EP0782672A1 - Regulating device for displacement pumps - Google Patents

Regulating device for displacement pumps

Info

Publication number
EP0782672A1
EP0782672A1 EP95932754A EP95932754A EP0782672A1 EP 0782672 A1 EP0782672 A1 EP 0782672A1 EP 95932754 A EP95932754 A EP 95932754A EP 95932754 A EP95932754 A EP 95932754A EP 0782672 A1 EP0782672 A1 EP 0782672A1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
channel
choke
spring
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.)
Granted
Application number
EP95932754A
Other languages
German (de)
French (fr)
Other versions
EP0782672B1 (en
Inventor
Konrad Eppli
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP0782672A1 publication Critical patent/EP0782672A1/en
Application granted granted Critical
Publication of EP0782672B1 publication Critical patent/EP0782672B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids

Definitions

  • the invention relates to a control device for positive displacement pumps, in particular vane pumps which have a pressure chamber which is connected to a pressure channel connected to an outlet via a bore in which a throttle piston can be displaced against the force of a spring.
  • the throttle piston controls an outlet cross-section depending on the pump speed or the flow rate.
  • a spring-loaded flow control piston is present in a housing bore, the front end face of which is connected to the pressure chamber.
  • a rear end face of the flow control piston projects into a chamber which contains the outlet pressure downstream of the throttle device.
  • the flow control piston releases a connection from the pressure chamber to a pump inlet channel depending on the differential pressure acting on the two end faces.
  • Such a control device is known from DE 41 01 210-A1.
  • the throttle piston moves with increasing speed due to a dynamic pressure acting on one end face.
  • a control edge cuts a piston opening connected to a pressure chamber, so that the reducing cross-section of the passage means that less and less pressure oil can flow out to an outlet.
  • This arrangement represents the throttle device.
  • the differential pressure acting on the flow control piston increases so that it regulates an ever increasing flow rate to the pump inlet side. Since the controllable opening is in the throttle piston, the differential pressure also acts on the rear of the piston of the throttle device. In a basic position, the throttle piston closes off with its end face a passage connected to the pressure chamber or the interior, for which purpose a relatively stiff spring is required. This spring force must be overcome by the delivery pressure when the pump starts. For this reason, a significantly higher pump pressure must be built up in one pressure zone in a double-flow pump, so that the pump runs relatively loud because of the different pressures. In addition, the piston is designed as a stepped piston with a snug fit, which requires a certain amount of production.
  • the invention has for its object to provide a control device for a falling flow rate characteristic with as little construction effort as possible, without significantly increasing the power consumption of the pump.
  • the falling characteristic curve should also be independent of the opening travel and the differential pressure of the flow control piston in order to avoid a disturbance variable.
  • the novel throttle device is designed in such a way that the pressure chamber in the area of the bore containing the throttle piston is continuously connected to a spring chamber via a bypass channel and the throttle piston controls the cross section of a throttle channel connecting the spring chamber to the outlet channel.
  • bypass channel Pour into a bearing housing in a T-shape, the vertical duct section being open towards the bore.
  • FIG. 1 shows a longitudinal section through a vane pump with the control device, in which the throttle piston and the flow control piston are in their basic position
  • Fig. 2 is a partial cross section along the line II-II in Fig. 1 and
  • FIG. 3 shows detail III of FIG. 1 on an enlarged scale.
  • the vane pump is used to deliver pressure oil in a container (not shown) to a consumer (not shown), for example an auxiliary power steering system.
  • a rotor set 3 is inserted in an oil-filled pressure chamber 1 of a housing 2.
  • the rotor set 3 consists of a cam ring 4 and a rotor 5.
  • the rotor 5 is arranged in the interior of the cam ring 4 and has radially directed slots in which vanes 6 can be displaced.
  • Working chambers are formed between the cam ring, the rotor 5 and the vanes 6 and are delimited in the axial direction by control surfaces of adjacent control plates 7 and 8.
  • the housing 2 is composed of a bearing housing 10 and a cup-shaped housing cover 11.
  • the rotor 5 is mounted in the bearing housing 10 via a drive shaft 12.
  • the bearing point in the bearing housing 10 is the only bearing of the drive shaft 12. This means that the drive shaft 12 is not supported in the housing cover 11 in the radial direction. Rather, the drive shaft is supported on the housing cover 11 in the axial direction.
  • a flow control valve 13 is provided in the bearing housing 10 for regulating the pressure oil led to the pressure connection.
  • the formation of the flow control valve 13 and a pressure relief valve, which is also still present and is not visible, is generally known, for example from US Pat. No. 5,098,259 and is therefore not described in more detail.
  • the suction and pressure channels which connect the working chambers to the suction connection, the flow control valve 13 and the pressure relief valve are arranged in the bearing housing 10. These channels are also generally known and are therefore not described in detail.
  • the control plate 7 has two openings 14 and 14A, which with the between Rotor 5, the cam ring 4 and the wings 6 formed pressure-carrying working chambers are connected.
  • the delivery pressure prevails in pressure chamber 1.
  • a piston bore 15 axially adjoins the upper opening 14.
  • the piston bore 15 contains a throttle piston 17, on which a spring 16 inserted into a spring chamber 15A presses.
  • the pressure chamber 1 is continuously connected via a bypass duct 18 via the spring chamber 15A and a throttle duct 20 controllable by the throttle piston 17 to an outlet duct 21 leading to the consumer.
  • a chamfer 19 on the throttle piston 17 controls the throttling process.
  • a suction channel 9 is connected to the oil container.
  • the bypass channel 18, as can be seen from the cross section in FIG. 2, is cast into the bearing housing 10 in a T-shape and is open towards the piston bore 15 with its vertically extending channel section 18A. In each position of the throttle piston 17, the connection from the pressure chamber 1 to the outlet channel 21 is therefore maintained. The throttle piston 17 therefore does not require a snug fit.
  • the spring 16 presses the throttle piston 17 against the control plate 7.
  • the vanes 6 push the oil trapped between them through the openings 14 and 14A.
  • the throttle piston 17 is displaced to the right by the dynamic pressure acting on its end face. The higher the flow rate through the opening 14, the further the throttle piston 17 moves against the force of the spring 16.
  • the throttle piston 17 reduces the outflow through the throttle duct 20 to the outlet duct 21 more or less.
  • the respective flow cross-section of the throttle duct 20, which specifies the delivery quantity of the pump available in the consumer, can be therefore change depending on the pump speed. The falling flow characteristic is obtained.
  • control piston 22 acts as a pressure compensator and this shifts to the right against the force of a spring 23 and against the force of the outlet pressure prevailing in a chamber 24.
  • the end face of the control piston 22 opens an inlet channel 25. A partial flow thus returns to the inlet side of the pump in a known manner.
  • the throttle piston 17 is not influenced by the differential pressure of the control piston 22 with its spring 23, but is shifted by the flow of the one opening 14 via the bypass channel 18. This measure provides a continuous displacement path of the throttle piston 17 with a small spring force.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

The invention relates to a displacement pump, e.g. a vane cell pump, with a flow regulating valve (13) on the control piston (22) of which act the pump pressure on the one hand and the consumer pressure taken via a choke device on the other. The control piston (22) acts as a pressure scale in which the pressure difference as the pump speed rises acts as a measure of the adjusted quantity conveyed. The choke device for setting the pressure difference contains a choke piston (17) movable against the force of a spring (16) in a piston drilling (15), which closes off an aperture (14) on the pressure side in a control disc (7) in the basic position. According to the invention, the piston drilling (15) has a by-pass channel (18) which continuously connects the pump with a spring chamber (15A) in the choke piston (17). In addition, depending on the flow rate, the choke piston controls the cross-section of a choke channel (20) providing a connection between the spring chamber (15A) and the outlet channel (21). The arrangement has the advantage that the differential pressure of the control piston (22) cannot affect the choke piston (17) of the choke device. As the spring force acting on the choke piston (17) can be reduced, power is saved.

Description

Regeleinrichtung für Verdrängerpumpen Control device for positive displacement pumps
Die Erfindung betrifft eine Regeleinrichtung für Ver- drängerpumpen, insbesondere Flügelzellenpumpen- die einen Druckraum aufweisen, der über eine Bohrung, in welcher ein Drosselkolben gegen die Kraft einer Feder verschiebbar ist, mit einem an einen Auslaß angeschlossenen Druckkanal in Verbindung steht. Der Drosselkolben steuert einen Auslaß- querschnitt in Abhängigkeit von der Pumpendrehzahl bzw. vom Förderstrom. In einer Gehäusebohrung ist außerdem ein fe¬ derbelasteter Stromregelkolben vorhanden, dessen vordere Stirnfläche mit dem Druckraum in Verbindung steht. Eine hintere Stirnfläche des Stromregelkolbens ragt in eine Kam- mer, die stromabwärts der Drosseleinrichtung den Ausla߬ druck enthält. Der Stromregelkolben gibt in Abhängigkeit des auf die beiden Stirnflächen wirkenden Differenzdruckes eine Verbindung vom Druckraum zu einem Pumpeneinlaßkanal frei .The invention relates to a control device for positive displacement pumps, in particular vane pumps which have a pressure chamber which is connected to a pressure channel connected to an outlet via a bore in which a throttle piston can be displaced against the force of a spring. The throttle piston controls an outlet cross-section depending on the pump speed or the flow rate. In addition, a spring-loaded flow control piston is present in a housing bore, the front end face of which is connected to the pressure chamber. A rear end face of the flow control piston projects into a chamber which contains the outlet pressure downstream of the throttle device. The flow control piston releases a connection from the pressure chamber to a pump inlet channel depending on the differential pressure acting on the two end faces.
Eine derartige Regeleinrichtung ist aus der DE 41 01 210-A1 bekannt. In dieser Pumpe verschiebt sich der Drosselkolben mit steigender Drehzahl durch einen auf eine Stirnseite wirkenden Staudruck. Dabei schneidet eine Steuerkante eine an einen Druckraum angeschlossene Kolben¬ öffnung an, so daß der sich verringernde Durchtrittsquer¬ schnitt immer weniger Drucköl zu einem Auslaß abströmen läßt. Diese Anordnung stellt die Drosseleinrichtung dar.Such a control device is known from DE 41 01 210-A1. In this pump, the throttle piston moves with increasing speed due to a dynamic pressure acting on one end face. A control edge cuts a piston opening connected to a pressure chamber, so that the reducing cross-section of the passage means that less and less pressure oil can flow out to an outlet. This arrangement represents the throttle device.
Durch die Verringerung des Durchtrittsquerschnitts er¬ höht sich der auf den Stromregelkolben einwirkende Diffe¬ renzdruck, so daß dieser einen immer größeren Förderstrom zur Pumpeneinlaßseite abregelt. Da sich die steuerbare Öff¬ nung im Drosselkolben befindet, wirkt der Differenzdruck auch auf die Rückseite des Kolbens der Drosseleinrichtung. Der Drosselkolben sperrt in einer Grundstellung mit seiner Stirnseite einen mit dem Druckraum bzw. dem Innenraum ver¬ bundenen Durchlaß ab, wozu eine verhältnismäßig steife Fe¬ der erforderlich ist. Diese Federkraft muß beim Anlauf der Pumpe vom Förderdruck überwunden werden. Aus diesem Grunde muß in einer zweiflutigen Pumpe in der einen Druckzone ein wesentlich höherer Pumpendruck aufgebaut werden, so daß die Pumpe wegen der unterschiedlichen Drücke verhältnismäßig laut läuft. Außerdem ist der Kolben als Stufenkolben mit Paßsitz ausgeführt, der einen gewissen Fertigungsaufwand erforderlich macht.By reducing the passage cross section, the differential pressure acting on the flow control piston increases so that it regulates an ever increasing flow rate to the pump inlet side. Since the controllable opening is in the throttle piston, the differential pressure also acts on the rear of the piston of the throttle device. In a basic position, the throttle piston closes off with its end face a passage connected to the pressure chamber or the interior, for which purpose a relatively stiff spring is required. This spring force must be overcome by the delivery pressure when the pump starts. For this reason, a significantly higher pump pressure must be built up in one pressure zone in a double-flow pump, so that the pump runs relatively loud because of the different pressures. In addition, the piston is designed as a stepped piston with a snug fit, which requires a certain amount of production.
Der Erfindung liegt die Aufgabe zugrunde, mit mög¬ lichst geringem Bauaufwand eine Regeleinrichtung für eine fallende Förderstromkennlinie zu schaffen, ohne die Lei¬ stungsaufnahme der Pumpe wesentlich zu erhöhen. Die fallen¬ de Kennlinie soll außerdem unabhängig vom Öffnungsweg und vom Differenzdruck des Stromregelkolbens sein, um eine Störgröße zu vermeiden.The invention has for its object to provide a control device for a falling flow rate characteristic with as little construction effort as possible, without significantly increasing the power consumption of the pump. The falling characteristic curve should also be independent of the opening travel and the differential pressure of the flow control piston in order to avoid a disturbance variable.
Diese Aufgabe ist durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Ausgestaltungen ergeben sich aus den Ansprüchen 2 und 3.This object is solved by the features of claim 1. Advantageous configurations result from claims 2 and 3.
Die neuartige Drosseleinrichtung ist so gestaltet, daß der Druckraum im Bereich der den Drosselkolben enthaltenden Bohrung über einen Umgehungskanal ständig mit einem Feder¬ raum in Verbindung steht und der Drosselkolben den Quer¬ schnitt eines den Federraum mit dem Auslaßkanal verbinden- den Drosselkanals steuert.The novel throttle device is designed in such a way that the pressure chamber in the area of the bore containing the throttle piston is continuously connected to a spring chamber via a bypass channel and the throttle piston controls the cross section of a throttle channel connecting the spring chamber to the outlet channel.
Nach Anspruch 2 ist es zweckmäßig, den Umgehungskanal T-förmig in ein Lagergehäuse einzugießen, wobei der senk¬ recht verlaufende Kanalabschnitt zur Bohrung hin offen ist.According to claim 2, it is useful to the bypass channel Pour into a bearing housing in a T-shape, the vertical duct section being open towards the bore.
Durch den Umgehungskanal ist die Wirkung des Diffe- renzdruckes vom Drosselkolben unabhängig, d. h., der Diffe¬ renzdruck am Regelkolben kann nicht auf den Drosselkolben einwirken. Dies ermöglicht den Einbau einer schwächeren Feder, wodurch geringere Leistungsverluste entstehen.Due to the bypass channel, the effect of the differential pressure is independent of the throttle piston. that is, the differential pressure at the control piston cannot act on the throttle piston. This enables the installation of a weaker spring, which results in lower power losses.
Schließlich ist es nach Anspruch 3 vorteilhaft, denFinally, it is advantageous according to claim 3
Beginn der Bewegung des Drosselkolbens durch eine enge Boh¬ rung in der Steuerplatte und damit die Förderströmkennlinie zu beeinflussen. Über diese Bohrung läßt sich ein Teil der Fördermenge zum Druckraum ableiten.To influence the beginning of the movement of the throttle piston through a narrow bore in the control plate and thus the flow characteristic. Part of the flow rate can be discharged to the pressure chamber via this bore.
Anhand der Zeichnung ist ein Ausführungsbeispiel der Erfindung näher erläutert. Es zeigen:An exemplary embodiment of the invention is explained in more detail with reference to the drawing. Show it:
Fig. 1 einen Längsschnitt durch eine Flügelzellen¬ pumpe mit der Regeleinrichtung, in welcher sich der Drosselkolben und der Stromregel¬ kolben in ihrer Grundstellung befinden;1 shows a longitudinal section through a vane pump with the control device, in which the throttle piston and the flow control piston are in their basic position;
Fig. 2 einen Teilquerschnitt nach der Linie II-II in Fig. 1 undFig. 2 is a partial cross section along the line II-II in Fig. 1 and
Fig. 3 die Einzelheit III der Fig. 1 in vergrößer¬ tem Maßstab.3 shows detail III of FIG. 1 on an enlarged scale.
Die Flügelze lenpumpe dient zum Fördern von Drucköl in einem nicht dargestellten Behälter zu einem nicht darge¬ stellten Verbraucher, beispielsweise einer Hilfskraftlen¬ kung. In einem ölgefüllten Druckraum 1 eines Gehäuses 2 ist ein Rotorensatz 3 eingesetzt. Der Rotorensatz 3 besteht aus einem Kurvenring 4 und einem Rotor 5. Der Rotor 5 ist im Inneren des Kurvenringes 4 angeordnet und weist radial ge- richtete Schlitze auf, in denen Flügel 6 verschiebbar sind. Zwischen dem Kurvenring, dem Rotor 5 und den Flügeln 6 sind Arbeitskammern gebildet, die von Steuerflächen benachbarter Steuerplatten 7 und 8 in axialer Richtung begrenzt sind.The vane pump is used to deliver pressure oil in a container (not shown) to a consumer (not shown), for example an auxiliary power steering system. A rotor set 3 is inserted in an oil-filled pressure chamber 1 of a housing 2. The rotor set 3 consists of a cam ring 4 and a rotor 5. The rotor 5 is arranged in the interior of the cam ring 4 and has radially directed slots in which vanes 6 can be displaced. Working chambers are formed between the cam ring, the rotor 5 and the vanes 6 and are delimited in the axial direction by control surfaces of adjacent control plates 7 and 8.
Das Gehäuse 2 ist aus einem Lagergehäuse 10 und einem topfförmigen Gehäusedeckel 11 zusammengesetzt. Der Rotor 5 ist über eine Antriebswelle 12 in dem Lagergehäuse 10 gela¬ gert. Die Lagerstelle in dem Lagergehäuse 10 ist die ein¬ zige Lagerung der Antriebswelle 12. Dies bedeutet, daß die Antriebswelle 12 in dem Gehäusedeckel 11 in radialer Rich¬ tung nicht gelagert ist. Die Antriebswelle stützt sich vielmehr an dem Gehäusedeckel 11 in axialer Richtung ab.The housing 2 is composed of a bearing housing 10 and a cup-shaped housing cover 11. The rotor 5 is mounted in the bearing housing 10 via a drive shaft 12. The bearing point in the bearing housing 10 is the only bearing of the drive shaft 12. This means that the drive shaft 12 is not supported in the housing cover 11 in the radial direction. Rather, the drive shaft is supported on the housing cover 11 in the axial direction.
Neben einem nicht sichtbaren Sauganschluß für den An- Schluß des Behälters sowie einem gleichfalls nicht sicht¬ baren Druckanschluß für den Verbraucher ist in dem Lager¬ gehäuse 10 ein Stromregelventil 13 für die Regelung des zu dem Druckanschluß geführten Drucköls vorgesehen. Die Aus¬ bildung des Stromregelventils 13 und eines außerdem noch vorhandenen, nicht sichtbaren Druckbegrenzungsventils ist allgemein bekannt, beispielsweise aus der US-A 5 098 259 und wird daher nicht näher beschrieben. Ebenso sind die Saug- und Druckkanäle, die die Arbeitskammern mit dem Saug¬ anschluß, dem Stromregelventil 13 und dem Druckbegrenzungs- ventil verbinden, in dem Lagergehäuse 10 angeordnet. Auch diese Kanäle sind allgemein bekannt und werden deshalb nicht näher beschrieben.In addition to an invisible suction connection for the connection of the container and an equally invisible pressure connection for the consumer, a flow control valve 13 is provided in the bearing housing 10 for regulating the pressure oil led to the pressure connection. The formation of the flow control valve 13 and a pressure relief valve, which is also still present and is not visible, is generally known, for example from US Pat. No. 5,098,259 and is therefore not described in more detail. Likewise, the suction and pressure channels which connect the working chambers to the suction connection, the flow control valve 13 and the pressure relief valve are arranged in the bearing housing 10. These channels are also generally known and are therefore not described in detail.
In einer zweiflutigen Pumpe hat die Steuerplatte 7 zwei Durchbrüche 14 und 14A, die mit dem zwischen dem Rotor 5, dem Kurvenring 4 und den Flügeln 6 gebildeten druckführenden Arbeitskammern in Verbindung stehen. Im Druckraum 1 herrscht dabei der Förderdruck. An den oberen Durchbruch 14 schließt axial eine Kolbenbohrung 15 an. Die Kolbenbohrung 15 enthält einen Drosselkolben 17, auf den eine in einen Federraum 15A eingesetzte Feder 16 drückt. Nach der Erfindung steht der Druckraum 1 über einen Umge¬ hungskanal 18 ständig über den Federraum 15A und einen durch den Drosselkolben 17 steuerbaren Drosselkanal 20 mit einem zum Verbraucher führenden Auslaßkanal 21 in Verbin¬ dung. Eine Fase 19 am Drosselkolben 17 steuert hierbei den Drosselvorgang. Ein Saugkanal 9 hat mit dem Ölbehälter Ver¬ bindung.In a double-flow pump, the control plate 7 has two openings 14 and 14A, which with the between Rotor 5, the cam ring 4 and the wings 6 formed pressure-carrying working chambers are connected. The delivery pressure prevails in pressure chamber 1. A piston bore 15 axially adjoins the upper opening 14. The piston bore 15 contains a throttle piston 17, on which a spring 16 inserted into a spring chamber 15A presses. According to the invention, the pressure chamber 1 is continuously connected via a bypass duct 18 via the spring chamber 15A and a throttle duct 20 controllable by the throttle piston 17 to an outlet duct 21 leading to the consumer. A chamfer 19 on the throttle piston 17 controls the throttling process. A suction channel 9 is connected to the oil container.
Der Umgehungskanal 18 ist, wie aus dem Querschnitt der Fig. 2 ersichtlich, T-förmig in das Lagergehäuse 10 einge¬ gossen und mit seinem senkrecht verlaufenden Kanalabschnitt 18A zur Kolbenbohrung 15 hin offen. In jeder Stellung des Drosselkolbens 17 bleibt daher die Verbindung von dem Druckraum 1 zum Auslaßkanal 21 erhalten. Der Drosselkol¬ ben 17 benötigt daher keinen Paßsitz.The bypass channel 18, as can be seen from the cross section in FIG. 2, is cast into the bearing housing 10 in a T-shape and is open towards the piston bore 15 with its vertically extending channel section 18A. In each position of the throttle piston 17, the connection from the pressure chamber 1 to the outlet channel 21 is therefore maintained. The throttle piston 17 therefore does not require a snug fit.
In der Ausgangsstellung, solange die Pumpe steht, drückt die Feder 16 den Drosselkolben 17 gegen die Steuer- platte 7. Sobald der Rotor 5 dreht, drücken die Flügel 6 das zwischen sich eingeschlossene Öl durch die Durchbrüche 14 und 14A. Dabei verschiebt sich der Drosselkolben 17 durch den auf seine Stirnfläche wirkenden Staudruck nach rechts. Je höher der Förderstrom durch den Durchbruch 14 ansteigt, desto weiter verschiebt sich der Drosselkolben 17 gegen die Kraft der Feder 16. Der Drosselkolben 17 verrin¬ gert dabei den Abfluß durch den Drosselkanal 20 zum Ausla߬ kanal 21 mehr oder weniger. Der jeweilige Durchström¬ querschnitt des Drosselkanals 20, der die im Verbraucher bereitstehende Fördermenge der Pumpe vorgibt, läßt sich daher in Abhängigkeit von der Pumpendrehzahl verändern. Man erhält dadurch die fallende Förderstromkennlinie.In the starting position, as long as the pump is stopped, the spring 16 presses the throttle piston 17 against the control plate 7. As soon as the rotor 5 rotates, the vanes 6 push the oil trapped between them through the openings 14 and 14A. The throttle piston 17 is displaced to the right by the dynamic pressure acting on its end face. The higher the flow rate through the opening 14, the further the throttle piston 17 moves against the force of the spring 16. The throttle piston 17 reduces the outflow through the throttle duct 20 to the outlet duct 21 more or less. The respective flow cross-section of the throttle duct 20, which specifies the delivery quantity of the pump available in the consumer, can be therefore change depending on the pump speed. The falling flow characteristic is obtained.
Mit steigender Drehzahl nimmt der Differenzdruck auf die dem Durchbruch 14A zugewandte Stirnfläche des zumWith increasing speed, the differential pressure on the end face facing the opening 14A increases
Stromregelventil 13 gehörenden Regelkolbens 22 zu. Der Re¬ gelkolben 22 wirkt als Druckwaage und dieser verschiebt sich gegen die Kraft einer Feder 23 und gegen die Kraft des in einer Kammer 24 herrschenden Auslaßdruckes nach rechts. Dabei öffnet die Stirnfläche des Regelkolbens 22 einen Ein¬ laßkanal 25. Ein Teilstrom gelangt somit in bekannter Weise wieder auf die ZulaufSeite der Pumpe.Flow control valve 13 belonging to control piston 22. The control piston 22 acts as a pressure compensator and this shifts to the right against the force of a spring 23 and against the force of the outlet pressure prevailing in a chamber 24. In this case, the end face of the control piston 22 opens an inlet channel 25. A partial flow thus returns to the inlet side of the pump in a known manner.
Wesentlich für die Erfindung ist, daß der Drosselkol- ben 17 nicht vom Differenzdruck des Regelkolbens 22 mit seiner Feder 23 beeinflußt wird, sondern durch den Förder¬ strom des einen Durchbruchs 14 über den Umgehungskanal 18 verschoben wird. Durch diese Maßnahme erhält man bei klei¬ ner Federkraft einen kontinuierlichen Verschiebeweg des Drosselkolbens 17.It is essential for the invention that the throttle piston 17 is not influenced by the differential pressure of the control piston 22 with its spring 23, but is shifted by the flow of the one opening 14 via the bypass channel 18. This measure provides a continuous displacement path of the throttle piston 17 with a small spring force.
Die fallende Kennlinie läßt sich durch folgende Kriterien verändern:The falling characteristic can be changed using the following criteria:
a) Durch eine Bohrung 26 in der Steuerplatte 8, wie strichpunktiert angedeutet, läßt sich der Beginn der Bewegung des Drosselkolbens 17 beeinflussen; b) Steife der Feder 16; c) Querschnitt des Umgehungskanals 18; d) Länge und Form des Drosselkolbens 17 und der Steuerfase 19; e) Durchmesser und Lage der Drosselbohrung 20. Bezugszeichena) Through a bore 26 in the control plate 8, as indicated by dash-dotted lines, the start of the movement of the throttle piston 17 can be influenced; b) stiffness of the spring 16; c) cross section of the bypass channel 18; d) length and shape of the throttle piston 17 and the control chamfer 19; e) Diameter and position of the throttle bore 20. Reference numerals
1 Druckraum1 pressure room
2 Gehäuse2 housings
3 Rotorsatz3 rotor set
4 Kurvenring4 curve ring
5 Rotor5 rotor
6 Flügel6 wings
7 Steuerplatte7 control plate
8 Steuerplatte8 control plate
9 Saugkanal9 suction channel
10 Lagergehäuse10 bearing housings
11 Gehäusedeckel11 housing cover
12 Antriebswelle12 drive shaft
13 Stromregelventil13 flow control valve
14 Durchbruch14 breakthrough
14A Durchbruch14A breakthrough
15 Kolbenbohrung15 piston bore
15A Federraum15A spring chamber
16 Feder16 spring
17 Drosselkolben17 throttle pistons
18 Umgehungskanal18 bypass channel
18A Kanalabschnitt18A channel section
19 Fase an 1719 chamfer on 17
20 Drosselkanal20 throttle channel
21 Auslaßkanal21 outlet duct
22 Regelkolben von 1322 control pistons from 13
23 Feder von 1323 spring of 13
24 Kammer von 1324 chamber of 13
25 Einlaßkanal25 inlet duct
26 Bohrung in 8 26 hole in 8

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Regeleinrichtung für Verdrängerpumpen, insbesondere Flügelzellenpumpen, mit folgenden Merkmalen: ein Druckraum (1) steht über eine Bohrung (15), in welcher ein Drosselkolben (17) gegen die Kraft einer Feder (16) verschiebbar ist, mit einem Ausla߬ kanal (21) in Verbindung; - der Kolben steuert einen Auslaßquerschnitt (Drosselka¬ nal 20) in Abhängigkeit vom Förderstrom; eine vordere Stirnfläche eines in einer Gehäusebohrung verschiebbaren, federbelasteten Regelkolbens (22) steht mit dem Druckraum in Verbindung; - eine hintere Stirnfläche des Regelkolbens (22) ragt in eine Kammer (24), die den Auslaßdruck enthält; der Regelkolben (22) gibt in Abhängigkeit des auf die beiden Stirnflächen wirkenden Differenzdruckes eine Verbindung vom Druckraum zu einem Pumpeneinlaß- kanal (25) frei, g e k e n n z e i c h n e t durch folgende Merkmale: der Druckraum (1) steht im Bereich der den Drosselkol¬ ben (17) enthaltenden Bohrung (15) über einen Umge¬ hungskanal (18) ständig mit einem Federraum (15A) des Drosselkolbens (17) in Verbindung und der Drosselkolben (17) steuert den Querschnitt eines den Federraum (15A) mit dem Auslaßkanal (21) verbin¬ denden Drosselkanals (20).1. Control device for positive displacement pumps, in particular vane pumps, with the following features: a pressure chamber (1) extends over a bore (15) in which a throttle piston (17) can be displaced against the force of a spring (16) with an outlet channel ( 21) in connection; - The piston controls an outlet cross section (Drosselka¬ channel 20) depending on the flow rate; a front end face of a spring-loaded control piston (22) which is displaceable in a housing bore is connected to the pressure chamber; - A rear end face of the control piston (22) protrudes into a chamber (24) containing the outlet pressure; the control piston (22) releases a connection from the pressure chamber to a pump inlet channel (25) depending on the differential pressure acting on the two end faces, characterized by the following features: the pressure chamber (1) is in the area of the throttle piston (17) containing bore (15) via a bypass channel (18) with a spring chamber (15A) of the throttle piston (17) in connection and the throttle piston (17) controls the cross section of the spring chamber (15A) with the outlet channel (21) the throttle channel (20).
2. Regeleinrichtung nach Anspruch 1, dadurch g e ¬ k e n n z e i c h n e t , daß der Umgehungskanal (18) T-förmig in ein Lagergehäuse (10) eingegossen ist und der senkrecht verlaufende Kanalabschnitt (18A) zur Bohrung (15) hin offen ist. 2. Control device according to claim 1, characterized ge ¬ indicates that the bypass channel (18) is T-shaped in a bearing housing (10) and the vertical channel section (18A) to the bore (15) is open.
3. Regeleinrichtung nach Anspruch 1, dadurch g e ¬ k e n n z e i c h n e t , daß sich durch eine Boh¬ rung (26) in der Steuerplatte (8) der Beginn der Bewegung des Drosselkolbens (17) und damit die Förderstromkennlinie beeinflussen läßt. 3. Control device according to claim 1, characterized in that the start of the movement of the throttle piston (17) and thus the flow characteristic can be influenced by a bore (26) in the control plate (8).
EP95932754A 1994-09-21 1995-09-15 Regulating device for displacement pumps Expired - Lifetime EP0782672B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4433598A DE4433598A1 (en) 1994-09-21 1994-09-21 Control device for positive displacement pumps
DE4433598 1994-09-21
PCT/EP1995/003629 WO1996009475A1 (en) 1994-09-21 1995-09-15 Regulating device for displacement pumps

Publications (2)

Publication Number Publication Date
EP0782672A1 true EP0782672A1 (en) 1997-07-09
EP0782672B1 EP0782672B1 (en) 1998-12-02

Family

ID=6528751

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95932754A Expired - Lifetime EP0782672B1 (en) 1994-09-21 1995-09-15 Regulating device for displacement pumps

Country Status (8)

Country Link
US (1) US5810565A (en)
EP (1) EP0782672B1 (en)
JP (1) JPH10505889A (en)
KR (1) KR100344812B1 (en)
BR (1) BR9508971A (en)
DE (2) DE4433598A1 (en)
ES (1) ES2124589T3 (en)
WO (1) WO1996009475A1 (en)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
WO2018059385A1 (en) * 2016-09-28 2018-04-05 比亚迪股份有限公司 Electric motor oil pump assembly, steering system and vehicle
WO2018059382A1 (en) * 2016-09-28 2018-04-05 比亚迪股份有限公司 Electric motor oil pump assembly, steering system and vehicle
EP3521627A4 (en) * 2016-09-28 2019-10-09 BYD Company Limited Electric motor oil pump assembly, steering system and vehicle

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DE19651386B4 (en) * 1996-12-11 2004-12-16 Zf Friedrichshafen Ag Vane pump
JP3771675B2 (en) 1997-06-24 2006-04-26 株式会社日立製作所 Flow control device for positive displacement pump
JP3656205B2 (en) * 1997-06-25 2005-06-08 株式会社日立製作所 Hydraulic pump for power steering system
DE19745118B4 (en) * 1997-10-11 2006-10-12 Wabco Gmbh & Co.Ohg Pressure generating equipment
DE19745448C1 (en) * 1997-10-15 1999-01-21 Zahnradfabrik Friedrichshafen Pressure pump for motor vehicle power steering
DE19747341A1 (en) * 1997-10-27 1999-04-29 Zahnradfabrik Friedrichshafen Displacement pump
JPH11148480A (en) * 1997-11-14 1999-06-02 Mitsubishi Heavy Ind Ltd Compressor
DE19833373A1 (en) * 1998-07-24 2000-01-27 Zahnradfabrik Friedrichshafen Supply flow regulating device for displacement pump, with movable sprung piston having throttle boring into which conical pin projects
DE19833700A1 (en) * 1998-07-27 2000-02-03 Zahnradfabrik Friedrichshafen Pressure control for hydraulic servo pump has a spring loaded control valve with a conical valve element to progressively close the hydraulic outlet with increasing pump pressure
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018059385A1 (en) * 2016-09-28 2018-04-05 比亚迪股份有限公司 Electric motor oil pump assembly, steering system and vehicle
WO2018059382A1 (en) * 2016-09-28 2018-04-05 比亚迪股份有限公司 Electric motor oil pump assembly, steering system and vehicle
EP3521627A4 (en) * 2016-09-28 2019-10-09 BYD Company Limited Electric motor oil pump assembly, steering system and vehicle
US11035386B2 (en) 2016-09-28 2021-06-15 Byd Company Limited Motor oil pump assembly, steering system, and vehicle

Also Published As

Publication number Publication date
JPH10505889A (en) 1998-06-09
US5810565A (en) 1998-09-22
ES2124589T3 (en) 1999-02-01
BR9508971A (en) 1997-11-11
DE4433598A1 (en) 1996-03-28
DE59504439D1 (en) 1999-01-14
EP0782672B1 (en) 1998-12-02
WO1996009475A1 (en) 1996-03-28
KR100344812B1 (en) 2002-11-07
KR970705707A (en) 1997-10-09

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