EP0392231A2 - Appareil de commande pour compresseur à piston rotatif - Google Patents

Appareil de commande pour compresseur à piston rotatif Download PDF

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Publication number
EP0392231A2
EP0392231A2 EP90105480A EP90105480A EP0392231A2 EP 0392231 A2 EP0392231 A2 EP 0392231A2 EP 90105480 A EP90105480 A EP 90105480A EP 90105480 A EP90105480 A EP 90105480A EP 0392231 A2 EP0392231 A2 EP 0392231A2
Authority
EP
European Patent Office
Prior art keywords
rotary
valve
control device
inlet
compressor
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.)
Withdrawn
Application number
EP90105480A
Other languages
German (de)
English (en)
Other versions
EP0392231A3 (fr
Inventor
Uwe Münkel
Christiane Römuss
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.)
Howden Turbo GmbH
Original Assignee
Siemens Turbomachinery Equipment GmbH
Kuehnle Kopp and Kausch AG
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 Siemens Turbomachinery Equipment GmbH, Kuehnle Kopp and Kausch AG filed Critical Siemens Turbomachinery Equipment GmbH
Publication of EP0392231A2 publication Critical patent/EP0392231A2/fr
Publication of EP0392231A3 publication Critical patent/EP0392231A3/fr
Withdrawn legal-status Critical Current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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the invention relates to a control device for a rotary compressor according to the features specified in the preamble of claim 1.
  • Such a control device for an internal-axis rotary piston compressor is known from EP 290 864 A2.
  • This rotary piston compressor contains an outer rotor in a housing, with which an inner rotor with n engaging parts is in meshing engagement.
  • the outer rotor has n + 1 working chambers, the volume of which is varied in accordance with the angular position of the inner rotor and outer rotor and which are rotated past inlet and outlet openings.
  • the internal-axis rotary lobe compressor can be used to charge motor vehicle engines.
  • a valve arrangement is provided between the inlet opening and the outlet opening, which is used on the one hand for part-load control and on the other hand to limit the boost pressure in the full-load range.
  • an internal-axis rotary piston compressor is known from EP 285 100 A2 for charging motor vehicle engines. which contains a valve for air circulation control in the partial load range.
  • the housing has an opening in the area in which compression occurs in the rotating working chambers. This opening is connected to the outlet opening via the valve mentioned. If the valve is closed, the maximum possible pressure is built up according to the internal compression. If, on the other hand, the valve is open, the pressure is built up only partially. The valve is either closed or fully open, so that fine control is not possible. Difficulties can arise in practice when using such valves with valve springs, especially since precise control is hardly possible in cooperation with the valve spring. Furthermore, vibrations and wear, which require additional measures, must be taken into account in such valves.
  • a control device for rotary piston machines with a control slide which is designed as a rotary slide.
  • This rotary slide valve is arranged axially parallel to the machine axis and, depending on the respective rotary position of the rotary slide valve, the position of a recess on the circumference of the rotary slide valve is changed continuously relative to the working chamber of the rotary piston machine.
  • the volume of the working chamber can be changed to enable the power to be continuously adjusted.
  • the object of the invention is to design the control device of the generic type with little design effort such that the pressure characteristics can be defined in a simple manner and, at the same time, noise reduction can be achieved.
  • the proposed control device is characterized by a functionally reliable construction and enables precise control of the rotary lobe compressor.
  • the pressure chamber is connected to the working chamber and / or the inlet chamber in accordance with the respective rotary position of the rotary valve.
  • the rotary valve enables precise control of the pressure in the pressure chamber of the compressor, depending on the respective angles of rotation thereof. Particularly when used to charge a motor vehicle engine, the noticeable reduction in noise is important, which results when the internal compression corresponds to the external compression and pressure surges are thus avoided. Furthermore, the small space and / or weight requirement of the control device when using the rotary piston compressor for charging a motor vehicle engine is important.
  • the rotary valve is rotatably mounted in a bore in a housing part and both the housing part and the rotary valve can be produced inexpensively in large quantities.
  • the housing part receiving the rotary slide valve is expediently an integral part of the compressor housing; Within the scope of the invention, the housing part can also be a separate component which is connected to the compressor via corresponding lines.
  • the compressor housing In the compressor housing there is a pre-inlet for connection to the working chamber in which the pressure is built up. Via the pre-inlet and in cooperation with the rotary valve, a connection can be opened or closed more or less between said working chamber and the pressure chamber. A continuous and position-dependent change in the cross-sectional area of the connection mentioned is achieved by means of the rotary valve.
  • the rotary valve is designed in such a way that the pressure chamber is connected to the inlet chamber as a function of its rotational angle position, in particular for the purpose of overpressure limitation in full-load operation of a motor vehicle engine.
  • the rotary piston compressor has a compressor housing 2 with an inlet chamber A, an inlet opening 5 and a pressure chamber 6 and outlet opening 7.
  • An outer rotor 8 is arranged in the compressor housing 2 so as to be rotatable about a longitudinal axis perpendicular to the plane of the drawing.
  • the outer rotor 8 contains three engagement parts 10 and between these three working chambers 12.
  • An inner rotor 14 is arranged eccentrically in the outer rotor 8 and is in tooth-tooth-like contact via its side surfaces with the engagement parts 10.
  • the inner rotor 14 and correspondingly the outer rotor 8 can have a different number of engagement parts.
  • the illustrated, diametrically opposite arrangement of inlet chamber 4 and pressure chamber 6 in the compressor housing 2 is expedient, as a result of which favorable flow conditions with minimal turbulence and deflections are achieved.
  • a rotary slide valve 22 with a recess 24 is rotatably arranged in a housing part 20; a second recess is contained outside the plane of the drawing in the rotary slide valve, as will be explained below with reference to FIG. 4.
  • This housing part 20 is expediently an integral part of the compressor housing 2, but it can also be designed as a separate housing part, the channels or lines to the compressor housing 2 explained below being provided accordingly.
  • a channel 26 leads to the pressure chamber 6 and a return line 28 to the inlet chamber 4.
  • a pre-inlet 30 is provided in the compressor housing 2. This pre-inlet 30 is seen in the direction of rotation 32 of the outer rotor 8 between the rear control edge 34 of the inlet chamber 4 and the front control edge 36 of the pressure chamber 6.
  • the pre-inlet 30 is arranged such that in the rotational position of the rotary valve 22 shown, the conveyed medium, in particular air, flows through the pre-inlet and the channel 26 to the pressure chamber 6 without being compressed.
  • the angular position of the pre-inlet 30 is predetermined as a function of the geometry of the outer rotor and the control edges of the compressor housing 2, so that no internal compression occurs in the case of recirculation control in the partial load range of a motor vehicle engine.
  • a second pre-inlet is arranged in the same way as the pre-inlet 30 shown in the direction of the longitudinal axis.
  • a channel 26 is arranged in the housing 2 over the entire width. The return line 28 is shut off in the case of circulating air control by means of the rotary valve 22.
  • FIG. 2 shows an axial section through the compressor housing 2, the outer rotor and the inner rotor not being shown are.
  • the compressor housing 2 is cup-shaped and is closed with a cover after the installation of the rotors on the right side in the drawing.
  • the pressure chamber 6 with the outlet opening 7 opens into the cylindrical inner wall 44 of the compressor housing 2.
  • the aforementioned channel 26 also opens into the pressure chamber 6.
  • the cylindrical inner wall 44 has two slots 46, 47 of the pre-inlets 30 already explained above.
  • the slots 46, 47 are arranged obliquely, so that a continuous change in the opening cross section is made possible in accordance with the rotational angle position of the rotary valve.
  • the slot 46 has an "upper" end 66. From the rotary valve, only an outwardly directed piston rod 48 can be seen.
  • FIG. 3 shows a top view of the compressor housing 2 with an actuator 50, which has a control lever 52. At the free end of the control lever 52 there is a rack 54, which is in engagement with a pinion 56 of the piston rod 48. With the actuator 50, the piston rod 48 and the rotary slide valve can thus be rotated about the axis 58.
  • Fig. 4 shows an axial section along the axis 58 of the rotary valve 22 in the housing part 20.
  • the rotary valve 22 has two recesses 24, 25 which cooperate with the two pre-inlets and channels mentioned.
  • the first recess 24 and the second recess 25 are arranged at a distance from one another in the axial direction and are otherwise designed to be identical; in particular the angular position with respect to the axis 58 of the rotary valve 22 is the same.
  • the rotary slide valve 22 also contains an additional recess 27 which is assigned to the return line into the inlet chamber.
  • the axial length of the additional Recess 27 is expediently smaller than the axial distance between the two recesses 24, 25.
  • the rotary slide valve 22 is rotatably mounted in the housing part 20 by means of roller bearings 60.
  • the bore of the housing part 20 receiving the rotary slide valve 22 is sealed off with a cover 62.
  • the above-mentioned recesses 24, 25 and 27 are designed as perforations which are rectangular in cross section and perpendicular to the axis of rotation 58 of the rotary slide 22, with straight control edges correspondingly being present.
  • the bottom surfaces of the recesses 24, 25 and 27 extend up to the axis of rotation 58 and are expediently aligned parallel to one another. In cooperation with the diagonally arranged pre-inlets, a continuous change in the cross-section to be released or blocked can take place in accordance with the rotational angle position of the rotary valve 22.
  • control edges of the recesses 24, 25 and 27 can also be designed, for example, as curved curves in order to obtain the desired dependence of the released cross-sectional area on the current rotational position.
  • the cross-sectional area to be released by means of the recesses 24, 25 for the pre-inlet or the two pre-inlets is larger than the cross-sectional area to be released with the additional recess 27 corresponding to the return line 28 smaller amount of air to be returned through the return line.
  • the rotary slide valve in the sectional plane along the section line AC according to FIG. 2 is shown in different rotational angle positions.
  • the rotary slide valve 22 is rotated counterclockwise by an angle.
  • the control edge 64 of the recess 24 already partially covers the pre-inlet 30.
  • a second recess is arranged axially spaced apart from the recess 24 shown here.
  • the following explanations for recess 24 apply accordingly to said second recess.
  • dash-dotted line 66 indicates the upper end of the sloping slot and pre-inlet. The rotary valve is brought into the position shown for full internal compression in full load operation.
  • the pre-inlet 30 is completely shut off by the rotary valve 22. 6, the maximum boost pressure for full-load operation is reached.
  • the compression ratio corresponds to the internal compression of the compressor. Even with a further rotation of the rotary valve 22 counterclockwise, the pre-inlet 30 is still blocked according to FIG. 7.
  • FIG. 10 Another operating state is explained with reference to FIG. 10.
  • the rotary slide valve 22 is rotated clockwise by approximately 45 °.
  • the channel 26, the pre-inlet 30 and the return line 28 are connected to one another via the recess 24, 25 as well as via the second recess, not shown here.
  • the rotary valve 22 assumes this position in partial load operation when the throttle valve of the motor vehicle engine is closed.
  • a pressure equalization takes place in partial load operation between the pressure chamber and the inlet chamber, so that the compressor works in idle mode and does not deliver against the closed throttle valve.
  • FIG. 11 shows an expedient embodiment of the actuator 50, which is designed here as a control box with a membrane 70 and two springs 72, 74.
  • This control box contains on the one hand a connection 76 and on the other hand the outwardly directed control lever 52 with the rack 54, which acts on the pinion 56 and thus on the rotary valve.
  • the connection 76 is connected via a line to a collector which is present between the throttle valve and the motor vehicle engine.
  • the two springs are in the zero position shown 72, 74 biased. In this position, the rotary slide valve assumes the rotational angle position shown in FIG. 1. 11, the control lever 52 is shifted to the left against the force of the spring 72 and the pinion 56 is rotated counterclockwise, the rotary valve assuming the rotational angle positions explained with reference to FIGS.
  • the control box contains a cup-shaped membrane plate 78, the free end face 80 of which serves as a stop to limit the maximum movement.
  • the end face 80 has reached the housing base according to the arrow 82, the maximum possible movement has been carried out and the rotary slide valve has assumed the position shown in FIG. 9. If the throttle valve is closed in part-load operation, a negative pressure is present at the connection 76, with the result that the control lever 52 is moved to the right according to FIG. 11.
  • the spring 74 is arranged within a cup-shaped part 84, which has a flange 86. A stop to limit the maximum movement in the negative direction is thus reached.
  • the rotary slide valve has assumed the rotational angle position shown in FIG. 10. Only the spring 72 is effective for the movement of the actuator within the area indicated by arrow 82. If, on the other hand, a movement in the area indicated by arrow 88 is carried out as a result of a negative pressure at connection 76, then the two springs 72 and 74 are effective.
  • the actuator described and designed as a control box enables the rotary slide valve to move in a positive direction in a positive manner in a positive direction in accordance with arrow 82 from part-load operation to full-load operation, including overpressure limitation. Furthermore, the movement in the other, negative direction is made possible for the partial-load operation when the throttle valve is closed.
  • FIG. 12 and 13 show a further embodiment, the rotary slide valve 22 including the housing part 22 now being integrated directly into the compressor housing 2.
  • the position of the rotary slide valve 22 corresponds to that of FIG. 10.
  • the pressure chamber 6 is connected to the inlet chamber 4 via the return line 28.
  • the working chamber is also connected to both the pressure chamber and the inlet chamber.
  • a position of the rotary slide valve 22, which corresponds to that of FIG. 1, is indicated by dash-dotted lines in FIG. 12.
  • the rotary slide valve 22 has no straight control edges in this embodiment. 13, an arcuate recess 90 is provided in the middle with a curved control edge 92, which merges into straight control edge regions at the axial ends. There may also be a curved curve or a milled surface.
  • the return line 28 is shut off and on the other hand a connection between the pre-inlet 30 and the pressure chamber 6 is created due to the arcuate central recess.
  • the pre-inlet is formed here by the free area between the contact surface 96 of the rotary valve 22 on the outer rotor and an outlet control edge 94 of the compressor housing 2.
  • control device in connection with an internal-axis rotary compressor does not limit the invention to such. Rather, the control device with the rotary slide valve can be used for rotary piston compressors of another type, a screw compressor and a roots blower being mentioned here by way of example.
  • a particularly electrically controlled servo motor, a hydraulically actuated actuating device or the like can be provided for adjusting the rotary slide valve.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP19900105480 1989-04-08 1990-03-23 Appareil de commande pour compresseur à piston rotatif Withdrawn EP0392231A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3911541 1989-04-08
DE3911541A DE3911541C1 (fr) 1989-04-08 1989-04-08

Publications (2)

Publication Number Publication Date
EP0392231A2 true EP0392231A2 (fr) 1990-10-17
EP0392231A3 EP0392231A3 (fr) 1991-01-09

Family

ID=6378234

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900105480 Withdrawn EP0392231A3 (fr) 1989-04-08 1990-03-23 Appareil de commande pour compresseur à piston rotatif

Country Status (5)

Country Link
EP (1) EP0392231A3 (fr)
JP (1) JPH02298691A (fr)
BR (1) BR9001635A (fr)
DE (1) DE3911541C1 (fr)
ZA (1) ZA902653B (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH685450A5 (de) * 1992-04-01 1995-07-14 Lindau Tech Forsch & Entw Gmbh Innenachsige Drehkolbenmaschine.
JPH08319839A (ja) * 1995-05-25 1996-12-03 Tochigi Fuji Ind Co Ltd スーパーチャージャ
DE102007060174A1 (de) * 2007-12-13 2009-06-25 Oerlikon Leybold Vacuum Gmbh Vakuumpumpe sowie Verfahren zum Betreiben einer Vakuumpumpe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE285468C (fr) *
DE423832C (de) * 1920-12-03 1926-01-12 Arnold Zoller Mehrstufiger Kompressor mit umlaufenden Fluegeln fuer Explosionskraftmaschinen
US1859264A (en) * 1924-06-21 1932-05-17 Zoller Arnold Engine provided with alpha rotary compressor
DE1024196B (de) * 1955-05-11 1958-02-13 Borsig Ag Vorrichtung zum Regeln der Foerderleistung von Drehkolbenverdichtern
EP0118039A1 (fr) * 1983-02-04 1984-09-12 Hitachi, Ltd. Machine à déplacement positif avec contrôle du volume refoulé
DE3528502A1 (de) * 1985-08-08 1987-02-19 Pierburg Gmbh & Co Kg Vorrichtung zum steuern einer drehkolbenmaschine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63243482A (ja) * 1987-03-31 1988-10-11 Aisin Seiki Co Ltd 回転ロ−タ装置
DE3716083A1 (de) * 1987-05-14 1988-11-24 Kuehnle Kopp Kausch Ag Innenachsige drehkolbenmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE285468C (fr) *
DE423832C (de) * 1920-12-03 1926-01-12 Arnold Zoller Mehrstufiger Kompressor mit umlaufenden Fluegeln fuer Explosionskraftmaschinen
US1859264A (en) * 1924-06-21 1932-05-17 Zoller Arnold Engine provided with alpha rotary compressor
DE1024196B (de) * 1955-05-11 1958-02-13 Borsig Ag Vorrichtung zum Regeln der Foerderleistung von Drehkolbenverdichtern
EP0118039A1 (fr) * 1983-02-04 1984-09-12 Hitachi, Ltd. Machine à déplacement positif avec contrôle du volume refoulé
DE3528502A1 (de) * 1985-08-08 1987-02-19 Pierburg Gmbh & Co Kg Vorrichtung zum steuern einer drehkolbenmaschine

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, unexamined applications, M Sektion, Band 7, Nr. 165, 20. Juli 1983 THE PATENT OFFICE JAPANESE GOVERNMENT Seite 127 M 230 * JP - A - 58 - 72 687 ( JIDOSHA ) * *
PATENT ABSTRACTS OF JAPAN, unexamined applications, M Sektion, Band 9, Nr. 187, 3. August 1985 THE PATENT OFFICE JAPANESE GOVERNMENT Seite 89 M 401 * JP - A - 60 - 53 692 ( MATSUSHITA ) * *

Also Published As

Publication number Publication date
EP0392231A3 (fr) 1991-01-09
DE3911541C1 (fr) 1990-03-29
BR9001635A (pt) 1991-05-07
ZA902653B (en) 1991-01-30
JPH02298691A (ja) 1990-12-11

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