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EP0251152A1 - Dispositif pour produire un jet de liquide à grande vitesse - Google Patents

Dispositif pour produire un jet de liquide à grande vitesse Download PDF

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Publication number
EP0251152A1
EP0251152A1 EP87109009A EP87109009A EP0251152A1 EP 0251152 A1 EP0251152 A1 EP 0251152A1 EP 87109009 A EP87109009 A EP 87109009A EP 87109009 A EP87109009 A EP 87109009A EP 0251152 A1 EP0251152 A1 EP 0251152A1
Authority
EP
European Patent Office
Prior art keywords
valve body
liquid
valve
pipeline
pressure
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.)
Withdrawn
Application number
EP87109009A
Other languages
German (de)
English (en)
Inventor
Gerd E.A. Dr. Meier
Andreas Unrau
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Max Planck Gesellschaft zur Foerderung der Wissenschaften
Original Assignee
Max Planck Gesellschaft zur Foerderung der Wissenschaften
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Max Planck Gesellschaft zur Foerderung der Wissenschaften filed Critical Max Planck Gesellschaft zur Foerderung der Wissenschaften
Publication of EP0251152A1 publication Critical patent/EP0251152A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/06—Use of pressure wave generated by fuel inertia to open injection valves
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61H—PHYSICAL THERAPY APPARATUS, e.g. DEVICES FOR LOCATING OR STIMULATING REFLEX POINTS IN THE BODY; ARTIFICIAL RESPIRATION; MASSAGE; BATHING DEVICES FOR SPECIAL THERAPEUTIC OR HYGIENIC PURPOSES OR SPECIFIC PARTS OF THE BODY
    • A61H9/00—Pneumatic or hydraulic massage
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/02—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to produce a jet, spray, or other discharge of particular shape or nature, e.g. in single drops, or having an outlet of particular shape
    • B05B1/08—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to produce a jet, spray, or other discharge of particular shape or nature, e.g. in single drops, or having an outlet of particular shape of pulsating nature, e.g. delivering liquid in successive separate quantities ; Fluidic oscillators
    • B05B1/083—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to produce a jet, spray, or other discharge of particular shape or nature, e.g. in single drops, or having an outlet of particular shape of pulsating nature, e.g. delivering liquid in successive separate quantities ; Fluidic oscillators the pulsating mechanism comprising movable parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B3/00—Cleaning by methods involving the use or presence of liquid or steam
    • B08B3/04—Cleaning involving contact with liquid
    • B08B3/10—Cleaning involving contact with liquid with additional treatment of the liquid or of the object being cleaned, e.g. by heat, by electricity or by vibration

Definitions

  • the invention relates to a device for generating a high-speed liquid pulse jet, having a pipe which has at one pipe end a valve with a valve body, which can be moved from an initial position into an operating position, and an actuating device acting on the valve body and at a distance from one another this pipe end is connected to a liquid inlet.
  • the invention achieves the object of designing such a device in such a way that the high-speed liquid pulse jet is generated using the flow energy of a low-pressure flow in the pipeline.
  • the pulse jet is thus generated by utilizing the known liquid hammer, which arises when a flow in a pipeline is braked very quickly within a period of time which, according to Joukowski, must be less than twice the pipeline length divided by the speed of sound in the liquid .
  • the liquid becomes compressible in the area of the rapid flow change, whereby a pressure pulse arises which, according to the invention, accelerates part of the liquid at the pipe end containing the valve, which exits the device as a high-pressure pulse jet through the jet opening.
  • valve body which controls a flow opening for the flow in the pipeline, is moved under the flow pressure against the force of a return spring onto its valve seat, as a result of which the flow opening is shut off and the flow is suddenly stopped while generating the liquid blow.
  • the resulting sound pulse is emitted via a membrane or the like.
  • a high-pressure pulse jet is generated by opening at least one jet opening at the pipe end having the valve, which is preferably designed as a converging nozzle and which is open at the latest in the operating position of the valve body, so that the liquid jet due to the pressure increase in the pipe can arise as a result of the occurrence of the liquid hammer in the operating position of the valve body.
  • the pressure that builds up due to the liquid hammer is many times higher than the excitation pressure for the liquid flow that is decelerated. Therefore, separate high-pressure generating devices are not required for the formation of the high-pressure jet.
  • the increase in pressure that occurs in the pipeline due to the liquid hammer subsequently decreases again, as a result of which the generated pulse jet decays.
  • the valve body is then moved back into its starting position, after which the flow in the pipeline is started again and, by moving the valve body into the operating position, it is braked again to generate a further pressure pulse and thus high-speed jet.
  • a targeted reduction of the pressure increase in the pipeline and therefore in the region of the jet opening can be favored in that the pipeline end facing away from the valve opens into an acoustically soft device which reflects the pressure wave generated by the liquid shock as a dilution wave.
  • the pressure is reduced by the dilution wave returning to the valve, as a result of which the velocity of the liquid jet discharged from the jet opening also decreases.
  • the wave of dilution is in turn according to Re flexion at the pipeline end having the valve is reflected at the acoustically soft pipeline end as a pressure wave which contributes to the renewed start of the flow towards the pipeline end having
  • the acoustically soft device can e.g. B. be a damping container with a gas volume, which is completed with a piston or a membrane to the associated pipe end.
  • a damping container with gas-filled elastomer bubbles such as rubber balls, e.g. Tennis balls, proven.
  • the device according to the invention it is necessary that in the pipeline under the supply pressure or by means of a separate flow drive arranged in the pipeline, a flow directed towards the pipeline end containing the valve is formed, which can then be braked suddenly with the generation of the liquid hammer.
  • the liquid column in the pipeline together with the valve body in the starting position which in this case is designed in the manner of a piston which can be displaced in the pipeline, can be accelerated to a sufficient flow rate.
  • a flow opening having a larger cross section than the jet opening is provided, the flow opening being open for the liquid passage in the starting position of the valve body and being closed by the valve body in the operating position.
  • the valve body can, for example, be a rotary body which can be rotated by means of the adjusting device about an axis running perpendicular to the pipe axis and is pierced perpendicularly to the axis of rotation, so that in its initial position it at least partially releases the pipe cross-section with the aid of the bore and after it has turned 90 ° is turned into its operating position, shuts off the cross section of the pipeline for braking the liquid flow.
  • the valve body is preferably pivotable or in particular displaceable in the axial direction of the pipeline, the operating position of the valve body being determined by a stop. It can be provided that the valve body is moved into its operating position by means of a controlled actuating device as soon as the liquid flow is to be braked, and is returned to the starting position by means of the actuating device or a separate resetting device.
  • the device according to the invention can also be designed such that the valve body is moved from its initial position into the operating position under the liquid pressure which acts on the valve body due to the fully developed liquid flow, without additional drive, the actuating device returning as the valve body in its initial position Reset device is formed.
  • This resetting device is in particular a spring acting on the valve body, which is weak enough on the one hand that the valve body moves under the flow pressure of the liquid in the fully developed flow against the force of the return spring into the operating position, but on the other hand is strong enough to move the valve body in its initial position can be attributed when the liquid pressure in front of the valve body has sufficiently decreased again after the liquid pulse jet has been emitted before the liquid flow is fully built up again. It is also possible to lock the valve body in its initial position and to release it in a controlled manner for the movement into the operating position at a selected point in time.
  • the resetting device can also be designed as a controllable actuator, from which the valve body is driven back from the operating position into the starting position and from which the valve body is released again in the starting position for its movement driven by the flow pressure into the operating position, possibly at a controlled predetermined time .
  • the pipeline can be designed as a pipeline section of limited length.
  • the pipeline can also be designed as a circulation line, which can be shut off by the valve body while interrupting the circulation flow.
  • the "pipe end" having the valve is understood to mean that part of the pipe which has the valve.
  • a liquid container can be connected into the circulation line, which on the one hand forms the liquid inlet by means of a pump arranged in the pipeline and in which on the other hand the liquid is returned with the valve open.
  • an adjustable stroke limiting device cooperating with the valve body in its starting position can be provided.
  • the frequency and the pressure value of the liquid pulse jet can be adjusted via the spring force acting on the valve body in the starting position as a function of the supply pressure.
  • the jet opening can also be open in the initial position of the valve body. Then, as soon as a liquid flow occurs in the pipeline, an initial jet with low flow velocity flows out of the jet opening before the liquid hammer occurs and the high-pressure jet is generated. However, since this has a significantly higher flow velocity than the initial jet, it can be "overtaken" by the high-pressure jet, which penetrates into the initial jet and can burst. If this is to be avoided depending on the field of application of the invention, it can be ensured that the jet opening is shut off in the starting position of the valve body, preferably also during its movement into the operating position until the liquid impact occurs.
  • valve body in cooperation with the pipe wall or - if the jet opening is formed in the valve body itself - by means of a shut-off device, e.g. B. a mandrel can be reached, which projects into the jet opening in the starting position of the valve body.
  • a pressure valve e.g. B. to provide a spring-loaded, outward-opening check valve, which only opens when there is a certain pressure relative to the normal pressure in the pipeline when the pressure rises due to the liquid hammer.
  • the pressure pulse When the liquid hammer occurs, when the flow at the valve body assuming its operating position and / or the pipeline end having the valve is braked, the pressure pulse also acts on the pipeline itself, so that it is accelerated. In order to avoid or at least mitigate such a setback, the end of the pipeline, which is remote from the valve, can be returned to the end having the valve in such a way that the pipeline ends point in the same direction and are aligned with one another. As a result, the pressure pulse for the pipeline acting on the pipeline end at which the liquid hammer is generated is at least partially compensated for.
  • the invention can be applied in such a way that when the pipeline is formed between the liquid inlet and the jet opening as a circulation line, in which a flow drive can be arranged, an annular flow is started, which is diverted to an accumulation device in order to generate the liquid impact by interrupting the annular flow, at which the deflected liquid is suddenly braked to produce the liquid impact and at which the jet opening opens.
  • This storage device can be directly a wall of the pipeline containing the jet opening.
  • the pipeline is preferably relatively stiff. If, however, the pipeline can increase its diameter and / or its length due to the pressure that acts on it during the liquid blow, this affects the pressure amplitude and the duration of the pulse jet emerging through the jet opening.
  • the invention can with appropriate training of the device, for. B. for vehicle cleaning, building cleaning, sewer cleaning, training massage showers, injecting fuel into the intake line or the cylinders of an internal combustion engine and the like. It is also possible to charge a high-pressure accumulator using the pulsating high-pressure jets.
  • embodiments are possible with which low-frequency or high-frequency interval operation for generating pulsating high-pressure jets, resonance operation or single-pulse operation with a large pressure amplitude of the high-speed impulse jet are possible.
  • the device contains a pipeline 5 which is connected to a liquid inlet 2 and at a distance from the river fluid inlet 2 has a valve head 22 with a plate valve body 3 which, in cooperation with a valve seat designed as a stop 8, controls a flow opening 7.
  • the valve body 3 is pierced to form a jet opening 12 and is pressed into the open position of the valve by a return spring 4.
  • the pipeline 5 opens into an acoustically soft device 1, which is designed as a damping container with pressure-compliant damping material.
  • the sound wave created by the liquid shock in the valve head 22 runs back in the pipeline 5 and is reflected on the acoustically soft device 1 as a dilution wave, by which the pressure in the valve head 2 is reduced. This also reduces the speed of the liquid jet emerging from the jet opening 12.
  • the dilution wave is reflected on the valve body 3 in its operating position as a dilution wave, whereby the pressure in the pipeline 5 is additionally reduced.
  • the frequency of this process and the pressure amplitude of the pressure pulse jet depend on the spring constant of the return spring 4, the ratio of the areas of the valve opening 7 to the jet opening 12, the stroke of the valve body 3 and the cross-sectional area of the pipeline 5.
  • An increase in the spring constant, the ratio of the cross-sectional areas of the flow opening 7 and the jet opening 12 and the stroke of the valve body 3 as well as a reduction in the cross section of the pipeline 5 result in a lowering of the frequency of the liquid pulse jet.
  • the frequency and pressure amplitude also depend on the supply pressure and the acoustic impedance of the system. If the frequency increases, the pressure amplitude of the liquid pulse jet output decreases, since the liquid in the pipeline 5 is no longer accelerated to very high flow rates.
  • an adjustable stroke limiting device 6 is additionally provided for the valve body 3.
  • the frequency of the output pulse beams can be controlled.
  • a low frequency of the pulse beams results in a high pressure of the same.
  • a low-frequency high-pressure interval operation is obtained in this frequency range.
  • the device works in high-frequency interval operation with liquid pulse jets of lower pressure.
  • the full width at half maximum of the pressure pulses depends on the impedance of the system. This means that by selecting suitable materials for the pipelines 5 (influence of elasticity) and the damping material in the acoustically soft device 1, the duration of the liquid pulse jet can be influenced.
  • the device can also be operated in resonance mode.
  • the frequency of the valve is synchronized with the running time of the sound waves in the pipeline 5.
  • the sound waves reflected in the pipeline 5 add up with the pressure increase due to the liquid jet when the valve closes. This increases the speed of the high pressure pulse jet again.
  • FIG. 3 enables the same operating modes as the embodiments according to FIGS. 1 and 2.
  • Valve body 3 is provided a swivel plate which has a return spring on its axis and which is pierced several times to form a plurality of jet openings 12.
  • the device from FIG. 4 is suitable for single-pulse operation with a large pressure amplitude of the output high-pressure jets.
  • the valve body 3 is designed as a piston which is displaceable in the valve head 22 and which can be moved back into the starting position by means of a controlled actuator 9 from the operating position in which the actuator body 3 blocks the flow opening 7.
  • the valve body 3 is released by the actuator 9, so that the valve body 3 is moved under the pressure of the liquid column flowing in the pipeline 5 against the stop 8 forming the valve seat, as a result of which the valve body 3 and thus the liquid column in the pipeline 5 are suddenly braked.
  • FIG. 5 A device according to the invention is shown schematically in FIG. 5, which corresponds in principle to that in FIGS. 1 to 4, the acoustically soft device 1 being a pneumatic container with a counter to the force of a spring 18, which is also represented by the compression of the gas volume in the container can, displaceable piston 17 is shown.
  • a stroke limiting device 6 is provided for the valve body 3 according to FIG. 5, which is simultaneously designed as a shut-off device 15, by which the jet opening 12 is shut off in the starting position of the valve body 3.
  • the adjustable stroke limiting device 6 for the valve body 3, of which the shut-off device 15 for the jet opening 12 is formed in the valve body 3 in its initial position is designed as an axially adjustable mandrel, which in the initial position of the valve body 3 in the jet opening 12 engages and therefore blocks it until the valve body 3 reaches its operating position, in which it is struck on the stop 8 while blocking the lateral flow opening 7.
  • the plurality of jet openings on the valve head 22 in the wall of the pipeline 5 are designed such that they are oriented obliquely backwards with respect to the flow in the pipeline 5.
  • This embodiment is particularly suitable as a cleaning head for sewer cleaning.
  • Pressure valves 13 are installed in the jet openings 12, from which the jet openings 12 are released when the liquid hammer is caused by the valve body 3 hitting the valve seat 8.
  • FIG. 8 A similar embodiment is shown in FIG. 8, in which, however, the jet openings 12 are formed in the cavity of the valve body 3 which is closed at the end and are only opened by means of the shut-off tube extension when the valve body 3 strikes the valve seat 8.
  • the jet openings 12 can open tangentially from the valve body 3 in such a way that the valve body 3 is rotated after the jet openings 12 are released and the high-pressure jets emitted from the jet openings 12 are therefore rotated, for example, for sewer cleaning.
  • the pipeline 5 is returned with its pipeline end facing away from the valve such that the pipeline ends point in the same direction and are aligned with one another. This allows the device to be largely free of setbacks.
  • valve body 3 is designed as a displaceable, pierced piston in the pipeline 5, from which the jet openings 12 formed in the pipeline wall are blocked until the flow openings 7 are closed and the valve body 3 strikes the stop 8.
  • FIG. 11 shows a schematic diagram of the application of the invention for the time-controlled injection of fuel into the intake line 21 of an internal combustion engine seem.
  • the fuel line 5 is designed as a circulation line, in which a fuel reservoir 19, a pump 20 and a shut-off valve are switched on, with the valve body 3 of which, in cooperation with a valve seat acting as a stop 8, the flow cross-section 7 of the pipeline 5 can be shut off at controlled times.
  • the valve body 3 is therefore actuated by a controlled actuator 9.
  • valve body 3 When the valve body 3 is adjusted by the actuator 9 against the valve seat 8, the circulation flow in the pipeline 5 on the valve body 3 is suddenly braked, as a result of which the liquid hammer occurs. Due to the pressure increase, the pressure valve 13 is opened, whereby a fuel pulse jet is injected through the jet opening 12 into the intake line 21. Thereafter, the valve body 3 is adjusted by the actuator 9 or by the pressure which has since been reduced again to its initial position, in which the flow opening 7 is opened, so that the circulation flow can form again for the next injection process.
  • the embodiment from FIG. 12 corresponds in principle to that from FIG. 1.
  • the valve body 3 according to FIG. 12, however, is designed as a pierced rotary body, which by means of an actuator 9 moves out of its initial position, in which it opens the flow opening 7 through its bore, through 90 ° its operating position can be rotated, in which it blocks the flow opening 7.
  • lateral jet openings 12 are formed on the pipeline 5, each of which is blocked by a pressure relief valve 13, which opens under the pressure increase when the liquid hammer occurs in order to output the pulse jet.
  • the damping container 1 at the pipe end facing away from the valve contains a gas volume which is blocked off from the pipe 5 by a piston 17.
  • the piston 17 is supported on a return spring 18, which can optionally also be formed by the gas volume itself.
  • the pipeline 5 behind the liquid inlet 2 is designed as a circulation line, in which an annular flow 10 is generated by means of a flow drive 14, which is arranged in the form of a paddle wheel in the pipeline 5.
  • a stowage device 16 in the form of a pipe socket is branched off from the latter, in the end wall of which a jet opening 12 is formed.
  • a valve At the transition from the ring line to the Storage device 16 is a valve, the valve body 3 of which is actuated by a controlled actuator 9 in order to interrupt the ring flow 10 at a preselected point in time and to divert the flowing liquid into the storage device 16.
  • the ring flow is gradually accelerated by the flow drive 14.
  • valve body 3 When the maximum speed is reached, the valve body 3 is adjusted by the actuator 9 into its operating position until it abuts the stop 8, so that the ring flow 10 is interrupted.
  • the liquid flow deflected thereby into the stowage device 16 is suddenly braked in the stowage device, so that the liquid hammer occurs and a high-pressure pulse jet is emitted from the jet opening 12.
  • This pulse jet lasts until the pressing liquid flow has come to a complete standstill. Since this time period is approximately twice the sound propagation time in the circulation line, such embodiments are particularly suitable for generating long-lasting pulse beams because of the relatively long length of the ring line, which can also consist of several spiral turns. Furthermore, this embodiment works independently of the pressure in the liquid inlet 2.

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  • Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Veterinary Medicine (AREA)
  • Rehabilitation Therapy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Animal Behavior & Ethology (AREA)
  • General Health & Medical Sciences (AREA)
  • Pain & Pain Management (AREA)
  • Physical Education & Sports Medicine (AREA)
  • Chemical & Material Sciences (AREA)
  • Epidemiology (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Valves (AREA)
EP87109009A 1986-06-24 1987-06-23 Dispositif pour produire un jet de liquide à grande vitesse Withdrawn EP0251152A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3621156 1986-06-24
DE3621156 1986-06-24

Publications (1)

Publication Number Publication Date
EP0251152A1 true EP0251152A1 (fr) 1988-01-07

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EP87109009A Withdrawn EP0251152A1 (fr) 1986-06-24 1987-06-23 Dispositif pour produire un jet de liquide à grande vitesse

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1434942B1 (fr) * 2001-10-04 2008-02-27 Robert Bosch Gmbh Soupape d'injection de carburant
CN110314885A (zh) * 2019-06-07 2019-10-11 张玉荣 一种小型机械加工工具清洗设备

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2935988A1 (de) * 1979-09-06 1981-04-02 Helmut Dipl.-Ing. 6200 Wiesbaden Sieke Verfahren und vorrichtung zum verspruehen von unter druck stehenden fluessigkeiten aus einer duese
DE3229596A1 (de) * 1981-08-25 1983-03-10 C.R. Bard, Inc., 07974 Murray Hill, N.J. Druckbetaetigte vorrichtung zum erzeugen eines pulsierenden stroemungsmittelstromes
SU1061845A1 (ru) * 1982-04-29 1983-12-23 Московский Ордена Трудового Красного Знамени Станкоинструментальный Институт Гидропульсационный распылитель
US4573637A (en) * 1982-12-06 1986-03-04 Dravo Corporation Accelerating slugs of liquid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2935988A1 (de) * 1979-09-06 1981-04-02 Helmut Dipl.-Ing. 6200 Wiesbaden Sieke Verfahren und vorrichtung zum verspruehen von unter druck stehenden fluessigkeiten aus einer duese
DE3229596A1 (de) * 1981-08-25 1983-03-10 C.R. Bard, Inc., 07974 Murray Hill, N.J. Druckbetaetigte vorrichtung zum erzeugen eines pulsierenden stroemungsmittelstromes
SU1061845A1 (ru) * 1982-04-29 1983-12-23 Московский Ордена Трудового Красного Знамени Станкоинструментальный Институт Гидропульсационный распылитель
US4573637A (en) * 1982-12-06 1986-03-04 Dravo Corporation Accelerating slugs of liquid

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1434942B1 (fr) * 2001-10-04 2008-02-27 Robert Bosch Gmbh Soupape d'injection de carburant
CN110314885A (zh) * 2019-06-07 2019-10-11 张玉荣 一种小型机械加工工具清洗设备

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