WO1995003490A1 - Soupape de cylindre hydraulique - Google Patents

Soupape de cylindre hydraulique Download PDF

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Publication number
WO1995003490A1
WO1995003490A1 PCT/GB1994/001598 GB9401598W WO9503490A1 WO 1995003490 A1 WO1995003490 A1 WO 1995003490A1 GB 9401598 W GB9401598 W GB 9401598W WO 9503490 A1 WO9503490 A1 WO 9503490A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
cylinder
valve seat
piston
operator
Prior art date
Application number
PCT/GB1994/001598
Other languages
English (en)
Inventor
John Varga
Original Assignee
Carding Specialists (Canada) Limited
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 Carding Specialists (Canada) Limited filed Critical Carding Specialists (Canada) Limited
Publication of WO1995003490A1 publication Critical patent/WO1995003490A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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

Definitions

  • This invention relates, in one aspect, to a hydraulically actuated cylinder valve, and is particularly, though not exclusively concerned with the hydraulic actuation of inlet and exhaust valves of positive displacement type air compressors (linearly displaceable piston type air compressors) . It should be understood, however, that the invention is not restricted to such use, and may be applied to the hydraulic actuation of other types of valve controlled pressure chambers which are filled with a fluid medium which is then pressurised, and exhausted, in repeated cycles of operation.
  • the invention is concerned with a linearly reciprocating piston type compressor which comprises a cylinder, a floating piston mounted for linear reciprocation in said cylinder, a piston rod coupled with said piston and guided so as to control the reciprocating movement of the piston in said cylinder so as to be substantially without direct metal to metal contact with the internal wall of the cylinder, at least one cylinder valve for controlling the admission, or exhaust of gas relative to the cylinder, a valve seat co-operable with said cylinder valve, and an improved actuator for controlling the operating movement of the cylinder valve.
  • a piston In the operation of a positive displacement type of air compressor, a piston is driven back and forth within a cylinder at relatively low speed, and inlet and outlet valves are operated in timed sequence with the movement of the piston so as to control (1 ) the induction of a charge of air (2) compression of the charge and (3) discharge of the compressed charge in a repeated cycle of operations.
  • the inlet valve is normally held open throughout the major part of the induction stroke of the piston, and is held closed against its valve seat during the compression and discharge stroke of the piston, whereas the exhaust valve is normally held closed against its valve seat during the ⁇ induction stroke and also the major part of the compression stroke, and is only held open for a short time interval at or near the end of the compression stroke to allow the compressed charge to be discharged.
  • positive displacement compressors are of the double acting type, so that each side of the piston can carry out its own cycle of operation with respect to the air chamber defined within the cylinder between that piston side and the facing end of the cylinder, and corresponding inlet and outlet valves are provided to control the air chambers defined on each side of the piston.
  • Each valve is movable towards and away from the respective valve seat as it moves between the open and closed position, and in some applications it is desirable to provide some form of resiliently deformable seal which is engaged by the valve as it moves to the closed position. In order for the seal to have a useful life, it is desirable to provide some means of actuation of each valve which minimises the impact of the closing force of the valve on the respective seal.
  • this is particularly beneficial for a preferred type of cylinder valve in which an O-ring type seal is provided, but it should be understood clearly that the invention is not restricted to such use, and will give advantages of wear reduction with many other types of valve seat.
  • a hydraulic actuator for a cylinder valve which comprises: a cyclic hydraulic flow generator for producing repeated cycles of hydraulic flow output in which each cycle has an oscillating waveform; a master circuit communicable with said generator; a slave circuit communicable with said master circuit; a valve operator communicable with said slave circuit and connectable to a cylinder valve, said operator being operable in a release mode to move the valve away from its valve seat and in a valve-closing mode to move the valve towards its valve seat; and, valve means for controlling the flow of hydraulic fluid in the master circuit and the slave circuit and operable at predetermined time intervals within each cycle of operation of the generator in order to apply selected samples of the oscillating waveform of the generator output to operate the valve operator in both modes of operation.
  • the selected sample of the oscillating waveform of the generator output will be taken from a portion of the waveform in which the flow is reducing i.e. in a phase of the waveform between a peak and a succeeding trough.
  • each valve makes a relatively gentle engagement with its seal as it completes its closing movement, and this will enhance the working life of such seals and reduce maintenance costs.
  • the invention is not, however, restricted to use either in a positive displacement type compressor having soft seals, or indeed in a positive displacement compressor as such, but has general application to hydraulic actuation of cylinder valves of other types of engine (pumps or motors) having valve controlled fluid pressure chambers which are filled, pressurised and then discharge pressure fluid in repeated • cycles of operation.
  • a hydraulically actuated cylinder valve which comprises: a valve seat; a linearly reciprocable valve element movable between open and closed positions with respect to the valve seat; a valve seal arranged to seal the valve element with respect to the valve seat, when the valve element is in the closed position; a valve operator connected to the valve element and operable in a release mode to move the valve element away from its valve seat and in a valve-closing mode to move the valve element towards its valve seat; and, a hydraulic actuator circuit communicable with said valve operator and operable to apply a closing motion to the valve element via the valve operator which reduces in speed as the valve element moves towards the valve seat and engages with the valve seal .
  • the valve seal comprises a resiliently deformable seal which may be an 0-rinq or other soft packing, and which may be housed in the closing face of the valve element, or in the portion of the valve seat engageable by a head of the valve element.
  • a resiliently deformable seal which may be an 0-rinq or other soft packing, and which may be housed in the closing face of the valve element, or in the portion of the valve seat engageable by a head of the valve element.
  • a linearly reciprocating piston type compressor which comprises a cylinder, a floating piston mounted for linear reciprocation in said cylinder, a piston rod coupled with said piston and guided so as to control the reciprocating movement of the piston in said cylinder so as to be substantially without direct metal to metal contact with the internal wall of the cylinder, at least- one cylinder valve for controlling the admission, or exhaust, of gas relative to the cylinder, a valve seat co-operable with said cylinder valve, and an actuator coupled with said cylinder valve and operable to move the valve towards its valve seat, in sequence with the reciprocation of the piston, and with a speed which reduces as the valve approaches and then engages the valve seat .
  • Figure 1 is a schematic illustration of a hydraulic actuator circuit for a cylinder valve according to the invention
  • Figure la is a detail of an alternative arrangement of part of the circuit shown in Figure 1 ;
  • Figure 2 is a series of graphs showing the operating cycles of the component parts of the circuit shown in Figure 1 ;
  • Figure 3 is a schematic illustration of a further circuit arrangement according to the invention.
  • the actuator circuit is particularly suitable for use with a positive displacement type compressor having a "floating piston”, and provided with soft seals or packings to seal the valves when in the closed positions.
  • a "floating piston” type of compressor is one in which the piston does not engage the internal wall of the cylinder by direct metal to metal contact, and does not have any piston rings, but has its reciprocating movement guided so that there is a small radial clearance between the cylinder wall and the periphery of the piston.
  • the absence of frictional contact between piston and cylinder contributes to a long service life of the compressor, and to low maintenance, as there is no wear and there are no piston seals which require routine inspections and replacement when necessary.
  • Figure 1 shows a hydraulic actuator circuit for a single cylinder valve, which can be the inlet valve or the exhaust valve, and Figure 2 shows cycles of operation of the inlet and exhaust valves.
  • the hydraulic actuator shown in Figure 1 is intended to operate a cylinder valve, shown schematically by reference 10, and which comprises a valve seat 11, and a valve element 12 which is linearly reciprocable between open and closed positions with respect to valve seat 11, element 12 having a valve head 13 which is engageable with valve seat 11 when in the closed position.
  • a resiliently defor able valve seal is provided, which may take the form of an O-ring or soft packing, and which is housed either in the closing face of head 13, or in a part of the valve seat 11 engaged by the head 13.
  • the hydraulic actuator which controls the linear reciprocation of valve element 12, will now be described in detail.
  • the actuator comprises a cyclic hydraulic motion generator for producing repeated cycles of hydraulic flow output having an oscillating waveform, and in the schematic illustration comprises a master cylinder 14 having a piston 15 which is driven back and forth within cylinder 14 under the action of a rotary crank mechanism 16.
  • the crank mechanism 16 will rotate in a proportional relationship to the operation of the cylinder whose valves are to be controlled, so that the inlet and exhaust valves can be operated at required time intervals during the induction, compression and exhaust stages of the air compressor.
  • Each cycle of operation of the hydraulic flow generator has an integral number of peaks and troughs per compressor cycle, and in the illustrated arrangement has six peaks and troughs of a sinusoidal waveform, as can be seen at graphs b and c in Figure 2.
  • Graph 2a shows a graph of movement of piston 17 of compressor cylinder 18 and the selected intervals of operation of the inlet and exhaust valves during each cycle of operation of the compressor.
  • the master cylinder 14 of the cyclic motion generator is communicable with a master circuit 19 having flow and return lines which communicate with opposite ends of the master cylinder 14, and which include a valve-controlled bridging line 20 provided with a diverter valve 21 whose operation between ⁇ open and closed positions is controlled as part of the operating sequence of the hydraulic actuator, as will be discussed in more detail below.
  • a slave circuit 22 is communicable with master circuit 19, and is connected to opposite ends of a slave cylinder 23 having actuator piston 24 coupled with the valve stem of valve element 12, and which thereby forms a valve operator which is operable in a release mode to move the valve element 12 away from valve seat 11 , and in a valve-closing mode to move the valve element 12 towards the valve seat 11.
  • valve means (21 ) The operation of the valve means (21 ) is controlled in such a way that the closing speed applied to the stem of the valve element 12 reduces as the head 13 approaches and then moves into engagement with the valve seat 11 i.e. at or near the end of the closing stroke of movement.
  • valves 21, 25 and 27, provide controlled application of selected portions only of the oscillating waveform produced by the master cylinder 14, in order to move the valve element 12 towards and away from the closed position, preferably a separate hydraulic pressure device is provided to maintain the valve element "locked" in the closed position when it has been moved to that position. Therefore, a high pressure source 26 is provided which is communicable with the slave circuit 22 via control valve 27, to apply a constant biasing force to piston 24 after the latter has been moved to the left upon completion of a closing movement under the control of valves 21 cind 25 of the master circuit 19 and slave circuit. 22.
  • the sequence of operation of valves 21, 25 and 27, for a typical cycle of operation will be described in more detail below.
  • Figure 2b shows the oscillating waveform produced by the suction valve master cylinder
  • Figure 2a shows the time intervals, during a cycle of operation, in which the suction valve carries out opening movement, as shown by the relatively short, section 28 of the graph, and by longer section 29 in which the valve is maintained open (preferably by means of a small spring biasing force), followed by short section 30 in which valve closing movement takes place, followed by further longer section 31 in which the valve remains closed.
  • Figure 2b shows the oscillating waveform of the suction valve master cylinder, and the two marked samples of this waveform, shown by references 32 comprise short duration predetermined time intervals at which diverter valve 21 is closed, in order to initiate suction valve opening at section 28 and suction valve closing shown by reference 30 in Figure 2a.
  • the suction valve While the diverter valve is open, the suction valve dwells (either closed or open) along lines 39 and 40 while the waveforms are being short-circuited or by-passed.
  • Figure 2c shows the oscillating (sinusoidal) waveform generated by the exhaust valve master, and very short predetermined selected sample of this waveform shown by reference 33 is the interval at which the diverter valve 21 of the exhaust valve master circuit is closed, it being understood that inlet valve master circuit has its own diverter valve 21 operated at predetermined short term intervals 32 described above with reference to Figure 2b.
  • the diverter valve 21 is only closed when valve 25 is open and control valve 27 closed, so that the sleeve (or piston) can move.
  • the high pressure from source 26 is used to keep the suction air valve closed during the compression stroke when, as is preferred, the air valve is located on top of the cylinder end plate which is convenient for some applications.
  • the master circuit and slave circuit described so far with reference to Figure 1 will be provided with replenishment lines and pressure relief lines, as shown schematically by reference 40 and 41 for the replenishment lines and relief lines respectively, and coupled with the master circuit 19m, and operating in a manner which will be well known to those of ordinary skill in the art.
  • Figure 1 provides an arrangement for controlling the movement of actuator sleeve 23 and its piston 24, and an alternative arrangement for diverter valve 21 is shown in Figure la.
  • the selected waveform is transmitted directly through the valve, while the unwanted waveforms are short-circuited, as in valve A of Figure 1.
  • the master waveforms are being short circuited, the sleeve circuit is locked in position; rather than being free to move as would be possible in the case of valve A in the Figure 1 arrangement.
  • valve A if either valve A is permanently open, or the valve of F'igure 1a is in position a_, circuit 13 is free to move when acted on by -1 l a - external forces and can then be unloaded if e.g. biasing spring S is applied.
  • variable differential drive input may be provided, which enables variation in the sampled waveform.
  • control valves which are illustrated schematically will preferably be electrically control valves e.g. solenoid valves.
  • FIG. 3 an alternative circuit arrangement according to the invention is shown in Figure 3, and in which parts corresponding with those already described are given the same reference numerals.
  • This is a "piggyback" type of arrangement, in which a double piston rod type of actuator has piston rods 1 and 2 of the same diameter. This is necessary, because otherwise short circuiting would not be possible, in that it would be self-locking.
  • This actuator is attached to valve element 13 to be pulled by it.
  • An objective of this arrangement is to avoid absorbing an unacceptable amount of energy, and in particular to avoid drawing on a 1,000 psi oil supply.
  • the locking piston must travel forwards (to the left in the drawing). Then, when the locking pressure is switched on, it must not allow any more fluid than the compressibility of the fluid in volume 3 allows.

Abstract

Organe de commande hydraulique (10) commandant le fonctionnement d'une soupape de cylindre possèdant un siège de soupape (11) et un élément de soupape (12) conçu pour effectuer un déplacement alternatif linéaire entre des positions ouverte et fermée par rapport au siège de soupape (11), un joint de soupape logé dans la face de fermeture de la tête de soupape (13) (ou une partie du siège de soupape (11) en contact avec la tête (13)), un organe de commande de soupape accouplé à l'élément de soupape (12) et fonctionnant en mode d'ouverture, de façon à éloigner ledit élément de soupape de son siège de soupape, et en mode de fermeture, de façon à déplacer ledit élément de soupape vers son siège de soupape, ainsi qu'un circuit de commande hydraulique (19, 22) communiquant avec l'organe de commande de soupape et servant à appliquer un mouvement de fermeture à l'élément de soupape (12) par l'intermédiaire dudit organe de commande, dont la vitesse diminue simultanément au déplacement de l'élément de soupape (12) vers le siège (11) et à son contact avec le joint de soupape. L'organe de commande hydraulique est particulièrement approprié pour commander le fonctionnement d'une soupape de cylindre d'un compresseur à déplacement positif possédant des joints 'mous', bien qu'il s'applique également à l'actionnement hydraulique de soupapes de cylindres d'autres types de moteur possédant des chambres de pression hydraulique réfulées par soupape et remplies, mises sous pression et déchargées selon des cycles de fonctionnement répétés.
PCT/GB1994/001598 1993-07-24 1994-07-25 Soupape de cylindre hydraulique WO1995003490A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB939315383A GB9315383D0 (en) 1993-07-24 1993-07-24 Hydraulically actuated cylinder valve
GB9315383.1 1993-07-24

Publications (1)

Publication Number Publication Date
WO1995003490A1 true WO1995003490A1 (fr) 1995-02-02

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PCT/GB1994/001598 WO1995003490A1 (fr) 1993-07-24 1994-07-25 Soupape de cylindre hydraulique

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GB (1) GB9315383D0 (fr)
WO (1) WO1995003490A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0694693A1 (fr) * 1994-07-29 1996-01-31 Hoerbiger Ventilwerke Aktiengesellschaft Méthode et dispositif pour la commande d'une soupape
WO1996022466A2 (fr) * 1995-01-20 1996-07-25 Carding Specialists (Canada) Limited Actuateur hydraulique
EP0801227A2 (fr) * 1996-04-12 1997-10-15 Hoerbiger Ventilwerke Aktiengesellschaft Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur
EP1491732A1 (fr) * 2003-06-23 2004-12-29 Magneti Marelli Powertrain S.p.A. Méthode et dispositif pour contrôler la vitesse des soupapes dans un moteur à combustion
US7331767B2 (en) 2002-09-19 2008-02-19 Hoerbiger Kompressortechnik Services Gmbh Method of stepless capacity control of a reciprocating piston compressor and piston compressor with such control
WO2019142155A1 (fr) * 2018-01-19 2019-07-25 Mohammad Oroojloo Compresseur d'air à commande hydraulique

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2135247A (en) * 1936-05-26 1938-11-01 Westinghouse Air Brake Co Compressor valve control
JPS60252113A (ja) * 1984-05-30 1985-12-12 Hino Motors Ltd エンジン・ブレ−キ動作装置
EP0391507A1 (fr) * 1989-04-03 1990-10-10 Mitsubishi Jukogyo Kabushiki Kaisha Dispositif de soupape pour moteur à combustion interne

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2135247A (en) * 1936-05-26 1938-11-01 Westinghouse Air Brake Co Compressor valve control
JPS60252113A (ja) * 1984-05-30 1985-12-12 Hino Motors Ltd エンジン・ブレ−キ動作装置
EP0391507A1 (fr) * 1989-04-03 1990-10-10 Mitsubishi Jukogyo Kabushiki Kaisha Dispositif de soupape pour moteur à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 126 (M - 477) 10 May 1986 (1986-05-10) *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0694693A1 (fr) * 1994-07-29 1996-01-31 Hoerbiger Ventilwerke Aktiengesellschaft Méthode et dispositif pour la commande d'une soupape
AT403835B (de) * 1994-07-29 1998-05-25 Hoerbiger Ventilwerke Ag Vorrichtung und verfahren zur beeinflussung eines ventils
WO1996022466A2 (fr) * 1995-01-20 1996-07-25 Carding Specialists (Canada) Limited Actuateur hydraulique
WO1996022466A3 (fr) * 1995-01-20 1996-09-12 Carding Spec Canada Actuateur hydraulique
EP0801227A2 (fr) * 1996-04-12 1997-10-15 Hoerbiger Ventilwerke Aktiengesellschaft Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur
EP0801227A3 (fr) * 1996-04-12 1999-03-03 HOERBIGER VENTILWERKE GmbH Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur
AT409655B (de) * 1996-04-12 2002-10-25 Hoerbiger Ventilwerke Ag Verfahren und einrichtung zur beeinflussung eines kompressor-saugventils
US7331767B2 (en) 2002-09-19 2008-02-19 Hoerbiger Kompressortechnik Services Gmbh Method of stepless capacity control of a reciprocating piston compressor and piston compressor with such control
EP1491732A1 (fr) * 2003-06-23 2004-12-29 Magneti Marelli Powertrain S.p.A. Méthode et dispositif pour contrôler la vitesse des soupapes dans un moteur à combustion
US7086358B2 (en) 2003-06-23 2006-08-08 Magneti Marelli Powertrain S.P.A. Method and device for controlling the speed of the valves of an internal combustion engine
WO2019142155A1 (fr) * 2018-01-19 2019-07-25 Mohammad Oroojloo Compresseur d'air à commande hydraulique

Also Published As

Publication number Publication date
GB9315383D0 (en) 1993-09-08

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