EP2097223B1 - Wasserstrahlvorrichtung - Google Patents

Wasserstrahlvorrichtung Download PDF

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Publication number
EP2097223B1
EP2097223B1 EP07857582A EP07857582A EP2097223B1 EP 2097223 B1 EP2097223 B1 EP 2097223B1 EP 07857582 A EP07857582 A EP 07857582A EP 07857582 A EP07857582 A EP 07857582A EP 2097223 B1 EP2097223 B1 EP 2097223B1
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EP
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Prior art keywords
pressure
pump
equalising
plunger
waterjet
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EP07857582A
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English (en)
French (fr)
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EP2097223A1 (de
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Donald Stuart Miller
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Finecut AB
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Finecut AB
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24C—ABRASIVE OR RELATED BLASTING WITH PARTICULATE MATERIAL
    • B24C9/00—Appurtenances of abrasive blasting machines or devices, e.g. working chambers, arrangements for handling used abrasive material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24C—ABRASIVE OR RELATED BLASTING WITH PARTICULATE MATERIAL
    • B24C1/00—Methods for use of abrasive blasting for producing particular effects; Use of auxiliary equipment in connection with such methods
    • B24C1/04—Methods for use of abrasive blasting for producing particular effects; Use of auxiliary equipment in connection with such methods for treating only selected parts of a surface, e.g. for carving stone or glass
    • B24C1/045—Methods for use of abrasive blasting for producing particular effects; Use of auxiliary equipment in connection with such methods for treating only selected parts of a surface, e.g. for carving stone or glass for cutting

Definitions

  • the present invention relates to an abrasive waterjet apparatus, and to a pressure fluctuation equalising device for an abrasive waterjet apparatus.
  • Advances in abrasive waterjet apparatus capabilities extend their operation from general machining with cutting jets greater than 300 microns in diameter to fine and micro machining with cutting jet diameters down to 50 microns or so. Low flow ultra high pressure pumps are required for such apparatuses.
  • Abrasive waterjets for fine and micro machining require water flows from under 1 litre per hour up to 10 litres or so per hour and at pressures from 500 bar to 4000 bar or so. Water pressures are similar to those generated by intensifier and crank pumps that power general machining abrasive waterjets (AWJs), but flows are 1 to 10 percent or so of the output of these pumps. Scaled down versions of intensifier pumps used for AWJs are complex and relatively expensive. In scaling down direct driven plunger pumps it is desirable to simplify pump design and to take advantage of electronically controlled, high response drives.
  • a valve is opened before a cutting head to allow ultra high pressure water to flow to a waterjet generating orifice.
  • Air entrainment by a waterjet commences and an abrasive on/off valve is opened in the base of an abrasive hopper, allowing abrasive to be carried by airflow to a cutting head through a tube that is usually more than 300 mm in length.
  • the water shut off valve is closed.
  • AWJs are not dynamic machining tools.
  • Abrasive waterjet machining systems compete most strongly with laser machining systems.
  • a laser can go through a thousand or so cutting cycles in the time that an AWJ goes through one cycle. This means that AWJs cannot compete with lasers when dynamic cutting is required, such as for marking and scribing, and in profiling, drilling and slotting of thin materials.
  • Valves that start and stop ultra high pressure water flow at AWJ cutting head operate for about 150,000 cycles before valve seats fail due to seat to seat impact loads, high water velocities and cavitation. This is not a serious problem for AWJs because they cannot operate in dynamic machining mode, so 150,000 valve cycles are typically reached after a thousand hours or so of cutting time.
  • Fine and micro abrasive waterjets can operate in dynamic machining mode with many starting and stopping cutting cycles per second. This means 150,000 valve on/off cycles can be reached in less than 10 hours of cutting operations.
  • the objective of the invention is to provide an abrasive waterjet apparatus that is able to operate more dynamically, i.e. an apparatus of long life that allows rapid cutting cycles.
  • the apparatus comprises a waterjet fluid flow circuit, a positive displacement pump connected to the waterjet fluid flow circuit, a pressure fluctuation equalising device for said circuit, and an abrasive cutting nozzle assembly.
  • the pressure fluctuation equalising device comprises a high pressure chamber connected to the waterjet fluid flow circuit, a low pressure chamber, and a moveable pressure equalising member that separates said chambers.
  • the moveable pressure equalising member is arranged to alter the volume of the high pressure chamber.
  • Said high pressure chamber can be designed so that fluid contained therein exerts a first force on a first part of the moveable pressure equalising member
  • the low pressure chamber can be designed so that fluid contained therein exerts a second force on a second part of the moveable pressure equalising member.
  • the pressure equalising member can be displaced in accordance with the first and the second force.
  • the cross section area of the first part of the moveable pressure equalising member can be smaller than the cross section area of the second part of the moveable pressure equalising member.
  • a relatively low pressure can be used in the low pressure chamber to balance the high pressure of the high pressure chamber.
  • the relationship of the high pressure and the low pressure may essentially be the same as the relationship of the area of the second part and the first part.
  • Sensor devices which are adapted to detect the position and/or motion of the moveable pressure equalising member, are used to monitor and control the abrasive waterjet apparatus. Further, a motor controller is provided for controlling the drive of the positive displacement pump. In this connection, a control system is used to control the pump on the basis of the position or motion of the moveable pressure equalising member. Now, it is possible to optimise the operation of the abrasive waterjet apparatus in accordance with the pressure of the waterjet fluid flow circuit. E.g., the pump motor may be operated with varying torque and/or speed over one pump revolution to thereby minimise pressure fluctuations.
  • a plunger of the positive displacement pump can be arranged to be returned by the fluid pressure of a fluid conduit.
  • the flow of said fluid conduit can be affected by the position of the pressure fluctuation equalising device. Thereby, the position of the moveable pressure equalising member can stop the pumping action.
  • a predetermined displacement of the moveable pressure equalising member may release the pressure of the fluid conduit.
  • the fluid conduit may be connected to the pressure fluctuation equalising device by means of a connection that can be closed by the moveable pressure equalising member so that a predetermined displacement of the moveable pressure equalising member opens the fluid conduit.
  • the volume of the high pressure chamber can be greater than the volume of waterjet fluid discharged through the nozzle assembly of the abrasive waterjet apparatus during one pump rotation.
  • a direct driven plunger pump feeds ultra high pressure water to a cutting head
  • closure of a valve at a cutting head requires actions that stop excessive water pressures occurring that could damage a pump and an abrasive waterjet flow circuit.
  • a pump is driven dynamically by a servo or other high response motor. Once a pump is operated dynamically it can be desirable to use the pump rather than a valve at a cutting head to start and stop cutting operations. Using a pump dynamically is practical for up to 10 or so cutting cycles per second with a 100 micron cutting jet diameter and at higher frequencies for cutting jets less than 100 microns in diameter.
  • Pressure relief devices for small water flows at ultra high pressures are unreliable and suffer rapid wear and are not suitable for preventing excessive water pressures in fine and micro machining abrasive waterjet apparatus when operating in dynamic machining mode.
  • Pumps for abrasive waterjets operate at the limits of sealing and material technologies. Water leakage from plunger seals can become unacceptable after a few hundred hours of running. Extreme cleanliness is required when replacing plunger seals because of the risk of contaminants blocking waterjet nozzles that, in the case of micro abrasive waterjets, can be less than 20 microns in diameter. It is, therefore, desirable to remove as a unit a pump plunger head including its seals. A replacement unit being fitted and the removed unit serviced in a clean environment.
  • Multi plunger roller cam pumps can generate the pressures and flows required for fine and micro abrasive waterjets.
  • a cam driven plunger is returned by a spring on a suction stroke.
  • using a spring to return a plunger of an ultra high pressure pump leads to design and assembly complexity and difficulties in removing a plunger head as a unit.
  • a spring is used to return a plunger it is not practical to stop a plunger returning for a new pumping stroke.
  • Pressurised fluid acting on a piston connected to a plunger can hold a plunger against a cam or a crank drive.
  • pressurised fluid preferably air
  • to return a plunger simplifies pump design and the removal and replacement of plunger units.
  • a plunger remains at the end of its delivery stroke. This means that, for control and safety reasons, pumping action can be stopped independent of a pump drive motor.
  • a pressure fluctuation equalising device When pump plungers are returned by air pressure, movement of a pressure fluctuation equalising device can be used to cause air pressure on pump pistons to be removed so as to leave pump plungers at the end of their delivery stroke and thereby stop pumping action within one pump rotation. It is beneficial for a pressure fluctuation equalising device plunger stroke volume to be greater than the volume of water discharged during one pump rotation. Alternatively it can be arranged that a pressure fluctuation equalising device plunger be allowed to withdraw through its seals to vent fluid pressure if other control actions to limit excessive water pressures fail. This option allows commonality of plunger assemblies between a pump and a pressure fluctuation equalising device.
  • Interfacing a servo or other high response pump drive and control system with a pressure fluctuation equalising device monitoring and control system allows considerable flexibility in carrying out abrasive waterjet machining operations.
  • the displacement or motion of a pressure fluctuation equalising device piston can be readily measured and fluid pressure acting on a piston accurately controlled.
  • Power input to a pump motor to achieve desired water pressures could be established from an electronically controlled power supply for a motor. Knowing the area/pressure ratio across a pressure fluctuation equalising device and varying the air pressure acting on a pressure fluctuation equalising device piston, whilst measuring pump speed and input power to just displace a pressure fluctuation equalising device plunger, a pump/flow system characteristic curve can be established. By establishing the characteristic curve a pressure sensor subjected to extreme pressure and fatigue loading is not needed in a water circuit. By routinely monitor the power input to achieve given water pressures, waterjet nozzle and seal wear and the operation of pump inlet and outlet valves can be monitored.
  • a pressure fluctuation equalising device can be used in a dynamic mode to damp out variations in pump pressure during steady state running.
  • a pressure fluctuation equalising device operates in a dynamic mode when the frequency of operation of a valve is such that a pump cannot respond sufficiently fast to maintain pressures below a set level.
  • an abrasive waterjet apparatus according to claim 1.
  • the pressurised fluid is preferably air.
  • Pressurised air acting on a first piston may be vented to leave a first plunger at the end of its delivery stroke.
  • Venting of pressurised air acting on first pistons may be initiated by movement of said second piston.
  • a second plunger can withdraw through its seals if other actions to avoid too high water pressure fail.
  • the pressurised fluid acting on second piston is preferably air.
  • Pumps preferably have three to five plungers.
  • the pump drive motor may be a high response electric, air or hydraulic motor.
  • a pump is driven by an electric servomotor.
  • the motor drive control system may be capable of limiting the pressure generated by first plungers.
  • the pump motor drive systems may be capable of varying the instantaneous pump motor rotational speed/torque to provide near constant water delivery pressure.
  • Movement of second plunger/piston may be monitored by a linear displacement transducer, or sensor/s or switch/s and signals fed to a pump motor drive and control system.
  • the pressurising fluid acting on the first pistons is air.
  • First pistons may act as linear bearings to carry side loads.
  • First plungers and first pistons are advantageously machined as a single unit from zirconia, tungsten carbide or other ceramic.
  • the inlet and outlet non-return valves for a plunger head may be in a manifold that connects and seals to the plunger head through the closure of a clamp or other device and separates from the plunger head on opening the clamp or other device.
  • the pressurised fluid acting on second piston is preferably air.
  • the pressure fluctuation equalising device may act as a pressure pulsation damper for pump delivery.
  • a plunger may be withdrawn through its high pressure sealing assembly to vent pump pressure if pumping action does not cease or to vent pressure in a flow circuit.
  • Fluid pressure acting on a piston of a pressure fluctuation equalising device may be vented when a pump is stopped to ensure depressurisation of abrasive waterjet apparatus.
  • Pressurise water may flow directly from a pump to said cutting head and pass through a waterjet generating device to create a high velocity waterjet that entrains abrasive particles to create an abrasive waterjet.
  • Pressurised water may flow to part of an apparatus where it generates an abrasive/water mixture that flows to a nozzle in a cutting head to generate an abrasive waterjet.
  • Pressurised water may flow to part of an apparatus where it causes abrasive/water mixture to flow to a nozzle in a cutting head to generate an abrasive waterjet.
  • FIG. 1 shows a cross section through a multi cylinder cam driven plunger pump.
  • Shaft 1 rotates in bearings 2 and 3, carried in housing 4, and has a cam bearing 5 located off the centre line of rotation of shaft 1.
  • the cam bearing 5 acts on plunger 6 that reciprocates in plunger head 7 retained to pump body 8.
  • Pump body 8 is attached to bearing housing 4.
  • plunger 6 in contact with cam bearing 5 forms a piston 9 that reciprocates in cylinder housing 10 located in pump body 8.
  • the piston 9 moving in cylinder housing 10 acts as a bearing to take side loads from the cam 5 and plunger 6 interaction.
  • Plunger 6 is advantageously made from ceramic material, either as a single item with piston 9 or piston section 9 may be made of a material such as hardened steel and shrunk fit or.attached by other means to plunger 6.
  • the piston section 9 of plunger 6 may have a polymeric or other bearing liner and the bore in plunger head 7 may have a polymeric or other bearing liner.
  • Cylinder housing 10 has a flange 11 retained between pump body 8 and plunger head 7 with an cylindrical extension 12 that locates plunger head 7 and retains plunger seal assembly 13 in plunger head 7. Passageways 18 in cylinder housing 10 vent any water leaking through plunge seal assembly 13 and/or allow a flow of cooling water for seal assembly 13.
  • Pressurised air from source 16 enters through a passageway 19 in cylinder housing 10 to space 17 in cylinder 10 that is formed between seal 15 on piston 9 and seal 14 in cylinder housing 10.
  • plunger 6 When air in space 17 is pressurised plunger 6 is held against cam 5 during suction strokes causing water from source 40 to flow throw inlet non-return valve assembly 41, passage 44 and into plunger bore 46 in plunger head 7.
  • cam 5 On a delivery stroke cam 5 causes plunger 6 to displace pressurised water through passage 45, non-return valve assembly 42 into connection 43.
  • air in space 17 is not pressurised plunger 6 is left at the end of its delivery stroke.
  • Shaft 1 may be driven by a motor, with or without a gearbox 70 with a shaft 71 that transmits power to pump shaft 1 through key 72 or splines.
  • Sensor 80 may detect rotational position of shaft 1 for use by a motor control system or a drive motor may have an encoder to provide rotational position.
  • a pump may be driven by a servo or other high response motor and have a control system that operates in torque limiting mode to minimise the risk of pump pressures exceeding safe levels.
  • Servo motors allow the instantaneous pump rotational speed to be varied over a pump revolution to compensate for non steady pressure/flow discharge characteristics that result from pumps having a finite number of plungers. The fluctuations in pump delivery pressure can be reduced by increasing the pump speed in order to counteract the fluid pressure valleys of the pump, i.e. during the phases when pump pressure falls below the average working pressure.
  • Plunger head 7 may be retained to pump body 8 by bolts or studs (not shown) or by a quick release mechanism.
  • Figure 2 shows a side view of a plunger assembly that differs from that in Figure 1 in that plunger head 7 is attached by threaded connection to cylinder housing 10 and has a feature 48 that locates in a mating feature 47 in pump body 8.
  • features 47 and 48 may be interrupted around their circumference a plunger assembly may be rotated an eighth of a turn or so to allow plunger head 7, cylinder housing 10 and plunger 6 to be withdrawn as a unit.
  • the inlet 41 and outlet 42 non-return valves may be combined in a separate assembly 80 that connects by passage 82 to plunge cylinder bore 45.
  • a metal to metal seal 83 between plunger head 7 and no-return valve assembly 80 may seal passageway 82 or alternatively a polymeric sealing arrangement can be used.
  • Non-return valve assembly 80 may be retained by a quick release clamp (not shown) to plunger head 7.
  • plunger head 7 and cylinder housing 10 When it is not required to remove plunger 6, plunger head 7 and cylinder housing 10 as a complete assembly the cylinder part of cylinder housing 10 may not be necessary. Piston section 9 of plunger 6 may reciprocate in a cylinder bore formed in pump body 8.
  • Figure 3 shows a pressure fluctuation equalising device 24 that has a plunger 20 connected to or acting on a piston 21 moving in chamber 29. Pressurised water from connection 27 connected to pump outlet 43 acts on water in high-pressure chamber 27'. Pressurised air from a controlled source 28 connected to chamber 29 acts on piston 21. When the pressure in chamber 27' times the area of plunger 20 exceeds the pressure in chamber 29 times the area of piston 21 plunger/piston 20/21 is displaced.
  • Sensors may be used to detect movement/displacement of piston 21 for use by a pump motor controller and/or abrasive waterjet controller. Sensor signals can be used to stop a pump, to vary the speed of a pump, and to set pump pressure in conjunction with a pressure controller for air source 28.
  • the ability to sense movement of piston 21 is particularly useful when a pump is operating in dynamic mode, such as machining multiple features per second that require a pump to cycle from near atmospheric pressure to water pressures that can exceed 3000 bar.
  • the air pressure in chamber 29 can be set so that the water pressure at a cutting nozzle is slightly above that desired before piston 21 moves.
  • the pump motor controller can then be set so that the motor speed or torque is slightly below that needed to move piston 21.
  • pressure fluctuation equalising device 24 can be used to stop pumping action by venting the air pressure from conduit 16 and space 17 to leave plunger/pistons 6/9 at the end of their stroke.
  • One arrangement for venting conduit 16 through a connection 30 to atmosphere is shown on Figure 3 .
  • Seal 22 on piston 21 prevents air from venting from connection 16' to connection 30 when piston 21 is held against seat 26 and seal 23 isolates air in volume 29 from connection 16'.
  • High-pressure seal assembly 25 provides a seal on plunger 20.
  • the length of chamber 29 may be made sufficient for plunger 20 to withdraw through high-pressure seal assembly 25 if pump water pressure at connection 27 does not decrease.
  • the volume swept by displacement of plunger 20 is preferentially greater than the water discharge during one pump revolution.
  • venting air from conduit 16 may involve mechanical connection from plunger/piston 20/21 to an air release valve located outside of the envelope of pressure fluctuation equalising device 24.
  • Sensing the velocity or acceleration of piston 21 could provide information to determine whether a pump motor should be stopped, such as when a nozzle blocks, or when pump speed should be reduced, such as when a cutting program calls for too high a pump speed or a valve on a multi headed cutting system is closed without instructions to a pump controller to reduce pump speed.
  • Such movement/displacement sensors for the piston 21 may be arranged in the low pressure chamber 29 wall or preferably located between high-pressure seal assembly 25 and piston 21 where sensors are effectively at atmospheric pressure and line of sight sensing is easily achieved.
  • Chamber 29 may be sized to accommodate compression of air in the chamber 29 when piston 21 moves or it may be connected through connection 28 to another air volume or to a controlled fluid pressure source.
  • pressure fluctuation equalising device 24 can act to damp out pump generated pressure fluctuations in connection 27. However, this will adversely effect the life of seal 25 making it desirable to use a servo motor drive with varying torque or speed control over one pump revolution to minimise pressure fluctuations.
  • Figure 4 shows a pump with 3 plunger assemblies feeding a water circuit for an abrasive cutting head 50. Also shown are connections 16 between cylinder volume 17 and the pressure fluctuation equalising device 24 of Figure 3 . Discharge from a plunger head 7 passes through non-return valves 42 into conduit 43 which is connected via conduit 53 to abrasive cutting nozzle assembly 50 and to pressure fluctuation equalising device 24 via conduit 27. Nozzle assembly 50 is fed with abrasive via conduit 52 from abrasive feed hopper 51. Conduits 16 connect the cylinder volumes 17 to the pressure fluctuation equalising device 24 and to fluid control unit 60. Fluid control unit 60 may have provision for rapidly increasing and decreasing the pressure in cylinder volumes 17, and in maintaining a bleed flow of air to compensate for air losses during normal pumping operations.
  • pressure fluctuation equalising device 24 can be used to supplement pump action and rapidly increase pressure in connection 27.
  • fluid pressure applied through connection 28 causes flow through connection 27 until pump pressure increases to the desired level or piston 21 reaches piston seat 26.
  • water pressure at nozzle assembly 50 can be rapidly reduced by venting pressure in connection 28 at the same time as stopping the pump motor.
  • Pumps may be driven by servomotors with encoders thereby allowing the rotational position of the pump to be continuously monitored. Forward prediction can be made as to when to load and off load plungers 6 to start and stop flows from cutting nozzles and also to vary power input to motors to minimise fluctuations in pump delivery pressure over one pump revolution. Pumps with multiple cylinders may have individual or sets of cylinder return piston spaces 17 connected to pressure fluctuation equalising devices 24 and/or fluid control units 60.
  • the diameter of piston 9 on pump plunger 6 and piston 21 on pressure fluctuation equalising device 24 depends on the pressure of air sources 16 and 28.
  • the diameter of pistons 9 and 21 can be minimised by operating at a high an air pressure as practical and this air pressure is generally above the 6 bar or so generally used in workshops.
  • the demand for air for sources 16 and 28 is small and may be met by a single cylinder compressor 61 driven by cam 5 as shown in Figure 5 .
  • Piston 57 with seal 58 slides in cylinder 56 that has air inlet 59 and air outlet 60 non-return valves.
  • Plunger 62 attached to piston 57 and reciprocating in bearing 54 is driven by cam 5 on a delivery stroke and returned by spring 55. If inlet non-return valve 59 is connected to a source of pressurised air spring 55 is not required.
  • An alternative method of providing air at pressures above those of source 16 is for air from source 16 to flow through a non return valve to space 17 in cylinder housing 10 for the return stroke of plunger 6 and to discharge air from space 17 through a non return valve to an accumulator that acts as source 28.
  • a means to vent air from space 17 can be provided to stop pumping action.
  • a pump plunger may be driven by a reciprocating member 70 as shown on Figure 6 .
  • Member 70 may be driven by a cam or a crank 75 and onto which the piston end 71 of plunger 80 can be held by pressurised air in space 17 in manner described in relation to the pump of Figure 1 .
  • Contact between plunger 76 and reciprocating member 70 can take the form of spherical seat and socket 74. Using an intermediary reciprocating member 70 between a cam or crank 75 and a plunger 76 is particularly beneficial in minimising bending loads on plunger 76.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (6)

  1. Abrasive Wasserstrahlvorrichtung, umfassend
    einen Wasserstrahlfluidströmungskreislauf (43),
    eine Druckpumpe, die mit dem Wasserstrahlfluidströmungskreislauf (43) verbunden ist,
    eine Druckfluktuationsausgleichsvorrichtung (24) für den Kreislauf (43) und
    eine abrasive Schneiddüsenanordnung (50),
    wobei die Druckfluktuationsausgleichsvorrichtung (24)
    eine Hochdruckkammer (27'), die mit dem Wasserstrahlfluidströmungskreislauf (43) verbunden ist,
    eine Niederdruckkammer (29) und
    ein bewegliches Druckausgleichselement (20, 21), das die Klammern (27', 29) trennt, aufweist,
    wobei das bewegliche Druckausgleichselement (20, 21) dazu angeordnet ist, das Volumen der Hochdruckkammer (27') zu verändern, um Druckfluktuationen in dem Wasserstrahlfluidströmungskreislauf (43) auszugleichen,
    dadurch gekennzeichnet, dass die abrasive Wasserstrahlvorrichtung
    eine oder mehrere Sensorvorrichtungen, die dazu angepasst sind, die Position und/oder Bewegung des beweglichen Druckausgleichselements (20, 21) zu detektieren,
    eine Motorsteuerung zum Steuern des Antriebs der Druckpumpe und
    ein Steuerungssystem, mit dem die Sensorvorrichtungen und die Motorsteuerung verbunden sind, wodurch das Steuerungssystem dazu angepasst ist, die Pumpe auf der Grundlage der Position oder Bewegung des beweglichen Druckausgleichselements (20, 21) zu steuern, umfasst.
  2. Abrasive Wasserstrahlvorrichtung nach Anspruch 1, wobei die Hochdruckkammer (27') so gestaltet ist, dass Fluid, das in ihr enthalten ist, eine erste Kraft auf einen ersten Teil (20) des beweglichen Druckausgleichselements ausübt, und die Niederdruckkammer (29) so gestaltet ist, dass Fluid, das in ihr enthalten ist, eine zweite Kraft auf einen zweiten Teil (21) des beweglichen Druckausgleichselements ausübt, und wobei das Druckausgleichselement (20, 21) so angeordnet ist, dass es in übereinstimmung mit der ersten und zweiten Kraft verschoben wird.
  3. Abrasive Wasserstrahlvorrichtung nach Anspruch 2, wobei die Querschnittsfläche senkrecht zu der Bewegungsrichtung des ersten Teils (20) des beweglichen Druckausgleichselements kleiner als die Querschnittsfläche senkrecht zu der Bewegungsrichtung des zweiten Teils (21) des beweglichen Druckausgleichselements ist.
  4. Abrasive Wasserstrahlvorrichtung nach einem der Ansprüche 1 bis 3, wobei ein Kolben (6) der Druckpumpe dazu angeordnet ist, durch den Fluiddruck einer Fluidleitung (16) zurückgeführt zu werden und wobei die Strömung der Fluidleitung (16) durch die Position der Druckfluktuationsausgleichsvorrichtung (24) beeinflusst wird, wodurch die Position des beweglichen Druckausgleichselements (20, 21) den Pumpbetrieb anhalten kann.
  5. Abrasive Wasserstrahlvorrichtung nach Anspruch 4, wobei die Fluidleitung (16) mit der Druckfluktuationsausgleichsvorrichtung (24) durch eine Verbindung (16') verbunden ist, welche Verbindung (16') dazu angeordnet ist, durch das bewegliche Druckausgleichselement (20, 21) geschlossen zu werden, und welche Verbindung (16) dazu angeordnet ist, auf eine Bewegung des beweglichen Druckausgleichselements (20, 21) geöffnet zu werden.
  6. Abrasive Wasserstrahlvorrichtung nach Anspruch 4 oder 5, wobei das Volumen der Hochdruckkammer (27') größer als das Volumen des Wasserstrahlfluids ist, das durch die Düsenanordnung (50) der abrasiven Wasserstrahlvorrichtung während einer Pumpenumdrehung abgegeben wird.
EP07857582A 2006-12-14 2007-12-14 Wasserstrahlvorrichtung Active EP2097223B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0624892.6A GB0624892D0 (en) 2006-12-14 2006-12-14 Plunger pump
PCT/EP2007/063936 WO2008071785A1 (en) 2006-12-14 2007-12-14 Waterjet device

Publications (2)

Publication Number Publication Date
EP2097223A1 EP2097223A1 (de) 2009-09-09
EP2097223B1 true EP2097223B1 (de) 2012-06-20

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EP07857582A Active EP2097223B1 (de) 2006-12-14 2007-12-14 Wasserstrahlvorrichtung

Country Status (4)

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US (1) US20100120332A1 (de)
EP (1) EP2097223B1 (de)
GB (1) GB0624892D0 (de)
WO (1) WO2008071785A1 (de)

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WO2013135538A1 (en) 2012-03-11 2013-09-19 Finepart Sweden Ab An abrasive jet system

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US8905817B2 (en) * 2009-09-16 2014-12-09 Penn United Technologies, Inc. Clamping assembly for a waterjet
US20140087637A1 (en) * 2012-09-25 2014-03-27 Paul L. Miller Abrasive Waterjet Cutting System For Subsea Operations
CN106286187A (zh) * 2016-08-30 2017-01-04 苏州品诺维新医疗科技有限公司 一种柱塞泵

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US5772414A (en) * 1997-01-24 1998-06-30 Tetra Laval Holdings & Finance, S.A. Pump head pressure equalizer with biasing member limited movement diaphragm
JPH10329890A (ja) * 1997-05-30 1998-12-15 Koei:Kk 粉粒体供給装置
GB9719550D0 (en) * 1997-09-16 1997-11-19 Miller Donald S Fluid abrasive jets for machining
CA2304407A1 (en) * 2000-04-03 2001-10-03 Gordon Enderle Multi-piston intensifier
GB0110134D0 (en) * 2001-04-25 2001-06-20 Miller Donald S Abrasive fluid jet machining apparatus and method

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013135538A1 (en) 2012-03-11 2013-09-19 Finepart Sweden Ab An abrasive jet system

Also Published As

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EP2097223A1 (de) 2009-09-09
US20100120332A1 (en) 2010-05-13
WO2008071785A1 (en) 2008-06-19
GB0624892D0 (en) 2007-01-24

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