EP0077031A1 - Compresseur à pistons rotatifs - Google Patents

Compresseur à pistons rotatifs Download PDF

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Publication number
EP0077031A1
EP0077031A1 EP82109274A EP82109274A EP0077031A1 EP 0077031 A1 EP0077031 A1 EP 0077031A1 EP 82109274 A EP82109274 A EP 82109274A EP 82109274 A EP82109274 A EP 82109274A EP 0077031 A1 EP0077031 A1 EP 0077031A1
Authority
EP
European Patent Office
Prior art keywords
rotor
main rotor
main
secondary rotor
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.)
Granted
Application number
EP82109274A
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German (de)
English (en)
Other versions
EP0077031B1 (fr
Inventor
Beteiligungsgesellsch Technika
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Individual
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Individual
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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 outer-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 known for example from DE-OS 25 05 113.
  • the published publication deals in particular with the formation of the tooth flanks of the secondary rotor, around 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, not as far as 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), should be kept as small as possible.
  • the rotors of screw compressors - in order to keep leakages as small as possible - must 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 involves several operations (pre-milling with so-called roughing cutters and then finishing with finishing or fine milling cutters) 1 .
  • a cutter set for a pair of rotors costs between DM 20,000 and 50,000 depending on the diameter.
  • 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 manufacture, so that too many expensive tools do not have to be manufactured and kept in stock. The result of this is that the individual types of rotary compressor are not operated directly in their optimal 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 be The optimum operating point lies - as can be seen from Fig.
  • the object of the invention is to provide a rotary compressor of the type mentioned, which is simple to manufacture is and in which relatively inexpensive tools for producing the profiles are required.
  • the dimensional control should also 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 because of the generating circles are formed by a steady, analytically definable curve shape from head point to head point, in this case circular arcs.
  • the tooth flanks are layered circle screw surfaces, the generating circles of which are (see also Wunderlich, descriptive geometry, volume 2 of the series B.I., university pocket books, volume 133, 1967, pages 188 ff.).
  • the flanks of the teeth are produced by a hobbing process using a profile milling cutter.
  • a profile milling cutter is one with a curved surface line, which can be designed according to the shape of the face cut.
  • 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 significantly more refined 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 'A C' (Fig. 1), so that the optimal 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 can be cheaper.
  • the individual rotary piston compressor of such a series can be driven directly without intermediate transmission, so that an improvement in efficiency can be achieved in this way alone.
  • Another advantage of the embodiment according to the invention also consists in the following: in known rotors the tooth depth, i.e. the groove depth between two neighboring head lines is large. As a result, the ratio of core diameter to outer diameter is also large. In known rotors, this value is between 0.4 to 0.5. However, in the rotor according to the invention, which is defined by the features of the characterizing part of claim 1, the ratio of the core diameter to the 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 to 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 in a housing 1? a compression chamber 14 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 disc 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 mounting of the bearings 4o and 42 takes place inside a nut 46 screwed onto the bearing pin 38 and outside via a compression spring 48, which is supported on a second end cover 5o, which is firmly connected to the housing via 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 mounting or axial fixation of the bearings 6o and 62 takes place on the inside diameter. on the inner ring of the bearings by means of a bearing journal 56 screwed nut 66 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 throat 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 the line III-III of FIG. 1.
  • 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 Haunt and secondary rotor to each other, in which the head point 8 2 of the main rotor 16 in the position shown, ie the Eu point center line lies exactly on the connecting line VV 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 likewise lies 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 1 8 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 is determined by the path of the head point 82.
  • the head point 9o 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 and secondary rotors from the connecting line between the centers of the two rotors.
  • the head point 82 of the main rotor is located in the area 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 9o 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 determined by the respective head point of the Main rotor formed, when a head point of the
  • Main rotor is located between two head points of the secondary rotor, the two head points mentioned lie 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)
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
DE19813140108 DE3140108A1 (de) 1981-10-09 1981-10-09 Drehkolbenverichter
DE3140108 1981-10-09

Publications (2)

Publication Number Publication Date
EP0077031A1 true EP0077031A1 (fr) 1983-04-20
EP0077031B1 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 (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0149446A3 (fr) * 1983-12-14 1985-08-07 Boge Kompressoren Otto Boge GmbH & Co. KG Compresseur à piston rotatif
EP0154673A3 (en) * 1983-11-30 1986-12-17 Hitachi, Ltd. Rotary fluid machine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD301062A7 (de) * 1989-01-17 1992-10-01 Kuehlautomat Berlin Gmbh Rotorpaar für Hochdruckschraubenverdichter
AT505405B1 (de) 2007-06-21 2009-01-15 Kraler Franz Rafflamellenstore
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT169479B (de) * 1946-07-18 1951-11-26 Ljungstroems Angturbin Ab Drehkolbenmaschine
CH384768A (de) * 1959-09-02 1965-02-26 Ingersoll Rand Co Strömungsmittelpumpe oder -motor
DE2360403A1 (de) * 1973-12-04 1975-06-05 H & H Licensing Corp Schraubenkompressoranlage zum verdichten von gasfoermigen medien, insbesondere fuer geringe ansaugvolumina
DE2505113A1 (de) * 1974-06-24 1976-01-15 Atlas Copco Ab Parallel- und aussenachsige drehkolbenmaschine mit schraegverzahntem kaemmeingriff

Family Cites Families (6)

* 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
US2486770A (en) * 1946-08-21 1949-11-01 Joseph E Whitfield Arc generated thread form for helical rotary members
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT169479B (de) * 1946-07-18 1951-11-26 Ljungstroems Angturbin Ab Drehkolbenmaschine
CH384768A (de) * 1959-09-02 1965-02-26 Ingersoll Rand Co Strömungsmittelpumpe oder -motor
DE2360403A1 (de) * 1973-12-04 1975-06-05 H & H Licensing Corp Schraubenkompressoranlage zum verdichten von gasfoermigen medien, insbesondere fuer geringe ansaugvolumina
DE2505113A1 (de) * 1974-06-24 1976-01-15 Atlas Copco Ab Parallel- und aussenachsige drehkolbenmaschine mit schraegverzahntem kaemmeingriff

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0154673A3 (en) * 1983-11-30 1986-12-17 Hitachi, Ltd. Rotary fluid machine
EP0149446A3 (fr) * 1983-12-14 1985-08-07 Boge Kompressoren Otto Boge GmbH & Co. KG Compresseur à piston rotatif

Also Published As

Publication number Publication date
EP0077031B1 (fr) 1985-08-14
DE3140108A1 (de) 1983-04-28
JPS58135394A (ja) 1983-08-11
US4619596A (en) 1986-10-28
ATE14916T1 (de) 1985-08-15

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