EP3273057B1 - Displacement unit and hydraulic start/stop system with such a displacement unit - Google Patents

Displacement unit and hydraulic start/stop system with such a displacement unit Download PDF

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Publication number
EP3273057B1
EP3273057B1 EP17172414.9A EP17172414A EP3273057B1 EP 3273057 B1 EP3273057 B1 EP 3273057B1 EP 17172414 A EP17172414 A EP 17172414A EP 3273057 B1 EP3273057 B1 EP 3273057B1
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EP
European Patent Office
Prior art keywords
displacement unit
fluid
engine
way valve
valve
Prior art date
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Application number
EP17172414.9A
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German (de)
French (fr)
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EP3273057A1 (en
Inventor
Patrick Wohlhauser
Lennard GEISSLER
Yannick WEIDNER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Liebherr Machines Bulle SA
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Liebherr Machines Bulle SA
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Publication of EP3273057A1 publication Critical patent/EP3273057A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
    • F02N7/06—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
    • F02N7/08—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1037—Flap valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1037—Flap valves
    • F04B53/1047—Flap valves the valve being formed by one or more flexible elements
    • F04B53/105—Flap valves the valve being formed by one or more flexible elements one flexible element oscillating around a fixed point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1002—Ball valves
    • F04B53/1017—Semi-spherical ball valves

Definitions

  • the present invention relates to a displacement unit and a hydraulic start-stop system with such a displacement unit.
  • the hydraulic drive system comprises a hydraulic pump whose delivery volume can be controlled or regulated, which is typically mechanically coupled to a primary drive designed as an internal combustion engine.
  • the internal combustion engine generally includes an electric starter for starting the internal combustion engine, which is fed by a battery. This battery is charged by a generator driven by the internal combustion engine.
  • the prior art provides a hydraulic start-stop system in which a displacement unit mechanically coupled to an internal combustion engine is not only controlled by the internal combustion engine in "pump operation”, but rather a start-up of the internal combustion engine by using the displacement unit in "motor operation". If hydraulic power is required for the working hydraulics, the displacement unit is driven with the aid of the mechanical coupling to the internal combustion engine and sucks in a fluid, typically an oil or the like, from a fluid reservoir and passes this on to the working hydraulics on the high pressure side. This enables the working hydraulics, for example, to move an excavator arm or to lift the blade of a caterpillar.
  • a fluid typically an oil or the like
  • a stopped internal combustion engine is started with the aid of the displacement unit.
  • a branching line is connected to the inlet opening of the displacement unit, which feeds a fluid in the direction of its engine, which can convert hydraulic power into rotary power, which is connected at one of its ends to a fluid reservoir via a one-way valve and to which other of its ends is connected to a pressure accumulator via a switchable valve.
  • the pressure accumulator has a sufficient amount of fluid under pressure, this fluid can be used to start a stationary internal combustion engine.
  • the lockable valve arranged in the path between the pressure accumulator and the engine of the displacement unit is opened in order to allow the pressurized fluid to flow into the displacement unit.
  • JP2007056810A and JPH10252642A disclose displacement units according to the preamble of claim 1.
  • the aim of the present invention is to advantageously develop a displacement unit suitable for the hydraulic start-stop system.
  • the displacement unit according to the invention which can in particular represent an axial piston machine, comprises a housing, a drive unit for converting the rotary power into hydraulic power and a suction connection for supplying a fluid to the drive unit.
  • the displacement unit is characterized by a one-way valve which is arranged in the housing of the displacement unit.
  • the arrangement of the one-way valve in the housing of the displacement unit leads to a reduction in the flow resistance between the hydraulic oil storage tank (also: fluid reservoir) and the drive mechanism of the displacement unit, which operates in pump mode.
  • a lower overall flow resistance ensures a higher suction limit speed, which characterizes an operating state of a pump in which a suction stroke is due to the formation of a vacuum and a filling deficiency occurs, which can lead to a reduction in the flow rate of the pump and damage to the pump due to cavitation erosion in the subsequent delivery stroke.
  • For a high suction limit speed it is advantageous to keep the flow resistance as low as possible.
  • the total flow resistance between the hydraulic oil storage tank (also: fluid reservoir) and the engine of the displacement unit results from the supply line from the storage tank to the one-way valve and the supply line from the one-way valve to the engine, the total flow resistance decreases when the section with the highest flow resistance, the Area around the one-way valve, located near the engine.
  • the reason for this is that the cross-section of the intake duct typically decreases in size from the suction connection of the displacement unit to the engine. With a constant pressure drop (or flow resistance), the flow cross-section of the check valve can then be made smaller, the closer it is to the engine.
  • a geometrically smaller check valve can be implemented more cost-effectively and requires less installation space. Therefore, in addition to the check valves (also: one-way valves) typically arranged outside the housing of the displacement unit in the prior art, the positive effects listed above can be achieved.
  • the displacement unit when used as a motor, there is a high pressure level of the fluid between the engine and the one-way valve. It follows that the oil connection between these two components must be high-pressure-tight. If the one-way valve were arranged outside the housing of the displacement unit, the corresponding hydraulic hose would have to withstand the high pressure load. According to the displacement unit according to the invention, in which the one-way valve is arranged in the housing itself, a hydraulic hose led to the suction connection of the displacement unit only has to be able to withstand the low pressure.
  • the one-way valve is arranged in the flow path between the suction connection and the engine.
  • the one-way valve is preferably integrated in the housing of the displacement unit.
  • the one-way valve prefferably be arranged in an intake duct of a connection plate of the displacement unit or to interact with the connection plate.
  • the cross-section of the flow path from the suction connection in the direction of the engine is reduced; this reduction preferably takes place continuously and the one-way valve is arranged at a position in the flow path where the cross-section of the flow channel is not at its maximum.
  • the one-way valve is preferably arranged in the flow path at a distance from the suction connection in the direction of the engine.
  • the one-way valve is designed to allow the fluid to flow only in the direction of the engine and to minimize or prevent a flow of the fluid in the opposite direction.
  • the one-way valve is a check valve or a slide valve, preferably a slide valve that can be actuated at high pressure.
  • the displacement unit further comprises a second connection for supplying a fluid to the engine, the flow paths emanating from the first suction connection and the second connection merging to form a common flow path and the one-way valve being arranged in the area between the first suction connection and the combined common flow path .
  • the displacement unit is particularly suitable for use in a hydraulic start-stop system.
  • the pump operation not the pump operation but the motor operation is used to start an internal combustion engine that is mechanically coupled to the displacement unit.
  • a fluid stored under pressure in a pressure accumulator is fed to the engine.
  • the one-way valve is provided in order to prevent the pressurized fluid from flowing into the storage tank. The inflow of a fluid at the second connection and the outflow from the first suction connection are therefore not possible.
  • the one-way valve is flow-optimized and interacts with a flow-optimized valve seat.
  • a flow-optimized one-way valve and a flow-optimized valve seat minimize the formation of eddies in the event of a fluid inflow along a fluid passage opening at the suction connection.
  • the flow path that can be closed by the one-way valve is preferably a Venturi contour that can be closed by the one-way valve at the point of the smallest flow cross-section in the region of the valve.
  • the Venturi contour has an optimized curve in order to minimize the formation of eddies in a fluid flowing through the one-way valve.
  • the suction connection can preferably be connected to a flange plate, which is designed as part of a Venturi contour formed with the flow path of the suction connection.
  • the invention also relates to a hydraulic start-stop system which comprises a displacement unit according to one of the variants presented above.
  • the hydraulic start-stop system further comprises an internal combustion engine which is mechanically coupled to the displacement unit and is designed to drive the displacement unit and to be driven by the displacement unit, and a pressure accumulator which is connected to an outlet connection of the displacement unit and to a second Connection for supplying a fluid is connected to the engine of the displacement unit, wherein the first suction connection is connected to a fluid reservoir.
  • an internal combustion engine which is mechanically coupled to the displacement unit and is designed to drive the displacement unit and to be driven by the displacement unit
  • a pressure accumulator which is connected to an outlet connection of the displacement unit and to a second Connection for supplying a fluid is connected to the engine of the displacement unit, wherein the first suction connection is connected to a fluid reservoir.
  • a pressurized fluid in the fluid reservoir is used to start an internal combustion engine in which a fluid flowing from the fluid reservoir drives the displacement unit and via the mechanical coupling between the displacement unit and internal combustion engine exerts a starting movement for the internal combustion engine, with a first valve between the fluid reservoir and the second connection and a second valve between the outlet connection and a connection to the fluid reservoir being preferably provided for guiding the fluid.
  • the present invention also relates to a mobile work machine, in particular a mobile excavator, a crawler excavator, a mobile crane, with a hydraulic start-stop system according to one of the variants described above.
  • Fig. 1 shows a schematic representation of a displacement unit according to the invention, for example an axial piston machine, in which the section around a suction connection 4 of the displacement unit 1 is detailed.
  • a check valve 3 is arranged in the housing 2 of the displacement unit 1.
  • a fluid flows through the suction connection 4 into the interior of the displacement unit 1, that is to say is sucked in by the engine (not shown).
  • the engine is driven via a mechanical coupling with an internal combustion engine, not shown. Due to the suction effect of the engine, the check valve 3 moves into its open position and enables a flow connection between a supply reservoir and the engine.
  • Fig. 2 shows an enlarged view of the displacement unit 1 in the area of the suction connection 4.
  • the housing 2 has a suction connection 4 and a second connection 7, both of which are designed to guide a fluid in the direction of the drive mechanism of the displacement unit 1.
  • the inflow of a fluid into the second connection 7 and outflow out of the suction connection 4 is prevented by the check valve 3. Therefore, a fluid flowing into the second connection 7 is fed to the engine of the displacement unit 1.
  • the flow path of the suction connection 4 and the flow path of the second connection 7 combine downstream to form a common flow path 8, via which a flow connection to the engine is established.
  • the check valve 3 is displaceably mounted in a recess, so that when the pressure of the check comes from the direction of the engine or the second connection 7, it changes into a closed position. However, if suction pressure is exerted on the check valve 3 due to the movement of the engine, it moves away from its closed position into its open position and a fluid can flow through the suction connection 4 and the fluid flow bores 13 in the direction of the engine. It can also be seen that a flange plate 6 is arranged on the housing 2 of the displacement unit, which flange plate has an intake channel 5. It can be seen that the intake channel 5 reduces its flow cross-section towards the position that can be closed by the check valve.
  • the intake channel 5 is provided with a fluid reservoir or connected to a storage tank of fluid.
  • a flow from the storage tank through the check valve 3 in the direction of the engine then takes place during pump operation of the displacement unit 1.
  • the displacement unit 1 is used to start an internal combustion engine or to assist with a starting process
  • a fluid under high pressure is transferred to the second connection 7 and the displacement unit used in engine operation.
  • the check valve 3 is forced into its closing position by the fluid flowing in at the second connection 7 in order to prevent the fluid from flowing into the storage tank. Instead, it flows in the direction of the engine, where it causes the engine to move, which in turn converts the output shaft of the internal combustion engine, which is mechanically fixed to the engine, into a starting movement.
  • Fig. 3 shows a flow-optimized representation of the check valve 3 and a flow-optimized valve seat 9.
  • the flow-optimized check valve 3 can be seen on the beveled surface of the valve piston 16. This comes into contact with the valve seat 9 with the wall of a flow path in such a way that a seal for the fluid occurs.
  • the flow path is provided with an optimized Venturi contour shape, which increases the flow rate and reduces the formation of eddies and thus reduces the flow resistance.
  • This Venturi contour shape is only interrupted at the valve seat in order to obtain a satisfactory sealing effect when the check valve 3 is closed.
  • Another O-ring 14 is also arranged circumferentially in the flow path between the Venturi contour shape protruding into the housing 2.
  • Fig. 4 shows an enlarged section Fig. 3 in the area of a valve seat 9. This shows the optimized, beveled contour of the Venturi shape 17, 18, which forms a seal when the valve piston 16 is placed on the valve seat 9 closes.
  • the element shown with the reference numeral 19 corresponds to an undercut.
  • Fig. 5 is a schematic representation of the hydraulic start-stop system 30.
  • An internal combustion engine 31 can be seen, which is coupled to the engine 39 of the displacement unit 1 via a mechanical coupling 35.
  • the one-way valve 3, here a check valve which is characteristic of the invention and is arranged within the housing 2 of the displacement unit 1.
  • the displacement unit 1 is connected to a fluid reservoir 34 at its suction connection 4. This fluid reservoir 34 serves as a storage tank for the fluid.
  • the displacement unit 1 has a second connection 7 which is designed to guide a fluid in the direction of the engine 39.
  • the second connection 7 is connected to a pressure accumulator 32 via a first valve 36.
  • the fluid reservoir 32 is designed to receive a fluid under a high pressure and to store it in itself.
  • the working hydraulics are connected to the outlet connection 33 of the displacement unit 1.
  • a second valve 37 and a third valve 38 are connected to the outlet connection 33.
  • the third valve 38 can close or open a flow path between the outlet port 33 and the fluid reservoir 34.
  • the second valve 37 can close or open a connection to the pressure accumulator 32.
  • Fig. 5 The system shown is explained on the basis of the various operating states that the system can assume.
  • a first operating state the working hydraulics are supplied with fluid.
  • the valves 38, 37 and 36 are in a closed state.
  • the displacement unit 1 is driven by the diesel engine 31.
  • the displacement unit 1 sucks in the working fluid, for example a hydraulic oil, via the check valve 3.
  • the check valve 3 is designed in such a way that this results in the lowest possible pressure drop along the flow direction.
  • the suction pressure must not fall below a certain level. As a result there is a line limitation by the suction pressure.
  • the displacement unit 1 conveys the fluid to the valve slide located in the working hydraulics.
  • the displacement unit 1 is subjected to a load-sensing control which ensures that the displacement unit 1 adapts the delivery volume flow in accordance with a volume flow requirement. In an axial piston machine, this is done by adjusting the helix angle.
  • FIG. 5 Another operating state of the Figure 5
  • the system shown loads the pressure accumulator 32.
  • the valves 38 and 36 are closed.
  • the valve 37 is in its open position.
  • the pressure accumulator 32 which can also be designed as a hydraulic accumulator, the fluid conveyed by the displacement unit 1 is conveyed into the pressure accumulator 32.
  • Starting the diesel engine can be seen as a further operating state. In order to be able to start the diesel engine, it must be in a stopped state. Then all valves 36, 37 and 38 are to be closed. Furthermore, when the diesel engine 31 is switched off, the hydraulic pressure accumulator 32 must be sufficiently charged in order to be able to meet a start request. To initiate the starting process, the valves 36 and 38 are opened, whereas the valve 37 remains closed. The pressurized fluid arrives from the pressure accumulator 32 via the second connection 7 to the suction channel of the displacement unit 1. The check valve 3 closes the connection between the pressure accumulator 32 and the fluid collection tank 34 according to the pressure ratio there. The intake channel 7 of the displacement unit 1 is thus under pressure and the displacement unit 1 operates by a motor.
  • the drive train is accelerated, as a result of which the starting speed of the motor is exceeded, as a result of which the started motor is dragged up to its operating speed immediately afterwards. Since the valve 38 is open, the fluid from the working connection 33 of the displacement unit 1 returns to the collecting tank 34. During this starting process, the working hydraulics cannot be supplied with hydraulic power.
  • the hydraulic start-stop system described above is particularly suitable for use in a mobile work machine. It is possible here for the working machine to drive one or more hydraulic displacement units on the internal combustion engine, possibly via a pump transfer gear. It is possible that the output of the internal combustion engine is converted into hydraulic power by means of an adjustable displacement unit. It should be noted that the at least one displacement unit is always mechanically connected to the internal combustion engine. Furthermore, it can be provided that the at least one displacement unit controls the working hydraulics of the mobile working machine, e.g. supplies an arm cylinder, a bucket cylinder, a boom cylinder and a traction drive. Typical applications would be mobile excavators, crawler excavators, mobile cranes, etc.
  • the hydraulic start-stop functionality should preferably only be used when the operating temperature of the drive system has been reached, i. H.
  • the primary drive should only be switched off when the operating temperature, in particular that of the engine oil, is reached. In a mobile work machine, this affects not only the operating temperature of the internal combustion engine, but also the hydraulic oil.
  • the dragging up of the internal combustion engine required for starting should preferably always take place with the hydraulic system, both for a cold start and for a warm start. In order for the latter to be possible, the internal combustion engine should only then be switched off and, if necessary, delayed until the hydraulic pressure accumulator is fully charged. There are two exceptions, the first being the detection of an emergency stop and the second being the detection of a leak in the pressure accumulator and the hydraulic line that is only used for accumulator operation.
  • the internal combustion engine should not only be switched off when the pressure accumulator is already fully charged, but rather which are taken into account due to the rotating masses in the drive system (flywheel, gearwheels in the pump distributor gear) and the energy that can be taken from it is fed to the pressure accumulator instead of continuing to charge it with continued fuel consumption.
  • the rotational energy present on the flywheel of the internal combustion engine or a separate speed sensor is used to determine the rotational energy that is still present.
  • the hydraulic oil temperature in the pressure accumulator and the pressure in the pressure accumulator are measured and taken into account. These three variables are read into a control unit. From this, the point in time is determined at which there is sufficient rotational energy to fully charge the pressure accumulator, taking into account the losses.
  • the requested shutdown of the internal combustion engine is enabled. The calculation is based on a map stored in the control unit with the input variables: speed, oil temperature, pressure level in the memory. This results in the energy that can be fed to the storage unit until the drive comes to a standstill. The characteristic is defined for each drive configuration by the results of functional tests.
  • the hydraulic start-stop system can also support the electrical starting process.
  • Applying torque to the drive train with the aid of the displacement unit is particularly advantageous if - based on the design of the internal combustion engine as a diesel engine, it is accelerated to at least its starting speed and advantageously to its working speed in the range from 1200 min -1 to 2200 min -1 , preferably from 1400 min -1 to 1900 min -1, particularly preferably to 1500 min -1 to 1800 min -1 .
  • An application of torque to the drive train with the aid of the displacement unit of an internal combustion engine operated in downspeeding mode can also be carried out to at least its starting speed.
  • an operating speed in the range from 1200 min -1 to 1500 min -1 is preferred. If the speed were to be reduced further, the hydraulic pumps required to convert mechanical power into hydraulic power would have a correspondingly large design. That would be uneconomical.
  • the output torque is almost proportional to the swivel angle of the swash plate of an axial piston machine at a quasi constant high pressure.
  • a hydraulic accumulator in particular a bladder accumulator or a piston accumulator, can be used as the pressure accumulator.
  • the maximum pressure level in the pressure accumulator is between 100 and 450 bar, preferably 150 to 300 bar and especially 200 bar.
  • the pressure accumulator can be charged directly via a displacement unit coupled to the internal combustion engine on the power take-off with a fixed ratio.
  • the displacement unit charging the pressure accumulator can also be located on the primary side of the pump distributor gear.
  • the displacement unit charging the pressure accumulator can also be located on the secondary side of the pump transfer case.
  • the displacement unit charging the pressure accumulator can be provided exclusively for charging the pressure accumulator.
  • the displacement unit charging the pressure accumulator can be provided for charging the pressure accumulator and for operating at least one secondary consumer. In this case it is possible that the displacement unit in question a) only charges the pressure accumulator, b) is only used to operate the at least one auxiliary consumer or c) supplies the pressure accumulator and at least one auxiliary consumer at the same time in a certain time interval.
  • the displacement unit charging the pressure accumulator can be provided for charging the pressure accumulator and for the operation of at least one main consumer, e.g. B. the drive.
  • the displacement unit in question a) only charges the pressure accumulator, b) is only used to operate the at least one main consumer or c) supplies the pressure accumulator and at least one main consumer at the same time.
  • the displacement unit charging the pressure accumulator can be identical to the displacement unit which is dragging up to start the internal combustion engine.
  • the displacement unit charging the pressure accumulator can be different from the displacement unit which takes over the dragging of the internal combustion engine when it is started.
  • Delay-free starting of the internal combustion engine immediately after a torque request or a work request by the driver requires a high torque in order to accelerate the drive train in a short time.
  • a hydraulic starting process of the intended system or the availability of a work function of the mobile work machine is faster than with today's electrical starting systems.
  • the primary function is the translational movement of the mobile work machine and the actuation of the work hydraulics.
  • the secondary functions such as (e.g. operating the air conditioning system, the lighting), which still have to be fulfilled by secondary consumers during stop operation, should preferably be fed from the conventional on-board network.
  • the invention enables an increase in comfort and safety through temporarily lower noise pollution at the place of use while the internal combustion engine is switched off.
  • the loading of the accumulator is also possible through recuperation z. B. possible during braking.
  • the storage tank can also be loaded by increasing the load point.
  • the target output power of the internal combustion engine is deliberately chosen to be higher than the required drive power.
  • the pressure accumulator is charged with the "excess" power.
  • a lowering of the load point is also conceivable.
  • the power output of the internal combustion engine is then reduced for a short time.
  • the "power deficit" required to supply the consumer is taken from the pressure accumulator.
  • the invention also enables an active boost for a brief power increase made available to the drive. Protection against stalling the internal combustion engine can also be obtained in this way.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Die vorliegende Erfindung betrifft eine Verdrängereinheit sowie ein hydraulisches Start-Stopp-System mit einer solchen Verdrängereinheit.The present invention relates to a displacement unit and a hydraulic start-stop system with such a displacement unit.

Es ist bekannt, dass mobile Arbeitsmaschinen hydraulische Vorrichtungen aufweisen und diese zum Ausführen einer Arbeitstätigkeit genutzt werden können. Dabei umfasst das hydraulische Antriebssystem eine vorzugsweise im Fördervolumen steuerbare bzw. regelbare Hydraulikpumpe, die typischerweise mit einem als Brennkraftmaschine ausgebildeten Primärantrieb mechanisch gekoppelt ist. Die Brennkraftmaschine umfasst dabei in der Regel einen Elektrostarter zum Starten der Brennkraftmaschine, der durch eine Batterie gespeist wird. Diese Batterie wird dabei durch einen von der Brennkraftmaschine angetriebenen Generator geladen.It is known that mobile work machines have hydraulic devices and these can be used to carry out a work activity. In this case, the hydraulic drive system comprises a hydraulic pump whose delivery volume can be controlled or regulated, which is typically mechanically coupled to a primary drive designed as an internal combustion engine. The internal combustion engine generally includes an electric starter for starting the internal combustion engine, which is fed by a battery. This battery is charged by a generator driven by the internal combustion engine.

Im Stand der Technik ist es bekannt, eine Brennkraftmaschine, insbesondere einen Dieselmotor, durch elektrische Starteranlagen, durch elektrische Startergeneratoren, die eine Vereinigung von Starteranlage und Generator in einem Bauteil darstellen, und durch hydraulische Start-Stopp-Systeme anzulassen. Bei einem Anlassvorgang einer Brennkraftmaschine ist es erforderlich, deren Ausgangswelle rotieren zu lassen, um die Arbeitstakte eines in der Brennkraftmaschine angeordneten Kolbens auszuführen.In the prior art it is known to start an internal combustion engine, in particular a diesel engine, by means of electrical starter systems, by means of electrical starter-generators, which represent a combination of starter system and generator in one component, and by means of hydraulic start-stop systems. During a starting process an internal combustion engine, it is necessary to let its output shaft rotate in order to execute the work cycles of a piston arranged in the internal combustion engine.

Der Stand der Technik sieht hierzu ein hydraulisches Start-Stopp-System vor, bei dem eine mechanisch mit einer Brennkraftmaschine gekoppelte Verdrängereinheit nicht nur durch die Brennkraftmaschine im "Pumpenbetrieb" angesteuert wird, sondern ein Anlassen der Brennkraftmaschine durch Nutzung der Verdrängereinheit im "Motorenbetrieb". Wird für die Arbeitshydraulik hydraulische Leistung benötigt, wird die Verdrängereinheit mit Hilfe der mechanischen Kopplung zu der Brennkraftmaschine angetrieben und saugt aus einem Fluidreservoir ein Fluid, typischerweise ein Öl oder dergleichen, an und gibt dies auf der Hochdruckseite an die Arbeitshydraulik weiter. Dadurch ist es der Arbeitshydraulik beispielsweise möglich, einen Baggerarm zu verfahren oder das Schild einer Raupe anzuheben.The prior art provides a hydraulic start-stop system in which a displacement unit mechanically coupled to an internal combustion engine is not only controlled by the internal combustion engine in "pump operation", but rather a start-up of the internal combustion engine by using the displacement unit in "motor operation". If hydraulic power is required for the working hydraulics, the displacement unit is driven with the aid of the mechanical coupling to the internal combustion engine and sucks in a fluid, typically an oil or the like, from a fluid reservoir and passes this on to the working hydraulics on the high pressure side. This enables the working hydraulics, for example, to move an excavator arm or to lift the blade of a caterpillar.

Im "Motorbetrieb" ist vorgesehen, dass eine gestoppte Brennkraftmaschine mit Hilfe der Verdrängereinheit angelassen wird. Dazu wird an die Einlassöffnung der Verdrängereinheit, die ein Fluid in Richtung ihres Triebwerks, das eine hydraulische Leistung in eine rotatorische Leistung wandeln kann, eine sich aufzweigende Leitung angeschlossen, die an einem ihrer Enden mit einem Fluidreservoir über ein Einwegventil in Verbindung steht und mit dem anderen ihrer Enden über ein schaltbares Ventil mit einem Druckspeicher in Verbindung steht. Weist der Druckspeicher eine ausreichende Menge an unter Druck stehendem Fluid auf, so kann dieses Fluid dazu genutzt werden, eine stillstehende Brennkraftmaschine anzulassen. Dazu wird das im Pfad zwischen dem Druckspeicher und dem Triebwerk der Verdrängereinheit angeordnete absperrbare Ventil geöffnet, um ein Einströmen des unter Druck stehenden Fluids in die Verdrängereinheit zu ermöglichen.In "engine operation" it is provided that a stopped internal combustion engine is started with the aid of the displacement unit. For this purpose, a branching line is connected to the inlet opening of the displacement unit, which feeds a fluid in the direction of its engine, which can convert hydraulic power into rotary power, which is connected at one of its ends to a fluid reservoir via a one-way valve and to which other of its ends is connected to a pressure accumulator via a switchable valve. If the pressure accumulator has a sufficient amount of fluid under pressure, this fluid can be used to start a stationary internal combustion engine. For this purpose, the lockable valve arranged in the path between the pressure accumulator and the engine of the displacement unit is opened in order to allow the pressurized fluid to flow into the displacement unit.

Erreicht das unter Druck stehende Fluid das Triebwerk, führt dies zu einer Rotation der mit der Verdrängereinheit gekoppelten Ausgangswelle der Brennkraftmaschine. Diese beim Anlassen einer Brennkraftmaschine notwendige Rotation der Ausgangswelle ersetzt dabei die typische Tätigkeit einer elektrischen Starter-Anlage.If the pressurized fluid reaches the engine, this leads to a rotation of the output shaft of the internal combustion engine, which is coupled to the displacement unit. This rotation of the output shaft, which is necessary when starting an internal combustion engine, replaces the typical activity of an electrical starter system.

JP2007056810A und JPH10252642A offenbaren Verdrängereinheiten nach dem Oberbegriff des Anspruchs 1. Es ist das Ziel der vorliegenden Erfindung eine für das hydraulische Start-Stopp-System geeignete Verdrängereinheit in vorteilhafter Weise weiterzubilden. JP2007056810A and JPH10252642A disclose displacement units according to the preamble of claim 1. The aim of the present invention is to advantageously develop a displacement unit suitable for the hydraulic start-stop system.

Die erfindungemäße Verdrängereinheit, die insbesondere eine Axialkolbenmaschine darstellen kann, umfasst ein Gehäuse, ein Triebwerk zum Wandeln der rotatorischen Leistung in eine hydraulische Leistung und einen Sauganschluss zum Zuführen eines Fluids an das Triebwerk. Die Verdrängereinheit ist durch ein Einwegventil gekennzeichnet, das im Gehäuse der Verdrängereinheit angeordnet ist.The displacement unit according to the invention, which can in particular represent an axial piston machine, comprises a housing, a drive unit for converting the rotary power into hydraulic power and a suction connection for supplying a fluid to the drive unit. The displacement unit is characterized by a one-way valve which is arranged in the housing of the displacement unit.

Die Anordnung des Einwegventils in dem Gehäuse der Verdrängereinheit führt zu einer Verringerung des Strömungswiderstands zwischen dem Hydrauliköl-Vorratstank (auch: Fluidreservoir) und dem im Pumpenbetrieb arbeitenden Triebwerk der Verdrängereinheit. Ein niedrigerer Gesamtströmungswiderstand sorgt für eine höhere Sauggrenzdrehzahl, die einen Betriebszustand einer Pumpe charakterisiert, bei dem in einem Saughub aufgrund einer Vakuumbildung ein Füllungsmangel auftritt, der zu einer Verminderung des Förderstroms der Pumpe und zu einer Schädigung der Pumpe durch Kavitationserosion im anschließenden Förderhub führen kann. Für eine hohe Sauggrenzdrehzahl ist es von Vorteil, den Strömungswiderstand möglichst gering zu halten.The arrangement of the one-way valve in the housing of the displacement unit leads to a reduction in the flow resistance between the hydraulic oil storage tank (also: fluid reservoir) and the drive mechanism of the displacement unit, which operates in pump mode. A lower overall flow resistance ensures a higher suction limit speed, which characterizes an operating state of a pump in which a suction stroke is due to the formation of a vacuum and a filling deficiency occurs, which can lead to a reduction in the flow rate of the pump and damage to the pump due to cavitation erosion in the subsequent delivery stroke. For a high suction limit speed, it is advantageous to keep the flow resistance as low as possible.

Da sich der Gesamtströmungswiderstand zwischen dem Hydrauliköl-Vorratstank (auch: Fluidreservoir) und dem Triebwerk der Verdrängereinheit aus der Zuleitung vom Vorratstank bis zum Einwegventil und der Zuleitung vom Einwegventil bis zum Triebwerk ergibt, sinkt der Gesamtströmungswiderstand, wenn sich der Abschnitt des höchsten Strömungswiderstands, der Bereich um das Einwegventil, in der Nähe des Triebwerks angeordnet ist. Dies ist darin begründet, da sich der Querschnitt des Ansaugkanals vom Sauganschluss der Verdrängereinheit zum Triebwerk hin typischerweise verkleinert. Es kann dann bei gleichbleibendem Druckabfall (bzw. Strömungswiderstand) der Durchlassquerschnitt des Rückschlagventils umso kleiner ausgeführt werden, je näher sich dieses am Triebwerk befindet. Zudem ist ein geometrisch kleiner ausgeführtes Rückschlagventil kostengünstiger zu realisieren und erfordert weniger Einbauraum. Daher lassen sich zu dem im Stand der Technik typischerweise außerhalb des Gehäuses der Verdrängereinheit angeordneten Rückschlagventile (auch: Einwegventile) die vorstehend aufgeführten positiven Effekte erreichen.Since the total flow resistance between the hydraulic oil storage tank (also: fluid reservoir) and the engine of the displacement unit results from the supply line from the storage tank to the one-way valve and the supply line from the one-way valve to the engine, the total flow resistance decreases when the section with the highest flow resistance, the Area around the one-way valve, located near the engine. The reason for this is that the cross-section of the intake duct typically decreases in size from the suction connection of the displacement unit to the engine. With a constant pressure drop (or flow resistance), the flow cross-section of the check valve can then be made smaller, the closer it is to the engine. In addition, a geometrically smaller check valve can be implemented more cost-effectively and requires less installation space. Therefore, in addition to the check valves (also: one-way valves) typically arranged outside the housing of the displacement unit in the prior art, the positive effects listed above can be achieved.

Darüber hinaus liegt bei einer motorischen Nutzung der Verdrängereinheit zwischen dem Triebwerk und dem zum Einwegventil ein Hochdruckniveau des Fluids vor. Hieraus folgt, dass die Ölverbindung zwischen diesen beiden Bauteilen hochdruckdicht sein muss. Wäre das Einwegventil außerhalb des Gehäuses der Verdrängereinheit angeordnet, müsste der entsprechende Hydraulikschlauch die Hochdruckbelastung aushalten. Nach der erfindungsgemäßen Verdrängereinheit, bei der das Einwegventil im Gehäuse selbst angeordnet ist, muss ein an den Sauganschluss der Verdrängereinheit geführter Hydraulikschlauch lediglich den Niederdruck aushalten können.In addition, when the displacement unit is used as a motor, there is a high pressure level of the fluid between the engine and the one-way valve. It follows that the oil connection between these two components must be high-pressure-tight. If the one-way valve were arranged outside the housing of the displacement unit, the corresponding hydraulic hose would have to withstand the high pressure load. According to the displacement unit according to the invention, in which the one-way valve is arranged in the housing itself, a hydraulic hose led to the suction connection of the displacement unit only has to be able to withstand the low pressure.

Nach einer optionalen Modifikation der Erfindung ist das Einwegventil im Strömungspfad zwischen Sauganschluss und Triebwerk angeordnet.According to an optional modification of the invention, the one-way valve is arranged in the flow path between the suction connection and the engine.

Vorzugsweise ist das Einwegventil im Gehäuse der Verdrängereinheit integriert.The one-way valve is preferably integrated in the housing of the displacement unit.

Nach einer weiteren Modifikation der Erfindung ist es möglich, dass das Einwegventil in einem Ansaugkanal einer Anschlussplatte der Verdrängereinheit angeordnet ist oder mit der Anschlussplatte zusammenwirkt.According to a further modification of the invention, it is possible for the one-way valve to be arranged in an intake duct of a connection plate of the displacement unit or to interact with the connection plate.

Nach einer bevorzugten Variation der Erfindung verkleinert sich der Querschnitt des Strömungspfads vom Sauganschluss in Richtung Triebwerk, vorzugsweise erfolgt diese Verkleinerung kontinuierlich und das Einwegventil ist an einer Position in dem Strömungspfad angeordnet, an dem der Querschnitt des Strömungskanals nicht maximal ist.According to a preferred variation of the invention, the cross-section of the flow path from the suction connection in the direction of the engine is reduced; this reduction preferably takes place continuously and the one-way valve is arranged at a position in the flow path where the cross-section of the flow channel is not at its maximum.

Vorzugsweise ist das Einwegventil im Strömungspfad vom Sauganschluss beabstandet in Richtung Triebwerk angeordnet.The one-way valve is preferably arranged in the flow path at a distance from the suction connection in the direction of the engine.

Nach einer optionalen Modifikation der Erfindung ist das Einwegventil dazu ausgelegt, das Fluid nur in Richtung Triebwerk strömen zu lassen und eine Strömung des Fluids in entgegengesetzte Richtung zu minimieren oder zu unterbinden.According to an optional modification of the invention, the one-way valve is designed to allow the fluid to flow only in the direction of the engine and to minimize or prevent a flow of the fluid in the opposite direction.

Nach einer Fortbildung der Erfindung ist das Einwegventil ein Rückschlagventil oder ein Schieberventil, vorzugsweise ein hochdruckbetätigbares Schieberventil.According to a further development of the invention, the one-way valve is a check valve or a slide valve, preferably a slide valve that can be actuated at high pressure.

Gemäß der Erfindung umfasst die Verdrängereinheit ferner einen zweiten Anschluss zum Zuführen eines Fluids an das Triebwerk, wobei die vom ersten Sauganschluss und vom zweiten Anschluss ausgehenden Strömungspfade sich zu einem gemeinsamen Strömungspfad vereinigen und das Einwegventil im Bereich zwischen erstem Sauganschluss und dem vereinigten gemeinsamen Strömungspfad angeordnet ist.According to the invention, the displacement unit further comprises a second connection for supplying a fluid to the engine, the flow paths emanating from the first suction connection and the second connection merging to form a common flow path and the one-way valve being arranged in the area between the first suction connection and the combined common flow path .

Durch das Vorsehen des zweiten Anschlusses zum Zuführen eines Fluids an das Triebwerk eignet sich die Verdrängereinheit besonders für den Einsatz in einem hydraulischen Start-Stopp-System. Wie bereits im einleitenden Teil der Beschreibung erläutert, wird für ein Anlassen einer mit der Verdrängereinheit mechanisch gekoppelten Brennkraftmaschine nicht der Pumpenbetrieb sondern der Motorbertrieb verwendet. Dafür wird ein in einem Druckspeicher unter Druck gespeichertes Fluid dem Triebwerk zugeführt. Um ein Strömen des unter Druck stehenden Fluids in den Vorratstank zu unterbinden ist das Einwegventil vorgesehen. Das Einströmen eines Fluids an dem zweiten Anschluss und das Ausströmen aus dem ersten Sauganschluss ist damit nicht möglich.By providing the second connection for supplying a fluid to the engine, the displacement unit is particularly suitable for use in a hydraulic start-stop system. As already explained in the introductory part of the description, not the pump operation but the motor operation is used to start an internal combustion engine that is mechanically coupled to the displacement unit. For this purpose, a fluid stored under pressure in a pressure accumulator is fed to the engine. In order to prevent the pressurized fluid from flowing into the storage tank, the one-way valve is provided. The inflow of a fluid at the second connection and the outflow from the first suction connection are therefore not possible.

Nach einer bevorzugten Ausführungsform der Erfindung ist das Einwegventil strömungsoptimiert und wirkt mit einem strömungsoptimierten Ventilsitz zusammen. Ein strömungsoptimiertes Einwegventil sowie ein strömungsoptimierter Ventilsitz minimieren die Wirbelbildung bei einer Fluideinströmung entlang einer Fluiddurchtrittsöffnung an dem Sauganschluss.According to a preferred embodiment of the invention, the one-way valve is flow-optimized and interacts with a flow-optimized valve seat. A flow-optimized one-way valve and a flow-optimized valve seat minimize the formation of eddies in the event of a fluid inflow along a fluid passage opening at the suction connection.

Vorzugsweise ist der durch das Einwegventil verschließbare Strömungspfad eine Venturi-Kontur, die durch das Einwegventil im Punkt eines geringsten Strömungsquerschnitts im Bereich des Ventils verschließbar ist.The flow path that can be closed by the one-way valve is preferably a Venturi contour that can be closed by the one-way valve at the point of the smallest flow cross-section in the region of the valve.

Beim Einströmen des Fluids, z.B. einem Hydrauliköl, in die im Pumpenbetrieb arbeitende Verdrängereinheit erreicht man an dem Punkt des geringsten Strömungsquerschnitts die maximale Strömungsgeschwindigkeit, was einen für den Pumpenbetrieb unterstützenden Saugeffekt hervorruft.When the fluid flows in, e.g. a hydraulic oil, into the displacement unit working in pump mode, the maximum flow speed is reached at the point of the smallest flow cross-section, which causes a suction effect that supports the pump operation.

Nach einer weiteren Fortbildung der Erfindung weist die Venturi-Kontur einen optimierten Krümmungsverlauf auf, um eine Wirbelbildung eines durch das Einwegventil strömenden Fluids zu minimieren.According to a further development of the invention, the Venturi contour has an optimized curve in order to minimize the formation of eddies in a fluid flowing through the one-way valve.

Vorzugsweise ist der Sauganschluss mit einer Flanschplatte verbindbar, die als ein Teil einer mit dem Strömungspfad des Sauganschlusses gebildeten Venturi-Kontur ausgeführt ist.The suction connection can preferably be connected to a flange plate, which is designed as part of a Venturi contour formed with the flow path of the suction connection.

Die Erfindung betrifft ferner ein hydraulisches Start-Stopp-System, das eine Verdrängereinheit nach einer der vorhergehend dargestellten Varianten umfasst.The invention also relates to a hydraulic start-stop system which comprises a displacement unit according to one of the variants presented above.

Vorzugsweise umfasst das hydraulische Start-Stopp-System ferner eine Brennkraftmaschine, die mit der Verdrängereinheit mechanisch gekoppelt ist und dazu ausgelegt ist, die Verdrängereinheit anzutreiben und von der Verdrängereinheit angetrieben zu werden, und einen Druckspeicher, der mit einem Auslassanschluss der Verdrängereinheit und mit einem zweiten Anschluss zum Zuführen eines Fluids an das Triebwerk der Verdrängereinheit verbunden ist, wobei der erste Sauganschluss mit einem Fluidreservoir verbunden ist.Preferably, the hydraulic start-stop system further comprises an internal combustion engine which is mechanically coupled to the displacement unit and is designed to drive the displacement unit and to be driven by the displacement unit, and a pressure accumulator which is connected to an outlet connection of the displacement unit and to a second Connection for supplying a fluid is connected to the engine of the displacement unit, wherein the first suction connection is connected to a fluid reservoir.

Nach einer optionalen Modifikation des hydraulischen Start-Stopp-Systems wird ein unter Druck stehendes Fluid in dem Fluidspeicher dazu genutzt, eine Brennkraftmaschine zu starten, in dem ein aus dem Fluidspeicher strömendes Fluid die Verdrängereinheit antreibt und über die mechanische Kopplung zwischen Verdrängereinheit und Brennkraftmaschine eine Anlassbewegung für die Brennkraftmaschine ausübt, wobei vorzugsweise zum Leiten des Fluids ein erstes Ventil zwischen Fluidspeicher und zweitem Anschluss und ein zweites Ventil zwischen dem Auslassanschluss und einer Verbindung zu dem Fluidreservoir vorgesehen sind.According to an optional modification of the hydraulic start-stop system, a pressurized fluid in the fluid reservoir is used to start an internal combustion engine in which a fluid flowing from the fluid reservoir drives the displacement unit and via the mechanical coupling between the displacement unit and internal combustion engine exerts a starting movement for the internal combustion engine, with a first valve between the fluid reservoir and the second connection and a second valve between the outlet connection and a connection to the fluid reservoir being preferably provided for guiding the fluid.

Ferner betrifft die vorliegende Erfindung auch eine Mobile Arbeitsmaschine, insbesondere einen Mobilbagger, einen Raupenbagger, einen Mobilkran, mit einem hydraulischen Start-Stopp-System nach einer der vorstehend beschriebenen Varianten.The present invention also relates to a mobile work machine, in particular a mobile excavator, a crawler excavator, a mobile crane, with a hydraulic start-stop system according to one of the variants described above.

Weitere Merkmale, Einzelheiten und Vorteile der Erfindung werden anhand der detaillierten Diskussion der nachfolgenden Figuren ersichtlich.Further features, details and advantages of the invention will become apparent from the detailed discussion of the following figures.

Dabei zeigen:

Fig. 1:
eine schematische Darstellung einer erfindungsgemäßen Verdrängereinheit mit einem integrierten Rückschlagventil,
Fig. 2:
eine schematische Darstellung eines Teils der erfindungsgemäßen Verdrängereinheit,
Fig. 3:
eine schematische Darstellung der erfindungsgemäßen Verdrängereinheit nach einer weiteren Ausführungsform,
Fig. 4:
eine vergrößerte Detailsansicht der weiteren Ausführungsform, und
Fig. 5:
einen Schaltplan für ein hydraulisches Start-Stopp-System nach der Erfindung.
Show:
Fig. 1:
a schematic representation of a displacement unit according to the invention with an integrated check valve,
Fig. 2:
a schematic representation of part of the displacement unit according to the invention,
Fig. 3:
a schematic representation of the displacement unit according to the invention according to a further embodiment,
Fig. 4:
an enlarged detailed view of the further embodiment, and
Fig. 5:
a circuit diagram for a hydraulic start-stop system according to the invention.

Fig. 1 zeigt eine schematische Darstellung einer erfindungsgemäßen Verdrängereinheit, beispielsweise eine Axialkolbenmaschine, bei der der Abschnitt um einen Sauganschluss 4 der Verdrängereinheit 1 detailliert ausgeführt ist. Man erkennt, dass ein Rückschlagventil 3 im Gehäuse 2 der Verdrängereinheit 1 angeordnet ist. Im regulären Pumpenbetrieb der Verdrängereinheit 1 strömt ein Fluid durch den Sauganschluss 4 in das Innere der Verdrängereinheit 1, wird also von dem Triebwerk (nicht dargestellt) angesaugt. Das Triebwerk wird über eine mechanische Kopplung mit einer nicht dargestellten Brennkraftmaschine angetrieben. Durch die Saugwirkung des Triebwerks verrückt das Rückschlagventil 3 in seine Offenstellung und ermöglicht eine Strömungsverbindung zwischen einem Vorratsreservoir und dem Triebwerk. Fig. 1 shows a schematic representation of a displacement unit according to the invention, for example an axial piston machine, in which the section around a suction connection 4 of the displacement unit 1 is detailed. One notices, that a check valve 3 is arranged in the housing 2 of the displacement unit 1. During regular pump operation of the displacement unit 1, a fluid flows through the suction connection 4 into the interior of the displacement unit 1, that is to say is sucked in by the engine (not shown). The engine is driven via a mechanical coupling with an internal combustion engine, not shown. Due to the suction effect of the engine, the check valve 3 moves into its open position and enables a flow connection between a supply reservoir and the engine.

Fig. 2 zeigt eine vergrößerte Darstellung der Verdrängereinheit 1 im Bereich des Sauganschlusses 4. Das Gehäuse 2 weist dabei einen Sauganschluss 4 und einen zweiten Anschluss 7 auf, die beide jeweils dazu ausgelegt sind, ein Fluid in Richtung des Triebwerks der Verdrängereinheit 1 zu führen. Das Einströmen eines Fluids in den zweiten Anschluss 7 und ein Herausströmen aus dem Sauganschluss 4 wird durch das Rückschlagventil 3 unterbunden. Daher wird ein in den zweiten Anschluss 7 strömendes Fluid dem Triebwerk der Verdrängereinheit 1 zugeführt. Der Strömungspfad des Sauganschlusses 4 und der Strömungspfad des zweiten Anschlusses 7 vereinigen sich stromabwärts zu einem gemeinsamen Strömungspfad 8, über den eine Strömungsverbindung zu dem Triebwerk hergestellt wird. Fig. 2 shows an enlarged view of the displacement unit 1 in the area of the suction connection 4. The housing 2 has a suction connection 4 and a second connection 7, both of which are designed to guide a fluid in the direction of the drive mechanism of the displacement unit 1. The inflow of a fluid into the second connection 7 and outflow out of the suction connection 4 is prevented by the check valve 3. Therefore, a fluid flowing into the second connection 7 is fed to the engine of the displacement unit 1. The flow path of the suction connection 4 and the flow path of the second connection 7 combine downstream to form a common flow path 8, via which a flow connection to the engine is established.

Das Rückschlagventil 3 ist dabei verschieblich in einer Ausnehmung gelagert, sodass bei einem aus Richtung des Triebwerks oder des zweiten Anschlusses 7 stammenden Drucks des Rückschlags in eine geschlossene Position übergeht. Wird jedoch aufgrund der Bewegung des Triebwerks ein Saugdruck auf das Rückschlagventil 3 ausgeübt, so bewegt es sich weg von seiner Schließstellung in seine Offenstellung und ein Fluid kann durch den Sauganschluss 4 und die Fluiddurchflussbohrungen 13 in Richtung des Triebwerks strömen. Ferner erkennt man, dass eine Flanschplatte 6 an dem Gehäuse 2 der Verdrängereinheit angeordnet ist, die einen Ansaugkanal 5 aufweist. Man erkennt, dass der Ansaugkanal 5 seinen Strömungsquerschnitt hin zu der Position, die durch das Rückschlagventil verschließbar ist, verkleinert. Verwendet man die so ausgebildete Verdrängereinheit 1 in einem hydraulischen Start-Stopp-System, so ist der Ansaugkanal 5 mit einem Fluidreservoir bzw. einem Vorratstank an Fluid verbunden. Eine Strömung von dem Vorratstank durch das Rückschlagventil 3 in Richtung des Triebwerks erfolgt dann bei einem Pumpenbetrieb der Verdrängereinheit 1. Wird die Verdrängereinheit 1 jedoch dazu genutzt, eine Brennkraftmaschine anzulassen oder bei einem Anlassvorgang zu unterstützen, wird ein unter einem großen Druck stehendes Fluid an dem zweiten Anschluss 7 angeströmt und die Verdrängereinheit im Motorbetrieb genutzt. Durch das an dem zweiten Anschluss 7 einströmende Fluid wird das Rückschlagventil 3 in seine schließende Position gedrängt, um ein Strömen des Fluids in den Vorratstank zu unterbinden. Stattdessen strömt es in Richtung des Triebwerks, wo es eine Bewegung des Triebwerks hervorruft, die wiederum die Ausgangswelle der Brennkraftmaschine, die mechanisch fest mit dem Triebwerk gekoppelt ist, in eine Anlassbewegung überführt.The check valve 3 is displaceably mounted in a recess, so that when the pressure of the check comes from the direction of the engine or the second connection 7, it changes into a closed position. However, if suction pressure is exerted on the check valve 3 due to the movement of the engine, it moves away from its closed position into its open position and a fluid can flow through the suction connection 4 and the fluid flow bores 13 in the direction of the engine. It can also be seen that a flange plate 6 is arranged on the housing 2 of the displacement unit, which flange plate has an intake channel 5. It can be seen that the intake channel 5 reduces its flow cross-section towards the position that can be closed by the check valve. If the displacement unit 1 constructed in this way is used in a hydraulic start-stop system, the intake channel 5 is provided with a fluid reservoir or connected to a storage tank of fluid. A flow from the storage tank through the check valve 3 in the direction of the engine then takes place during pump operation of the displacement unit 1. However, if the displacement unit 1 is used to start an internal combustion engine or to assist with a starting process, a fluid under high pressure is transferred to the second connection 7 and the displacement unit used in engine operation. The check valve 3 is forced into its closing position by the fluid flowing in at the second connection 7 in order to prevent the fluid from flowing into the storage tank. Instead, it flows in the direction of the engine, where it causes the engine to move, which in turn converts the output shaft of the internal combustion engine, which is mechanically fixed to the engine, into a starting movement.

Fig. 3 zeigt eine strömungsoptimierte Darstellung des Rückschlagventils 3 sowie einen Strömungsoptimierten Ventilsitz 9. Man erkennt das strömungsoptimierte Rückschlagventil 3 an der abgeschrägten Fläche des Ventilkolbens 16. Dieser kommt an den Ventilsitz 9 derart mit der Wandung eines Strömungspfads in Kontakt, dass eine Abdichtung für das Fluid erfolgt. Dabei ist der Strömungspfad mit einer optimierten Venturi-Konturform versehen, die eine Strömungsgeschwindigkeitserhöhung sowie Verminderung von Wirbelbildungen und damit das Absenken des Strömungswiderstands erwirkt. Diese Venturi-Konturform ist lediglich am Ventilsitz unterbrochen, um eine zufriedenstellende Dichtwirkung in einem geschlossenen Zustand des Rückschlagventils 3 zu erhalten. Zudem erkennt man, dass es im Übergangsbereich der Flanschplatte 6 zu dem Gehäuse 2 einen O-Ring 14 gibt, um Dichtheit zu erlangen. Ein weiterer O-Ring 14 ist auch umfangseitig in dem Strömungspfad zwischen der in das Gehäuse 2 hineinragenden Venturi-Konturform angeordnet. Fig. 3 shows a flow-optimized representation of the check valve 3 and a flow-optimized valve seat 9. The flow-optimized check valve 3 can be seen on the beveled surface of the valve piston 16. This comes into contact with the valve seat 9 with the wall of a flow path in such a way that a seal for the fluid occurs. The flow path is provided with an optimized Venturi contour shape, which increases the flow rate and reduces the formation of eddies and thus reduces the flow resistance. This Venturi contour shape is only interrupted at the valve seat in order to obtain a satisfactory sealing effect when the check valve 3 is closed. It can also be seen that there is an O-ring 14 in the transition area of the flange plate 6 to the housing 2 in order to achieve tightness. Another O-ring 14 is also arranged circumferentially in the flow path between the Venturi contour shape protruding into the housing 2.

Fig. 4 zeigt einen vergrößerten Ausschnitt aus Fig. 3 im Bereich eines Ventilsitzes 9. Hieran erkennt man gut die optimierte, abgeschrägte Kontur der Venturi-Form 17, 18, die beim Aufsetzen des Ventilkolbens 16 auf dem Ventilsitz 9 dichtend schließt. Das mit dem Bezugszeichen 19 dargestellte Element entspricht dabei einem Freistich. Fig. 4 shows an enlarged section Fig. 3 in the area of a valve seat 9. This shows the optimized, beveled contour of the Venturi shape 17, 18, which forms a seal when the valve piston 16 is placed on the valve seat 9 closes. The element shown with the reference numeral 19 corresponds to an undercut.

Fig. 5 ist eine schematische Darstellung des hydraulischen Start-Stopp-Systems 30. Man erkennt eine Brennkraftmaschine 31, die über eine mechanische Kopplung 35 mit dem Triebwerk 39 der Verdrängereinheit 1 gekoppelt ist. Zudem erkennt man das für die Erfindung charakteristisch innerhalb des Gehäuses 2 der Verdrängereinheit 1 angeordnete Einwegventil 3, hier ein Rückschlagventil. Ferner ist die Verdrängereinheit 1 an ihrem Sauganschluss 4 mit einem Fluidreservoir 34 verbunden. Dieses Fluidreservoir 34 dient als Vorratstank für das Fluid. Fig. 5 is a schematic representation of the hydraulic start-stop system 30. An internal combustion engine 31 can be seen, which is coupled to the engine 39 of the displacement unit 1 via a mechanical coupling 35. In addition, one recognizes the one-way valve 3, here a check valve, which is characteristic of the invention and is arranged within the housing 2 of the displacement unit 1. Furthermore, the displacement unit 1 is connected to a fluid reservoir 34 at its suction connection 4. This fluid reservoir 34 serves as a storage tank for the fluid.

Darüber hinaus weist die Verdrängereinheit 1 einen zweiten Anschluss 7 auf, der dazu ausgelegt ist, ein Fluid in Richtung des Triebwerks 39 zu führen. Der zweite Anschluss 7 ist dabei über ein erstes Ventil 36 mit einem Druckspeicher 32 in Verbindung. Der Fluidspeicher 32 ist dazu ausgelegt, ein Fluid unter einem hohen Druck aufzunehmen und dieses in sich zu speichern. Am Auslassanschluss 33 der Verdrängereinheit 1 steht die Arbeitshydraulik in Verbindung. Ferner steht mit dem Auslassanschluss 33 ein zweites Ventil 37 und ein drittes Ventil 38 in Verbindung. Das dritte Ventil 38 kann einen Strömungspfad zwischen dem Auslassanschluss 33 und dem Fluidreservoir 34 schließen oder öffnen. Das zweite Ventil 37 kann eine Verbindung zu dem Druckspeicher 32 schließen oder öffnen.In addition, the displacement unit 1 has a second connection 7 which is designed to guide a fluid in the direction of the engine 39. The second connection 7 is connected to a pressure accumulator 32 via a first valve 36. The fluid reservoir 32 is designed to receive a fluid under a high pressure and to store it in itself. The working hydraulics are connected to the outlet connection 33 of the displacement unit 1. Furthermore, a second valve 37 and a third valve 38 are connected to the outlet connection 33. The third valve 38 can close or open a flow path between the outlet port 33 and the fluid reservoir 34. The second valve 37 can close or open a connection to the pressure accumulator 32.

Das in Fig. 5 dargestellte System wird anhand der verschiedenen Betriebszustände, die das System einnehmen kann, erläutert. In einem ersten Betriebszustand wird die Arbeitshydraulik mit Fluid versorgt. Dies entspricht einem Normalbetrieb. Hierin sind die Ventile 38, 37 und 36 in einem geschlossenen Zustand. Im Normalbetrieb wird die Verdrängereinheit 1 vom Dieselmotor 31 angetrieben. Dabei saugt die Verdrängereinheit 1 das Arbeitsfluid, beispielsweise ein Hydrauliköl, über das Rückschlagventil 3 an. Das Rückschlagventil 3 ist dabei so ausgeführt, dass sich hierüber entlang der Durchlassrichtung ein möglichst geringer Druckabfall ergibt. Je nach Volumenstrom, d.h. Drehzahl und Verdrängervolumen der Verdrängereinheit 1 darf ein bestimmter Ansaugdruck nicht unterschritten werden. Als Folge hieraus ergibt sich eine Leitungsbegrenzung durch den Ansaugdruck. Aus dem Auslassanschluss 33 (auch: Arbeitsanschluss) fördert die Verdrängereinheit 1 das Fluid an dem sich in der Arbeitshydraulik befindenden Ventilschieber. Die Verdrängereinheit 1 ist dabei einer Load-Sensing-Regelung unterzogen, die dafür sorgt, dass die Verdrängereinheit 1 entsprechend einer Volumenstromanforderung den Fördervolumenstrom anpasst. Bei einer Axialkolbenmaschine geschieht dies durch Anpassen des Schrägwinkels.This in Fig. 5 The system shown is explained on the basis of the various operating states that the system can assume. In a first operating state, the working hydraulics are supplied with fluid. This corresponds to normal operation. Here the valves 38, 37 and 36 are in a closed state. In normal operation, the displacement unit 1 is driven by the diesel engine 31. The displacement unit 1 sucks in the working fluid, for example a hydraulic oil, via the check valve 3. The check valve 3 is designed in such a way that this results in the lowest possible pressure drop along the flow direction. Depending on the volume flow, ie the speed and displacement volume of the displacement unit 1, the suction pressure must not fall below a certain level. As a result there is a line limitation by the suction pressure. From the outlet connection 33 (also: working connection), the displacement unit 1 conveys the fluid to the valve slide located in the working hydraulics. The displacement unit 1 is subjected to a load-sensing control which ensures that the displacement unit 1 adapts the delivery volume flow in accordance with a volume flow requirement. In an axial piston machine, this is done by adjusting the helix angle.

Ein weiterer Betriebszustand des in der Figur 5 dargestellten Systems lädt den Druckspeicher 32. In diesem Zustand sind die Ventile 38 und 36 geschlossen. Das Ventil 37 ist in seiner offenen Position. Zum Laden des Druckspeichers 32, der auch als Hydrospeicher ausgeführt sein kann, wird das von der Verdrängereinheit 1 geförderte Fluid in den Druckspeicher 32 gefördert.Another operating state of the Figure 5 The system shown loads the pressure accumulator 32. In this state, the valves 38 and 36 are closed. The valve 37 is in its open position. To charge the pressure accumulator 32, which can also be designed as a hydraulic accumulator, the fluid conveyed by the displacement unit 1 is conveyed into the pressure accumulator 32.

Als weiteren Betriebszustand kann man das Starten des Dieselmotors ansehen. Um den Dieselmotor starten zu können, muss dieser in einem gestoppten Zustand sein. Dann sind alle Ventile 36, 37 und 38 zu schließen. Ferner muss der hydraulische Druckspeicher 32 bei abgeschalteten Dieselmotor 31 ausreichend geladen sein, um eine Startanforderung erfüllen zu können. Zur Einleitung des Startvorgangs werden die Ventile 36 und 38 geöffnet, wohingegen das Ventil 37 geschlossen bleibt. Das unter Druck stehende Fluid gelangt vom Druckspeicher 32 über den zweiten Anschluss 7 an den Saugkanal der Verdrängereinheit 1. Dabei schließt das Rückschlagventil 3 entsprechend dem dort anliegendem Druckverhältnis die Verbindung zwischen dem Druckspeicher 32 und dem Sammeltank 34 des Fluids. Der Ansaugkanal 7 der Verdrängereinheit 1 steht somit unter Druck und die Verdrängereinheit 1 arbeitet motorisch. Der Antriebsstrang wird beschleunigt, wodurch die Startdrehzahl des Motors überschritten wird, wodurch unmittelbar nachfolgend der gestartete Motor auf seine Betriebsdrehzahl hochgeschleppt wird. Da das Ventil 38 geöffnet ist, gelangt das Fluid vom Arbeitsanschluss 33 der Verdrängereinheit 1 zurück in den Sammeltank 34. Während dieses Startvorgangs kann die Arbeitshydraulik nicht mit hydraulischer Leistung versorgt werden.Starting the diesel engine can be seen as a further operating state. In order to be able to start the diesel engine, it must be in a stopped state. Then all valves 36, 37 and 38 are to be closed. Furthermore, when the diesel engine 31 is switched off, the hydraulic pressure accumulator 32 must be sufficiently charged in order to be able to meet a start request. To initiate the starting process, the valves 36 and 38 are opened, whereas the valve 37 remains closed. The pressurized fluid arrives from the pressure accumulator 32 via the second connection 7 to the suction channel of the displacement unit 1. The check valve 3 closes the connection between the pressure accumulator 32 and the fluid collection tank 34 according to the pressure ratio there. The intake channel 7 of the displacement unit 1 is thus under pressure and the displacement unit 1 operates by a motor. The drive train is accelerated, as a result of which the starting speed of the motor is exceeded, as a result of which the started motor is dragged up to its operating speed immediately afterwards. Since the valve 38 is open, the fluid from the working connection 33 of the displacement unit 1 returns to the collecting tank 34. During this starting process, the working hydraulics cannot be supplied with hydraulic power.

Das vorstehend beschriebene hydraulische Start-Stopp-System eignet sich besonders für den Einsatz in einer Mobilen Arbeitsmaschine. Dabei ist es möglich, dass die Arbeitsmaschine, bei der an der Brennkraftmaschine gegebenenfalls über ein Pumpenverteilergetriebe ein oder mehrere hydraulische Verdrängereinheiten antreibt. Dabei ist es möglich, dass die abgegebene Leistung der Brennkraftmaschine mittels verstellbarer Verdrängereinheit in hydraulische Leistung umgesetzt wird. Es ist zu beachten, dass die mindestens eine Verdrängereinheit jederzeit mechanisch mit der Brennkraftmaschineverbunden ist. Ferner kann vorgesehen sein, dass die mindestens eine Verdrängereinheit über einen Steuerschieber die Arbeitshydraulik der Mobilen Arbeitsmaschine, wie z.B. einen Stielzylinder, einen Löffelzylinder, einen Auslegerzylinder und einen Fahrantrieb versorgt. Typische Anwendungen wären beispielsweise Mobilbagger, Raupenbagger, Mobilkräne etc.The hydraulic start-stop system described above is particularly suitable for use in a mobile work machine. It is possible here for the working machine to drive one or more hydraulic displacement units on the internal combustion engine, possibly via a pump transfer gear. It is possible that the output of the internal combustion engine is converted into hydraulic power by means of an adjustable displacement unit. It should be noted that the at least one displacement unit is always mechanically connected to the internal combustion engine. Furthermore, it can be provided that the at least one displacement unit controls the working hydraulics of the mobile working machine, e.g. supplies an arm cylinder, a bucket cylinder, a boom cylinder and a traction drive. Typical applications would be mobile excavators, crawler excavators, mobile cranes, etc.

Vorzugsweise ist die Nutzung der hydraulischen Start-Stopp-Funktionalität erst bei der Erreichung der Betriebstemperatur des Antriebssystems einzusetzen, d. h. wie bei PKW-Start-Stopp-Systemen bekannt, soll eine Abschaltung des Primärantriebs erst bei Erreichung der Betriebstemperatur insbesondere der des Motorenöls erfolgen. In einer Mobilen Arbeitsmaschine betrifft das nicht nur die Betriebstemperatur der Brennkraftmaschine, sondern auch das Hydrauliköl.The hydraulic start-stop functionality should preferably only be used when the operating temperature of the drive system has been reached, i. H. As is known in car start-stop systems, the primary drive should only be switched off when the operating temperature, in particular that of the engine oil, is reached. In a mobile work machine, this affects not only the operating temperature of the internal combustion engine, but also the hydraulic oil.

Das zum Starten notwendige Hochschleppen der Brennkraftmaschine soll sowohl bei einem Kaltstart als auch bei einem Warmstart bevorzugt immer mit dem hydraulischen System erfolgen. Damit Letzteres möglich ist, soll eine Abschaltung der Brennkraftmaschine nur dann erfolgen und ggf. solange verzögert werden bis der hydraulische Druckspeicher voll aufgeladen ist. Dabei gibt es zwei Ausnahmen, wobei die erste das Detektieren eines Not-Aus ist und die zweite das Detektieren einer Undichtheit des Druckspeichers und der nur für den Speicherbetrieb vorhandenen Hydraulikleitung.The dragging up of the internal combustion engine required for starting should preferably always take place with the hydraulic system, both for a cold start and for a warm start. In order for the latter to be possible, the internal combustion engine should only then be switched off and, if necessary, delayed until the hydraulic pressure accumulator is fully charged. There are two exceptions, the first being the detection of an emergency stop and the second being the detection of a leak in the pressure accumulator and the hydraulic line that is only used for accumulator operation.

Wird ein Abschalten der Brennkraftmaschine aufgrund eines noch nicht voll aufgeladenen Druckspeichers unterdrückt, soll die Abschaltung der Brennkraftmaschine nicht erst dann erfolgen, wenn der Druckspeicher bereits voll aufgeladen ist, sondem die aufgrund der im Antriebssystem rotierenden Massen (Schwungrad, Zahnräder im Pumpenverteilergetriebe) berücksichtigt werden und der daraus entnehmbare Energieanteil dem Druckspeicher zugeführt werden, anstatt diesen weiterhin unter fortdauerndem Kraftstoffverbrauch zu laden.If a shutdown of the internal combustion engine is suppressed because the pressure accumulator is not yet fully charged, the internal combustion engine should not only be switched off when the pressure accumulator is already fully charged, but rather which are taken into account due to the rotating masses in the drive system (flywheel, gearwheels in the pump distributor gear) and the energy that can be taken from it is fed to the pressure accumulator instead of continuing to charge it with continued fuel consumption.

Zur Bestimmung der noch vorhandenen Rotationsenergie dient der am Schwungrad der Brennkraftmaschine vorhandene oder ein separater Drehzahlsensor. Zur Berücksichtigung des Anteils der Rotationsenergie, die dem Druckspeicher zugeführt werden kann, werden die im Druckspeicher vorliegende Hydrauliköltemperatur und der im Druckspeicher vorliegende Druck gemessen und berücksichtigt. In einem Steuergerät werden diese drei Grössen eingelesen. Daraus wird der Zeitpunkt bestimmt an dem unter Berücksichtigung der Verluste genügend Rotationsenergie zur vollständigen Aufladung des Druckspeichers vorliegt. Zu diesem Zeitpunkt wird die angeforderte Abschaltung der Brennkraftmaschine freigegeben. Die Berechnung erfolgt anhand einem im Steuergerät hinterlegten Kennfeld mit den Eingangsgrössen: Drehzahl, Öltemperatur, Druckniveau im Speicher. Hieraus ergibt sich die Energie, die dem Speicher bis zum Stillstand des Antriebs zugeführt werden kann. Die Kennlinie wird für jede Antriebskonfiguration durch die Ergebnisse von Funktionsversuchen definiert.The rotational energy present on the flywheel of the internal combustion engine or a separate speed sensor is used to determine the rotational energy that is still present. To take into account the portion of the rotational energy that can be supplied to the pressure accumulator, the hydraulic oil temperature in the pressure accumulator and the pressure in the pressure accumulator are measured and taken into account. These three variables are read into a control unit. From this, the point in time is determined at which there is sufficient rotational energy to fully charge the pressure accumulator, taking into account the losses. At this point in time, the requested shutdown of the internal combustion engine is enabled. The calculation is based on a map stored in the control unit with the input variables: speed, oil temperature, pressure level in the memory. This results in the energy that can be fed to the storage unit until the drive comes to a standstill. The characteristic is defined for each drive configuration by the results of functional tests.

Zudem ist denkbar, dass konventionelle Starteinrichtung nach wie vor als Back-Up für Warmstarts und für "Kaltstarts" zur Verfügung stehen.It is also conceivable that conventional starting devices are still available as a back-up for warm starts and for "cold starts".

Weiter kann das hydraulische Start-Stopp-System den elektrischen Startvorgang unterstützen.The hydraulic start-stop system can also support the electrical starting process.

Eine Drehmomentbeaufschlagung des Antriebstranges mit Hilfe der Verdrängereinheit ist besonders vorteilhaft, wenn man - bezogen auf die Ausführung der Brennkraftmaschine als Dieselmotor mindestens auf seine Startdrehzahl beschleunigt und vorteilhafterweise auf seine Arbeitsdrehzahl im Bereich von 1200 min-1 bis 2200 min-1, bevorzugt von 1400 min-1 bis 1900 min-1 besonders bevorzugt auf 1500 min-1 bis 1800 min-1.Applying torque to the drive train with the aid of the displacement unit is particularly advantageous if - based on the design of the internal combustion engine as a diesel engine, it is accelerated to at least its starting speed and advantageously to its working speed in the range from 1200 min -1 to 2200 min -1 , preferably from 1400 min -1 to 1900 min -1, particularly preferably to 1500 min -1 to 1800 min -1 .

Eine Drehmomentbeaufschlagung des Antriebstranges mit Hilfe der Verdrängereinheit einer im Downspeeding-Modus betriebenen Brennkraftmaschine mindestens auf ihre Startdrehzahl kann ebenfalls vorgenommen werden. Bezogen auf die Ausführung der Brennkraftmaschine als Dieselmotor ist eine Arbeitsdrehzahl im Bereich von 1200 min-1 bis 1500 min-1 bevorzugt. Bei einer weiteren Absenkung der Drehzahl hätten die zur Umwandlung von mechanischer in hydraulische Leistung benötigten Hydraulikpumpen eine entsprechend grosse Bauform. Das wäre unwirtschaftlich.An application of torque to the drive train with the aid of the displacement unit of an internal combustion engine operated in downspeeding mode can also be carried out to at least its starting speed. In relation to the design of the internal combustion engine as a diesel engine, an operating speed in the range from 1200 min -1 to 1500 min -1 is preferred. If the speed were to be reduced further, the hydraulic pumps required to convert mechanical power into hydraulic power would have a correspondingly large design. That would be uneconomical.

Auch könnte man eine Drehmomentbeaufschlagung des bereits unter Last stehenden Antriebstranges mit Hilfe der Verdrängereinheit vornehmen, um eine Brennkraftmaschine mindestens auf ihre Startdrehzahl zu beschleunigen.It would also be possible to apply torque to the drive train, which is already under load, with the aid of the displacement unit in order to accelerate an internal combustion engine at least to its starting speed.

Bei der zum Hochschleppen der Brennkraftmaschine verwendeten Verdrängereinheit ist bei quasi konstantem Hochdruck das Abtriebsdrehmoment nahezu proportional zum Schwenkwinkel der Schrägscheibe einer Axialkolbenmaschine.In the displacement unit used to drag up the internal combustion engine, the output torque is almost proportional to the swivel angle of the swash plate of an axial piston machine at a quasi constant high pressure.

Als Druckspeicher kann ein Hydrospeicher, insbesondere ein Blasenspeicher oder ein Kolbenspeicher eingesetzt werden.A hydraulic accumulator, in particular a bladder accumulator or a piston accumulator, can be used as the pressure accumulator.

Das maximale Druckniveau im Druckspeicher liegt zwischen 100 und 450 bar, bevorzugt 150 bis 300 bar und besonders bei 200 bar.The maximum pressure level in the pressure accumulator is between 100 and 450 bar, preferably 150 to 300 bar and especially 200 bar.

Der Druckspeicher kann direkt über eine am Nebenabtrieb mit fester Übersetzung an die Brennkraftmaschine gekoppelten Verdrängereinheit geladen werden. Die den Druckspeicher aufladende Verdrängereinheit kann sich auch auf der Primärseite des Pumpenverteilergetriebes befinden. Die den Druckspeicher aufladende Verdrängereinheit kann sich auch auf der Sekundärseite des Pumpenverteilergetriebes befinden.The pressure accumulator can be charged directly via a displacement unit coupled to the internal combustion engine on the power take-off with a fixed ratio. The displacement unit charging the pressure accumulator can also be located on the primary side of the pump distributor gear. The displacement unit charging the pressure accumulator can also be located on the secondary side of the pump transfer case.

Die den Druckspeicher aufladende Verdrängereinheit kann ausschliesslich zur Aufladung des Druckspeichers vorgesehen sein. Die den Druckspeicher aufladende Verdrängereinheit kann zur Aufladung des Druckspeichers und für den Betrieb mindestens eines Nebenverbrauchers vorgesehen sein. In diesem Fall ist es möglich, dass die betreffende Verdrängereinheit in einem bestimmten Zeitintervall a) nur den Druckspeicher auflädt, b) nur zum Betrieb des mindestens einen Nebenverbrauchers eingesetzt wird oder c) den Druckspeicher und simultan mindestens einen Nebenverbraucher versorgt.The displacement unit charging the pressure accumulator can be provided exclusively for charging the pressure accumulator. The displacement unit charging the pressure accumulator can be provided for charging the pressure accumulator and for operating at least one secondary consumer. In this case it is possible that the displacement unit in question a) only charges the pressure accumulator, b) is only used to operate the at least one auxiliary consumer or c) supplies the pressure accumulator and at least one auxiliary consumer at the same time in a certain time interval.

Die den Druckspeicher aufladende Verdrängereinheit kann zur Aufladung des Druckspeichers vorgesehen sein und für den Betrieb mindestens eines Hauptverbrauchers, z. B. dem Fahrantrieb. In diesem Fall ist es möglich, dass die betreffende Verdrängereinheit in einem bestimmten Zeitintervall a) nur den Druckspeicher auflädt, b) nur zum Betrieb des mindestens einen Hauptverbrauchers eingesetzt wird oder c) den Druckspeicher und simultan mindestens einen Hauptverbraucher versorgt.The displacement unit charging the pressure accumulator can be provided for charging the pressure accumulator and for the operation of at least one main consumer, e.g. B. the drive. In this case it is possible that the displacement unit in question a) only charges the pressure accumulator, b) is only used to operate the at least one main consumer or c) supplies the pressure accumulator and at least one main consumer at the same time.

Die den Druckspeicher aufladende Verdrängereinheit kann identisch mit der zum Starten der Brennkraftmaschine hochschleppenden Verdrängereinheit sein. Die den Druckspeicher aufladende Verdrängereinheit kann eine andere sein als diejenige Verdrängereinheit, die beim Starten der Brennkraftmaschine das Hochschleppen desselben übernimmt.The displacement unit charging the pressure accumulator can be identical to the displacement unit which is dragging up to start the internal combustion engine. The displacement unit charging the pressure accumulator can be different from the displacement unit which takes over the dragging of the internal combustion engine when it is started.

Verzugsfreies Starten der Brennkraftmaschine unmittelbar nach einer Drehmomentanforderung bzw. einem Arbeitswunsch durch den Fahrer bedingt ein hohes Drehmoment, um den Antriebstrang in kurzer Zeit zu beschleunigen. Als Folge davon ist ein hydraulischer Startvorgang des vorgesehenen Systems bzw. die Verfügbarkeit einer Arbeitsfunktion der Mobilen Arbeitsmaschine schneller als bei den heutigen elektrischen Startsystemen.Delay-free starting of the internal combustion engine immediately after a torque request or a work request by the driver requires a high torque in order to accelerate the drive train in a short time. As a result, a hydraulic starting process of the intended system or the availability of a work function of the mobile work machine is faster than with today's electrical starting systems.

Es lässt sich zudem eine Kraftstoffeinsparung durch Abschalten der Brennkraftmaschineerzielen, wenn keine Leistungsabgabe zur Nutzung der Primärfunktionen erforderlich ist. Als Primärfunktion werden die translatorische Bewegung der Mobilen Arbeitsmaschine und die Betätigung der Arbeitshydraulik bezeichnet. Die im Bedarfsfall während des Stopp-Betriebs weiterhin durch Nebenverbraucher zu erfüllenden Sekundärfunktionen wie (z. B. der Betrieb der Klimaanlage, die Beleuchtung sollen bevorzugt aus dem konventionellen Bordnetz gespeist werden.In addition, fuel savings can be achieved by switching off the internal combustion engine when there is no power output to use the primary functions is required. The primary function is the translational movement of the mobile work machine and the actuation of the work hydraulics. The secondary functions, such as (e.g. operating the air conditioning system, the lighting), which still have to be fulfilled by secondary consumers during stop operation, should preferably be fed from the conventional on-board network.

Die Erfindung ermöglicht eine Erhöhung des Komforts und der Sicherheit durch temporäre geringere Lärmbelastung am Einsatzort während der Abschaltung der Brennkraftmaschine.The invention enables an increase in comfort and safety through temporarily lower noise pollution at the place of use while the internal combustion engine is switched off.

Das Laden des Druckspeichers ist auch durch Rekuperationsleistung z. B. bei Bremsvorgängen möglich.The loading of the accumulator is also possible through recuperation z. B. possible during braking.

Das Laden des Speichers ist auch durch eine Lastpunktanhebung möglich. Dabei wird die Sollabgabeleistung der Brennkraftmaschine bewusst höher gewählt als die benötigte Antriebsleistung. Mit der "überschüssigen" Leistung wird der Druckspeicher aufgeladen.The storage tank can also be loaded by increasing the load point. The target output power of the internal combustion engine is deliberately chosen to be higher than the required drive power. The pressure accumulator is charged with the "excess" power.

Auch ist eine Lastpunktabsenkung denkbar. Die Leistungsabgabe der Brennkraftmaschine wird dann kurzzeitig reduziert. Das zur Versorgung der Verbraucher benötigte "Leistungsdefizit" wird aus dem Druckspeicher entnommen.A lowering of the load point is also conceivable. The power output of the internal combustion engine is then reduced for a short time. The "power deficit" required to supply the consumer is taken from the pressure accumulator.

Die Erfindung ermöglicht zudem einen Aktiv Boost für eine kurzzeitige dem Antrieb zur Verfügung gestellte Leistungserhöhung. Auch kann damit ein Schutz vor dem Abwürgen der Brennkraftmaschineerhalten werden.The invention also enables an active boost for a brief power increase made available to the drive. Protection against stalling the internal combustion engine can also be obtained in this way.

Claims (14)

  1. A displacement unit (1), in particular an axial piston machine, comprising:
    a housing (2),
    an engine for converting rotary power into hydraulic power and vice versa,
    a suction port (4) for supplying a fluid to the engine and a one-way valve (3) which is arranged in the housing (2) of the displacement unit (1),
    characterized by
    a second port (7) for supplying a fluid to the engine, wherein the flow paths proceeding from the suction port (4) and from the second port (7) unite downstream to form a common flow path (8), and
    wherein the one-way valve (3) is arranged in the area between the suction port (4) and the united common flow path (8).
  2. The displacement unit (1) according to claim 1, wherein the one-way valve (3) is arranged in the flow path between suction port (4) and engine.
  3. The displacement unit (1) according to any of the preceding claims, wherein the one-way valve (3) is integrated in the housing (2) of the displacement unit (1).
  4. The displacement unit (1) according to any of the preceding claims, wherein the one-way valve (3) is arranged in a suction channel (5) of a connecting plate (6) of the displacement unit (1).
  5. The displacement unit (1) according to any of the preceding claims, wherein the cross-section of the flow path decreases from the suction port (4) towards the engine, preferably continuously, and the one-way valve (3) is arranged at a position in the flow path where the cross-section of the flow channel is not maximum.
  6. The displacement unit (1) according to any of the preceding claims, wherein the one-way valve (3) is arranged in the flow path at a distance from the suction port (4) in the direction of the engine.
  7. The displacement unit (1) according to any of the preceding claims, wherein the one-way valve (3) is designed to let the fluid flow only in the direction of the engine and to minimize or inhibit a flow of the fluid in the opposite direction.
  8. The displacement unit (1) according to any of the preceding claims, wherein the one-way valve (3) is a non-return valve or a slide valve, preferably a non-return valve to be actuated by high pressure.
  9. The displacement unit (1) according to any of the preceding claims, wherein the one-way valve (3) is flow-optimized and cooperates with a flow-optimized valve seat (9).
  10. The displacement unit (1) according to any of the preceding claims, wherein the flow path to be closed by the one-way valve (3) is a Venturi contour and/or the one-way valve (3) is designed to close the flow path at the point of a smallest flow cross-section.
  11. The displacement unit (1) according to claim 10, wherein the Venturi contour has an optimized curvature in order to minimize turbulence of a fluid flowing through the one-way valve (3).
  12. The displacement unit (1) according to any of claims 10 to 11, wherein the suction port (4) is connectable to a flange plate (6) which is configured as a part of a Venturi contour formed with the flow path of the suction port (4).
  13. A hydraulic start-stop system (30), comprising:
    a displacement unit (1) according to any of the preceding claims, an internal combustion engine (31) which is mechanically coupled to the displacement unit (1) and is adapted to drive the displacement unit (1) and to be driven by the displacement unit (1), and
    a pressure accumulator (32) which is connected to an outlet port (33) of the displacement unit (1) and to a second port (7) for supplying a fluid to the engine of the displacement unit (1), wherein the first suction port (4) of the displacement unit (1) is connected to a fluid reservoir (34).
  14. The hydraulic start-stop system (30) according to claim 13, wherein a pressurized fluid in the fluid reservoir (32) is used to start an internal combustion engine (31) by a fluid flowing out of the pressure accumulator (32) driving the displacement unit (1) and exerting a starting movement for the internal combustion engine (31) via the mechanical coupling (35), wherein preferably for conducting the fluid a first valve (36) is provided between the fluid reservoir (32) and the second port (7) and a second valve (38) is provided between the outlet port (33) and a connection to the fluid reservoir (34).
EP17172414.9A 2016-07-18 2017-05-23 Displacement unit and hydraulic start/stop system with such a displacement unit Active EP3273057B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH00919/16A CH712781A1 (en) 2016-07-18 2016-07-18 Displacer unit and hydraulic start-stop system with such a displacer unit.

Publications (2)

Publication Number Publication Date
EP3273057A1 EP3273057A1 (en) 2018-01-24
EP3273057B1 true EP3273057B1 (en) 2020-12-30

Family

ID=58772432

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17172414.9A Active EP3273057B1 (en) 2016-07-18 2017-05-23 Displacement unit and hydraulic start/stop system with such a displacement unit

Country Status (2)

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EP (1) EP3273057B1 (en)
CH (1) CH712781A1 (en)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3849032A (en) * 1973-07-02 1974-11-19 Perfect Pump Co High pressure reciprocating pump
JPH10252642A (en) * 1997-03-11 1998-09-22 Hitachi Constr Mach Co Ltd Axial piston type hydraulic pump
JP4064016B2 (en) * 1999-09-13 2008-03-19 本田技研工業株式会社 Start control device for internal combustion engine
DE20306851U1 (en) * 2003-04-24 2003-08-14 Pickel Peter Fast start equipment using pressurized fluid to operate a hydrostatic pump as starter motor
US7654283B2 (en) * 2003-10-21 2010-02-02 Seiko Epson Corporation Check valve and pump including check valve
JP2007056810A (en) * 2005-08-25 2007-03-08 Komatsu Ltd Swash plate type axial piston pump motor
FR2975731B1 (en) * 2011-05-27 2015-12-11 Poclain Hydraulics Ind HYDRAULIC TRANSMISSION DEVICE WHICH CAN CONSTITUTE A COMPACT HYDRAULIC STARTER
DE102012111296A1 (en) * 2012-11-22 2014-05-22 Linde Hydraulics Gmbh & Co. Kg Drive train of a vehicle, in particular a mobile work machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CH712781A1 (en) 2018-01-31
EP3273057A1 (en) 2018-01-24

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