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EP0077031B1 - Compresseur à pistons rotatifs - Google Patents

Compresseur à pistons rotatifs Download PDF

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Publication number
EP0077031B1
EP0077031B1 EP82109274A EP82109274A EP0077031B1 EP 0077031 B1 EP0077031 B1 EP 0077031B1 EP 82109274 A EP82109274 A EP 82109274A EP 82109274 A EP82109274 A EP 82109274A EP 0077031 B1 EP0077031 B1 EP 0077031B1
Authority
EP
European Patent Office
Prior art keywords
rotor
main rotor
main
piston compressor
head
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP82109274A
Other languages
German (de)
English (en)
Other versions
EP0077031A1 (fr
Inventor
Beteiligungsgesellschaft Mbh Technika
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT82109274T priority Critical patent/ATE14916T1/de
Publication of EP0077031A1 publication Critical patent/EP0077031A1/fr
Application granted granted Critical
Publication of EP0077031B1 publication Critical patent/EP0077031B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19953—Worm and helical

Definitions

  • the invention relates to a parallel and external axis rotary compressor with at least one helically toothed main rotor and in each case a secondary rotor meshing therewith.
  • Such a rotary compressor is e.g. B. known from DE-OS 2505113.
  • the published publication deals in particular with the formation of the tooth flanks of the secondary rotor, in order to avoid the blow hole of the compressor toothing present in rotary lobe compressors, which arises from the fact that the line of contact, along which the tooth flanks of one tooth of the main and secondary rotor of an engaged pair of teeth lie against one another down to the edge of the housing, which is the intersection of the two housing bores, (see also Rinder, Springer-Verlag Vienna, New York, 1979, p. 72 ff.).
  • US Pat. No. 2,622,787 is concerned with reducing the leakage caused by the blow hole.
  • the rotors of screw compressors - in order to keep leakages as small as possible - have to be manufactured with the greatest precision, which requires complex and expensive tools and machine tools. Due to the complicated design of the individual profiles, separate milling cutters are required, whereby the manufacture of a rotor usually requires several work steps (pre-milling with so-called roughing cutters and then finishing with finishing or fine milling cutters). A cutter set for a pair of rotors costs between DM 20,000 and 50,000, depending on the diameter. In addition, there is the effort for the necessary final checks.
  • Rotary lobe compressors with different delivery volumes are commercially available in order to meet the respective desired requirements. Accordingly, the manufacturers offer compressor series in which the distance between the stages is chosen to be relatively large because of the expensive production, so that too many expensive tools do not have to be manufactured and kept in stock. The consequence of this is that the individual rotary compressor types in a series are not operated directly in their optimum range or in the vicinity of the optimum range, but rather over a larger range.
  • 1 shows the specific power consumption in (kW / m 3 / min) over the delivery volume (m 3 / min).
  • the circumferential speed of a rotor or its speed could also be plotted on the abscissa; the qualitative statement would not change here.
  • the optimum operating point is - as can be seen from FIG.
  • the rotary lobe compressors currently on the market run in the BAC range, i.e. not exclusively in or close to the optimal range, which would be around B 'AC', in order to allow the flow rate of one type to be connected as seamlessly as possible to that of the next larger type.
  • the expansion of the flow rate range for each type must be achieved by changing the speed by means of a transmission gear (belt or gear drives or by speed control of the drive motor). If you wanted to operate the rotary lobe compressors in area B 'AC', the delivery volume would have to be reduced. However, as indicated above, this would again require a larger number of rotary lobe compressor types and thus a larger number of expensive tools.
  • the object of the invention is to provide a rotary compressor of the type mentioned, which is simple to manufacture and which requires relatively inexpensive tools for producing the profiles. Furthermore, the dimensional control should be able to be carried out precisely, inexpensively and simply.
  • tooth flanks of the main rotor are layered circle screw surfaces which are generated by screwing a circle whose plane is perpendicular to the screw axis.
  • a further advantageous embodiment of the invention can be such that the tooth flanks of the secondary rotor are generated and determined by the relative path of a point lying on a head line (main rotor head point) during the rolling of the main rotor and secondary rotor.
  • the main rotor advantageously has at least three teeth.
  • the tooth flanks of the main rotor are not composed of curve segments, but are formed by a constant, uniformly analytically definable curve shape from head point to head point, in this case circular arcs, because of the generating circles.
  • the tooth flanks here are stratified circle screw surfaces, the generating circles of which are (see also Wunderlich, Representative Geometry, Vol. 2 of the B.I. series, University Pocket Books, Vol. 133, 1967, p. 188 ff.).
  • the flanks of the teeth are produced by a hobbing process using a profile milling cutter. Such a profile cutter is one with a curved one. Surface line, which can be designed according to the shape of the forehead.
  • the tooth flanks of the secondary rotor are formed by a wheel curve, which can be produced with a profile cutter with an arc-like shape.
  • a rotary lobe compressor series can be offered with a significantly more sophisticated gradation compared to known compressor series. It is possible to optimize the efficiency of the individual rotary lobe compressors in the series by choosing the optimum circumferential speeds in the absence of gears (gears and pinions or belts, adapted to the standard electrical speed of the drive, which is designed as an electric motor, for example).
  • the individual rotary compressor can be operated in direct drive in the area B 'AC' (Fig. 1), so that the optimum working area can be used.
  • the geometry of the manufactured rotor is also much easier to measure, which, as mentioned above, makes the final inspection less expensive.
  • the individual rotary compressor of such a series can be driven directly without the interposition of an intermediate gear, so that an improvement in efficiency can be achieved in this way alone.
  • a further advantage of the configuration according to the invention also consists in the following: in known rotors, the tooth depth, ie the groove depth between two adjacent head lines, is large. As a result, the ratio of core diameter to outer diameter is also large. In known rotors, this value is - tween 0.4 to 0.5. In the rotor according to the invention, however, which is defined by the features of the characterizing part of claim 1, the ratio of core diameter to outer diameter is approximately 0.95.
  • the deflections to be expected in the main rotor according to the invention are therefore practically zero in comparison with the known main rotors. As a result, the tolerances can be kept very small and the individual main rotor is also very robust. Due to these tolerances, the efficiency can be further improved.
  • the rotary piston compressor which is generally designated 10, has a compression chamber 14 in a housing 12, in which a main rotor 16 and a secondary rotor 18 meshing therewith are arranged.
  • the main rotor 16 has at one end an extension 24 divided into two areas 20 and 22 with different diameters, of which one area 20 with a larger diameter of the bearing by means of roller bearings 26 and the other area 22 with a smaller diameter for connecting a drive, not shown serves.
  • the bearing 26 is located in a bearing recess 28 in a bearing disk 30 which is fixedly connected to the housing 12 together with an end cover 32 via a screw connection 34.
  • a sealing ring 36 is provided to seal the bearing 26 to the outside.
  • the main rotor 16 has a further journal 38 which is mounted in a roller bearing 40 and in a ball bearing 42 in a first bearing opening 44 of the housing 12.
  • the bearings 40 and 42 are held on the inside by means of a nut 46 screwed onto the bearing pin 38 and on the outside by means of a compression spring 48 which is supported on a second end cover 50, which is firmly connected to the housing by means of screw bolts 52, with the interposition of a fixing sleeve 53 .
  • the secondary rotor 18 has a bearing journal 54 and 56 on the end face, of which the bearing journal 54 is supported in a roller bearing 58 in the bearing washer 30 and the bearing journal 56 in a roller bearing 60 and a ball bearing 62 in a second bearing opening 64 in the housing 12 .
  • the bearings 60 and 62 are held or axially fixed on the inner diameter or on the inner ring of the bearings by means of a nut 66 screwed onto the bearing journal 56 and on the outside of the bearing outer ring via a compression spring 68 with the interposition of a fixing sleeve 70.
  • the reference number 72 denotes the fillet line of the main rotor and the reference number 74 the dashed line of the secondary rotor.
  • the reference numbers 76 and 78 denote the top lines of the main and secondary rotors.
  • FIG. 3 shows a cross section along line AB of FIG. 2.
  • the main rotor 16 has a total of four teeth, the head points of which are represented by the reference numbers 80, 82, 84 and 86 in the section according to FIG. 3.
  • the teeth of the main rotor are formed by screwing a circle with the radius of the projection of the fillet screw line onto a plane perpendicular to the screw axis; the " screw deflection" is selected according to the radius of the head line.
  • the main rotor is manufactured using a hobbing process with a profiled milling cutter.
  • the secondary rotor 18 has nine teeth (which are not numbered in detail), wherein, as can be seen from FIGS. 4 to 7, the tooth flanks between the teeth are determined by the relative path of the head points 80 to 84 of the main rotor 16.
  • the secondary rotor tooth flanks in the case of pointed secondary rotor teeth are not circles, but intertwined epitrochoids, which, however, can be approximately replaced by their circles of curvature during manufacture, that is, by arcs.
  • FIG. 4 shows a first position of the main rotor and the secondary rotor relative to one another, in which the head point 82 of the main rotor 16 in the position shown, ie. H. the center point of the head point lies exactly on the connecting line V-V of the central axes of the rotors.
  • the head point 82 is also aligned with the throat point 82 'of the secondary rotor 18, which is also on the connecting line between the center points of the two rotors.
  • the center line of the head and the center of the throat coincide.
  • the head points 88 and 90 of the secondary rotor 18 lie exactly on the tooth flank of the tooth which has the head point 82.
  • the head point center line with the head point 82 moves clockwise, the head point 82 running exactly on the tooth flank of the secondary rotor in such a way that the tooth flank of the secondary rotor passes through the Path of the head point 82 is determined.
  • the head point 90 of the secondary rotor 18 is still on the other tooth flank.
  • the throat center line of the secondary rotor 18 has migrated counterclockwise by a smaller amount in accordance with the speed ratio between the main rotor and the secondary rotor from the connecting line of the center points of the two rotors.
  • the head point 82 of the main rotor is located in the region of the head point 88 of the secondary rotor, the head point 90 still lying on the tooth flank of the main rotor.
  • FIG. 7 it can be seen that the head point 82 has come free from the secondary rotor, but the head point 90 still remains on the tooth flank.
  • the head point 84 comes into engagement with the secondary rotor, and the sequence or the geometry is the same as in FIGS. 4 to 7: the tooth flanks of the secondary rotor are formed by the respective head point of the main rotor, when if a head point of the main rotor is located between two head points of the secondary rotor, the two mentioned head points rest on the tooth flank or the tooth flanks of the main rotor.
  • tooth flanks of the secondary rotor are formed by the head point of the main rotor in the case of pointed secondary rotor teeth, an explicit calculation of the tooth flanks of the secondary rotor, which can be regarded as a convoluted wheel line, is possible by calculation with electronic data processing.
  • blow hole is practically zero due to the profile shape of the main and secondary rotor.
  • profile shape is also particularly advantageously suitable for small delivery volumes, where even the smallest leakage can lead to a significant reduction in efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)

Claims (3)

1. Compresseur à pistons rotatifs parallèles et excentrés, comprenant au moins un rotor principal mené à denture oblique et un rotor auxiliaire engrenant dans ce dernier, caractérisé par le fait que les flancs des dents du rotor principal sont des surfaces hélicoïdales circonférentielles agencées par étages, qui sont engendrées par le vrillage d'un centre dont le plan est perpendiculaire à l'axe de l'hélice.
2. Compresseur à pistons rotatifs selon la revendication 1, caractérisé par le fait que les flancs des dents du rotor auxiliaire sont engendrés et déterminés par la trajectoire relative d'un point situé sur une ligne des crêtes (point de crête du rotor principal) lors de la dérive du rotor principal et du rotor auxiliaire.
3. Compresseur à pistons rotatifs selon l'une des revendications 1 ou 2, caractérisé par le fait que le rotor principal comporte au moins trois dents.
EP82109274A 1981-10-09 1982-10-07 Compresseur à pistons rotatifs Expired EP0077031B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82109274T ATE14916T1 (de) 1981-10-09 1982-10-07 Drehkolbenverdichter.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3140108 1981-10-09
DE19813140108 DE3140108A1 (de) 1981-10-09 1981-10-09 Drehkolbenverichter

Publications (2)

Publication Number Publication Date
EP0077031A1 EP0077031A1 (fr) 1983-04-20
EP0077031B1 true EP0077031B1 (fr) 1985-08-14

Family

ID=6143718

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82109274A Expired EP0077031B1 (fr) 1981-10-09 1982-10-07 Compresseur à pistons rotatifs

Country Status (5)

Country Link
US (1) US4619596A (fr)
EP (1) EP0077031B1 (fr)
JP (1) JPS58135394A (fr)
AT (1) ATE14916T1 (fr)
DE (1) DE3140108A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2006483A2 (fr) 2007-06-21 2008-12-24 Franz Kraler Store à lamelles

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60116920A (ja) * 1983-11-30 1985-06-24 Hitachi Ltd 回転流体機械におけるスラスト軸受の保持装置
DE8434596U1 (de) * 1983-12-14 1985-02-21 Boge Kompressoren Otto Boge Gmbh & Co Kg, 4800 Bielefeld Drehkolbenverdichter
DD301062A7 (de) * 1989-01-17 1992-10-01 Kuehlautomat Berlin Gmbh Rotorpaar für Hochdruckschraubenverdichter
CN114635849B (zh) * 2022-05-19 2022-08-12 冰轮环境技术股份有限公司 一种四转子容积泵及流量调节方法

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB254986A (en) * 1925-10-06 1926-07-15 Alexander Johan Mollinger Improvements in or relating to screw pumps
AT169479B (de) * 1946-07-18 1951-11-26 Ljungstroems Angturbin Ab Drehkolbenmaschine
US2486770A (en) * 1946-08-21 1949-11-01 Joseph E Whitfield Arc generated thread form for helical rotary members
CH384768A (de) * 1959-09-02 1965-02-26 Ingersoll Rand Co Strömungsmittelpumpe oder -motor
US3138110A (en) * 1962-06-05 1964-06-23 Joseph E Whitfield Helically threaded intermeshing rotors
US3282495A (en) * 1964-04-29 1966-11-01 Dresser Ind Sealing arrangement for screw-type compressors and similar devices
GB1197432A (en) * 1966-07-29 1970-07-01 Svenska Rotor Maskiner Ab Improvements in and relating to Rotary Positive Displacement Machines of the Intermeshing Screw Type and Rotors therefor
SE390751B (sv) * 1973-07-20 1977-01-17 Atlas Copco Ab Skruvrotormaskin
DE2360403A1 (de) * 1973-12-04 1975-06-05 H & H Licensing Corp Schraubenkompressoranlage zum verdichten von gasfoermigen medien, insbesondere fuer geringe ansaugvolumina

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2006483A2 (fr) 2007-06-21 2008-12-24 Franz Kraler Store à lamelles

Also Published As

Publication number Publication date
EP0077031A1 (fr) 1983-04-20
ATE14916T1 (de) 1985-08-15
JPS58135394A (ja) 1983-08-11
DE3140108A1 (de) 1983-04-28
US4619596A (en) 1986-10-28

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