EP0801227B1 - Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur - Google Patents

Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur Download PDF

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Publication number
EP0801227B1
EP0801227B1 EP97890047A EP97890047A EP0801227B1 EP 0801227 B1 EP0801227 B1 EP 0801227B1 EP 97890047 A EP97890047 A EP 97890047A EP 97890047 A EP97890047 A EP 97890047A EP 0801227 B1 EP0801227 B1 EP 0801227B1
Authority
EP
European Patent Office
Prior art keywords
pressure
opening
control device
closure member
control
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
Application number
EP97890047A
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German (de)
English (en)
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EP0801227A3 (fr
EP0801227A2 (fr
Inventor
Peter Dr. Steinrück
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.)
Hoerbiger Kompressortechnik Services GmbH
Original Assignee
Hoerbiger Kompressortechnik Services GmbH
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.)
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Publication date
Application filed by Hoerbiger Kompressortechnik Services GmbH filed Critical Hoerbiger Kompressortechnik Services GmbH
Publication of EP0801227A2 publication Critical patent/EP0801227A2/fr
Publication of EP0801227A3 publication Critical patent/EP0801227A3/fr
Application granted granted Critical
Publication of EP0801227B1 publication Critical patent/EP0801227B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F04B2201/0601—Opening times
    • F04B2201/06011—Opening times of the inlet valve only

Definitions

  • the invention relates to a method for influencing the pressure-dependent automatic, periodic opening movement of a closing element Suction valve of a reciprocating compressor by means of a, if necessary at least via a part of the crank circuit acting on the closing member control device. Furthermore, the invention also relates to a corresponding device to influence the pressure-dependent, automatic, periodic Opening movement of a closing element of a suction valve of a reciprocating compressor, with, if necessary, at least over part of the crank circuit on the closing member acting control device which a Hydraulic control cylinder, which periodically via a control member can be acted upon and relieved of pressure medium.
  • the lifespan of automatic, mostly used on the suction and pressure side Compressor valves are primarily affected by the impact stress alternating impact of the actual locking element on the seat or catcher affected.
  • the spring is selected accordingly Sufficient closing speed to reduce the closing stroke kept low.
  • the system of the known as double damping in which the opening closing member after overcoming a partial stroke on a movable in the opening direction Damper plate or the like strikes, is braked by it and then together with the damper plate overcomes the remaining stroke, the now significantly increased moving mass a further decrease in acceleration of the locking member and thus a simple such valves significantly reduced impact speed of the Closing element on the catcher results.
  • the object of the invention is to provide a method and a device to improve the type mentioned so that the impact stress mentioned of the closing member or catcher at the end of the opening stroke in a simple manner reduced and thus their impact on the life of the valve is reduced becomes.
  • the invention is based on the finding that in conventional valve designs of the type described above when the pressure equilibrium is reached the closing element of the valve between the cylinder space and the suction space is closed under the effect of its feathering. This sets the expansion of the gas enclosed in the cylinder with undiminished Speed continues, which results in a rapid negative pressure in the cylinder space arises from a certain value while overcoming the feathering the locking member a strong momentary acceleration of the locking member towards the catcher.
  • this existing control device to reduce the opening stroke used, according to the invention shortly before reaching the Pressure equilibrium between the cylinder chamber and the suction chamber of the compressor Closing member forcibly opened under the influence of the control device becomes.
  • the control device or the lifting gripper thus becomes a few degrees Crank angle before reaching the pressure equilibrium on the closing element introduced and this shortly before reaching the pressure equilibrium raised, which means that otherwise for automatic valves of the type described characteristic suction in the indicator diagram is avoided.
  • the closing element of the suction valve for example a one-part or multi-part Valve plate is open when pressure equilibrium is reached, a Pressure equalization between the cylinder volume and suction space take place, with which the Decompression phase in the cylinder has ended.
  • the one that follows maximum negative pressure in the cylinder chamber is only due to the throttle loss of the already opened valve determined and much less than in the previously mentioned conventional case.
  • Another opening of the Differential pressure causing the closing element of the suction valve is significantly reduced, which also results in a significantly lower acceleration or impact speed of the locking mechanism on the catcher.
  • control device delivered just before reaching the pressure equilibrium, so that the impulse for example, the lifting gripper is sufficient, the closing member or Open the valve plate before pressure equilibrium is reached, see above the result is sufficient to achieve the desired effect premature, permanent opening of the locking mechanism.
  • the forced opening of the closing element which is preferably in the area from 20 ° to 0 ° crank angle before reaching the pressure equilibrium between Cylinder and suction space is carried out in a further preferred embodiment the invention by an impact of the control device on the closing member initiated, the crank angle or timing of the impact, as well as the Mass ratio and the relative speed of the collision partners selected be that after the impact the opening speed of the closing element not to zero up to the stop on the catcher and preferably not below 10% the speed that occurs immediately after the impact drops.
  • control device being a hydraulic control cylinder has, which is periodically acted upon by a control element with pressure medium and is relieved, it is provided that the periodic opening of the Closing member causing pressure on the control cylinder or control member - or else the volume flow of the pressure medium, preferably by measuring the pressure drop on a throttle used in the inlet to the control unit - monitored and for the indirect determination or monitoring of the opening speed the locking device is used.
  • the control element of the device designed according to the invention can preferably have an electrically switching 3/2-way valve, the Control electronics is connected to an evaluation unit, which furthermore with at least one measuring sensor for monitoring the opening movement of the locking device is connected.
  • the control device or the mentioned lifting gripper is thereby thus hydraulically operated, the feed movement preferably via a electrically switching, fast directional valve is initiated.
  • Point of time the start of the corresponding infeed movement is by switching this directional control valve determines and can with a suitable device Specification, for example of the switching crank angle, or by a control system, which determines the optimal time.
  • the hydraulic pressure in the inlet for example of the 3/2-way valve mentioned be measured.
  • the measuring location essentially the system pressure measured in the feed line.
  • the following Opening the valve causes a dilution wave that coincides with Propagates the speed of sound in the supply line.
  • a steep drop to ambient pressure occur.
  • the pressure fluctuates between a maximum System pressure and ambient pressure.
  • the control device or the lifting gripper fades away the pressure pulsations.
  • the frequency of these pulsations is determined by the distance of the 3/2-way valve from the next hydro-pneumatic pulsation damper arranged in the feed line or other expansion tank determined.
  • the control device or the lifting gripper can Open the closing element or the valve plate immediately. Only after the the closing element remains together with the end position determined by the valve catcher Control device at rest, with which the pressure increase described above at the measuring location occurs only once during one cycle of the compressor.
  • control device If the control element or 3/2-way valve is switched too late the control device is also only when the catcher reaches it certain end position stopped. This results in an optimal changeover time the earliest point in time of the control member or the 3/2-way valve that the steep pressure increase described above only once per work cycle of the compressor. This also applies if the locking device rebounds after reaching the end position and with the one still in motion Control device collides. The ratio of the mass of the control device in this case, the mass of the locking element is only minimal Deceleration of the control device and no significantly ascertainable Compression wave.
  • the actually interesting course of movement of the closing element opened according to the invention over the course of the pressure on the control cylinder causing the periodic opening of the closing member or the control device is to determine the current one Pressure drop at a throttle used in the inlet to the control element monitor.
  • This throttle is to be dimensioned accordingly, so that at a measurable drop in the medium pressure at the expected speeds behind the throttle.
  • the differential pressure measured at the throttle also increases.
  • the control device reaches the closing element and comes up this to a standstill because the delivery time was selected too early and when the closing device is reached by the control device there is high cylinder chamber pressure, the one to be determined at the throttle reaches Differential pressure a minimum.
  • the course of the indicator pressure in the cylinder chamber is monitored and the Time of opening of the closing member should be chosen so that the suction tip minimized or made to disappear in the indicator diagram is.
  • the Crank angle or time of the opening of the closing member but also so be chosen that the intensity of the vibration monitoring in the Valve range determined opening stroke is minimized.
  • the opening blow of valves causes a pulsed excitation of the natural vibrations of the valve holding devices. These structure-borne vibrations sound within a characteristic time quickly.
  • the intensity of the opening stroke can now in the manner described by measuring, for example, on Valve cover accelerations occurring in the direction of the valve axis in Time window after the valve opens until after the decay behavior characteristic time can be quantified. These detectable accelerations are usually in very high frequency ranges.
  • the optimal delivery time of the control device or a lifting gripper or the like advantageously directly by minimizing the Intensity of the vibrations caused by the opening stroke of the valve be determined.
  • the invention can also be provided ongoing monitoring and Adjust the start of the delivery of the control device to perform. Continuous monitoring of one of the above is then used for this Measured variables and the periodic execution of the described optimization processes necessary.
  • FIG. 1 shows a basic circuit diagram for the method and Device according to the present invention
  • Fig. 2 is a schematic image of a other device according to the invention or for performing the invention 3, the time course of the stroke of the closing member for different. Delivery times of the control device
  • Fig. 4 the corresponding Course of the opening speed of an actuated according to FIG. 3 5, the time course of the pressure in the cylinder space just before and after reaching the pressure equilibrium between the cylinder space and suction space
  • Fig. 6 shows an example of the effect of varying the time or crank angle of the positive feed of the control device on the intensity of the opening by the suction valve or the opening stroke caused acceleration or vibration signal
  • Fig. 7 to 10 each show variants of schematic devices for implementation of process configurations according to the present invention.
  • the reciprocating compressor shown schematically in FIG. 1 has one Crankshaft 1 on which a flywheel 2 is flanged and which over Connecting rods or push rods 3 each have pistons 4 of double-acting cylinders 5 actuated.
  • About the oscillating movement of the piston 4 is gas via suction valves 6 sucked, the closing member 7 between a catcher 8 and the Valve seat 9 can move.
  • the gas sucked in becomes after the automatic Closing the respective suction valve 6 compressed in the cylinder 5 or via the here also automatic pressure valves 10 are pushed out.
  • the pressure-dependent automatic periodic opening movement of the Closing members 7, for example a valve plate or the like, the Suction valves 6 is by means of, if necessary, at least part of the Control circuit 12 acting on the closing member 7 affected.
  • This control device 12 can, for example, only one here have indicated lifting gripper 13, via a hydraulic control cylinder 14 the closing member 7 shortly before reaching the pressure equilibrium between the cylinder chamber 15 and outside of the suction valve 6 Suction chamber of the compressor forcibly opens.
  • the control device 12 comprises in addition to the control cylinder 14 an electronic not shown here Control, which is coordinated by means of a bus connection 16, which the Exchange of information between the control device 12 and an evaluation unit 17 causes.
  • the evaluation unit 17 is the signal of a via a line 18 Flywheel 2 arranged encoder 19 for dead center or crank angle supplied, thus influencing the closing members via the lifting grippers 13 7 can be synchronized with the oscillating movement of the piston 4.
  • the control device 12 from FIG. 1 is on one of the two Suction valves 6 shown in more detail.
  • the on the locking member 7 of the Suction valve 6 acting, again only symbolically shown lifting gripper 13 is actuated by a hydraulic control cylinder 14. That about one Inlet line 21 fed hydraulic fluid can in the position shown one here designed as a 3/2-way valve 20 control member 22 on the Control cylinders 14 act and thus the lifting gripper 13 on the closing member 7 press down.
  • 7 gas forces apply to the closing element try to close valve 6.
  • Due to the action of a check valve 23 is the hydraulic fluid locked in the control cylinder 14 at the return flow hindered and thereby the closing member 7 of the suction valve 6 in the open Location blocked.
  • FIG. 3 shows typical courses of the opening movement of a closing element (7 in Fig. 1 and 2) of a suction valve (6 in Fig. 1 and 2), which is controlled by the inventive method.
  • the one on the Vertical stroke applied as related to the total stroke of the locking device relative stroke plotted over a dimensionless ratio time.
  • the time scale is chosen so that when the in the display is reached dimensionless time with -1 and when reached of the lower end point of movement is set to 0.
  • Fig. 4 shows the to Fig. 3 belonging course of the speed of the locking member on the dimensionless ratio time, with a suitable, not of interest Speed scale was selected.
  • Fig. 5 shows accordingly the pressure curves in the compressor cylinder.
  • the curves labeled A represent the case where the Lifting gripper (13 in FIGS. 1 and 2) is delivered too late.
  • the locking organ 7 opens only under the effect of the differential pressure between Cylinder chamber and suction chamber of the compressor.
  • the rapid drop in cylinder pressure after passing through the pressure equilibrium causes a strong Acceleration of the locking mechanism, a high impact speed on the Catcher (8 in Fig. 1 and 2) and thus a strong and undesirable opening blow.
  • the locking member can under the effect of bounce back usual valve springing and only after one or several bumps come to rest in the open position.
  • the curves labeled B represent the opening course for a delivery time optimized according to the present invention the lifting gripper (13 in Fig. 1 and 2).
  • the closing element of the suction valve just before reaching the pressure equilibrium according to the effect of the grab impact so that at Reaching the pressure equilibrium between the cylinder space and the suction space Suction valve is already open to a large extent.
  • the conventional ones Suction valves occurring and described in the introduction suction tip is largely avoided. Consequently, engage the locking device of the Suction valve clearly compared to a conventionally designed suction valve reduced opening forces on and - as can be seen from Fig. 4 - this applies Closing device with significantly reduced impact speed on the catcher of the valve.
  • the lifting gripper (13 in FIGS. 1 and 2) is in accordance with the C If the marked curves are delivered too early, the brakes in the compressor cylinder still existing overpressure the initiated opening movement of the suction valve quickly and the gripper plus locking system comes to a standstill again. Only when the opening force and differential pressure balance each other hold, the opening movement can start again. Since the locking organ in is only slightly open when the pressure equilibrium is reached, the cylinder pressure drops similarly to when the lifting gripper is delivered too late quickly and a strong suction occurs. On the locking organ high opening forces act after a short time, so that it in turn struck the catch limiting the opening at high speed becomes.
  • the curves labeled A have a KWoff of 38 °
  • the curves marked B have a KWoff of 34 °
  • the curves marked C correspond to a KWoff of 32 °.
  • FIG. 6 shows on the basis of measurement results with another embodiment the influence of the time of delivery of the lifting gripper (13 in FIG. 1 and 2) on the opening stroke. Over time in ms are for different Points in time or crank angle of the delivery of the lifting gripper at the valve nest measured vibrations or accelerations.
  • Also shown in Fig. 6 is the time course of the indicator pressure (cylinder interior) - the the corresponding curve is denoted by H.
  • Fig. 7 shows in a similar representation as Fig. 2 an example of the Application of the method according to the invention for the indirect determination of the Opening speed of the closing member 7 by monitoring the Hydraulic medium pressure, which the periodic opening of the closing member 7th causes.
  • a via a line 27 with the inlet line 21 in Connected measuring sensor 28 used for the inlet pressure the Measurement signals evaluated by the electronics circuit arranged in the housing 26 become.
  • Figure 8 relates to a variant of the method in which the indirect Monitoring the opening speed of the sealing element 7 a Measurement or monitoring of the pressure drop at one in the feed line 21 to the control member 22 used throttle 29 by means of a differential pressure in front of and behind the throttle 29 receiving measuring sensor 28 is carried out.
  • the time of the enforced Opening of the closing member 7 selected so that the intensity of the means of Measuring sensor 28 detected via vibration monitoring in the valve area Opening stroke is minimized.
  • the one that acts as an acceleration sensor Measuring sensor 28 could, apart from being attached to the control device 12 also directly on the cylinder 5 at a suitable point, for example in the immediate vicinity Near the suction valve 6, be attached. Signals from the measuring sensor 28 are in turn arranged in the housing 26 in a manner not shown Circuit electronics evaluated and to determine the introduction the opening process of the closing member 7 is used.
  • the indicator pressure is shown here using the Measured as a pressure sensor measuring sensor 28 measured, the signal a measuring amplifier 30 amplified and with the aid of a suitable display device 31 shown as an indicator diagram over the piston stroke or alternatively is also displayed as a time signal.
  • the time of the opening of the locking mechanism can also be changed here can be selected in the manner mentioned the suction tip in the indicator diagram is minimized.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (10)

  1. Procédé pour influencer le mouvement d'ouverture périodique, autonome en fonction de la pression, d'un obturateur (7) d'une soupape d'aspiration (6) d'un compresseur à piston alternatif au moyen d'un dispositif de commande (12) agissant en cas de besoin sur l'obturateur (7) sur une partie au moins d'un cercle du vilebrequin, caractérisé en ce que peu avant d'atteindre l'équilibre de pression entre la chambre de cylindre (15) et la chambre d'aspiration du compresseur, l'obturateur (7) est ouvert à force sous faction du dispositif de commmande (12).
  2. Procédé selon la revendication 1, caractérisé en ce que l'ouverture à force s'effectue dans une plage de 90° à 0° de l'angle de vilebrequin avant d'atteindre l'équilibre de pression entre la chambre de cylindre (15) et la chambre d'aspiration.
  3. Procédé selon Tune ou l'autre des revendications 1 et 2, caractérisé en ce que l'ouverture à force est appliquée par un impact du dispositif de commande (12) sur l'obturateur (7), l'angle de vilebrequin ou l'instant de l'impact ainsi que le rapport des masses et la vitesse relative des partenaires d'impact étant choisis de telle sorte qu'après l'impact, la vitesse d'ouverture de l'obturateur (7) jusqu'à la venue en butée contre un arrêt ne chute pas à zéro et de préférence pas au-dessous de 10 % de la vitesse qui apparaít immédiatement après l'impact.
  4. Procédé selon la revendication 3, dans lequel le dispositif de commande (12) comprend un cylindre de commande hydraulique (14) qui est chargé en fluide sous pression et déchargé périodiquement via un organe de commande (22), caractérisé en ce que la pression, procurant l'ouverture périodique de l'obturateur (7), au niveau du cylindre de commande (14) ou de l'organe de commande (22) est surveillée et utilisée pour la détection ou la surveillance indirecte de la vitesse d'ouverture de l'obturateur (7).
  5. Procédé selon la revendication 3, dans lequel le dispositif de commande (12) comprend un cylindre de commande hydraulique (14) qui est chargé en fluide sous pression et déchargé périodiquement via un organe de commande (22), caractérisé en ce que le courant volumétrique du fluide sous pression est surveillé de préférence via une mesure de la chute de pression au niveau d'un étranglement (29) mis en place dans la conduite d'alimentation vers l'organe de commande (22), et utilisé pour la détection ou la surveillance indirecte de la vitesse d'ouverture de l'obturateur (7).
  6. Procédé selon l'une ou plusieurs des revendications 1 à 3, caractérisé en ce que l'on surveille l'évolution de la pression indicative dans la chambre de cylindre (15) et on choisit l'instant de l'ouverture de l'obturateur (7) de manière à minimiser la pointe de sous-aspiration dans le diagramme indicatif.
  7. Procédé selon Tune ou plusieurs des revendications 1 à 3, caractérisé en ce que l'on choisit l'angle de vilebrequin ou l'instant de l'ouverture de l'obturateur (7) de manière à minimiser l'intensité de l'impact d'ouverture constaté dans la zone de soupape via une surveillance des vibrations.
  8. Procédé selon l'une des revendications 3 à 7, caractérisé en ce que le choix ou le réglage du début de l'approche du dispositif de commande (12) s'effectue uniquement lors de la mise en service ou de l'inspection du compresseur.
  9. Procédé selon Tune des revendications 3 à 7, caractérisé en ce que dans des compresseurs que l'on fait fonctionner dans des conditions de fonctionnement fluctuantes, telles que des relations de pression fluctuantes, des gaz à exposant isentropique fluctuant et similaires, on prévoit une surveillance et une adaptation continues du début de l'approche du dispositif de commande (12).
  10. Dispositif pour influencer le mouvement d'ouverture périodique, autonome en fonction de la pression, d'un obturateur (7) d'une soupape d'aspiration (6) d'un compresseur à piston alternatif, comportant un dispositif de commande (12) agissant en cas de besoin sur l'obturateur (7) sur une partie au moins d'un cercle du vilebrequin, dispositif qui comprend un cylindre de commande hydraulique (14) qui est susceptible d'être chargé en fluide sous pression et d'être déchargé périodiquement via un organe de commande (22), caractérisé en ce que l'organe de commande (22) comprend une valve (20) à 3 voies/2 positions à commutation électrique, dont l'unité électronique de pilotage (26) est reliée à une unité d'évaluation (17) qui est en outre en liaison avec au moins un détecteur de mesure (28) pour surveiller le mouvement d'ouverture de l'obturateur (7).
EP97890047A 1996-04-12 1997-03-14 Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur Expired - Lifetime EP0801227B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT0066296A AT409655B (de) 1996-04-12 1996-04-12 Verfahren und einrichtung zur beeinflussung eines kompressor-saugventils
AT662/96 1996-04-12
AT66296 1996-04-12

Publications (3)

Publication Number Publication Date
EP0801227A2 EP0801227A2 (fr) 1997-10-15
EP0801227A3 EP0801227A3 (fr) 1999-03-03
EP0801227B1 true EP0801227B1 (fr) 2003-07-09

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EP97890047A Expired - Lifetime EP0801227B1 (fr) 1996-04-12 1997-03-14 Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur

Country Status (6)

Country Link
US (1) US5988985A (fr)
EP (1) EP0801227B1 (fr)
JP (1) JPH1030564A (fr)
AT (1) AT409655B (fr)
DE (1) DE59710392D1 (fr)
ES (1) ES2203781T3 (fr)

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Publication number Publication date
ATA66296A (de) 2002-02-15
EP0801227A3 (fr) 1999-03-03
US5988985A (en) 1999-11-23
ES2203781T3 (es) 2004-04-16
EP0801227A2 (fr) 1997-10-15
JPH1030564A (ja) 1998-02-03
AT409655B (de) 2002-10-25
DE59710392D1 (de) 2003-08-14

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