EP1086312B1 - Piston-type accumulator for a hydraulic fluid to be supplied to a consumer in a hydraulic installation - Google Patents
Piston-type accumulator for a hydraulic fluid to be supplied to a consumer in a hydraulic installation Download PDFInfo
- Publication number
- EP1086312B1 EP1086312B1 EP99927842A EP99927842A EP1086312B1 EP 1086312 B1 EP1086312 B1 EP 1086312B1 EP 99927842 A EP99927842 A EP 99927842A EP 99927842 A EP99927842 A EP 99927842A EP 1086312 B1 EP1086312 B1 EP 1086312B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- tappet
- cylinder
- control valve
- type accumulator
- 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
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
- B61D7/00—Hopper cars
- B61D7/14—Adaptations of hopper elements to railways
- B61D7/16—Closure elements for discharge openings
- B61D7/24—Opening or closing means
- B61D7/28—Opening or closing means hydraulic or pneumatic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/027—Installations or systems with accumulators having accumulator charging devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/04—Accumulators
- F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
- F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/20—Accumulator cushioning means
- F15B2201/205—Accumulator cushioning means using gas
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/30—Accumulator separating means
- F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/40—Constructional details of accumulators not otherwise provided for
- F15B2201/41—Liquid ports
- F15B2201/411—Liquid ports having valve means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/40—Constructional details of accumulators not otherwise provided for
- F15B2201/415—Gas ports
- F15B2201/4155—Gas ports having valve means
Definitions
- the invention relates to a piston accumulator for a consumer in one Hydraulic system pressure fluid to be supplied, in particular for hydraulic Actuation of the unloading device with not self-propelled Vehicles for bulk goods, with one flying in a cylinder, dividing the cylinder into an oil space and a gas space Piston, connections provided on the oil space for supply of the charging fluid flow and discharge of the working fluid flow, one axially in the cylinder movable shift plunger, which with its inner end with the piston cooperates and with its outer end in the gas space delimiting Cylinder cover is guided, and with a shutdown device for the switching fluid serving the charging fluid flow, which via a switchable Bypassing the bypass pipeline serving with the piston accumulator the connection for the charging fluid flow connected to the oil space and through the outer end of the switching plunger is actuated, which is sealed by the Cylinder cover led outwards and on the outside of the cylinder as Actuator for the switching valve is accessible, which one at the The outside of the cylinder cover forms a detachably
- a piston accumulator of this type is known, which for Operation of the bulk material unloading device provided for railway wagons is.
- the hydraulic system provided in such wagons has at least one hydraulic pump driven by a relevant wheel set on a charging fluid flow during the movement of the wagon pumps into the piston accumulator If the set operating pressure in the When memory reaches, the shutdown device causes the charging fluid flow via the bypass pipeline to the tank connection of the hydraulic system is diverted and thus flows into the fluid reservoir.
- the invention has for its object a piston accumulator of said To create kind that stands out in a compact design by a special distinguishes good operating behavior.
- This inner guidance opens up the possibility of defining the gas space Form part of the cylinder in a considerable length, which is achieved that the volume of the gas space within the piston accumulator very large compared to the piston displacement in the oil chamber can be.
- This has the particular advantage that it covers the entire area Working stroke of the piston resulting pressure difference despite compact design the memory remains relatively small, which for the safe Operation of the hydraulic system in question, i.e. in the special case of the bulk material unloading device, is particularly cheap.
- the cylinder of a piston accumulator is designated by 1, the interior of which is divided into an oil chamber 5 and a gas chamber 7 by an overhung separating piston 3.
- Fig. 2 shows the piston 3 in its end position against the cylinder base 9, which corresponds to the operating state in which the oil chamber 5 is not charged by a supplied charging fluid flow, the volume of the oil chamber 5 under the influence of the compressed gas in the gas chamber 7 (at Embodiment N 2 ) is therefore practically reduced to zero by moving the piston 3.
- the cylinder base 9 For the supply of the charging fluid flow to the oil space 5, the cylinder base 9 a port 11 to which the pressure fluid from the associated Hydraulic pump 13 can be fed via a check valve 15.
- a second Connection 17 on the cylinder base 9 enables the working fluid flow to be removed via a check valve 19 to the consumer concerned, i.e. in the special case mentioned to the working cylinder of the assigned Bulk unloading.
- One on the check valve 15 with the Connection 11 on the oil chamber 5 connecting bypass pipeline 21 forms a bridging of the piston accumulator for the charging fluid stream and forms in cooperation with one with the pipeline 21 connected, interacting with the check valve 69
- Switching valve 23 a switch-off device for the charging fluid flow.
- a switching plunger 25 is in the form of an actuator for the switching valve 23 a relatively long round rod in the cylinder 1 axially displaceable.
- the Switch plunger 25 is by the spring force of a spring assembly, which at embodiment shown by a plate spring assembly 33 (see in particular Fig. 3) is formed for its advanced against the separating piston 3 Biased end position, which is shown in Fig. 2, in which the Switch plunger 25 with its relevant end 35 via the partition 29 protrudes by a distance that the actuating path of the actuator 37 of the switching valve 23 is adapted.
- the partition 29 forms a mechanical one Stop for limiting the flow of fluid through the charge effected lifting movement of the separating piston 3, which is in contact with the Partition 29 in cooperation with the end 35 of the switching plunger 25 this against the spring force of the plate spring assembly 33 for actuating the Switching valve 23 moves (in Fig. 2 to the right).
- the partition extends 29 opposite, outer end of the switching plunger 25 by a closure of the gas space 7 screwed into the relevant end of the cylinder 1 Cylinder cover 39 through, with a set of seals 41 for Formation of a seal against the bore 45 of the cylinder cover 39 cooperates with a tapered section 43 of the switching plunger 25.
- This tapered section 43 extends through a dirt deflector 47 into an extension 49 of the bore 45 into which the Switch plunger 25 to form a shoulder surface 51 in a diameter passes even further tapered, end-side shaft portion 53.
- the extension 49 takes the plate spring assembly 33 surrounding the shaft part 53 on the one hand on the shoulder surface 51 of the switching plunger 25 and on the other hand, in an internal thread 55 of the bore extension 49 screwed threaded sleeve 57 supports.
- Fig. 2 filling valve can be seen for the supply of the compressed gas to the gas space 7 designated 59.
- the end of the shaft part forms 53 of the switching plunger 25, a coupling member 61 for the articulated connection with the actuator 37 of the switching valve 23.
- a commercial directional control valve of the slide type which as removable unit can be unscrewed directly from a base plate 72 is that via a holding frame 63 and a screw 65 with the Cylinder cover 30 is connected.
- the bypass pipeline 21 with the switching valve 23 connected which when actuated, i.e. when the switching plunger 23 Actuator 37 moves against the acting spring force (in the drawing to the right), the charge pressure of the oil space prevailing in the pipeline 21 5 connects to a control line 67.
- the Control line 67 becomes hydraulic connected to it unlockable check valve 69 unlocked.
- the check valve 69 is like this switched that it is in the unlocked state upstream of it
- Throttle 70 provides fluid communication from the bypass pipe 21 to the Tank connection 71 releases.
Abstract
Description
Die Erfindung betrifft einen Kolbenspeicher für einem Verbraucher in einer Hydraulikanlage zuzuführendes Druckfluid, insbesondere zur hydraulischen Betätigung der Entladeeinrichtung bei nicht mit Eigenantrieb versehenen Fahrzeugen für Schüttgüter, mit einem in einem Zylinder fliegend angeordneten, den Zylinder in einen Ölraum und einen Gasraum unterteilenden Kolben, am Ölraum vorgesehenen Anschlüssen für Zufuhr des Lade-Fluidstromes und Abfuhr des Arbeits-Fluidstromes, einem im Zylinder axial beweglichen Schaltstößel, der mit seinem inneren Ende mit dem Kolben zusammenwirkt und mit seinem äußeren Ende im den Gasraum begrenzenden Zylinderdeckel geführt ist, und mit einem als Abschalteinrichtung für den Lade-Fluidstrom dienenden Schaltventil, das über eine als schaltbare Überbrückung des Kolbenspeichers dienende Umgehungs-Rohrleitung mit dem Anschluß für den Lade-Fluidstrom am Ölraum verbunden und durch das äußere Ende des Schaltstößels betätigbar ist, das unter Abdichtung durch den Zylinderdeckel nach außen geführt und an der Außenseite des Zylinders als Betätigungsglied für das Schaltventil zugänglich ist, welches eine an der Außenseite des Zylinderdeckels abnehmbar anbringbare Baueinheit bildet.The invention relates to a piston accumulator for a consumer in one Hydraulic system pressure fluid to be supplied, in particular for hydraulic Actuation of the unloading device with not self-propelled Vehicles for bulk goods, with one flying in a cylinder, dividing the cylinder into an oil space and a gas space Piston, connections provided on the oil space for supply of the charging fluid flow and discharge of the working fluid flow, one axially in the cylinder movable shift plunger, which with its inner end with the piston cooperates and with its outer end in the gas space delimiting Cylinder cover is guided, and with a shutdown device for the switching fluid serving the charging fluid flow, which via a switchable Bypassing the bypass pipeline serving with the piston accumulator the connection for the charging fluid flow connected to the oil space and through the outer end of the switching plunger is actuated, which is sealed by the Cylinder cover led outwards and on the outside of the cylinder as Actuator for the switching valve is accessible, which one at the The outside of the cylinder cover forms a detachably attachable unit.
Aus der DE-A-1 185 025 ist ein Kolbenspeicher dieser Art bekannt, der zur Betätigung der Schüttgut-Entladeeinrichtung bei Eisenbahnwaggons vorgesehen ist. Die bei derartigen Waggons vorgesehene Hydraulikanlage weist mindestens eine durch einen betreffenden Radsatz angetriebene Hydropumpe auf, die während der Fahrbewegung des Waggons einen Lade-Fluidstrom in den Kolbenspeicher pumpt Wird hierbei der eingestellte Betriebsdruck im Speicher erreicht, bewirkt die Abschalteinrichtung, daß der Lade-Fluidstrom über die Umgehungs-Rohrleitung drucklos zum Tankanschluß der Hydraulikanlage umgeleitet wird und somit in den Fluid-Vorratsbehälter abfließt.From DE-A-1 185 025 a piston accumulator of this type is known, which for Operation of the bulk material unloading device provided for railway wagons is. The hydraulic system provided in such wagons has at least one hydraulic pump driven by a relevant wheel set on a charging fluid flow during the movement of the wagon pumps into the piston accumulator If the set operating pressure in the When memory reaches, the shutdown device causes the charging fluid flow via the bypass pipeline to the tank connection of the hydraulic system is diverted and thus flows into the fluid reservoir.
Der Erfindung liegt die Aufgabe zugrunde, einen Kolbenspeicher der besagten Art zu schaffen, der sich bei kompakter Bauweise durch ein besonders gutes Betriebsverhalten auszeichnet.The invention has for its object a piston accumulator of said To create kind that stands out in a compact design by a special distinguishes good operating behavior.
Bei einem Kolbenspeicher der eingangs genannten Art ist diese Aufgabe erfindungsgemäß dadurch gelöst, daß der Schaltstößel an seinem für die Zusammenwirkung mit dem Kolben vorgesehenen inneren Ende in einer im Gasraum befindlichen, an der Innenwand des Zylinders befestigten Traverse längsverschiebbar geführt.In the case of a piston accumulator of the type mentioned at the outset, this is the task solved according to the invention in that the switching plunger on his for Interaction with the piston provided in an inner end Traverse located on the inner wall of the cylinder guided longitudinally.
Diese innere Führung eröffnet die Möglichkeit, den den Gasraum definierenden Teil des Zylinders in einer beträchtlichen Baulänge auszubilden, wodurch erreicht wird, daß das Volumen des Gasraumes innerhalb des Kolbenspeichers gegenüber dem Hubvolumen des Kolbens im Ölraum sehr groß werden kann. Dies hat den besonderen Vorteil, daß die sich über den gesamten Arbeitshub des Kolbens ergebende Druckdifferenz trotz kompakter Bauweise des Speichers verhältnismäßig gering bleibt, was für den sicheren Betrieb der betreffenden Hydraulikanlage, also im speziellen Fall der Schüttgut-Entladeeinrichtung, besonders günstig ist.This inner guidance opens up the possibility of defining the gas space Form part of the cylinder in a considerable length, which is achieved that the volume of the gas space within the piston accumulator very large compared to the piston displacement in the oil chamber can be. This has the particular advantage that it covers the entire area Working stroke of the piston resulting pressure difference despite compact design the memory remains relatively small, which for the safe Operation of the hydraulic system in question, i.e. in the special case of the bulk material unloading device, is particularly cheap.
Nachstehend ist die Erfindung an Hand eines in der Zeichnung dargestellten Ausführungsbeispieles im einzelnen erläutert. Es zeigen:
- Fig. 1
- eine schematisierte Blockdarstellung des Kolbenspeichers mit zugehöriger hydraulischer Schaltung;
- Fig. 2
- einen Längsschnitt des Kolbenspeichers und
- Fig. 3
- einen gegenüber Fig. 2 in größerem Maßstab gezeichneten Teillängsschnitt, in dem ein Teil des Zylinderdeckels mit zugehörigen Komponenten gezeigt ist.
- Fig. 1
- a schematic block diagram of the piston accumulator with associated hydraulic circuit;
- Fig. 2
- a longitudinal section of the piston accumulator and
- Fig. 3
- a partial longitudinal section compared to Fig. 2 drawn on a larger scale, in which a part of the cylinder cover is shown with associated components.
In der Blockdarstellung von Fig. 1 ist der Zylinder eines Kolbenspeichers
mit 1 bezeichnet, dessen Innenraum durch einen fliegend angeordneten
Trennkolben 3 in einen Ölraum 5 und einen Gasraum 7 unterteilt ist. Fig. 2
zeigt den Kolben 3 in seiner am Zylinderfuß 9 anliegenden Endstellung,
was dem Betriebszustand entspricht, bei dem der Ölraum 5 nicht durch
einen zugeführten Lade-Fluidstrom aufgeladen ist, das Volumen des Ölraumes
5 unter Einfluß des im Gasraum 7 befindlichen Druckgases (beim
Ausführungsbeispiel N2) durch Verschieben des Kolbens 3 daher praktisch
auf null reduziert ist.In the block diagram of FIG. 1, the cylinder of a piston accumulator is designated by 1, the interior of which is divided into an oil chamber 5 and a
Für die Zufuhr des Lade-Fluidstromes zum Ölraum 5 weist der Zylinderfuß
9 einen Anschluß 11 auf, zu dem das Druckfluid von der zugeordneten
Hydro pumpe 13 über ein Rückschlagventil 15 zuführbar ist. Ein zweiter
Anschluß 17 am Zylinderfuß 9 ermöglicht die Abfuhr des Arbeits-Fluidstromes
über ein Rückschlagventil 19 zum betreffenden Verbraucher,
d.h. im erwähnten speziellen Fall zum Arbeitszylinder der zugeordneten
Schüttgut-Entladeeinrichtung. Eine über das Rückschlagventil 15 mit dem
Anschluß 11 am Ölraum 5 in Verbindung stehende Umgehungs-Rohrleitung
21 bildet für den Lade-Fluid strom eine Überbrückung des Kolbenspeichers
und bildet in Zusammenwirkung mit einem mit der Rohrleitung
21 verbundenen, mit dem Rückschlagventil 69 zusammenwirkenden
Schaltventil 23 eine Abschalteinrichtung für den Lade-Fluidstrom.For the supply of the charging fluid flow to the oil space 5, the cylinder base
9 a
Als Betätigungsglied für das Schaltventil 23 ist ein Schaltstößel 25 in Form
eines verhältnismäßig langen Rundstabes im Zylinder 1 axial längsverschiebbar.
Eine an einer Rippe 27 an der Innenwand des Zylinders 1 befestigte
Trennwand 29 mit einem Gasdurchlaß 31 bildet am inneren Endbereich
des Schaltstößels 25 eine Führung für dessen Axialbewegung. Der
Schaltstößel 25 ist durch die Federkraft einer Federanordnung, die beim
gezeigten Ausführungsbeispiel durch ein Tellerfederpaket 33 (siehe insbesondere
Fig. 3) gebildet ist, für seine gegen den Trennkolben 3 hin vorgeschobene
Endstellung vorgespannt, die in Fig. 2 gezeigt ist, bei der der
Schaltstößel 25 mit seinem betreffenden Ende 35 über die Trennwand 29
hinaus um eine Strecke vorspringt, die dem Betätigungsweg des Stellgliedes
37 des Schaltventiles 23 angepaßt ist. Die Trennwand 29 bildet einen mechanischen
Anschlag für die Begrenzung der durch den Lade-Fluidstrom
bewirkten Hubbewegung des Trennkolbens 3, der bei Anlage an der
Trennwand 29 in Zusammenwirkung mit dem Ende 35 des Schaltstößels 25
diesen gegen die Federkraft des Tellerfederpakets 33 zur Betätigung des
Schaltventiles 23 verschiebt (in der Fig. 2 nach rechts).A
Wie den Fig. 2 und 3 zu entnehmen ist, erstreckt sich das der Trennwand
29 entgegengesetzte, äußere Ende des Schaltstößels 25 durch einen als Abschluß
des Gasraumes 7 in das betreffende Ende des Zylinders 1 eingeschraubten
Zylinderdeckel 39 hindurch, wobei ein Dichtungssatz 41 zur
Bildung einer Abdichtung gegenüber der Bohrung 45 des Zylinderdeckels
39 mit einem verjüngten Abschnitt 43 des Schaltstößels 25 zusammenwirkt.
Dieser verjüngte Abschnitt 43 erstreckt sich durch einen Schmutzabweiser
47 hindurch in eine Erweiterung 49 der Bohrung 45 hinein, in der der
Schaltstößel 25 unter Bildung einer Schulterfläche 51 in einen im Durchmesser
noch weiter verjüngten, endseitigen Schaftteil 53 übergeht. Die Erweiterung
49 nimmt das den Schaftteil 53 umgebende Tellerfederpaket 33
auf, das sich einerseits an der Schulterfläche 51 des Schaltstößel 25 und
andererseits an einer in ein endseitiges Innengewinde 55 der Bohrungserweiterung
49 eingeschraubten Gewindehülse 57 abstützt. Ein nur in Fig. 2
zu sehendes Füllventil für die Zufuhr des Druckgases zum Gasraum 7 ist
mit 59 bezeichnet.As can be seen in FIGS. 2 and 3, the partition extends
29 opposite, outer end of the
Wie insbesondere aus Fig. 3 zu ersehen ist, bildet das Ende des Schaftteiles
53 des Schaltstößels 25 ein Kupplungsglied 61 für die gelenkige Verbindung
mit dem Stellglied 37 des Schaltventiles 23. Dieses ist beim Ausführungsbeispiel
ein handelsübliches Wegeventil vom Schieber-Typ, das als
abnehmbare Baueinheit von einer Grundplatte 72 unmittelbar abschraubbar
ist, die über einen Halterahmen 63 und eine Verschraubung 65 mit dem
Zylinderdeckel 30 verbunden ist.As can be seen in particular from FIG. 3, the end of the shaft part forms
53 of the
Wie Fig. 1 zeigt, ist die Umgehungs-Rohrleitung 21 mit dem Schaltventil 23
verbunden, welches bei Betätigung, d.h., wenn der Schaltstößel 23 das
Stellglied 37 gegen die wirkende Federkraft verschiebt (in der Zeichnung
nach rechts), den in der Rohrleitung 21 herrschenden Ladedruck des Ölraumes
5 zu einer Steuerleitung 67 durchschaltet. Durch den Druck der
Steuerleitung 67 wird ein mit dieser in Verbindung stehendes, hydraulisch
entsperrbares Rückschlagventil 69 entsperrt. Das Rückschlagventil 69 ist so
geschaltet, daß es im entsperrten Zustand über eine ihm vorgeschaltete
Drossel 70 eine Fluidverbindung von der Umgehungs-Rohrleitung 21 zum
Tankanschluß 71 freigibt.As shown in FIG. 1, the
Wenn bei Erreichen eines vorbestimmten Ladedruckes im Ölraum 5 der
Kolben 3 den Schaltstößel 25 beaufschlagt und gegen die wirkende Federkraft
zur Betätigung des Schaltventils 23 verschiebt und dieses dementsprechend
den in der Umgehungs-Rohrleitung 21 herrschenden Ladedruck zur
Steuerleitung 67 durchschaltet, erfolgt über das entsperrte Rückschlagventil
69 und die vorgeschaltete Drossel 70 die drucklose Abfuhr des Lade-Fluidstromes,
so daß der Kolbenspeicher hydraulisch überbrückt ist. Aufgrund
der am Schaltventil 23 und dem Schaltstößel 25 wirkenden, vorspannenden
Federkraft kehrt bei einem Abfall des Ladedruckes im Ölraum
5, bei dem sich der Kolben 3 vom Ende 35 des Schaltstößels 25 entfernt,
das Schaltventil 23 in den Schaltzustand zurück, bei dem der mit der Rohrleitung
21 verbundene Anschluß gesperrt ist und die Steuerleitung 67 mit
dem Tankanschluß 71 verbunden, d.h drucklos ist. Somit ist das Rückschlagventil
69 nicht länger entsperrt, und die Überbrückung des Kolbenspeichers
über die Umgehungs-Rohrleitung 21 ist unterbunden, so daß der
Lade-Fluidstrom zur Aufladung des Kolbenspeichers wieder wirksam werden
kann.If when a predetermined boost pressure in the oil chamber 5 is reached
Piston 3 acts on the
Claims (7)
- Piston-type accumulator for hydraulic liquid delivered to a consumer in a hydraulic system, notably for hydraulic actuation of a discharge unit on bulk goods vehicles without their own drive, with a piston (3) supported at one side in a cylinder (1), dividing the cylinder into an oil chamber (5) and a gas chamber (7), with ports (11 or 17) provided at the oil chamber (5) for delivery of the charge fluid and discharging the working fluid, with a tappet (25) co-acting at its inner end (35) with the piston (3) and guided with its outer end in the cylinder cover (39) delimiting the gas chamber (7), and with a control valve (23) serving as a cut-out device for the charge fluid, the said control valve communicating, via the by-pass line (21) serving as a controllable line bridging the piston-type accumulator, with the port (11) for the charge fluid at the oil chamber (5) and actuated by the outer end of the tappet (25) which is guided towards the outside by passing in a sealed manner through the cylinder cover (39) and being accessible at the outside of the cylinder (1) as the actuating element for the control valve (23) which forms a removably mountable unit on the outside of the cylinder cover (39), characterised in that the tappet (25) is guided movably in the longitudinal direction at its inner end (35) envisaged for co-acting with the piston (3), in a cross beam (29) located in the gas chamber (7) and attached to the inner wall of the cylinder (1).
- A piston-type accumulator according to Claim 1, characterised in that the cross beam is in the form of a separating wall (29) with at least one gas passage (31), forming a stop limiting the movement of the piston (3) above which the end (35) of the tappet (25) protrudes by an amount equivalent to the length of the operating stroke of the control valve under the effect of a pre-loading spring force when the piston (3) is in a position away from the stop, so that the tappet (25) is slidable when the piston (3) abuts at the stop against the spring force to operate the control valve (23).
- A piston-type accumulator as in Claim 2, characterised in that a stack of spring washers (33) is provided to produce the spring force, the said stack of spring washers being accommodated within an enlarged section (49) of the bore (45) provided for the tappet (25) to pass through the cylinder cover (39), at its end.
- A piston-type accumulator according to Claim 3, characterised in that the tappet (25) has at its outer end a shank (53), with a reduced diameter to form a shoulder face (51), extending in the enlarged section (49) of the bore (45) in the cylinder cover (39) through the stack of spring washers (33) supported at one end at the shoulder face (51) of the tappet (25) and at the other at a threaded sleeve (57) screwed into the enlarged section (49) of the bore (45) in the cylinder cover (39).
- A piston-type accumulator according to Claim 4, characterised in that the end of the tappet (25) serving as the actuating member of the control valve has a coupling member (61) for connecting to the movable adjusting member (37) of the control valve (23) attachable at the cylinder cover (39).
- A piston-type accumulator according to one of the Claims 1 to 5, characterised in that a commercial-type way-valve (23) is envisaged as the control valve.
- A piston-type accumulator according to one of the Claims 1 to 6, characterised in that a non-return valve (69), hydraulically unblockable by means of the control valve, with a throttle valve (70) upstream of it, is envisaged for creating a hydraulic connection effecting the cutting off of the charge flow between the by-pass line (21) and the tank connection (71) of the hydraulic system.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19827363 | 1998-06-19 | ||
DE19827363A DE19827363A1 (en) | 1998-06-19 | 1998-06-19 | Piston store for hydraulic fluid in vehicle for friable goods without own drive |
PCT/EP1999/003816 WO1999067536A1 (en) | 1998-06-19 | 1999-06-02 | Piston-type accumulator for a hydraulic fluid to be supplied to a consumer in a hydraulic installation |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1086312A1 EP1086312A1 (en) | 2001-03-28 |
EP1086312B1 true EP1086312B1 (en) | 2003-05-21 |
Family
ID=7871409
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99927842A Expired - Lifetime EP1086312B1 (en) | 1998-06-19 | 1999-06-02 | Piston-type accumulator for a hydraulic fluid to be supplied to a consumer in a hydraulic installation |
Country Status (9)
Country | Link |
---|---|
US (1) | US6332477B1 (en) |
EP (1) | EP1086312B1 (en) |
JP (1) | JP2002519590A (en) |
AT (1) | ATE241087T1 (en) |
DE (2) | DE19827363A1 (en) |
DK (1) | DK1086312T3 (en) |
ES (1) | ES2200523T3 (en) |
PT (1) | PT1086312E (en) |
WO (1) | WO1999067536A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101435450B (en) * | 2007-11-13 | 2011-09-07 | 中国国际海运集装箱(集团)股份有限公司 | Hydraulic unit, castor assembly and container moving device and method |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10244705B3 (en) * | 2002-09-24 | 2004-01-08 | Gesellschaft für technische Entwicklungen mbH | Device for reducing and equalizing the pressure of a viscous medium |
EP2058527A3 (en) * | 2007-11-08 | 2012-05-30 | Parker-Hannifin Corporation | Lightweight high pressure repairable piston composite accumulator with slip flange |
EP2060797A3 (en) | 2007-11-13 | 2012-11-14 | Parker-Hannifin Corporation | Lightweight high pressure repairable piston tie rod composite accumulator |
US9127661B2 (en) | 2010-10-25 | 2015-09-08 | Hamilton Sundstrand Corporation | Bootstrap accumulator system with telescoping actuator cylinder |
ITBO20120233A1 (en) * | 2012-04-27 | 2013-10-28 | Magneti Marelli Spa | HYDRAULIC SERVO OF A SERVO-CHANGE |
CN105604741B (en) * | 2016-03-14 | 2018-01-12 | 武汉科技大学 | Dimethyl ether engine Premixed combustion combustion system valve opening control device |
US10954966B2 (en) | 2017-10-25 | 2021-03-23 | Raytheon Company | Bootstrap accumulator containing integrated bypass valve |
US11885454B2 (en) * | 2019-12-27 | 2024-01-30 | Performance Pulsation Control, Inc. | Bladder saver device |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2743741A (en) * | 1952-09-29 | 1956-05-01 | Techron Ltd | Hydraulic accumulator |
US2797708A (en) * | 1953-06-02 | 1957-07-02 | Gen Motors Corp | Accumulator |
US3043341A (en) * | 1957-07-12 | 1962-07-10 | Loewy Eng Co Ltd | Hydraulic accumulator |
DE1188247B (en) * | 1959-10-17 | 1965-03-04 | Friedrich Stuebbe | Pressure fluid accumulator for the hydraulic drive of injection molding machines, machine tools or the like. |
FR1297881A (en) * | 1961-05-26 | 1962-07-06 | Sealing packing | |
DE1185025B (en) * | 1962-06-13 | 1965-01-07 | Montan Hydraulik G M B H & Co | Pressure oil accumulator for hydraulic equipment controlled by a valve |
US3979910A (en) * | 1973-04-16 | 1976-09-14 | Canada Wire And Cable Limited | Closed circuit hydraulic control system |
US3901279A (en) * | 1974-01-30 | 1975-08-26 | Karl Schnell | Filling apparatus for pasty media, particularly for sausage meat |
JPS51133631A (en) * | 1975-05-16 | 1976-11-19 | Hitachi Ltd | Dash pot |
DE3048651A1 (en) * | 1980-12-23 | 1982-07-15 | Gesellschaft für Hydraulik-Zubehör mbH, 6603 Sulzbach | Pressure vessel with moving wall - has plunger in stationary wall acting on external switch |
US4343477A (en) * | 1981-02-04 | 1982-08-10 | Combustion Engineering, Inc. | Sealing device with thermal expansion pressure accumulator |
US4457348A (en) * | 1982-07-07 | 1984-07-03 | Mueller Martin J | Food product fill pump |
DE3705642A1 (en) * | 1986-07-02 | 1988-01-14 | Man Nutzfahrzeuge Gmbh | ENERGY STORAGE AND DELIVERY DEVICE |
DE3744179A1 (en) * | 1987-12-24 | 1989-07-06 | Integral Hydraulik Co | Mounting and filling device for a hydropneumatic piston accumulator |
DE9113007U1 (en) * | 1991-10-19 | 1991-12-19 | Bolenz & Schaefer Maschinenfabrik Gmbh, 3560 Biedenkopf, De | |
US6116585A (en) * | 1997-08-11 | 2000-09-12 | Mannesmann Sachs Ag | Pressure holder with an enclosed gas mass |
-
1998
- 1998-06-19 DE DE19827363A patent/DE19827363A1/en not_active Withdrawn
-
1999
- 1999-06-02 DE DE59905659T patent/DE59905659D1/en not_active Expired - Fee Related
- 1999-06-02 PT PT99927842T patent/PT1086312E/en unknown
- 1999-06-02 WO PCT/EP1999/003816 patent/WO1999067536A1/en active IP Right Grant
- 1999-06-02 EP EP99927842A patent/EP1086312B1/en not_active Expired - Lifetime
- 1999-06-02 JP JP2000556159A patent/JP2002519590A/en active Pending
- 1999-06-02 ES ES99927842T patent/ES2200523T3/en not_active Expired - Lifetime
- 1999-06-02 US US09/601,134 patent/US6332477B1/en not_active Expired - Fee Related
- 1999-06-02 DK DK99927842T patent/DK1086312T3/en active
- 1999-06-02 AT AT99927842T patent/ATE241087T1/en not_active IP Right Cessation
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101435450B (en) * | 2007-11-13 | 2011-09-07 | 中国国际海运集装箱(集团)股份有限公司 | Hydraulic unit, castor assembly and container moving device and method |
Also Published As
Publication number | Publication date |
---|---|
PT1086312E (en) | 2003-10-31 |
DE59905659D1 (en) | 2003-06-26 |
US6332477B1 (en) | 2001-12-25 |
DK1086312T3 (en) | 2003-09-15 |
WO1999067536A1 (en) | 1999-12-29 |
ES2200523T3 (en) | 2004-03-01 |
EP1086312A1 (en) | 2001-03-28 |
DE19827363A1 (en) | 1999-12-23 |
ATE241087T1 (en) | 2003-06-15 |
JP2002519590A (en) | 2002-07-02 |
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