CN1791750A - Eccentric screw pump - Google Patents

Abstract

The invention relates to an eccentric screw pump (1) having a stator (2) and a rotor (3), between which material is conveyed from a feed region (4) on the suction side to a discharge region (5) on the pressure side when the rotor (3) is rotated in the stator (2), wherein a rotor head (7) which closes off the discharge region (5) on the pressure side and is fixed to an end face (6) of the rotor (3) and rotates together with the rotor (3) is provided, which rotor head has at least one recess (8) which runs through the head and is arranged in the rotor head (7) in such a way that the recess (8) which rotates in unison with the rotor (3) in the conveying direction (10) opens the pressure-volume region (11, 11') concomitantly and a recess-free rotor head portion (13) in the pressure-volume region (11), 11 ') for a duration of opening that maintains the opposing suction-volume zones (12, 12') sealed closed.

Description

Eccentric screw pump

The invention relates to an eccentric screw pump, which has a stator and a rotor, between the stator and the rotor, when the rotor rotates in the stator, the material is moved from a suction side feed area to a pressure side discharge Material area, wherein, in the discharge area on the pressure side, a pressure-volume area and a suction-volume area opposite are changed and converted between the stator and the rotor as the rotor rotates.

Known eccentric screw pumps of this type comprise a rotor configured as a worm in the form of a high-pitch, deep-threaded round-threaded rod, and a stator with a thread-type internal structure and therefore in the form of a worm housing . Due to the threaded inner structure of the stator, a plurality of axial cavities are formed sequentially from the suction side to the pressure side, and the rotor rotates in such cavities. During the rotation of the rotor, the inner surface part of the stator is in contact with the outer surface part of the rotor. At this time, there is a delivery chamber and an attached sealing area between the inner surface of the stator and the outer surface of the rotor. The rotor rotates in the cavity of the stator , the material in the conveying chamber moves from the suction side to the pressure side along the conveying section.

In document EP 0 713 974, such an eccentric screw pump is known, which enables the continuous conveying of abrasive materials by the rotation of the rotor in the cavity of the stator. In this case, the stator is made of elastic material and rests against the rotor by prestressing, so that the end of the conveying chamber always forms a seal during operation. Abrasive material expelled from the discharge cavity on the pressure side is limited by the existing material in the pressure tube that continues to guide the material, and is pressed against the material pushed behind by the opposite external pressure. This conveying process therefore builds up an internal pressure, in particular relative to the sealing area.

To ensure a secure seal, the higher the external pressure that builds up in the pressure tube, the greater the prestress between stator and rotor must be.

There is a problem here, that is, there is wear on the stator and rotor, especially during conveying material. This wear occurs primarily at the pitch of the stator, which is formed as a cavity seal, starting from the side of the discharge area on the pressure side in the direction of the inlet area on the suction side. The increase in wear leads to a reduction in the delivery power of the eccentric screw pump.

The elastic stator is attached to the rotor by means of prestress. Therefore, high wear may occur between the stator and the rotor due to the presence of materials, and this wear increases with the increase of the pressure. The wear gradually moves from the pressure side to the suction side and destroys the original sealing area. When the internal pressure cannot overcome the external pressure, an interruption of the delivery process will eventually occur.

Therefore, the pressure-dependent conveying of materials in the conveying chamber depends to a large extent on the sealing condition of the sealing area between the stator and the rotor. In order to control the problem of wear disturbances in the sealing area between the outer surface of the rotor and the inner surface of the stator over a longer operating time, an eccentric screw pump in the form of a re-tightenable stator is known, with which a pump is equipped with a certain Clamping plate integral with the stator, or a closeable clamping device that can be manually inserted next to the pump. With this clamping device, the radial compression of the stator as a whole can be carried out slightly or according to the need, under the condition of recognizable wear inside the sealing area, so that the inner surface of the stator can be pressed against the outer surface of the rotor, and at the same time cause the sealing A pristine seal is formed in the area.

Document DE 33 04 751 C2 also describes an eccentric screw pump with a non-retightenable stator, in which the stator tapers from the suction side to the pressure side with the same rotor radial dimensions, or With identical stator dimensions, the rotor has a spiral cross-section that increases from the suction side to the pressure side.

The problem is that both the production and the quality control require a high material, monitoring and personnel investment in both variants and in the case of a combination of the two variants for keeping the seal stable.

In the document DE 202 15 849.7, there is also an eccentric screw pump, which has a non-return valve device that allows abrasive materials to pass beside the discharge area on the pressure side, and belongs to this device. There is also a rigidly fixed stator Lock washer on end face. The end face of the rotor turns on the locking washer, so that a variable pressure-volume and suction-volume seal can be achieved. The lock washer fixed on the stator has two fixed through-holes for material discharge, each of which is equipped with a non-return valve. These two valved through-holes are assigned to the pressure-volume area and suction-volume area occupied by the discharge area of the rotor, and continue when the internal pressure in the respective volume area between the stator and the rotor is greater than that adjacent to the valve. Open when the external pressure inside the pressure tube that guides the material.

The problem here is that this design of the lock washer and valve fastened to the stator requires additional structural elements. After using the eccentric screw pump at least the valve must be cleaned.

The object of the present invention is to provide an eccentric screw pump which is designed in the discharge area for easy installation and maintenance. At the same time, the wear in the sealing area of the stator and rotor, in particular in the pressure area of the pressure-side discharge cavity, should be significantly reduced or greatly reduced. The already short stator and rotor as well as the length of the conveying path should also be further shortened, and the actual conveying performance should be maintained to a large extent over a longer period of time.

This object is achieved by the features of claim 1 . In the case of an eccentric screw pump of the type specified in the preamble of claim 1, a rotor head which closes the discharge area on the pressure side and which is fastened to the end face of the rotor and rotates together with the rotor is provided, said rotor head having at least one through-head recess which, associated with the fixed rotor end face, is arranged in the rotor head in such a way that the pressure-volume region is concomitantly opened with the recess which rotates concordantly with the rotor in the conveying direction, and A void-free rotor head portion keeps the opposing suction-volume region hermetically closed for the duration of the opening of the pressure-volume region.

The rotor head is fastened to the rotor end face by screwing, welding or the like at the back of the rotor head.

The rotor head can be fixed on the rotor end face in such a way that the central axis of the rotor head can coincide with the center of the rotor end face. In this case, the movement of the central axis is a concentric straight line extension, and in the case of mismatch, it will run an eccentric curved trajectory.

The continuous recess is arranged in the rotor head directly laterally close to the end face of the rotor, wherein the dimensions of the recess cross-section are adapted to the pressure build-up in the pressure-volume region due to the rotation of the rotor and the discharge of the material.

The rotor head can preferably be a rotor hole disk with a circular surface. The associated continuous recess can preferably be a substantially bean-shaped elongated hole in plan view in section.

The rotor head is mounted on the rotor end face in such a way that the bore starts from the edge of the bearing rotor end face in the radial direction, with its effective opening cross-section adapted to the pressure generation of the rotor in the pressure-volume area, and enters with the bore start area to the pressure-volume region, and then exit the pressure-volume region with the hole termination region.

The through-going opening of the rotor head can also optionally be made as a radially oriented sector-shaped through-hole or sector-shaped opening starting from the edge of the fixed rotor end face, which is like a slotted hole structure, with them The effective opening cross-section is adapted for the rotor to generate pressure in the pressure-volume region, enter the pressure-volume region, and exit the pressure-volume region after passing through the pressure-volume region.

In order to reduce the pressure to the sealing area in the stator, the rotor head has such a circumferential dimension that the rotor head with its remaining void-free part keeps the suction-volume area formed in the stator opening area sealed each time it rotates .

The rotor is designed as a round-threaded worm with a large pitch and a large thread depth, while the stator is a worm housing that contains the axially successive cavities of a delivery path - at least one suction-side feed cavity and one The discharge cavity on the pressure side, between the inner surface of the stator and the outer surface of the rotor, forms a conveying chamber due to the matching sealing area between the stator and the rotor, when the rotor rotates in the cavity of the stator, the material in the conveying chamber It can move from the suction side feed area to the pressure side discharge area.

A pressure line, which continues to convey the material, can be fastened to the end face of the stator, and the pressure line can be fastened to the stator in a sealing manner by means of at least one support element surrounding the stator and the pressure line.

The invention makes it possible to separate the pressure chamber originally associated with the pressure tube after the pump outlet from the pressure side discharge cavity originally associated with the pump due to the presence of the rotor head or the rotor orifice in the discharge area of the pressure side. After the discharge area on the pressure side has been opened each time the rotor rotates by means of the through gap, a subsequent filling of material is obtained from the intake area on the suction side by rotation of the rotor.

Improvements and other designs are described in the further dependent claims.

The invention is explained in detail by means of an exemplary embodiment with reference to the drawings. The accompanying drawings indicate:

Fig. 1 is a schematic perspective view of a disassembled eccentric screw pump according to the invention, with a rotor head detached from the end face of the rotor and a connectable pressure pipe detached from the end face of the stator,

Fig. 2 The end face of the rotor hole plate with one hole - a schematic top view, the position when the material starts to discharge from the pressure-volume area, the specified rotor-angle α = 0°,

Fig. 3 is a schematic view of the end face of the rotor orifice disc with holes - the top view, the position where the material is discharged from the pressure-volume area to the maximum, and the rotor is rotated by one rotor-angle α = 90° according to Fig. 2,

Figure 4 is the end face of the rotor hole plate with holes - a schematic top view, the position where the material is discharged from the pressure-volume area so far, or the position when the material is discharged from the newly formed, relative pressure-volume area, the rotor according to Figure 2 Rotate one rotor - angle α = 180°,

Fig. 5 is a longitudinal sectional view of a shortened eccentric screw pump with a rotor orifice, along the I-I longitudinal line according to Fig. 3 .

In the disassembled schematic diagram of Figure 1, an eccentric screw pump 1 is shown. It has a stator 2 and a rotor 3. When the rotor 3 rotates in the stator 2, the material is drawn between them from the inlet on the suction side. The material zone 4 is moved to the discharge zone 5 on the pressure side. At the same time, a pressure-volume zone 11 and a suction zone 11 and a suction zone 11 are formed between the stator 2 and the rotor 3 in the discharge zone 5 and the volume is changed and converted based on the rotation of the rotor. Into - volume zone 12 .

According to the invention, there is provided a rotor head 7 which closes the pressure-side discharge zone 5, is fastened to the end face 6 of the rotor 3 and rotates together with the rotor 3, and has at least one through-head recess 8 , this recess is arranged on the rotor head 7 in association with the fixed rotor end face 6 in such a way that the recess 8, which rotates in unison with the rotor 3 in the conveying direction 10, opens together with the pressure-volume region 11, while at the pressure - The duration of the opening of the volume 11 keeps the opposite suction-volume 12 hermetically closed.

The rotor head 7 is preferably formed in the form of a rotor disc whose rear face 30 is planar and which is fastened with the rotor head rear face 30 to the end face 6 of the rotor 3 in the form of a worm by screwing, welding or the like. It is the end face of the rotor worm - on. The rotor head 7 is therefore a fixed component of the rotor 3 outside the stator 2 .

In the case of a circular disk front 9 and a circular disk back 30, the rotor hole disk 7 can be fixed on the rotor end face 6 with its disk back 30 in such a way that the central axis 33 of the rotor hole disk 7 is preferably aligned with the The center 28 of the rotor end face 6 coincides, and the center axis 33 extends only in a straight line. However, if the central axis 33 of the rotor hole disk 7 leaves the center 28 of the rotor end face 6, then what is running is not a concentric straight line extension, but an eccentric curved path.

The front side 9 and the rear side 30 can also be oval-shaped with respect to their circumference, pear-shaped or oval-shaped in cross-section, etc., in particular shapes that reduce material consumption can be selected. FIG. 2 illustrates a second type of rotor head 27 (in dashed lines) that reduces material consumption.

What is important is that the gap 8 should be designed in such a way that the suction-volume areas 12, 12' remain hermetically closed during the rotation of the rotor, while the pressure-volume areas 11, 11' open in a manner adapted to the rotor.

The rotor bore plate 7 in FIG. 1 has, as a continuous recess 8 , an elongated hole, preferably substantially bean-shaped in plan view in section.

As also shown in FIGS. 2 to 4 , the elongated holes 8 start directly from the side edges and extend radially into the rotor hole disk 7 next to the end face 6 of the rotor 3 , while simultaneously connecting with the pressure-volume region 11 The pressure build-up and the discharge of the material from the pressure-volume area 11 by the rotation of the rotor are adapted to the size of the bore cross-section in plan view.

The rotor 3 is constructed in the form of a large-pitch, deep-threaded round thread (knurled thread) rod, which acts as a material pusher and acts as a space between the rotor 3 and the stator 2 from the feed area 4 on the suction side to the pressure side. The role of the longitudinal sealer of the conveying section 14 of the discharge area 5. The stator 2 includes three cavities 15, 16, 17 formed axially sequentially and limited by the pitch and depth of the thread—the feed cavity 15 on the suction side, the delivery cavity 16 in the middle, and the discharge cavity on the pressure side. Material cavity 17, at the same time, between the stator inner surface 18 and the rotor outer surface 19, three delivery chambers 20, 21, 22 have been formed due to the sealing area 23, 24 established between the stator 2 and the rotor 3, when the rotor 3 During rotation in the cavities 15 , 16 , 17 of the stator 2 , the material in the delivery chambers 20 , 21 , 22 is conveyed from the intake area 4 on the suction side to the discharge area 5 on the pressure side.

The rotor 3 conveys the material by means of its worm-shaped structure in the axial direction 10 along the conveying path 14 and at the same time passes conveying chambers 20 , 21 , 22 alternately in the discharge cavity 17 in the radial direction relative to the central axis 26 of the pump. This enters into the volume areas 11 , 12 provided for this purpose, formed and opposed to each other, which are part of the pressure-side discharge chamber 17 .

The rotor head 7 that allows the material to pass through the gap 8 is located in the row of the discharge cavity 17 on the pressure side corresponding to approximately "half" of the intermediate cavity 16, similar to the first delivery chamber 20 shown in FIG. In the material zone 5, for better explanation in FIG. 1, the rotor hole disk 7 is separated from the rotor end face 6 in the disassembled schematic diagram, and according to the present invention, when it is fixed on the rotor end face 6 butt against the end face 25 of the stator.

Both the rotor head rear face 30 and the stator end face 25 are planar and each have an angle of approximately 90° with respect to the pump central axis 26 .

The front face 9 of the rotor head can be flat in the case of a disk, but also spherical and/or equipped with at least one profile with wings or other projections to improve the passage and mixing of the material.

The discharge area 5 on the pressure side of the eccentric screw pump 1 comprises the last part of the eccentric screw pump 1 which discharges material, whereas the feed area 4 on the suction side is the first part of the eccentric screw pump 1 which receives material.

The invention thus makes it possible for the material pressed out from the discharge side of the eccentric screw pump 1 to no longer flow back through the imperforate disk part 13 after the pressure-volume zone 5 has been opened on condition of the rotor rotation and the suction-volume zone 12 has been closed. , and will not press against the material pushed or sucked by the rotor 3.

The holes 8 allow the material to pass there without significant resistance, while a reverse flow of the material in the direction of the suction-volume area 12 via the imperforate disk part 13 is prevented.

As a result, a second and final unloading of the sealing region 24 takes place at least in the region of the stator 2 and rotor 3 each time the rotor 3 rotates, resulting in reduced wear.

As shown in FIG. 1 , a pressure pipe 34 facing the front face 9 of the rotor head can be fixed on the stator end face 25 , through which the material is conveyed further.

The pressure line 34 can be fastened to the stator 2 in a sealing manner by means of at least one support element (not shown), which in particular surrounds the stator and the pressure line.

In FIG. 2 , the rotor 3 is situated with its round rotor end face 6 in the suction volume region 12 at an angular and rotational position 28 , in which position the rotor angle is defined, for example: α=0°. The rotor hole disk 7 is mounted on the rotor end face 6 in such a way that the bean-shaped elongated hole 8 covers the pressure-volume region 11 starting from its small portion of the hole start region 35 compared to its effective opening cross section. Corresponding to the pressure in the pressure-volume area 11 due to the rotation of the rotor 3 , the effective cross-sectional size of the elongated hole covering the opening for the pressure-volume area 11 also becomes larger. The remaining and non-slotted disc portion 13 closes off the remainder of the pressure-volume zone 11 and seals off the suction-volume zone 12 depending on the size of the slots 8 . The position of the rotor hole plate 7 relative to the rotor 3 in FIG. 2 is almost the same as the position of the rotor hole plate 7 relative to the stator 2 in FIG. 1 .

In Fig. 3, the rotor 3 is rotated to the central position 28' at an angle α=90°, at which time the bean-shaped elongated hole 8, including the hole start region 35 and the hole end region 36, covers the complete hole cross section Most of the pressure-volume area 11 is thus opened, while the imperforate disc portion 13 also seals the suction-volume area 12 hermetically all the time.

In Fig. 4, since the rotor 3 continues to rotate through an angle of α=90°, that is, a total of 180° has been rotated, the discharge process of the material from the pressure-volume area 11 ends at the central position 28 ". The hole 8 is defined by its hole The terminal zone 36 emerges from the decompressed pressure-volume zone 11. The original suction-volume zone 12 is still hermetically closed by means of the imperforate disk portion 13, but due to the rotation of the rotor, as the pressure-volume zone 11 in Fig. 2 The volume region 11' begins to open in accordance with the rotation of the rotor. The bore 8 enters the established opposite pressure-volume region 11' with its bore start region 35 .

It is also shown in FIG. 4 that the hole 8 as a continuous recess can be formed in the form of another radial sector-shaped opening 32 or sector-shaped notch 31 starting from the end face 6 of the supporting rotor, the opening and the notch respectively Drawn with dotted lines.

In FIGS. 2, 3, and 4, the rotor hole disk 7 shown in top view for reducing the pressure at least into the sealing area 24 of the eccentric screw pump 1 has such a circumferential dimension that the stator opening 27 is located in the rotor hole disk 7. During the rotation, the suction-volume area 12 which occurs at that time is always kept tightly closed.

In FIG. 5 , an eccentric screw pump 1 is schematically depicted in a shortened longitudinal section along the line I-I in FIG. 3 . The rotor bore disk 7 is dimensioned in such a way that it remains within its range of motion during the rotation of the rotor, preferably within the stator housing 29 , that is to say does not protrude beyond the stator housing. The rotor bore disk 7 is fixedly connected with its disk back 30 to the rotor end face 6 . The disk back 30 is planar in the non-perforated part 13 in such a way that it rests firmly against the likewise preferably planar stator end face 25 and forms an angle of approximately 90° with respect to the central axis 26 of the pump. The holes 8 open the passage of the material to the rear pressure tube 26 for the pressure-volume zone 11 . The imperforate disk part 13 keeps the suction-volume area 12 closed of the pressure-side discharge cavity 17 .

In FIG. 5 , according to the invention, only one sealing area 24 of one worm pitch can be formed in the shortest configuration of the stator 2 , while the pressure side discharge area 5 can be directly connected to the suction side feed area 4 . The positional stability of the rotor 3 within the worm pitch is provided by the rotor head 7 resting on the stator end face 25 .

The working principle of the eccentric screw pump 1 of the present invention is as follows:

A metallic rotor 3 (worm) rotates in a stator 2 (worm housing) made of elastic material and seals off the delivery chambers 20 , 21 , 22 on the inner surface 18 of the stator. Through the rotation of the rotor 3 , the materials in the conveying chambers 20 , 21 , 22 are conveyed from the feed zone 4 on the suction side to the discharge zone 5 on the pressure side. This results in a continuous material flow in the stator 2 which leaves the bores 8 of the rotor head 7 in a pulsating manner.

If the material flow is pushed into the pressure-side discharge cavity 17, especially through the delivery chamber 22, then the material within the reduced volume zone 11 is squeezed through hole 8, while the suction-volume area 12 remains closed.

In order to end the discharge process by continuing the rotation of the rotor, the rotor end face 6 reaches position 28 "in which the reduced pressure-volume area 11 is switched to a pressure-volume area 11' completely filled with material, this volume area So far is the suction-volume zone 12. Through the rotation angle of α=180° of the rotor, pressure is generated in the formed pressure-volume zone 11', which pushes the material out of the hole 8 along the rotor. To The pressure-volume area 11 so far is transferred into the newly formed suction-volume area 12' with the rotation of the rotor. The pressure-volume area 11 that has been opened so far is then closed by means of the imperforate disc portion 13 and the suction- Volume area 12'. Therefore, no back pressure will be formed on the existing material in the subsequent delivery chamber 21, and the sealing area 24, 23, especially the last sealing area 24 of the discharge cavity 17 on the pressure side will not be back pressure loaded. On the contrary, through the enlarged suction-volume area 12', a strong suction force is exerted on the subsequent material from the conveying chamber 21.

On the condition that the rotor 3 is switched to the radially opposite volume regions 11, 12 or 12', 11' in the discharge cavity 17 on the pressure side at the two extreme positions 28, 28", by means of the rotor orifice disc 7 of the present invention, in In the discharge cavity 17 there is a switchover between the suction and suction processes of the material, wherein a higher degree of material filling is achieved there by suction of the material into the respective disk-enclosed volume 12 or 12'.

The invention makes possible a shortened conveying section 14 and can involve two "cavity lengths" or a "feed cavity-cavity-discharge cavity" configuration 15-16-17. Optionally, the conveying section 14 can be shortened to one worm pitch of the stator 2 .

By mounting the rotor head according to the invention, in particular the addition of the rotor hole disk 7 on the rear end of the conventional eccentric screw pump rotor and the beneficial possible shortening of already produced eccentric screw pumps with relatively long stators and rotors, Even with a less powerful electric motor, the required transmission power can be achieved, which also saves energy and material.

The increase in delivery pressure is achieved in principle by increasing the prestressing force between the stator 2 and the rotor 3 , a problem that is conventionally solved in the axial plane, for example by means of a clamping housing surrounding the stator 2 .

The problem here is that this increases the energy consumption of the pump drive correspondingly.

In order for the eccentric screw pump 1 according to the invention to operate powerfully even at increased delivery pressures, it is provided that the prestressing force is correspondingly increased with as little axial modification as possible in the radial orientation relative to the central axis 26 .

For this purpose, the radial cross-section can be selectively reduced starting from the rotor end face 6 in the region of the stator 2 with an integral number of pitches corresponding to one revolution of the worm housing thread.

In the case of a rotor 2 with more than one worm casing thread, a radial cross-sectional reduction element (not shown) can be provided for the stator 2 in the region starting from the rotor end face 6 at approximately a distance corresponding to one worm casing thread of the stator 2 .

This radial cross-section reducing element can be constructed and arranged in an annular manner in and/or outside the stator housing 29 as an element system which can be selectively controlled or adjusted in the radial direction by means of an actuator. The radial prestress of the sealing regions 23 , 24 of the stator 2 relative to the rotor 3 can be adjusted stepwise or continuously with this element system, stepwise or continuously.

The invention discloses the possibility, in addition to delaying the wear formation in time, to combine with known retightenable and non-retightenable eccentric screw pumps as well as with known eccentric screw pumps with a set at the end region of the stator. Compared with the complex structure of the one-way valve device, the manufacturing cost can also be reduced.

Table of reference signs

1 Eccentric screw pump

2 stator

3 rotors

4 Feed area on the suction side

5 Discharge area on the pressure side

6 Rotor end face

7 The first rotor head

8 through gaps

9 The front of the rotor head

10 Turn the conveying direction

11 The first pressure-volume zone

11’ second pressure-volume zone

12 First suction-volume zone

12’ second suction-volume zone

13 Rotor head section without slotted holes

14 Conveyor section

15 Feed cavity on the suction side

16 The feeding cavity in the middle

17 Discharge cavity on the pressure side

18 Inner surface of stator

19 The outer surface of the rotor

20 The first delivery room

21 Second conveying chamber

22 The third conveying room

23 The first sealing area

24 Second sealing area

25 Stator end face

26 Central axis of the pump

27 Stator opening

28 When α＝0°, the rotor end face center

28' α＝90° when the center of the rotor end face

28” α＝180° at the center of the rotor end face

29 stator housing

30 Back of rotor head

31 scalloped notches

32 Segment-shaped opening

33 Center axis of rotor head

34 pressure pipe

35 well start area

36 hole terminal area

37 Second rotor head

Claims (18)

1. eccentrie helical totorpump (1), it has a stator (2) and a rotor (3), between stator and rotor, when rotor (3) rotates in stator (2), material is transplanted on the pressure side a material discharge region (5) by the feeding zone (4) from an inspiration side, wherein, in material discharge region (5) on the pressure side, an opposed pressure-volume district (11) and an inspiration-containment volume (12) change along with rotor rotation between stator (2) and rotor (3) and change, it is characterized in that, the material discharge region (5) of a confining pressure side is set, the rotor head (7) that the end face (6) that is fixed on rotor (3) is gone up and together rotated with rotor (3), described rotor head has at least one space (8) that connects head, described space is arranged in such a way in the rotor head (7) explicitly with the rotor end-face of fixing (6), make that going up consistent rotating space (8) with rotor (3) at throughput direction (10) opens pressure-volume district (11 concomitantly, 11 '), and a void-free rotor head part (13) is in pressure-volume district (11,11 ') open the relative inspiration-containment volume of duration chien shih (12,12 ') and keep hermetically closing.

2. according to the eccentrie helical totorpump of claim 1, it is characterized in that rotor head (7) has such circumferential size, that is, rotor head (7) is opened pressure-volume district (11,11 ') when rotating, and the inspiration-containment volume (12,12 ') that remains in stator openings (27) zone is closed.

3. according to the eccentrie helical totorpump of claim 1 and/or 2, it is characterized in that, rotor head (7) is fixed on the rotor end-face (6) with the rotor head back side (30) by bolt, welding or similar mode, wherein, the remaining rotor head back side (30) and stator faces (25) are the planes, and form about 90 a ° angle with the central axis (26) of pump.

4. according at least one eccentrie helical totorpump of aforesaid right requirement, it is characterized in that, the space of described perforation (8) preferably directly is set in the rotor head (7) near rotor (3) end face in the side (6), and, the size adaptation of free cross-section is in discharging material by rotor rotation in from pressure-volume district (11,11 ').

5. according at least one eccentrie helical totorpump of aforesaid right requirement, it is characterized in that, the space (8) of the perforation of rotor head (7) can select to be configured to one preferably from the pass through openings (32) of the sector shape edge, radial directed of fixing rotor end-face (6) or fan-shaped breach (31), it always is adapted to rotor in pressure-volume district (11 with its effective opening section, 11 ') pressure in enters pressure-volume district (11 with producing, 11 '), skimming over pressure-volume district (11,11 ') come out from pressure-volume district (11,11 ') again after.

6. according at least one eccentrie helical totorpump of aforesaid right requirement, it is characterized in that rotor head (7) is a rotor porose disc preferably, and the space of described perforation (8) are preferably a kind of slotted hole that is beans shape in overlooking the cross section substantially.

7. according to the eccentrie helical totorpump of claim 6, it is characterized in that rotor porose disc (7) is fixed on the rotor end-face (6) like this, make the central axis (33) of rotor porose disc (7) can select to coincide with the mid point (28) of rotor end-face (6).

8. according at least one eccentrie helical totorpump of aforesaid right requirement, it is characterized in that, rotor porose disc (7) is installed on the rotor end-face (6) like this, make hole (8) be adapted to rotor in pressure-volume district (11 with its effective opening section, 11 ') pressure in enters pressure-volume district (11,11 ') with sintering, hole (35) with producing, is skimming over pressure-volume district (11,11 ') come out from pressure-volume district (11,11 ') with termination environment, hole (36) again after.

9. according at least one eccentrie helical totorpump of aforesaid right requirement, it is characterized in that the rotor head back side (30) constitute with stator faces (25) plane earth and become about 90 a ° angle with pump central axis (26) respectively.

10. according at least one eccentrie helical totorpump of aforesaid right requirement, it is characterized in that, deviate from the rotor head front (9) of rotor end-face (6) and can select to be the plane, that be ball collar shape and/or to be equipped with the profile that passes through to reach mixed performance that is used to improve material that at least one has the wing or other projection for disc-shaped structure.

11. at least one eccentrie helical totorpump according to the aforesaid right requirement, it is characterized in that, rotor (3) is configured to a worm screw with round thread form of the large screw pitch and the major thread degree of depth, and stator (2) is a worm screw shell, it comprises each cavity (15 that axially constitutes successively of carrying highway section (14), 16,17)-charging cavity (15) and a discharge cavity (17) on the pressure side of at least one inspiration side, wherein, between stator inner surface (18) and rotor outer surface (19), because the sealing area (23) of coupling between stator (2) and the rotor (3), 24) form conveying chamber (20,21,22), when the cavity (15 of rotor (3) at stator (2), when rotating 16,17), conveying chamber (20,21,22) material in can be by feeding zone (4) the migration material discharge region (5) on the pressure side of inspiration side.

12. at least one eccentrie helical totorpump according to the aforesaid right requirement, it is characterized in that, on stator faces (25), can fix a pressure tube (26), continue conveying material by this pressure tube, wherein, described pressure tube (26) can be fixed on the stator (2) hermetically by at least one supporting element that especially surrounds stator and pressure tube.

13. at least one eccentrie helical totorpump according to the aforesaid right requirement, it is characterized in that, can be chosen in the zone of pressure tube (26) and a hold down gag is set on the end face (25) of stator (2) for rotor head (7), in order to strengthen the sealing of the inspiration-containment volume (12,12 ') between rotor (3) and the stator (2).

14. at least one eccentrie helical totorpump according to the aforesaid right requirement is characterized in that, carries highway section (14) preferably to relate to the structural arrangements (15-16-17) of two cavity lengths or a kind of " charging cavity-cavity-discharge cavity ".

15. at least one eccentrie helical totorpump according to the aforesaid right requirement is characterized in that, carries highway section (14) to shorten to a pitch worm of stator (2), wherein rotor head (7) especially helps the position stability of rotor (3).

16. at least one eccentrie helical totorpump according to the aforesaid right requirement is characterized in that, in the zone of stator (2), to be equivalent to a preferred integer spacing of a worm screw outer casing screw that changes, (6)s can be selected radial cross section is dwindled from rotor end-face.

17. eccentrie helical totorpump according to claim 16, it is characterized in that, under rotor (2) has situation more than a worm screw outer casing screw, with about one spacing that is equivalent to a worm screw outer casing screw of rotor (2), (zone of 6)s is that stator (2) sets a reduced cross-sectional element radially from rotor end-face.

18. eccentrie helical totorpump according to claim 17, it is characterized in that, described reduced cross-sectional element radially in stator casing (29) and/or outside be constructed and arranged to an element system in the ring set mode, this element system can be selected to be controlled and maybe can be adjusted in radial direction by actuator and can change, and, utilize this element system to regulate the radially prestressing force of stator (2) step by step or continuously according to discharge pressure given in advance with respect to the sealing area (23,24) of rotor (3).

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