SE466301B - MAKE HYDRAULIC DRIVE WHEELS ON A VEHICLE - Google Patents
MAKE HYDRAULIC DRIVE WHEELS ON A VEHICLEInfo
- Publication number
- SE466301B SE466301B SE8902893A SE8902893A SE466301B SE 466301 B SE466301 B SE 466301B SE 8902893 A SE8902893 A SE 8902893A SE 8902893 A SE8902893 A SE 8902893A SE 466301 B SE466301 B SE 466301B
- Authority
- SE
- Sweden
- Prior art keywords
- constant
- axle torque
- rear axle
- torque
- speed
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/356—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having fluid or electric motor, for driving one or more wheels
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H59/46—Inputs being a function of speed dependent on a comparison between speeds
- F16H2059/465—Detecting slip, e.g. clutch slip ratio
- F16H2059/467—Detecting slip, e.g. clutch slip ratio of torque converter
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Control Of Fluid Gearings (AREA)
Description
466 301 10 15 20 25 30 35 2 sluten, hydraulisk arbetskrets med från en inställnings- pump matade hjulmotorer och en direkt av motorn driven in- ställnings- och styrpump, varvid arbetsfluidumströmmen resp -trycket styrs av den kopplingsbara styrpumpsströmmen och varvid arbetsfluidumtrycket regleras genom överlagring av arbetsfluidumströmstyrningen enligt förloppet för en valbar, förbestämd funktion som beror på förhållandet mel- lan motor- och omvandlarsteg- eller växellåde-utgångsvarv- talet (DE-PS 33 31 651). 466 301 10 15 20 25 30 35 2 closed, hydraulic working circuit with from a setting pump fed wheel motors and a directly driven motor position and control pump, whereby the working fluid flow resp pressure is controlled by the switchable control pump current and wherein the working fluid pressure is regulated by superimposition of the working fluid flow control according to the course of a selectable, predetermined function depending on the relationship between motor and converter stage or gearbox output speed century (DE-PS 33 31 651).
Enligt ett sådant reglersätt bestäms arbetstrycket för arbetskretsen medelst en stegformig, förutbestämd funktion. Detta har till nackdel att till följd av den icke finavstämbara regleringen kommer de extra drivna framhjulen att rotera antingen snabbare eller långsammare i förhållande till bakhjulen. Ändamålet med uppfinningen är att med ringa insats åstadkomma en extra drivning av framhjulen på fordon, som såväl är vuxen den råa drivmiljön för byggfordon som sä- kerställer en styrd fördelning av drivlasten från fram- och bakaxeln.According to such a rule, the working pressure is determined for the working circuit by means of a step-shaped, predetermined feature. This has the disadvantage that as a result of it non-fine-tuned regulation comes the extra driven the front wheels to rotate either faster or slower in relation to the rear wheels. The object of the invention is to make little effort provide an extra drive of the front wheels of vehicles, which both adult is the raw driving environment for construction vehicles and establishes a controlled distribution of the propellant load from and the rear axle.
Lösningen av det för uppfinningen grundläggande än- damålet anvisas i det sätt som motsvarar den känneteck- nande delen av huvudpatentkravet.The solution of the basic object of the invention the target is indicated in the manner corresponding to the part of the main patent claim.
Fördelen med uppfinningen består i att redan den enk- la konstruktionen av en styrning räcker för att ställa in det extra, drivande framaxelmomentet, icke endast för lika rotation, utan därutöver också särskilt säkerställa och därmed optimera en andel av arbetet för framaxeln och bak- axeln, i motsvarighet till axeltrycket.The advantage of the invention is that already the single la the design of a control is sufficient to set the extra, driving front axle torque, not only for equal rotation, but in addition also particularly ensure and thereby optimizing a share of the work for the front axle and rear the shaft, corresponding to the axle load.
Ytterligare vidareutvecklingar av uppfinningen beskrives i de beroende patentkraven. 3. u Med hjälp av ett i ritningen schematiskt återgivet utföringsexempel beskrivs i det följande uppfinningen när- mare.Further developments of the invention described in the dependent claims. 3. u Using one schematically represented in the drawing exemplary embodiments are described in the following invention in mare.
I figuren utgår man från en effektkrets enligt anord- ningen som anges i den tyska patentskriften 33 31 651. En motor 1, företrädesvis en förbränningsmotor, driver via en 10 15 20 25 30 35 466 391 3 vridmomentomvandlare 2, inklusive dess omvandlarsteg, och en växellåda 3 huvuddrivhjulen 4 pà ett fordon. Samtidigt driver motorn 1 via en axel direkt en reglerpump 5 och en styrpump 6. Dessa båda element i en automatisk styrning arbetar i en sluten, hydraulisk arbetskrets, vilken matar hjulmotorer 7 och 8 och därmed sätter de extra, drivna hjulen 9 och 10 i rullning. Mellan de báda finns hydrau- liskt ställbara kopplingar ll och 12 återgivna. Vidare visas att hjulmotorerna är säkrade medelst tvà tryckbe- gränsningsventiler 13, 14.The figure is based on a power circuit according to German Patent Specification 33 31 651. En engine 1, preferably an internal combustion engine, drives via a 10 15 20 25 30 35 466 391 3 torque converter 2, including its converter stage, and a gearbox 3 the main drive wheels 4 of a vehicle. At the same time drives the motor 1 via a shaft directly a control pump 5 and a control pump 6. These two elements in an automatic control working in a closed, hydraulic work circuit, which feeds wheel motors 7 and 8 and thus put the extra, driven wheels 9 and 10 in rolling. Between the two are hydraulic adjustable couplings 11 and 12 shown. Further it is shown that the wheel motors are secured by two pressure limit valves 13, 14.
Styrvinkeln för reglerpumpen 5 inställs medelst ett på-inställningselement 15 och ett av-inställningselement 16 i motsvarighet till matning till dem fràn en propor- tionalventil 17. En övertrycksventil 21 begränsar styr- trycket till ett inställbart, fast värde i styrkretsen. Av samma fluidumström till styrpumpen 6 försörjes via envägs- ventiler 22, 23 arbetskretsen med fluidum.The control angle of the control pump 5 is set by means of one on setting element 15 and an off setting element 16 corresponding to feeding to them from a proportional pressure valve 17. A pressure relief valve 21 limits the control the pressure to an adjustable, fixed value in the control circuit. Of the same fluid flow to the control pump 6 is supplied via one-way valves 22, 23 working circuit with fluid.
Vid en så långt känd anordning är nu i vridmomentom- vandlaren i mätpunkterna 28, 29 börvärdes-givare anordna- de, vilken avger signaler för omvandlaringångsvarvtalet NE och för omvandlarutgàngsvarvtalet NA. bildare 25 framtas kvoten mellan omvandlarutgángsvarvtalet och omvandlaringángsvarvtalet. Med detta värde som abskis- sa kan ett ordinatavärde NAE återhämtas och vidarebearbe- tas ur minnets 26 karakteristiska kurva, fràn den däri lagrade funktionen för kvoten mellan omvandlarutgàngsmo- mentet MA och omvandlaringàngsmomentet ME.In such a device known so far, the torque is now the converter in the measuring points 28, 29 setpoint sensor those which emit signals for the converter input speed NE and for the converter output speed NA. generator 25, the ratio between the converter output speed is calculated and the conversion input speed. With this value as absurd an NAE ordinate value can be retrieved and further processed. taken from the 26 characteristic curve of memory, from the one therein stored the function of the ratio between the converter output modes the MA element and the ME conversion element.
I en proportional- Bestämningen av omvandlaringàngsmomentet sker på att i sig känt vis, med hjälp av en i ett funktionsminno 27 registrerad kurva för det uppmätta omvandlaringàngsmouen- tet ME vid konstant omvandlaringàngsvarvtal NE i beroende av förhållandet mellan omvandlaringàngsvarvtalet och om- vandlarutgàngsvarvtalet. Det fràn funktionsminnet 27 av- givna värdet multipliceras i en multiplikator 24 med kvad- raten pá kvoten mellan omvandlaringàngsvarvtalet NE och det ovannämnda konstanta omvandlaringàngsvarvtalet och tillförs en huvudmultiplikator 20. Den i multiplikatorn 466 301 10 15 20 30 35 4 bildade produkten med det ovannämnda värdet MAE, från utgången från minnet 26 återger ett räknemässigt framtaget värde för bakaxelmomentet MHA, under fullständigt iaktta- gande av drivsystemegna, konstanta, åtminstone intervall- konstanta, faktorer Kl __n, vilka kan återskapas med hjälp av ilagd växel, bakaxelöverföringen och även verknings- graden för bakhjulsdrivningen. I den därmed matade uppde- laren 19 låter sig en Valbar andel X% därav återvinnas som ett börvärde för framaxelmomentet MVA. Vid vanlig kontinu- erlig drift kommer denna andel för framaxelmomentet i för- hållande till bakaxelmomentet motsvara andelen av axel- trycket, alltså ungefär 1/3 till 1. Vid speciella förhål- landen, exempelvis vid lutningar eller vid isbildning kan dock fordonets förare ställa in andelen framaxelmoment.In a proportional The determination of the conversion input moment takes place on that in a manner known per se, by means of one in a function memory 27 registered curve of the measured conversion input momentum ME at constant conversion input speed NE in dependent of the ratio between the conversion input speed and the the converter output speed. From the function memory 27 the given value is multiplied in a multiplier 24 by the the rate of the ratio between the conversion input speed NE and the aforementioned constant conversion input speed and is added to a main multiplier 20. The one in the multiplier 466 301 10 15 20 30 35 4 formed the product with the above value MAE, from the output of the memory 26 represents an arithmetic generated value for the rear axle torque MHA, while fully propulsion system characteristics, constant, at least interval constant, factors Kl __n, which can be recreated with help of engaged gear, the rear axle transmission and also the the degree of rear-wheel drive. In the feed thus supplied a selectable proportion of X% thereof may be recovered as a setpoint for the front axle torque MVA. During normal continuum- normal operation, this share of the front axle torque in to the rear axle torque corresponds to the proportion of pressure, i.e. about 1/3 to 1. In special conditions countries, for example on slopes or ice formation can however, the driver of the vehicle set the proportion of front axle torque.
Börvärdet för framaxelmomentet MVA omformas i omfor- maren 18 i enlighet med den karakteristiska kurvan för den i sig kända proportionalventilen 17 till en elektrisk reg- lersignal iback eller ifram för reglering av magnetventil- ingångarna 32, 33.The setpoint for the front axle torque MVA is converted into maren 18 in accordance with the characteristic curve of it per se known proportional valve 17 to an electric control signal backwards or forwards for regulating the solenoid valve inputs 32, 33.
Vidare är proportionalventilen 17, på i sig känt sätt, hydrauliskt via ledningarna 34, 35 förbunden med ar- betskretsen och via förbindelserna 36, 37 förbunden med på-inställningselementet 15 och av-inställningselementet 16. Matningen av proportionalventilen 17 sker via en tillförsel 38 från styrpumpen 6.Furthermore, the proportional valve 17 is known per se hydraulically via the lines 34, 35 connected to the circuit and via the connections 36, 37 connected to on-setting element 15 and off-setting element 16. The feeding of the proportional valve 17 takes place via a supply 38 from the control pump 6.
En alternativ möjlighet att återge utgångsvarvtalet NÄ består i att man, såsom anvisas i ritningen, multipli- cerar bakhjulsvarvtalet NAG med en karakteristisk växel- storlek iväxel i en faktorbildare 40 och därefter inför detta i beräkningsförloppet. Den karakteristiska växel- storleken iväxel levererar vidare via ett ELLER-element 39 en alternativ information 30 resp 31 till omvandlaren 18, vardera i beroende om bakaxeln befinner sig i drift framåt eller bakåt.An alternative option to reproduce the output speed NÄ consists in multiplying, as shown in the drawing, the rear wheel speed NAG with a characteristic gear ratio size shift in a factor former 40 and thereafter before this in the calculation process. The characteristic gear the size of the gear further delivers via an OR element 39 an alternative information 30 and 31 respectively to the converter 18, each in depending on whether the rear axle is in forward operation or backwards.
Den ovanstående, beskrivna styranordningen kan genom- föras med ringa insats och reglerar företrädesvis ett fin- inställbart, i drivkraftens fördelning inställbart sätt för extra drivning av hjul på ett fordon.The control device described above can be implemented carried out with little effort and preferably regulates a fine adjustable, adjustable in the distribution of the driving force for extra driving of wheels on a vehicle.
Claims (5)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19883842405 DE3842405A1 (en) | 1988-12-16 | 1988-12-16 | METHOD FOR ADDITIONAL HYDRAULIC DRIVE OF WHEELS ON A VEHICLE |
Publications (3)
Publication Number | Publication Date |
---|---|
SE8902893D0 SE8902893D0 (en) | 1989-09-01 |
SE8902893L SE8902893L (en) | 1990-06-17 |
SE466301B true SE466301B (en) | 1992-01-27 |
Family
ID=6369342
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
SE8902893A SE466301B (en) | 1988-12-16 | 1989-09-01 | MAKE HYDRAULIC DRIVE WHEELS ON A VEHICLE |
Country Status (6)
Country | Link |
---|---|
JP (1) | JPH02237818A (en) |
CA (1) | CA2005691C (en) |
DE (1) | DE3842405A1 (en) |
FR (1) | FR2640558B1 (en) |
GB (1) | GB2227079B (en) |
SE (1) | SE466301B (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL9100927A (en) * | 1991-05-29 | 1992-12-16 | Vredo Dodewaard Bv | SELF-PROPELLED AGRICULTURAL VEHICLE. |
FI94041C (en) * | 1991-11-08 | 1995-07-10 | Raunisto Airi | transmission system |
DE4210251C2 (en) * | 1992-03-28 | 1995-04-27 | Orenstein & Koppel Ag | Control arrangement for vehicles with hydrostatic auxiliary drive |
DE19805809C2 (en) * | 1998-02-12 | 2000-02-17 | Biotul Bio Instr Gmbh | Determination of the surface plasmon resonance using locally or temporally modified layers |
DE10115797B4 (en) | 2001-03-30 | 2015-04-09 | Joseph Vögele AG | Method for controlling a self-propelled construction machine and self-propelled construction machine |
JP4632771B2 (en) * | 2004-02-25 | 2011-02-16 | 株式会社小松製作所 | Hydraulic steering type work vehicle |
DE102008027333A1 (en) | 2008-06-07 | 2009-12-31 | Cnh Baumaschinen Gmbh | Control arrangement for vehicles with hydrostatic auxiliary drive |
DE102011116268A1 (en) * | 2011-10-19 | 2013-04-25 | Wirtgen Gmbh | Self-propelled construction machine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2401419A1 (en) * | 1974-01-12 | 1975-07-17 | Bosch Gmbh Robert | VEHICLE WITH A HYDROSTATIC AND MECHANICAL DRIVE |
GB2022786B (en) * | 1978-05-30 | 1982-09-02 | Deere & Co | Hydrostatic vehicle auxiliary wheel drive system |
US4444286A (en) * | 1982-05-13 | 1984-04-24 | Sundstrand Corporation | Torque-control with overspeed regulation and method of controlling a hydrostatic drive |
DE3331651C1 (en) * | 1983-09-02 | 1985-05-02 | O & K Orenstein & Koppel Ag, 1000 Berlin | Method for the selectable supplementary hydraulic drive of wheels on a vehicle |
DE3620163A1 (en) * | 1986-06-14 | 1987-12-17 | Sauer Getriebe Ag | Method for the control or adjustment of a hydrostatic drive by way of the front wheels of a vehicle with mechanical, hydrodynamic or hydrostatic transmission and piston internal combustion engine as rear drive and arrangement for performing the method |
-
1988
- 1988-12-16 DE DE19883842405 patent/DE3842405A1/en active Granted
-
1989
- 1989-09-01 SE SE8902893A patent/SE466301B/en not_active IP Right Cessation
- 1989-11-02 JP JP28504689A patent/JPH02237818A/en active Pending
- 1989-11-23 FR FR8915405A patent/FR2640558B1/en not_active Expired - Fee Related
- 1989-12-15 CA CA 2005691 patent/CA2005691C/en not_active Expired - Fee Related
- 1989-12-18 GB GB8928472A patent/GB2227079B/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE3842405A1 (en) | 1990-06-28 |
CA2005691C (en) | 1995-03-28 |
SE8902893L (en) | 1990-06-17 |
GB8928472D0 (en) | 1990-02-21 |
GB2227079B (en) | 1992-10-14 |
JPH02237818A (en) | 1990-09-20 |
SE8902893D0 (en) | 1989-09-01 |
FR2640558B1 (en) | 1993-03-19 |
CA2005691A1 (en) | 1990-06-16 |
DE3842405C2 (en) | 1992-11-12 |
GB2227079A (en) | 1990-07-18 |
FR2640558A1 (en) | 1990-06-22 |
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