WO2009012877A1

WO2009012877A1 - Rotary cylinder rotary slide positive-displacement pump

Info

Publication number: WO2009012877A1
Application number: PCT/EP2008/005512
Authority: WO
Inventors: Werner E. Friedrich
Original assignee: Friedrich Werner E
Priority date: 2007-07-20
Filing date: 2008-07-05
Publication date: 2009-01-29
Also published as: EP2179182A1; EP2179182B1; DE202008017328U1; DE102007034051A1

Abstract

The rotary cylinder rotary slide positive-displacement pump described here makes it possible for three of four chamber walls to co-rotate during the pumping process. Said three chamber walls thus move together with the pump fluid through the working chamber. The result of this and the design of the pump lead to a favourable energetic and volumetric efficiency. The reduced friction reduces the energy requirement for the pumping work. The inner walls, which are smooth and solid on all sides, of the working chambers allow the pump fluid to be conveyed in a gentle manner. This technology provides fewer wear surfaces for abrasive substances. The pumping volume per rotation is greater than the volume of the pump chamber. The pump is of compact design. It is self-priming and capable of dry running. It reaches high pressures which can be kept constant. In contrast to many conventional pump types, no drive shaft leads through the pump chamber. The sum of the properties of this pump technology and the favourable conditions for further technical embodiments make this product suitable as a process pump in industrial applications.

Description

Rotary Cylinder Rotary Vane Displacement Pump Description

State of the art

Since the beginning of industrialization, vane and vane pumps have been used successfully and to the satisfaction of users and manufacturers for the most diverse applications. The increasing energy shortage and the associated ever-increasing energy prices are forcing the industry today to make ever more stringent checks on the energy balance of all areas of their business. This also includes the pump technology and the pump units used there, which represent a significant share of energy consumption and the associated costs for many companies.

Technical suggestions for improvements in rotating systems can be traced worldwide over many years. Examples of this are u.a. US 1,712,935 (1926), DE 451,285 (1927), US 4,553,916 (1985), JP P 61-271934 (1986), DE 3738484 C2 (1987). Nevertheless, the diversity of parts and technically difficult-to-implement solutions have not been able to bring any success to many such techniques. The patents US Pat. No. 1,712,935 and US Pat. No. 4,553,916 as well as DE 101 03580 B4 and DE 101 02852 C2 disclose technical features which have hitherto come closest to the subject-matter filed here.

Object of the invention

The aim of the new development was primarily the further improvement of the energetic and volumetric efficiency of that rotating pump system, as described in the German patents DE 101 03 580 B4 and DE 101 02 852 C2. If it is possible to rotate a third pump chamber wall in addition to the two rotary cylinders (= two pump chamber walls), then the result must allow a further reduction of the friction work and also a gentler conveying. In addition, if the pump is driven by the outer rotary cylinder, then the cheaper translations achieved in this way have further advantages in addition to the structural advantage that z. B. a passage of the drive shaft through the pump chamber can be avoided. The design of an improved pump technology should also be suitable for industrial use as a process pump beyond. A construction example of the rotary cylinder displacement pump according to the invention The technical solution of the new objective of the invention is achieved by the features formulated in the patent claims.

In a pump housing (03) two rotating cylinders (01 + 02) are mounted. The hollow outer rotary cylinder (01) with a diameter slightly smaller than the cylindrical pump housing (03) finds its bearing on a first level in the inner side rounding (04) of this pump housing (03). The inner rotary cylinder (02) is mounted with its round flange (05) on a second level in a in the rear wall (06) of the pump housing (03) applied cylinder pot (07) so that this second inner rotary cylinder (02) in each rotational position Sealing line (08) with the inner circumferential surface (15) of the outer rotary cylinder (01) forms. A rotary valve (09) is articulated on a pivot (10) fixedly but movably on the inside (15) of the outer rotary cylinder (01) and at the same time in the inner rotary cylinder (02), this centering, slidably mounted. This bearing (11) centrally through the inner rotary cylinder (02) divides this rotary cylinder (02) into two symmetrical parts (02a + 02b), with a view similar to that of two half-moons reflecting. The advantageous properties sought with the further optimization of this pump technology required some relevant changes. Thus, the rotary valve displacer (09) fixed to the rotary joint (10) of the outer rotary cylinder (01) has been divided into two such that the one part (09a) is movably but firmly connected to this rotary joint (10) as before. Also pass through the two parts of the rotary valve (09a + 09b) in the middle of the inner rotary cylinder (02). If such a pump is driven via the outer rotary cylinder (01), then this rotary cylinder (01) takes the rotary slide valve (09) and at the same time the inner rotary cylinder (02) forcibly guided along. The two rotary slide parts (09a + 09b) can by the articulation (10) to the outer rotary cylinder (01) and by their displaceable mounting by the inner rotary cylinder (02) on the one hand during one revolution constantly changing angular positions to the outer rotary cylinder (01) smoothly balance and at the same time ensure the necessary continuously changing Diameter of the rotary valve (09) in each rotational position. For the turn to the hinged rotary slide part (09a) slidably mounted other rotary slide part (09b) now always passes through the open to both sides rotary valve bearing (11) of the inner rotary cylinder (02) through to the opposite inner chamber wall (15) of the outer rotary cylinder ( 01). It is obvious that this displaceably mounted second rotary slide part (09b) must receive a forced guidance if its sealing function on the inner cylinder wall (15) of the outer rotary cylinder (01) is to be ensured in each rotational position. For a technical solution was found that can contribute two benefits to improve the efficiency of the pump.

Thus, a cylinder cover (16) mounted coaxially rotatably in an edge groove (13) of the outer rotary cylinder (01) closes the working chamber (12) located between the two rotary cylinders (01 + 02) towards this side. This rotatable cylinder cover (16) has on the inner side towards the working chamber (12) a guide pin (17). This Führungszapfβn (17) engages in a bore (18) in the displaceable part (09b) of the rotary valve (09) and is thus taken from this rotary slide part (09b). The drehverschiebliche cylinder cover (16) in turn holds the sliding rotary slide part (09b) in this way in each rotational position at a defined distance from the inner cylinder wall (15) (= working chamber wall) of the outer rotary cylinder (01).

Also, the cylinder cover (16) mounted on the outer rotary cylinder (01), guided by the displaceable rotary slide part (09b), rotates with the rotary cylinder (01) in a rotationally displaceable manner. The friction of the displaceable rotary slide part (09b) on the cylinder wall (16) is largely reduced to a limited partial surface of this co-rotating cylinder wall (16) as the rotary slide part (09b) by the inner rotary cylinder (02) during one revolution, the outer rotary cylinder (01 ) and then runs after.

These aspects of friction work considered here take into account a situation in which sealing material is used for sealing. If the seal is controlled by slot widths, other necessities arise accordingly. The pump is driven by the outer rotary cylinder. This results in more favorable gear ratios compared to a drive on the inner rotary cylinder. However, as described in the earlier patents, this technique also allows for drive via the inner rotary cylinder.

Due to the design of the rotary valve displacer (09), the angular position shown in Fig. D / Fig. 7 input and output closed simultaneously. In this position, the largest possible suction volume per half turn is reached. This intake volume is thus conveyed twice in one complete revolution. The delivery volume of a complete revolution thus significantly exceeds the total volume of the working chamber. Achievable benefits

From the above description, the achievable with the improved design of the Drehzylin- vane rotary displacement pump advantages are traceable. The technique described here makes it possible to transport three (14, 15, 16) of the four working chamber sidewalls together with the pumping fluid through this working chamber. The friction work of the rotary valve displacer of the pump still to be performed on the co-rotating side walls is reduced to a minimum. These three of four walls of the pump chamber (12), that is, in each case a part of the outer circumferential surface (14) of the inner rotary cylinder (02), the inner circumferential surface (15) of the outer rotary cylinder (01) and the drehverschieblichen rotary cylinder side cover (16) of the rotary cylinder (01), constantly function-tight, this is during one entire revolution of the pump, the pumping fluid and the working chamber (12). During the pumping process, the pumping fluid is surrounded by three fixed side walls and quasi "carried" gently through the chamber, not squeezed through, as in some other pumping techniques.

The reduced friction surfaces mean that fluids containing abrasive substances have less friction and thus less frequent process interruptions due to the necessity of having to renew abraded consumed functional parts. The rotary valve displacer (09) must reduce friction losses only on the rear wall (06) of the pump housing (03) and a portion of the drehverschieblichen cylinder ceiling (16) (= working chamber wall) of the outer rotary cylinder (01) and the partially swept lateral surfaces of the two rotary cylinder 01, 02).

Since the technical solutions of the pump described here also make it possible to dispense with a drive shaft through the pump housing or through the pump chamber, there are more conceptual design options and greater freedom in the formation of individual functional parts.

Thus, the structural concept of this pump allows the non-contact rotation of the functional fluid-contacting parts and also the non-contact adjustment of the rotating parts to the flat (06 + 16) and cylindrical (14 + 15) side walls of the working chamber (12). The pump is self-priming and dry-running. The easy access from all sides into / into the interior and exterior of the pump allows for additional technical equipment, such as heat input and output, uncoupling the pump from the production cycle in ongoing production, replacement of pump parts without interrupting production.

The pump can be built robust. As a result, higher pressures can be achieved. Also, higher speeds should be possible.

The housing can be hermetically sealed off. A magnetic coupling can also be set up well in conjunction with the outer rotary cylinder (01). If some pump fluids are sensitive to a near magnetic field, this technique could also be used to solve a magnetic coupling at a necessary distance from the pump chamber (12) in a technically reasonable manner.

image Description

Sheet 1 - shows two views (Figures 1 and 3) and a sectional drawing

(Fig. 2) of the empty pump housing.

The sectional view according to FIG. 2 corresponds in each case to the sectional lines SL of FIGS. 1 and 2. FIG. 1 illustrates the view of an observer in the empty pump housing, as shown in the sectional drawing FIG. 2, seen from the right edge of the image into the housing.

The view from the picture left on the sectional drawing gem. FIG. 2 corresponds to the rearward exterior view of the housing as shown in FIG. 3. FIG.

Sheet 2 - In Fig. 4, the movements of the functional parts of the pump in the

Rotation traceable.

The displaceable cylinder ceiling (16) guided in the peripheral groove (13) of the outer rotary cylinder (01) is missing in order to clear the view into the interior.

Sheet 3 - Figures 5 and 6 and their sections Fig. 5a and 6a

Embodiments of the co-rotating Arbeitskammerseiten- wall, the cylinder ceiling (16) and (16a).

Sheet 4 - Fig. 7 illustrates the all-round smooth working chamber walls for a gentle promotion of the pumping fluid. In this position, the input and output are closed. The largest possible pump volume has been reached. Continuing to rotate opens the outlet and the pumping process starts again.

The drive shaft does not have to be guided through the working chamber. The drive takes place via the cylindrical ISs by means of mechanical or magnetic coupling. Bezugszeichenlistθ

01 Outer rotary cylinder

02 - Inner rotary cylinder

03 - Pump housing

04 - Bearing of outer rotary cylinder 01

05 - Round flange of inner rotary cylinder 02

06 - Rear wall of the pump housing

07 - Cylinder pot (bearing of the rotary cylinder 02)

08 - Dichtliniβ

09 - rotary valve displacer

09a - Rotary slide part hinged

09b - Rotary slide part displaceable

10 - Swivel / Gel enkbdzen

11 - Bearing in the rotary cylinder 02 for rotary valve 09

12 - working chamber

13 - edge groove in outer rotary cylinder 01

14 - Outer lateral surface of the inner rotary cylinder 02

15 - Inner circumferential surface of the outer rotary cylinder 01

16 - Movable cylinder ceiling

16a - Cylinder cover fixed on rotary cylinder 01

17 - guide pin on cylinder ceiling 16

18 - hole in rotary valve part 09b

19 - Pipe flange

20 - coupling part

21 input channel

22 - output channel

SL - cutting line

Direction of movement of the pump parts

- Flow direction of the pumping fluid

Claims

claims

1. Drehzylinderdrehschieberverdrängerpumpe with a housing (03) and mounted on a first level hollow outer rotary cylinder (01) having a first diameter and a in and to this outer rotary cylinder (01) on a second plane parallelachsig mounted inner rotary cylinder (02) with a second smaller diameter, with a working chamber (12) between the outer (01) and the inner (02) rotary cylinder, with input (21) and output channels (22) in this working chamber (12), which inner rotary cylinder (02) with the inner cylinder wall (15) of the outer rotary cylinder (01) between the inlet (21) and outlet channel (22) forms a sealing line (08) and which inner rotary cylinder (02) has a center diagonal continuous to two sides open storage (11), in which bearing (11) a rotary valve displacer (09) is mounted and guided, finally with a to the outer rotary cylinder (01) coaxially guided and with this rotating cylinder cover (16) in the function of a co-rotating side wall of the working chamber.

2. Drehzylinderdrehschieberverdrängerpumpe with features according to claim 1, characterized by a on the inner cylinder wall (15) of the outer rotary cylinder (01) hinged rotary valve displacer (09).

3. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 2, characterized by an at least two-part rotary valve displacer (09).

4. Drehzylinderdrehschieberverdrängerpumpe having features of claims 1 to 3, characterized by a two-part rotary valve displacer (09) consisting of a first at a rotary joint (10) on the inner cylinder wall (15) of the outer rotary cylinder (01) hinged rotary slide part (09 a) and one to this first articulated rotary slide part (09a) in turn displaceably mounted second rotary slide part (09b).

5. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 4, characterized by a co-rotating cylinder cover (16) which rotatably rotatable to the outer rotary tumbler (01) and can be performed.

6. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 5, characterized by such a drehverschiebliche cylinder cover (16), preferably stored and guided in an edge groove (13) of the outer rotary cylinder (01) and / or otherwise coaxial with the outer rotary cylinder (01) out.

7. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 6, characterized by a cylinder ceiling (16), which can forcibly guide the sliding rotary slide part (09b) with a guide technology.

8. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 7, characterized by a drehverschiebliche cylinder cover (16), which preferably engages with a guide pin (17) in a bore (18) of the displaceable rotary slide part (09b).

9. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 8, characterized by a displaceable rotary slide part (09b), which can forcibly guide the drehverschiebliche cylinder cover (16) with a guide technology.

10. Drehzylinderdrehschieberverdrängerpumpe with features of claims 1 to 9, characterized by a displaceable rotary slide part (09b) which engages with a guide pin in a bore of the drehverschiebliche cylinder ceiling (16).

11. Drehzylinderdrehschieberverdrängerpumpe having features of claims 1 to 10, characterized by a with the outer rotary cylinder (01) fixedly connected and synchronously mitrotierende cylinder ceiling (16 a) in the function of a co-rotating side wall of the working chamber and a corresponding part of a magnetically coupled or by others Technic coupled drive.