EP3273057A1 - 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 PDFInfo
- Publication number
- EP3273057A1 EP3273057A1 EP17172414.9A EP17172414A EP3273057A1 EP 3273057 A1 EP3273057 A1 EP 3273057A1 EP 17172414 A EP17172414 A EP 17172414A EP 3273057 A1 EP3273057 A1 EP 3273057A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- displacer unit
- engine
- fluid
- way valve
- unit
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000006073 displacement reaction Methods 0.000 title claims abstract description 15
- 239000012530 fluid Substances 0.000 claims abstract description 72
- 238000002485 combustion reaction Methods 0.000 claims description 47
- 230000015572 biosynthetic process Effects 0.000 claims description 5
- 230000008878 coupling Effects 0.000 claims description 5
- 238000010168 coupling process Methods 0.000 claims description 5
- 238000005859 coupling reaction Methods 0.000 claims description 5
- 239000010720 hydraulic oil Substances 0.000 description 6
- 230000009467 reduction Effects 0.000 description 5
- 239000007858 starting material Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000006870 function Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 244000037459 secondary consumers Species 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000001514 detection method Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000006735 deficit Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 238000011990 functional testing Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000003319 supportive effect Effects 0.000 description 1
- 238000005496 tempering Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
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- 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 displacer unit and a hydraulic start-stop system with such a displacer unit.
- the hydraulic drive system comprises a preferably controllable in the flow volume or controllable hydraulic pump, which is typically mechanically coupled to a primary drive designed as an internal combustion engine.
- the internal combustion engine usually includes an electric starter for starting the internal combustion engine, which is powered by a battery. This battery is charged by a generator driven by the internal combustion engine.
- the prior art provides for this purpose a hydraulic start-stop system, in which a mechanically coupled to an internal combustion engine displacer unit is driven not only by the internal combustion engine in the "pump mode", but a tempering of the internal combustion engine by using the displacer unit in the "engine operation". If hydraulic power is required for the working hydraulics, the displacer unit is driven by means of the mechanical coupling to the internal combustion engine and sucks a fluid, typically an oil or the like, from a fluid reservoir and transfers this to the working hydraulics on the high pressure side. As a result, it is possible for the working hydraulics, for example, to move an excavator arm or lift the shield of a caterpillar.
- a stopped internal combustion engine is started by means of the displacer unit.
- a branching line which communicates at one of its ends with a fluid reservoir via a one-way valve in connection and with the another of their ends is connected via a switchable valve with a pressure accumulator. If the pressure accumulator has a sufficient amount of fluid under pressure, then 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 displacer unit is opened in order to allow inflow of the pressurized fluid into the displacer unit.
- the displacer unit according to the invention which may in particular constitute an axial piston machine, comprises a housing, an engine for converting the rotary power into a hydraulic power and a suction port for supplying a fluid to the engine.
- the displacer unit is characterized by a one-way valve, which is arranged in the housing of the displacer unit.
- the arrangement of the one-way valve in the housing of the displacer unit leads to a reduction of the flow resistance between the hydraulic oil storage tank (also: fluid reservoir) and the pump operating engine of the displacer unit.
- a lower total flow resistance provides a higher suction limit speed, which characterizes an operating condition of a pump in which a filling stroke occurs due to a vacuum formation in a suction stroke, which can lead to a reduction of the flow rate of the pump and damage to the pump by 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 from the supply line from the storage tank to the one-way valve and the supply line from the one-way valve results in the engine, the total flow resistance decreases when the portion of the highest flow resistance, the Area around the one-way valve, located near the engine.
- a geometrically smaller executed check valve is cheaper to implement and requires less installation space. Therefore, the check valves (also: one-way valves) arranged in the prior art typically outside the housing of the displacer unit can achieve the above-mentioned positive effects.
- the one-way valve is arranged in the flow path between the suction port and the engine.
- the one-way valve is integrated in the housing of the displacer unit.
- the one-way valve is arranged in an intake passage of a connection plate of the displacer unit or cooperates with the connection plate.
- the cross-section of the flow path decreases from the suction port toward the engine, preferably this reduction is continuous and the one-way valve is located at a position in the flow path where the cross-section of the flow channel is not maximal.
- the one-way valve is arranged in the flow path from the suction port spaced towards 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 high-pressure actuated slide valve.
- the displacer unit further comprises a second port for supplying a fluid to the engine, wherein the flow paths emanating from the first suction port and the second port combine to form a common flow path and the one-way valve in the region between the first suction port and the unified common flow path is arranged.
- the displacer unit is particularly suitable for use in a hydraulic start-stop system.
- the pump operation not the pump operation but the engine operation is used for starting an engine mechanically coupled to the displacer unit.
- a pressure accumulator under pressure fluid is supplied to the engine.
- the one-way valve is provided in order to prevent a flow of the pressurized fluid into the storage tank. The inflow of a fluid at the second port and the outflow from the first suction port is thus not possible.
- the one-way valve is flow-optimized and cooperates with a flow-optimized valve seat.
- a flow-optimized one-way valve and a flow-optimized valve seat minimize vortex formation during a fluid inflow along a fluid passage opening at the suction port.
- the flow path which can be closed by the one-way valve is preferably a Venturi contour, which 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 curvature profile in order to minimize vortex formation of a fluid flowing through the one-way valve.
- the suction port is connectable to a flange plate which is designed as part of a Venturi contour formed with the flow path of the suction port.
- the invention further relates to a hydraulic start-stop system comprising a displacer unit according to one of the variants presented above.
- the hydraulic start-stop system further comprises an internal combustion engine mechanically coupled to the displacer unit and configured to drive the displacer unit and driven by the displacer unit and a pressure accumulator communicating with one outlet port of the displacer unit and with a second one Connection for supplying a fluid to the engine of the displacer unit is connected, wherein the first suction port is connected to a fluid reservoir.
- an internal combustion engine mechanically coupled to the displacer unit and configured to drive the displacer unit and driven by the displacer unit
- a pressure accumulator communicating with one outlet port of the displacer unit and with a second one Connection for supplying a fluid to the engine of the displacer unit is connected, wherein the first suction port 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 displacer unit and via the mechanical coupling between the displacer unit and internal combustion engine exerts a starting movement for the internal combustion engine, wherein preferably for directing the fluid, a first valve between the fluid reservoir and the second port and a second valve between the outlet port and a connection to the fluid reservoir are provided.
- the present invention also relates to a mobile work machine, in particular a wheeled 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 displacer unit according to the invention, for example an axial piston machine, in which the section around a suction port 4 of the displacer unit 1 is executed in detail.
- a check valve 3 is arranged in the housing 2 of the displacer unit 1.
- a fluid flows through the suction port 4 into the interior of the displacer unit 1, that is to say it is sucked in by the engine (not shown).
- the engine is driven by a mechanical coupling with an internal combustion engine, not shown. Due to the suction of the engine crazy check valve 3 in its open position and allows a flow connection between a reservoir and the engine.
- Fig. 2 shows an enlarged view of the displacer unit 1 in the region of the suction port 4.
- the housing 2 in this case has a suction port 4 and a second port 7, both of which are each designed to guide a fluid in the direction of the engine of the displacer unit 1.
- the inflow of a fluid into the second port 7 and an outflow from the suction port 4 is prevented by the check valve 3. Therefore, a fluid flowing into the second port 7 is supplied to the engine of the displacer unit 1.
- the flow path of the suction port 4 and the flow path of the second port 7 merge downstream to a common flow path 8, via which a flow connection to the engine is made.
- the check valve 3 is displaceably mounted in a recess, so that passes in a coming from the direction of the engine or the second port 7 pressure of the recoil in a closed position.
- a suction pressure is exerted on the check valve 3 due to the movement of the engine, it moves away from its closed position to its open position and a fluid can flow through the suction port 4 and the fluid flow holes 13 in the direction of the engine.
- a flange plate 6 is arranged on the housing 2 of the displacer unit, which has a suction channel 5. It can be seen that the intake passage 5 reduces its flow cross-section towards the position which can be closed by the check valve.
- the intake channel 5 is provided with a fluid reservoir or a storage tank connected to fluid.
- a flow from the storage tank through the check valve 3 in the direction of the engine then takes place during a pump operation of the displacer unit 1.
- a fluid under high pressure is at the second port 7 flows and used the displacer unit in engine operation.
- the check valve 3 is urged into its closing position to prevent flow of the fluid into the storage tank. Instead, it flows in the direction of the engine, where it causes a movement of the engine, which in turn converts the output shaft of the internal combustion engine, which is mechanically fixed to the engine, in a starting movement.
- Fig. 3 shows the flow-optimized check valve 3 on the tapered surface of the valve piston 16. This comes to the valve seat 9 so in contact with the wall of a flow path that a seal for the fluid takes place.
- the flow path is provided with an optimized Venturi contour shape, which causes a flow rate increase and reduction of vortex formation and thus the lowering of the flow resistance.
- This Venturi contour shape is interrupted only at the valve seat to obtain a satisfactory sealing effect in a closed state of the check valve 3.
- Another O-ring 14 is also circumferentially arranged in the flow path between the protruding into the housing 2 Venturi contour shape.
- Fig. 4 shows an enlarged section Fig. 3 In the region of a valve seat 9. This can be seen well the optimized, bevelled contour of the Venturi mold 17, 18, the sealing when placing the valve piston 16 on the valve seat 9 closes.
- the element represented by the reference numeral 19 corresponds to an undercut.
- Fig. 5 is a schematic representation of the hydraulic start-stop system 30.
- One recognizes an internal combustion engine 31, which is coupled via a mechanical coupling 35 with the engine 39 of the displacer unit 1.
- one recognizes the characteristic of the invention within the housing 2 of the displacer unit 1 arranged one-way valve 3, here a check valve.
- the displacer unit 1 is connected at its suction connection 4 to a fluid reservoir 34.
- This fluid reservoir 34 serves as a storage tank for the fluid.
- the displacer 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 via a first valve 36 to a pressure accumulator 32 in connection.
- the fluid reservoir 32 is configured to receive a fluid under a high pressure and store it in itself.
- the working hydraulics is in communication.
- a second valve 37 and a third valve 38 communicate with the outlet port 33.
- the third valve 38 may close or open a flow path between the outlet port 33 and the fluid reservoir 34.
- the second valve 37 may close or open a connection to the pressure accumulator 32.
- a first operating state the working hydraulics is supplied with fluid.
- the valves 38, 37 and 36 are in a closed state.
- the displacer unit 1 is driven by the diesel engine 31.
- the displacer unit 1 sucks in the working fluid, for example a hydraulic oil, via the check valve 3.
- the check valve 3 is designed so that this results along the passage direction as low as possible pressure drop.
- a certain suction pressure must not be exceeded. As a result of this results in a line limitation by the suction pressure.
- the displacer unit 1 conveys the fluid to the valve spool located in the working hydraulics.
- the displacer unit 1 is subjected to a load-sensing control, which ensures that the displacer unit 1 adapts the delivery volume flow in accordance with a volumetric flow demand. In an axial piston machine, this is done by adjusting the skew angle.
- FIG. 5 Another operating state of the in the FIG. 5 shown system loads the pressure accumulator 32.
- the valves 38 and 36 are closed.
- the valve 37 is in its open position.
- the conveyed by the displacer unit 1 fluid is conveyed into the pressure accumulator 32.
- the suction channel 7 of the displacer unit 1 is thus under pressure and the displacer unit 1 operates by motor.
- the powertrain is accelerated, thereby exceeding the starting engine speed, which immediately tows the engine started up to its operating speed. Since the valve 38 is opened, the fluid from the working port 33 of the displacer unit 1 returns to the collecting tank 34. During this starting operation, the working hydraulics can not 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 that the working machine in which, if necessary, drives one or more hydraulic displacement units on the internal combustion engine via a pump distributor gearbox. It is possible that the output power of the internal combustion engine is converted by means of adjustable displacement unit in hydraulic power. It should be noted that the at least one displacement unit is mechanically connected to the internal combustion engine at all times. Furthermore, it can be provided that the at least one displacement unit via a spool the working hydraulics of the mobile working machine, such as. a stem cylinder, a bucket cylinder, a boom cylinder and a drive supplied. Typical applications would be, for example, wheeled excavators, crawler excavators, mobile cranes, etc.
- the use of the hydraulic start-stop functionality is only to be used when the operating temperature of the drive system has been reached, i. H.
- a shutdown of the prime mover should take place only when the operating temperature, in particular that of the engine oil. In a mobile work machine, this not only concerns the operating temperature of the internal combustion engine, but also the hydraulic oil.
- a shutdown of the internal combustion engine is suppressed due to a not yet fully charged pressure accumulator, the shutdown of the engine should not take place until the pressure accumulator is already fully charged, but which are taken into account due to the rotating masses in the drive system (flywheel, gearwheels in the pump transfer case) and the removable energy portion are fed to the pressure accumulator, instead of continuing to load it under continuous fuel consumption.
- the remaining rotational energy is used at the flywheel of the internal combustion engine or a separate speed sensor.
- the present in the accumulator hydraulic oil temperature and the pressure present in the accumulator pressure are measured and taken into account.
- these three variables are read. From this, the time is determined at which, taking into account the losses, sufficient rotational energy for completely charging the pressure accumulator is present.
- the requested shutdown of the internal combustion engine is released. The calculation is based on a stored in the control unit map with the input variables: speed, oil temperature, pressure level in the memory. This results in the energy that can be supplied to the memory to the standstill of the drive. The characteristic is defined for each drive configuration by the results of functional tests.
- hydraulic start-stop system can assist the electric starting operation.
- a torque application of the drive train with the aid of the displacer unit is particularly advantageous when - based on the design of the internal combustion engine as a diesel engine at least accelerated to its starting speed and advantageously to its working speed in the range of 1200 min -1 to 2200 min -1 , preferably 1400 min -1 to 1900 min -1, more preferably 1500 min -1 to 1800 min -1 .
- a torque application of the drive train with the aid of the displacer unit of an internal combustion engine operated in downspeeding mode at least to its starting rotational speed can likewise be undertaken.
- a working speed in the range of 1200 min -1 to 1500 min -1 is preferred. If the speed were to be lowered further, the hydraulic pumps needed to convert mechanical to hydraulic power would have a correspondingly large design. That would be uneconomical.
- the output torque is almost proportional to the swivel angle of the swashplate of an axial piston machine, with the quasi-constant high pressure.
- a hydraulic accumulator in particular a bladder accumulator or a piston accumulator can be used.
- the maximum pressure level in the pressure accumulator is between 100 and 450 bar, preferably 150 to 300 bar and especially at 200 bar.
- the pressure accumulator can be loaded directly via a displacement unit coupled to the internal combustion engine at the power take-off with a fixed ratio.
- the pressure accumulator charging displacer unit can also be located on the primary side of the pump distributor gearbox.
- the pressure accumulator charging displacer unit can also be located on the secondary side of the pump distributor gearbox.
- the pressure accumulator charging displacer unit can be provided exclusively for charging the pressure accumulator.
- the pressure accumulator charging displacer unit can be provided for charging the pressure accumulator and for the operation of at least one secondary consumer. In this case, it is possible that the relevant displacement unit in a certain time interval a) only charges the accumulator, b) is used only for operating the at least one secondary consumer or c) supplies the pressure accumulator and simultaneously at least one secondary consumer.
- the pressure accumulator charging displacer unit may be provided for charging the pressure accumulator and for the operation of at least one main consumer, eg. B. the traction drive.
- the displacer unit in question in a certain time interval a) only charges the accumulator, b) is used only for operating the at least one main consumer or c) supplies the pressure accumulator and simultaneously at least one main consumer.
- the displacer unit charging the pressure accumulator may be identical to the displacer unit that tows up to start the internal combustion engine.
- the pressure accumulator charging displacer unit may be other than the one displacer unit which takes over the same when starting the internal combustion engine.
- Warp-free starting of the internal combustion engine immediately after a torque request or a work request by the driver requires a high torque to accelerate the drive train in a short time.
- a hydraulic starting operation of the proposed system or the availability of a working function of the mobile work machine is faster than in today's electrical starting systems.
- the primary function is the translational movement of the mobile working machine and the operation of the working hydraulics.
- the secondary functions such as (for example, the operation of the air conditioning system, the lighting should preferably be fed from the conventional electrical system during stop operation by secondary consumers to be satisfied.
- the invention enables an increase in comfort and safety due to temporary lower noise pollution at the place of use during the shutdown of the internal combustion engine.
- the loading of the accumulator is also by Rekuperations aber z. B. possible during braking.
- the loading of the memory is also possible by a load point increase.
- the target output power of the internal combustion engine is deliberately chosen to be higher than the required drive power. With the "excess" power, the pressure accumulator is charged.
- the invention also allows an active boost for a short-term power increase provided to the drive. Also, it can be a protection against the stalling of the internal combustion engine obtained.
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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)
Abstract
Die vorliegende Erfindung betrifft eine Verdrängereinheit, insbesondere eine Axialkolbenmaschine, umfassend: ein Gehäuse, ein Triebwerk zum Wandeln einer rotatorischen Leistung in eine hydraulische Leistung, und einen Sauganschluss zum Zuführen eines Fluids an das Triebwerk, wobei ein Einwegventil, das im Gehäuse der Verdrängereinheit angeordnet ist.The present invention relates to a displacement unit, in particular an axial piston machine, comprising: a housing, an engine for converting a rotary power into a hydraulic power, and a suction port for supplying a fluid to the engine, wherein a one-way valve, which is arranged in the housing of the displacer unit ,
Description
Die vorliegende Erfindung betrifft eine Verdrängereinheit sowie ein hydraulisches Start-Stopp-System mit einer solchen Verdrängereinheit.The present invention relates to a displacer unit and a hydraulic start-stop system with such a displacer 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 preferably controllable in the flow volume or controllable hydraulic pump, which is typically mechanically coupled to a primary drive designed as an internal combustion engine. The internal combustion engine usually includes an electric starter for starting the internal combustion engine, which is powered 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 electric starter systems, by electric starter generators representing a combination of starter system and generator in one component, and by hydraulic start-stop systems. During a starting process an internal combustion engine, it is necessary to rotate the output shaft to perform the working 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 for this purpose a hydraulic start-stop system, in which a mechanically coupled to an internal combustion engine displacer unit is driven not only by the internal combustion engine in the "pump mode", but a tempering of the internal combustion engine by using the displacer unit in the "engine operation". If hydraulic power is required for the working hydraulics, the displacer unit is driven by means of the mechanical coupling to the internal combustion engine and sucks a fluid, typically an oil or the like, from a fluid reservoir and transfers this to the working hydraulics on the high pressure side. As a result, it is possible for the working hydraulics, for example, to move an excavator arm or lift the shield 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 by means of the displacer unit. For this purpose, to the inlet opening of the displacer unit, which connects a fluid in the direction of its engine, which can convert a hydraulic power into a rotary power, a branching line which communicates at one of its ends with a fluid reservoir via a one-way valve in connection and with the another of their ends is connected via a switchable valve with a pressure accumulator. If the pressure accumulator has a sufficient amount of fluid under pressure, then 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 displacer unit is opened in order to allow inflow of the pressurized fluid into the displacer 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.When the fluid under pressure reaches the engine, this leads to a rotation of the output shaft of the internal combustion engine coupled to the displacer unit. This necessary when starting an internal combustion engine rotation of the output shaft replaces the typical activity of an electric starter system.
Es ist das Ziel der vorliegenden Erfindung eine für das hydraulische Start-Stopp-System geeignete Verdrängereinheit in vorteilhafter Weise weiterzubilden.It is the object of the present invention advantageously to develop a displacer 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 displacer unit according to the invention, which may in particular constitute an axial piston machine, comprises a housing, an engine for converting the rotary power into a hydraulic power and a suction port for supplying a fluid to the engine. The displacer unit is characterized by a one-way valve, which is arranged in the housing of the displacer 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 displacer unit leads to a reduction of the flow resistance between the hydraulic oil storage tank (also: fluid reservoir) and the pump operating engine of the displacer unit. A lower total flow resistance provides a higher suction limit speed, which characterizes an operating condition of a pump in which a filling stroke occurs due to a vacuum formation in a suction stroke, which can lead to a reduction of the flow rate of the pump and damage to the pump by 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 from the supply line from the storage tank to the one-way valve and the supply line from the one-way valve results in the engine, the total flow resistance decreases when the portion of the highest flow resistance, the Area around the one-way valve, located near the engine. This is due to the fact that the cross section of the intake duct typically decreases in size from the suction connection of the displacer unit to the engine. It can then be carried out at a constant pressure drop (or flow resistance) of the passage cross-section of the check valve the smaller the closer it is to the engine. In addition, a geometrically smaller executed check valve is cheaper to implement and requires less installation space. Therefore, the check valves (also: one-way valves) arranged in the prior art typically outside the housing of the displacer unit can achieve the above-mentioned positive effects.
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, with a motorized use of the displacer unit between the engine and the one-way valve, a high pressure level of the fluid is present. 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 displacer unit, the corresponding hydraulic hose would have to withstand the high-pressure load. According to the displacer unit according to the invention, in which the one-way valve is arranged in the housing itself, a hydraulic hose routed to the suction connection of the displacer unit must be able to withstand only 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 port and the engine.
Vorzugsweise ist das Einwegventil im Gehäuse der Verdrängereinheit integriert.Preferably, the one-way valve is integrated in the housing of the displacer 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 that the one-way valve is arranged in an intake passage of a connection plate of the displacer unit or cooperates 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 decreases from the suction port toward the engine, preferably this reduction is continuous and the one-way valve is located at a position in the flow path where the cross-section of the flow channel is not maximal.
Vorzugsweise ist das Einwegventil im Strömungspfad vom Sauganschluss beabstandet in Richtung Triebwerk angeordnet.Preferably, the one-way valve is arranged in the flow path from the suction port spaced towards 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 development of the invention, the one-way valve is a check valve or a slide valve, preferably a high-pressure actuated slide valve.
Nach einer Fortbildung 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 a development of the invention, the displacer unit further comprises a second port for supplying a fluid to the engine, wherein the flow paths emanating from the first suction port and the second port combine to form a common flow path and the one-way valve in the region between the first suction port and the unified common flow path is arranged.
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 port for supplying a fluid to the engine, the displacer 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 engine operation is used for starting an engine mechanically coupled to the displacer unit. For a stored in a pressure accumulator under pressure fluid is supplied to the engine. In order to prevent a flow of the pressurized fluid into the storage tank, the one-way valve is provided. The inflow of a fluid at the second port and the outflow from the first suction port is thus 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 cooperates with a flow-optimized valve seat. A flow-optimized one-way valve and a flow-optimized valve seat minimize vortex formation during a fluid inflow along a fluid passage opening at the suction port.
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 which can be closed by the one-way valve is preferably a Venturi contour, which 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.As the fluid flows in, e.g. a hydraulic oil, in the pump operating in the displacement unit is reached at the point of the smallest flow cross section, the maximum flow velocity, which causes a supportive for the pump operation suction effect.
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 curvature profile in order to minimize vortex formation of 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.Preferably, the suction port is connectable to a flange plate which is designed as part of a Venturi contour formed with the flow path of the suction port.
Die Erfindung betrifft ferner ein hydraulisches Start-Stopp-System, das eine Verdrängereinheit nach einer der vorhergehend dargestellten Varianten umfasst.The invention further relates to a hydraulic start-stop system comprising a displacer 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 mechanically coupled to the displacer unit and configured to drive the displacer unit and driven by the displacer unit and a pressure accumulator communicating with one outlet port of the displacer unit and with a second one Connection for supplying a fluid to the engine of the displacer unit is connected, wherein the first suction port 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.After 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 displacer unit and via the mechanical coupling between the displacer unit and internal combustion engine exerts a starting movement for the internal combustion engine, wherein preferably for directing the fluid, a first valve between the fluid reservoir and the second port and a second valve between the outlet port and a connection to the fluid reservoir are provided.
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.Furthermore, the present invention also relates to a mobile work machine, in particular a wheeled 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.
- Fig. 1:
- a schematic representation of a displacer unit according to the invention with an integrated check valve,
- Fig. 2:
- a schematic representation of a portion of the displacer unit according to the invention,
- 3:
- a schematic representation of the displacer unit according to the invention according to a further embodiment,
- 4:
- an enlarged detail view of the further embodiment, and
- Fig. 5:
- a circuit diagram for a hydraulic start-stop system according to the invention.
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
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
Das in
Ein weiterer Betriebszustand des in der
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.As another operating condition you can look at the starting of the diesel engine. In order to start the diesel engine, it must be in a stopped state. Then all
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 that the working machine in which, if necessary, drives one or more hydraulic displacement units on the internal combustion engine via a pump distributor gearbox. It is possible that the output power of the internal combustion engine is converted by means of adjustable displacement unit in hydraulic power. It should be noted that the at least one displacement unit is mechanically connected to the internal combustion engine at all times. Furthermore, it can be provided that the at least one displacement unit via a spool the working hydraulics of the mobile working machine, such as. a stem cylinder, a bucket cylinder, a boom cylinder and a drive supplied. Typical applications would be, for example, wheeled 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.Preferably, the use of the hydraulic start-stop functionality is only to be used when the operating temperature of the drive system has been reached, i. H. As known in car start-stop systems, a shutdown of the prime mover should take place only when the operating temperature, in particular that of the engine oil. In a mobile work machine, this not only concerns 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 necessary for starting Hochschleppen the internal combustion engine should preferably always be done with the hydraulic system both at a cold start and a warm start. In order for the latter to be possible, shutdown of the internal combustion engine should only take place and possibly be 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 the detection of leakage in the pressure accumulator and the hydraulic line present only for the storage 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, sondern 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 due to a not yet fully charged pressure accumulator, the shutdown of the engine should not take place until the pressure accumulator is already fully charged, but which are taken into account due to the rotating masses in the drive system (flywheel, gearwheels in the pump transfer case) and the removable energy portion are fed to the pressure accumulator, instead of continuing to load it under continuous 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.To determine the remaining rotational energy is used at the flywheel of the internal combustion engine or a separate speed sensor. To account for the proportion of the rotational energy that can be supplied to the pressure accumulator, the present in the accumulator hydraulic oil temperature and the pressure present in the accumulator pressure are measured and taken into account. In a control unit, these three variables are read. From this, the time is determined at which, taking into account the losses, sufficient rotational energy for completely charging the pressure accumulator is present. At this time, the requested shutdown of the internal combustion engine is released. The calculation is based on a stored in the control unit map with the input variables: speed, oil temperature, pressure level in the memory. This results in the energy that can be supplied to the memory to the standstill of the drive. 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 equipment is still available as a back-up for warm starts and for "cold starts".
Weiter kann das hydraulische Start-Stopp-System den elektrischen Startvorgang unterstützen.Further, the hydraulic start-stop system can assist the electric starting operation.
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.A torque application of the drive train with the aid of the displacer unit is particularly advantageous when - based on the design of the internal combustion engine as a diesel engine at least accelerated to its starting speed and advantageously to its working speed in the range of 1200 min -1 to 2200 min -1 , preferably 1400 min -1 to 1900 min -1, more preferably 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.A torque application of the drive train with the aid of the displacer unit of an internal combustion engine operated in downspeeding mode at least to its starting rotational speed can likewise be undertaken. Based on the design of the internal combustion engine as a diesel engine, a working speed in the range of 1200 min -1 to 1500 min -1 is preferred. If the speed were to be lowered further, the hydraulic pumps needed to convert mechanical to 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.Also, one could make a torque application of the already under load drive train using the displacer unit 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 case of the displacer unit used to tow the engine up, the output torque is almost proportional to the swivel angle of the swashplate of an axial piston machine, with the quasi-constant high pressure.
Als Druckspeicher kann ein Hydrospeicher, insbesondere ein Blasenspeicher oder ein Kolbenspeicher eingesetzt werden.As a pressure accumulator, a hydraulic accumulator, in particular a bladder accumulator or a piston accumulator can be used.
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 at 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 loaded directly via a displacement unit coupled to the internal combustion engine at the power take-off with a fixed ratio. The pressure accumulator charging displacer unit can also be located on the primary side of the pump distributor gearbox. The pressure accumulator charging displacer unit can also be located on the secondary side of the pump distributor gearbox.
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 pressure accumulator charging displacer unit can be provided exclusively for charging the pressure accumulator. The pressure accumulator charging displacer unit can be provided for charging the pressure accumulator and for the operation of at least one secondary consumer. In this case, it is possible that the relevant displacement unit in a certain time interval a) only charges the accumulator, b) is used only for operating the at least one secondary consumer or c) supplies the pressure accumulator and simultaneously at least one secondary consumer.
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 pressure accumulator charging displacer unit may be provided for charging the pressure accumulator and for the operation of at least one main consumer, eg. B. the traction drive. In this case, it is possible that the displacer unit in question in a certain time interval a) only charges the accumulator, b) is used only for operating the at least one main consumer or c) supplies the pressure accumulator and simultaneously at least one main consumer.
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 displacer unit charging the pressure accumulator may be identical to the displacer unit that tows up to start the internal combustion engine. The pressure accumulator charging displacer unit may be other than the one displacer unit which takes over the same when starting the internal combustion engine.
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.Warp-free starting of the internal combustion engine immediately after a torque request or a work request by the driver requires a high torque to accelerate the drive train in a short time. As a result, a hydraulic starting operation of the proposed system or the availability of a working function of the mobile work machine is faster than in 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 economy can be achieved by shutting down the engine when there is no power output to utilize the primary functions is required. The primary function is the translational movement of the mobile working machine and the operation of the working hydraulics. The secondary functions such as (for example, the operation of the air conditioning system, the lighting should preferably be fed from the conventional electrical system during stop operation by secondary consumers to be satisfied.
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 due to temporary lower noise pollution at the place of use during the shutdown of the internal combustion engine.
Das Laden des Druckspeichers ist auch durch Rekuperationsleistung z. B. bei Bremsvorgängen möglich.The loading of the accumulator is also by Rekuperationsleistung 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 loading of the memory is also possible by a load point increase. The target output power of the internal combustion engine is deliberately chosen to be higher than the required drive power. With the "excess" power, the pressure accumulator is charged.
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.Also, a load point reduction is conceivable. The power output of the internal combustion engine is then reduced for a short time. The "power deficit" required to supply the consumers is taken from the 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 allows an active boost for a short-term power increase provided to the drive. Also, it can be a protection against the stalling of the internal combustion engine obtained.
Claims (15)
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Application Number | Priority Date | Filing Date | Title |
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CH00919/16A CH712781A1 (en) | 2016-07-18 | 2016-07-18 | Displacer unit and hydraulic start-stop system with such a displacer unit. |
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EP3273057A1 true EP3273057A1 (en) | 2018-01-24 |
EP3273057B1 EP3273057B1 (en) | 2020-12-30 |
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Citations (5)
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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 |
DE20306851U1 (en) * | 2003-04-24 | 2003-08-14 | Pickel, Peter, Prof. Dr.-Ing., 06116 Halle | Fast start equipment using pressurized fluid to operate a hydrostatic pump as starter motor |
US20050175490A1 (en) * | 2003-10-21 | 2005-08-11 | Takeshi Seto | Check valve and pump including check valve |
JP2007056810A (en) * | 2005-08-25 | 2007-03-08 | Komatsu Ltd | Swash plate type axial piston pump motor |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
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 |
-
2016
- 2016-07-18 CH CH00919/16A patent/CH712781A1/en not_active Application Discontinuation
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2017
- 2017-05-23 EP EP17172414.9A patent/EP3273057B1/en active Active
Patent Citations (5)
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 |
DE20306851U1 (en) * | 2003-04-24 | 2003-08-14 | Pickel, Peter, Prof. Dr.-Ing., 06116 Halle | Fast start equipment using pressurized fluid to operate a hydrostatic pump as starter motor |
US20050175490A1 (en) * | 2003-10-21 | 2005-08-11 | Takeshi Seto | Check valve and pump including check valve |
JP2007056810A (en) * | 2005-08-25 | 2007-03-08 | Komatsu Ltd | Swash plate type axial piston pump motor |
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EP3273057B1 (en) | 2020-12-30 |
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