EP0193640B1 - Seated-valve device - Google Patents

Seated-valve device Download PDF

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Publication number
EP0193640B1
EP0193640B1 EP85110597A EP85110597A EP0193640B1 EP 0193640 B1 EP0193640 B1 EP 0193640B1 EP 85110597 A EP85110597 A EP 85110597A EP 85110597 A EP85110597 A EP 85110597A EP 0193640 B1 EP0193640 B1 EP 0193640B1
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EP
European Patent Office
Prior art keywords
valve
seat
plunger
stop
arrangement according
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
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EP85110597A
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German (de)
French (fr)
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EP0193640A1 (en
Inventor
Wolfgang Ing. Grad. Kaltenthaler
Manfred Ing Grad. Kramer
Hans-Dieter Gelse
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Wabco Westinghouse Fahrzeugbremsen GmbH
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Wabco Westinghouse Fahrzeugbremsen GmbH
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Publication of EP0193640A1 publication Critical patent/EP0193640A1/en
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Publication of EP0193640B1 publication Critical patent/EP0193640B1/en
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    • 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
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group

Definitions

  • the invention relates to a seat valve device according to the preamble of patent claim 1.
  • Such a seat valve device is such. B. in the "Handbook of Motor Vehicle Technology" by Buschmann / Koessler Volume 1, pages 199 and 200.
  • a compressor which is to switch from the delivery phase to the idling phase when a predetermined pressure is exceeded in a compressed air device connected to the compressor.
  • the changeover from the delivery phase to the idling phase takes place in such a way that an actuating device controlled by the predetermined pressure in the compressed air device moves the valve tappet of the seat valve device into a position in which the compression chamber of the compressor is connected to the suction chamber.
  • the compressor operates largely without pressure in the idling phase. If the pressure in the compressed air device falls below the predetermined value, the valve tappet is moved back into its starting position by the actuating device, in which the connection between the compression chamber and the suction chamber which is present through the seat valve device is closed and the compressor is working in the delivery phase.
  • a seat valve device with a valve tappet of the type described in the introduction, which serves to regulate the idle speed of a compressor, is known from US-A-2594815.
  • This valve device is arranged laterally offset in the cylinder head with respect to the compression chamber, so that the problem of a seat valve immersed in the compression chamber does not arise and consequently a limitation of the valve stroke in the opening direction by a stop is not necessary. For this, however, an increase in the dead space has to be accepted disadvantageously.
  • valve tappet When using a fixed stop for the valve tappet, however, the problem arises that when the seat valve device is opened and closed, the valve tappet is suddenly moved by suddenly acting, high control forces and is also stopped suddenly by an unyielding stroke limitation. This can result in a breakage of the valve stem or a deformation of the stop as a result of overstressed material.
  • valve tappet becomes unstable in the opening and closing phase and carries out so-called fluttering movements, which are further supported by the compression work of the compressor piston. It is known that such flutter movements of valve lifters, which are comparable to hammer blows, result in destruction of the valve seat and the valve lifter head.
  • the invention is therefore based on the object to improve a device of the type mentioned with simple means in comparison to the known devices so that when opening and closing the valve device despite sudden stroke movements of the valve stem, the forces acting on the functional parts of the valve device so it is small that destruction of the functional parts or their premature wear is largely avoided even during continuous operation.
  • the invention has the advantage that the operational safety of the valve device is increased and its service life is extended.
  • the drawing shows a partial representation of a compressor with a seat valve device in the embodiment according to the invention with a suction chamber 1, a pressure chamber 2 and a compression chamber 3.
  • a valve device 7 is arranged, which in the open position, As shown in the drawing, the compression chamber 3 connects to the suction chamber 1 via a valve seat 8 and to the atmosphere via a suction connection 9.
  • the seat valve device 7 has a valve tappet 10, a stop 11 and an actuating device for the valve tappet 10, which in the present exemplary embodiment consists of a valve piston 12.
  • the valve piston 12 is guided in a sliding and sealing manner in a bush 13 and is loaded by a spring 14 in the closing direction of the seat valve device 7.
  • the valve piston 12 is connected to the valve tappet 10 by means of a wedge connection 15 known per se in a conical, central bore 16 of the valve piston 12.
  • valve piston 12 there is a control pressure chamber 17, which is connected via a control input 26 to one on the pressure side of the com pressors is connected via a pressure connection 27 connected compressed air device.
  • the valve stem 10 has a stem 18 and a stem head 19.
  • the stem 18 is divided into three areas 20, 21 and 22 with different cross sections.
  • the shaft 18 In its central region 20, the shaft 18 has a smaller cross section than the regions 21 and 22 adjoining the central region 20 on both sides.
  • the central region 20 extends approximately to Ya of the total length of the shaft 18. The transitions from the central region 20
  • the shaft 18 to the regions 21 and 22 adjoining the central region 20 on both sides are rounded.
  • the valve piston 12 has at least one stop surface 23 which is arranged around the central axis of the valve tappet 10 and which faces a stop surface 24 of the stop 11 and which can be supported on the stop surface 24 of the stop 11.
  • the stop 11 is annular and is arranged coaxially to the central axis of the valve lifter.
  • the stop 11 has at least one stop surface 24 arranged around the central axis of the stop 11 on the side facing the valve piston 12 and at least one support surface 25 arranged around the central axis of the stop 11 on the side facing away from the valve piston 12.
  • the stop surfaces 23 and 24 and the support surface 25 can each consist of a closed ring surface or of an annular surface formed from separate surfaces.
  • the distance of the stop surface 24 from the central axis of the stop 11 is different from the distance of the support surface 25 from the central axis of the stop 11, as a result of which the stop 11 is designed to be elastic in the manner of a plate spring.
  • the stop 11 is supported with its support surface 25 against the housing part 4 of the cylinder head 5.
  • the stop surface 24 of the stop 11 serves as a stroke limiter for the valve tappet.
  • a further load which corresponds to a pressure load acting on the stop 11, is introduced into the stop 11 by the stop surface 23 of the valve lifter 10 via the stop surface 24 of the stop 11.
  • This pressure load is partially converted by the different distances between the stop surface 24 and the support surface 25 to the central axis of the stop 11 in a bending stress, which is effective in the wall area between the stop surface 24 and the support surface 25 of the stop 11 in the manner of a plate spring.
  • a remaining portion of the pressure load is supported via the support surface 25 of the stop 11 on the housing part 4 of the cylinder head 5.
  • the conversion of the pressure load into a bending stress which takes place in part due to the shape of the stop 11 described, additionally has a damping effect on the tensile stress wringing on the valve tappet 10.
  • the control pressure chamber 17 is connected to the atmosphere via the control input 26.
  • the valve tappet 10 with the valve piston 12 is suddenly moved by the spring 14, supported by the compression work of the compressor piston, into the starting position in which the seat valve device 7 is closed.
  • This stroke movement of the valve tappet 10 is stopped by the tappet head 19 of the valve tappet 10 hitting the valve seat 8.
  • the braked mass formed by the area 21 of the valve tappet 10 and the valve piston 12, causes a tensile stress in the central area 20 of the stem 18, which, as already described, is partially compensated for by the shape of the stem 18.
  • valve lifter 10 and the stop 11 Due to the shape of the valve lifter 10 and the stop 11 according to the invention, material stresses that suddenly occur when the seat valve device 7 is opened and closed are partially compensated elastically so that a break in the stem 18, a deformation of the valve piston 12 and the stop 11 in the area of the stop surfaces 23 and 24 and destruction of the sealing surface on the tappet head 19 and on the valve seat 8 is avoided.
  • the seat valve device 7 shown in the exemplary embodiment is not limited to use in connection with a compressor, but can be used in other devices in which the forces acting on such a seat valve device are of the same type or similar.
  • the actuation of the seat valve device 7 by compressed air selected in the exemplary embodiment can also take place hydraulically, electro-hydraulically or electro-pneumatically, as well as by purely mechanical actuating means.

Description

Die Erfindung betrifft eine Sitzventileinrichtung gemäss dem Oberbegriff des Patentanspruchs 1.The invention relates to a seat valve device according to the preamble of patent claim 1.

Eine solche Sitzventileinrichtung ist z. B. in dem «Handbuch der Kraftfahrzeugtechnik» von Buschmann/Koessler Band 1, Seiten 199 und 200 beschrieben. Es besteht das Bedürfnis, eine solche in einem Ottomotor übliche Einrichtung auch bei einem Kompressor zu verwenden, der bei Überschreiten eines vorgegebenen Druckes in einer mit dem Kompressor verbundenen Drucklufteinrichtung von der Förderphase in die Leerlaufphase umschalten soll. Das Umschalten von der Förderphase in die Leerlaufphase geschieht derart, dass eine von dem vorgegebenen Druck in der Drucklufteinrichtung angesteuerte Betätigungseinrichtung den Ventilstössel der Sitzventileinrichtung in eine Stellung bewegt, in der der Verdichtungsraum des Kompressors mit dem Saugraum verbunden ist. In dieser Schaltstellung der Sitzventileinrichtung arbeitet der Kompressor weitgehend drucklos in der Leerlaufphase. Bei Unterschreiten des vorgegebenen Druckes in der Drucklufteinrichtung wird der Ventilstössel durch die Betätigungseinrichtung wieder in seine Ausgangsstellung zurückbewegt, in der die durch die Sitzventileinrichtung vorhandene Verbindung zwischen dem Verdichtungsraum und dem Saugraum geschlossen ist und der Kompressor in der Förderphase arbeitet.Such a seat valve device is such. B. in the "Handbook of Motor Vehicle Technology" by Buschmann / Koessler Volume 1, pages 199 and 200. There is a need to use such a device, which is common in a gasoline engine, also in a compressor which is to switch from the delivery phase to the idling phase when a predetermined pressure is exceeded in a compressed air device connected to the compressor. The changeover from the delivery phase to the idling phase takes place in such a way that an actuating device controlled by the predetermined pressure in the compressed air device moves the valve tappet of the seat valve device into a position in which the compression chamber of the compressor is connected to the suction chamber. In this switching position of the seat valve device, the compressor operates largely without pressure in the idling phase. If the pressure in the compressed air device falls below the predetermined value, the valve tappet is moved back into its starting position by the actuating device, in which the connection between the compression chamber and the suction chamber which is present through the seat valve device is closed and the compressor is working in the delivery phase.

Im Gegensatz zu der in Ottomotoren verwendeten Sitzventileinrichtung, deren nockengesteuerter Ventilstössel ohne festen Anschlag in der Öffnungsrichtung federnd aufgehängt ist, ergibt sich bei dem beschriebenen Einsatz einer solchen Einrichtung in einem Kompressor die Notwendigkeit, für den Ventilstössel in Öffnungsrichtung des Ventilsitzes einen festen Anschlag derart vorzusehen, dass der Kopf des Ventilstössels nicht in den Verdichtungsraum hineinragen kann. Ein in den Verdichtungsraum hineinragender Stösselkopf würde eine konstruktive Vergrösserung des sogenannten Schadraumes, d. h. des Verdichtungsraumes oberhalb des Kompressorkolbens in der oberen Totpunktstellung erforderlich machen und damit die Leistung des Kompressors herabsetzen.In contrast to the poppet valve device used in gasoline engines, the cam-controlled valve tappet of which is resiliently suspended in the opening direction without a fixed stop, when using such a device in a compressor it is necessary to provide a fixed stop for the valve tappet in the opening direction of the valve seat, that the head of the valve lifter cannot protrude into the compression chamber. A plunger head protruding into the compression space would result in a constructive enlargement of the so-called harmful space, i.e. H. of the compression chamber above the compressor piston in the top dead center position and thus reduce the performance of the compressor.

Eine Sitzventileinrichtung mit einem Ventilstössel der eingangs beschriebenen Art, die der Leerlaufregelung eines Kompressors dient, ist durch die US-A-2594815 bekannt. Diese Ventileinrichtung ist bezüglich des Verdichtungsraumes seitlich versetzt im Zylinderkopf angeordnet, so dass sich das Problem eines in den Verdichtungsraum eintauchenden Sitzventils nicht stellt und mithin eine Begrenzung des Ventilhubes in Öffnungsrichtung durch einen Anschlag nicht erforderlich ist. Hierfür muss jedoch nachteilig eine Schadraumvergrösserung in Kauf genommen werden.A seat valve device with a valve tappet of the type described in the introduction, which serves to regulate the idle speed of a compressor, is known from US-A-2594815. This valve device is arranged laterally offset in the cylinder head with respect to the compression chamber, so that the problem of a seat valve immersed in the compression chamber does not arise and consequently a limitation of the valve stroke in the opening direction by a stop is not necessary. For this, however, an increase in the dead space has to be accepted disadvantageously.

Bei der Verwendung eines festen Anschlages für den Ventilstössel ergibt sich jedoch das Problem, dass beim Öffnen und Schliessen der Sitzventileinrichtung der Ventilstössel durch plötzlich wirksam werdende, hohe Steuerkräfte schlagartig bewegt und durch eine unnachgiebige Hubbegrenzung ebenso schlagartig gestoppt wird. Hierbei kann es zu einem Bruch des Ventilstössels oder zu einer Verformung des Anschlages infolge überbeanspruchten Materials kommen.When using a fixed stop for the valve tappet, however, the problem arises that when the seat valve device is opened and closed, the valve tappet is suddenly moved by suddenly acting, high control forces and is also stopped suddenly by an unyielding stroke limitation. This can result in a breakage of the valve stem or a deformation of the stop as a result of overstressed material.

Um diesem Mangel entgegenzuwirken, wäre es naheliegend, die auf die Ventileinrichtung wirkenden Steuerkräfte zu reduzieren und/oder sie allmählich ansteigend bzw. abfallend wirken zu lassen. Hierdurch wird jedoch der Ventilstössel in der Öffnungs- und Schliessphase instabil und führt sogenannte Flatterbewegungen aus, die durch die Kompressionsarbeit des Kompressorkolbens noch unterstützt werden. Es ist bekannt, dass derartige Flatterbewegungen von Ventilstösseln, die mit Hammerschlägen vergleichbar sind, eine Zerstörung des Ventilsitzes und des Ventilstösselkopfes zur Folge haben.To counteract this deficiency, it would be obvious to reduce the control forces acting on the valve device and / or to make them gradually increase or decrease. As a result, however, the valve tappet becomes unstable in the opening and closing phase and carries out so-called fluttering movements, which are further supported by the compression work of the compressor piston. It is known that such flutter movements of valve lifters, which are comparable to hammer blows, result in destruction of the valve seat and the valve lifter head.

Der Erfindung liegt deshalb die Aufgabe zugrunde, eine Einrichtung der eingangs genannten Art mit im Vergleich zu den bekannten Einrichtungen einfachen Mitteln, so zu verbessern, dass beim Öffnen und Schliessen der Ventileinrichtung trotz schlagartiger Hubbewegungen des Ventilstössels die dadurch auf die Funktionsteile der Ventileinrichtung wirkenden Kräfte so gering sind, dass eine Zerstörung der Funktionsteile oder deren vorzeitiger Verschleiss auch bei Dauerbetrieb weitgehend vermieden wird.The invention is therefore based on the object to improve a device of the type mentioned with simple means in comparison to the known devices so that when opening and closing the valve device despite sudden stroke movements of the valve stem, the forces acting on the functional parts of the valve device so it is small that destruction of the functional parts or their premature wear is largely avoided even during continuous operation.

Diese Aufgabe wird durch die im Patentanspruch 1 angegebene Erfindung gelöst. Weiterbildungen und vorteilhafte Ausführungsbeispiele der Erfindung sind in den Unteransprüchen angegeben.This object is achieved by the invention specified in claim 1. Further developments and advantageous exemplary embodiments of the invention are specified in the subclaims.

Die Erfindung hat den Vorteil, dass die Betriebssicherheit der Ventileinrichtung erhöht und deren Lebensdauer verlängert wird.The invention has the advantage that the operational safety of the valve device is increased and its service life is extended.

Die Erfindung wird anhand eines Ausführungsbeispiels, das in der Zeichnung dargestellt ist, näher erläutert.The invention is explained in more detail using an exemplary embodiment which is illustrated in the drawing.

Die Zeichnung zeigt eine Teildarstellung eines Kompressors mit einer Sitzventileinrichtung in der erfindungsgemässen Ausführungsform mit einem Saugraum 1, einem Druckraum 2 und einem Verdichtungsraum 3. In einem Zylinderkopf 5 ist neben einem Einlassventil 6 in einem Gehäuseteil 4 eine Ventileinrichtung 7 angeordnet, die in geöffneter Stellung, wie in der Zeichnung dargestellt, den Verdichtungsraum 3 über einen Ventilsitz 8 mit dem Saugraum 1 und über einem Sauganschluss 9 mit der Atmosphäre verbindet.The drawing shows a partial representation of a compressor with a seat valve device in the embodiment according to the invention with a suction chamber 1, a pressure chamber 2 and a compression chamber 3. In a cylinder head 5, in addition to an inlet valve 6 in a housing part 4, a valve device 7 is arranged, which in the open position, As shown in the drawing, the compression chamber 3 connects to the suction chamber 1 via a valve seat 8 and to the atmosphere via a suction connection 9.

Die Sitzventileinrichtung 7 hat einen Ventilstössel 10, einen Anschlag 11 und eine Betätigungseinrichtung für den Ventilstössel 10, die im vorliegenden Ausführungsbeispiel aus einem Ventilkolben 12 besteht. Der Ventilkolben 12 ist gleitend und dichtend in einer Buchse 13 geführt und durch eine Feder 14 in Schliessrichtung der Sitzventileinrichtung 7 belastet. Der Ventilkolben 12 ist mittels einer an sich bekannten Keilverbindung 15 in einer konischen, zentralen Bohrung 16 des Ventilkolbens 12 mit dem Ventilstössel 10 verbunden.The seat valve device 7 has a valve tappet 10, a stop 11 and an actuating device for the valve tappet 10, which in the present exemplary embodiment consists of a valve piston 12. The valve piston 12 is guided in a sliding and sealing manner in a bush 13 and is loaded by a spring 14 in the closing direction of the seat valve device 7. The valve piston 12 is connected to the valve tappet 10 by means of a wedge connection 15 known per se in a conical, central bore 16 of the valve piston 12.

Oberhalb des Ventilkolbens 12 befindet sich eine Steuerdruckkammer 17, die über einen Steuereingang 26 mit einer an der Druckseite des Kompressors über einen Druckanschluss 27 angeschlossenen Drucklufteinrichtung verbunden ist.Above the valve piston 12 there is a control pressure chamber 17, which is connected via a control input 26 to one on the pressure side of the com pressors is connected via a pressure connection 27 connected compressed air device.

Der Ventilstössel 10 hat einen Schaft 18 und einen Stösselkopf 19. Der Schaft 18 ist in drei Bereiche 20, 21 und 22 mit unterschiedlichem Querschnitt aufgeteilt. Der Schaft 18 hat in seinem mittleren Bereich 20 einen geringeren Querschnitt, als die sich an den mittleren Bereich 20 beiderseits anschliessenden Bereiche 21 und 22. Der mittlere Bereich 20 erstreckt sich etwa auf Ya der Gesamtlänge des Schaftes 18. Die Übergänge von dem mittleren Bereich 20 des Schaftes 18 zu den sich beiderseits an den mittleren Bereich 20 anschliessenden Bereichen 21 und 22 sind gerundet ausgebildet. Der Ventilkolben 12 hat mindestens eine um die Mittelachse des Ventilstössels 10 herum angeordnete Anschlagfläche 23, die einer Anschlagfläche 24 des Anschlages 11 zugewandt ist und die auf der Anschlagfläche 24 des Anschlages 11 abstützbar ist.The valve stem 10 has a stem 18 and a stem head 19. The stem 18 is divided into three areas 20, 21 and 22 with different cross sections. In its central region 20, the shaft 18 has a smaller cross section than the regions 21 and 22 adjoining the central region 20 on both sides. The central region 20 extends approximately to Ya of the total length of the shaft 18. The transitions from the central region 20 The shaft 18 to the regions 21 and 22 adjoining the central region 20 on both sides are rounded. The valve piston 12 has at least one stop surface 23 which is arranged around the central axis of the valve tappet 10 and which faces a stop surface 24 of the stop 11 and which can be supported on the stop surface 24 of the stop 11.

Der Anschlag 11 ist ringförmig ausgebildet und koaxial zur Mittelachse des Ventilstössels angeordnet.The stop 11 is annular and is arranged coaxially to the central axis of the valve lifter.

Der Anschlag 11 hat auf der, dem Ventilkolben 12 zugewandten Seite mindestens eine um die Mittelachse des Anschlages 11 herum angeordnete Anschlagfläche 24 und auf der dem Ventilkolben 12 abgewandten Seite mindestens eine um die Mittelachse des Anschlages 11 herum angeordnete Stützfläche 25. Die Anschlagflächen 23 und 24 sowie die Stützfläche 25 können jeweils aus einer geschlossenen Ringfläche oder aus einer aus gesonderten Flächen gebildeten Ringfläche bestehen. Der Abstand der Anschlagfläche 24 von der Mittelachse des Anschlages 11 ist unterschiedlich zu dem Abstand der Stützfläche 25 von der Mittelachse des Anschlages 11, wodurch der Anschlag 11 elastisch in der Art einer Tellerfeder ausgebildet ist. Der Anschlag 11 stützt sich mit seiner Stützfläche 25 gegen den Gehäuseteil 4 des Zylinderkopfes 5 ab. Die Anschlagfläche 24 des Anschlages 11 dient dem Ventilstössel als Hubbegrenzung.The stop 11 has at least one stop surface 24 arranged around the central axis of the stop 11 on the side facing the valve piston 12 and at least one support surface 25 arranged around the central axis of the stop 11 on the side facing away from the valve piston 12. The stop surfaces 23 and 24 and the support surface 25 can each consist of a closed ring surface or of an annular surface formed from separate surfaces. The distance of the stop surface 24 from the central axis of the stop 11 is different from the distance of the support surface 25 from the central axis of the stop 11, as a result of which the stop 11 is designed to be elastic in the manner of a plate spring. The stop 11 is supported with its support surface 25 against the housing part 4 of the cylinder head 5. The stop surface 24 of the stop 11 serves as a stroke limiter for the valve tappet.

Die Wirkungsweise dieser Einrichtung ist wie folgt:

  • Bei Überschreiten eines vorgegebenen Druckes in der mit dem Kompressor verbundenen Drucklufteinrichtung wird über den Steueranschluss 26 der Steuerdruckkammer 17 der Sitzventileinrichtung 7 ein Steuerdruck zugeführt, der den Ventilkolben 12 mit dem Ventilstössel 10 gegen die Kraft der Feder 14 in die Öffnungsstellung der Sitzventileinrichtung 7 bewegt. Diese Hubbewegung des Ventilstössels 10 wird gestoppt, wenn die Anschlagfläche 23 des Ventilkolbens 10 auf die Anschlagfläche 24 des Anschlages 11 auftrifft. Hierbei treten am Ventilstössel 10 und am Anschlag 11 schlagartige Belastungen auf. Die Belastung am Ventilstössel 10 entspricht wegen des Bewegungsimpulses des Stösselkopfes 19 einer Zugbeanspruchung, die durch den verjüngten Querschnitt im mittleren Bereich 20 des Schaftes 18 und damit durch eine erhöhte Dehnfähigkeit des Schaftes 18 teilweise kompensiert wird, so dass einem Bruch des Ventilstössels 10 entgegengewirkt wird.
This device works as follows:
  • When a predetermined pressure in the compressed air device connected to the compressor is exceeded, a control pressure is fed via the control connection 26 to the control pressure chamber 17 of the seat valve device 7, which moves the valve piston 12 with the valve tappet 10 against the force of the spring 14 into the open position of the seat valve device 7. This stroke movement of the valve plunger 10 is stopped when the stop surface 23 of the valve piston 10 strikes the stop surface 24 of the stop 11. Sudden loads occur on the valve lifter 10 and on the stop 11. The load on the valve tappet 10 corresponds to a tensile stress due to the movement impulse of the tappet head 19, which is partially compensated for by the tapered cross section in the central region 20 of the stem 18 and thus by an increased elasticity of the stem 18, so that breakage of the valve tappet 10 is counteracted.

Eine weitere Belastung, die einer auf den Anschlag 11 wirkenden Druckbelastung entspricht, wird durch die Anschlagfläche 23 des Ventilstössels 10 über die Anschlagfläche 24 des Anschlages 11 in den Anschlag 11 eingeleitet. Diese Druckbelastung wird teilweise durch die unterschiedlichen Abstände der Anschlagfläche 24 und der Stützfläche 25 zur Mittelachse des Anschlages 11 in eine Biegebeanspruchung umgewandelt, die im Wandungsbereich zwischen der Anschlagfläche 24 und der Stützfläche 25 des Anschlages 11 nach Art einer Tellerfeder wirksam wird. Ein übriger Anteil der Druckbelastung stützt sich über die Stützfläche 25 des Anschlages 11 auf den Gehäuseteil 4 des Zylinderkopfes 5 ab.A further load, which corresponds to a pressure load acting on the stop 11, is introduced into the stop 11 by the stop surface 23 of the valve lifter 10 via the stop surface 24 of the stop 11. This pressure load is partially converted by the different distances between the stop surface 24 and the support surface 25 to the central axis of the stop 11 in a bending stress, which is effective in the wall area between the stop surface 24 and the support surface 25 of the stop 11 in the manner of a plate spring. A remaining portion of the pressure load is supported via the support surface 25 of the stop 11 on the housing part 4 of the cylinder head 5.

Die durch die beschriebene Formgebung des Anschlages 11 teilweise erfolgende Umwandlung der Druckbelastung in eine Biegebeanspruchung wirkt zusätzlich dämpfend auf die am Ventilstössel 10 wrikende Zugbeanspruchung.The conversion of the pressure load into a bending stress, which takes place in part due to the shape of the stop 11 described, additionally has a damping effect on the tensile stress wringing on the valve tappet 10.

Bei Absinken des Druckes in der Drucklufteinrichtung unter einen vorgegebenen Wert wird die Steuerdruckkammer 17 über den Steuereingang 26 mit der Atmosphäre verbunden. Dadurch wird der Ventilstössel 10 mit dem Ventilkolben 12 durch die Feder 14, unterstützt durch die Kompressionsarbeit des Kompressorkolbens, schlagartig in die Ausgangsposition, in der die Sitzventileinrichtung 7 geschlossen ist, bewegt. Diese Hubbewegung des Ventilstössels 10 wird gestoppt, indem der Stösselkopf 19 des Ventilstössels 10 auf den Ventilsitz 8 aufschlägt. Durch die gebremste Masse, gebildet durch den Bereich 21 des Ventilstössels 10 und den Ventilkolben 12, tritt im mittleren Bereich 20 des Schaftes 18 eine Zugbeanspruchung auf, die durch die Form des Schaftes 18, wie bereits beschrieben, teilweise kompensiert wird.When the pressure in the compressed air device drops below a predetermined value, the control pressure chamber 17 is connected to the atmosphere via the control input 26. As a result, the valve tappet 10 with the valve piston 12 is suddenly moved by the spring 14, supported by the compression work of the compressor piston, into the starting position in which the seat valve device 7 is closed. This stroke movement of the valve tappet 10 is stopped by the tappet head 19 of the valve tappet 10 hitting the valve seat 8. The braked mass, formed by the area 21 of the valve tappet 10 and the valve piston 12, causes a tensile stress in the central area 20 of the stem 18, which, as already described, is partially compensated for by the shape of the stem 18.

Durch die erfindungsgemässe Formgebung des Ventilstössels 10 und des Anschlages 11 werden beim Öffnen und Schliessen der Sitzventileinrichtung 7 schlagartig auftretende Materialbeanspruchungen teilweise elastisch so kompensiert, dass ein Bruch des Schaftes 18, eine Verformung des Ventilkolbens 12 und des Anschlages 11 im Bereich der Anschlagflächen 23 und 24 sowie eine Zerstörung der Dichtfläche am Stösselkopf 19 und am Ventilsitz 8 vermieden wird.Due to the shape of the valve lifter 10 and the stop 11 according to the invention, material stresses that suddenly occur when the seat valve device 7 is opened and closed are partially compensated elastically so that a break in the stem 18, a deformation of the valve piston 12 and the stop 11 in the area of the stop surfaces 23 and 24 and destruction of the sealing surface on the tappet head 19 and on the valve seat 8 is avoided.

Die in dem Ausführungsbeispiel dargestellte Sitzventileinrichtung 7 ist nicht auf eine Verwendung in Verbindung mit einem Kompressor beschränkt, sondern in anderen Einrichtungen verwendbar, in denen die auf eine solche Sitzventileinrichtung wirkenden Kräfte gleicher Art oder ähnlich sind.The seat valve device 7 shown in the exemplary embodiment is not limited to use in connection with a compressor, but can be used in other devices in which the forces acting on such a seat valve device are of the same type or similar.

Die in dem Ausführungsbeispiel gewählte Ansteuerung der Sitzventileinrichtung 7 durch Druckluft kann auch hydraulisch, elektro-hydraulisch oder elektro-pneumatisch, sowie durch rein mechanische Betätigungsmittel erfolgen.The actuation of the seat valve device 7 by compressed air selected in the exemplary embodiment can also take place hydraulically, electro-hydraulically or electro-pneumatically, as well as by purely mechanical actuating means.

Claims (9)

1. Seat valve arrangement having the following features:
a) a valve seat and a valve plunger movable relative thereto are provided;
b) the valve plunger has a stem and a plunger head, wherein the plunger head, together with the valve seat, forms the seat valve;
c) the stem of the valve plunger has a reduction in its cross-section forming a region which is resiliently extensible, the transitions of which region to the adjoining regions on either side are of rounded construction;
characterized by the following features:
d) a stop (11) for limiting the movement of the valve plunger (10) in the opening direction of the seat valve (8, 19) is provided;
e) the cross-sectional reduction is located in a middle region (20) of the stem (18), which region extends for about one third of the length of the stem (18) and which in the direction of the plunger head (19) extends beyond a region (21) of the valve plunger (10) in which the forces exerted by the stop (11) on the valve plunger (10) are initiated.
2. Seat valve arrangement according to claim 1, characterized by the following feature: an actuating device for the movement of the valve plunger (10) in the opening direction of the seat valve (8, 19) is provided.
3. Seat valve arrangement according to claim 2, characterized by the following feature: the actuating device for the valve plunger (10) consists of a valve piston (12) which is connected to the valve plunger (10).
4. Seat valve arrangement according to claim 3, characterized by the following feature: the valve piston (12) is connected by means of a wedge connection (15) known per se to the valve plunger (10).
5. Seat valve arrangement according to claim 4, characterized by the following feature: the valve piston (12) has a tapering, central bore which is a part of the wedge connection (15).
6. Seat valve arrangement according to claim 1, characterized by the following feature: the stop (11) for limiting the movement of the valve plunger (10) is of annular construction and is arranged coaxially with respect to the central axis of the valve plunger (10).
7. Seat valve arrangement according to claim 6, characterized by the following feature: the stop (11) is constructed to be resilient in the form of a cup spring.
8. Seat valve arrangement according to claim 1, characterized by the following feature: the seat valve arrangement (7) is used in conjunction with a compressor having a piston moving backwards and forwards, with spring-loaded inlet and outlet valves, with a pressure chamber, a suction chamber and a compression chamber.
9. Seat valve arrangement according to claim 8, characterized by the following feature: for the duration of a given operating state of a compressed air device connected to the compressor, the seat valve arrangement (7) connects the compression chamber with the suction chamber of the compressor.
EP85110597A 1984-12-18 1985-08-23 Seated-valve device Expired EP0193640B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843446096 DE3446096A1 (en) 1984-12-18 1984-12-18 SEAT VALVE DEVICE
DE3446096 1984-12-18

Publications (2)

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EP0193640A1 EP0193640A1 (en) 1986-09-10
EP0193640B1 true EP0193640B1 (en) 1988-10-26

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Application Number Title Priority Date Filing Date
EP85110597A Expired EP0193640B1 (en) 1984-12-18 1985-08-23 Seated-valve device

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US (1) US4685653A (en)
EP (1) EP0193640B1 (en)
DE (2) DE3446096A1 (en)

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Also Published As

Publication number Publication date
US4685653A (en) 1987-08-11
DE3446096A1 (en) 1986-06-19
EP0193640A1 (en) 1986-09-10
DE3565876D1 (en) 1988-12-01

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