EP2619416B1 - Vane cell pump - Google Patents

Description

The invention relates to a vane pump with a mounted in a pump housing, driven by a shaft rotor, a plurality of radially slidably mounted in the outer periphery of this rotor wing plates and a surrounding the rotor and the wing plates, arranged directly in the pump housing outer shell.

In the prior art, the most varied versions of vane pumps have become known. A disadvantage of vane pumps is generally that in the lower speed range of the pump, i. up to speeds of approx. 400 rpm, the centrifugal force of the blades is insufficient to ensure a secure, tight contact of the blades with the outer jacket.

Therefore, it comes without additional aids in vane pumps of simple design only in the higher speed range to a defined pressure build-up.

However, in order to ensure a concern of the wings on the outer shell, even in the lower speed range of the vane pumps, the most varied "wing-pressing means" have been used in the prior art.

So are in the art for a long time under each wing arranged springs, such as in the DE 2 313 480 A1 described above, but also as in the DE 101 42 712 B4 suggested to be connected together, or even as in the DE 10 2009 037 443 A1 can be designed as a self-contained annular coil spring, or as a rubber-elastic O-ring. The main disadvantage of these designs is that, especially for small vane pumps with very thin-walled wing panels such solutions require a very high manufacturing and assembly costs to ensure reliable operation.

Furthermore, in the prior art, including in the U.S. Patent No. 2,832,293 or in the DE 2 313 480 A1 Designs described above, in which act on the inner wing edge hydraulic piston.

Such solutions generally require a very high manufacturing and assembly costs which increases progressively with increasing reduction of the size of the pump. For small vane pumps with very thin-walled wing panels then such solutions are generally no longer reliable use.

In other designs, as in the DE 29 01 851 A1 vorbeschrieben, intersecting, with their narrow sides, in intersecting guide grooves adjacent pump impeller pairs, or as in the DE 10 2006 038 946 A1 proposed, thin, connecting the opposite wing bolt used to ensure, for example, even at low speeds, a system of wings on the outer jacket.

Also is from the EP 0 466 581 B1 Another solution known in which also the opposite wings in pairs work together.

In this solution after the EP 0 466 581 B1 are arranged projecting through the pump shaft, decoupled from the wings wing tappets, the acting on the wings opposite each other, that the lifting movement is always driven by the wing guide rail of the wing, and by the wing, which is in its movement to the pivot point of the pump axis out, which always in this solution, the respective opposing wing always to each other work in reverse.

All of these solutions, in which the opposing wings always work in opposite directions, can by no means be used in conjunction with a double-acting vane pump, since two double-action vane pumps, two pump chambers on the circumference of the impeller are offset by 180 ° to each other, and therefore the impeller each other arranged opposing wing necessarily always at the same time either completely "extended" or completely "retracted" must be.

All these solutions, in which the opposing wings always in pairs together, and work in opposite directions, require a high manufacturing and assembly costs and also limit the same time the number of rotor blades to be arranged on a strong, ie in the solution after the EP 0 466 581 B1 , the number of wings is limited, here to a multiple of the number 4.

From the US 3 904 327 A Another solution is known in which to ensure a minimum wing head play by means of mechanical positive guidance of the wing, here by the constant contact of two on each side of each wing rotatably mounted on pins, biased by clamping rings guided wing guide rollers, both "on and off "directed lifting function is ensured.

This in the US 3 904 327 A presented solution inevitably builds very large, and also requires due to the storage of the wing guide rollers high production costs (which increases disproportionately with smaller size of the pump).

In addition, this solution is very susceptible to wear, especially against solid particles entrained in the fluid.

At the same time, the guide rollers with a decreasing pump size greatly limit the number of wing plates to be arranged on the rotor.

As a result of the constant "mechanical frictional contact" on the clamping rings and the bearing of the guide rollers occur in this solution after the US 3 904 327 A With increasing speed disproportionately increasing friction losses, which then have a decreasing with increasing speed overall efficiency of the vane pump result. From the DE 102 02 721 A1 another vane pump is known in which the inner edge edges are forcibly guided by a circular guide element such that during the entire revolution of the rotor, the wings abut the outer jacket.

The main disadvantage of these designs is especially in designs with very thin-walled wing panels in the high susceptibility to wear and a resulting reduced reliability.

Furthermore, from the DE 10 2005 007 603 A1 a vane pump has become known, which achieves an accelerated pressure build-up in the starting phase, characterized in that the wings and the cam ring are at least partially magnetically and arranged to each other so that they attract each other and so even at very low speeds a secure seal between the front of the Ensure wings and the outer jacket.

The main disadvantage of these designs is that special materials are required for the blades, and that the rotor is advantageously not magnetic.

From the DE 10 2004 051 561 A1 In addition, a vane pump has become known in which the slots are arranged in the rotor so that at least a portion of the inertial force of the wing is directed in the direction of the slot opening, so that even at the start of the rotor by this additional inertial force, a faster extension of the wings.

The main disadvantage of these designs is that especially for small ones, e.g. in small double-acting vane pump due to the low mass of the wing plates, a faster extension of the wings in the "very" lower speed range, i. during startup, from 0 rpm, can not be guaranteed.

In other designs of the prior art, such as in the DE 10 2004 009 840 A1 , or even in the DE 10 2009 000 155 A1 vorbeschrieben, Hinterflügelkanäle are formed on the rotor, which are connected to one or more different pressure sources and ensure a secure tight contact of the wings on the outer jacket via a hydraulic pressurization of the inner wing edge.

However, this hydraulic pressurization requires in addition to a required minimum wing plate width in addition, that the pump has already built a corresponding fluid pressure, so that the wing plates can be pressed against the outer shell of this pump pressure.

Therefore, these solutions, which are based on a hydraulic pressure application of the inner wing edge not suitable in the start-up phase, from the speed 0 rpm, to significantly improve the delivery characteristics of the pump.

Especially with small ones, such as In small double-acting vane pump, occur in the prior art due to the small width, as well as the low mass of the wing plates and their resulting low inertia, start-up problems that limit the "start speed" of such pump strong "down".

The GB 235,095 discloses the features of the preamble of claim 1.

The object of the invention is now to develop a vane pump, which eliminates the aforementioned disadvantages of the prior art, no new wing materials and no new wing geometries required, and with a simple structural design, with easier cost-effective production and assembly, even with small double-acting vane pump can ensure optimum full filling of the pump chambers already in the speed range from 0 to 400 rpm, and at the same time always maintenance-free, works with high reliability and high efficiency.

According to the invention, this object is achieved by a vane pump according to the features of the main claim of the invention by the wing movement in the lower speed range by inventive, positively driven, of the wing plates (5) decoupled pins, the guide pins (12) is effected, the unpressurized operation on both sides of the Rotor (3) in the present invention in the / the end face / s of the pump housing (1) and / or in the front side of the pump housing (1) arranged pump housing cover / n (9) arranged control grooves, the guide grooves (13) are positively driven, and which, after the pressure has built up and with the speed not only the mass inertial force of the wing plates (5) but also the guide pins (12) was effective, then inside "free" abut the Flügelplatteninnenkanten (6) and thereby the wing plates (5) Depending on the centrifugal force, additionally press against the outer casing (8).

Advantageous embodiments, details and features of the invention will become apparent from the dependent claims and the following description of an embodiment of the invention in conjunction with four drawings for the solution according to the invention.

The invention will now be explained in more detail with reference to an embodiment in conjunction with two figures.

Figur 1:

die Explosionsdarstellung einer erfindungsgemäßen, doppeltwirkenden, kleinen Flügelzellenpumpe von "links";

Figur 2:

die Explosionsdarstellung der in Figur 1 dargestellten, erfindungsgemäßen, doppeltwirkenden, kleinen Flügelzellenpumpe von "rechts";

Figur 3:

die Seitenansicht der in Figur 1 dargestellten, erfindungsgemäßen, doppeltwirkenden, kleinen Flügelzellenpumpe in zusammengebautem Zustand;

Figur 4:

die den Schnitt bei A-A gemäß der in der Figur 3 dargestellten, erfindungsgemäßen, doppeltwirkenden, kleinen Flügelzellenpumpe in zusammengebautem Zustand.

It shows:

FIG. 1:

the exploded view of a double-acting, small vane pump according to the invention from "left";

FIG. 2:

the exploded view of in FIG. 1 illustrated, double-acting, small vane pump according to the invention from "right";

FIG. 3:

the side view of in FIG. 1 illustrated, double-acting, small vane pump according to the invention in the assembled state;

FIG. 4:

the cut at AA according to the in the FIG. 3 illustrated, double-acting, small vane pump according to the invention in the assembled state.

In the illustrations for the embodiment of an inventive, double-acting, small vane pump with a mounted in a pump housing 1, driven by a shaft 2 rotor 3, a plurality of bearing grooves 4 of the rotor 3 radially displaceably mounted wing plates 5 with Flügelplatteninnenkanten 6 and wing outer edges 7 and a the Rotor 3 and the wing plate outer edges 7 surrounding outer shell 8 is shown, wherein on both sides of the end faces of the pump housing 1 pump housing cover 9 are arranged.

On both sides of the rotor 3 of the double-acting, small vane pump are two mutually offset by 180 ° suction cups 10 and to these Saugnieren 10 each offset in turn two pressure kidneys 11 are arranged.

Essential to the invention is now that in the bearing grooves 4, the wing inner edges 6 of the wing plates 5 "free" adjacent, ie decoupled from the respectively adjacent wing plate 5, both sides of the wing plate width and the rotor 3 superior guide needles 12 are arranged, and that these rotor 3 projecting portions of the guide needles 12 on both sides of the rotor 3 in a work cycle provided with guide grooves 13, which here in arranged on the front side of the pump housing 1 pump housing cover / n 9 are arranged such that in both the guide grooves 13 as well as in the bearing grooves 4 guided guide pins 12, as well as at the guide pins 12 with the Flügelplatteninnenkanten 6 adjacent wing plates 5, the wing plate outer edges 7 of the wing plates 5 abut the outer casing 8, wherein the guide grooves 13 are connected to the pressure side of the pump, ie via pressure holes 14 and / or Druckführungsnuten 15 directly or indirectly with the pressure kidneys 11, so that a low-friction, maintenance-free guidance of the guide pins 12 and an optimal Function of the wing plates 5 is given high reliability and high efficiency of the pump.

As part of the development of the present solution, experiments were also carried out, each to connect the entire wing plate 5 fixed with an associated guide element and so the wing plates 5 rigidly guided on the respective wing plate 5 guide elements under duress.

As part of this series of experiments it was found that the guide elements were excited in the guideways to high-frequency oscillations, which were transmitted directly to the wing plates 5. These high-frequency vibrations caused by internal forces, both mechanical and hydraulic, had the result that the guide elements fixedly connected to the wing panels 5 as well as their guideways were destroyed after a relatively short time.

In the solution according to the invention, the guide element is a guide needle 12, in the present embodiment, a metal pin which is decoupled from the wing plate 5 of the vane pump, so that through this inventive decoupling of the guide member of the wing plate 5 a possible vibration of the wing plate 5 in the slot direction can be fully compensated to a certain extent.

Another advantage of the solution according to the invention is also that no special blade plate modifications is required, which means that no changes in the manufacturing technology of the wing plates 5 are required.

Another essential feature of the solution according to the invention is a highly playful leadership of the guide elements, here the guide pins 12 according to the invention in the guide grooves 13, the wing plates 5 only at low speed, i. from 0 to about 500 U / min, run circumferentially, but never press the wing plates 5 with their wing outer edges 7 directly to the outer shell 8.

However, as soon as the rotational speed continues to rise, follow the guide needle 12 due to the centrifugal force acting on these the Flügelplatteninnenkanten 6 and lose contact with the lateral walls of the guide grooves 13, so that they then "free" inside abut the Flügelplatteninnenkanten 6 and the wing plates 5 additionally press "centrifugally dependent" on the outer jacket 8.

Essential to the invention is in this context also that the oil holes 14 frontally "only" segment open into the guide grooves 13, so that due to the inventively provided diameter differences between oil drilling segment and diameter of the guide needle 12 penetration / dropping the guide pins 12 is excluded in the oil holes 14 , so that with high reliability always optimal lubrication of the sliding in the guide grooves 13 guide pins 12 and all adjacent modules is guaranteed. It is also characteristic that the guide grooves 13 are connected via oil guide grooves 15 to the passage bore 16 of the shaft 2 in the end face (s) of the pump housing 1 and / or in the pump housing cover (s) 9 arranged on the end side of the pump housing 1, so that optimal lubrication of all modules can be guaranteed.

It is also essential that pressure pockets 17 are arranged on both sides of the rotor 3 in the end face (s) of the pump housing 1 and / or in the end face / pump housing 1 arranged between the passage bore 16 of the shaft 2 and the guide grooves 13 which are connected via oil holes 14 directly or indirectly with the pressure kidneys 11, and thus ensure that the friction losses are minimized at the rotor wall in continuous operation.

It is also essential that between the pressure pockets 17 and the passage bore 16 of the shaft oil guide grooves 15 are arranged, which cause optimal lubrication of all components is given, so that the friction losses are minimized and always a high efficiency is guaranteed.

REFERENCE SYMBOL

1

pump housing

2

wave

3

rotor

4

bearing groove

5

wing plate

6

Wing plate inner edge

7

Wing plate outer edge

8th

outer sheath

9

Pump housing cover

10

suction kidney

11

pressure kidney

12

guide needle

13

guide

14

oil well

15

oil guide groove

16

Through bore

17

Printed bag

Claims (6)

1. Vane cell pump driven by a rotor (3) on bearings driven by a shaft (2) in a pump housing (1), with several movable radial vanes (5) of the rotor (3) positioned in the bearing grooves (4) with inside vane edges (6) of the rotor (3) and outside vane edges (7) and an outside jacket (8) surrounding the rotor (3) and the outside vane edges (7), which is positioned directly in the pump housing (1), with one/several intake manifold(s) (10) and one/several pressure manifold(s) (11) offset against each other located on the front side(s) of the of the pump housing (1), and/or in the pump housing cover(s) (9) located on the front side(s) at the pump housing (1) and characterized by the fact

   - that the freely adjacent inside vane edges (6) of the vanes (5)-uncoupled from the adjacent vane (5) - are positioned in the bearing grooves (4) and that guide pins (12) are also positioned to protrude over both sides along the width of the vanes and the rotor (3), and

   - that guide slots (13) provided with play are positioned along both sides of the rotor (3) on the front side(s) of the pump housing (1) and/or in the pump housing cover(s) (9) located on the front side(s) of the pump housing (1) in such a way

   - that the guide pins (12) introduced into the guide slots (13) and also simultaneously into the bearing grooves (4) for the vanes (5) adjacent to the guide pins (12) with their inside vane edges (6) are adjacent to the outside jacket (8), and

   - that the guide slots (13) are connected with the pressure side of the pump via oil injection holes (14) either directly or indirectly with pressure manifolds (11) in other words.
2. Vane cell pump according to claim 1, characterized by the fact that the oil injection holes (14) only discharge in the region of the guide slots (13).
3. Vane cell pump according to claim 1, characterized by the fact that the guide slots (13) are connected via the oil supply grooves (15) with the passage hole (16) of the shafts (2) on the front side(s) of the pump housing (1) and/or in the pump housing cover(s) (9) located on the front side(s) of the pump housing (1).
4. Vane cell pump according to claim 1, characterized by the fact that the pressure pockets (17) are positioned on both sides of the rotor (3) on the front side(s) of the pump housing (1) and/or in the pump housing cover(s) (9) located on the front side(s) of the pump housing (1) between the passage hole (16) of the shaft (2) and the guide slots (13).
5. Vane cell pump according to claim 4, characterized by the fact that the pressure pockets (17) are connected via oil injection holes (14) directly or indirectly with the pressure manifolds (11).
6. Vane cell pump according to claim 4, characterized by the fact that oil supply grooves (15) are located between the pressure pockets (17) and the passage hole (16) of the shaft (2).

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