EP0781896B1 - Turbinenrad für Impulsturbinen - Google Patents

Turbinenrad für Impulsturbinen Download PDF

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Publication number
EP0781896B1
EP0781896B1 EP96120835A EP96120835A EP0781896B1 EP 0781896 B1 EP0781896 B1 EP 0781896B1 EP 96120835 A EP96120835 A EP 96120835A EP 96120835 A EP96120835 A EP 96120835A EP 0781896 B1 EP0781896 B1 EP 0781896B1
Authority
EP
European Patent Office
Prior art keywords
disc
turbine wheel
drive
opening
braking
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 - Lifetime
Application number
EP96120835A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0781896A1 (de
Inventor
Werner Trojahn
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.)
Joisten and Kettenbaum GmbH and Co JOKE KG
Original Assignee
Joisten and Kettenbaum GmbH and Co JOKE KG
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 Joisten and Kettenbaum GmbH and Co JOKE KG filed Critical Joisten and Kettenbaum GmbH and Co JOKE KG
Publication of EP0781896A1 publication Critical patent/EP0781896A1/de
Application granted granted Critical
Publication of EP0781896B1 publication Critical patent/EP0781896B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/06—Adaptations for driving, or combinations with, hand-held tools or the like control thereof
    • F01D15/067—Adaptations for driving, or combinations with, hand-held tools or the like control thereof characterised by non-bladed rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/34—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes

Definitions

  • the present invention relates to a turbine wheel for Drive turbines, in particular of metalworking machines, consisting of a disc-shaped wheel body with a central bearing opening and concentric to it Inlet openings arranged on the circumference in a disk side surface of drive air ducts running in the disc body, each in one in the disk peripheral surface lying outlet opening and one in the disc body extending in the direction of the disk peripheral surface Outflow section has.
  • Such a turbine wheel is from DE-12 16 616 C. known.
  • the drive air channels are slit on the sides and end at the Baffle so that there are no discrete inlet openings have.
  • Turbine wheels are also known, their outlet openings of the drive air ducts in the opposite of the inlet openings Disc side surface of the wheel body lie. These known turbine wheels have on their peripheral surfaces pocket-shaped recesses that the attack surface form incoming brake air for the turbine wheel. The The efficiency of these known turbine wheels deteriorates from 70 to 75% of the final speed of the turbine wheels.
  • the present invention is based on the object to improve the turbine wheel described at the outset, that the efficiency especially at high Speeds, in the area of the final speed is improved. According to the invention this is achieved in that the drive air channels an approximately axially extending inflow section have, the inlet opening in the form of a Ellipse has its small semiaxis in the radial median plane and their large semi-axis perpendicular to this runs.
  • a essentially axial flow and an approximately radially flowing outflow of the drive compressed air is reached. The radial outflow enables one large effective normal component over a large Angle of rotation is available.
  • the drive compressed air has better ventilation, since the Impact of the radial force components occurring in the drive compressed air are amplified by the centrifugal force and thus the ventilation is improved.
  • the effective ventilation the drive air ducts is important, because with one Compressed air jam no new drive compressed air in the drive air ducts can flow in.
  • Training the drive air ducts can redirect the Driving air inside the wheel body from the approximately axial directed flow in the direction of the wheel body circumference directed outflow can be optimized in such a way that a large normal force component is reached and also quick ventilation.
  • Turbine wheel from a disc-shaped wheel body 1.
  • Ein such a turbine wheel has a diameter, for example 25 - 100 mm and a thickness of e.g. about 6 - 10 mm.
  • the wheel body 1 has a central bearing opening 2, with which he, for example, on a wave that is not shown is stored.
  • Concentric to the opening 2 are on a disc side surface 3 on the outer Scope inlet openings 4 of drive air channels 5 are arranged.
  • the inlet openings are 4 with a division of about 9 ° on the circumference of the Disc side surface 3 arranged.
  • the drive air ducts 5 have an approximately axially extending inflow section 6 and one in the disk body towards the disk peripheral surface 7 extending outflow section 8.
  • the Inlet openings 4 go into a dome-shaped depression 9 in the disc side surface 3, from the bottom of the recess from the inflow section 6 of the respective Drive air duct 5 extends into the wheel body 1 from itself.
  • the inlet openings 4 have the shape of an ellipse. How 4, the course runs Longitudinal axis X-X of the respective inflow section 6 of the Drive channel 5 at an acute angle to the radial center plane Y-Y through the center of the elliptical Inlet opening 4 in the drive direction Z of the turbine wheel seen.
  • the longitudinal axis runs in one transverse plane perpendicular to the central plane Y-Y.
  • the longitudinal axis X-X of the inflow section 6 runs here through the front focal point seen in the drive direction the elliptical inlet opening 4.
  • a blow-out nozzle 11 arranged on the side of the wheel body 1 arranged for the drive air and its nozzle opening is designed such that its blow-out opening 12 in the maximum blowing position coaxial with the inlet opening 4 runs, see Fig. 4 when these two openings coincide, the outlet opening 12 of the injection nozzle 11 is less than or equal to the inlet opening 4.
  • inlet openings 4 extends obliquely to Disc side surface 3, preferably under one acute angle less than 45 °.
  • the inlet openings 4 are like this trained that their large semiaxis in each case for Radial central axis Y-Y perpendicular transverse plane through the The center of the elliptical inlet opening 4 runs and their small semi-axis in the radial central plane.
  • the longitudinal axis B-b of the respective outflow section 8 of the drive air channels 5 runs under one acute angle obliquely opposite to the radial central plane Y-Y to drive direction of rotation Z.
  • the brake bags 15 have one perpendicular to the longitudinal axis B-B of the outflow section running floor surface 16, in each case the outlet opening 14, and one at an angle greater than 90 ° and less than 180 ° to the bottom surface 16 extending baffle 17.
  • These brake pockets 15 work together with a brake air nozzle 18 arranged on the circumference of the wheel body 1 in this way is that the outlet opening 19 of the brake air nozzle 18th the circumferential contour of the wheel body 1 is adapted.
  • the brake air nozzle 18 is here in relation to the wheel body 1 aligned that its longitudinal axis D-D in that Position in which its outlet opening 19 with the opening of the Brake bags 15 coincides with an obtuse angle the baffle 17 forms.
  • the formation of the baffle 17 can in Size, shape and angle of attack should be such that optimal braking efficiency can be achieved.
  • FIG. 5 is a so-called duplex version of a Turbine wheel according to the invention shown.
  • this turbine wheel is a two-sided compressed air supply by means of the two-sided arranged blow-out nozzles 11, which in the inlet openings Blow in 4 separate drive air ducts 5.
  • the present invention is not based on the embodiment shown limited, but also includes all in For the purposes of the invention, equivalent designs. So can another division of the inlet openings on the circumference of the Turbine wheel can be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Supercharger (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)
EP96120835A 1995-12-28 1996-12-23 Turbinenrad für Impulsturbinen Expired - Lifetime EP0781896B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29520650U 1995-12-28
DE29520650U DE29520650U1 (de) 1995-12-28 1995-12-28 Turbinenrad für Antriebsturbinen, insbesondere von Metallbearbeitungsmaschinen

Publications (2)

Publication Number Publication Date
EP0781896A1 EP0781896A1 (de) 1997-07-02
EP0781896B1 true EP0781896B1 (de) 2001-06-13

Family

ID=8017310

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96120835A Expired - Lifetime EP0781896B1 (de) 1995-12-28 1996-12-23 Turbinenrad für Impulsturbinen

Country Status (7)

Country Link
EP (1) EP0781896B1 (es)
JP (1) JPH09287401A (es)
AT (1) ATE202184T1 (es)
DE (2) DE29520650U1 (es)
DK (1) DK0781896T3 (es)
ES (1) ES2107989T3 (es)
PT (1) PT781896E (es)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001020701A (ja) * 1999-07-01 2001-01-23 Ntn Corp エアタービン駆動スピンドル装置
JP4567225B2 (ja) * 2001-03-26 2010-10-20 瓜生製作株式会社 エアツール用エアモータ
CN101608597B (zh) * 2009-06-23 2011-05-04 李玉森 可控轮槽缓流式水轮/水泵机
DE202015106402U1 (de) * 2015-11-24 2017-02-27 Woco Industrietechnik Gmbh Fluidgetriebener Antrieb und Aktuator

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191307894A (en) * 1912-11-18 1913-08-07 Roehrenreinigung M B H Ges Improvements in Apparatus for Cleaning or Scaling Tubes or Pipes.
US1329626A (en) * 1918-12-16 1920-02-03 Frank W Oman Turbine-engine
FR1190147A (fr) * 1957-11-14 1959-10-09 Lipi Ag Turbine
DE1216616B (de) * 1959-02-18 1966-05-12 Albrecht Nikes Druckturbine mit einer in einem Gehaeuse rotierenden, Druckkanaele enthaltenden Scheibe
FR1323406A (fr) * 1962-05-29 1963-04-05 Garrett Corp Perfectionnements aux turbines miniatures
US3372906A (en) * 1965-06-22 1968-03-12 Jerry D. Griffith Small volumetric flow reaction turbine
DE2753106A1 (de) * 1977-11-29 1979-06-07 Messerschmitt Boelkow Blohm Wellenantrieb, wechselweise fuer beide drehrichtungen

Also Published As

Publication number Publication date
ATE202184T1 (de) 2001-06-15
DK0781896T3 (da) 2001-09-03
PT781896E (pt) 2001-11-30
ES2107989T1 (es) 1997-12-16
EP0781896A1 (de) 1997-07-02
DE59607082D1 (de) 2001-07-19
DE29520650U1 (de) 1997-04-24
JPH09287401A (ja) 1997-11-04
ES2107989T3 (es) 2001-09-01

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