Spindle compressor

Abstract

A spindle rotor pair of a spindle compressor has a two-toothed spindle rotor and a three-toothed spindle rotor meshing the other without contact. The wrap angle related to the two-toothed spindle rotor is at least 800 angular degrees. A range of at least 30 m/sec is achieved as the mean circumferential speed of the rotor head. In the transverse section, both spindle rotors have arc sectors and cycloid profile contour flanks. In the case of the two-toothed spindle rotor, they are primarily above its gear-tooth pitch circle and of convex design, however, in the case of the three-toothed spindle rotor, they are below its ear-tooth pitch circle and of concave, i.e., hollow, design. Preferably, the transverse sections of each spindle rotor are symmetrical in a way that in each transverse section, the centre of gravity of the profile surfaces comes to lie on the respective rotor pivot point.

1 - 23 . (canceled) 
     
     
         24 . A spindle compressor operating in a working chamber without operating fluid medium as a two-shaft rotary displacement machine to convey and compress gaseous media for vacuum pressure and positive pressure applications, the spindle compressor comprises a spindle rotor pair driven true to the rotational angle and counter-rotating with an external synchronization arrangement outside the compressor's working chamber in a surrounding compressor housing with an inlet and a discharge outlet for the conveying medium, wherein the two spindle rotors are designed with a different number of teeth: one two-toothed spindle rotor and one three-toothed spindle rotor meshing the other without contact, with a wrap angle related to the two-toothed spindle rotor of at least 800 angular degrees, whereby the spindle rotors rotate at high speed such that a range of at least 30 msec is reached as the rotor head's mean circumferential speed, that both spindle rotors in the transverse section are provided with arc sectors and with cycloid profile contour flanks which in the two-toothed spindle rotor are primarily above gear-tooth pitch circle with a convex design, and that in the three-toothed spindle rotor they are primarily below its gear-tooth pitch circle with a concave, i.e. hollow design, and that the transverse sections of each spindle rotor are preferably of symmetrical design, such that in every transverse section the profile area's center of gravity comes to lie at the respective rotor's pivot point. 
     
     
         25 . The spindle compressor according to  claim 24 , wherein the working chamber volume on the inlet side is larger than the working chamber volume on the discharge outlet side. 
     
     
         26 . The spindle compressor according to  claim 25 , wherein the transverse section on the inlet side has a larger cross-sectional area than the transverse section of the outlet side, which is achieved in at least one, but preferably in both spindle rotors in the direction of the rotor's longitudinal axis by means of a specific preferably continuously monotonic shortening of the tip radii by more than 3% and at most 20% with the corresponding increase in the respectively engaging root circle radii. 
     
     
         27 . The spindle compressor according to  claim 25 , wherein the spindle pitch m(z) of the rotor pair decreases in the direction of the rotor's longitudinal axis such that the spindle pitch at the inlet is at least 1.5 times and at most 4 times greater than the spindle pitch at the outlet. 
     
     
         28 . The spindle compressor according to  claim 24 , wherein with the change of the outer rotor diameters, a conical outer shape results for each spindle rotor with at least one right-angle bevel value per spindle rotor, and that preferably in the inlet region a cylindrical region with a constant outer diameter of the rotor head is provided for each spindle rotor. 
     
     
         29 . The spindle compressor according to  claim 24 , wherein in the Inlet region, the profile flanks are designed such that in the three-toothed spindle rotor, the profile contour flanks are also extended in length above its pitch circles, preferably cycloid, which means that according to the gear tooth system, the profile flanks in the two-toothed spindle rotor must also be extended in length below its pitch circles. 
     
     
         30 . The spindle compressor according to  claim 24 , wherein the spindle rotors are both designed and operated with a conical interior rotor fluid cooling system via a coolant fluid. 
     
     
         31 . The spindle compressor according to  claim 24 , the compressor housing is also provided with a fluid cooling system for heat dissipation, which is operated with an interior rotor fluid cooling system for the spindle rotors, preferably jointly in a cycle via a coolant fluid. 
     
     
         32 . The spindle compressor according to  claim 24 , wherein in the direction of the rotor's longitudinal axis, the rotor design parameters such as the angular pitch of the rotor head profile and the tip radii per spindle rotor are designed such that the mean rotor temperature of the two-toothed spindle rotor deviates by less than 25%, better yet less than 10% from the mean rotor temperature of the three-toothed spindle rotor. 
     
     
         33 . The spindle compressor according to  claim 24 , wherein the mean temperature of the surrounding compressor housing over the size of the coolant-contacted surfaces of the compressor housing and over the coolant flow parameters, especially pertaining to the coolant mass flow and the coolant temperature level deviates by less than 25%, better yet by less than 10% from the highest mean spindle rotor temperature. 
     
     
         34 . The spindle compressor according to  claim 24 , wherein Thread-like recesses are provided profile-symmetrically in the respective internal rotor cooling cone bore holes such that these recesses are below the respective spindle rotor teeth. 
     
     
         35 . The spindle compressor according to  claim 24 , wherein the rotor's tip circle central angle in the two-toothed spindle rotor in preferably every transverse section is greater than the respective compressor housing opening angle in Rotor. 
     
     
         36 . The spindle compressor according to  claim 24 , wherein the outer diameter of the rotor mounting on the gear side in the two-toothed spindle rotor is configured larger than the outer diameter of the synchronization gear of the two-toothed spindle rotor. 
     
     
         37 . The spindle compressor according to  claim 24 , wherein manufacturing of the different profile contours, in particular in the direction of the rotor's longitudinal axis, is done successively by turning the individual point-sequence helix lines on a lathe in the direction of the rotor's longitudinal axis, which in combination are then resulting in the outer profile contour flanks. 
     
     
         38 . The spindle compressor according to  claim 24 , wherein preferably for positive-pressure applications the coolant-touching lines in the outlet-side transverse section for the spindle rotor pair are at least 5% and no more than 100% greater than the working-chamber lines on the conveying-medium side. 
     
     
         39 . The spindle compressor according to  claim 24 , wherein for positive-pressure applications in the three-toothed spindle rotor, there is an intermediate range with greater decrease in tip radius values which, with values greater than the pitch circle radius of the three-toothed spindle rotor with a preferably cylindrical beginning at the inlet in the direction of the outlet chamber declines continuously monotonically within the first half of the total length of the spindle rotor's pumping screw. 
     
     
         40 . The spindle compressor according to  claim 24 , wherein the actual rotor head lines have a plane and curvature-constant configuration. 
     
     
         41 . The spindle compressor according to  claim 24 , wherein a regulating means R and additional bore holes and are provided, and in case of “over-compression”, i.e. when the pressure in the working chambers prior to opening at the outlet is greater than the pressure in the outlet chamber, an over-pressure conveying gas flow is conducted to the conveying-gas aftercooler. 
     
     
         42 . The spindle compressor according to  claim 24 , wherein a regulating means and additional bore holes are provided, and in case of “under-compression”, i.e. when the pressure in the working chambers prior to opening at the outlet is smaller than the pressure in the outlet chamber, an under-pressure conveying gas flow, which preferably has already been cooled by the conveying gas aftercooler, is conducted via the regulating means and the at least one additional bore hole. 
     
     
         43 . The spindle compressor according to  claim 24 , wherein the diameters ØV.Pi of the working chamber bore holes and are smaller than the width of the spindle rotor head Δm.Ki in the respective transverse section.