WO2000043676A1

WO2000043676A1 - Vane-cell pump or motor

Info

Publication number: WO2000043676A1
Application number: PCT/EP2000/000416
Authority: WO
Inventors: Willi Schneider; Eckhard Schulze; Bernd Hess
Original assignee: Joma-Hydromechanic Gmbh
Priority date: 1999-01-20
Filing date: 2000-01-20
Publication date: 2000-07-27
Also published as: DE19902017A1

Abstract

The invention relates to a vane-cell pump or motor with a rotor (10) supported by a drive shaft (12). Said rotor is eccentrically supported in the rotor chamber (15) of a stator (16) which supports the drive shaft (12). Said rotor chamber comprises an inlet (13) and an outlet (14). The rotor carries on its periphery plate-shaped rotor blades (30) which are radially displaceable in relation to one another at a certain angle distance. The aim of the invention is to improve such a vane-cell pump or motor in such a manner that a flow agent is conveyed already when, at a rotor speed larger than zero or when the rotor starts to rotate, the centrifugal force does not suffice to displace the rotor blades in the rotor to their maximum outer radial position. To this end, the front ends of the rotor blades (30) or a shoulder (57 or 58) projecting therefrom engage, with their side facing away from the peripheral wall (52) of the rotor chamber (15), with a circular guideway (59). Said guideway is provided at the front face of the rotor chamber (15) and coaxially thereto and maintains the rotor blades (30) in a defined position of conveyance.

Description

Vane pump or motor

description

The invention relates to a vane pump or motor with the features explained in the preamble of claim 1.

A vane pump of this type is known (DE 37 39 078 AI).

In this construction, the plate-like rotor blades, which are radially displaceably guided in the pump rotor, are held in a desired conveying position by circular guideways provided on the end face and coaxial to the rotor chamber. The guideways are formed by annular grooves in which the rotor blades engage with radial play with peg-like projections, which protrude from one of the front ends of the rotor blades.

The guideways are formed by the outer, cylindrical groove walls of the annular grooves, against which the peg-like projections of the rotor blades rest during centrifugal force during the rotation of the rotor with their peripheral part facing the peripheral wall of the rotor chamber.

The distance between the peg-like projections of the rotor blades to their outer longitudinal edge facing the peripheral wall of the rotor chamber and the eccentricity of the circular guideways are matched to one another in such a way that the outer longitudinal edge of the rotor blades does not come into contact with the peripheral wall of the rotor chamber during the rotation of the rotor and thus from

CONFIRMATION COPY Frictional heat remains free, which has minimized the friction of such vane pumps.

A disadvantage of this pump design, however, is that the rotor blades only come into contact with the guideways from a certain rotor speed under the action of centrifugal force, and only from this point in time does a chamber seal come about between adjacent rotor blades, which causes a reliable delivery of a gaseous or liquid fluid.

The delivery process of such vane pumps therefore only begins after the maximum radial adjustment of the rotor vanes in the rotor caused by the centrifugal force. Vane pumps of this type can therefore not be used, for example, for the lubricant supply to internal combustion engines in which lubrication is essential even at low speeds.

This is where the invention begins. It is based on the task of improving a vane pump or motor of the type explained in the preamble of claim 1 in such a way that a conveying process already occurs when the centrifugal force is still present at a rotor speed greater than zero or when the vane pump or vane motor starts up is not sufficient to move the rotor blades in the rotor into their maximum outer radial position.

This object is achieved according to the invention by the characterizing features of claim 1.

The construction according to the invention thus ensures that the rotor blades in the rotor, even when it is at a standstill, are in such a radial position with respect to the peripheral wall of the rotor chamber that fluid is conveyed at the beginning of a rotor rotation. In this context, it should be mentioned that a vane pump is already known from US-A-2,225,803, the rotor vanes of which are guided by means of rollers mounted on their vane front ends in respective end grooves of the rotor chamber forming guideways in such a way that the rotor vanes with their outer longitudinal vane edge close to the Circumferential wall of the rotor chamber are held.

In this vane pump, however, the rotor chamber is divided into two subchambers separated from one another by a chamber insert for the inflow and outflow of the fluid, and the guide grooves that control the rotor vanes serve the purpose of only interacting with a partially cylindrical section of the peripheral wall of the rotor chamber when the rotor is turned fully Slide the rotor blades radially inwards over the remaining circumferential area in order to steer them past the chamber insert.

As far as the construction according to the invention is concerned, the guiding of the rotor blades can be made according to claim 2 or 3, wherein due to the reduction in frictional resistance achievable in the latter case, a considerable extension of the service life can be achieved.

The interaction of annular guideways and rotor blades ensures that the latter always remain at a defined distance from the chamber circumferential wall during their circulation. There is thus the possibility of adjusting the gap between the rotor blades and the chamber peripheral wall in such a way that there is no mechanical contact between them and nevertheless sufficient leak protection and thus constant delivery is ensured by the gap width present. A further design variant is the subject of claim 4. In this case, the diameter of the inner guideway can be dimensioned such that the rotor blades are held in the conveying position and by the diameter of the outer guideway

Centrifugal force can be kept in contact or without contact with the peripheral wall of the rotor chamber.

A preferred embodiment of this construction variant is the subject of claim 5.

A further, advantageous embodiment of the invention can consist in that the amount of fluid to be conveyed or put into circulation can be changed at a constant rotor speed.

A vane cell pump or motor of this type, which is adjustable in terms of volume flow, is possible by arranging the rotor chamber according to claim 7. In this case, the bearing of the rotor shaft is decoupled from the stator and this can be adjusted transversely to the shaft axis relative to the rotor in the bearing housing, which can preferably be done continuously.

The rotor setting can be done manually, depending on volume flow, speed or pressure.

In the drawing, exemplary embodiments of the invention are shown in highly schematic form. Show it:

1 shows a cross section through a first embodiment of a vane pump along the line I-I of Figure 2;

Figure 2 shows a section along the line II -II of Figure 1; FIG. 3 shows a cross section through a second embodiment of a vane pump;

Figure 4 shows a section along the line IV-IV of Figure 3;

Figure 5 shows a section along the line V-V of Figure 4;

FIG. 6 shows a cross section of a vane pump according to FIG. 3, which is adjustable in volume flow;

Figure 7 is a section along the line VII-VII of Figure 6;

Figure 8 is a representation similar to Figure 6 for

Illustration of the position of the stator for the delivery rate 0;

Figure 9 is a section along the line IX-IX of Figure 8;

FIG. 10 shows a cross section of a vane pump according to FIG. 1, which is adjustable in volume flow;

Figure 11 is a section along the line XI -XI of Figure 10; and

FIG. 12 shows a representation similar to FIG. 10 to illustrate the position of the stator for the delivery rate zero.

With 10 a rotor is designated, which is rotatably mounted on a drive shaft 12. The rotor 10 is arranged within a rotor chamber 15 of a stator 16 connected to an inlet 13 and an outlet 14, in the end walls 22 and 24 of which the drive shaft 12 is mounted in bearings 26 and 28. With 30 rotor blades are designated, which project radially from the rotor 10 at the same angular distance from one another and have the axial rotor dimension and with their wing end faces 32, 34 together with the adjacent counter end faces 40, 42 of the rotor chamber 15 (FIG. 2) for the tight formation of one of adjacent rotor blades 30 and a circumferential section 44 of the rotor chamber 15 defined delivery cell 46 each form gap seals.

As FIG. 1 shows, the strip-like rotor blades 30 are each guided radially displaceably in a guide slot 48 of the rotor 10 such that they, which cannot be seen from the drawing because of the scale, preferably have a defined radial distance during their rotation with their outer blade edge 50 to the chamber peripheral wall 52 of the rotor chamber 15 and thus remain mechanically contactless with it. The remaining gap width is selected in such a way that sufficient leakage security is guaranteed.

This radial vane setting is accomplished by a vane guide device, of which there is an annular collar 54 and 56 on each counter end face 40, 42 of the rotor chamber 15, the outer circumferential surface of which forms a guide track 59.

The end faces of the rotor blades 30 each overlap one of the annular collars 54, 56 and are constantly in engagement with the outer circumferential surface 59 thereof.

A design variant for the rotor blade control is shown in FIGS. 3-5, wherein parts that correspond to the corresponding parts shown in FIGS. 1 and 2 are identified by the same reference numbers.

Here, the control of the rotor blades 30 is accomplished in that the latter have one each at their ends Wear neck 57 or 58, preferably in the form of a pin, each of which engages with a guide groove 60 or 62, which is assigned to these in the chamber end walls 22, 24 and is concentric with the rotor chamber 15. The outer groove wall 64 (see FIG. 5) can be dimensioned such that the rotor blades 30 bear against the inner circumferential surface 52 of the rotor chamber 15 under the influence of centrifugal force.

Figures 6 to 12 show the vane pumps described above in an embodiment that allows the delivery volume to be changed continuously.

For this purpose, the stator 16 in the housing space 19 of a bearing housing 20 having the inflow and outflow 13 or 14 can be adjusted by the radial path a (FIG. 7), the rotor position for the delivery rate zero being shown in FIG.

In this position, the rotor 16 is located inside the bearing housing 20 in the lowest position according to FIGS. 9 and 12, in which the annular guide grooves 60, 62 and the guide track 59 are in a concentric position to the drive shaft 12. Accordingly, all the rotor blades 30 in the rotor 10 assume the same radial position (FIGS. 8 and 12, respectively).

In its maximally displaced position in the radial direction, the stator 16 in the bearing housing 20 relative to the rotor 10 assumes the position shown in FIGS. 6 and 10, ie the stator 16 is located in the housing space 19 in its uppermost position, in which the feed cells 46 have their largest funding volume.

For the sake of simplicity, an illustration of a one-piece device that enables the stator 16 to be adjusted in the bearing housing 20 has been omitted. The components of the vane pump or vane motor can be made entirely of metal or plastic or a combination of both materials. It is also advantageous for these parts to be paired with plastics or plastic compounds or ceramic or plastic / ceramic compounds.

Such material pairings can be used in particular to reduce the rotating mass of the rotor 10 and its rotor blades 30 in order to achieve further improvements in the area of hydraulic-mechanical efficiency.

Finally, I have the seal between the rotor blades 30 and the mating surfaces of the rotor chamber 14 of the stator 16 interacting therewith in that the rotor blades 30 are equipped with molded sealing lips, by means of which the radial and / or axial seal between the rotor blades 30 and increase the counter surfaces assigned to them accordingly and at the same time minimize the sliding friction between them.

The sealing lips formed on the rotor blades 30, which are not shown in the drawing for the sake of simplicity, can be made of plastic or suitable plastic connections or of rubber or rubber / plastic connections.

Claims

claims

1. Vane pump or motor, with a rotor (10) seated on a drive shaft (12), which in a rotor chamber (15) having an inflow (13) and an outflow (14) of a stator (16) supporting the drive shaft (12) ) is mounted eccentrically and carries the plate-like rotor blades (30), which are radially displaceable at an angular distance from one another on the circumference, the blade ends of which are provided with a circular circular face each in the rotor chamber (15), which is provided coaxially and holds the rotor blades (30) in a defined conveying position Guide path (59) are engaged, characterized in that the front ends of the rotor blades (30) or in each case a projection (57 or 58) projecting from them with the side facing away from the peripheral wall (52) of the rotor chamber (15) on the associated side Guide track (59).

2. Vane pump or motor according to claim 1, characterized in that the rotor blades (30) bear in their radial position defined by the guide track (59) on the peripheral wall (52) of the rotor chamber (15).

3. Vane pump or motor according to claim 1, characterized in that the rotor blades (30) in their radial position defined by the guide track (59) are contactless with the peripheral wall (52) of the rotor chamber (15).

4. Vane pump or motor according to claim 1 or 3, characterized in that each guideway (59) is assigned a further, this surrounding guideway (64) concentrically, which in cooperation with the wing ends or their approaches (57, 58) Holds rotor blades (30) in a radial position defined to the peripheral wall (52) of the rotor chamber (15).

5. Vane pump or motor according to claim 4, characterized in that mutually concentrically assigned guideways are each formed by a groove wall in one of the end walls (22 or 24) of the rotor chamber (15) formed annular groove (60 or 62).

6. Vane pump or motor according to claim 4 or 5, characterized in that the rotor blades (30) in their by the outer guide track (64) defined, outer radial position with the peripheral wall (52) of the rotor chamber (15) are contactless.

7. Vane pump or motor according to one of the preceding claims, characterized in that the rotor chamber (15) having stator (16) within a bearing housing (20) to the drive shaft (12) is arranged radially adjustable.

8. Vane pump or motor according to claim 7, characterized in that the stator (16) within the bearing housing (20) can be adjusted radially as a function of volume flow by means of an adjusting device.

9. Vane pump or motor according to claim 7, characterized in that the radial adjustment of the stator

(16) is speed-dependent.

10. Vane pump or motor according to claim 1 or 2, characterized in that the radial adjustment of the stator (16) is pressure-dependent.

11. Vane pump or motor according to one of the preceding claims, characterized in that the components of the vane pump or vane motor are made of different materials.

12. Vane pump or motor according to claim 11, characterized in that a pairing of plastics or plastic connections is provided for the components of the vane pump or vane motor.

13. Vane pump or motor according to claim 11, characterized in that the components of the vane cell pump or the vane motor are made of ceramic.

14. Vane pump or motor according to claim 11, characterized in that a pair of materials made of ceramic or ceramic compounds and plastic is provided for the components of the vane cell pump or the vane cell motor.