Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P7/00—Controlling of coolant flow
  • F01P7/02—Controlling of coolant flow the coolant being cooling-air
  • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
  • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives
• • 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
  • B60K25/00—Auxiliary drives
  • B60K25/02—Auxiliary drives directly from an engine shaft
  • B60K2025/026—Auxiliary drives directly from an engine shaft by a hydraulic transmission
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P2025/00—Measuring
  • F01P2025/60—Operating parameters
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P7/00—Controlling of coolant flow
  • F01P7/02—Controlling of coolant flow the coolant being cooling-air
  • F01P7/06—Controlling of coolant flow the coolant being cooling-air by varying blade pitch
• • 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
  • F16H61/4148—Open loop circuits

Definitions

• the invention relates to a hydrostatic fan drive for internal combustion engines according to the preamble of patent claim 1,
• cooling is necessary to dissipate the often considerable heat loss, which is usually amplified by a rotating fan.
• the fan is driven directly by a power take-off shaft of an internal combustion engine or via a hydraulic circuit, which has a driven by the power take-off shaft pump and a fan motor driving motor.
• a disadvantage of such hydrostatic fan drives is their coupling to the driving internal combustion engine, which does not allow fan operation when the internal combustion engine is turned off.
• the internal combustion engine is reduced in its power output, even if it is retrieved maximum power.
• the object of the invention is to provide a hydrostatic fan drive for internal combustion engines, which allows fan operation, even if the internal combustion engine is turned off. Furthermore, an increase in over- gang-way maximum achievable performance of the engine despite fan operation can be achieved.
• the inventive hydrostatic fan drive for internal combustion engines has a primary unit which can be driven by the internal combustion engine, and a fan motor with which a fan wheel can be driven.
• a hydraulic accumulator is connected to a high-pressure line which connects the primary unit to the fan motor.
• a storage shut-off valve is arranged in a connecting line which connects the high-pressure line and the hydraulic accumulator. This allows the hydraulic accumulator, e.g. if it is filled, separated and switched on only when needed again.
• the primary unit is an adjustable axial cam machine.
• a lossy pressure reducing valve for controlling the fan power can be omitted.
• the internal combustion engine is coupled to at least one wheel of a land vehicle or to at least one propeller of a watercraft.
• the fan drive according to the invention in such vehicles
• axial piston machine can be loaded into the hydraulic accumulator.
• a fan shut-off valve is arranged in a section of the high pressure line which connects the fan motor to the hydraulic accumulator or to the connecting line.
• the Latederabsperrventil is formed by a 2/2-way valve whose Ventii influences connects in a biased by a spring position a high pressure port of the axial piston engine via the high pressure line with a high pressure port of the fan motor, while it shuts off this connection in its switching position ,
• the fan motor is a constant Axialkobenmotor for cost reasons, which has connected to the high pressure line high-pressure port and further connected via a tank line to a tank low pressure port.
• the accumulator shut-off valve is formed by a 3/3-way valve whose valve body connects in its first switching positions the high-pressure line to the hydraulic accumulator via the connecting line, while it closes the connection to the tank line.
• the high-pressure line is connected to the tank line, while the hydraulic accumulator is shut off.
• the hydraulic accumulator and furthermore the connection of the high-pressure line to the tank line are shut off.
• the first switching positions allow the hydraulic accumulator to be charged or by the second switching positions and by the basic position of the hydraulic accumulator is shut off (eg in a charged state).
• the Speicherabsperrventil be formed for cost reasons of a 2/2-way valve, the valve body connects in its switching position, the high pressure line to the hydraulic accumulator via the connecting line, and shuts off this connection in its biased by a spring basic position.
• the fan motor is an adjustable Axialkobenmotor whose speed is adjustable by adjusting a pivot angle.
• a first connection of the fan motor via a first working line and a second connection of the fan motor via a second working line are connected to a reversing valve which is connected via the high pressure line to the primary unit and a tank line to a tank. This allows the direction of rotation of the fan wheel to be changed, e.g. Dirt from the ribs or fins of a radiator.
• the reversing valve is formed by a 2/2-way valve whose valve body connects in a biased by a spring position, the high pressure line to the first working line and the second working line to the tank line, and in its switching position, the high pressure line the second working line and the first working line connects to the tank line.
• the fan motor is an adjustable Axialkobenmotor whose speed and direction are adjustable by adjusting a pivot angle, wherein a high-pressure port of the fan motor is connected to the high pressure line, and wherein a low-pressure connection of the fan motor via a tank line with connected to a tank.
• the direction of rotation of the fan wheel can also be changed, for example, to blow out dirt from the ribs or fins of a radiator.
• a pressure relief valve may be provided adjacent to the hydraulic accumulator at a portion of the connecting line, which relieves the pressure to the tank.
• the fan drive according to the invention has an electronic control unit, via which the pivot angle of the primary unit and / or the positions of the respective valve body of the L Representativeerabsperrventils, the Speicherabsperrventils and the reversing valve and possibly the pivot angle of the fan motor are adjustable.
• the controller may be connected to an electronic engine control unit of the internal combustion engine.
• a pressure sensor may be provided at the portion of the connecting pipe which is disposed between the accumulator stop valve and the hydraulic accumulator or at a portion of the connecting pipe which is disposed between the accumulator stop valve and the high-pressure pipe. This is also in connection with the control unit.
• a speed sensor is arranged on the fan or on the fan motor, which is also in communication with the control unit.
• the fan shut-off valve and / or the reversing valve and / or the accumulator shut-off valve are continuously adjustable proportional valves.
• a throttled flow can be produced, which can be set to quickly increase the operating or exhaust gas temperature of the internal combustion engine, which is e.g. is necessary for the regeneration of a particulate filter.
• bumpless switching also protects the fan motor and wheel.
• a cooler is arranged in the tank line, wherein from For reasons of system security in a parallel to the radiator arranged bypass line a spring-biased check valve is provided, which releases the bypass line at a minimum pressure is exceeded.
• a swivel angle of the axial piston pump is set via a setpoint braking torque and a swivel angle of the fan motor via a setpoint speed and via a fan-pressure-speed characteristic curve.
• a pivot angle of the fan motor is set via a fan pressure-speed curve and simultaneously set a pivot angle of the axial piston pump to zero when the pressure in the hydraulic accumulator is sufficient for a target speed of the fan motor.
• Figure 1 is a circuit diagram of a first embodiment of a hydrostatic fan drive according to the invention
• Figure 2 is a circuit diagram of a second embodiment of a hydrostatic fan drive according to the invention.
• Figure 3 is a circuit diagram of a third embodiment of a hydrostatic fan drive according to the invention.
• FIG. 1 shows a block diagram of a first exemplary embodiment of a hydrostatic fan drive according to the invention. It essentially has an adjustable axial piston machine 1, which is connected via a shaft 2 to an internal combustion engine 4.
• the fan drive has a designed as a constant axial piston motor fan motor 6, which drives a fan 10 via an output shaft 8.
• a fan 10 cooling air is conveyed by a (not shown) radiator of the engine 4.
• the axial piston machine 1 and the fan motor 6 are arranged in an open hydraulic circuit with a tank T, which is connected via a suction line 12 to a low pressure port 1 a of the axial piston 1, and a high pressure port 1 b of the axial piston 1 with a high pressure port 14 a, 14 b High pressure port 6a of the fan motor 6 connects. Furthermore, the fan motor 6 has a low-pressure connection 6b which is connected to the tank T via a tank line 16a, 16b.
• a hydraulic accumulator 20 is connected to the high pressure line 14a, 14b.
• a continuously adjustable 3-way valve 22 is arranged, which is designed as a 3-position valve.
• the valve 22 is connected to the two sections 18b, 19 of the connecting line and to a further connecting line 24, which opens into the tank line 16a, 16b.
• a cooler 26 is arranged in the tank line 16a, 16b and parallel to a bypass line 28.
• a check valve 30 is provided, which is in the direction of the tank T at a predetermined pressure opens against a spring.
• a fan check valve 32 is disposed in a section 14b of the high pressure line 14a, 14b upstream of the terminal of the hydraulic accumulator 20, a fan check valve 32 is disposed. It is designed as a 2/2-way valve whose valve body in a biased by a spring basic position (0) the high pressure port 1 b of the axial piston machine 1 via the high pressure line 14a, 14b with the high pressure port 6a of the fan motor 6 connects. Upon actuation of an electromagnet 32a of the fan check valve 32, its valve body is displaced against the spring in a switching position (a), so that the high-pressure line 14a, 14b is shut off.
• this has an electronic engine control unit 34.
• this has an electronic control unit 36.
• the control unit 36 receives from a speed sensor 38, a measurement signal with respect to the rotational speed of the fan motor 6 with the output shaft 8 and with the fan 10. Furthermore, the controller 36 receives from a pressure sensor 40th a measurement signal with respect to the pressure in the hydraulic accumulator 20 and from a sensor 42 a measurement signal with respect to the pivot angle of the axial piston machine first
• the controller 36 outputs control signals to a Schwenkwinkeleinstellvortechnisch 44 of the axial piston machine 1 and to the electromagnets 32 a, 22 a, 22 b of the L favorableerabsperrventils 32 and the 3/3-way valve 22 from.
• the internal combustion engine 4 drives via the shaft 2 to the axial piston machine 1, which is operated as a pump. It conveys from the tank T via the suction line 12 and via the high-pressure line 14a, 14b pressure fluid to the fan motor 6, thereby driving the fan 10.
• the valve body of the Lendederabsperrventils 32 is in its spring-biased home position (0). From the fan motor 6, the pressure medium flows via the tank line 16a, 16b back to the tank T. It flows through the radiator 26 or at high flow resistance through the bypass line 28, the check valve 30 opens in this case against the spring.
• the power at the fan 10 is controlled by adjusting a piston stroke of the axial piston machine via its Schwenkwinkeleinstellvorraum 44.
• a valve body of the 3/3-way valve 22 can be adjusted in the direction of its positions a, so that from the high pressure line 14 a pressure medium via the connecting line 18 a, 18b, 19 flows to the hydraulic accumulator 20 and charges it.
• the 3/3-way valve 22 can be opened when the hydraulic accumulator 20 is charged. If in this case the fan check valve 32 is opened, the fan motor 6 can be supplied with pressure medium, even if the engine is 4 or not enough pressure medium is conveyed through the axial piston machine 1. If, on the other hand, the fan shut-off valve 32 is closed, the pressure medium of the hydraulic accumulator 20 can supply the axial piston machine 1 with pressure medium at its high-pressure connection 1b, so that it will operate as a motor.
• the internal combustion engine 4 is additionally driven or assisted by the fan drive according to the invention, which is particularly advantageous when the internal combustion engine 4 is to be operated at maximum load.
• FIG. 2 shows the circuit diagram of a second embodiment of the fan drive according to the invention.
• He has the adjustable axial piston machine 1, which is driven via the shaft 2 from the engine 4.
• the axial piston machine 1 conveys pressure fluid from the tank T via the suction line 12, via the high-pressure line 14a, 14b and via a working line 115 to an adjustable fan motor 106, whose output shaft 8 drives the fan wheel 10.
• Low pressure side the pressure fluid from the fan motor 106 via another working line 117 and via the tank line 16a, 16b back to the tank T. It is between the high pressure line 14a, 14b and the working line 115 and between the working line 117 and the tank line 16a, 16b a Reversing valve 132 is arranged.
• It is designed as a 2/2-way valve that connects the high-pressure line 14b to the working line 115 and the working line 117 to the tank line 16a in its spring-biased basic position (0), while in its switching position (a) the high-pressure line 14b to the working line 117th and the working line 115 connects to the tank line 16a.
• a Speicherabsperrventil 122 is arranged, which is designed as a 2/2-way valve. It closes in a spring-biased basic position (0) the connecting line 18a, 18b, 19, while in a switching position (a) the connecting line 18a, 18b, 19 free and thus the high pressure line 14a, 14b connects to the hydraulic accumulator 20.
• an adjustable pressure relief valve 134 is arranged between the 2/2-way valve 122 and the hydraulic accumulator 20 branches off a line from the connecting line 18a, 18b, 19, in which an adjustable pressure relief valve 134 is arranged. It opens when a predetermined pressure in the hydraulic accumulator 20 is exceeded by a spring and thereby relieves the tank T. Between the high-pressure line 14a, 14b and the 2/2-way valve 122, a pressure sensor 140 is arranged.
• this has a control unit 136. It receives measurement signals from the pressure sensor 140 with respect to the pressure in the connection line 18a, 18b and thus also in the high-pressure line 14a, 14b.
• the control unit 136 sends actuating signals to the axial piston machine 1 and to the fan motor 106 with respect to their pivoting angle. Furthermore, the control unit 136 supplies the solenoids 132a, 122a of the reversing valve 132 and the 2/2-way valve 122 with actuating signals.
• the second embodiment of the fan drive according to the invention also allows adjustment of the fan power directly on the fan motor 106 by changing its pivot angle.
• FIG 3 shows the circuit diagram of a third embodiment of the fan drive according to the invention, this embodiment is substantially similar to that of Figure 2.
• the adjustable axial piston 1 instead of the adjustable axial piston 1, an adjustable axial piston pump 101 is provided, and that an adjustable fan motor 206 is also adjustable beyond its 0 ° position, so that in this third embodiment, a reversal of the direction of rotation Fan wheel 10 can be achieved with the above advantage, without the need for a reversing valve (see Figure 2) is necessary.
• a pressure sensor 241 is arranged, which is connected to the control unit 236. It is used inter alia to diagnose the pressure during an automatic emptying after starting a vehicle (ignition off), in which the fan drive according to the invention is arranged, or for calculating the current state of charge of the hydraulic accumulator 20 with the 2/2-way valve 122 closed.
• Fuel can also be saved for the internal combustion engine 4 in the third exemplary embodiment according to FIG. 3 since the energy stored in the hydraulic accumulator 20 can be used to drive the fan 10, 206 and this energy does not have to be applied by the internal combustion engine 4.
• the third embodiment further offers the possibility of integration without great safety precautions in an existing hydraulic fan drive, which is used for cooling a diesel engine of a bus. This can only be achieved because the stored energy in the hydraulic accumulator 20 is used to operate the fan 10, 206 and is not fed back into the drive train.
• V gJan of the likewise variable fan motor 106, 206 is adjusted so that the required speed ri fan desired is set via the moment-speed relationship of the fan wheel 10.
• the axial piston pump 101 and the fan motor 106, 206 are thus each torque-controlled.
• the fan motor 106, 206 may also be speed-controlled, for this purpose the speed sensor 38 according to FIG. 1 is necessary.
• the requirements of a decelerating torque can be carried out by a higher-level control, which takes into account the discharge of the accelerator pedal, the brake pedal and an operating point shift of the internal combustion engine 4.
• the fan controller provides information about the possible representable moments
• the exemplary embodiments according to FIGS. 1 and 2 have a fan shut-off valve 32 and an axial piston machine 1 whose pivoting angle can be changed via the 0 ° position.
• the axial piston machine according to FIG. 1 can be used as a motor to thereby start the internal combustion engine 4 or increase its maximum output.
• the fan check valve 32 of the first and second embodiments, the inversion valve 132 of the second embodiment, and the accumulator cutoff valve 122 of the second and third embodiments may be continuously adjustable. leads his. This spares the fan drive from pressure spikes and momentary surges.
• the constant fan motor 6 of the first exemplary embodiment can also be designed as an adjustable fan motor 106 according to FIG. 2 or as an adjustable swing-through fan motor 206 according to FIG.
• the latter variant of the fan motor 206 is only necessary if the fan 10 must be rotatable in both directions to blow out dirt.
• the speed of the fan 6, 106, 10 may also be controlled by the valve 32 when the pressure level in the conduit 14a is higher than that required by the fan 6, 106, 10.
• the valve 32 is either a flow control valve or a pressure reducing valve.
• a flow control valve directly controls the flow for the fan motor 6, 106.
• a pressure reducing valve controls the pressure level and thus the speed of the fan motor 6, 106, because there is a fixed relationship between the fan speed and the working pressure of the fan motor 6, 106.
• a certain fan speed requires a certain torque (i.e., pressure for the fan motor 6, 106). This relationship can be represented as a fan line in a coordinate system on one axis of which the fan speed and on the other axis of the fan torque are plotted.
• the setting of the valve 32 is determined by the controller 36.
• a hydrostatic fan drive for internal combustion engines with a primary unit that can be driven by the internal combustion engine, and with a fan motor with which a fan is driven.
• a hydraulic accumulator is arranged on a high-pressure line which connects the primary unit to the fan motor.
• Axial piston machine a Low pressure connection b High pressure connection

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• 2010
  • 2010-01-21 US US13/145,339 patent/US20120060777A1/en not_active Abandoned
  • 2010-01-21 WO PCT/DE2010/000068 patent/WO2010083816A1/de active Application Filing
  • 2010-01-21 CN CN201080005054.7A patent/CN102292528B/zh not_active Expired - Fee Related
  • 2010-01-21 DE DE102010005319A patent/DE102010005319A1/de not_active Withdrawn
  • 2010-01-21 JP JP2011546590A patent/JP5542844B2/ja not_active Expired - Fee Related
  • 2010-01-21 EP EP10706485A patent/EP2389503A1/de not_active Withdrawn

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