EP0620898A1 - Compact controllable vane pump. - Google Patents

Compact controllable vane pump.

Info

Publication number
EP0620898A1
EP0620898A1 EP93901592A EP93901592A EP0620898A1 EP 0620898 A1 EP0620898 A1 EP 0620898A1 EP 93901592 A EP93901592 A EP 93901592A EP 93901592 A EP93901592 A EP 93901592A EP 0620898 A1 EP0620898 A1 EP 0620898A1
Authority
EP
European Patent Office
Prior art keywords
adjusting ring
recess
vane pump
pressure
housing
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
EP93901592A
Other languages
German (de)
French (fr)
Other versions
EP0620898B1 (en
Inventor
Bodo Stich
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.)
Daimler Benz AG
Original Assignee
Glyco Metall Werke Glyco BV and Co KG
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 Glyco Metall Werke Glyco BV and Co KG filed Critical Glyco Metall Werke Glyco BV and Co KG
Publication of EP0620898A1 publication Critical patent/EP0620898A1/en
Application granted granted Critical
Publication of EP0620898B1 publication Critical patent/EP0620898B1/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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • the present invention relates to a vane pump with a housing, a sealing ring which is tightly guided in the housing and which can be moved transversely to its axial direction relative to a rotor mounted in the housing and encompassed by the adjusting ring, a suction area of the pump being increased by a volume increasing in the direction of rotation of the rotor between two adjacent vanes, the rotor and the adjusting ring, and a pressure range is defined by a decreasing volume of the vane in the direction of rotation, and at least one actuator is provided which adjusts the position of the adjusting ring as a function of the respective pump parameters
  • the pump parameters that influence the position of the adjusting ring can in particular be the delivery volume of the pump, but above all the pressure occurring on the pressure side.
  • a vane pump is also known from German Offenlegungsschrift No. 40 11 671, which essentially has the features specified above, but the arrangement and position of any actuators is not described. Apart from the special arrangement of actuators and the corresponding design of the adjusting ring, however, the vane pump described in DE 40 11 671 A1 is identical to the vane pump described in the present application, so that with regard to the other design and the advantageous properties associated with that application Reference can be made that goes back to the same inventor
  • the actuators require a considerable amount of space, as shown in particular by the closest prior art according to US Pat. No. 3,218,292 already mentioned.
  • oil pumps are regularly used as auxiliary units for other machines, in particular as lubricant pumps in motors and other machines, the additional space requirement is undesirable and often also has considerable disadvantages. It also increases the weight of the pump, which is also undesirable.
  • the control lines for the actuator or the actuators require additional bores and bushings in the housing so that the pump parameters mentioned can act on the actuators, which in turn change the collar position and thus regulate the pump parameters to a desired value.
  • the present invention has for its object to provide a vane pump with the features mentioned, which has a space-saving and or simple and cost-saving structure.
  • At least one cutout which is open to the outside of the adjusting ring and in the adjusting direction, is provided on the adjusting ring in the vicinity of its pressure region for receiving an actuator.
  • the actuator can be largely integrated into the Steilri ⁇ g itself or the recess provided thereon and requires little or no additional space in the housing outside the collar.
  • a double-walled design of the adjusting ring on the pressure side of the adjusting ring leads to the formation of an additional pressure chamber between the two walls forming the double wall, which lies radially outside the area covered by the rotor vanes (pressure space), radial openings in the wall facing the vane cells connecting the connection the pressure chamber and the pressure chamber.
  • the pressure chamber is thus emptied more easily and quickly, so that even at very high speeds of the rotor no excessively high pressure builds up and above all hard pressure surges are avoided.
  • the adjusting ring is not or only a little larger than without the recess for the actuator due to the additional recess to be provided according to the invention.
  • the inner wall of one Such recess can namely easily project into the pressure chamber, since the pressure chamber does not have to have a uniform cross section over the entire axial length of the adjusting ring in order to fulfill its function.
  • the collar wall can be double-walled to form a recess in the pressure area, the recess being formed between the inner and the outer wall.
  • the outer adjusting ring wall is in turn double-walled again at least in a partial area in order to provide the corresponding recess.
  • two cavities or recesses are provided on opposite sides of the adjusting ring, these cavities being open at least in the direction of adjustment.
  • the direction of adjustment is understood to mean the directions from which the actuator or the steep elements exert a force on the adjusting ring.
  • the two cavities are separated by an intermediate wall.
  • two oppositely acting actuators are provided on such a collar, which react in different ways to the displacement of the collar position and the pump parameters mentioned above. With a suitable selection, a desired state of equilibrium is then established.
  • cutouts or cavities mentioned preferably have a cylindrical cross section, since actuators in their simplest embodiment also often have a cylindrical cross section.
  • An embodiment of the invention is particularly preferred in which the outer wall of the adjusting ring in the pressure region, i.e. either the outer wall of the pressure chamber, or, if present, the outer wall of a pressure chamber additionally present radially outside the pressure chamber is itself double-walled at least in a partial area, the desired recess for receiving the actuator being formed between the two parts forming the double wall.
  • an embodiment of the invention is preferred in which a steep piston can be provided with pressure in one of the recesses.
  • the steep piston in a Correspondingly shaped recess is guided tightly and if, in addition, an opening is provided in the wall inwardly delimiting the recess, which creates a connection to the pressure chamber or to the pressure chamber of the pump. This opening is expediently provided at the inner end of the recess.
  • the counterforce required to have the adjusting ring in an equilibrium position is expediently applied by a compression spring which is received in a recess opposite the first recess and which is supported with its end protruding from the recess on the opposite housing wall.
  • a compression spring which is received in a recess opposite the first recess and which is supported with its end protruding from the recess on the opposite housing wall.
  • An embodiment of the invention is particularly preferred in which the inner wall of the housing is lined with a sheet-metal insert made of spring steel, which offers an essentially wear-free or at least very low-wear contact surface for the ends of the actuating elements which engage with it
  • an embodiment of the invention is preferred in which the adjusting ring is pivotably suspended on its side facing away from the actuators. You then get by with a single pair of eccentrically mounted actuators, which, however, during the pivoting of the adjusting ring necessarily also perform movements perpendicular to the actuating path, so that then in particular the aforementioned configurations with wear-free or low-wear sliding surfaces at the ends of the actuators and their areas of attack from Are advantage.
  • FIG. 1 and 2 show two mutually perpendicular sectional views of a vane pump according to the prior art
  • FIG. 1 denotes a housing, in the interior 14 of which a rotor 1 is arranged with a fixed axis, which rotates on a shaft 1 'and has guide slots 2' for vanes 2 running in the radial and axial direction.
  • the blades are resiliently biased from the center of the rotor 1 and are thus pressed outward in the radial direction.
  • the rotor 1 is surrounded by an essentially cylindrical interior of an adjusting ring 4.
  • the hatched surfaces of the adjusting ring 4 in FIG. 1 lie against the flat surface 16 of the housing 3, as can be seen in FIG.
  • the adjusting ring is essentially mirror-symmetrical, so that, on the opposite side, identical surfaces of the adjusting ring 4 rest on the housing in mirror image.
  • the adjusting ring also has openings 9 and 10 in the radial direction for the inflow or outflow of the conveyed medium.
  • the pumped medium flows through the housing bore 41 into the space 14 surrounding the adjusting ring 4, but in some cases also directly into the area 17 of the suction space 7 covered by the vane cells.
  • the vanes 2 in the vane cells 5 defined between adjacent vanes 2 take delivery medium from the suction chamber 7 and release it in the pressure chamber 8, since in the pressure area the volume of the vane cells 5 between the rotor and the lower one Wall 6 of the collar 4 decreases.
  • the pumped medium exits through openings 10 in the radial direction and into the pressure chamber 11 and from there through the axial opening 12 into the pressure-side bore 40 of the housing 3.
  • the mouth 13 of the bore 40 also in the area of the pressure chamber 8 lie and the wall 6 could rest against the walls 16 of the housing 3 in the pressure region of the adjusting ring, so that the vane cells could be emptied in the axial direction into a correspondingly designed mouth 13 (see FIG.
  • FIG. 1 the adjustment possibility of the adjusting ring 4 is indicated by the double arrow 18. If the adjusting ring 18 in FIG. 1 is shifted more to the left, when the suction chamber 7 or the pressure chamber 8 is swept over, the flight cell volume changes less than in the state shown in FIG. Accordingly, less pumped medium is pumped, so that, assuming a constant demand on the pressure side, the pressure in the pressure area decreases In Figures 1 and 2, however, there are corresponding actuators which move the adjusting ring relative to the rotor 1 and the housing 3 and so on Adjust delivery volume and pressure, not shown. Pistons and springs which act against one another generally serve as actuators, a corresponding piston generally being guided in the housing and being acted upon from the housing side by the pump medium which is branched off from the pressure side, for example from the bore 40.
  • pistons can move the ring in parallel, but the ring can also be suspended pivotably about an axis, as is shown in connection with the configuration of the pump according to the invention in FIGS. 3 and 4.
  • FIGS. 3 to 7 the adjusting ring is pivotably mounted about a shaft 30 received in the upper part of the housing.
  • the actuators 22, 23 are arranged just so that, conversely, as in Figure 1, the delivery volume is reduced when the collar from the left pans to the right, and is enlarged when it is panned from right to left.
  • the mode of operation of the vane pump shown in FIGS. 1 and 2 is identical to the air line pumps shown in FIGS. 3 to 6.
  • the special features of the new airline line pumps lie in the cutouts 20, 21 which are provided in the lower area, ie in the pressure area of the adjusting ring.
  • the adjusting ring 4 is double-walled in the pressure area to form an additional pressure chamber 11.
  • the pressure chamber 11 lies between the inner wall 6 and the outer wall 6 'of the adjusting ring.
  • the outer wall 6 'in turn is now double-walled in its central region. Concretely, one recognizes two cylindrical cavities 20, 21 which are open on opposite sides and separated by an intermediate wall 28, of which the cavity or the recess 20 has a piston 22 guided tightly in this recess receives, while the cavity 21 receives a helical compression spring 23.
  • the two cavities 20, 21 are open in opposite directions, the course of the cavities 20, 21 thus defined from the closed to the open end or vice versa Defined direction of adjustment, which must always run transversely to the axis of the rotor 1, which is no longer shown in FIGS. 3 to 6, and in any case has a radial component with respect to the rotor 1, since the vane volume is defined by the radial distance between the rotor surface and the inner surface of the adjusting ring 4 becomes.
  • the pumped medium flows from the pressure chamber 8 first in the radial direction into the pressure chamber 11 and from there through the axially directed opening 12 of the pressure chamber 11 into the mouth 13 of the housing bore 40.
  • the bulging of the inner wall of the cavities 20, 21 into this pressure chamber 11 only insignificantly hinders the flow of the conveying medium, since the free cross section between the wall 6 and the inner wall of the cutouts 20, 21 can easily be kept larger than the cross section of the bore 40 in the housing 3.
  • an opening 26 can also be seen in the wall of the cutout 20 towards the pressure chamber 11. Through this opening 26, the pumped medium also enters the cavity 20 and thus acts on the piston
  • FIGS. 3 and 5 essentially differ only in the sheet 25 made of spring steel inserted into the housing 3 in FIG. 5 and the cap 27 of the compression spring 23.
  • FIG. 5 shows a state of the pump, in which relatively low pressure, a relatively large amount of pumped medium is pumped; the adjusting ring has an almost maximum deflection to the left and thus a maximum eccentricity with respect to the rotor 1 (not shown), the center of which, however, can be thought, for example, at the intersection of the dash-dotted lines 32, 33.
  • the housing design is much simpler in the embodiments according to the invention than in the prior art, in which piston guides and in particular also bores or lines which feed the pressurized medium to the piston were required.
  • the compression spring also need not be stored in the housing. Instead, the corresponding components are all arranged on the adjusting ring, which anyway and especially in the example of the double-walled design with a pressure chamber 11 requires a certain volume, which is not significantly increased by the additional recesses for the actuators.
  • the housing 3 can thus be made much simpler and more compact overall.
  • the piston expediently has a preferably spherically rounded end face 24 and the compression spring 23 is provided with a cap 27 which is likewise rounded on its outside.
  • the inner surface of the housing 3 in the area where the piston 22 or its end face 24 and the cap 27 of the compression spring 23 engage with the housing inner wall is designed with a sheet 25 made of spring steel.
  • the materials of the cap 27 and the end face 24 of the Pistons 22 are preferably selected so that they slide easily on the spring steel of the plate 25.
  • the spring steel sheet 25 is preferably inserted in one piece in the lower region of the housing 3 and could optionally be clamped with the ends under corresponding projections or a shoulder on the inner wall of the housing 3. This insertion of the spring steel sheet 25 in one piece facilitates the assembly process and lowers the production costs.
  • Figure 6 shows in an axial section through the housing and the collar only one variant in the design of the openings 10 between the pressure chamber and the pressure chamber, which are shown in the example of Figure 6 as two parallel, circumferential slots, with the axial ends of the collar 4 still Sections 6a of the wall 6 of the collar have remained.
  • FIG. 4 only in the central region, both on the pressure side and on the suction side, has a wall section 6 remained, which serves as a guide for the wings 2.
  • FIGS. 4 and 6 Compared to the prior art shown in FIG. 2, the embodiments of FIGS. 4 and 6 only differ in that the suction-side openings 31 in the Housing wall are provided, which lies opposite the housing wall, in which the pressure-side openings 13 are provided.
  • both openings lie on one side of the housing, in particular if, as shown in FIGS. 4 and 6, the housing consists of a cavity which is essentially open on one side and which after the rotor has been installed and collar is only provided with a wall or a lid that closes the open side of the housing
  • the invention also includes embodiments in which the adjusting ring 4 is completely closed along its circumference and only in the axial direction it is possible for the conveying medium to flow into or out of the vane cells formed between the rotor and the adjusting ring.
  • the suction-side opening 31 and the pressure-side opening 13 have to be arranged in the area of the vane cells 5.
  • the recesses 20 and 21 can then be formed by a double-walled design of the lower wall 6 of the adjusting ring 4. Such an embodiment is shown in FIGS. 7 and 8.
  • the cylindrical cavity 20 is connected via an opening 26 to the pressure chamber inside the collar 4 'and a piston 22 is guided tightly in the cavity 20 so that it is pressed out of the cylindrical cavity 20 when the pressure rises, on the Supports the inner wall of the housing 3 and, due to the reaction force, presses the adjusting ring 4 'in the direction of lower eccentricity.
  • a spring 23 is in turn arranged, which applies a corresponding counterforce, so that an equilibrium state is established between the spring force and the pump pressure.
  • either the lower cavities 20, 21 can be molded or cast directly, but the adjusting ring can also be made separately first, whereupon a tube which is closed in the middle is simply welded to the underside of the adjusting ring 4 'after the opening 26 was made, for example, in the form of a bore, in the cross-sectional view according to FIG. 7 it is also not necessary for the adjusting ring 4 'to be guided with its maximum (horizontal) diameter into the region of the cavities 20, 21; The outer surface of the adjusting ring 4 'runs parallel to its inner surface in a circular shape to tightly over a tubular extension which forms the cavities 20, 21 mentioned.
  • the vane cell pump according to the invention is relatively inexpensive and, above all, can be manufactured with low weight and small dimensions.
  • the somewhat more complex design of the adjusting ring is easily compensated for by corresponding savings in the design of the housing, so that overall the advantageous properties of the new airline pumps outweigh them.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • External Artificial Organs (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Une pompe à cellules semi-rotative comprend un boîtier (3), une bague de réglage (4) guidée étanche dans le boîtier (3) et mobile transversalement au sens axial d'un rotor (1) qui est monté dans le boîtier (3) et entouré par la bague de réglage (4). La zone d'aspiration (7, 14) de la pompe est définie par le volume croissant dans le sens de rotation du rotor (1) d'une cellule rotative (5) formée entre deux pales adjacentes (2), le rotor (1) et la bague de réglage, et la zone de refoulement (8, 11) est définie par le volume décroissant dans le sens de rotation de la cellule rotative (5). Au moins un organe de réglage (22, 23) ajuste la position de la bague de réglage (4) en fonction des paramètres respectifs de la pompe. Afin d'obtenir une pompe à cellules semi-rotative ayant une construction compacte et/ou simple et économique, au moins un évidement (20, 21) de réception d'un organe de réglage (22, 23) ouvert vers le côté extérieur de la bague de réglage (4) est ménagé dans la bague de réglage (4) à proximité de la zone de refoulement (8, 11).A semi-rotary cell pump comprises a housing (3), an adjusting ring (4) sealed in the housing (3) and movable transversely in the axial direction of a rotor (1) which is mounted in the housing (3) ) and surrounded by the adjustment ring (4). The suction zone (7, 14) of the pump is defined by the increasing volume in the direction of rotation of the rotor (1) of a rotating cell (5) formed between two adjacent blades (2), the rotor (1 ) and the adjusting ring, and the discharge zone (8, 11) is defined by the volume decreasing in the direction of rotation of the rotary cell (5). At least one adjusting member (22, 23) adjusts the position of the adjusting ring (4) according to the respective parameters of the pump. In order to obtain a semi-rotary cell pump having a compact and / or simple and economical construction, at least one recess (20, 21) for receiving an adjusting member (22, 23) open towards the outer side of the pump. the adjustment ring (4) is provided in the adjustment ring (4) near the discharge zone (8, 11).

Description

Regelbare Flügelzellenpumpe in kompakter Bauweise Adjustable vane pump in a compact design
Die vorliegende Erfindung betrifft eine Flügelzellenpumpe mit einem Gehäuse, einem im Gehäuse dicht geführten Stellring, der relativ zu einem im Gehäuse gelagerten und vom Stellring umfaßten Rotor quer zu dessen Achsrichtung bewegbar ist, wobei ein Saugbereich der Pumpe durch ein in Drehrichtung des Rotors zunehmendes Volumen einer zwischen zwei benachbarten Flügeln, dem Rotor und dem Stellring gebildeten Rügelzelle, und ein Druckbereich durch ein in Drehrichtung abnehmendes Volumen der Flügelzelle definiert ist, und wobei mindestens ein Stellglied vorgesehen ist, welches die Position des Stellringes in Abhängigkeit von den jeweiligen Pumpenparametern einstelltThe present invention relates to a vane pump with a housing, a sealing ring which is tightly guided in the housing and which can be moved transversely to its axial direction relative to a rotor mounted in the housing and encompassed by the adjusting ring, a suction area of the pump being increased by a volume increasing in the direction of rotation of the rotor between two adjacent vanes, the rotor and the adjusting ring, and a pressure range is defined by a decreasing volume of the vane in the direction of rotation, and at least one actuator is provided which adjusts the position of the adjusting ring as a function of the respective pump parameters
Als Pumpenparameter, welche die Position des Stellringes beeinflussen können dabei insbesondere das Fördervolumen der Pumpe, vor allem aber der auf der Druckseite auftretende Druck verwendet werden.The pump parameters that influence the position of the adjusting ring can in particular be the delivery volume of the pump, but above all the pressure occurring on the pressure side.
Eine derartige Flügelzellenpumpe ist aus der US 2,318,292 bekannt.Such a vane pump is known from US 2,318,292.
Aus der deutschen Offenlegungsschrift Nr. 40 11 671 ist ebenfalls eine Flügelzellenpumpe bekannt, welche im wesentlichen die vorstehend angegebenen Merkmale aufweist, wobei jedoch die Anordnung und Lage etwaiger Stellglieder nicht beschrieben ist. Abgesehen von der speziellen Anordnung von Stellgliedern und der entsprechenden Ausgestaltung des Stellringes ist jedoch die in der DE 40 11 671 A1 beschriebene Flügelzellenpumpe mit der in der vorliegenden Anmeldung beschriebenen Flügelzellenpumpe identisch, so daß bezüglich der sonstigen Ausgestaltung und der damit verbundenen vorteilhaften Eigenschaften auf jene Anmeldung Bezug genommen werden kann, die auf denselben Erfinder zurückgehtA vane pump is also known from German Offenlegungsschrift No. 40 11 671, which essentially has the features specified above, but the arrangement and position of any actuators is not described. Apart from the special arrangement of actuators and the corresponding design of the adjusting ring, however, the vane pump described in DE 40 11 671 A1 is identical to the vane pump described in the present application, so that with regard to the other design and the advantageous properties associated with that application Reference can be made that goes back to the same inventor
Die Stellglieder haben einen erheblichen Platzbedarf, wie insbesondere der nächstliegende Stand der Technik gemäß der oben bereits erwähnten US 3,218,292 zeigt Da derartige Flügelzel- lenpumpen regelmäßig als Hilfsaggregate für andere Maschinen Verwendung finden, ins¬ besondere als Schmiermittelpumpen in Motoren und anderen Maschinen, ist der zusätzliche Platzbedarf unerwünscht und oft auch mit erheblichen Nachteilen verbunden. Außerdem nimmt dadurch auch das Gewicht der Pumpe zu, was ebenfalls unerwünscht ist. Schließlich erfordern auch die Steuerleitungen für das Stellglied oder die Stellglieder zusätzliche Bohrungen und Durch¬ führungen im Gehäuse, damit die erwähnten Pumpenparameter auf die Stellglieder wirken können, die ihrerseits die Stellringposition verändern und damit die Pumpenparameter auf einen gewünschten Wert einregeln.The actuators require a considerable amount of space, as shown in particular by the closest prior art according to US Pat. No. 3,218,292 already mentioned. oil pumps are regularly used as auxiliary units for other machines, in particular as lubricant pumps in motors and other machines, the additional space requirement is undesirable and often also has considerable disadvantages. It also increases the weight of the pump, which is also undesirable. Finally, the control lines for the actuator or the actuators require additional bores and bushings in the housing so that the pump parameters mentioned can act on the actuators, which in turn change the collar position and thus regulate the pump parameters to a desired value.
Bei diesem Stand der Technik liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine Flügelzellenpumpe mit den eingangs genannten Merkmalen zu schaffen, welche einen platzsparenden und oder einfachen und kostensparenden Aufbau hat.In this prior art, the present invention has for its object to provide a vane pump with the features mentioned, which has a space-saving and or simple and cost-saving structure.
Diese Aufgabe wird dadurch gelöst, daß am Stellring in der Nähe seines Druckbereiches mindestens eine zur Außenseite des Stellringes und in Stellrichtung offene Aussparung zur Aufnahme eines Stellgliedes vorgesehen ist.This object is achieved in that at least one cutout, which is open to the outside of the adjusting ring and in the adjusting direction, is provided on the adjusting ring in the vicinity of its pressure region for receiving an actuator.
Damit kann das Stellglied weitgehend in den Steilriπg selbst bzw. die daran vorgesehene Aussparung integriert werden und benötigt keinen oder nur wenig zusätzlichen Platz im Gehäuse außerhalb des Stellringes.Thus, the actuator can be largely integrated into the Steilriπg itself or the recess provided thereon and requires little or no additional space in the housing outside the collar.
Eine doppelwandige Ausbildung des Stellringes auf der Druckseite des Stellringes führt zur Ausbildung einer zusätzlichen Druckkammer zwischen den beiden die Doppelwand bildenden Wänden, die radial außerhalb des von den Rotorflügelπ überstrichenen Bereiches (Druckraum) liegt, wobei radiale Öffnungen in der den Flügelzellen zugewandten Wand die Verbindung zwischen dem Druckraum und der Druckkammer herstellen. Der Druckraum wird so leichter und schneller entleert, so daß sich auch bei sehr hohen Drehzahlen des Rotors kein übermäßig hoher Druck aufbaut und vor allem harte Druckstöße vermieden werden.A double-walled design of the adjusting ring on the pressure side of the adjusting ring leads to the formation of an additional pressure chamber between the two walls forming the double wall, which lies radially outside the area covered by the rotor vanes (pressure space), radial openings in the wall facing the vane cells connecting the connection the pressure chamber and the pressure chamber. The pressure chamber is thus emptied more easily and quickly, so that even at very high speeds of the rotor no excessively high pressure builds up and above all hard pressure surges are avoided.
Ein Nachteil dieser Ausgestaltung mit einem doppelwandigen Stellring und einer zusätzlichen Druckkammer auf der Druckseite des Stellringes liegt jedoch im zusätzlichen Platzbedarf des Stellringes, so daß auch das Gehäuse entsprechend größer werden muß.A disadvantage of this configuration with a double-walled collar and an additional pressure chamber on the pressure side of the collar lies in the additional space required by the collar, so that the housing must also be correspondingly larger.
Insbesondere bei der letztgenannten Ausführungsform mit einer zusätzlichen Druckkammer am Stellring wird der Stellring durch die erfindungsgemäß zusätzlich vorzusehende Aussparung nicht oder nur um sehr wenig größer als ohne die Aussparung für das Stellglied. Die Innenwand einer solchen Aussparung kann nämlich ohne weiteres in die Druckkammer hinein vorspringen, da die Druckkammer nicht über die gesamte axiale Länge des Stellringes einen gleichmäßigen Querschnitt haben muß, um ihre Funktion zu erfüllen.Particularly in the case of the last-mentioned embodiment with an additional pressure chamber on the adjusting ring, the adjusting ring is not or only a little larger than without the recess for the actuator due to the additional recess to be provided according to the invention. The inner wall of one Such recess can namely easily project into the pressure chamber, since the pressure chamber does not have to have a uniform cross section over the entire axial length of the adjusting ring in order to fulfill its function.
Die Stellringwand kann zur Ausbildung einer Aussparung im Druckbereich doppelwandig ausgeführt werden, wobei die Aussparung zwischen der inneren und der äußeren Wand gebildet wird. Bei einem Stellring, der unter Bildung einer zusätzlichen Druckkammer im Druckbereich ohnehin schon doppelwandig ausgebildet ist, wird die äußere Stellringwand ihrerseits nochmals zumindest in einem Teilbereich doppelwandig ausgebildet, um die entsprechende Aussparung vorzusehen.The collar wall can be double-walled to form a recess in the pressure area, the recess being formed between the inner and the outer wall. In the case of an adjusting ring, which is already double-walled to form an additional pressure chamber in the pressure area, the outer adjusting ring wall is in turn double-walled again at least in a partial area in order to provide the corresponding recess.
In der bevorzugten Ausführungsform der Erfindung sind zwei Hohlräume bzw. Aussparungen auf gegenüberliegenden Seiten des Stellringes vorgesehen, wobei diese Hohlräume zumindest in Verstellrichtung offen sind. Unter Verstellrichtung werden dabei die Richtungen verstanden, von welchen aus das Stellglied oder die Steilglieder eine Kraft auf den Stellring ausüben. Die beiden Hohlräume sind durch eine dazwischenliegende Wand getrennt.In the preferred embodiment of the invention, two cavities or recesses are provided on opposite sides of the adjusting ring, these cavities being open at least in the direction of adjustment. The direction of adjustment is understood to mean the directions from which the actuator or the steep elements exert a force on the adjusting ring. The two cavities are separated by an intermediate wall.
Im allgemeinen sind an einem solchen Stellring zwei gegensätzlich wirkende Stellglieder vorgesehen, die in unterschiedlicher Weise auf die Verschiebung der Stellringpositioπ und die oben angesprochenen Pumpenparameter reagieren. Bei geeigneter Auswahl stellt sich dann ein gewünschter Gleichgewichtszustand ein.In general, two oppositely acting actuators are provided on such a collar, which react in different ways to the displacement of the collar position and the pump parameters mentioned above. With a suitable selection, a desired state of equilibrium is then established.
Weiterhin haben die erwähnten Aussparungen bzw. Hohlräume vorzugsweise zylindrischen Querschnitt, da auch Stellglieder in ihrer einfachsten Ausführungsform oftmals zylindrischen Querschnitt haben.Furthermore, the cutouts or cavities mentioned preferably have a cylindrical cross section, since actuators in their simplest embodiment also often have a cylindrical cross section.
Besonders bevorzugt ist eine Ausführungsform der Erfindung, bei welcher die Außenwand des Stellringes im Druckbereich, d.h. entweder die Außenwand des Druckraumes, oder, falls vorhanden, die Außenwand einer zusätzlich radial außerhalb des Druckraumes vorhandenen Druckkammer ihrerseits zumindest in einem Teilbereich doppelwandig ausgebildet ist, wobei zwischen den beiden die Doppelwand bildenden Teilen die gewünschte Aussparung zur Aufnahme des Stellgliedes entsteht.An embodiment of the invention is particularly preferred in which the outer wall of the adjusting ring in the pressure region, i.e. either the outer wall of the pressure chamber, or, if present, the outer wall of a pressure chamber additionally present radially outside the pressure chamber is itself double-walled at least in a partial area, the desired recess for receiving the actuator being formed between the two parts forming the double wall.
Weiterhin ist eine Ausführungsform der Erfindung bevorzugt, bei welcher in einer der Aus¬ sparungen ein mit Druck beaufschlagbarer Steilkolben vorgesehen ist. Bei einer solchen Ausführungsform hat es sich als besonders zweckmäßig erwiesen, wenn der Steilkolben in einer entsprechend geformten Aussparung dicht geführt wird und wenn außerdem in der die Aussparung nach innen begrenzenden Wand eine Öffnung vorgesehen ist, welche eine Verbindung zur Druckkammer bzw. zum Druckraum der Pumpe herstellt Diese Öffnung ist zweckmäßigerweise an dem inneren Ende der Aussparung vorgesehen. Bei Druckbeaufschlagung wird der Kolben dann aus der Aussparung herausgetrieben und stützt sich mit seinem aus der Aussparung herausragenden Ende beispielsweise an der Innenwand des Pumpengehäuses ab. Durch das Druckmedium wird dabei eine entsprechende Reaktionskraft auf die dem Kolben abgewandte Stirnwand der Aussparung ausgeübt, wodurch der Stellring von der Wand des Gehäuses wegbewegt wird, an welcher der Kolben angreift.Furthermore, an embodiment of the invention is preferred in which a steep piston can be provided with pressure in one of the recesses. In such an embodiment, it has proven to be particularly useful if the steep piston in a Correspondingly shaped recess is guided tightly and if, in addition, an opening is provided in the wall inwardly delimiting the recess, which creates a connection to the pressure chamber or to the pressure chamber of the pump. This opening is expediently provided at the inner end of the recess. When pressure is applied, the piston is then driven out of the recess and, with its end protruding from the recess, is supported, for example, on the inner wall of the pump housing. A corresponding reaction force is exerted by the pressure medium on the end wall of the recess facing away from the piston, as a result of which the adjusting ring is moved away from the wall of the housing on which the piston engages.
Die dabei erforderliche Gegenkraft, um den Stellring in einer Gleichgewichtsposition zu hatten, wird zweckmäßigerweise durch eine Druckfeder aufgebracht, die in einer der ersten Aussparung gegenüberliegenden Aussparung aufgenommen ist und die sich mit ihrem aus der Aussparung herausragenden Ende an der gegenüberliegenden Gehäusewand abstützt. Bei einer derartigen Ausgestaltung der Vorrichtung ist es vorteilhaft, wenn das aus der erstgenannten Aussparung herausragende Ende des Kolbens mit einer abgerundeten Stirnfläche ausgebildet ist und wenn beispielsweise die als Spiralfeder ausgebildete Druckfeder an ihrem aus der Aussparung herausragenden Ende eine Kappe aufweist, die eine entsprechend runde und gleitfähige Oberfläche hat Während der Bewegung des Stellringes können diese an den Wänden angreifenden Flächen von Kolben und Druckfedern leichter gleiten, ohne Verschleißspuren zu hinterlassen.The counterforce required to have the adjusting ring in an equilibrium position is expediently applied by a compression spring which is received in a recess opposite the first recess and which is supported with its end protruding from the recess on the opposite housing wall. In such a configuration of the device, it is advantageous if the end of the piston projecting from the first-mentioned recess is formed with a rounded end face and if, for example, the compression spring designed as a spiral spring has a cap on its end protruding from the recess which has a correspondingly round and has a slippery surface During the movement of the adjusting ring, the surfaces of the pistons and compression springs that engage the walls can slide more easily without leaving any traces of wear.
Besonders bevorzugt ist dabei eine Ausführungsform der Erfindung, bei weicher die Innenwand des Gehäuses mit einer Blecheinlage aus Federstahl ausgekleidet ist, die für die damit in Eingriff tretenden Enden der Stellglieder eine im wesentlichen verschleißfreie oder zumindest sehr verschleißarme Angriffsfläche bietetAn embodiment of the invention is particularly preferred in which the inner wall of the housing is lined with a sheet-metal insert made of spring steel, which offers an essentially wear-free or at least very low-wear contact surface for the ends of the actuating elements which engage with it
Schließlich ist eine Ausführungsform der Erfindung bevorzugt, bei weicher der Stellring an seiner den Stellgliedern abgewandten Seite schwenkbar aufgehängt ist. Man kommt dann mit einem einzigen Paar von exzentrisch angebrachten Stellgliedern aus, die allerdings während des Verschwenkens des Stellringes notwendigerweise auch Bewegungen senkrecht zum Stellweg ausführen, so daß dann insbesondere die zuvor erwähnten Ausgestaltungen mit verschleißfreien oder verschleißarmen Gleitfiächen an den Enden der Stellglieder und ihren Angriffsbereichen von Vorteil sind.Finally, an embodiment of the invention is preferred in which the adjusting ring is pivotably suspended on its side facing away from the actuators. You then get by with a single pair of eccentrically mounted actuators, which, however, during the pivoting of the adjusting ring necessarily also perform movements perpendicular to the actuating path, so that then in particular the aforementioned configurations with wear-free or low-wear sliding surfaces at the ends of the actuators and their areas of attack from Are advantage.
Weitere Vorteile, Merkmale und Anwendungsmögüchkeiten der vorliegenden Erfindung werden deutlich anhand der folgenden Beschreibung und der zugehörigen Figuren. Es zeigen:Further advantages, features and application possibilities of the present invention will be clear from the following description and the associated figures. Show it:
Figuren 1 und 2 zwei zueinander senkrechte Schnittansichten einer Flügelzel¬ lenpumpe nach dem Stand der Technik,1 and 2 show two mutually perpendicular sectional views of a vane pump according to the prior art,
Figuren 3 und 4 den Figuren 1 und 2 entsprechende Schnitte einer bevorzugtenFigures 3 and 4 sections of a preferred one corresponding to Figures 1 and 2
Ausführungsform der erfindungsgemäßen Flügelzellenpumpe,Embodiment of the vane pump according to the invention,
Figuren 5 und 6 zusätzliche Merkmale und Abweichungen zu den in den FigurenFigures 5 and 6 additional features and deviations from those in the figures
3 und 4 dargestellten Ausführungsformen in entsprechenden Schnittansichten und3 and 4 illustrated embodiments in corresponding sectional views and
Figuren 7 und 8 Schnittansichten durch eine weitere Ausführungsform ohne radialeFigures 7 and 8 sectional views through a further embodiment without radial
Druckkammer.Pressure chamber.
Die wesentlichen Funktionen der Pumpe werden kurz anhand des Standes der Technik gemäß den Figuren 1 und 2 beschrieben. Mit 3 ist ein Gehäuse bezeichnet, in dessen Innenraum 14 mit einer ortsfesten Achse ein Rotor 1 angeordnet ist, der auf einer Welle 1 ' umläuft und in radialer und axialer Richtung verlaufende Führungsschlitze 2' für Flügel 2 hat. Die Flügel sind vom Zentrum des Rotors 1 her federnd vorgespannt und werden so in radialer Richtung nach außen gedrückt. Den Rotor 1 umgibt im Abstand ein im wesentlichen zylindrischer Innenraum eines Stellringes 4. Die schraffierten Flächen des Stellringes 4 in Figur 1 liegen an der planen Fläche 16 des Gehäuses 3 an, wie man in Figur 2 erkennen kann. Der Stellring ist im wesentlichen spiegelsymmetrisch ausgebildet, so daß auf der gegenüberliegenden Seite spiegelbildlich gleiche Flächen des Stellringes 4 am Gehäuse anliegen. Wie man jedoch in Figur 2 außerdem erkennt, weist der Stellring auch in radialer Richtung Öffnungen 9 und 10 für das Ein- bzw. Ausströmen des Fördermediums auf. Das Fördermedium strömt über die Gehäusebohrung 41 in den den Stellring 4 umgebenden Raum 14, teilweise jedoch auch direkt in den von den Flügelzellen überstrichenen Bereich 17 des Saugraumes 7 ein.The essential functions of the pump are briefly described with reference to the prior art according to Figures 1 and 2. 3 denotes a housing, in the interior 14 of which a rotor 1 is arranged with a fixed axis, which rotates on a shaft 1 'and has guide slots 2' for vanes 2 running in the radial and axial direction. The blades are resiliently biased from the center of the rotor 1 and are thus pressed outward in the radial direction. At a distance, the rotor 1 is surrounded by an essentially cylindrical interior of an adjusting ring 4. The hatched surfaces of the adjusting ring 4 in FIG. 1 lie against the flat surface 16 of the housing 3, as can be seen in FIG. The adjusting ring is essentially mirror-symmetrical, so that, on the opposite side, identical surfaces of the adjusting ring 4 rest on the housing in mirror image. However, as can also be seen in FIG. 2, the adjusting ring also has openings 9 and 10 in the radial direction for the inflow or outflow of the conveyed medium. The pumped medium flows through the housing bore 41 into the space 14 surrounding the adjusting ring 4, but in some cases also directly into the area 17 of the suction space 7 covered by the vane cells.
Wie man aus Figur 1 leicht erkennt, nehmen die Flügel 2 in den zwischen benachbarten Flügeln 2 definierten Flügelzellen 5 Fördermedium aus dem Saugraum 7 mit und geben es im Druckraum 8 wieder ab, da im Druckbereich das Volumen der Flügelzellen 5 zwischen dem Rotor und der unteren Wand 6 des Stellringes 4 abnimmt. Das Fördermedium tritt durch Öffnungen 10 in radialer Richtung aus und in die Druckkammer 11 ein und von dort durch die axiale Öffnung 12 in die druckseitige Bohrung 40 des Gehäuses 3. Es versteht sich, daß die Mündung 13 der Bohrung 40 auch im Bereich des Druckraumes 8 liegen und die Wand 6 im Druckbereich des Stellringes an den Wänden 16 des Gehäuses 3 anliegen könnte, so daß die Flügelzellen in axialer Richtung in eine entsprechend gestaltete Mündung 13 entleert werden könnten (siehe Figur 7). ln Figur 1 ist durch den Doppelpfeil 18 die Verstellmögiichkeit des Stellringes 4 angedeutet. Wird der Stellring 18 in Figur 1 mehr nach links verschoben, so ändert sich beim Überstreichen des Saugraumes 7 oder auch des Druckraumes 8 das Flügefzellenvolumen weniger als in dem in Figur 1 dargestellten Zustand. Dementsprechend wird weniger Fördermedium gepumpt, so daß, ein konstanter Bedarf auf der Druckseite vorausgesetzt, der Druck im Druckbereich abnimmt In den Figuren 1 und 2 sind jedoch entsprechende Stellglieder, weiche eine Verschiebung des Stellringes relativ zum Rotor 1 und zum Gehäuse 3 vornehmen und so das Fördervolumen und den Druck regulieren, nicht dargestellt. Im allgemeinen dienen als Stellglieder gegenein- anderwirkende Kolben und Federn, wobei ein entsprechender Kolben im allgemeinen im Gehäuse geführt wird und von der Gehäuseseite her mit dem Pumpmedium beaufschlagt wird, welches von der Druckseite, z.B. von der Bohrung 40 her, abgezweigt wird.As can easily be seen from FIG. 1, the vanes 2 in the vane cells 5 defined between adjacent vanes 2 take delivery medium from the suction chamber 7 and release it in the pressure chamber 8, since in the pressure area the volume of the vane cells 5 between the rotor and the lower one Wall 6 of the collar 4 decreases. The pumped medium exits through openings 10 in the radial direction and into the pressure chamber 11 and from there through the axial opening 12 into the pressure-side bore 40 of the housing 3. It goes without saying that the mouth 13 of the bore 40 also in the area of the pressure chamber 8 lie and the wall 6 could rest against the walls 16 of the housing 3 in the pressure region of the adjusting ring, so that the vane cells could be emptied in the axial direction into a correspondingly designed mouth 13 (see FIG. 7). In FIG. 1, the adjustment possibility of the adjusting ring 4 is indicated by the double arrow 18. If the adjusting ring 18 in FIG. 1 is shifted more to the left, when the suction chamber 7 or the pressure chamber 8 is swept over, the flight cell volume changes less than in the state shown in FIG. Accordingly, less pumped medium is pumped, so that, assuming a constant demand on the pressure side, the pressure in the pressure area decreases In Figures 1 and 2, however, there are corresponding actuators which move the adjusting ring relative to the rotor 1 and the housing 3 and so on Adjust delivery volume and pressure, not shown. Pistons and springs which act against one another generally serve as actuators, a corresponding piston generally being guided in the housing and being acted upon from the housing side by the pump medium which is branched off from the pressure side, for example from the bore 40.
Dabei können mehrere Kolben parallel den Ring verschieben, der Ring kann jedoch auch um eine Achse schwenkbar aufgehängt sein, wie dies im Zusammenhang mit der erfindungsgemäßen Ausgestaltung der Pumpe in den Figuren 3 und 4 dargestellt ist.Several pistons can move the ring in parallel, but the ring can also be suspended pivotably about an axis, as is shown in connection with the configuration of the pump according to the invention in FIGS. 3 and 4.
Man erkennt in den Figuren 3 bis 7, daß der Stellring um eine im oberen Teil des Gehäuses aufgenommene Welle 30 schwenkbar gelagert ist. Im Unterschied zu der Darstellung in Figur 1 , welche zwar nicht die Stellglieder, jedoch die Verstellmögiichkeit des Stellringes 4 zeigt, sind jedoch die Stellglieder 22, 23. gerade so angeordnet daß umgekehrt wie bei Figur 1 das Fördervolumen verringert wird, wenn der Stellring von links nach rechts schwenkt, und vergrößert wird, wenn er von rechts nach links verschwenkt wird. Im Prinzip ist jedoch die Funktionsweise der in den Figuren 1 und 2 dargestellten Flügelzellenpumpe mit den in den Figuren 3 bis 6 dargestellten Flügeizelienpumpen identisch.It can be seen in FIGS. 3 to 7 that the adjusting ring is pivotably mounted about a shaft 30 received in the upper part of the housing. In contrast to the illustration in Figure 1, which shows not the actuators, but the Verstellmögiichkeit of the collar 4, the actuators 22, 23 are arranged just so that, conversely, as in Figure 1, the delivery volume is reduced when the collar from the left pans to the right, and is enlarged when it is panned from right to left. In principle, however, the mode of operation of the vane pump shown in FIGS. 1 and 2 is identical to the air line pumps shown in FIGS. 3 to 6.
Die Besonderheiten der neuen Flügeizelienpumpen liegt in den Aussparungen 20, 21 , die im unteren Bereich, d.h. im Druckbereich des Stellringes, vorgesehen sind. Bei allen dargestellten Ausführungsformen der Figuren 3 bis 6 ist der Stellring 4 im Druckbereich unter Bildung einer zusätzlichen Druckkammer 11 doppelwandig ausgebildet. Die Druckkammer 11 liegt zwischen der Innenwand 6 und der Außenwand 6' des Stellringes. Die Außenwand 6' ist nun ihrerseits in ihrem mittleren Bereich doppelwandig ausgebildet Konkreterkennt man zwei nach gegenüberliegenden Seiten hin offene und durch eine Zwischenwand 28 getrennte zylindrische Hohlräume 20, 21 , von denen der Hohlraum bzw. die Aussparung 20 einen dicht in dieser Aussparung geführten Kolben 22 aufnimmt, während der Hohlraum 21 eine schraubenförmige Druckfeder 23 aufnimmt. Die beiden Hohlräume 20, 21 sind in entgegengesetzten Richtungen offen, wobei der so definierte Verlauf der Hohlräume 20, 21 vom geschlossenen zum offenen Ende oder umgekehrt die Versteilrichtung definiert, die immer quer zur Achse des in den Figuren 3 bis 6 nicht mehr dargestellten Rotors 1 verlaufen muß und auf jeden Falle eine radiale Komponente bezüglich des Rotors 1 hat, da das Flügelzellenvolumen durch den radialen Abstand zwischen Rotoroberfläche und Innenfläche des Stellringes 4 definiert wird.The special features of the new airline line pumps lie in the cutouts 20, 21 which are provided in the lower area, ie in the pressure area of the adjusting ring. In all of the illustrated embodiments of FIGS. 3 to 6, the adjusting ring 4 is double-walled in the pressure area to form an additional pressure chamber 11. The pressure chamber 11 lies between the inner wall 6 and the outer wall 6 'of the adjusting ring. The outer wall 6 'in turn is now double-walled in its central region. Concretely, one recognizes two cylindrical cavities 20, 21 which are open on opposite sides and separated by an intermediate wall 28, of which the cavity or the recess 20 has a piston 22 guided tightly in this recess receives, while the cavity 21 receives a helical compression spring 23. The two cavities 20, 21 are open in opposite directions, the course of the cavities 20, 21 thus defined from the closed to the open end or vice versa Defined direction of adjustment, which must always run transversely to the axis of the rotor 1, which is no longer shown in FIGS. 3 to 6, and in any case has a radial component with respect to the rotor 1, since the vane volume is defined by the radial distance between the rotor surface and the inner surface of the adjusting ring 4 becomes.
Beim Pumpen strömt das Fördermedium aus dem Druckraum 8 zunächst in radialer Richtung in die Druckkammer 11 und von dort durch die axial gerichtete Öffnung 12 der Druckkammer 11 in die Mündung 13 der Gehäusebohrung 40 hinein. Die Vorwölbung der innen gelegenen Wand der Hohlräume 20, 21 in diesen Druckraum 11 hinein behindert dabei die Strömung des Vördermedi- ums nur unwesentlich, da der freie Querschnitt zwischen der Wand 6 und der Innenwand der Aussparungen 20, 21 ohne weiteres größer gehalten werden kann als der Querschnitt der Bohrung 40 im Gehäuse 3.When pumping, the pumped medium flows from the pressure chamber 8 first in the radial direction into the pressure chamber 11 and from there through the axially directed opening 12 of the pressure chamber 11 into the mouth 13 of the housing bore 40. The bulging of the inner wall of the cavities 20, 21 into this pressure chamber 11 only insignificantly hinders the flow of the conveying medium, since the free cross section between the wall 6 and the inner wall of the cutouts 20, 21 can easily be kept larger than the cross section of the bore 40 in the housing 3.
In den dargestellten bevorzugten Ausführungsformen der Figuren 3 bis 6 erkennt man außerdem eine Öffnung 26 in der Wand der Aussparung 20 zur Druckkammer 11 hin. Durch diese Öffnung 26 gelangt das Fördermedium auch in den Hohlraum 20 hinein und beaufschlagt so den KolbenIn the preferred embodiments shown in FIGS. 3 to 6, an opening 26 can also be seen in the wall of the cutout 20 towards the pressure chamber 11. Through this opening 26, the pumped medium also enters the cavity 20 and thus acts on the piston
22 von innen her mit Druck. Die in den Figuren 3 und 5 dargestellten Ausführungsformen unter¬ scheiden sich im wesentlichen nur durch das in Figur 5 in das Gehäuse 3 eingelegte Blech 25 aus Federstahl und die Kappe 27 der Druckfeder 23. Ansonsten zeigt Figur 5 einen Zustand der Pumpe, bei welchem bei relativ geringem Druck relativ viel Fördermedium gepumpt wird; der Stellring hat eine nahezu maximale Auslenkung nach links und damit eine maximale Exzentrizität gegenüber dem nicht dargestellten Rotor 1 , dessen Zentrum jedoch beispielsweise im Schnittpunkt der strichpunktierten Linien 32, 33 gedacht werden kann. Ist nun beispielsweise der Bedarf an Fördermedium auf der Druckseite geringer, so wird bei dem gegebenen Pumpvolumen der Druck zunehmen, was dazu führt, daß von dem mit Druck beaufschlagten Kolben 22 eine stärkere Reaktionskraft auf die der Stirnseite 24 des Kolbens abgewandte innere Wand der Aussparung 20 ausgeübt wird. Dadurch wird der Stellring 4 mehr in Richtung der in Figur 3 dargestellten Position verschwenkt, bis die durch die dabei weiter zusammengedrückte Druckfeder22 from the inside with pressure. The embodiments shown in FIGS. 3 and 5 essentially differ only in the sheet 25 made of spring steel inserted into the housing 3 in FIG. 5 and the cap 27 of the compression spring 23. Otherwise, FIG. 5 shows a state of the pump, in which relatively low pressure, a relatively large amount of pumped medium is pumped; the adjusting ring has an almost maximum deflection to the left and thus a maximum eccentricity with respect to the rotor 1 (not shown), the center of which, however, can be thought, for example, at the intersection of the dash-dotted lines 32, 33. If, for example, the requirement for pumped medium on the pressure side is lower, the pressure will increase at the given pump volume, which leads to a greater reaction force from the piston 22 pressurized to the inner wall of the recess 20 facing away from the end face 24 of the piston is exercised. As a result, the adjusting ring 4 is pivoted more in the direction of the position shown in FIG. 3 until the compression spring is compressed further
23 ausgeübte Gegenkraft die von dem Kolben aufgrund des höheren Druckes ausgeübte Kraft gerade wieder kompensiert. Das Fördervolumen nimmt dabei ab, so daß auch der Druck ent¬ sprechend sinkt. Im Ergebnis steif sich ein Gleichgewichtszustand zwischen den beiden extremen Positionen ein, die in den Figuren 3 und 5 dargestellt sind, wobei in Figur 3 der Rotor als zentriert im Stellring 4 gedacht ist (Pumpleistung Null) und in Figur 5 die Position maximaler Exzentrizität erreicht ist (Pumpleistung maximal).23 counterforce exerted compensates for the force exerted by the piston due to the higher pressure. The delivery volume decreases, so that the pressure also drops accordingly. As a result, a state of equilibrium stiffens between the two extreme positions, which are shown in FIGS. 3 and 5, the rotor in FIG. 3 being intended to be centered in the adjusting ring 4 (pump power zero) and the position of maximum eccentricity in FIG. 5 (Maximum pumping power).
Die Gehäusegestaltung ist bei den erfindungsgemäßen Ausführungsformen wesentlich einfacher als beim Stand der Technik, bei welchem Kolbenführuπgen und insbesondere auch Bohrungen oder Leitungen, die dem Kolben das unter Druck stehende Medium zuführen, erforderlich waren.The housing design is much simpler in the embodiments according to the invention than in the prior art, in which piston guides and in particular also bores or lines which feed the pressurized medium to the piston were required.
Auch die Druckfeder braucht nicht im Gehäuse gelagert zu sein. Stattdessen sind die entsprechenden Komponenten alle an dem Stellring angeordnet, der ohnehin und vor allem im Beispiel der doppelwandigen Ausführung mit einer Druckkammer 11 ein bestimmtes Volumen beansprucht, welches durch die zusätzlichen Aufnahmeaussparungen für die Stellglieder nicht nennenswert vergrößert wird.The compression spring also need not be stored in the housing. Instead, the corresponding components are all arranged on the adjusting ring, which anyway and especially in the example of the double-walled design with a pressure chamber 11 requires a certain volume, which is not significantly increased by the additional recesses for the actuators.
Das Gehäuse 3 kann damit insgesamt wesentlich einfacher und kompakter gestaltet werden.The housing 3 can thus be made much simpler and more compact overall.
Wie man beim Vergleich der beiden Figuren 3 und 5 erkennt, müssen die aus den Aussparungen 20 bzw. 21 herausragenden Enden des Kolbens 22 bzw. der Druckfeder 23 auch auf den ihnen zugewandten Innenflächen des Gehäuses 3 gleiten. Zweckmäßigerweise hat dazu der Kolben eine vorzugsweise kugelförmig abgerundete Stirnfläche 24 und die Druckfeder 23 ist mit einer an ihrer Außenseite ebenfalls abgerundeten Kappe 27 versehen. Weiterhin ist die Innenfläche des Gehäuses 3 in dem Bereich, wo Kolben 22 bzw. dessen Stirnfläche 24 und die Kappe 27 der Druckfeder 23 mit der Gehäuseinnenwand in Eingriff treten, mit einem Blech 25 aus Federstahl ausgelegt Die Materialien von Kappe 27 und der Stirnfläche 24 des Kolbens 22 werden vorzugsweise so ausgewählt, daß sie leicht auf dem Federstahl des Bleches 25 gleiten. Das Federstahlblech 25 wird vorzugsweise einstückig in den unteren Bereich des Gehäuses 3 eingelegt und könnte gegebenenfalls mit den Enden unter entsprechenden Vorsprüngen oder einer Schulter an der Innenwand des Gehäuses 3 festgeklemmt werden. Dieses Einlegen des Federstahlbleches 25 in einem Stück erleichtert den Moπtagevorgang und senkt die Produktions¬ kosten.As can be seen when comparing the two FIGS. 3 and 5, the ends of the piston 22 and the compression spring 23 protruding from the cutouts 20 and 21 must also slide on the inner surfaces of the housing 3 facing them. For this purpose, the piston expediently has a preferably spherically rounded end face 24 and the compression spring 23 is provided with a cap 27 which is likewise rounded on its outside. Furthermore, the inner surface of the housing 3 in the area where the piston 22 or its end face 24 and the cap 27 of the compression spring 23 engage with the housing inner wall is designed with a sheet 25 made of spring steel. The materials of the cap 27 and the end face 24 of the Pistons 22 are preferably selected so that they slide easily on the spring steel of the plate 25. The spring steel sheet 25 is preferably inserted in one piece in the lower region of the housing 3 and could optionally be clamped with the ends under corresponding projections or a shoulder on the inner wall of the housing 3. This insertion of the spring steel sheet 25 in one piece facilitates the assembly process and lowers the production costs.
Figur 6 zeigt in einem Axialschnitt durch Gehäuse und Stellring lediglich eine Variante in der Gestaltung der Öffnungen 10 zwischen Druckraum und Druckkammer, die im Beispiel der Figur 6 als zwei parallele, in Umfangsrichtung verlaufende Schlitze dargestellt sind, wobei an den axialen Enden des Stellringes 4 noch Abschnitte 6a der Wand 6 des Stellringes stehen geblieben sind. Dagegen ist in der Ausführungsform der Figur 4 lediglich im mittleren Bereich sowohl druckseitig als auch saugseitig ein Wandabschnitt 6 stehengeblieben, der als Führung für die Flügel 2 dient.Figure 6 shows in an axial section through the housing and the collar only one variant in the design of the openings 10 between the pressure chamber and the pressure chamber, which are shown in the example of Figure 6 as two parallel, circumferential slots, with the axial ends of the collar 4 still Sections 6a of the wall 6 of the collar have remained. In contrast, in the embodiment of FIG. 4, only in the central region, both on the pressure side and on the suction side, has a wall section 6 remained, which serves as a guide for the wings 2.
Gegenüber dem in Figur 2 dargestellten Stand der Technik unterscheiden sich die Ausführungs- formen der Figuren 4 und 6 lediglich noch dadurch, daß die saugseitigen Öffnungen 31 in der Gehäusewand vorgesehen sind, die der Gehäusewand gegenüberliegt, in welcher die druckseitigen Öffnungen 13 vorgesehen sind.Compared to the prior art shown in FIG. 2, the embodiments of FIGS. 4 and 6 only differ in that the suction-side openings 31 in the Housing wall are provided, which lies opposite the housing wall, in which the pressure-side openings 13 are provided.
Auch dies ist jedoch kein notwendiges Merkmal der Erfindung. Es kann im Gegenteil zweckmäßi¬ ger sein, wenn beide Öffnungen auf einer Seite des Gehäuses liegen, insbesondere wenn, wie in den Figuren 4 und 6 dargestellt, das Gehäuse aus einem im wesentlichen auf einer Seite offenen Hohlraum besteht, der nach der Montage von Rotor und Stellring lediglich noch mit einer Wand bzw. einem Deckel versehen wird, der die offene Seite des Gehäuses abschließtHowever, this is also not a necessary feature of the invention. On the contrary, it can be expedient if both openings lie on one side of the housing, in particular if, as shown in FIGS. 4 and 6, the housing consists of a cavity which is essentially open on one side and which after the rotor has been installed and collar is only provided with a wall or a lid that closes the open side of the housing
Die Erfindung schließt jedoch auch Ausführungsformen ein, bei welchen der Stellring 4 entlang seines Umfanges vollständig geschlossen ist und lediglich in Axialrichtung ein Einströmen bzw. Ausströmen des Fördermediums in die zwischen Rotor und Stellring gebildeten Flügelzellen bzw. aus diesen heraus möglich ist. Hierzu müssen lediglich die saugseitige Öffnung 31 und die druckseitige Öffnung 13 im Bereich der Flügelzellen 5 angeordnet werden. Die Aussparungen 20 bzw. 21 können dann durch eine doppelwandige Gestaltung der unteren Wand 6 des Stellringes 4 gebildet werden. Eine solche Ausführungsforrp ist in den Figuren 7 und 8 dargestellt.However, the invention also includes embodiments in which the adjusting ring 4 is completely closed along its circumference and only in the axial direction it is possible for the conveying medium to flow into or out of the vane cells formed between the rotor and the adjusting ring. For this purpose, only the suction-side opening 31 and the pressure-side opening 13 have to be arranged in the area of the vane cells 5. The recesses 20 and 21 can then be formed by a double-walled design of the lower wall 6 of the adjusting ring 4. Such an embodiment is shown in FIGS. 7 and 8.
Man erkennt in den Figuren 7 und 8 eine Flügelzellenpumpe mit einem einfacheren Stellring 4', der keine radial außerhalb des Druckraumes 8 liegende Druckkammer aufweist, so die Innenwand 6 mitder Außenwand 6' der vorher beschriebenen Ausführungsformen zusammenfällt Dennoch sind an der Unterseite des Stellringes 4* zwei im wesentlichen miteinander fluchtende zylindrische Hohlräume 20 und 21 vorgesehen, die sich in etwa tangential entlang der Außenseite des Stellringes 4' an dessen der Aufhängung gegenüberliegendem Ende erstrecken. Dabei ist der zylindrische Hohlraum 20 über einen Durchbruch 26 mit dem Druckraum im Inneren des Stellringes 4' verbunden und ein Kolben 22 ist dicht in dem Hohlraum 20 geführt, so daß er bei Ansteigen des Druckes aus dem zylindrischen Hohlraum 20 herausgedrückt wird, sich an der Innenwand des Gehäuses 3 abstützt und aufgrund der Reaktionskraft den Stellring 4' in Richtung geringerer Exzentrizität drückt Im gegenüberliegenden Hohlraum 21 ist wiederum eine Feder 23 angeordnet, welche eine entsprechende Gegenkraft aufbringt, so daß sich zwischen Federkraft und dem Pumpdruck ein Gleichgewichtszustand einstellt. Bei der Herstellung einer solchen Pumpe können entweder die unteren Hohlräume 20, 21 unmittelbar angeformt bzw. mitgegossen werden, der Stellring kann jedoch auch zunächst separat hergestellt werden, woraufhin einfach ein in der Mitte verschlossenes Rohr an die Unterseite des Stellringes 4' angeschweißt wird, nachdem der Durchbruch 26 z.B. in Form einer Bohrung angebracht wurde, im Querschnittbild gemäß Figur 7 ist es auch nicht erforderlich, daß der Stellring 4' mit seinem maximalen (horizontalen) Durchmesser bis in den Bereich der Hohlräume 20, 21 geführt wird, vielmehr kann die Außenfläche des Stellringes 4' parallel zu seiner Innenfläche kreisförmig bis dicht über einen rohrförmigen Ansatz verlaufen, der die erwähnten Hohlräume 20, 21 bildet.It can be seen in Figures 7 and 8, a vane pump with a simpler collar 4 'which has no radially located outside of the pressure chamber 8 the pressure chamber, the inner wall 6 mitder outer wall 6' of the previously described embodiments coincides Nevertheless, at the bottom of the adjusting ring 4 * two substantially aligned cylindrical cavities 20 and 21 are provided, which extend approximately tangentially along the outside of the adjusting ring 4 'at its end opposite the suspension. The cylindrical cavity 20 is connected via an opening 26 to the pressure chamber inside the collar 4 'and a piston 22 is guided tightly in the cavity 20 so that it is pressed out of the cylindrical cavity 20 when the pressure rises, on the Supports the inner wall of the housing 3 and, due to the reaction force, presses the adjusting ring 4 'in the direction of lower eccentricity. In the opposite cavity 21, a spring 23 is in turn arranged, which applies a corresponding counterforce, so that an equilibrium state is established between the spring force and the pump pressure. In the manufacture of such a pump, either the lower cavities 20, 21 can be molded or cast directly, but the adjusting ring can also be made separately first, whereupon a tube which is closed in the middle is simply welded to the underside of the adjusting ring 4 'after the opening 26 was made, for example, in the form of a bore, in the cross-sectional view according to FIG. 7 it is also not necessary for the adjusting ring 4 'to be guided with its maximum (horizontal) diameter into the region of the cavities 20, 21; The outer surface of the adjusting ring 4 'runs parallel to its inner surface in a circular shape to tightly over a tubular extension which forms the cavities 20, 21 mentioned.
Die erfinduπgsgemäße Flügelzellenpumpe ist relativ kostengünstig und vor allem mit geringem Gewicht und geringen Abmessungen herstellbar. Die etwas aufwendigere Gestaltung des Stellringes wird ohne weiteres wettgemacht durch entsprechende Einsparungen in der Gestaltung des Gehäuses, so daß insgesamt die vorteilhaften Eigenschaften der neuen Flügeizelienpumpen überwiegen. The vane cell pump according to the invention is relatively inexpensive and, above all, can be manufactured with low weight and small dimensions. The somewhat more complex design of the adjusting ring is easily compensated for by corresponding savings in the design of the housing, so that overall the advantageous properties of the new airline pumps outweigh them.

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Flügelzellenpumpe mit einem Gehäuse (3), einem im Gehäuse (3) dicht geführten Stellring (4), der relativ zu einem im Gehäuse (3) gelagerten und vom Stellring (4) umfaßten Rotor (1) quer zur Achsrichtung des Rotors (1) bewegbar ist, wobei ein Saugbereich (7, 14) der Pumpe durch ein in Drehrichtung des Rotors (1) zunehmendes Volumen einer zwischen zwei benachbarten Flügeln (2), dem Rotor (1) und dem Stellring gebildeten Flügelzelle (5), und ein Druckbereich (8, 11) durch ein in Drehrichtung abnehmendes Volumen der Flügelzelle (5) definiert ist, und wobei mindestens ein Stellglied (22, 23) vorgesehen ist, welches die Position des Stellringes (4) in Abhängigkeit von den jeweiligen Pumpenparametern einstellt, dadurch gekennzeichnet daß am Stellring (4) in der Nähe des Druckbereiches (8, 11) mindestens eine zur Außenseite des Stellringes (4) offene Aussparung (20, 21) zur Aufnahme eines Stellgliedes (22, 23) vorgesehen ist.1. Vane pump with a housing (3), an adjusting ring (4) which is tightly guided in the housing (3) and which, relative to a rotor (1) mounted in the housing (3) and surrounded by the adjusting ring (4), transversely to the axial direction of the rotor ( 1) is movable, a suction area (7, 14) of the pump being caused by a volume of a vane cell (5) formed between two adjacent vanes (2), the rotor (1) and the adjusting ring, increasing in the direction of rotation of the rotor (1), and a pressure range (8, 11) is defined by a decreasing volume of the vane cell (5) in the direction of rotation, and at least one actuator (22, 23) is provided which adjusts the position of the adjusting ring (4) as a function of the respective pump parameters, characterized in that on the adjusting ring (4) in the vicinity of the pressure area (8, 11) at least one recess (20, 21) open to the outside of the adjusting ring (4) is provided for receiving an actuator (22, 23).
2. Flügelzellenpumpe nach Anspruch 1 , dadurch gekennzeichnet, daß zwei Aussparungen (20, 21) auf gegenüberliegenden Seiten des Stellringes (4) vorgesehen sind.2. Vane pump according to claim 1, characterized in that two recesses (20, 21) are provided on opposite sides of the adjusting ring (4).
3. Flügelzellenpumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß mindestens eine Aussparung (20, 21) einen zylindrischen Querschnitt hat.3. Vane pump according to one of claims 1 or 2, characterized in that at least one recess (20, 21) has a cylindrical cross section.
4. Flügelzellenpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Stellring (4) auf der Druckseite doppelwandig ausgebildet ist und der von den Flügeln (2) des Rotors (1) überstrichene Druckraum (8) radiale Öffnungen (10) zu einer durch die Doppeiwand (6, 6') gebildeten Druckkammer (11) aufweist4. Vane pump according to one of claims 1 to 3, characterized in that the adjusting ring (4) is double-walled on the pressure side and the pressure chamber (8) swept over the radial openings (10) by the vanes (2) of the rotor (1) has a pressure chamber (11) formed by the double wall (6, 6 ')
5. Flügelzellenpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Aussparung durch eine teilweise doppeiwandige Ausbildung der druckseitigen Außenwand (6') des Stellringes (4) gebildet ist5. Vane pump according to one of claims 1 to 4, characterized in that the recess is formed by a partially double-walled design of the pressure-side outer wall (6 ') of the adjusting ring (4)
6. Flügelzellenpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß ein in der Aussparung (20) verschiebbarer Steilkolben (22) vorgesehen ist.6. Vane pump according to one of claims 1 to 5, characterized in that a steep piston (22) is provided in the recess (20).
7. Flügelzellenpumpe nach Anspruch 6, dadurch gekennzeichnet, daß der Steilkolben (22) in der Aussparung (20) dicht geführt ist und daß eine den Druckbereich (8, 11) und die Aussparung (20) verbindende Öffnung (26) vorgesehen ist, so daß der Steilkolben (22) über die Öffnung (26) von der Innenseite der Aussparung (20) her mit dem Druck auf der Druckseite beauf¬ schlagt wird.7. Vane pump according to claim 6, characterized in that the steep piston (22) in the recess (20) is tight and that a pressure area (8, 11) and the recess (20) connecting opening (26) is provided, so that the steep piston (22) over the Opening (26) from the inside of the recess (20) is acted upon by the pressure on the pressure side.
8. Vorrichtung nach Anspruch 6 oder 7, dadurch gekennzeichnet, daß der Kolben (22) ans einem aus der Aussparung (20) herausragenden Ende eine abgerundete Stirnwand (24) aufweist8. Apparatus according to claim 6 or 7, characterized in that the piston (22) at one end of the recess (20) projecting end has a rounded end wall (24)
9. Stellring nach Anspruch 2 oder einem der auf Anspruch 2 rückbezogenen Ansprüche, dadurch gekennzeichnet, daß in der der ersten Aussparung (20) gegenüberiiegenden Aussparung (21) eine Druckfeder (23) aufgenommen ist.9. collar according to claim 2 or one of the claims referring back to claim 2, characterized in that in the first recess (20) opposite recess (21) a compression spring (23) is received.
10. Flügelzellenpumpe nach Anspruch 9, dadurch gekennzeichnet, daß die Druckfeder (23) an ihrem aus der Aussparung (21) herausragenden Ende mit einer Gleitkappe (27) versehen ist.10. Vane pump according to claim 9, characterized in that the compression spring (23) at its end projecting from the recess (21) is provided with a sliding cap (27).
11. Flügelzellenpumpe nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Innenwand des Gehäuses (3) mindestens in dem von den Stellgliedern (22, 23) beauf¬ schlagten Bereich mit einem verschleißfesten Material ausgekleidet ist.11. Vane pump according to one of claims 1 to 10, characterized in that the inner wall of the housing (3) is lined with a wear-resistant material at least in the area acted upon by the actuators (22, 23).
12. Flügelzellenpumpe nach Anspruch 11 , dadurch gekennzeichnet, daß das ver¬ schleißfeste Material ein Federstahlblech (25) ist.12. Vane pump according to claim 11, characterized in that the ver¬ wear-resistant material is a spring steel sheet (25).
13. Flügelzellenpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß der Stellring (4) an seiner den Aussparungen (20, 21) abgewandten Seite schwenkbar gelagert ist. 13. Vane pump according to one of claims 1 to 12, characterized in that the adjusting ring (4) is pivotally mounted on its side facing away from the recesses (20, 21).
EP93901592A 1992-01-09 1992-12-15 Compact controllable vane pump Expired - Lifetime EP0620898B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4200305A DE4200305C2 (en) 1992-01-09 1992-01-09 Adjustable vane pump in a compact design
DE4200305 1992-01-09
PCT/DE1992/001059 WO1993014318A1 (en) 1992-01-09 1992-12-15 Compact controllable vane pump

Publications (2)

Publication Number Publication Date
EP0620898A1 true EP0620898A1 (en) 1994-10-26
EP0620898B1 EP0620898B1 (en) 1995-08-02

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US (1) US5484271A (en)
EP (1) EP0620898B1 (en)
JP (1) JPH07502796A (en)
KR (1) KR100209862B1 (en)
AT (1) ATE125905T1 (en)
BR (1) BR9207029A (en)
DE (2) DE4200305C2 (en)
ES (1) ES2078816T3 (en)
MX (1) MX9300092A (en)
WO (1) WO1993014318A1 (en)

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WO1993014318A1 (en) 1993-07-22
DE4200305C2 (en) 1995-06-08
KR100209862B1 (en) 1999-07-15
JPH07502796A (en) 1995-03-23
EP0620898B1 (en) 1995-08-02
DE59203138D1 (en) 1995-09-07
BR9207029A (en) 1995-12-05
ES2078816T3 (en) 1995-12-16
DE4200305A1 (en) 1993-07-15
US5484271A (en) 1996-01-16
KR940703971A (en) 1994-12-12
ATE125905T1 (en) 1995-08-15
MX9300092A (en) 1993-07-01

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