DE19849098A1 - Excentric screw pump for gases as vacuum pump uses one-turn inner rotor rotating without contact inside housing rotor within scoop space. - Google Patents

Abstract

The excentric screw pump consists of a rotating inner rotor (1) housed in a fixed rotor (2) and is so controlled in movement that the inner rotor (1) moves in the scoop space (3) without contact with the housing rotor (2). The inner spindle pump runs dry and the inner rotor is drive at 3000 min <->1. Several scoop spaces can be boxed in sequence between the single-turn inner rotor (1) and the two-turn housing rotor (2) and the inlet or suction side of the scoop space volume exceeds that on the outlet side. The circular endface diameter of the inner rotor and/or the inner rotor piston should be reduced. The scoop space is fitted at the space volume transition points with blow-over or bypass valves on the double-toothed housing rotor so as to connect to the gas outlet and the different endface circles of the inner rotor (1) are so axially related and positioned round the respective centers on the rolling circle that the inner rotor as a whole provides mass to balance the inner rotor movement.

Description

State of the art

Dry-compressing pumps are becoming increasingly important, especially in vacuum technology, because due to increasing obligations in environmental protection regulations and increasing operating and disposal costs as well as increased requirements for the purity of the pumped medium, the well-known wet-running vacuum systems, such as liquid ring machines and rotary vane pumps, are becoming increasingly common dry compressing pumps replaced. These dry compacting machines include screw pumps, claw pumps, diaphragm pumps, piston pumps, scroll machines and roller piston pumps. However, these machines have in common that they still do not meet today's demands with regard to reliability and robustness, as well as size and weight, while at the same time maintaining a low price level. This concerns in particular the very piece-intensive pumping speed range between 10 and 100 m ³ / h, which is currently still clearly dominated by the so-called wet-running vacuum pumps of the liquid ring machines and the oil-lubricated rotary vane pumps.

The object of the present invention is a simple and robust as well as special inexpensive and compact dry compressing vacuum to create pump so that through the dry running How vacuum generation works compared to State of the art, significant progress has been made becomes.

According to the invention, this object is achieved by the features of the claims solved. It will be expedient the area of application of the liquid pumps Eccentric screw pump, also known as the "Mohno" pump called, is modified so that the Be movement of the rotating inner rotor on the drive side of the is specifically controlled that is in the pumpar the accessible internal rotor is always in touch freely moved in and in the two-speed housing rotor consequently at a much higher speed can be driven than has been the case with these "Mohno" pumps as a liquid-conveying machine is known.

This high-speed, internally toothed, precisely controlled and therefore always in the work area without contact working machine is for promotion and compaction used for gases, both as a vacuum pump and also working in the overpressure area, and from then on ver simply called ISP = internal spindle pump.  

A key parameter of this machine is one of them the distance between the two rotor centers, i.e. from the revolve the catchy inner rotor and the fixed two common housing rotor. This center distance is in hereinafter referred to as center distance a. The required non-contact movement of the rotating inner rotor in the fixed housing rotor is now, for example wise through a gear synchronization stage is enough, in which a gear on the by the value a running inner rotor with the pitch circle radius of the axis distance a in an internally toothed gearwheel with exact Rolls twice as large pitch circle.

This type of pump uses mechanical engineering Peculiarity that every point on the pitch circle is one Gear, which according to the gearing law in a gear wheel that is exactly twice as large rolls, always an exact straight line through the middle point of the internal gear on the length of the Internal gear pitch circle diameter describes.

To achieve the desired vacuum-specific, very high compression ratios, a corresponding series connection of the individual closed scooping chambers is realized between the catchy inner rotor and the two-speed housing rotor. The required degree of delivery of this machine is achieved by the significantly higher speed mentioned, which is at least 3000 min ^-1 , but should preferably be chosen to be about twice as large thanks to the non-contact movement.

With the controlled and non-contact in the ladle Movement of the inner rotor is used to achieve it required number of stages as a series connection closed working chambers the slope on the inside rotor and thus also on the housing rotor opposite the be known progressing cavity pumps significantly reduced. The slope describes the degree of rotation of the always circular inner rotor end cuts in rotor longitudinal axis.

According to the invention it is further proposed that the inlet / suction side of this internal spindle pump Scoop chamber volume larger than that on the outlet side Is the chamber volume. To implement this scoop Chamber reduction becomes the circular face Diameter of the inner rotor and / or the slope of the inner rotor reduced. In return, self-ver the housing rotor always made the corresponding change tion at the same longitudinal axis position as well exhibit. This "inner compression" reduces significantly Lich the energy requirement and thus also the occurrence the temperatures during gas production.

The ratio of the inlet / suction side to the outlet sided scoop chamber volume is preferably in Range of values between 3 and 8. This change in Scoop chamber volume takes place in the longitudinal axis of the rotor tion and can be both continuous and jump detained. At these points, the The change in the volume of the scoop is well known Blow-by / bypass valves on the 2-tooth housing rotor provided to arise at higher inlet pressures  relieving excess pressure in the scoop chamber and thus the drive power at higher intake pressures to keep low.

These measures reduce energy consumption may be significant and is below the performance value the well-known rotary vane pumps.

The "Mohno" movement and the internal compression caused by changing the inner rotor end section diameter are shown as examples in the attached FIG. 2:

The points A, B, C and D lie on the pitch circle of the revolving inner rotor gear with the radius a. The This pitch circle is fixed and centered with the inner rotor connected and with the distance a around the housing main axis driven so that the center this pitch circle and thus the inner rotor always on the circular line shown in dotted lines moves. Soon this inner rotor pitch circle rolls precisely in the twice as large internally toothed pitch circle, the is fixedly connected to the stationary housing rotor. This gives the driven and inside-rolling In nenrotor an additional rotation around its own Center axis superimposed so that each point of his Pitch circle each on an exact straight line four times the length of the center distance through the middle point of the main housing rotor axis.

Points A to D extend in the longitudinal direction tion and each have a circular forehead cross-section with a decreasing half  measured value so that the working chamber volume (for position A as a cross-sectional area is exemplary hatched) reduced. This working chamber volume change can preferably additionally by a in the axial direction different longitudinal distance of the individual points, i.e. the slope, are reinforced.

An essential design criterion, especially with regard to the increased speed, is the necessary balancing of the rotating parts. On the one hand, the rotation around the inner rotor axis and on the other hand, the movement around the main housing axis must be taken into account. On the basis of Fig. 2 it is clear that the balancing quality is determined during the rotation about the internal rotor axis of the circular cross sections at the respective centers on the pitch circle, so that balance the through specific design in the relative positioning of the individual NEN face cuts in the axial direction to each other, a Mas of entire unit can be easily reached, but the internal bending stress is unavoidable because the leveling would be quite complex.

When moving around the main axis of the housing rotor, the previously described specifically "Mohno" course of the individual inner rotor center points of the circular cross sections has a favorable effect by the path of each center being exactly halved by the main axis of the housing, so that here, too, in the design satisfactory balance of the entire unit can be achieved. The balancing of the center distance crank body can be safely reached via corresponding equal dimensions ( 19 ) in FIG. 1.

Completed via the series connection of several its chamber volume in the axial direction simultaneous reduction in the size of the chamber and the increased rotor speed is the ge desired compression ratio simply and safely accessible without the "games", ie the flanks distance values between the catchy inner rotor and the two-speed housing rotor made too low must be, so that a sufficient reliability speed and robustness. These game values are preferably in the range between 0.1 and 0.2 mm. The number of cascaded, abge closed working chambers depends essentially on that desired compression capacity and should be larger be as 2, preferably as a vacuum pump in the range between 3 and 6.

It is further proposed that the single-start inner rotor ( 1 ) according to FIG. 1 is preferably made of a different material than the two-start housing rotor ( 2 ) by the material of the inner rotor having a lower thermal expansion coefficient than the material of the housing rotor. Steel is preferably selected for the inner rotor and an aluminum alloy for the housing rotor.

According to the invention it is further proposed that this inner-spindle pump is designed to run completely dry, that is to say neither in the work area nor in the other areas of the machine is the supply of the known resources, such as water or oil, necessary. There is only a one-time, factory before increasing lifetime grease lubrication for storage and teeth, the storage possible as hybrid storage, i.e. ceramic balls in steel rings, and the fixed, internally toothed gear ( 6 ) in Fig. 1 is optionally carried out as a plastic gear.

In any case, however, the synchronization teeth ( 6 ) and ( 7 ) according to the invention must be modified in the following way:
The sliding components in the engagement of the two gear wheels are minimized by limiting the contact between the tooth flanks to the immediate vicinity of the pitch circle. Because the profile overlap also practically goes to zero, the required total overlap is practically realized only via the overlap. Advantageously, who the choice of the orientation of the helix angle of the teeth, the occurring Zahnungsa xial forces on the inner rotor gear now leads out such that they act exactly opposite to the axial forces on the inner rotor due to the pressure difference of the medium and are approximately in the same order of magnitude To minimize bearing load.

During storage, the grease is secured, in particular for the rotating inner bearing, by pronounced grease deposition and by current shielding elements ( 20 ) on the inner and outer rings, so that the grease is forced outwards by centrifugal force and thus remains in the desired area for bearing lubrication. In the teeth such shielding plates are also provided, as is exemplified in the accompanying Fig. 1 represents.

The inner rotor bearing ( 8 a and 8 b) in the rotating driven center distance crank body ( 10 ) is preferably carried out in a flying version, ie: on the inlet side there is no storage and thus no scoop shaft sealing, only on the outlet and drive side is a stable and robust position tion realized the driving center distance crank body and the enclosed inner rotor shaft ( 8 and 9 ), wherein preferably the transmission synchronization unit ( 6 and 7 ) is integrated to generate the required inner rotor movement. This means that two scoop shaft seals ( 21 ) are only required on the outlet side, but advantageously do not have to seal against vacuum conditions.

In the case of the flying inner rotor bearing and the increased speed, the inner rotor ( 1 ) must be hollow in the displacement area with regard to the bending-critical speed and the inner rotor shaft must also be provided with sufficient rigidity.

There are three embodiments for the bearing ( 9 ) of the driving center distance of the crank body:

• 1. The drive motor ( 11 ) is located between the bearing of the center distance crank body. In which the rotating around the main axis of the drive motor rotor to the inner rotor shaft ( 24 ) summarizes, there is a relatively large motor diameter and thus an increased torque, which is conveniently used as a breakaway torque to always ensure the required starting torque for this pump . This before geous solution is shown in the accompanying Fig. 1.
• 2. The center distance crank body has no autonomy storage but is directly on the type drive motor shaft end of a standard electric motor assembled.
• 3. The center distance crank body has its own Storage and is connected to the clutch Standard electric motor connected.

For all more difficult applications, such as increased amounts of dirt, liquids, particles etc. in the gas flow, or if vibrations, impacts, one-sided loading or overload are to be expected, a "Mohno" support bearing is also installed on the inlet side ( 12 ) in Fig. 1 and the separate representation in Fig. 3 with reduced play between the inner rotor pin ( 25 ) in Fig. 3 and the housing rotor guide ( 26 ) in fixed connection to the inlet cover ( 23 ) before seen to "catch" such interference with special use of the rolling and "freewheel" parts in the movement of the "Mohno" inner rotor pin ( 25 ) within the housing rotor guide ( 26 ). This avoids the more critical contact between the significantly larger inner rotor diameter and the housing rotor in the working chamber on the inlet side. These support bearing contact surfaces are also carried out in a material combination with particularly wear-resistant and contactable material pairing for the possible, that is to say only occasionally, to catch one of the above-mentioned faults.

This support bearing can possibly be designed in several stages with a corresponding angular offset in order to be able to better absorb the deflections that occur from the different directions. Is proposed as shown in Fig. 2, a support bearing journal on opposite rolling circle positions, such as A and C or B and D, so that two mutually perpendicular Füh approximately tracks with improved support effect. Furthermore, if necessary. the support bearing contact can be executed alternatively in a sliding block with an internal swivel joint.

Of course, a solution similar to the drive side is conceivable as shown in Fig. 4, in which two robust rolling bearings ( 28 a / b) in Fig. 4 assume a permanently acting support on a fixed pin ( 27 ). This is, for example, a more economical solution for a double-flow version of this pump or for a higher number of stages for the purpose of improved final pressure values with a correspondingly longer rotor. The dead space in this storage area should be minimized in order to keep the harmful gas flow through storage as low as possible. Furthermore, this storage should be made particularly robust due to the choice of material, right down to the all-ceramic bearing.

The high robustness and reliability of the well-known Eccentric screw pumps ("Mohno" pumps) in the liquid speed pump range also allows for these struck internal spindle pump a superior suitability in more difficult applications, for example wise liquids, dust and particles are promoted Need to become. The special form of movement of the umlau fend rotating inner rotor in the fixed Ge house rotor made of rolling and sliding parts ensures in Zu cooperate with the aforementioned measures for a "scraping" of the rotor flank surfaces, so that ap the dangerous layer structure depending on the application is avoided. This allows this internal spindle pump but at the same time also amounts of dirt in the gas conveyor cope with current, which for today's dry-runner this order of magnitude is unreachable. The increased on drive torque by the increased (because of the necessary encompassing the inner rotor shaft) motor diameter supports this positive aspect partly.

The necessary adjustment of the synchronization between the revolving inner rotor and the fixed housing rotor to ensure freedom from contact in the pump workspace is done favorably on the internally toothed gear ( 6 ), whose housing fixed positioning with subsequent fixation via the fixed bearing pin ( 28 ) the required surface Backlash adjustment between the inner rotor and the housing rotor safely and easily and always guaranteed exactly.

The proposed internal spin is advantageous delpump constructed as a modular system, in which the entire pump from a drive unit and a displacement unit is assembled:

This drive unit consists of the motor ( 11 ), the bearings on both sides for the center distance crank body ( 9 a / b) and including the inner rotor bearing ( 8 a / b), which is also double-sided, and the integrated gear unit ( 6 , 7 ) for generating the required inner rotor movement . Furthermore, there are also fans ( 17 ), housing ( 15 ) and the scoop shaft seals ( 21 ) and a few other small parts, such as the outer sheathing plate ( 14 ) with an inner noise damping layer ( 13 ), for the independently running drive unit.

The drive motor ( 11 ) is carried out with / without frequency converter with increased speed, for example as a universal motor with global voltage suitability with simple implementation of the increased speed in order to increase both the degree of delivery and the energy density, so that at the same time the manufacturing costs are still significantly reduced . The speed variation of the drive unit can, as is well known, advantageously used directly for the application-specific suction capacity adjustment or also directly as overload protection.

The displacement unit consists of the inner rotor ( 1 ), the housing rotor ( 2 ) with outlet flange ( 5 ) and outer ribs ( 18 ) and the inlet-side cover ( 23 ) with the inlet flange ( 4 ). In the housing rotor, the well-known overpressure / bypass valves are also integrated at the points where, due to the internal compression at higher intake pressures, the overpressure is reduced by the overflow connections to the outlet which are also integrated (not shown).

The required external heat dissipation for the drive and displacement unit is achieved by an intensive, axially flowing cooling air flow of the integrated fan ( 17 ). The ambient air sucked in the axial direction is guided in the comprehensive sheet metal casing ( 14 ) via the ribbing ( 16 ) of the drive motor, and then the required amount of heat of the gas compression is taken from the outlet flowing towards the inlet via the ribbing ( 18 ) of the housing rotor dissipated via the air flow. The axially directed cooling air flow is advantageous because there is no mutual harmful influence of adjacent spindle pumps. In addition, the flow direction from the outlet to the inlet conveniently ensures a more uniform temperature level throughout the machine. Furthermore, an aluminum alloy is proposed for the material of the ribbed housing, so that thanks to the significantly better thermal conductivity, a significantly more compact and lighter machine is created than is possible to date.

The comprehensive sheet metal sheathing not only ensures a targeted air flow with correspondingly lower heat transfer values, but at the same time, thanks to the integrated inner coating ( 13 ) of the sheathing sheet ( 14 ), ensures simple but very efficient noise reduction.

With the modular concept structure, a complete Internal spindle pump series with various suction connections assets are now favorably different Displacement units with a drive unit comb niert, whose speed is adjusted if necessary. This modular construction concept for the entire construction series of such a type of machine with one type drive unit for several neighboring pumping speeds sizes significantly improve the cost situation while reducing the number of parts required Provision of payments with maximum flexibility in Meeting the respective customer requirements by the desired displacement unit to an An drive unit is mounted.

To achieve the lowest possible manufacturing costs the total number of parts is advantageously low  be. In addition, the complexity of all construction parts extremely simple, the production takes place via weighing as a simple turned part, or over the well-known manufacturing process of whirling.

Due to the increased speed and simple implementation the required multi-level becomes an extreme compact and lightweight pump that all known pumps in the mentioned suction assets is clearly superior. Besides, is the proposed internal spindle pump cheaper and at the same time more reliable and ro buster than the machines known today.

In the illustrated embodiments shows

Fig. 1 shows a longitudinal section through a possible inner spindle pump according to this invention. This machine is preferably carried out in a horizontal shaft position. The Ga inlet ( 4 ) is located on the front opposite the drive side, and the outlet ( 5 ) is at the bottom at the geodetically lowest position so that liquids and other entrained parts of the gas flow can quickly and easily leave the pump.

Fig. 2 shows the "Mohno" forms of motion of the revolving the single-rotor inner rotor in the fixed two-speed housing rotor with the rolling conditions and the linear motion generation for some selected points on the inner rotor pitch circle. Furthermore, the possibility of implementing the internal compression by reducing the inner rotor cross-sections is illustrated with various line types as described ben.

Fig. 3 shows a possible embodiment of the additional union-side inner rotor support bearing as a "Mohno" support bearing for catching possible malfunctions.

Fig. 4 shows an alternative embodiment of the additional inlet-side inner rotor support bearing with a permanently acting support effect.

The above statements are primarily for the Va vacuum technology is particularly advantageous, but they apply also for other applications for promotion and ver sealing of gases.  

Reference list

1

Single-start inner rotor (rotating, driven)

2nd

Double-start housing rotor (fixed)

3rd

Creative space

4th

Gas inlet opening

5

Gas outlet opening

6

Internal toothed gear for the housing rotor (fixed)

7

External toothed internal rotor gear

8th

Storage of the rotating inner rotor

8th

a Fixed bearing side of the inner rotor bearing

8th

b Floating side of the inner rotor bearing

9

Storage of the driving axle distance crank body pers

9

a Fixed bearing side of the center distance crankcase bearing

9

b Floating side of the center distance crankcase bearing

10th

Center distance crank body (with fixed motor rotor)

11

Drive motor (stator and motor rotor)

12th

Inner rotor support bearing, "Mohno" support bearing (optional)

13

Noise dampening layer

14

Sheathing sheet

15

Drive unit housing

16

Ribbing of the drive housing

17th

Fan

18th

Ribbing of the housing rotor

19th

Balancing mass

20th

Lubricant shielding elements

21

Bucket shaft seals

22

Outlet cover

23

Inlet cover

24th

Inner rotor shaft

25th

Inner rotor spigot

26

Housing rotor guide

27

Fixed pin for support bearing support

28

Fixed bearing journal for synchronization adjustment

Claims (41)

1. Using an eccentric screw pump as Ver press machine for conveying and compacting Gases, preferably as a vacuum pump. 2. A method of operating an eccentric screw pump / internal spindle pump with a rotating inner rotor ( 1 ) in a fixed housing rotor ( 2 ) with a suction chamber ( 3 ) with Ga inlet opening ( 4 ) and gas outlet opening ( 5 ), characterized in that the revolving rotating inner rotor ( 1 ) is constantly controlled in its movement in such a way that the inner rotor ( 1 ) in the scooping chamber ( 3 ) moves substantially without contact in the fixed housing rotor ( 2 ). 3. The method according to claim 2, characterized in net that the internal spindle pump operated dry becomes.   4. The method according to claim 1, 2 or 3, characterized in that the catchy inner rotor ( 1 ) is driven at an increased speed, but at least at a drive speed of 3000 min ^-1 . 5. For an operating method according to claims 2 to 4 suitable dry-compressing internal spindle pump as a displacement machine for conveying and compressing gases with a rotating ro single-rotor inner rotor ( 1 ) in a fixed two-speed housing rotor ( 2 ) with a closed pump chamber ( 3 ) with Gas inlet opening ( 4 ) and gas outlet opening ( 5 ), characterized in that the rotating inner rotor ( 1 ) outside the scooping space ( 3 ) is constantly controlled in such a way that this catchy inner rotor ( 1 ) in the scooping space ( 3 ) at least in its working area be moved without contact in the fixed two-speed housing rotor ( 2 ). 6. Dry compressing internal spindle pump according to An saying 5, characterized in that between the catchy inner rotor and the two-course Housing rotor several individually closed Scooping chambers connected in series are. 7. Dry compressing internal spindle pump according to An saying 5 or 6, characterized in that the  inlet / suction-side scooping chamber volume larger than the scoop chamber volume on the outlet side. 8. Dry compressing internal spindle pump according to An saying 7, characterized in that the forehead sided circular diameter of the inner rotor and / or the slope of the inner rotor in the outlet axis direction can be reduced. 9. Dry compressing internal spindle pump according to An saying 7, characterized in that at the Make the change in the scoop volume Blow / bypass valves on the bidentate housing rotor Connection to the gas outlet are provided. 10. Dry compressing internal spindle pump after one of the preceding claims, characterized records that the different inner rotor forehead cross-sectional areas around the respective Mit points on the pitch circle like this in Achsrich direction relative to each other and position be kidney that for the entire inner rotor mass balance for the inner rotor movement is reached. 11. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the balancing of the center distance of the crank body takes place via appropriate compensating measures ( 19 ). 12. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the single-start inner rotor ( 1 ) is made of a different material than the two-start Ge house rotor ( 2 ). 13. Dry-compressing internal spindle pump according to claim 12, characterized in that the material of the Inner rotor has a lower thermal expansion coefficient than the material of the housing rotor having. 14. Dry compressing internal spindle pump according to An saying 12 and 13, characterized in that the catchy inner rotor made of steel and the two-speed housing rotor made of aluminum government exists. 15. Dry compressing internal spindle pump after one of the preceding claims, characterized records that the internal spindle pump completely is running dry, i.e. neither in the ar still in the other areas of Ma Schine is the feed of the well-known company medium, such as water or oil. 16. Dry compressing internal spindle pump according to claim 15, characterized in that for the storage ( 8 and 9 ) and the synchronization toothing ( 6 and 7 ) there is a one-time, lifetime grease lubrication to be carried out at the factory. 17. Dry compressing internal spindle pump according to claim 15 and 16, characterized in that the bearing ( 8 and 9 ) as a hybrid bearing, so Ke ceramic balls in steel rings is executed. 18. Dry compressing internal spindle pump according to claim 15 and 16, characterized in that the fixed, internally toothed gear ( 6 ) is designed as a plastic gear. 19. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the contact between the Zahnflan ken the synchronization teeth ( 6 and 7 ) is limited to the immediate vicinity of the pitch circle, so that the sliding components in a grip of the two gears is minimized become. 20. Dry compressing internal spindle pump according to An Proverb 19, characterized in that the tooth tip circle diameter only a few tenths of a millimeter ter larger than the respective pitch circle diameter it is. 21. Dry compressing internal spindle pump according to An Proverb 19, characterized in that he total coverage required over the jump cover by appropriate choice of the slope angle and the tooth width is realized. 22. Dry compressing internal spindle pump according to An Proverb 20, characterized in that the Ori  Entry of the helix angle of the toothing is chosen so that the teeth occurring axial forces on the internal rotor gear exactly opposite to the axial forces on the inner rotor due to the pressure difference of the medium Act. 23. Dry compressing internal spindle pump according to An Proverb 22, characterized in that the Ver tooth axial forces on the inner rotor gear are designed to be as large as the axial forces on the inner rotor due to the pressure difference of the Medium. 24. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the inner rotor bearing ( 8 a and 8 b) in the rotating driven center distance crank body ( 10 ) in a flying design, it follows, so that only on the outlet / drive side Storage ( 8 and 9 ) of the driving axle spacing crank body and the enclosed inner rotor shaft is realized. 25. Dry compressing internal spindle pump according to claim 24, characterized in that the drive motor ( 11 ) between the bearings ( 9 a and 9 b) of the center distance crank body ( 10 ). 26. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that an additional support bearing ( 12 ) is provided on the inlet side. 27. Dry compressing internal spindle pump according to claim 26, characterized in that the support bearing ( 12 ) with reduced clearance between the inner rotor pin ( 25 ) and the housing rotor guide ( 26 ), which is firmly connected to the inlet cover ( 23 ) . 28. Dry compressing internal spindle pump according to claim 27, characterized in that the play of the support bearing ( 12 ) with special use of the rolling and "freewheeling" parts in the movement of the "Mohno" inner rotor pin ( 25 ) within the housing rotor guide ( 26 ) is designed. 29. Dry compressing internal spindle pump according to claim 27, characterized in that the support bearing ( 12 ) is carried out in a material combination with particularly wear-resistant and contactable material properties. 30. Dry-compressing internal spindle pump according to claim 27, characterized in that the support bearing ( 12 ) is carried out in several stages with a corresponding angular offset. 31. Dry-compressing internal spindle pump according to claim 27, characterized in that the con tact in the support bearing ( 12 ) is designed in a sliding block with an inner swivel joint. 32. Dry compressing internal spindle pump according to claim 27, characterized in that the support bearing ( 12 ) as a permanent support on the drive side with two robust roller bearings ( 28 a / b) on a fixed pin ( 27 ) is performed. 33. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the setting of the synchronization between the inner rotor ( 1 ) and the housing rotor ( 2 ) for ensuring the contact-free unit in the pump work space ( 3 ) on the internally toothed gear ( 6 ) is carried out by the housing-fixed position with subsequent fixation is carried out via the fixed bearing journal ( 28 ). 34. Dry compressing internal spindle pump after one of the preceding claims, characterized records that the proposed inner spindle pump constructed as a modular system is by the entire pump from one An drive unit and a displacement unit together is set. 35. Dry compressing internal spindle pump according to one of the preceding claims, characterized in that the drive motor ( 11 ) is designed as a universal motor with universal voltage suitability. 36. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the heat dissipation takes place primarily for the drive motor ( 11 ) and housing rotor ( 2 ) via an integrated fan ( 17 ). 37. Dry-compressing inner spindle pump according to claim 36, characterized in that the cooling air flow of the fan ( 17 ) flows axially around the inner spindle pump mainly. 38. Dry-compressing internal spindle pump according to claim 37, characterized in that the cooling air flow is guided in a sheet metal jacket ( 14 ) comprising the internal spindle pump. 39. Dry compressing internal spindle pump according to claim 38, characterized in that the sheet metal casing ( 14 ) on the inside with egg ner noise damping layer ( 13 ) is provided. 40. Dry compressing internal spindle pump according to An pronoun 37, characterized in that the cooling Airflow from the outlet towards the inlet is directed. 41. Dry-compressing internal spindle pump according to one of the preceding claims, characterized in that the inner rotor ( 1 ) is richly hollow inside in the displacer.