hydraulic machines

With reference to figure 1, hydraulic variable machine 110 comprises modularization fixed air cylinder body 112.Cylinder block 112 has a plurality of cylinders 114 (only demonstrating), the wherein piston 116 of a plurality of corresponding couplings to-and-fro motion (maximum extended position is located at piston 116 ') between the retracted position of piston 116 and variable extended position.Each piston has a ballhead 118 that is installed on the neck 120 at an end of the axial cylindrical body portion 122 of elongation, and axial cylindrical body portion 122 length with each respective cylinder 114 basically is the same.Each spherical piston head 118 is engaged within the corresponding hoof piece 124, hoof piece 124 can be formed on slip on the rotor 128 lip-deep planes 126, rotor 128 pivotally is connected to driving element (that is the axle 130 of the bearings of the thorax inside at cylinder block 112 centers).

Hydraulic press 110 has modular valve member 133, valve member 133 is used bolt, as the top cover of the left end of modularization cylinder block 112, and valve member 133 comprises that a plurality of adjustings flow into and flow out the guiding valve 134 (only showing) of the fluid of cylinder 114.

Machine 110 can be used as pump or as motor operations.During as motor operations, at each circuit of transmission shaft 130 between first halftime, high-pressure liquid from inlet 136 enters the valve end of each respective cylinder 114 by port one 37, thereby each piston is driven into the position that it launches fully from its retracted position.During second half cycles of each circuit, because returning to it, each piston returns to the position fully, so low-pressure fluid withdraws from from each respective cylinder by port one 37 and fluid output 139.

During as pump work, during each circuit half cycles of transmission shaft 130, when each piston 116 all moved to extended position, low-pressure fluid was inhaled in each cylinder 114, by 136 " closed-loop path " entry ports 137 from the circulating liquid hydraulic fluid that enter the mouth.During the next half cycles of each circuit, the driving force of getting back to each respective pistons 116 of its complete retracted position imports high-pressure liquid the oil hydraulic circuit of closing from port one 37 by exporting 139.High-pressure liquid is sent in the hydraulic press (for example above-mentioned hydraulic press that discusses 110) of coupling by suitable closed-loop path groove (not shown) then, the piston that causes supporting machine is moved with the speed that changes along with high-pressure liquid volume (gallon per minute) variation, and high-pressure liquid adopts known technology to transmit.

The cylindrical wall of each cylinder 114 is by associated lubrication groove 140 crosscut radially that is circumferentially formed in the modularization cylinder block 112.A plurality of paths 142 are connected to each other whole lubrication grooves 140, thereby form the continuous lubrication path in cylinder block 112.

During the whole stroke of each piston, each lubrication groove 140 is closed by the axial cylindrical body 122 of each respective pistons 116 in fact.That is to say that the effect of the outer circumference of each cylindrical body 122 is just as the wall that encapsulates each lubrication groove 140 always.Therefore, even when piston 116 passes through the maximum stroke to-and-fro motion, make whole lubrication groove 140 interconnected continuous lubrication paths in fact still keep isolating.Continuous lubrication path 140,142 is formed on cylinder block 112 inside simply, economically.

In 110 operation periods of hydraulic press, enter each cylinder 114 and just almost be full of all interconnected lubrication grooves 140 immediately by port one 37 by the minimum discharge of the high-pressure liquid that pressurizes between the cylinder wall of each piston 116 and the outer circumference from inlet 136.The lubricating fluid loss of each lubrication groove 140 is subjected to the restriction around strip of paper used for sealing 144, approaches the opening end of each cylinder 114 around strip of paper used for sealing 144 positions.However, because the continuous minimum discharge between the axial cylindrical body of the respective cylindrical wall of each cylinder and each respective pistons is in response to piston motion and in response to the pressure change in each rotation halftime of transmission shaft 130 when the reciprocating motion of the pistons, so the appropriateness of the lubricating fluid in the closed continuous lubrication path of lubrication groove 140 and flowing continuously.Because the pressure of each cylinder 114 is kept to low pressure in the backhaul of each piston 116, drive the fluid of the more high pressure in different closed lubrication passages 140,142 between main body 122 outer circumferences of each cylinder 114 wall and each piston 116, each piston 116 enters into the valve end of each cylinder 114 that just experiences this decompression.

Because secondary minimal fluid flow dynamic response in piston motion and in response to when reciprocating motion of the pistons the time pressure change in each the rotation halftime at transmission shaft 130, so the mobile appropriateness of the lubricating fluid in closed continuous lubrication path 140,142 and continuously.

The rotor 128 of pump 110 pivotally is installed to perpendicular on the transmission shaft 130 around the axle 129 of axle 132.Therefore, when rotor 128 during around transmission shaft 130 rotation, it preferably becomes positive and negative 25 degree from 0 degree (that is, vertical) with respect to the inclination angle of axle 130.In Fig. 1, rotor 128 tilts with 25 degree.Control to this variable incidence is as follows: near the pivot of the rotor 128 axle 129 is determined by the position around the sliding collar 180 of transmission shaft 130, and the pivot of rotor 128 can be with respect to axially being moved.Control link 182 connects the axle collar 180 that has rotor 128, so that the axle collar 180 causes that along the axial motion of transmission shaft 130 rotor 128 is around axle 129 rotations.Such as, when the axle collar 180 moves to the right side in Fig. 1, the inclination angle of rotor 128 from shown in positive 25 degree inclination angles get back to 0 degree (that is, vertical) and get back to then in the successive ranges of negative 25 degree and change.

Moving axially by the pin 184 of lasso 186 of the axle collar 180 controlled, when the hinged axle center rotation around lasso axle 190 of lasso 186 by lasso control arm 188.Lasso 186 is driven by the general lienar servomechanism (not shown) that is connected to lasso arm 188 bottoms.Although all the other elements of lasso 186 all are included in the modularization swash plate shell 192, and lasso axle 190 supported by the bearing that is fixed in shell 192, and lasso control arm 188 is positioned at outside the shell 192.Swash plate rotor 128 keeps balances by identical with control link 182 basically shade connecting rod 194, and is connected to the axle collar 180 similarly, but is in tossing about of the axle collar 180.

With reference to figure 1 and Fig. 2, the cylindrical wall of each cylinder 114 is by associated lubrication groove 140 crosscut radially that is circumferentially formed thereon.The whole lubrication grooves 140 of a plurality of path 142 interconnection, thus continuous lubrication groove in cylinder block 112, formed.In the whole stroke of each piston, each associated lubrication groove 140 is basically by axial cylindrical body 122 closures of each respective pistons 116.That is to say that the outer circumference of each cylindrical body 122 is as the wall that comprises each associated lubrication groove 140 always.Therefore, even when piston 116 to-and-fro motion reach maximum stroke, the continuous lubrication path of whole lubrication grooves 140 that interconnect still is in closure basically.Continuous lubrication passages 140,142 is formed at cylinder block 112 inside simple and economically, and these can get the best understanding from the schematic representation of Fig. 2, for the sake of clarity, has amplified the relative size of fluid slot and connecting path among Fig. 2.

In hydraulic press 110 operation process, all the lubrication grooves 140 of interconnection almost are full of by the minimum discharge from the high-pressure liquid of inlet 36 immediately, and these fluids enter each cylinder 114 and pressurized between the cylinder wall of each piston 116 and outer circumference by port one 37.Be subjected to being positioned at restriction from the Lubricants of each lubrication groove 140 losses around strip of paper used for sealing 144 near each cylinder 114 opening ends.However, Lubricants appropriateness in the continuous lubrication path of the closure of this lubrication groove 140 and flowing continuously is because the continuous minimum discharge of the fluid between the axial cylindrical body of the respective cylindrical wall of each cylinder and each respective pistons is in response to piston motion and in response to pressure generation in each rotation halftime of transmission shaft 130 when the reciprocating motion of the pistons.Because the pressure of each cylinder 114 is kept to low pressure on the return stroke of each piston 116, the fluid of the more high pressure in the lubrication passages 140,142 of closure between the outer circumference of the wall of each cylinder 114 and each piston 116 main bodys 122 is driven to the valve end of each cylinder that experiences this pressure drop 114 once more.

With reference to figure 3A and 3B, be used for hydraulic press press down assembly comprise have a plurality of annular openings 160 press down element 154, each trip ring is around the neck 120 of respective pistons 116.The swash plate angle is positive 25 degree in Fig. 3 A and 3B.Fig. 3 A shows the press table of axially overlooking down 154 from rotor 128, perhaps the press table 154 that obtains from the 3A-3A plane of Fig. 1.Locate a plurality of special packing rings 156 respectively pressing down between element 154 and each the piston hoof piece 124.Each packing ring 156 has an extension 158, and the outer circumference that extension 158 touches corresponding hoof piece 124 is permanently connected to the plane 126 that keeps hoof piece and rotor 128.Each corresponding hoof piece chamber is connected with piston groove 164 with suitable hoof piece groove 162, equals the hydrodynamic pressure of the head of each piston 116 thereby guarantee to be in the hoof piece-hydrodynamic pressure on rotor border always.

Hydrodynamic pressure keep along the direction offset piston 116 of rotor 128, and provide exemplary thrust plate assembly to carry load.Yet, the required speed of automobilism (for example, 4000rpm) under, additional offset placed load is to guarantee that constant contact is necessary between the plane 126 of piston hoof piece 124 and rotor 128.Variable hydraulic press provides this additional biasing by using three simple spring biasings to press down one of assembly.

Be used for first of hydraulic press 110 and press down assembly and comprise helical spring 150, helical spring 150 is formed in the suitable crack 152 in the cylinder block 112 around being positioned to be centered around axle 132 around the axle 130 and along circumference.Helical spring 150 biasing presses down element 154 along what circumference was centered around axle 130 and axle 132 location equally.Press down element 154 and have a plurality of circular opens 160, each opening is all around the neck 120 of each piston 116.A plurality of special packing rings 156 are separately positioned on and press down between element 154 and each the piston hoof piece 124.Thereby each packing ring 156 has the extension 158 that the outer circumference that touches each hoof piece 124 is permanently connected to the plane 126 of hoof piece and rotor 128.

Because the inclination angle of rotor 128 changes during machine run, so swash plate positions and piston hoof piece press down relative change the in position of assembly.Referring to the relative position of these parts under the 0 degree inclination angle situation, each respective circular opening 160 has identical radial location to each piston groove 164 in the element 154 with respect to pressing down.In the whole inclination angles except that 0 degree, each piston groove 164 is with respect to the relative radius position difference of each opening 160, and the relative position of each special packing ring 156 is also different.Because rotor 128 is rotated and nutating by a complete cycle under every kind of inclination angle, the different relative position of each opening in nine openings 160 is their constant variation.Such as, under the situation at the degree of 25 shown in Fig. 3 A inclination angle, if on the top that presses down element 154 (promptly each cycle period people of rotor 128, in 12 o'clock direction) observe and only pass through the motion that opening 160 takes place, observed part relative position will continuously change in the open-topped 160 so, thereby mate the relative position shown in each of other 8 openings 160.

Under the inclination angle except 0 degree, in each cycle period of rotor 128, when each hoof piece 124 slipped over the plane 126 of rotor 128, each special packing ring 156 slipped over pressing down element 154 surfaces.Each part passes all places that can see from each opening other 8 openings 160 and changes with respect to himself opening 160 in these parts.Each all follows the endless path (it is lemniscate that trace looks like, that is, " 8 font ") of each piston 116 horizontal position size variation in the angle of internal friction that has swash plate rotor 128 and the fixed air cylinder body 112.For the good contact between the plane 126 that guarantees each corresponding hoof piece 124 and rotor 128, be the border preferred size of each opening 160, so that the border of opening 160 still keeps always and the contacting of half surface that surpasses each special packing ring 156 in each cycle period at rotor 128 whole inclination angles.

Local amplification view with the single piston of hydraulic press 210 in Fig. 4 shows that schematically second presses down assembly.Each piston 216 is positioned in the modularization fixed air cylinder body 212 of cylinder 214 inside, associated lubrication groove 240 crosscut radially that the latter is formed along a circumference thereof.With the same way as according to another hydraulic press of above detailed description, the similar groove in other the cylinder of each lubrication groove 240 and this machine interconnects, thereby forms the continuous lubrication path in cylinder block 212.Optional can be positioned opening end, minimize thereby further make from the lubricating fluid of each lubrication groove 240 losses near each cylinder 214 around strip of paper used for sealing 244.

Fixed air cylinder body 212 neither comprises big axial circumference helical spring, does not also comprise being used to keep helical spring axial circumference crack.The modularization fixed air cylinder body 212 of hydraulic press 210 can connection mode blocking tilt fixing swash plate assembly or modularization variable-angle swash plate assembly, but in either case, hydraulic press 210 all provides a kind of assembly that more simply presses down.That is to say, among this embodiment press down assembly only comprise a corresponding pot type piston hoof piece 224 that is used for each piston 216 and with only corresponding helical spring 250 of its combination, the latter also is associated with each respective pistons 216.

Each piston hoof piece 224 is similar to first and presses down the common hoof piece shown in the assembly, and is installed on the ballhead 218 of piston 216, thereby slips over the plane 226 that forms on machine swash plate rotor 228 surfaces.The valve end upper edge circumference that each helical spring 250 is arranged in each respective cylinder 214 respectively is centered around around the hydrovalve port 237, and is positioned in the main body of each respective pistons 216.

Each hoof piece 224 slips over the plane 226 of rotor 228 along the lemniscate stroke, in the lemniscate stroke horizontal position of each piston 216 vary in size and rotor 228 also different with respect to the size at the inclination angle of axle 232.During hydraulic press 210 ran well, hoof piece 224 was kept in touch by the plane 226 of hydraulic pressure and swash plate.Therefore, the spring biasing that provides by helical spring 250 is minimum, but is enough to make each hoof piece 224 and plane 226 lacking under the situation of hydraulic pressure in the sliding contact of remaining valid of each cylinder 214 valve end.The biasing of the minimum of spring 250 not only is convenient to assemble but also has been stoped between erecting stage and fine dust of carrying secretly under abrasion condition and metal detritus.

Referring to Fig. 5, be used for the 3rd of hydraulic press 310 and press down assembly and comprise that improved common separation swash plate arranges.A plurality of pistons 316 include corresponding slip hoof piece 324, to-and-fro motion in a plurality of pistons 316 each cylinder 314 in the cylinder block 312 identical with cylinder block 112.Each hoof piece 324 slips on the plane 326 that forms on the eccentric wheel 327, eccentric wheel 327 is installed on the rotor 328 of coupling by suitable bearing 372,374, bearing 372,374 is allowed eccentric wheel 327 nutating under the situation that does not have rotation, and while rotor 328 is according to known technology nutating and rotation.Control by the position of sliding collar 380, control link 382 and balance shade connecting rod 394 around the eccentric wheel 327 of axle 329 and the inclination angle of rotor 328.

Hoof piece 324 presses down by being same as first assembly that presses down that presses down assembly in fact, yet bigger single helical spring 150 is replaced by a plurality of less independent spiral springs.

Press table 354 is fixed on the eccentric wheel 327.Each hoof piece 324 receives the circumferential extension of each special packing ring 356, and the neck of each piston 316 is positioned at the inside of one of a plurality of corresponding opening 360 by press table 354 formation.Son 328 rotations although eccentric wheel 327 does not rotate, the nutating of eccentric wheel 327 is identical with the nutating of rotor 328, and therefore, the relative movement between the plane 326 of hoof piece 324 and eccentric wheel 327 is also with first to press down the relative movement of assembly identical.

A plurality of independent spiral springs 350 provide minimum spring biasing, thereby lack under the situation of hydraulic pressure in the valve end of each cylinder 314, keep the effective sliding contact between the plane 326 of each hoof piece 324 and eccentric wheel 327.Each helical spring 350 along circumferential registration around each hoof piece 324, at each special packing ring 356 with between the axle collar that forms on the bottom of each hoof piece 324, be fixed just.

With reference to figure 6, during known " closed-loop path " arranged, no matter motor or pump, each hydraulic press is preferably supporting with another hydraulic press (supporting pump or motor).Such as, the high-pressure liquid that withdraws from from the outlet 139 of hydraulic press 110 directly is passed to the input 136 ' of supporting hydraulic press 110 ', and directly is passed to the input 136 of supporting hydraulic press 110 from the low-pressure fluid that the outlet 139 ' of hydraulic press 110 ' is withdrawed from.Hydraulic press 110 ' is as the motor except hydraulic press 110 is used as pump, and hydraulic press 110 structurally can be identical with hydraulic press 110 '.Segment fluid flow in this closed loop system constantly is lost in " seepage " and in fuel tank and is collected, and fluid refunds in the closed-loop path from fuel tank automatically, thereby keeps the fluid of prearranging quatity in closed-loop system always.

Hydraulic transformer

In one embodiment, shown in Fig. 7 A, two hydraulic presses are according to end to end form setting, and shown in Fig. 7 B, two hydraulic presses are according to form setting side by side in another embodiment.In end to end embodiment, pump 400 comprises the pump shaft 402 of driven pump swash plate 404, the long-term job plug in the pump swash plate 404 driven pump cylinder block 406.Oil hydraulic circuit 408 is connected to motor 410 with pump 400.Oil hydraulic circuit 408 makes liquid flow between pump cylinder block 406 and motor cylinder block 412.Come the supporting roll hydraulic fluid drive motor piston of self-pumping 400, thus drive motor swash plate 414 rotation motor transmission shafts 416.In embodiment side by side, oil hydraulic circuit 418 is configured to connect two cylinder block adjacent one another are 406,412.In this embodiment, pump 400 can link to each other along their common side structure with motor 410, thereby provides constancy for pump-motor unit.

Although end to end form is simpler, light, the part that connects pump and motor still less, the length of scheme is obviously shorter side by side.Long 25 inches of end to end 12 cubic inches of model machines, 10 inches of diameters, weigh 150 pounds.12 cubic inches of model machines side by side are 17 inches of length and wide 20 inches.These two model machines rock the pressurized fluid of 12 cubic inches of the each circulation pumpings in place at complete pump.Two model machine efficient are very high, so that almost do not have energy to be lost with the form of heat.In the running all processes, cylinder block remains quite cool with respect to existing hydraulic press.Two kinds of model machines also all are quite quiet between on-stream period.

As previously mentioned, the electronics control of speed changer is quite simple.Engine speed, fluid operating pressure and take-off (propeller) shaft speed come under observation with fuel consumption and driver's deceleration and braking index signal, and controlled variable only is engine RPM and swash plate angle in oil hydraulic pump and oil hydraulic motor.In addition, after reaching highway speed, motor swashplate changes, thereby improves from 1: 1 to about 0.5: 1 continuous stepless overdrive.

In one embodiment of the invention, hydraulic transformer is modular.The term of Shi Yonging " modularization " is specifically designed to and describes the unit that can be used as " will not change " in this article, thereby substitutes the existing speed changer of vehicle of operation at present or design.Thereby might allow current petrol engine vehicle operating to get up to have higher fuel efficiency according to modular transmission of the present invention, this fuel efficiency can be compared with the fuel efficiency of the diesel-engine road vehicle of similar size.

Fig. 8 A is a schematic representation, has described front-drive car in proportion, expresses " from east westerly " motor 401 between front tyre 405a, the 405b and before trailing wheel 405c, 405d.The speed changer of described vehicle is dismantled, and replaces and go up the of the present invention end to end modularization embodiment shown in Fig. 7 A, that is to say that oil hydraulic pump 400 is connected to oil hydraulic motor 410 by oil hydraulic circuit 408.This module is according to being illustrated with respect to one of motor 401 suitable position, and pump shaft 402 is connected to the accessory part transmission shaft 403a of motor 401 by belt 411.Wheel shaft 422 before bindiny mechanism 424 will be connected to from the output of the hydraulic module of motor drive shaft 416.

Preferably, by exporting identical mechanism with receiving the original speed changer of vehicle, output is connected to vehicle front-wheel.In one embodiment, bindiny mechanism 424 is mechanical coupling that unique motor output shaft 416 arrives preceding wheel shaft 422.In another embodiment, bindiny mechanism 424 comprises mechanically motor output 416 is merged with motor output 403b, thereby wheel shaft 422 provides power forward.In two embodiments, the power that offers wheel drive shaft 422 is mainly by changing the output of hydraulic pressure setting change hydraulic module.In two embodiments, can change the power that offers live axle 422 by the rotating speed that changes motor 401 with assisting.In a second embodiment, bindiny mechanism 424 can comprise single track device, thereby will merge from output of the power of motor drive shaft 416 and output from engine driveshaft 403b.

Fig. 8 B is a schematic representation, described rear wheel drive truck in proportion, expresses " from north orientation south " motor 401a between front tyre 405a, 405b.The speed changer of this car is dismantled, and replaces and go up the end to end modularization embodiment of the present invention shown in Fig. 7 A, that is to say that oil hydraulic pump 400 is connected to oil hydraulic motor 410 by oil hydraulic circuit 408.This module is illustrated according to a possible position with respect to motor 401, and pump shaft 402 is connected to the accessory part transmission shaft 403a of motor 401 by belt 411.Bindiny mechanism 428 will be connected to drive shaft of rear wheel 426 from the output of the hydraulic module of motor drive shaft 416.

Preferably, by exporting identical mechanism with receiving the original speed changer of vehicle, output is connected to the trailing wheel of vehicle.In one embodiment, bindiny mechanism 428 is mechanical coupling that unique motor output shaft 416 arrives drive shaft of rear wheel 426.In another embodiment, bindiny mechanism 428 comprises mechanically motor output 416 is merged with motor output 403b, thereby provides power to drive shaft of rear wheel 426.In two embodiments, the power that offers wheel drive shaft 426 is mainly by changing the output that hydraulic pressure changes hydraulic module.In two embodiments, can change the power that offers wheel transmission shaft 426 by changing motor 401 speed with assisting.In a second embodiment, bindiny mechanism 428 can comprise single track device, thereby will merge from output of the power of motor drive shaft 416 and output from engine driveshaft 403b.

Similarly, Fig. 9 A and Fig. 9 B are schematic representation, described the top view and the rear view of the front end of common rear wheel drive vehicle in proportion, express common " from north orientation south " the motor 401a between vehicle front tyre 405c, 405d.Equally, the speed changer of this car is dismantled, and replaces and go up the present invention modularization embodiment side by side shown in Fig. 7 B.Although oil hydraulic pump 400 still is connected to oil hydraulic motor 410 by the oil hydraulic circuit 408 of rear side, the module front portion comprises the connecting box 407 that has fixed plate 419.Module with bolt to the flywheel casing 409 that is positioned at motor 401a rear portion.The pump shaft of oil hydraulic pump 400 is connected to the main drive shaft (not shown) of motor 401a by common unit, and the output of hydraulic module also is connected to output shaft 417 by connecting box 407 inner common unit (not shown)s, and output shaft 417 is by exporting the wheel that identical mechanism is connected in vehicle with the original speed changer of reception vehicle.In a second embodiment, connecting box 407 can comprise single track device, thereby will merge from output of the power of motor drive shaft 402 (referring to Fig. 7 B) and output from engine driveshaft.

Vehicle operating

The vehicle motor operation begins in normal way, allows the gear level of vehicle be positioned at " STOP ".(note: be called as " driving model selector " below the gear level of vehicle.) when motor moved with idling conditions, for example, when approximately 750RPM and vehicle still were in " STOP ", speed changer and its computer control were in waiting mode.By accelerator pedal operation, motor can dally with neutral gear.In case the driving model selector is not in the " STOP " position, computer control begins according to following real-time input engine speed and car speed to be controlled:

A) position of driving model selector

B) position of accelerator pedal

C) position of brake pedal

D) based on the car speed of engine output shaft speed and wheel shaft speed

E) fuel flow rate of flow direction engine

F) swash plate positions on pump-motor

G) oil hydraulic circuit pressure.

Computer control uses these inputs that following assembly is produced output in real time:

A) the high-pressure and hydraulic safety valve on pump-motor

B) the swash plate servo position valve on pump-motor

C) adjust to the engine throttle of optimal engine rotating speed.

The various communication between components of computer control and automobile are schematically illustrated in Figure 10.When motor car engine was started, computer control 450 constantly monitored driver's input, just the position of the position of the position of driving model selector 452, break 454 and gas pedal 456.Computer control is the speed of monitor engine transmission shaft 458 also, determining whether and need adjust, thereby changes the speed of transmission shaft 458.When the driver imports 452,454,456 when showing that needs change shaft speed 458, computer control is determined: (a) the fuel oil flow rate of flow direction engine 460 is as the indirect measurement of engine speed; (b) value of the hydraulic pressure 462 in pump and the motor and (c) pump swash plate 464a and (d) position of motor swashplate 464b.

Computer control 450 uses pre-defined algorithm full blast ground needing to realize the shaft speed 458 of change then.Realize above-mentioned situation by carrying out one or more following changes: computer control 450 can be adjusted engine throttle 466, thereby change to the fuel oil flow rate of motor 460, and/or can adjust swash plate servovalve 470, thereby one of adjust among pump and motor swashplate 464a, the 464b or the two position.

Vehicle in conjunction with speed changer of the present invention preferably has following feature:

1, change " driving " or " neutral gear " into from " STOP " when the driving model selector, and when still slamming break, this system remains on 0 degree position with the pump swash plate, thereby avoids producing in closed-system any hydraulic pressure.

2, change " driving " or " neutral gear " into from " STOP " when the driving model selector, and when no longer slamming break, the pump swash plate remains 0 degree and motor swashplate is stayed positive 25 degree places.As long as the pump swash plate remains on 0 degree, the whole fluids in the closed-loop path remain on the condition of " not having to flow " so.This makes the wheel transmission shaft remain on " locking " position, thereby a kind of " slope is fixed " feature is provided.In case vehicle is under extreme upward slope or the descending situation, although promptly rear propeller shaft is locked in this case, vehicle moves because of gravity, the pump swash plate controlled just or negative direction increase flowing of fluid a little, thereby keep the car speed of 0MPH.

3, when the driving model selector is in " driving " and does not step on break, as long as depress accelerator, requirement is more than overcoming the required hydraulic pressure/moment of torsion of tractive resistance moment of torsion, pump swash plate angle stably increases according to postive direction so, fluid moved to motor and increase the rotation of motor rotation and vehicular transmission shaft, make the car acceleration.In these cases, vehicle will continue to quicken, and equal till the tractive resistance moment of torsion of wheel of vehicle on this landform up to hydraulic pressure/moment of torsion.If the pressure on the accelerator reduces, require lower pressure set-point, pump swash plate angle reduces so, thereby reduces the acceleration of vehicle, till reaching this set point.

Speed changer of the present invention has fundamentally changed the mode that automobile is made a response to driver's input.In the automobile that has standard or automatic gear-shift transmission, when the driver steps on accelerator requirement acceleration, power is increased on the wheel transmission shaft by increasing engine speed.In case quicken continuously, when motor reached a certain high speed, speed changer automatically or by the driver was imported via clutch, thereby changed higher gear into, and engine speed descends.In having the automobile of stepless speed variator of the present invention, when the driver requires to quicken by accelerator pedal, increase power by the swash plate ratio that changes in the speed changer, and the engine speed maintenance is constant.In case quicken continuously, to have only when the swash plate ratio reaches particular value, engine speed is just accelerated, thereby more power is provided.

Because hydraulic transformer of the present invention provides Operating torque with extremely low engine RPM, the petrol engine vehicle that replaces the original torque converter transmission of vehicle with the present invention is with much lower engine speed running.This feature comes to use to be had the fixed air cylinder body and is realizing very significantly efficiengy-increasing from negative 25 hydraulic presses of spending the wobbler that changes in the preferred continuum of states of positive 25 degree at least.

Speed changer of the present invention can utilize the minimum change to engine speed to change shaft speed.Therefore, the present invention allow engine speed remain on relative narrower in the low scope, the easier burning that is controlled in the hcci engine in this scope.Speed changer of the present invention is highly suitable for being used in the hcci engine that has more fuel efficiency on the petrol power car.

Pump-motor of the present invention does not preferably use " dog bone formula member ".They preferably have minimum " seepage " property, promptly preferably less than 0.1 gallon per minute.They preferably connect with " closed-loop path ".Pump-motor preferably has traditional separation swash plate, improves by increasing bearing, thereby is supported on the eccentric wheel part of only carrying out nutating on nutating/rotor element.In one embodiment of the invention, these bearings are needle bearings.They preferably have the machinery valve system.Each pump-motor preferably includes the press table by a plurality of spring biasings, around each spring is arranged on the slip hoof piece relevant with each piston head along circumference respectively.This combination that separates swash plate and press down element has reduced the surface velocity of relative movement between hoof piece and the swash plate significantly, has therefore reduced wearing and tearing and cost, and has increased gear efficiency significantly.

Example: the installation and the assessment of 2004 Chevy Tahoe full hydraulic speed changers

In order to show the fuel efficiency of modular nature and quantification full hydraulic speed changer of the present invention, the automatic transmission of 2004 Chevrolet Tahoe is removed, and in its position speed changer of the present invention has been installed.

Vehicle powertrain comprises the GM5.3L V8 motor that is directly coupled to continuous variable transmission by non-reduction gear.Speed changer comprises oil hydraulic pump and the motor that only is coupled by flow of pressurized.Produce the swash plate controlled flow of necessary sensing oil hydraulic motor by engine-driven pump.Position by motor swashplate and be directly coupled to the transmission shaft that is used for driving wheel of vehicle, motor produces necessary moment of torsion corresponding to the driving wheel resistive torque.

Adopted following input from vehicle control module to the continuous variable transmission controller:

1, the driving model selector that has parking, reversing, neutral gear, driving and parking locking.

2, be used for the accelerator pedal position sensor that the driver indicates required drive.

What 3, be used for that the Redundant Control driver pedal is in complete closed position closes the idle running switch.

4, be used for the driver and indicate the brake pedal sensor of accelerating deceleration.

In order to import, following transmission element has been installed to computer control:

1, three hydrostatic sensors are used to monitor high-pressure service pump, motor and management loop pressure.

2, two velocity transducers are used to monitor speed changer input and back kick moving axis output speed from motor.

3, two fuel flowmeters are used for motor supply and return.

4, two pumps and motor swashplate position LVDT.

5, hydraulic pressure management loop stream amount meter.

Output from computer control:

6, high-pressure and hydraulic security solenoid valve.

7, two high-pressure service pumps and motor swashplate servovalve.

At first calculate all various accelerator pedals/swash plate angles ratio is set, utilize the dynamometer data to test then by computer control.For model machine, the initial race of engine state that is calculated as is arranged on 200 PSI with system pressure, makes to be 3,800 PSI to the maximum, and it is per 1 to have 167 lb-fts of moments of torsion, the change of 000PSI pressure difference.For model machine Tahoe vehicle, primary Calculation shows that the engine RPM scope is limited in 750 to 2,200, have 25: the 1 velocity ratio restriction of (low speed-low speed) to 0.67: 1 (overdrive).The purpose of model machine design is to make that motor keeps the enough moments of torsion to whole EPA tests when turning round with minimum RPM.Because for needed specified rate moment of torsion, motor can be created in the value in RPM and the fuelling level scope, so the computer control algorithm is selected to obtain the highest fuel economy.

Be to adopt modularization to come existing speed changer in the gasoline replacing engine vehicle although should be pointed out that the object of the invention, also can adopt the unit that producer installs and be used for diesel-engine vehicles.

In this, the present invention will be used for having (popular such as the 1960-70 age) more petrolic vehicle of existing high speed of low speed/higher torque engines, perhaps Modularly replaces (popular such as the 1960-70 age) more existing high speed petrol engine of low speed/higher torque engines, and gasoline efficient will improve more significantly.

Therefore, speed changer of the present invention not only weight is lighter, more simple and manufacture cost is lower, but also allow people to keep its huge petrol engine basic facilities, improved simultaneously can with the fuel consumption that compares favourably by diesel engine, therefore realized the needs of energy saving and can not destroy world's fuel distribution.

The invention enables automotive industry might return to the motor of the certified more slow-speed of revolution/higher moment of torsion, allow to utilize motor lighter, that cost is lower to realize more high efficiency improvement.

Therefore, should be understood that embodiments of the invention as herein described only are the examples that the principle of the invention is used.The details of the exemplary embodiment that this paper relates to is not the restriction to the claim scope, and those features as claimed in claim are considered to essential feature of the present invention.

Claims

1, a kind of modular transmission that is applicable to vehicle, described vehicle has motor, be used to indicate accelerator that the expectation of car speed changes, be used to indicate break that the expectation of car speed reduces and the output driver that is used to drive described wheel of vehicle, and described speed changer comprises:

-a plurality of hydraulic presses, the swash plate of reciprocating lengthened piston and adjustable angle in the cylinder that each described hydraulic press has rotating shaft, form in the fixed air cylinder body, by the angular adjustment of described swash plate, that described piston has is variable, reach the stroke of predetermined maximum flow at the most;

-described hydraulic press is respectively: (a) with being turned round as described oil hydraulic pump by the corresponding hydraulic pump shaft of the engine rotation of described vehicle; (b) the corresponding oil hydraulic motor axle that rotates the described output driver of described vehicle with being operably connected turns round as described oil hydraulic motor; And (c) in the hydraulic pressure closed-loop path, interconnect;

-controller, be used for determining the relative velocity of the described output driver of described vehicle, described controller can begin in the running of described vehicle motor laggard line operate and in response to:

The speed of-described hydraulic pump shaft;

The speed of-described oil hydraulic motor axle; And

-change by the expectation of the indicated car speed of the operation of described accelerator and described break; And

Described controller is determined:

The described angular adjustment of the swash plate of-described oil hydraulic pump;

The described angular adjustment of the swash plate of-described oil hydraulic motor; And

The speed of-described motor;

-described controller changes the running that changes described vehicle according to the described expectation by the indicated car speed of the operation of described accelerator and described break, simultaneously the change of vehicle load and the change of topography of described vehicle process are compensated, and automatically adjust the speed of described motor, with the maximization predefined parameter relevant with fuel economy.

2, modular transmission as claimed in claim 1, wherein, described controller changes:

The described output driver of the described vehicle of the variable increase in no polar region reaches till one up to described ratio with respect to the speed of described hydraulic pump shaft; And

Reach after one at described ratio, the described output driver of the described vehicle of the variable increase in no polar region is with respect to the speed of described hydraulic pump shaft;

Therefore, the maximization described predefined parameter relevant in whole vehicle operation process with fuel economy, described vehicle operation process is included in described ratio and reaches during afterwards the overdrive.

3, described modular transmission as claimed in claim 1, wherein, when described controller when the running of described vehicle motor begins laggard line operate, described expectation by the indicated car speed of the operation of described accelerator and described break changes the velocity variations that causes direct not relevant with the change of described engine speed described vehicle, and the speed of described motor is determined by described modular transmission.

4, modular transmission as claimed in claim 1, wherein, described motor is the homogeneous charge compression-ignition h type engine h.

5, a kind of hydraulic transformer that is used for automobile, described automobile have motor, by described engine-driven engine driveshaft and be used to drive a plurality of wheels to move the wheel transmission shaft of described automobile, described speed changer comprises:

Oil hydraulic pump that in the hydraulic pressure closed-loop path, is connected and oil hydraulic motor, described pump and motor include:

Nonrotational cylinder block is formed with a plurality of cylinders in the described nonrotational cylinder block, described cylinder around the described rotatingshaft of driving element, along circumference with the described rotatingshaft distance first radial distance setting of described driving element;

A plurality of corresponding long-term job plugs, but be installed on the described cylinder to the to-and-fro motion of described a plurality of long-term job plug, each long-term job plug comprises piston body and is connected to the ballhead of described piston body, and each corresponding cylinder has the opening head part, and described piston head always extends described opening head part;

By the separation swash plate that described driving element drives, described separation swash plate comprises:

The variable tilted rotor of rotation and nutating; And

Eccentric wheel with plane of only nutating;

Wherein, the stroke of each described piston changes according to the inclination angle of described swash plate, reaches predetermined maximum value at the most; And

The described driving element of described oil hydraulic pump is driven by described engine driveshaft; And

The described driving element of described oil hydraulic motor is to described wheel transmission shaft transmitting torque and power;

Wherein, when described motor turns round with relative low RPM with constant relatively speed, described oil hydraulic pump and described oil hydraulic motor provide enough moment of torsion and power to described wheel transmission shaft, thereby need not in continuous accelerated motion to change under the situation of any intermediate gear transmission of any kind, described automobile is moved to fast state from state of rest.

6, speed changer as claimed in claim 5, wherein, each corresponding hydraulic press also comprises corresponding slip hoof piece, described slip hoof piece pivotally and directly is attached on each described piston head and without any middle dog bone formula member, each corresponding slip hoof piece keeps and the direct sliding contact in described eccentric plane during whole relevant the rotatablely moving between described piston and the described plane.

7, speed changer as claimed in claim 5, wherein, the angle of described swash plate spends-25+change between 25 degree.

8, speed changer as claimed in claim 5, wherein, each corresponding hydraulic press also comprises:

Corresponding lubrication groove, described lubrication groove is formed on the cylindrical wall of each cylinder in the described cylinder block, is used to keep pressurized fluid;

Whole described lubrication grooves interconnect, thereby form the continuous lubrication path in described cylinder block;

During the full stroke of each piston, by the closed described pressurized fluid that keeps in the described continuous lubrication path of essence that the outer surface by each respective pistons axial cylindrical body forms each corresponding lubrication groove, the minimum discharge of the described fluid between the described axial cylindrical body of each corresponding cylindrical wall that unique source of the pressurized fluid that described continuous lubrication path receives is each cylinder and each respective pistons; And

Described closed continuous lubrication path is formed entirely in described cylinder block inside, each described cylinder of described closed continuous lubrication path crosscut, and be center circumferential according to certain radial distance and distribute, described certain radial distance is same as the rotatingshaft of described driving element and the radial distance between the described cylinder axis in fact.

9, speed changer as claimed in claim 5, wherein, each corresponding hydraulic press also comprises and presses down assembly, is used for each slip hoof piece is setovered towards described eccentric described plane.

10, speed changer as claimed in claim 5, wherein, described motor is the homogeneous charge compression-ignition h type engine h.

11, a kind of method that is used for replacing the automatic transmission of automotive transmission chamber, described automobile has motor, by engine-driven engine driveshaft and be used to drive a plurality of wheels to move the wheel transmission shaft of described automobile, said method comprising the steps of:

A) described automatic transmission is disconnected and being connected of described engine driveshaft and described wheel transmission shaft;

B) from described speed changer chamber, remove described automatic transmission;

C) hydraulic transformer that will comprise pump and motor is placed on described variator cavities chamber interior fully;

D) described engine driveshaft is connected on the described pump and with described wheel transmission shaft is connected on the described motor; And

E) provide computer control, to control the operation of described hydraulic transformer;

Wherein, described hydraulic transformer replaces described automatic transmission, and changes moment of torsion and power from described motor, thereby provides enough moment of torsion and power to described wheel transmission shaft, so that described automobile moves to fast state from state of rest.

12, method as claimed in claim 11, wherein, described motor is the homogeneous charge compression-ignition h type engine h.

13, a kind of control provides the method for power to the wheel transmission shaft of automobile, described automobile has motor, driving model selector, accelerator pedal, brake pedal and speed changer, described speed changer comprises pump swash plate with can regulate swash plate angle and the motor swashplate with can regulate swash plate angle, said method comprising the steps of:

A) position, the position of accelerator pedal and the position of brake pedal of measurement driving model selector;

B) measure engine speed and car speed; And

C) control described pump swash plate angle and described motor swashplate angle based on the position of the position of the position of described driving model selector, described accelerator pedal, described brake pedal, described engine speed and described car speed, in the predetermined range of described pump swash plate angle and described motor swashplate angle, keep constant engine speed simultaneously.

14, method as claimed in claim 13, wherein, described motor is the homogeneous charge compression-ignition h type engine h.

15, method as claimed in claim 13, further comprising the steps of:

D) only when described pump swash plate angle and described motor swashplate angle reach predetermined value and described wheel transmission shaft and need bigger power, just increase described engine speed; And

E) only when described engine speed surpasses idle running and described wheel transmission shaft and needs more low-power, just reduce described engine speed.

16, a kind of control provides the method for power to the wheel transmission shaft of automobile, described motor car engine has from the extension of described motor the place ahead and by described engine-driven attachment driving shaft and from described motor rear extension and by described engine-driven main drive shaft, said method comprising the steps of:

A) drive hydraulic module, described hydraulic module comprises the oil hydraulic pump in the closed-loop path with oil hydraulic motor, and uses described attachment driving shaft to produce hydraulic pressure output from described oil hydraulic motor;

B) mechanically described wheel transmission shaft is coupled in described hydraulic pressure output, to provide power to described wheel transmission shaft; And

C) by adjusting described pump swash plate angle and motor swashplate angle, no polar region changes the power that offers described wheel transmission shaft.

17, method as claimed in claim 16, also comprise the step that mechanically described main drive shaft is coupled to described wheel transmission shaft, wherein, the output of described hydraulic pressure output and described main drive shaft mechanically merges, thereby produces the speed changer output that is used for providing to described wheel transmission shaft power.