WO2015124134A1

WO2015124134A1 - Rotary vane pump

Info

Publication number: WO2015124134A1
Application number: PCT/DE2015/000067
Authority: WO
Inventors: Andreas Blechschmidt
Original assignee: Nidec Gpm Gmbh
Priority date: 2014-02-22
Filing date: 2015-02-12
Publication date: 2015-08-27
Also published as: DE102014002524B3

Abstract

The invention relates to a rotary vane pump comprising a rotor which is mounted in a pump housing and is driven by a shaft, multiple vane plates which are mounted in the outer circumference of said rotor in a radially movable manner, and an outer casing which surrounds the rotor and the vane plates and is arranged directly in the pump housing. The aim of the invention is to develop a novel rotary vane pump which ensures an optimal, complete filling of the pump chambers already in the rotational speed range from approximately 0 rpm to 400 rpm while having a simple structural design and being simply and inexpensively produced and which also operates in the range of high rotational speeds of up to 8,500 rpm in an optimized manner with respect to wear, without requiring maintenance, and with a high degree of reliability and efficiency. The rotary vane pump according to the invention, said rotary vane pump comprising guide needles (12) which are decoupled from the vane plates (5) in a forcibly guided manner and which are forcibly guided in guide grooves (13) arranged on both sides of the rotor (3) in the end face(s) of the pump housing (1) and/or the pump housing cover(s) (9), is characterized in that a stroke ring (17) is floatingly mounted in each of the guide grooves (13), which are filled with a pumping medium, and each stroke ring (17) has a track (18) and a collar (19). The stroke needles (12), which are also being guided in the bearing grooves (4) at the same time, circulate radially on the tracks (18) of the stroke rings (17) and are simultaneously guided in an axial manner on the collar (19) of the stroke rings (17).

Description

Vane pump

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 jacket.

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 presser" were used in the prior art.

Thus, feathers arranged under each wing have long been described in the prior art, which are connected to each other, or as a in Closed annular coil spring, or may be formed as a rubber elastic O-ring.

The main disadvantage of these designs is that, especially for small vane pumps with very thin-walled wing plates such solutions require a very high manufacturing and assembly costs to ensure reliable operation.

Furthermore, in the prior art designs are described above, in which act on the inner wing edge hydraulic piston.

Such solutions generally require a very high manufacturing and assembly effort, which increases progressively with increasing 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 cross-over, with their narrow sides, in intersecting guide grooves adjacent pump impeller pairs, or even thin, connecting the opposite wing bolts are used to ensure, for example, even at low speeds, the wings on the outer shell.

Thus, EP 0 466 581 B1 discloses a solution in which the opposing wings cooperate in pairs with one another.

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

In this case, all these solutions, in which the opposing wings always work opposite to each other, can not be used in conjunction with a double-acting vane pump, as in double-acting vane pumps, two pump chambers on the periphery of Impeller are arranged offset by 180 ° to each other, and therefore the impeller on the opposite wing arranged necessarily always at the same time either completely "extended" or completely "retracted" must be.

All these solutions, in which the opposing wings always work in pairs together and opposite to each other, require a high manufacturing and assembly costs and also limit the same time the number of rotor blades to be arranged strongly, so that for example in the solution according to EP 0 466 581 B1 the number of wings is limited to a multiple of the number 4.

From DE 102 02 721 A1 a further 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 DE 10 2005 007 603 A1 a vane pump is known, which achieves an accelerated pressure build-up in the start-up phase, that the wings and the cam ring are at least partially magnetically formed and arranged to each other so that they attract each other and so already at ensure very low speeds between the front of the wing and the outer sheath a secure seal.

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

From DE 10 2004 051 561 A1 a vane pump is also known, in which the slots are arranged in the rotor such that at least a part of the inertial force of the wings 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 takes place.

The main disadvantage of these designs is that especially for small ones, e.g. In the case of small double-action vane pumps due to the low mass of the wing plates, a faster extension of the wings in the "very" lower speed range, that is starting at 0 U / min, can not be guaranteed.

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

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 pressurization 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.

In the prior art are further described, for example, in GB 235 095 A, US 3,904,327 and US 6,070,409 A vane pumps with protruding beyond the edge of the wing plates pins with / without guide rollers, which by means of mechanical positive guidance to ensure a minimal Flügelkopfspiels on both sides of the wing plates in guide grooves, that are guided by a constant contact in the pump housing, while ensuring both an inward, as well as an outward lifting function. These solutions build on the one hand because of the used in GB 235 095 A and US 3,904,327 A wing guide rollers inevitably very large, and also require due to the storage of the wing guide rollers high production costs (which increases disproportionately with smaller size of the pump).

For example, as a result of the constant "mechanical frictional contact" in the bearings of the guide rollers in this solution according to GB 235 095 A and US 3,904,327 A with increasing speed disproportionately increasing friction losses on a decreasing with increasing speed overall efficiency of the vane pump Episode.

In addition, the guide rollers restrict the number of rotor blades to be arranged on the rotor with decreasing pump size.

All the above-mentioned solutions according to GB 235 095 A, those according to US 3 904 327 A and those according to US 6 070 409 A are very susceptible to wear, so also with respect to the solid particles entrained by the conveying medium.

WO 2007/062 116 A1 discloses an internal combustion engine, a rotary internal combustion engine, based on the mode of operation of a double-stroke vane pump. In this solution, movable vanes are arranged in a rotor with radial slots.

The movement of each of the wings is arranged by two pairwise on both sides of the opposite side edges of each wing, in conjunction with a guide ring acting, ie controlled inside and outside of a guide ring, wing guide roller pairs controlled. On the guide ring itself lie on the inner track larger roles, and on the outer web smaller roles of the respective wing guide roller pairs. These wing guide roller pairs arranged on each side of each of the wings control the extension and retraction of the wings, and in turn have, inter alia, the disadvantageous effects of wing guide rollers which have already been explained in connection with GB 235 095 A and US 3 904 327 A. In particular, in small, such as small double-acting vane pump occur in the 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 the "start speed" of such pump strong "after down restrict ".

Therefore, WO 2012/041 283 A2 has proposed a solution for pumps with relatively low drive speeds, which has proven itself particularly in the drive speed range from 20 rpm to 3,000 rpm.

In this solution, the guide elements of the wing plates are no longer connected to the wing plates, but as both sides of the wing plate width and the rotor superior Hubnadeln, "free" adjacent, the Flügelplatteninnenkanten the slidably mounted in the bearing grooves of the rotor wing plates, ie decoupled from the wing plates, On both sides of the rotor guide grooves are arranged in the end faces of the pump housing to the faulty working cycle leadership of Hubnadeln.

The guided in both the guide grooves and at the same time in the bearing grooves Hubnadeln ensure, at, with their Flügelplatteninnenkanten to the Hubnadeln, adjacent wing plates, that the wing plate outer edges abut the outer shell of the pump working space. The guide grooves are via oil holes with the pressure side of the pump, i. associated with the print kidneys.

This solution presented in WO 2012/041 283 A2, with a simple structural design, and with simple cost-effective production and assembly, even with small double-acting vane pump optimal, complete filling of the pump chambers even in the speed range of 20 U / min to 400 U / min , operates in the speed range up to 3,000 rpm maintenance-free, with high reliability and high pump efficiency. However, in the range of higher speeds, ie in the range of 3,000 rpm to 8,500 rpm, it has been found, in particular in the context of endurance tests with a longer service life in this speed range, ie an operating time of more than 2,000 hours, that the lifting needles, in particular For pump housings made of diecast aluminum, visible wear marks are left in their guide grooves, especially in areas where the blade stroke direction changes, even if these areas have already been optimized for stroke dynamics.

The object of the invention is now to develop a vane pump, which eliminates the aforementioned disadvantages of the prior art, and with a simple design and simple cost-effective production and assembly, even with small double-acting vane pump optimal complete filling of the pump chambers already in the speed range of close to 0 rpm to 400 rpm, and at the same time also works in the area of higher speeds of up to 8,500 rpm wear-optimized, maintenance-free and 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. 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 six 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 six figures. It shows:

1 shows the exploded view of a double-acting vane pump according to the invention,

FIG. 2 shows the component cam ring 17 shown in FIG

Top view,

FIG. 3 shows the component cam ring 17 shown in FIG. 2 in section at A-A in the side view;

FIG. 4 shows the component shown in FIG

Pump housing cover 9 in plan view,

FIG. 5: the component shown in FIG

Pump housing cover 9 in section at B-B in side view,

FIG. 6 shows the detail X of FIG

Pump housing cover 9 in the side view.

FIGS. 1 to 6 show an exemplary embodiment of a double-acting, small vane pump according to the invention with a rotor 3 driven in a pump housing 1, a plurality of wing plates 5 radially displaceable in bearing grooves 4 of the rotor 3 with wing inner edges 6 and wing outer edges 7 and an outer jacket 8 surrounding the rotor 3 and the wing plate outer edges 7, a pump housing cover 9 being arranged on both sides on the end faces of the pump housing 1. On both sides of the rotor 3 of the double-acting, small vane pump are two mutually offset by 180 ° suction cups 10 and each of these Saugnieren 10 offset again two pressure kidney 1 1 arranged.

In the bearing grooves 4, the wing plate inner edges 6 of the wing plates 5 are "freely" adjacent, i.e. decoupled from the respectively adjacent wing plate 5, both sides of the wing plate width and also the rotor 3 superior Hubnadeln 12 arranged.

In the front side of the pump housing 1 arranged pump housing cover / n 9 guide grooves 13 are arranged.

These guide grooves 13 are connected to the pressure side of the pump, i. via pressure holes 14 and / or Druckführungsnuten 15 directly or indirectly connected to the / the Druckniere / n 1 1.

Essential to the invention is that in each case a lifting ring 17 is mounted floating in the filled with conveying medium guide grooves 13.

According to the invention is also that each cam 17 has a raceway 18 and a collar 19, and that at the same time guided in the bearing grooves 4 Hubnadeln 12 radially on the raceways 18 of the lifting rings 17 rotate while axially guided against the collar 19 of the lifting rings 17 ,

The arranged on the raceways 18 of the lifting rings 17 collar 19 is used according to the invention, on the one hand, the axial guidance of the lifting needles 12, but at the same time also to achieve optimum bending and torsional rigidity of the invention 17 Hubringe.

According to the invention, it is also the case that the lifting rings 17 have a geometry adapted to the outer casing 8, which ensures that lifting needles 12 which are arranged centrally in the guide grooves 13 and radially on the raceways 18 of the lifting rings 17 rotate with their wing plate inner edges 6 slide the Hubnadeln 12 adjacent wing plates 5 with their wing plate outer edges 7 on the outer shell 8 with movement play along. It is advantageous that in the filled with conveying medium guide grooves 13 mounted lifting rings 17, with a working cycle s, which, as shown in Figure 6, is calculated from s = s ^ i + s ₂ and in the range of 0.1 mm to 0.5 mm are arranged.

The arrangement of this invention in the filled with conveying fluid guide grooves 13 floating mounted 17 rings surprisingly causes a wear-optimized storage of the lifting needles 12 in the pump housing, so that even with pump housings made of die-cast aluminum in continuous operation of the vane pump at speeds in the range of up to 8,500 rev / min no functionally relevant signs of wear more occur at the lifting needles 12 and / or the lifting needles 12 adjacent components of the vane pump.

From the current point of view, this surprising effect in the areas of the stroke direction change of the wing plates 5, which are always associated with a change in the direction of acceleration, due to a hydraulically damped, minimal dodging (swinging) of floating in the filled with conveying fluid guide grooves 13 17 which minimize the contact load of both the lifting rings 17 as well as the lifting needles 12 when "lifting" the lifting needles 12 on the cam ring 17.

It is also essential to the invention that the lifting rings 17 shown completely in FIGS. 1, 2, 3 and 4 have a geometry adapted to the respective outer casing 8 of the vane pump, which ensures that lifting needles 12 circulate radially on the raceways 18 of the lifting rings 17. with their wing inner edges 6 abutting the lifting needles 12 wing plates 5 with their wing plate outer edges 7 on the outer shell 8 with movement play along.

It is advantageous if the working cycle shown in Figure 6 (s = Si + s ₂ ) of the guide grooves 13 floating mounted lifting rings 17 is 0.1 mm to 0.5 mm, whereby a low-friction, maintenance-free guidance of the lifting needles 12 and a optimal function of the wing panels 5 at high Reliability and high efficiency of the pump is given, which is characterized in particular by the fact that on the one hand at low / low speed, ie in the speed range from greater than 0 to about 400 U / min, by a highly playful leadership of the invention Hubnadeln 12, the wing plates 5 circumferentially be guided so that these wing plates 5 are pressed with their wing plate outer edges 7 never directly to the outer shell 8.

However, as the speed continues to increase, the vanes 5, due to the centrifugal force acting on them, i. "Centrifugal force dependent", pressed against the outer jacket 8.

According to the invention, the guide grooves 13, as can be seen in particular from FIG. 4, are provided with pressure guide grooves 15 in the end face (s) of the pump housing 1 and / or in the pump housing cover 9 arranged on the front side on the pump housing 1 Through hole 16 of the shaft 2 are connected, so that always a reliable, optimal floating storage of the lifting rings 17 is guaranteed even under extreme conditions.

On the one hand a simple production, but also to ensure a high reliability at the same time, it is advantageous if the smallest clearance between the outer radius of the rotor 3 and the outer casing 8 is about 0.05 mm to 0.3 mm.

It is advantageous if, on the one hand, the lifting needles 12 have a minimum hardness of 55 HRC, and the lifting rings 17, on the other hand, have a strength of at least 1 000 N / mm ² , so even at very high speeds as a result of the associated high-frequency vibration loads a reliable wear-optimized circulation of Lifting pins 12 is ensured on the lifting rings 17.

It is advantageous if the lifting ring 17 is made of sheet steel in spring steel grade, hardened and tempered.

As shown in the present embodiment, the lifting needle 12 designed as metal pins and the wing plates 5 of the vane pump are decoupled, even a possible vibration of the wing plate 5 in the slot direction can be compensated to some degree.

The then remaining vibrations are optimally damped by the, in conveying medium filled with guide grooves 13 floating, lifting rings 17, so that in conjunction with the inventive material pairing of lifting needle 12 and cam 17 by means of the inventive arrangement of these components even at very high speeds over long Operating periods high reliability of the vane pump can be guaranteed with minimal maintenance.

In the final assembly state, the embodiment of the vane cell pump according to the invention shown in FIGS. 1 to 6 is pinned in a position-adjusted manner with the positioning pins 20 shown in FIG. 1 and screwed dynamically securely by means of the connecting screws 21.

By means of the solution according to the invention, it is thus possible to develop a vane pump which eliminates the disadvantages of the prior art, and with a simple structural design and simple cost-effective production and assembly, even with small double-acting vane pump optimal complete filling of the pump chambers already in the speed range of close to 0 rpm to 400 rpm, and at the same time also works in the range of higher speeds of up to 8,500 rpm wear-optimized, maintenance-free and works with high reliability and high efficiency.

REFERENCE SYMBOL

1 pump housing

2 wave

3 rotor

4 storage groove

5 wing plate

6 wing inside edge

7 wing outer edge

8 outer jacket

9 pump housing cover

10 suckers

11 print kidney

12 lifting needle

13 guide groove

14 pressure hole

15 pressure guide groove

16 through hole

17 lifting ring

18 career

19 collar

20 positioning pin

21 Connecting screw s working cycle

51 working game at the point 1

52 working game at the point 2

Claims

claims

1. vane pump with a in a pump housing (1) mounted by a shaft (2) driven rotor (3), a plurality of bearing grooves (4) of the rotor (3) radially displaceably mounted wing plates (5) with wing inner edges (6) and wing outer edges (7) and an outer jacket (8) surrounding the rotor (3) and the outer wing edges (7), which is arranged directly in the pump housing (1), in the end face (s) of the pump housing (1), and / or in the pump housing cover / s (9) arranged at the end face on the pump housing (1), arranged suction member (s) (10) and pressure kidney (s) (1) arranged offset therewith, with in the bearing grooves (4) , the Flügelplatteninnenkanten (6) of the wing plates (5) arranged "freely" adjacent, on both sides of the wing plate width and the rotor (3) superior Hubnadeln (12), wherein both sides of the rotor (3) in the / the end of the pump housing (1 ) and / or in the front side of the pump housing ( 1) arranged pump housing cover / s (9) guide grooves (13) for guiding the Hubnadeln (12), wherein the guide grooves (13) via pressure holes (14) are connected to the pressure side of the pump, characterized

- That in the filled with conveying medium guide grooves (13) each have a cam ring (17) is floatingly mounted, and each cam ring (17) has a raceway (18) and a collar (19), wherein at the same time in the bearing grooves (4) guided Hubnadeln (12) radially on the raceways (18) of the lifting rings (17) rotate and at the same time axially to the collar (19) of the lifting rings (17) are guided,

- That the lifting rings (17) have a to the outer jacket (8) adapted geometry, which ensures that centrally in the guide grooves (13) arranged lifting rings (17) and radially on the raceways (18) of the lifting rings (17) rotate lifting needles (12), which rest with their wing inner edges (6) on the lifting needles (12) Sliding wing plates (5) with their wing plate outer edges (7) on the outer casing (8) along with movement play.

2. vane pump according to claim 1, characterized in that the working cycle (S = Si + S2) in the guide grooves (13) floating mounted lifting rings (17) is 0.1 mm to 0.5 mm.

3. vane pump according to claim 1 or claim 2, characterized in that the smallest clearance between the outer radius of the rotor (3) and the outer casing (8) is 0.05 mm to 0.3 mm.

4. Vane pump according to one or more of claims 1 to 3, characterized in that the lifting needles (12) have a minimum hardness of 55 HRC, and the lifting rings (17) have a strength of at least 1,000 N / mm ² .

5. vane pump according to one or more of claims 1 to 4, characterized in that the guide grooves (13) via Druckführungsnuten (15) which in the / the end face / s of the pump housing (1) and / or in the / the front side Pump housing (1) arranged pump housing cover / s (9) are arranged, with the passage bore (16) of the shaft (2) are connected.