EP0620898A1 - Compact controllable vane pump. - Google Patents

Compact controllable vane pump.

Info

Publication number
EP0620898A1
EP0620898A1 EP19930901592 EP93901592A EP0620898A1 EP 0620898 A1 EP0620898 A1 EP 0620898A1 EP 19930901592 EP19930901592 EP 19930901592 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
characterized
housing
vane pump
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
EP19930901592
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
Priority to DE4200305 priority Critical
Priority to DE19924200305 priority patent/DE4200305C2/en
Application filed by Glyco Metall Werke Glyco BV and Co KG filed Critical Glyco Metall Werke Glyco BV and Co KG
Priority to PCT/DE1992/001059 priority patent/WO1993014318A1/en
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
Application status is Expired - Lifetime legal-status Critical

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22Control 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
    • F04C14/223Control 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
    • F04C14/226Control 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

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). A semi-rotary pump cell comprises a housing (3), an adjusting ring (4) sealingly guided in the housing (3) and movable transversely to the axial direction of a rotor (1) which is mounted in the housing (3 ) and surrounded by the adjusting ring (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). 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 rotary cell (5) formed between two adjacent blades (2), the rotor (1 ) and the adjusting ring, and the delivery zone (8, 11) is defined by the decreasing volume in the direction of rotation of the rotary unit (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. At least one adjusting member (22, 23) adjusts the position of the adjusting ring (4) according to the respective parameters of the pump. 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). To obtain a semi-rotary pump cell having a compact construction and / or simple and inexpensive, at least one recess (20, 21) for receiving an adjustment member (22, 23) open towards the outside of the adjusting ring (4) is provided in the adjusting ring (4) near the discharge region (8, 11).

Description

Adjustable vane pump in a compact design

The present invention relates to a vane pump having a housing, a tightly guided in the housing collar, the stored relative to a in the housing and the adjusting ring comprised rotor transverse to the axial direction is movable, wherein a suction region of the pump by an increasing in the direction of rotation of the rotor volume of a is defined between two adjacent vanes, the rotor and the adjusting ring Rügelzelle formed, and a pressure area by a decreasing in the direction of rotation volume of the vane, and wherein at least one actuator is provided, which adjusts the position of the controlling collar in dependence on the respective pump parameters

As pump parameters which can influence the position of the adjusting ring in particular the delivery of the pump, but occurring on the delivery side pressure are mainly used.

Such a vane pump is known from US 2,318,292.

From German Offenlegungsschrift no. 40 11 671 a vane pump is also known, which substantially has the features indicated above, however, the arrangement and location of any actuators is not described. Apart from the particular arrangement of actuators and the corresponding configuration of the adjusting ring, however, the vane pump as described in the present application vane pump described in DE 40 11 671 A1 is identical, so that with respect to the other configuration and the advantageous properties associated to that application reference can be made, going back to the same inventor

The actuators have shown a considerable amount of space, in particular the closest prior art according to the above already mentioned US 3,218,292, since such Flügelzel- lenpumpen regularly used as auxiliary power units for other machines, ins¬ particular as lubricant pumps in engines and other machines, the additional footprint undesirable and often associated with significant disadvantages. In addition, this also increases the weight of the pump, which is also undesirable. Finally, the control lines for the actuator or actuators require additional drilling and Durch¬ guides in the housing, so that the mentioned pump parameters may act on the actuators, in turn, change the setting ring position and thus Set the off pump parameters to a desired value.

In this prior art, the present invention has for its object to provide a vane pump with the features mentioned initially, which has a space-saving and simple or and cost-saving construction.

This object is achieved in that at least one of the outer side of the adjusting ring and open in the direction of adjustment recess for receiving an actuator is provided in the vicinity of its printing area on the adjusting ring.

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 of the adjusting ring.

A double-walled construction of the adjusting ring on the pressure side of the adjusting ring leads to the formation of an additional pressure chamber between the two double-wall-forming walls which is located radially outwardly of the path swept by the Rotorflügelπ area (pressure chamber), said radial openings in the vane wall facing the connection between produce the pressure chamber and the pressure chamber. The pressure chamber is more easily and more quickly emptied, so that even at very high speeds of the rotor no excessively high pressure builds and especially hard pressure surges are avoided.

A disadvantage of this embodiment with a double-walled collar and an additional pressure chamber on the pressure side of the adjusting ring is located in the additional space requirement of the adjusting ring, so that the housing must be correspondingly larger.

In particular, in the latter embodiment with an additional pressure chamber at the adjusting ring the locking ring is carried in the invention to be provided in addition to recess or only very slightly larger than without the recess for the actuator. The inner wall of such a recess can project into the pressure chamber into namely readily, because the pressure chamber does not have a uniform cross section over the entire axial length of the adjusting ring in order to fulfill their function.

The adjusting ring wall can be double-walled to form a recess in the pressure range, wherein the recess between the inner and the outer wall is formed. In an adjusting ring, which is already double-walled to form an additional pressure chamber in the printing region, the outer wall of the adjusting ring is in turn again at least double-walled in a partial region, to provide the corresponding recess.

In the preferred embodiment of the invention, two cavities or recesses are provided on opposite sides of the adjusting ring, which cavities are open at least in the adjustment direction. Among the directions of adjustment are understood to be made of which the actuator or the ball members exert a force on the adjusting ring. The two cavities are separated by an intervening wall.

In general, two oppositely acting actuators are provided on a collar such that react in different ways to the displacement of the Stellringpositioπ and the pump parameters mentioned above. With proper selection then adjusts to a desired state of equilibrium.

Furthermore, the recesses or cavities mentioned are preferably of cylindrical cross-section, as well as actuators in its simplest embodiment, often have cylindrical cross section.

Particularly preferred is an embodiment of the invention in which the outer wall of the adjusting ring in the pressure range, that is, either the outer wall of the pressure chamber, or, if present, the outer wall of an additionally radially existing outside of the pressure chamber pressure chamber is in turn a double-walled at least in a partial area, wherein between both the double wall parts forming the desired recess for receiving the actuator is produced.

Furthermore, an embodiment of the invention is preferred, in which in one of the savings Aus¬ a pressurizable ball piston is provided. In such an embodiment, it has proved to be particularly advantageous when the ball piston is guided tightly in a correspondingly shaped recess, and further when the recess is provided to the inside wall defining an opening which connect to the pressure chamber or to the pressure chamber of the pump producing This opening is advantageously provided at the inner end of the recess. When pressure is applied, the piston is then driven out of the recess and is supported with its protruding from the recess end, for example, on the inner wall of the pump housing. By the printing medium while a corresponding reaction force is exerted on the facing away from the piston end wall of the recess, whereby the adjusting ring is moved away from the wall of the housing on which the piston acts.

The case counterforce required to have the adjusting ring in an equilibrium position, is advantageously applied by a compression spring, the opposite recess is incorporated in one of the first recess and is supported on the opposite housing wall with its projecting out of the recess end. In such an embodiment of the device it is advantageous if the protruding out of the first mentioned recess end of the piston is formed with a rounded end face, and if, for example, which is designed as spiral spring compression spring has a cap at its protruding from the recess end, a correspondingly round and slippery surface has During the movement of the adjusting ring this attacking on the walls surfaces of pistons and springs can slide more easily, leaving no traces of wear.

Particularly preferred is an embodiment of the invention in soft inner wall of the housing is lined with a metal insert made of spring steel, which provides a substantially wear-free or at least very wear-resistant surface for the so-engaging ends of the actuators

Finally, an embodiment of the invention is preferred, is pivotally suspended in softer the collar on its side remote from the actuators. then comes out with a single pair of eccentrically mounted actuators, which, however, necessarily run during pivoting of the adjusting ring also moves perpendicular to the travel, so that then in particular the aforementioned embodiments with wear-free or low-wear Gleitfiächen at the ends of the actuators and their attack regions of are beneficial.

Further advantages, features and Anwendungsmögüchkeiten of the present invention will become apparent from the following description and the accompanying drawings. Show it:

Figures 1 and 2 show two mutually perpendicular sectional views of a Flügelzel¬ lenpumpe according to the prior art,

Figures 3 and 4 Figures 1 and 2 corresponding sections of a preferred

Embodiment of the invention vane pump,

Figures 5 and 6, additional features and variations to the figures in the

Embodiments in corresponding sectional views 3 and 4,

Figures 7 and 8 are sectional views of another embodiment without radial

Pressure chamber.

The main functions of the pump will be briefly described with reference to the prior art shown in FIGS. 1 and 2 3, a housing is referred to, is arranged in the interior space 14 with a fixed axis, a rotor 1 'is rotated and running in the radial and axial direction guide slots 2' on a shaft 1 for wing 2 has. The wings are resiliently biased from the center of the rotor 1 so forth and be pressed outward in the radial direction. Surrounds the rotor 1 at a distance from a substantially cylindrical interior an adjustment ring 4. The shaded areas of the adjusting ring 4 abut against the flat surface 16 of the housing 3 in Figure 1, as can be seen in FIG. 2 The adjusting ring is formed mirror-symmetrically substantially so that abut on the opposite side mirror-image areas of the adjusting ring 4 on the housing. However, as can be seen in Figure 2 also has the adjusting ring in the radial direction of openings 9 and 10 for the inlet and discharge of the pumped medium. The pumped liquid flows into the the positioning ring 4 surrounding space 14, partially but directly in the path swept by the vane portion 17 of the suction chamber 7 through the housing bore 41st

As seen from Figure 1 easy to take the wing 2 in the space defined between adjacent vanes 2 vane 5 pumping medium from the suction chamber 7 and enter it in the pressure chamber 8 again, as in the pressure range, the volume of the vane 5 between the rotor and the lower wall 6 of the adjusting ring 4 decreases. The fluid enters through openings 10 in the radial direction and in the pressure chamber 11 and from there 3rd through the axial opening 12 in the pressure-side bore 40 of the housing, it should be understood that the orifice 13 of the bore 40 in the area of ​​the pressure chamber 8 lie and the wall 6 in the pressure range of the adjusting ring may bear against the walls 16 of the housing 3 so that the vane in axial direction may be emptied into a correspondingly shaped opening 13 (see Figure 7). In Figure 1 is indicated by the double arrow 18, the Verstellmögiichkeit of the adjusting ring. 4 If the adjusting ring 18 is displaced in Figure 1 more to the left, so changes when passing over the suction chamber 7 or the pressure chamber 8, the Flügefzellenvolumen less than in the example illustrated in Figure 1 state. Accordingly, less feed medium is pumped so that, assuming a constant demand on the pressure side, the pressure in the pressure range decreases to Figures 1 and 2, however, are appropriate actuators, soft make relative to the rotor 1 and the housing 3 and thus the displacement of the adjusting ring regulate oil flow and the pressure, not shown. In general, with a corresponding piston is generally performed in the housing and is acted upon by the housing side with the pumping medium, which is branched off from the pressure side, for example from the bore 40 here serve against each as actuators, on the other acting pistons and springs.

A plurality of pistons may move parallel to the ring, but the ring can also be pivotably suspended about an axis, as shown in connection with the inventive design of the pump in Figures 3 and 4. FIG.

It can be seen in Figures 3 to 7, that the adjusting ring is pivotably mounted about an accommodated in the upper part of the housing shaft 30th In contrast to the illustration in Figure 1, which indeed does not show the actuators, but the Verstellmögiichkeit of the adjusting ring 4, but the actuators 22, 23 arranged straight so that, as in Figure 1, the flow volume is reduced, conversely, when the actuating ring from left swings to the right, and is increased when it is swung from right to left. In principle, however, the operation of the vane pump shown in Figures 1 and 2 with the results shown in Figures 3 to 6 is identical Flügeizelienpumpen.

The features of the new Flügeizelienpumpen located in the recesses 20, 21 which ie, in the pressure range of the adjusting ring, is provided in the lower region. In all the illustrated embodiments of Figures 3 to 6 of the collar 4 is double-walled in the pressure range under formation of an additional pressure chamber. 11 The pressure chamber 11 is located between the inner wall 6 and the outer wall 6 'of the adjusting ring. The outer wall 6 'is now in turn a double-walled in its central region Concretely, one recognizes two to opposite sides open and separated by an intermediate wall 28 cylindrical cavities 20, 21, of which the cavity or recess 20 a guided tightly in said recess piston 22 receiving, while the cavity 21 housing a helical compression spring 23rd The two cavities 20, 21 are open in opposite directions, with the profile thus defined of the cavities 20, 21 from the closed reversed defines the Versteilrichtung to the open end, or that always transverse to the axis of the rotor not shown in the Figures 3 to 6 1 must be parallel 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 inner surface of the adjusting ring. 4

When pumping the pumped fluid from the pressure chamber 8 initially flows into 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 40th The protrusion of the inner lying wall of the cavities 20, 21 in this pressure chamber 11 into disabled while the flow of Vördermedi- killed only insignificantly, since the free cross-section between the wall 6 and the inner wall of the recesses 20, 21 can be kept larger readily than the cross section of the bore 40 in the housing. 3

In the illustrated preferred embodiments of the Figures 3 to 6 also can be seen through an opening 26 in the wall of the recess 20 to the pressure chamber. 11 Through this opening 26, the pumped liquid enters into the cavity 20 in, and so acts on the piston

22 from the inside by pressure. The embodiments unter¬ shown in Figures 3 and 5 are deposited substantially only by the inserted in Figure 5 into the housing 3 plate 25 is made of spring steel and the cap 27 of the compression spring 23. Otherwise shows 5 shows a state of the pump, wherein, in relatively low pressure relatively large amount of conveying medium is pumped; the adjusting ring has a near maximum deflection to the left and thus a maximum eccentricity with respect to the rotor 1 is not shown, the center of which, however, for example, the intersection of the phantom lines 32 33 can be thought. for example, is now the need for conveying medium on the pressure side is lower, will increase at the given pumping volume of the pressure, which results in a stronger reaction force from the pressurized piston 22 on the end face 24 of the piston facing away from inner wall of the recess 20 is applied. Characterized the adjusting ring 4 is pivoted more in the direction of the position shown in Figure 3, to thereby further by the compressed compression spring

23 counterforce exerted the force exerted by the piston due to the higher pressure just compensated. The delivery volume decreases while, so that the pressure will drop correspondingly. As a result, an equilibrium state between the two extreme positions stiff, which are shown in Figures 3 and 5, wherein thought in Figure 3 of the rotor and centered in the collar 4 is (pump power zero) and reaches the position of maximum eccentricity in Figure 5 is (pump power maximum).

The housing design is much simpler than in the prior art, in which Kolbenführuπgen and in particular bores or lines which supply to the piston, the pressurized medium were required in the embodiments of the invention.

The compression spring need not be mounted in the housing. Instead, the respective components are all arranged on the adjusting ring, which requires a certain volume and anyway especially in the example of double-walled design with a pressure chamber 11 which is not increased significantly by the additional receiving recesses for the actuators.

The housing 3 can therefore be designed overall much simpler and more compact.

As can be seen when comparing the two Figures 3 and 5, which protrudes from the recesses 20 and 21, ends of the piston 22 or the compression spring 23 must also slide on them facing inner surfaces of the housing. 3 Conveniently, the piston has to a preferably spherical rounded end face 24 and the compression spring 23 is provided with a likewise rounded on their outside cap 27th Furthermore, the inner surface of the housing 3 in the area where piston 22 and the end face 24 and the cap tread 27 of the compression spring 23 into engagement with the housing inner wall, with a sheet 25 of spring steel construed The materials of the cap 27 and the end face 24 of the piston 22 are preferably selected so that they can easily slide on the spring steel of the sheet 25th The spring steel sheet 25 is preferably integrally inserted into the lower portion of the housing 3 and may optionally be clamped to the ends with corresponding projections or shoulder on the inner wall of the housing. 3 This insertion of the spring steel sheet 25 in one piece facilitates Moπtagevorgang and reducing the costs of Produktions¬.

6 shows in an axial section through the housing and the adjusting ring only a variation in the design of the openings 10 between the pressure chamber and pressure chamber in the example of Figure 6 as two parallel, circumferentially extending slots are shown, at the axial ends of the adjusting ring 4 is still sections are stopped 6a of the wall 6 of the adjusting ring. In contrast, a wall section stopped in the embodiment of Figure 4 only in the central region, both on the pressure side and the suction side 6 which serves as a guide for the blades. 2

Compared with the example shown in Figure 2 the prior art, the execution are different shapes of Figures 4 and 6 only still characterized in that the suction openings are provided in the housing wall 31, which faces the housing wall, in which the pressure-side openings are provided. 13

However, even this is not a necessary feature of the invention. It may be zweckmäßi¬ ger on the contrary, if both openings are located on one side of the housing, particularly when, as shown in Figures 4 and 6, the housing consists of a substantially open on one side cavity by the assembly of rotor and adjusting ring is only additionally provided with a wall or a lid which closes the open side of the housing

However, the invention also includes embodiments, a is in which the positioning ring 4 is completely closed along its circumference and only in the axial direction of an inflow or outflow of the pumped medium is possible in the space formed between the rotor and the adjusting ring vane or out of these. For this purpose, only the suction port 31 and the pressure-side opening 13 in the region of the vane 5 must be disposed. The recesses 20 and 21 may then be formed by a double-walled design of the bottom wall 6 of the adjusting ring. 4 Such Ausführungsforrp is shown in Figures 7 and 8. FIG.

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 * 20 and 21 are provided two aligned with each other substantially cylindrical cavities extending tangentially extend approximately along the outer side of the adjusting ring 4 'of which the suspension opposite end. In this case, the cylindrical cavity 20 is connected via an opening 26 with the pressure space in the interior of the actuator ring 4 'and a piston 22 is sealingly guided in the cavity 20 so that it is squeezed out at the pressure increases from the cylindrical cavity 20, at supporting inner wall of the housing 3 and due to the reaction force of the collar 4 'in the direction of lesser eccentricity presses the opposite cavity 21 is, in turn, a spring 23 is arranged, which applies an appropriate reaction force, so that adjusts a state of equilibrium between the spring force and the pump pressure. In the manufacture of such a pump, either the lower cavities 20, 21 are directly molded or cast together, the locking ring whereupon simply a sealed in the center pipe is welded to the underside of the adjusting ring 4 'may, however, can also be produced separately first, after the breakthrough was applied in the form of a bore 26, for example, the cross sectional view according to FIG 7, it is also not necessary that the positioning ring 4 'with its maximum (horizontal) diameter up to the area of ​​the cavities 20, 21 is passed, rather, the outer surface of the adjusting ring 4 'parallel to its circular inner surface to closely pass through a tubular extension which forms the cavities 20, 21 mentioned.

The erfinduπgsgemäße vane pump is relatively inexpensive and above all with low weight and small dimensions produced. The somewhat more complicated design of the adjusting ring is easily compensated by corresponding savings in the design of the housing, so that a total of the advantageous properties of the new Flügeizelienpumpen predominate.

Claims

P atentanspr ü che
1. vane pump having a housing (3) guided tightly in the housing (3) adjusting ring (4) to a housing (3) mounted relative to and from the adjusting ring (4) covered rotor (1) transversely to the axial direction of the rotor ( 1) is movable, wherein a suction area (7, 14) of the pump through a (in the rotational direction of the rotor 1) formed increasing volume of a (between two adjacent vanes 2), the rotor (1) and the collar vane (5), and a pressure area (8, 11) is defined by a decreasing in the direction of rotation volume of the vane (5), and wherein at least one actuator (22, 23) is provided, which adjusts the position of the adjusting ring (4) in dependence on the respective pump parameters, characterized in that at the adjusting ring (4) in the vicinity of the printing area (8, 11) at least open one to the outside of the controlling collar (4) recess (22, 23) is provided (20, 21) for receiving an actuator.
2. Vane pump according to claim 1, characterized in that two recesses (20, 21) on opposite sides of the adjusting ring (4) are provided.
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. 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 from the wings (2) of the rotor (1) swept pressure chamber (8) has radial openings (10) to having a Doppeiwand by the pressure chamber (6, 6 ') (11) formed
5. Vane pump according to one of claims 1 to 4, characterized in that the recess is formed by a partial doppeiwandige forming the pressure side outer wall (6 ') of the adjusting ring (4)
6. Vane pump according to one of claims 1 to 5, characterized in that into the recess (20) displaceable ball plunger (22) is provided.
7. Vane pump according to claim 6, characterized in that the ball plunger (22) in the recess (20) is guided in a sealed and that a pressure region (8, 11) and the recess (20) connecting the opening (26) is provided, so will strike that the ball plunger (22) via the opening (26) of the inside of the recess (20) here with the pressure on the pressure side acted upon.
8. Apparatus according to claim 6 or 7, characterized in that the piston (22) to the one of the recess (20) protruding end a rounded end wall (24)
9. Collar according to claim 2 or any one of the claims referring back to claim 2 claims, characterized in that in the first recess (20) gegenüberiiegenden recess (21) a compression spring (23) is accommodated.
10. Vane pump according to claim 9, characterized in that the compression spring (23) is provided at its out of the recess (21) protruding end with a sliding cap (27).
11. Vane pump according to one of claims 1 to 10, characterized in that the inner wall of the housing (3) at least in the of the actuators (22, 23) acted upon estimated area is lined with a wear-resistant material.
12. Vane pump according to claim 11, characterized in that the ver¬ schleißfeste material is a spring steel sheet (25).
13. Vane pump according to one of claims 1 to 12, characterized in that the adjusting ring (4) at its recesses (20, 21) facing away side is pivotally mounted.
EP19930901592 1992-01-09 1992-12-15 Compact controllable vane pump Expired - Lifetime EP0620898B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE4200305 1992-01-09
DE19924200305 DE4200305C2 (en) 1992-01-09 1992-01-09 Adjustable vane pump in a compact design
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

Family

ID=6449225

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930901592 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) AT125905T (en)
BR (1) BR9207029A (en)
DE (1) DE4200305C2 (en)
ES (1) ES2078816T3 (en)
MX (1) MX9300092A (en)
WO (1) WO1993014318A1 (en)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5738500A (en) * 1995-10-17 1998-04-14 Coltec Industries, Inc. Variable displacement vane pump having low actuation friction cam seal
US6623250B2 (en) 2000-02-17 2003-09-23 Goodrich Pump And Engine Control Systems, Inc. Fuel metering unit
US6896489B2 (en) * 2000-12-12 2005-05-24 Borgwarner Inc. Variable displacement vane pump with variable target regulator
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
AU2003215934A1 (en) * 2002-03-16 2003-09-29 In-Sook Oh Vane pump
US7726948B2 (en) * 2002-04-03 2010-06-01 Slw Automotive Inc. Hydraulic pump with variable flow and variable pressure and electric control
JP2004251267A (en) * 2002-04-03 2004-09-09 Borgwarner Inc Variable displacement pump and its control system
US6962485B2 (en) * 2003-04-14 2005-11-08 Goodrich Pump And Engine Control Systems, Inc. Constant bypass flow controller for a variable displacement pump
US6996969B2 (en) * 2003-09-09 2006-02-14 Goodrich Pump & Engine Control Systems, Inc. Multi-mode shutdown system for a fuel metering unit
US20050100447A1 (en) * 2003-11-11 2005-05-12 Desai Mihir C. Flow control system for a gas turbine engine
EP1934478B1 (en) * 2005-10-06 2009-01-28 Joma-Hydromechanic GmbH Vane cell pump
DE102006018124A1 (en) * 2006-04-19 2007-10-25 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Adjustable rotary pump with wear reduction
US8079826B2 (en) * 2007-01-19 2011-12-20 Magna Powertrain Inc. Vane pump with substantially constant regulated output
CA2664067C (en) 2008-04-25 2016-09-27 Magna Powertrain Inc. Variable displacement vane pump with enhanced discharge port
US20100296956A1 (en) * 2009-05-20 2010-11-25 Hoehn Richard T Variable displacement pumps and vane pump control systems
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
KR200483681Y1 (en) 2015-04-03 2017-06-14 김제봉 pipe clamp with fire material and refractory material
IT201600082659A1 (en) * 2016-08-04 2018-02-04 Vhit Spa Positive displacement pump vane
KR200487404Y1 (en) 2016-08-17 2018-09-12 김제봉 pipe clamp with fire material and refractory material
DE102018206450A1 (en) * 2018-04-26 2019-10-31 Volkswagen Aktiengesellschaft Oil pump assembly for a motor vehicle and method for controlling an oil pump

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2142275A (en) * 1937-08-24 1939-01-03 Eclipse Aviat Corp Fluid pump
US2309148A (en) * 1939-09-14 1943-01-26 Wilson Edward Hydraulic motor system
US2318292A (en) * 1941-08-21 1943-05-04 Chandler Evans Corp Fluid pump
US2894458A (en) * 1954-03-01 1959-07-14 Vickers Inc Power transmission
US2929329A (en) * 1956-12-06 1960-03-22 Gen Motors Corp Constant pressure variable displacement pump
DE3333647C2 (en) * 1982-09-21 1986-10-30 Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden, De
SE457010B (en) * 1983-09-17 1988-11-21 Glyco Antriebstechnik Gmbh adjustable smoerjmedelspump
JPS6261797B2 (en) * 1983-08-04 1987-12-23 Nissan Motor
DE4011671C2 (en) * 1990-04-11 1994-04-28 Glyco Metall Werke Adjustable vane pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9314318A1 *

Also Published As

Publication number Publication date
WO1993014318A1 (en) 1993-07-22
EP0620898B1 (en) 1995-08-02
BR9207029A (en) 1995-12-05
DE4200305C2 (en) 1995-06-08
US5484271A (en) 1996-01-16
KR940703971A (en) 1994-12-12
AT125905T (en) 1995-08-15
DE4200305A1 (en) 1993-07-15
MX9300092A (en) 1993-07-01
JPH07502796A (en) 1995-03-23
KR100209862B1 (en) 1999-07-15
ES2078816T3 (en) 1995-12-16

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