EP0694693B1 - Vorrichtung und Verfahren zur Beeinflussung eines Ventils - Google Patents
Vorrichtung und Verfahren zur Beeinflussung eines Ventils Download PDFInfo
- Publication number
- EP0694693B1 EP0694693B1 EP95890141A EP95890141A EP0694693B1 EP 0694693 B1 EP0694693 B1 EP 0694693B1 EP 95890141 A EP95890141 A EP 95890141A EP 95890141 A EP95890141 A EP 95890141A EP 0694693 B1 EP0694693 B1 EP 0694693B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- control
- closure member
- way
- 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.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
- F04B7/0266—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated the inlet and discharge means being separate members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- 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
- F04B39/08—Actuation of distribution members
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
Definitions
- the invention relates to a device with at least one over one Lifting gripper in the lifting direction on a closing element of a valve of a piston compressor acting control cylinder, which has a control element for influencing the periodic stroke movement of the closing element periodically with Pressure medium can be acted upon and relieved, and a method for Influencing the periodic stroke movement of the closing element of a valve a piston compressor, one using a lifting gripper in the lifting direction control cylinder acting on the locking member periodically with pressure medium is acted upon and relieved.
- an electromagnetically operated regulation of the Suction valves of piston compressors have been known for a long time, in which an Sealing element of the suction valve engaging lifting gripper via a on the valve cover attached electromagnet is moved, the periodic excitation done by a collector, which is synchronous with the crankshaft of the Compressor rotates. Due to the sometimes very large backflow forces, which on Sealing element of the suction valves act, are large electromagnets with corresponding Power consumption required, which is mostly disadvantageous and undesirable is.
- a pneumatic control device for a long time to keep suction valves open during part of the pressure stroke is known in which the influence of the valves to be kept open by the compressing gas itself. The control takes place by means of a rotary valve, over which several individual cylinders in which gripper pistons work, periodically controlled. The complexity of the Appearance of further spread apparently.
- the object of the present invention is a device and a Process of the type mentioned to improve so that the mentioned Disadvantages of the known devices and methods are avoided and that influencing the periodic, in particular with simple means Stroke of the closing member can be done so that even with large required Pressing the pressure medium acting on the control cylinder and highly dynamic control processes created a reliable arrangement will not reach those mentioned, even over a long period of operation Disorders tends.
- control member at least one in supply and / or discharge switched on the print medium and this or its print up and / or -Degradation and thus the lifting movement of the closing member at least gradually has variably accelerating or decelerating control element, and that a check valve between the control element and an upstream pressure medium source is provided.
- the corresponding embodiment of the invention The method is characterized in that the pressurization and / or relief via the stroke of the closing member at least in stages variable, the reaction of the compressor pressure via the closing element to the pressure medium source is prevented by means of a check valve.
- the control element mentioned can be used, for example, for a over the control cylinder for a certain part of the compression stroke open suction valve of a piston compressor, the pressure relief for example, control so that at the beginning of the flow forces released Closing movement of the valve plate of the suction valve relieves this pressure largely unthrottled and thus the corresponding valve plate movement takes place very quickly, whereas before opening the valve plate by reducing the pressure relief on the seat by switching can take place that a braked and at least within limits the valve plate hits the valve seat gently. Similar Movement influences of the closing element of the valve can of course also make sense in the opening direction of the valve plate, for example, if the unbraked stop of the opening valve plate on a catcher should be prevented.
- the check valve mentioned offers the advantage that the input pump pressure is not the greatest via the closing element retroactive force must correspond to the installed pump capacity and energy consumption can also be reduced.
- the control member can, for example, at least one variably controllable Switching element, for example a piezo valve, with several switching positions have, which also forms the control element.
- the control member has at least one separate switching element, preferably a Solenoid valve or a piezo valve, with several switch positions and one independent control element, with at least one by means of the pressure medium movable displacement piston, which is a switching element for switching of the pressure medium flow between at least two different actuated throttled ways.
- the controllable Switching element e.g.
- one Piston compressor by keeping at least one suction valve open at least a portion of the compression stroke by pressurizing the closing element of the suction valve via a lifting gripper is another Embodiment of the inventive method is advantageous, according to which on Pressure relief at the end of the periodically kept section initially at least largely unthrottled and then more restricted he follows.
- This also results in this type of compressor control Advantage that the locking device which is initially open is not under the influence the backflow forces that are already too great at the time of release high speed hits the valve seat without braking, which too Damage to the valve seat and valve plate or lead to spring breaks could.
- FIG. 1 and 2 show schematic embodiments of the invention and FIG. 3 shows curves of the speed v and the pressure p for different operating points of a suction valve control according to the invention on the one hand and the state of the art on the other.
- a pump, motor, tank and adjustable pressure relief valve equipped hydraulic unit 1 supplies via supply lines 3 a magnetically operated 3/2-way valve 5 with pressure medium, for example.
- a spring 7 presses the valve 5 in the shift position shown. Pressure fluid thus flows into the work space 9 of the control cylinder 8 and acts on the control piston 10. This presses the Power transmission device 11 to the sealing element 12 of the compressor valve.
- the back pressure fluid flows an auxiliary cylinder 16, which has a piston 17 and working spaces 18, 19th having.
- the working space 18 of the auxiliary cylinder 16 is shown in the Example chosen so that except for losses on the bypass through the Throttle 21 receives the stroke movement of the piston 17 that part of the pressure medium, that during the first part of the movement of the control piston thereof is ousted.
- the pressure medium displaced by the piston 17 from the working space 19 flows through the throttle 22, which is the flow resistance here
- the overall arrangement symbolizes and is designed with as little loss as possible.
- the power transmission device 11 is only with the sealing element 12 occasionally in contact. Therefore, the power transmission device 11 lifts off Sealing element 12 as soon as it has reached its end position on the seat 13.
- the Residual movement of the power transmission device 11 is due to the strong Throttling the outflow of the pressure medium is strongly damped, so that the power transmission device 11 then came to a standstill by the shortest route. It can thus safely be avoided that the control piston 10 him assigned stroke limit actually reached, thus damaging the Control piston 10 and the associated control cylinder 8 is avoided.
- a stroke limitation becomes constructive, for example designed so that a hydraulic cushioning is guaranteed.
- the control piston 10 reaches it However, not the end position, so that the known disadvantage of hydraulic End position damping, namely the difficult breakaway from the end position at Initiation of the counter movement, can be avoided.
- the rest position of the 3/2-way valve 5 is the safety requirements to choose according to.
- pressure fluid reservoir 2 or 23 as a pulsation damper in the supply and return of the pressure medium, the avoidance of liquid hammer and associated undesirable Effects on the movement of the control piston 10 and thus the power transmission device 11 and the sealing element 12 serve.
- Curves 1.1 and 1.2 apply to full load curves 2.1, 2.2 and 3.1 and 3.2 for Partial load. The curves are based on the maximum impact velocity v-max Sealing element 12 on the valve seat (determined over all load cases).
- Fig. 3b are the corresponding curves of the pressure p in the work area of the compressor over time t.
- the designated 1.1, 2.1 and 3.1 Curves represent the behavior of a compressor stage, whose suction valves are equipped with variable movement damping.
- the dashed curves marked with 1.2, 2.2 and 3.2 stand for Suction valves with constant movement damping (according to the state of the art), wherein the damping is designed so that the maximum impact speed of the sealing element 12 on the valve seat for variable and constant damping is about the same size.
- the curves 1.1 and 1.2 apply in the event that the closing movement of the Sealing element 12 at the bottom dead center of the respective compressor cylinder is initiated by switching the control element.
- the working medium of the compressor With increasing piston speed and the beginning of compression the working medium of the compressor an increasing closing force on the sealing element 12, which the Force of the closing springs 15 (see FIGS. 1 and 2) is superimposed.
- the pressure medium can initially flow out almost undamped, so that the closing force largely to accelerate the sealing element and Power transmission device is available.
- the throttle should be chosen many times smaller, so that at the beginning one Most of the closing force is required to overcome the throttle resistance becomes. Accordingly, the sealing element approaches with variable damping according to the present invention, the valve seat faster than the constant State-of-the-art damping.
- control element If the control element is actuated at a later time (Curves 2.1, 2.2, 3.1 and 3.2), the delivery rate is reduced and thus the drive power consumed by the compressor.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Check Valves (AREA)
- Valve Device For Special Equipments (AREA)
- Lift Valve (AREA)
- Compressor (AREA)
Description
Claims (4)
- Vorrichtung mit zumindest einem über einen Abhebegreifer (11) in Hubrichtung auf ein Schließorgan (12) eines Ventils eines Kolbenkompressors einwirkenden Steuerzylinder (8), der über ein Steuerorgan (5) zur Beeinflußung der periodischen Hubbewegung des Schließorganes (12) periodisch mit Druckmedium beaufschlagbar und entlastbar ist, dadurch gekennzeichnet, daß das Steuerorgan (5, 16) zumindest ein in Zu- und/oder Ableitung (3, 24) des Druckmediums eingeschaltetes und dieses bzw. dessen Druckauf- und/oder -abbau und damit die Hubbewegung des Schließorganges (12) zumindest stufenweise variabel beschleunigendes bzw. verzögerndes Steuerelement (16) aufweist, und daß zwischen Steuerorgan (5) und einer vorgeschalteten Druckmittelquelle (1) ein Rückschlagventil (4) vorgesehen ist.
- Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Steuerorgan (5, 16) zumindest ein separates Schaltelement (5), vorzugsweise ein Magnetventil oder ein Piezoventil, mit mehreren Schaltstellungen und ein davon unabhängiges Steuerelement (16), mit zumindest einem mittels des Druckmediums bewegbaren Verdrängerkolben (17), welcher ein Umschaltelement zur Umschaltung des Druckmittelstromes zwischen zumindest zwei unterschiedlich gedrosselten Wegen betätigt, aufweist.
- Verfahren zur Beeinflussung der periodischen Hubbewegung des Schließorganes eines Ventils eines Kolbenkompressors, wobei ein über einen Abhebegreifer in Hubrichtung auf das Schließorgan einwirkender Steuerzylinder periodisch mit Druckmedium beaufschlagt und entlastet wird, dadurch gekennzeichnet, daß die Druckbeaufschlagung und/oder -entlastung über den Hub des Schließorganes zumindest in Stufen variabel erfolgt, wobei die Rückwirkung des Kompressordruckes über das Schließorgan auf die Druckmittelquelle mittels eines Rückschlagventils unterbunden wird.
- Verfahren nach Anspruch 3 zur Rückströmregelung eines Kolbenverdichters durch Offenhalten zumindest eines Saugventils über zumindest einen Teilbereich des Verdichtungshubes mittels Druckbeaufschlagung des Schließorganes des Saugventils über einen Abhebegreifer, dadurch gekennzeichnet, daß am Ende des jeweils periodisch offengehaltenen Teilbereiches die Druckentlastung vorerst zumindest weitgehend ungedrosselt und sodann stärker gedrosselt erfolgt.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT0149894A AT403835B (de) | 1994-07-29 | 1994-07-29 | Vorrichtung und verfahren zur beeinflussung eines ventils |
AT1498/94 | 1994-07-29 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0694693A1 EP0694693A1 (de) | 1996-01-31 |
EP0694693B1 true EP0694693B1 (de) | 1998-10-21 |
Family
ID=3515139
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95890141A Expired - Lifetime EP0694693B1 (de) | 1994-07-29 | 1995-07-26 | Vorrichtung und Verfahren zur Beeinflussung eines Ventils |
Country Status (8)
Country | Link |
---|---|
US (1) | US5833209A (de) |
EP (1) | EP0694693B1 (de) |
JP (1) | JP3720086B2 (de) |
KR (1) | KR100350461B1 (de) |
CN (1) | CN1045653C (de) |
AT (1) | AT403835B (de) |
DE (1) | DE59503972D1 (de) |
ES (1) | ES2123225T3 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0801227A2 (de) * | 1996-04-12 | 1997-10-15 | Hoerbiger Ventilwerke Aktiengesellschaft | Verfahren und Einrichtung zur Beeinflussung eines Kompressor-Saugventils |
WO2001059266A1 (de) | 2000-02-07 | 2001-08-16 | Compart Compressor Technology Gmbh & Co. Kg | Vorrichtung und verfahren zur steuerung einer kolbenmaschine |
Families Citing this family (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2815075B1 (fr) * | 2000-10-05 | 2003-01-24 | Renault Sport | Dispositif d'actionnement de soupapes, et procede de commande pour un tel dispositif |
AT413234B (de) * | 2002-09-19 | 2005-12-15 | Hoerbiger Kompressortech Hold | Hubkolbenkompressor und verfahren zur stufenlosen fördermengenregelung desselben |
ITGE20060067A1 (it) | 2006-06-28 | 2007-12-29 | Dott Ing Mario Cozzani Srl | Apparato per la regolazione continua della portata di compressori alternativi. |
CN100412365C (zh) * | 2006-12-22 | 2008-08-20 | 浙江大学 | 一种基于时间控制顶开活塞压缩机进气阀的装置 |
CN101173658B (zh) * | 2007-09-03 | 2010-08-25 | 西安交通大学 | 一种往复活塞压缩机排气量无级调节方法 |
ITGE20080036A1 (it) * | 2008-04-30 | 2009-11-01 | Dott Ing Mario Cozzani Srl | Metodo per il controllo della posizione di un attuatore elettromeccanico per valvole di compressori alternativi. |
AT507320B1 (de) * | 2008-10-02 | 2010-10-15 | Hoerbiger Kompressortech Hold | Hubkolben-kompressor |
CN102472265B (zh) * | 2009-07-23 | 2015-07-01 | 伯克哈特压缩机股份公司 | 供给量控制方法和具有供给量控制功能的往复活塞式压缩机 |
EP2683950B1 (de) * | 2011-03-10 | 2016-07-20 | Dresser-Rand Company | Stufenlose elektronische steuerungs-stelleinheit |
AT511238B1 (de) | 2011-04-14 | 2013-03-15 | Hoerbiger Kompressortech Hold | Hubkolbenverdichter mit fördermengenregelung |
CN102536753A (zh) * | 2012-02-16 | 2012-07-04 | 汤斌 | 压气或透平装置 |
CN102937084A (zh) * | 2012-10-30 | 2013-02-20 | 合肥通用机械研究院 | 一种压缩机气量调节系统 |
CN103967762B (zh) * | 2013-02-01 | 2016-03-16 | 陈镇汉 | 一种压缩机气量调节液压执行器 |
US9181825B2 (en) * | 2013-04-23 | 2015-11-10 | Edward Hall Batchelor, JR. | Internal combustion engine independent valve actuator |
CN103291596B (zh) * | 2013-06-18 | 2016-02-10 | 合肥通用机械研究院 | 一种基于余隙调节的压缩机流量调节系统 |
CN103487959B (zh) * | 2013-10-15 | 2015-12-02 | 深圳市华星光电技术有限公司 | 真空吸附力可调的转写辊及用该转写辊的薄膜贴附方法 |
CN104712617B (zh) * | 2015-03-18 | 2016-08-24 | 浙江志高机械股份有限公司 | 全液压延时系统及其方法 |
CN105889050B (zh) * | 2015-04-14 | 2019-02-19 | 康茨(上海)压缩机技术服务有限公司 | 一种用于活塞压缩机气阀智能启闭控制方法 |
DK178787B1 (en) * | 2015-05-06 | 2017-02-06 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | A large turbocharged two-stroke self-igniting internal combustion engine with an exhaust valve actuation system |
ITUB20150797A1 (it) * | 2015-05-22 | 2016-11-22 | Nuovo Pignone Tecnologie Srl | Valvola per un compressore alternativo |
KR101801936B1 (ko) * | 2016-03-25 | 2017-11-27 | 삼성중공업 주식회사 | 셧다운 시스템 |
IT201800006557A1 (it) | 2018-06-21 | 2019-12-21 | Reciprocating compressor valve body made by additive manufacturing / corpo di valvola di compressione alternativa ottenuta con tecnica di costruzione additiva | |
CN110285100B (zh) * | 2019-06-28 | 2024-07-09 | 三一重机有限公司 | 减震液压系统及工程机械 |
CN112628426B (zh) * | 2020-12-24 | 2022-09-20 | 牡丹江石油工具有限责任公司 | 一种用于石油、天然气钻井的止回阀 |
AT525119B1 (de) * | 2021-05-10 | 2023-04-15 | Hoerbiger Wien Gmbh | Kolbenkompressor mit variabler Kapazitätsregelung |
US11725548B2 (en) * | 2021-06-23 | 2023-08-15 | L&T Technology Services Limited | Camless engine |
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US3104801A (en) * | 1963-09-24 | Infinite step controlling device for compressors | ||
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JPS60113008A (ja) * | 1983-11-22 | 1985-06-19 | Yanmar Diesel Engine Co Ltd | 内燃機関の油圧作動動弁装置 |
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DE3604233A1 (de) * | 1986-02-11 | 1987-08-13 | Bosch Gmbh Robert | Ventilsteuervorrichtung fuer eine hubkolben-brennkraftmaschine |
DE3836725C1 (de) * | 1988-10-28 | 1989-12-21 | Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
JPH0791969B2 (ja) * | 1989-03-20 | 1995-10-09 | 川崎重工業株式会社 | 内燃機関の弁駆動装置 |
DE3939934A1 (de) * | 1989-12-02 | 1991-06-06 | Man Nutzfahrzeuge Ag | Ventilsteuerung fuer gaswechselventile von brennkraftmaschinen |
JP2527268Y2 (ja) * | 1990-05-11 | 1997-02-26 | 三菱重工業株式会社 | 内燃機関の動弁装置 |
GB9022439D0 (en) * | 1990-10-16 | 1990-11-28 | Lotus Car | A method and apparatus for testing an internal combustion engine |
US5275136A (en) * | 1991-06-24 | 1994-01-04 | Ford Motor Company | Variable engine valve control system with hydraulic damper |
US5421359A (en) * | 1992-01-13 | 1995-06-06 | Caterpillar Inc. | Engine valve seating velocity hydraulic snubber |
GB9315383D0 (en) * | 1993-07-24 | 1993-09-08 | Carding Spec Canada | Hydraulically actuated cylinder valve |
DE4341848C2 (de) * | 1993-12-08 | 1996-07-18 | Danfoss As | Regelventil |
US5378117A (en) * | 1994-03-28 | 1995-01-03 | Dresser-Rand Company | Valve unloading means, and a valve unloading actuator therefor |
-
1994
- 1994-07-29 AT AT0149894A patent/AT403835B/de not_active IP Right Cessation
-
1995
- 1995-07-26 KR KR1019950022187A patent/KR100350461B1/ko not_active IP Right Cessation
- 1995-07-26 EP EP95890141A patent/EP0694693B1/de not_active Expired - Lifetime
- 1995-07-26 ES ES95890141T patent/ES2123225T3/es not_active Expired - Lifetime
- 1995-07-26 DE DE59503972T patent/DE59503972D1/de not_active Expired - Lifetime
- 1995-07-28 US US08/508,453 patent/US5833209A/en not_active Expired - Lifetime
- 1995-07-28 JP JP19384395A patent/JP3720086B2/ja not_active Expired - Lifetime
- 1995-07-28 CN CN95115811A patent/CN1045653C/zh not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0801227A2 (de) * | 1996-04-12 | 1997-10-15 | Hoerbiger Ventilwerke Aktiengesellschaft | Verfahren und Einrichtung zur Beeinflussung eines Kompressor-Saugventils |
WO2001059266A1 (de) | 2000-02-07 | 2001-08-16 | Compart Compressor Technology Gmbh & Co. Kg | Vorrichtung und verfahren zur steuerung einer kolbenmaschine |
Also Published As
Publication number | Publication date |
---|---|
ES2123225T3 (es) | 1999-01-01 |
JP3720086B2 (ja) | 2005-11-24 |
US5833209A (en) | 1998-11-10 |
CN1045653C (zh) | 1999-10-13 |
CN1118048A (zh) | 1996-03-06 |
AT403835B (de) | 1998-05-25 |
DE59503972D1 (de) | 1998-11-26 |
EP0694693A1 (de) | 1996-01-31 |
KR100350461B1 (ko) | 2002-11-04 |
JPH0868471A (ja) | 1996-03-12 |
ATA149894A (de) | 1997-10-15 |
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