EP0620898B1 - Compact controllable vane pump - Google Patents

Compact controllable vane pump Download PDF

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Publication number
EP0620898B1
EP0620898B1 EP93901592A EP93901592A EP0620898B1 EP 0620898 B1 EP0620898 B1 EP 0620898B1 EP 93901592 A EP93901592 A EP 93901592A EP 93901592 A EP93901592 A EP 93901592A EP 0620898 B1 EP0620898 B1 EP 0620898B1
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EP
European Patent Office
Prior art keywords
vane pump
controlling
recess
collar
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93901592A
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German (de)
French (fr)
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EP0620898A1 (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
Mercedes Benz AG
Glyco Metall Werke Glyco BV and Co KG
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Publication of EP0620898A1 publication Critical patent/EP0620898A1/en
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    • 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, an adjusting 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 surrounded 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 collar formed vane, 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 collar depending on 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 2,318,292 already mentioned above. Because such vane pumps are regularly used as auxiliary units for other machines, in particular as lubricant pumps in engines 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 holes 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 above, 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 collar 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 blades (pressure chamber), with 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 inside 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 actuators 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 an actuating piston which can be pressurized is provided in one of the cutouts.
  • the actuating piston in a appropriately shaped recess is tightly sealed and if an opening is also provided in the wall delimiting the recess inward, 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 hold 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.
  • 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.
  • 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 pivotally 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 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 mirror-like surfaces of the adjusting ring 4 rest on the housing. However, as can also be seen in FIG. 2, the adjusting ring also has openings 9 and 10 for the insertion and removal in the radial direction. Outflow of the 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 with them from the suction chamber 7 and release it again in the pressure chamber 8, since in the pressure region 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.
  • Pistons and springs which act in opposition to 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 discharged from the pressure side, e.g. is branched off 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 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 vane pump shown in FIGS. 3 to 6.
  • the special features of the new vane 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 ' is in turn double-walled in its central region. Specifically, 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 receives a piston 22 guided tightly in this recess, 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 adjustment direction, which must always run transversely to the axis of the rotor 1 not shown in Figures 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 the bore 40 in the housing 3.
  • 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 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.
  • 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 piston 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.
  • the embodiments of Figures 4 and 6 differ only 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 are 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 and adjusting ring have been assembled, is installed 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.
  • FIGS. 7 and 8 show a vane pump with a simpler adjusting ring 4 ', which has no pressure chamber lying radially outside the pressure chamber 8, so that the inner wall 6 coincides with the outer wall 6' of the previously described embodiments. Nevertheless, two substantially aligned cylindrical cavities 20 and 21 are provided on the underside of the adjusting ring 4 ', 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 pushed out of the cylindrical cavity 20 when the pressure rises, on the Supported inner wall of the housing 3 and presses the collar 4 'in the direction of lower eccentricity due to the reaction force.
  • a spring 23 is in turn arranged, which applies a corresponding counterforce, so that a state of equilibrium is established between the spring force and the pump pressure.
  • either the lower cavities 20, 21 can be directly molded on or cast in, but the adjusting ring can also be manufactured separately first, whereupon a tube which is closed in the middle is simply welded onto the underside of the adjusting ring 4 'after the breakthrough 26 was made, for example, in the form of a hole.
  • the adjusting ring 4 'with its maximum (horizontal) diameter it is also not necessary for the adjusting ring 4 'with its maximum (horizontal) diameter to be guided 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 closely over a tubular extension which forms the cavities 20, 21 mentioned.
  • the vane pump according to the invention is relatively inexpensive and, above all, can be manufactured with a lower 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 vane pumps outweigh.

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  • 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)
  • Reciprocating Pumps (AREA)
  • External Artificial Organs (AREA)

Abstract

PCT No. PCT/DE92/01059 Sec. 371 Date Sep. 13, 1994 Sec. 102(e) Date Sep. 13, 1994 PCT Filed Dec. 15, 1992 PCT Pub. No. WO93/14318 PCT Pub. Date Jul. 22, 1993.A vane pump has a casing, a controlling collar guided leaktightly in the casing and movable relative to a rotor mounted in the casing and surrounded by the controlling collar. The movement of the collar is transverse to the axial direction of the rotor. A suction region of the pump is defined by a volume increasing in the direction of rotation of the rotor, of a vane cell formed between two adjacent vanes and decreasing to the pressure region. At least one adjustment member is provided to adjust the position of the controlling collar in dependence on the prevailing pumping parameters. In order to provide a vane pump of space-saving and/or simple and cost-saving design, at least one recess is open towards the outside of the controlling collar and is provided on the controlling collar close to the pressure region to accommodate and adjustment member.

Description

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 Flügelzelle, 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 einstellt.The present invention relates to a vane pump with a housing, an adjusting 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 surrounded 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 collar formed vane, 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 collar depending on 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 zurückgeht.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.

Die Stellglieder haben einen erheblichen Platzbedarf, wie insbesondere der nächstliegende Stand der Technik gemäß der oben bereits erwähnten US 2,318,292 zeigt. Da derartige Flügelzellenpumpen regelmäßig als Hilfsaggregate für andere Maschinen Verwendung finden, insbesondere als Schmiermittelpumpen in Motoren und anderen Maschinen, ist der zusätzliche Platzbedarf unerwünscht und oft auch mit erheblichen Nachteilen verbunden. Außerdem nimmt dadurch auch da Gewicht der Pumpe zu, was ebenfalls unerwünscht ist. Schließlich erfordern auch die Steuerleitungen für das Stellglied oder die Stellglieder zusätzliche Bohrungen und Durchführungen 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 2,318,292 already mentioned above. Because such vane pumps are regularly used as auxiliary units for other machines, in particular as lubricant pumps in engines 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 holes 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 above, 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 Stellring 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 collar 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 Rotorflügeln 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 blades (pressure chamber), with 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 inside 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 Stellglieder 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 actuators 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 Stellringposition 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 Aussparungen ein mit Druck beaufschlagbarer Stellkolben vorgesehen ist. Bei einer solchen Ausführungsform hat es sich als besonders zweckmäßig erwiesen, wenn der Stellkolben 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 an actuating piston which can be pressurized is provided in one of the cutouts. In such an embodiment, it has proven to be particularly useful if the actuating piston in a appropriately shaped recess is tightly sealed and if an opening is also provided in the wall delimiting the recess inward, 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 halten, 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 hold 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 pistons and pressure 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 bietet.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.

Schließlich ist eine Ausführungsform der Erfindung bevorzugt, bei welcher 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 Gleitflächen 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 pivotally 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 Anwendungsmöglichkeiten der vorliegenden Erfindung werden deutlich anhand der folgenden Beschreibung und der zugehörigen Figuren. Es zeigen:

Figuren 1 und 2
zwei zueinander senkrechte Schnittansichten einer Flügelzellenpumpe nach dem Stand der Technik,
Figuren 3 und 4
den Figuren 1 und 2 entsprechende Schnitte einer bevorzugten Ausführungsform der erfindungsgemäßen Flügelzellenpumpe,
Figuren 5 und 6
zusätzliche Merkmale und Abweichungen zu den in den Figuren 3 und 4 dargestellten Ausführungsformen in entsprechenden Schnittansichten und
Figuren 7 und 8
Schnittansichten durch eine weitere Ausführungsform ohne radiale Druckkammer.
Further advantages, features and possible uses of the present invention will become apparent clear from the following description and the associated figures. Show it:
Figures 1 and 2
two mutually perpendicular sectional views of a vane pump according to the prior art,
Figures 3 and 4
1 and 2 corresponding sections of a preferred embodiment of the vane pump according to the invention,
Figures 5 and 6
Additional features and deviations from the embodiments shown in FIGS. 3 and 4 in corresponding sectional views and
Figures 7 and 8
Section views through a further embodiment without radial 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 mirror-like surfaces of the adjusting ring 4 rest on the housing. However, as can also be seen in FIG. 2, the adjusting ring also has openings 9 and 10 for the insertion and removal in the radial direction. Outflow of the 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).As can easily be seen from FIG. 1, the vanes 2 in the vane cells 5 defined between adjacent vanes 2 take delivery medium with them from the suction chamber 7 and release it again in the pressure chamber 8, since in the pressure region 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 Figur 1 ist durch den Doppelpfeil 18 die Verstellmöglichkeit 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 Flügelzellenvolumen 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, welche eine Verschiebung des Stellringes relativ zum Rotort 1 und zum Gehäuse 3 vornehmen und so das Fördervolumen und den Druck regulieren, nicht dargestellt. Im allgemeinen dienen als Stellglieder gegeneinanderwirkende 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.In Figure 1, the possibility of adjusting the collar 4 is indicated by the double arrow 18. If the adjusting ring 18 is shifted more to the left in FIG. 1, the vane cell volume changes less than in the state shown in FIG. 1 when the suction chamber 7 or the pressure chamber 8 is swept over. Accordingly, less fluid 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, corresponding actuators, which move the adjusting ring relative to the rotor location 1 and the housing 3 and thus regulate the delivery volume and the pressure, are not shown. Pistons and springs which act in opposition to 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 discharged from the pressure side, e.g. is branched off 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 Verstellmöglichkeit 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 Flügelzellenpumpen 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 possibility of adjusting the collar 4, the actuators 22, 23 are arranged 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 vane pump shown in FIGS. 3 to 6.

Die Besonderheiten der neuen Flügelzellenpumpen 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. Konkret erkennt 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 Verstellrichtung 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 vane 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 'is in turn double-walled in its central region. Specifically, 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 receives a piston 22 guided tightly in this recess, 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 adjustment direction, which must always run transversely to the axis of the rotor 1 not shown in Figures 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 Vördermediums 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 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 Kolben 22 von innen her mit Druck. Die in den Figuren 3 und 5 dargestellten Ausführungsformen unterscheiden 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 Druckfeder 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 entsprechend sinkt. Im Ergebnis stellt 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).In 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 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 at a relatively low level Pressure is pumped relatively much fluid; 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 counterforce exerted by the compression spring 23, which is compressed further, just compensates for the force exerted by the piston due to the higher pressure. The delivery volume decreases, so that the pressure drops accordingly. As a result, a state of equilibrium is established 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 being reached in FIG. 5 (Maximum pumping power).

Die Gehäusegestaltung ist bei den erfindungsgemäßen Ausführungsformen wesentlich einfacher als beim Stand der Technik, bei welchem Kolbenführungen 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 Montagevorgang und senkt die Produktionskosten.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 piston 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 Ausführungsformen 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 Figure 2, the embodiments of Figures 4 and 6 differ only 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 zweckmäßiger 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 abschließt.However, this is also not a necessary feature of the invention. On the contrary, it can be more expedient if both openings are 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 and adjusting ring have been assembled, is installed 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 Ausführungsform 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 mit der 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.FIGS. 7 and 8 show a vane pump with a simpler adjusting ring 4 ', which has no pressure chamber lying radially outside the pressure chamber 8, so that the inner wall 6 coincides with the outer wall 6' of the previously described embodiments. Nevertheless, two substantially aligned cylindrical cavities 20 and 21 are provided on the underside of the adjusting ring 4 ', 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 pushed out of the cylindrical cavity 20 when the pressure rises, on the Supported inner wall of the housing 3 and presses the collar 4 'in the direction of lower eccentricity due to the reaction force. In the opposite cavity 21, a spring 23 is in turn arranged, which applies a corresponding counterforce, so that a state of equilibrium 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 directly molded on or cast in, but the adjusting ring can also be manufactured separately first, whereupon a tube which is closed in the middle is simply welded onto the underside of the adjusting ring 4 'after the breakthrough 26 was made, for example, in the form of a hole. In the cross-sectional image according to FIG. 7, it is also not necessary for the adjusting ring 4 'with its maximum (horizontal) diameter to be guided 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 closely over a tubular extension which forms the cavities 20, 21 mentioned.

Die erfindungsgemäße Flügelzellenpumpe ist relativ kostengünstig und vor allem mit geringern 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 Flügelzellenpumpen überwiegen.The vane pump according to the invention is relatively inexpensive and, above all, can be manufactured with a lower 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 vane pumps outweigh.

BezugszeichenlisteReference list

11
Rotorrotor
1'1'
Wellewave
22nd
Flügelwing
2'2 '
FührungsschlitzeGuide slots
33rd
Gehäusecasing
4, 4'4, 4 '
StellringCollar
55
FlügelzellenWing cells
66
Wandabschnitt, InnenwandWall section, inner wall
6'6 '
AußenwandOuter wall
6a6a
Abschnitte der Wand 6Sections of the wall 6
77
SaugraumSuction chamber
88th
DruckraumPressure room
9, 109, 10
Öffnungenopenings
1111
DruckkammerPressure chamber
1212th
axiale Öffnungaxial opening
1313
Mündung der Bohrung 40Mouth of hole 40
1414
Innenrauminner space
1616
Wände, FlächeWalls, surface
1717th
BereichArea
1818th
DoppelpfeilDouble arrow
20, 2120, 21
Aussparungen, HohlräumeRecesses, cavities
2222
Kolbenpiston
2323
DruckfederCompression spring
2424th
StirnflächeFace
2525th
FederstahlblechSpring steel sheet
2626
Durchbruch, ÖffnungBreakthrough, opening
2727
Kappecap
2828
ZwischenwandPartition
3030th
Wellewave
3131
Öffnungenopenings
32, 3332, 33
strichpunktierte Liniendash-dotted lines
4040
GehäusebohrungHousing bore
4141
GehäusebohrungHousing bore

Claims (13)

  1. Vane pump comprising a casing (3), a controlling collar (4) which is guided in a leakproof manner in the casing (3) and is movable, relative to a rotor (1) mounted in the casing (3) and surrounded by the controlling collar (4), transversely to the axial direction of the rotor (1), wherein an intake region (7, 14) of the pump is defined by a volume, increasing in the direction of rotation of the rotor (1), of a cell (5) formed between two adjacent vanes (2), the rotor (1) and the controlling collar, and a discharge region (8, 11) is defined by a volume, decreasing in the direction of rotation, of the cell (5), and wherein at least one controlling component (22, 23) is provided for setting the position of the controlling collar (4) in dependence on the prevailing pumping parameters, characterised in that the controlling collar (4) is provided in the vicinity of the discharge region (8, 11) with at least one recess (20, 21) which is open towards the outside of the controlling collar (4) and serves for receiving a controlling component (22, 23).
  2. Vane pump according to claim 1, characterised in that two recesses (20, 21) are provided situated on opposite sides of the controlling collar (4).
  3. Vane pump according to claim 1 or 2, characterised in that at least one recess (20, 21) has a cylindrical cross-section.
  4. Vane pump according to any one of claims 1 to 3, characterised in that the controlling collar (4) is at the discharge side made double-walled and the discharge space (8) swept by the vanes (2) of the rotor (1) comprises radial openings (10) leading to a discharge chamber (11) formed by the double wall (6, 6').
  5. Vane pump according to any one of claims 1 to 4, characterised in that the recess is formed by a partly double-walled construction of the outer wall (6') of the controlling collar (4) on the discharge side.
  6. Vane pump according to any one of claims 1 to 5, characterised in that a controlling piston (22) is provided in the recess (20).
  7. Vane pump according to claim 6, characterised in that the controlling piston (22) is guided in a leakproof manner and that an opening (26) interconnecting the discharge region (8, 11) and the recess (20) is provided, so that the controlling piston (22) is subjected to the pressure on the discharge side through the opening (26) from the inner side of the recess (20).
  8. Vane pump according to claim 6 or 7, characterised in that the piston (22) has a rounded end face (24) at the end projecting from the recess (20).
  9. Vane pump according to claim 2 or any claim appended to claim 2, characterised in that a compression spring (23) is received in the recess (21) which is situated opposite the first recess (20).
  10. Vane pump according to claim 9, characterised in that the compression spring (23) is at its end projecting from the recess (21) provided with a sliding cap (27).
  11. Vane pump according to any one of claims 1 to 10, characterised in that the inner wall of the casing (3) is lined with a wear-resistant material at least in the region exposed to the action of the controlling components (22, 23).
  12. Vane pump according to claim 11, characterised in that the wear-resistant material is a spring steel sheet.
  13. Vane pump according to any one of claims 1 to 12, characterised in that the controlling collar (4) is swingably mounted at its side remote 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 EP0620898A1 (en) 1994-10-26
EP0620898B1 true EP0620898B1 (en) 1995-08-02

Family

ID=6449225

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93901592A Expired - Lifetime EP0620898B1 (en) 1992-01-09 1992-12-15 Compact controllable vane pump

Country Status (10)

Country Link
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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US6790013B2 (en) 2000-12-12 2004-09-14 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US7674095B2 (en) * 2000-12-12 2010-03-09 Borgwarner Inc. Variable displacement vane pump with variable target regulator
US7108493B2 (en) * 2002-03-27 2006-09-19 Argo-Tech Corporation Variable displacement pump having rotating cam ring
DE10138187B4 (en) * 2001-07-27 2013-03-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable volume vane pump
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CN103541898B (en) 2008-04-25 2015-11-18 麦格纳动力系有限公司 There is the variable displacement vane pump of the exhaust port of enhancing
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EP2351934A1 (en) * 2010-01-11 2011-08-03 Pierburg Pump Technology GmbH Variable-displacement lubricant pump
JP5364606B2 (en) * 2010-01-29 2013-12-11 日立オートモティブシステムズ株式会社 Vane pump
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IT201600082659A1 (en) * 2016-08-04 2018-02-04 Vhit Spa PALETTE VOLUMETRIC PUMP
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Also Published As

Publication number Publication date
ATE125905T1 (en) 1995-08-15
KR100209862B1 (en) 1999-07-15
BR9207029A (en) 1995-12-05
KR940703971A (en) 1994-12-12
ES2078816T3 (en) 1995-12-16
JPH07502796A (en) 1995-03-23
WO1993014318A1 (en) 1993-07-22
DE4200305C2 (en) 1995-06-08
DE59203138D1 (en) 1995-09-07
MX9300092A (en) 1993-07-01
US5484271A (en) 1996-01-16
DE4200305A1 (en) 1993-07-15
EP0620898A1 (en) 1994-10-26

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