Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
  • B60W30/18—Propelling the vehicle
  • B60W30/188—Controlling power parameters of the driveline, e.g. determining the required power
  • B60W30/1882—Controlling power parameters of the driveline, e.g. determining the required power characterised by the working point of the engine, e.g. by using engine output chart
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
  • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
  • B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
  • B60W10/101—Infinitely variable gearings
  • B60W10/103—Infinitely variable gearings of fluid type
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
  • B60W30/18—Propelling the vehicle
  • B60W30/1819—Propulsion control with control means using analogue circuits, relays or mechanical links
• • 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/38—Control of exclusively fluid gearing
  • F16H61/40—Control of exclusively fluid gearing hydrostatic
  • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
  • F16H61/421—Motor capacity control by electro-hydraulic control means, e.g. using solenoid valves
• • 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/38—Control of exclusively fluid gearing
  • F16H61/40—Control of exclusively fluid gearing hydrostatic
  • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
  • F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves
• • 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/38—Control of exclusively fluid gearing
  • F16H61/40—Control of exclusively fluid gearing hydrostatic
  • F16H61/46—Automatic regulation in accordance with output requirements
  • F16H61/475—Automatic regulation in accordance with output requirements for achieving a target power, e.g. input power or output power
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
  • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
  • B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W2510/00—Input parameters relating to a particular sub-units
  • B60W2510/10—Change speed gearings
  • B60W2510/1015—Input shaft speed, e.g. turbine speed
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
  • B60W2510/00—Input parameters relating to a particular sub-units
  • B60W2510/10—Change speed gearings
  • B60W2510/1075—Change speed gearings fluid pressure, e.g. oil pressure
• • 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H2061/0015—Transmission control for optimising fuel consumptions
• • 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
  • F16H59/14—Inputs being a function of torque or torque demand
  • F16H59/26—Inputs being a function of torque or torque demand dependent on pressure
• • 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
  • F16H59/38—Inputs being a function of speed of gearing elements
  • F16H59/42—Input shaft speed
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/40—Engine management systems
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
  • Y02T10/84—Data processing systems or methods, management, administration

Definitions

• the invention relates to a method and computer program for controlling a drive with a drive machine and a hydrostatic transmission.
• the invention has the object to provide a method for controlling a drive, in which the overall efficiency is improved.
• Hydromotors determined.
• the method according to the invention is based on the finding that different settings of the hydraulic pump and the hydraulic motor are possible for a given transmission ratio of the hydrostatic transmission to achieve this predetermined transmission ratio and these different settings lead to different efficiencies on the part of the hydrostatic transmission. While maintaining the predetermined transmission ratio, that operating point of the hydrostatic transmission is therefore sought, which allows optimum overall efficiency.
• optical in connection with the delivery and absorption volumes or the efficiencies to be determined and subsequently included include those operating points which do not correspond to the maximum of the respective value For example, it may be necessary to operate the operating point of an axial piston machine, for example, to achieve improved cooling outside the most economically favorable operating point and therefore to set a delivery and displacement volume which is increased in terms of efficiency.
• a control unit of the hydrostatic transmission at least one
• At least a first pressure value and a second pressure value are measured in the hydraulic circuit and a pressure difference is calculated. This is taken into account when determining the optimal absorption volume and the optimal delivery volume.
• the volumetric efficiency of the hydraulic pump and the hydraulic motor is taken into account.
• both the mechanical hydraulic efficiency and the volumetric efficiency and additionally the line pressure loss in the hydraulic circuit is taken into account in determining the optimum displacement volume or the optimal delivery volume at a given transmission ratio. Since the efficiency curves partly compensate each other over the broad, conceivable adjustment range of the delivery volume and the absorption volume, an improved overall efficiency of the hydrostatic transmission can thus be set at a specific set transmission ratio, taking into account all three contributions to efficiency. In this way, for example, in traction drives of commercial vehicles savings of
• Fig. 1 is a schematic representation of a drive for carrying out the method according to the invention for controlling such a drive;
• Fig. 2 is a diagram for explaining the setting of a hydraulic transmission ratio
• 4 shows a flow chart for carrying out the method according to the invention
• 5 shows a characteristic diagram of a diesel internal combustion engine for determining the operating point of the engine
• FIG. 6 is a characteristic diagram of the hydrostatic transmission for determining a delivery volume to be set and a volume of intake to be set.
• a drive 1 is shown in which by means of a drive machine, which is designed in the illustrated embodiment as a diesel engine 2, a hydrostatic transmission 3 is driven.
• the hydrostatic transmission 3 comprises an adjustable hydraulic pump 4 and an adjustable
• Hydromotor 5 The hydraulic pump 4 and the hydraulic motor 5 are connected to each other via a first working line 6 and a second working line 7 in a closed hydraulic circuit.
• a drive torque is generated on a drive shaft 8.
• the diesel engine 2 is connected to the hydraulic pump 4 via the drive shaft 8, so that the hydraulic pump 4 is driven by the torque generated by the diesel engine 2.
• pressure medium is conveyed either in the first working line 6 or in the second working line 7 by the hydraulic pump.
• This produces an output torque in the closed hydraulic circuit as a function of the set intake volume.
• the output torque is from the hydraulic motor 5 via an output shaft 9, for example, to a driven wheel 10 transmitted.
• the direct drive of a driven vehicle wheel 10 is represented by the hydraulic motor 5 for the sake of simplicity. However, it is also possible, for example, to retain a power shift transmission to the hydrostatic drive.
• Motor adjustment device 12 is provided.
• the pump adjusting device 11 and the motor adjusting device 12 each interact with an adjusting mechanism of the hydraulic pump 4 and the hydraulic motor 5, respectively.
• both the hydraulic pump 4 and the hydraulic motor 5 are carried out starting from a neutral position adjustable in both directions.
• the hydraulic pump 4 and the hydraulic motor 5 are preferably swash plate type axial piston machines.
• an injection pump 13 is given a flow rate by a first control unit 14. For this purpose, a corresponding signal is transmitted via a first signal line 28 from the first control unit 14 to the injection pump 13.
• the setting of the hydrostatic transmission 3 is carried out by at least a second control unit 15.
• the second control unit 15 includes a first control unit 16 and a second control unit 17.
• an integrated construction is preferred in which the first control unit 16 of the hydraulic pump 4 is assigned and the second control unit 17 is associated with the hydraulic motor 5. Accordingly becomes by the first control unit 16 of the
• Pump adjustment device 11 transmits a control signal.
• the second control unit 17 transmits the motor adjusting device 12 a corresponding control signal.
• the pump adjusting device 11 and the motor adjusting device 12 are designed to be electro-proportional. In a manner not shown adjusting pressures are generated by control valves, for example, act on an adjusting piston, which cooperates with the respective adjusting mechanism.
• the two control units 16, 17 of the second controller 15 have a common interface unit 18. Via the common interface unit 18, those signals are received or output, which are based on the setting of the hydraulic pump 4 and the hydraulic motor 5 in the same way.
• the second control unit 15 receives a signal of a driving lever 19, which is supplied via a driving signal line 20 to the common interface unit 18.
• a driving desire for direction and speed is given by an operator.
• the first control unit 14 and the second control unit 15 are connected via a communication line 25 with each other.
• a signal via the first signal line 28 is transmitted to the injection pump 13 and set the diesel engine 2 to this predetermined idle speed.
• the predetermined idle speed is preferably determined by the second control unit 15 by a speed of the diesel engine 2 is set at which the predetermined by the drive lever 19 driving desire of a user can be realized.
• a difference between the predefined idle speed and the actual speed determined by the speed sensor 21 is calculated, and this so-called depression via the communication line 25 is preferably transmitted to the second control unit 15.
• a table is stored in which a predetermined idle speed is assigned a pressing value. This table is created in dependence on a map of the diesel engine 2, so that for each a given idle speed a cheap actual speed is stored. To achieve this actual speed or a specific push, the transmission ratio ihydr of the hydrostatic transmission 2 is adjusted accordingly. By the second control unit 15th Consequently, a transmission ratio i h y dr is determined for the hydrostatic transmission.
• the hydraulic pump 4 and the hydraulic motor 5 are set to their optimal delivery volume and the optimal absorption volume, wherein preferably in addition to the mechanical-hydraulic Wirkgrade ⁇ mh of the two reciprocating engines and the volumetric efficiency ⁇ v and the pressure loss ⁇ P are taken into account in the lines.
• the efficiency curves are preferably stored in tables in the second control unit. Starting from the first determined
• Gear ratio i h y dr of the hydrostatic transmission 3, taking into account the pressure drops in the working lines 6, 7 of the hydrostatic transmission 3 calculated from the values of the pressure sensors 23.1 to 23.4 is thus by the first control unit 16 and the second control unit 17, for example when using swash plate machines determines the swivel angle of the swash plate and via a second signal line 26 and a third signal line 27, a corresponding value to the Pumpenverstellvortechnisch 11 and der Motorverstellvoretti 12 exactly.
• a first operating point a with a maximum delivery volume V g , p of the hydraulic pump 4 and maximum displacement V g , M of the hydraulic motor 5 and with an identical transmission ratio ihy dr an optimal delivery volume and absorption volume at operating point b are shown.
• Total efficiency ⁇ ges are shown in FIG. 3.
• the illustration shows the individual efficiency contributions ⁇ i, which contribute to the overall efficiency ⁇ ges , assuming a constant transmission ratio ihy dr and a constant load.
• the abscissa is scaled with arbitrary units and shows the course in the direction of increasing pressure, ie simultaneously decreasing volume flow in the working lines 6, 7.
• V, M of the pump and motor deteriorates with increasing pressure, ie decreasing delivery volume, but to a certain extent this is achieved by simultaneously improving the mechanical-hydraulic efficiency ⁇ mh, M and ⁇ mh , P.
• the curve shown for a specific gear ratio ihy dr thus results for the overall efficiency ⁇ ges of the hydrostatic transmission 3.
• FIG. 4 shows the method according to the invention in a simplified flow chart.
• the measurement result of the rotational speed sensor 21 is transmitted to the second control device 15 via the first control device 14 and the communication line 25 (step 32).
• the optimum operating point of the diesel internal combustion engine 2 is first determined in step 33 with the aid of the characteristic diagram of the diesel internal combustion engine 2.
• the data describing the map of the diesel engine 2 are stored in a corresponding table in the second electronic control unit 15.
• the transmission ratio ihy d r is determined.
• step 34 finally, the efficiency of the hydrostatic transmission 3 is optimized by taking into account the individual influencing factors, namely the individual efficiencies of the hydraulic pump 4 and the hydraulic motor 5 and in addition the line losses for the determined gear ratio ihy dr the optimal flow rate for the hydraulic pump and the optimal displacement of the hydraulic motor 5 are determined.
• the values determined in this way are transferred to the pump adjusting device 11 in the manner already described
• FIG. 5 again shows the procedure relating to the diesel internal combustion engine 2 (corresponds to step 33).
• 5 shows a simplified map of a diesel engine 2.
• the idle speed is designated by the point 0.
• the deviation of the actual speed at point 1, 2 from the predetermined idle speed is referred to as Drückung and is directly related to the ratio of the hydrostatic transmission 3.
• Throttle position of the drive lever 19 is determined and is adapted to the expected power decrease.
• the operating point is on the full load line 36.
• step 34 The further procedure (step 34) is shown once again in FIG.
• the ratio i hydr is plotted.
• the dashed lines indicate the sum of the operating states with identical efficiency ⁇ hydr .
• the operating point 2 in the diagram is controlled instead of the operating point 1. This is done without a change in the ratio i hydr of the hydrostatic transmission 3 solely by a corresponding adjustment of both the delivery volume and at the same time the displacement of the hydraulic pump 4 and hydraulic motor. 5
• the invention is not limited to the illustrated embodiment. Rather, individual features of the method according to the invention can be combined with other features in any desired manner.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Automation & Control Theory (AREA)
• Control Of Fluid Gearings (AREA)
• Control Of Transmission Device (AREA)
• Operation Control Of Excavators (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=38180615

Family Applications (1)

Country Status (5)

Families Citing this family (12)

Family Cites Families (11)

• 2006
  • 2006-04-18 DE DE102006017792.4A patent/DE102006017792B4/de not_active Expired - Fee Related
• 2007
  • 2007-04-05 CN CNA2007800006415A patent/CN101326086A/zh active Pending
  • 2007-04-05 US US12/297,583 patent/US20090069990A1/en not_active Abandoned
  • 2007-04-05 EP EP07724051A patent/EP1899205A1/de not_active Withdrawn
  • 2007-04-05 WO PCT/EP2007/003110 patent/WO2007121846A1/de active Application Filing

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events