EP0321782B1 - Rotationskolben-Verdrängungsmaschine - Google Patents

Rotationskolben-Verdrängungsmaschine Download PDF

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Publication number
EP0321782B1
EP0321782B1 EP88120415A EP88120415A EP0321782B1 EP 0321782 B1 EP0321782 B1 EP 0321782B1 EP 88120415 A EP88120415 A EP 88120415A EP 88120415 A EP88120415 A EP 88120415A EP 0321782 B1 EP0321782 B1 EP 0321782B1
Authority
EP
European Patent Office
Prior art keywords
inlet
peripheral wall
spiral
delivery space
displacement body
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
EP88120415A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0321782A1 (de
Inventor
Roland Kolb
Fritz Spinnler
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.)
BBC Brown Boveri AG Switzerland
Original Assignee
BBC Brown Boveri AG Switzerland
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 BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Priority to AT88120415T priority Critical patent/ATE67273T1/de
Publication of EP0321782A1 publication Critical patent/EP0321782A1/de
Application granted granted Critical
Publication of EP0321782B1 publication Critical patent/EP0321782B1/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
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0246—Details concerning the involute wraps or their base, e.g. geometry

Definitions

  • the invention relates to a rotary piston displacement machine for compressible media, with at least one conveying space delimited by spiral peripheral walls extending vertically from a side wall of a fixed housing, which leads from an inlet lying outside the spiral to an outlet lying inside the spiral, and with one spiral-shaped displacement body protruding into the conveying space, which is mounted in relation to the conveying space to perform a circular, torsion-free movement and whose center is offset eccentrically relative to the center of the peripheral walls such that the displacement body always has both the outer and the inner peripheral wall of the conveying space almost touches on at least one progressive sealing line, and the spiral shape is selected so that the theoretically the largest possible inlet volume in the delivery space between the displacement body and the outer peripheral wall e is reached before the orbiting rotor, which carries the vertical displacement bodies, assumes the 0 ° / 360 ° position with respect to the delivery chamber, in which the displacement body rests with its inlet-side end on the outer peripheral wall.
  • a rotary machine the principle of which is known from DE-C3-2603462, is suitable for charging an internal combustion engine, since it is characterized by an almost pulsation-free conveyance of the working medium, which consists, for example, of air or an air / fuel mixture.
  • the working medium which consists, for example, of air or an air / fuel mixture.
  • a machine of the type mentioned is known from DE-A-3138585.
  • the fact that the theoretically maximum inlet volume is larger than the actually achievable volume results from the fact that the spiral is composed of several adjoining circular arc segments, each with a smaller radius.
  • a schematic diagram of this behavior is shown in FIG. 2 to be described later.
  • the displacement body lies in the so-called 0 ° / 360 ° position on the outer circumferential wall, which means that the suction process is considered complete.
  • tests using water models have now shown that with this configuration, a not inconsiderable part of the medium drawn in flows back from the delivery chamber into the inlet during the closing process.
  • the invention is therefore based on the object of designing the inlet area of such a machine in such a way that that the backflow is reduced, which improves the volumetric efficiency.
  • this is achieved in that the sealing line at the inlet-side end of the outer peripheral wall is advanced by an angle ⁇ between 5 ° and 50 ° relative to the 0 ° / 360 ° position, the outer peripheral wall forming an arc in this angular region which extends from a radially inner, inlet-side region of the peripheral wall leads to a radially outer region of the peripheral wall.
  • the machine shown is shown for the sake of simplicity with only one delivery chamber 6 and only one displacer. It goes without saying, however, that the displacer can have an entire system of spirals in the same plane, which can, for example, convey each from its own inlet 2 into a common outlet 3.
  • the disk-shaped rotor is designated as a whole by 1.
  • Spiral displacement bodies 5 are arranged on one or on both sides of the disk 4. These engage in a delivery chamber 6 of the fixed housing 7 and seal against it via sealing strips 14 inserted into the end wall. It runs from an inlet 2 arranged on the outer circumference of the spiral in the housing to an outlet 3 arranged in the interior of the housing. It has essentially parallel circumferential walls 8, 9 arranged at a constant distance from one another, which here - like the displacement body - have a spiral of more than include 360 °.
  • the displacement body 5 is guided between these peripheral walls 8, 9. Its curvature is dimensioned such that it almost touches the inner and outer peripheral walls simultaneously in several places.
  • the center 10 of the displacement body 5 is offset eccentrically with respect to the center 11 of the delivery chamber 6.
  • the spiral shape of the delivery chamber and displacement body is made up of quarter-circle arches.
  • the eccentric drive of the disk-shaped rotor 1 carrying the displacement body 5 results in a circular movement of each of the points of the displacement body, this circular movement being limited by the peripheral walls of the delivery chamber.
  • crescent-shaped working spaces 12 which enclose the working medium, result on both sides of the displacement body, which on the occasion of the circular movement of the displacement body through the delivery space in Towards the outlet. The volume of these working spaces is reduced and the pressure of the working fluid increases accordingly.
  • the principle sketch according to FIG. 2 shows why the geometrically possible suction volume in such a machine is larger than the volume actually enclosed in the first working space.
  • the spiral shape is given by two adjacent semicircles.
  • the displacement body 5 is in the 0 ° / 360 ° position, i.e. it forms a sealing line with the outer peripheral wall 9 in the inlet area. Line because the peripheral walls 8, 9 and the displacer 5 extend perpendicular to the plane of the drawing.
  • the suction process has ended and the crescent-shaped working space 12 is composed of the three partial areas A, B and C.
  • the invention is based on this finding.
  • ⁇ an optimal value for the angle ⁇ cannot be specified in the present case, since this depends on numerous parameters, for example on the spiral shape, eccentricity, leading edge of the displacement body, expected throttle losses, etc. From the However, the observation given above shows that even small angles lead to results.
  • the displacer 5 is rounded at its leading edge in terms of flow, here semicircularly with the radius R1.
  • the center of the semicircle is the geometric location that rotates on the dashed circle of eccentrics.
  • the displacement position represents the starting position, i.e. the suction cycle begins. It is the displacement position, as it is also shown in Fig. 1 and which is defined as a 180 ° position.
  • the displacer forms a sealing line with the inner circumferential wall 8 and the upper delivery chamber is opened with the fully available cross section against the inlet 2.
  • Fig. 6 the opposite 0 ° / 360 ° position is shown.
  • the displacer 5 bears against the outer peripheral wall 9. In this position, the suction process is complete without the new measure.
  • the closing edge 13 On the outer peripheral wall 9, the closing edge 13 is advanced by the angle ⁇ relative to the plane which marks the 0 ° / 360 ° position. 5, the first sealing line occurs considerably earlier on the occasion of the circular movement of the displacer 5 compared to the conventional case. The suction process is therefore ended earlier.
  • the volume enclosed in the working space 12 is, in view of the explanations relating to FIG. 2, greater than that which is shown in FIG. 6. That means nothing else than that the desired compression process starts earlier. For this, however, it is necessary that from the closing point 13 to the 0 ° position permanently is sealed so that there is no backflow from the working space 12 into the inlet 2.
  • radius R2 is a function of the displacer leading edge. If the displacement body 5 were terminated with a sharp edge, the radius R2 would correspond to the eccentricity e. In the example shown with a semicircular end, the radius R2 corresponds to the sum of the radii R1 of the semicircle and e to the eccentricity.
  • the displacer position according to Fig. 4, i.e. The 270 ° position is only intended to show that the new measure does not really impair the inlet flow cross-section. Furthermore, it goes without saying that the closing edge 13 does not have to be sharp-edged per se. A possibly more favorable flow-wise transition of the circular arc 9 'to the channel wall of the inlet 2 is easily conceivable.
  • the spiral section under consideration on the outer circumferential wall 9, of which only the first 360 ° of the overall wrap is essential - the section that encompasses the crescent-shaped working space 12 after the suction has ended - is composed of two semicircles with the radii 68 mm and 52 mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Reciprocating Pumps (AREA)
  • Screw Conveyors (AREA)
EP88120415A 1987-12-21 1988-12-07 Rotationskolben-Verdrängungsmaschine Expired - Lifetime EP0321782B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88120415T ATE67273T1 (de) 1987-12-21 1988-12-07 Rotationskolben-verdraengungsmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4981/87 1987-12-21
CH4981/87A CH673679A5 (enrdf_load_stackoverflow) 1987-12-21 1987-12-21

Publications (2)

Publication Number Publication Date
EP0321782A1 EP0321782A1 (de) 1989-06-28
EP0321782B1 true EP0321782B1 (de) 1991-09-11

Family

ID=4285885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88120415A Expired - Lifetime EP0321782B1 (de) 1987-12-21 1988-12-07 Rotationskolben-Verdrängungsmaschine

Country Status (7)

Country Link
US (1) US4997348A (enrdf_load_stackoverflow)
EP (1) EP0321782B1 (enrdf_load_stackoverflow)
JP (1) JPH01200085A (enrdf_load_stackoverflow)
AT (1) ATE67273T1 (enrdf_load_stackoverflow)
CH (1) CH673679A5 (enrdf_load_stackoverflow)
DE (1) DE3864805D1 (enrdf_load_stackoverflow)
ES (1) ES2026245T3 (enrdf_load_stackoverflow)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5395222A (en) * 1989-11-02 1995-03-07 Matsushita Electric Industrial Co., Ltd. Scroll compressor having recesses on the scroll wraps
JPH04140492A (ja) * 1990-10-01 1992-05-14 Toshiba Corp ガス圧縮装置
EP0545190B1 (de) * 1991-12-05 1996-05-29 AGINFOR AG für industrielle Forschung Verdrängermaschine nach dem Spiralprinzip
DE59806600D1 (de) * 1997-08-26 2003-01-23 Crt Common Rail Tech Ag Spiralverdrängermaschine für kompressible Medien
CN103511293B (zh) * 2013-10-14 2016-05-18 黄少平 一种空气动力增能器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR48616E (fr) * 1936-12-23 1938-04-19 Perfectionnements au capsulisme à excentrique
CH586348A5 (enrdf_load_stackoverflow) * 1975-02-07 1977-03-31 Aginfor Ag
GB2033476A (en) * 1978-09-21 1980-05-21 Ingersoll Rand Co Rotary positive-displacement fluid-machines
DE3138585A1 (de) * 1981-09-29 1983-07-21 Volkswagenwerk Ag, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien
JPS58172405A (ja) * 1982-04-05 1983-10-11 Hitachi Ltd スクロ−ル流体機械

Also Published As

Publication number Publication date
DE3864805D1 (de) 1991-10-17
ES2026245T3 (es) 1992-04-16
EP0321782A1 (de) 1989-06-28
JPH01200085A (ja) 1989-08-11
CH673679A5 (enrdf_load_stackoverflow) 1990-03-30
US4997348A (en) 1991-03-05
ATE67273T1 (de) 1991-09-15

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