EP1640613B1 - Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters - Google Patents

Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters Download PDF

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Publication number
EP1640613B1
EP1640613B1 EP04022170A EP04022170A EP1640613B1 EP 1640613 B1 EP1640613 B1 EP 1640613B1 EP 04022170 A EP04022170 A EP 04022170A EP 04022170 A EP04022170 A EP 04022170A EP 1640613 B1 EP1640613 B1 EP 1640613B1
Authority
EP
European Patent Office
Prior art keywords
feed chamber
rotary piston
piston compressor
question
inflow
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
EP04022170A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1640613A1 (de
EP1640613A8 (de
Inventor
Norbert Düwel
Hans-Ulrich Fleige
Christian-Philipp Hage
Günter Seidel
Olaf Tanner
Oliver Palm
Björn IRTEL
Ditmar Lenger
Hans Nissen
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.)
Aerzener Maschinenfabrik GmbH
Original Assignee
Aerzener Maschinenfabrik GmbH
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
Priority to PL04022170T priority Critical patent/PL1640613T3/pl
Application filed by Aerzener Maschinenfabrik GmbH filed Critical Aerzener Maschinenfabrik GmbH
Priority to DE502004002191T priority patent/DE502004002191D1/de
Priority to EP04022170A priority patent/EP1640613B1/de
Priority to AT04022170T priority patent/ATE347036T1/de
Priority to ES04022170T priority patent/ES2276204T3/es
Priority to DK04022170T priority patent/DK1640613T3/da
Priority to US11/228,238 priority patent/US20060067835A1/en
Publication of EP1640613A1 publication Critical patent/EP1640613A1/de
Publication of EP1640613A8 publication Critical patent/EP1640613A8/de
Application granted granted Critical
Publication of EP1640613B1 publication Critical patent/EP1640613B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C18/12—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 of other than internal-axis type
    • F04C18/126—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 of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type

Definitions

  • the present invention relates to a rotary compressor for compressing gaseous media, comprising two wound rotors enclosed by a housing, each having at least three vanes for forming a number of delivery chambers between the vanes and the inner wall of the housing, and a method for operating such a rotary compressor.
  • Rotary or Roots compressor of the type mentioned are long known and disclosed for example in DE 33 21 992 A1, DE 34 14 039 C2 or DE 34 14 064 C2. Due to increased demands, rotary piston compressors are now operated at high speeds, whereby the gas mass flow is increased accordingly. However, the increased speeds have the consequence that for each individual intake inevitably only a smaller amount of time is available. This has the disadvantageous effect of a poorer filling (lower degree of delivery) and thus a reduction in the per mass of rotation promoted gas mass. The increase in the mass flow of the compressible, gas or fluid Medium thus takes place only to a lesser extent than the increase in speed. This results in a limited or decreasing volumetric efficiency.
  • the present invention is based on the idea to increase the degree of delivery of the rotary compressor in that generated in the respective delivery chamber, a fluid dynamic shock in the fluid to be compressed and used selectively.
  • the filling in the respective delivery chamber is significantly increased and thus achieved a very good degree of delivery even at higher speeds.
  • to achieve a pressure surge in known rotary compressors often only minor structural and / or operational adjustments or changes required, so that the principles of the present invention are economically applicable.
  • the generation of a pressure surge is carried out according to the invention by a flow through a delivery chamber with velocity component in the delivery chamber longitudinal direction and rapid separation of the respective delivery chamber from the area of increase in volume. This is for efficient use of the fluid dynamic shock generated thereby According to the invention provided that the inflow side of the respective delivery chamber is still open to the intake and only at a suitable time, but before a connection of the relevant delivery chamber to the pressure side, is closed so that increases the filling of the delivery chamber by shock charging.
  • a closing time from the separation of the relevant delivery chamber through which the delivery chamber extends is increased from the region of increase in volume until the relevant delivery chamber is closed on the inflow side such that the filling of the delivery chamber is increased by impact charging becomes.
  • gas-dynamic shock refers to a phenomenon, as occurs for example in pipelines in a sudden closing of a slide upstream of the slide. This creates a pressure front, which moves approximately at the speed of sound upstream through the medium. This dynamic process adds another component to the static pressure in the medium, increasing the pressure and, for compressible media, the degree of filling.
  • the operation of the rotary compressor by changing controlled geometric variables and / or the rotational speed of the rotary compressor, taking into account the temperature and the type of gaseous medium.
  • the temperature and the nature of the gaseous medium determine the rate of propagation of a gas-dynamic impact within the medium and are therefore specifically taken into account in the operation of the rotary compressor according to the invention.
  • the speed of the rotary compressor has an immediate effect on the closing time and the separation time to be discussed below and is therefore an important parameter in the operation of a rotary compressor according to the invention.
  • the individual geometric parameters will be discussed in more detail below.
  • the rapid separation takes place within a separation time in which the rotors respectively pass through a rotation angle from the amount of the twisting angle and which is smaller than the 2.0.degree. ause the duration of the gas-dynamic shock for the passage of the respective delivery chamber in winningfflelCodesraum.
  • the separation time is to be gradually limited to 1.5 times, 1.0 times, 0.75 times and 0.5 times, respectively.
  • an inflow opening is preferably provided, which allows at least in phases an inflow, in conveying chamber longitudinal direction.
  • the starting point of this preferred embodiment is the fact that the pressure surge generated in the relevant delivery chamber generates a suction effect.
  • This suction effect is used according to the invention to increase the filling of the respective delivery chamber, wherein the medium required to increase the filling enters the relevant delivery chamber via the inflow opening.
  • the inflow opening is at least partially limited by a control edge, the shape of which preferably approximates that of a wing or tooth portion, which passes in advance during operation of the rotary compressor, the control edge.
  • a control edge the shape of which preferably approximates that of a wing or tooth portion, which passes in advance during operation of the rotary compressor, the control edge.
  • the inflow has an adjustable geometry, and in particular the control edge is adjustable.
  • the control edge is adjustable.
  • Fig. 1 shows a schematic perspective view of two twisted rotors 10, 20 for a rotary compressor according to the present invention.
  • the rotors 10, 20 are equipped in the present embodiment, each with three blades or teeth 12, 14, 16, 22, 24, 26 and are arranged to mesh with each other. At their respective ends, the rotors 10, 20 have only indicated waves 18, 28, by means of which the rotors can be rotatably mounted and driven in a housing or the like.
  • the rotors 10, 20 are wound around their longitudinal axis, wherein the degree of distortion can be given by an angle ⁇ , which indicates the twist angle between the respective ends of the rotors 10, 20.
  • the twist angle ⁇ is 40 ° in the present embodiment, although the present invention is not limited thereto. Rather, the torsion angle ⁇ may in principle assume any desired values, as long as it does not become so large that a short circuit between the pressure side and the suction side results.
  • FIG. 2 shows a schematic perspective view of a rotary compressor 1 as a preferred embodiment of the present invention.
  • the rotary piston compressor 1 shown in FIG. 2 contains the twisted rotors 10, 20 already described with reference to FIG. 1, which are enclosed by a housing 2 and are rotatably mounted therein via the shafts 18, 28. Between the wings or teeth 12, 14, 16, 22, 24, 26 of the rotors 10, 20 and an inner wall 2 'of the housing 2 conveying chambers 4 are formed, which are flowed through during the operation of the rotary compressor from a medium to be conveyed. It should be noted that during operation of the rotary compressor are continuously formed by two rotors 10, 20 delivery chambers and dissolved, but by way of example only one delivery chamber 4 is discussed below. Further, in the area between the rotors 10, 20, a region of volume increase V is formed, i. an area in which increases in a rotation of the rotors 10, 20, the volume between adjacent vanes and thereby feed medium is sucked.
  • the inflow of the pumped medium into the rotary compressor 1 takes place on an inflow side 4 'via inflow openings 30, which are provided in such a way that the inflow into the rotary compressor takes place at least partially axially.
  • the inflow openings 30 are, as can be seen in Fig. 2, each bounded on one side by a control edge 32, whose shape corresponds to that of a wing section, the control edge 32 passes in advance during operation of the rotary compressor.
  • a fixed control edge 32 is shown, the geometry of the control edge 32 can be adjustable in particular during operation of the rotary compressor 1.
  • the respective delivery chamber 4 is flowed through by the conveying medium in the longitudinal direction from an inflow side 4 'to an outlet side 4 ", i. in the direction from the viewer in Fig. 2 facing side to the side facing away from the viewer in Fig. 2.
  • the upstream ends of the vanes or teeth are designated 12 ', 14', 16 ', 22', 24 ', 26', while the opposite ends of the vanes are 12 ", 14". , 16 ", 22", 24 “, 26” (see also Fig. 1).
  • Fig. 3 shows "Phase I", in which in the region of the increase in volume V delivery medium is sucked into the rotary compressor 1, which is to be ejected later on the pressure side in the region of an ejection opening A.
  • the direction of rotation of the rotors 10, 20 is indicated by two arrows in Fig. 3 and the following Figs. the rotor 10 rotates counterclockwise while the rotor 20 rotates in the clockwise direction.
  • Phase II is initiated by the fact that the delivery chamber 4, between the teeth 12, 14 of the Rotor 10 and the inner wall 2 'of the housing 2 is formed, is separated from the area of the increase in volume V. This separation takes place in that the rear end 14 "of the rotor tooth 14 is brought into abutment with the housing inner wall 2 'at the point indicated in FIG. 4 by a suction-side ridge angle fs, and thus the delivery chamber 4 from the area of the increase in volume V.
  • a gas-dynamic impact is generated in the delivery chamber 4 approximately at the time shown in FIG.
  • the separation of the delivery chamber 4 from the region of the increase in volume V takes place in a period of time in which the rotors 10, 20 each pass through a rotation angle of the amount of the torsion angle ⁇ , which thus decreases with increasing speed.
  • phase II the delivery chamber 4 via the inflow opening 30 (see also Fig. 2) further connected to the inflow side, so that under the Effect of the gas-dynamic impact further medium enters the delivery chamber 4 and the filling of the delivery chamber 4 is continuously increased.
  • phase IV the delivery medium contained in the delivery chamber 4 is discharged to the discharge port A on the delivery side.
  • the phase IV is initiated in that the inflow-side end section 14 'of the tooth 14 passes over the line of the pressure-side ridge angle f D , so that the considered delivery chamber 4 is connected to the pressure side and the discharge opening A.
  • a state of the rotary pistons during phase IV is shown schematically in FIG. In this case, the delivery chamber 4 is connected to the discharge opening A and the medium is continuously ejected by the progressive rotation of the rotors 10, 20.
  • analogous processes to the above explanations take place in the other delivery chambers.
  • FIG. 7 A modified embodiment of the rotary compressor 1 is shown in Fig. 7 in a schematic sectional view, in a Fig. 4 corresponding operating phase.
  • the embodiment shown in Fig. 7 differs from the previous embodiment in that the control edge 32 has a contour whose shape approximates that of a wing portion, which in the operation of the Rotary compressor, the control edge 32 passes in advance.
  • the inflow of medium into the respective delivery chamber 4 can be effectively controlled by flowing large amounts of medium into the delivery chamber 4 until the end of the closing time t s , while the delivery chamber 4 is disconnected as quickly as possible when the closing time t s expires, in order to prevent in this way a "fuming" of the gas-dynamic shock generated in the delivery chamber 4 particularly effective and to achieve the best possible filling of the delivery chamber 4.
  • the control edge 32 may also assume a somewhat flattened shape than shown in FIG. 7 and, in a preferred embodiment, may also be adjustable as a function of the operating parameters of the rotary compressor 1, for example as a function of the operating speed, etc.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Toys (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP04022170A 2004-09-17 2004-09-17 Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters Expired - Lifetime EP1640613B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DE502004002191T DE502004002191D1 (de) 2004-09-17 2004-09-17 Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters
EP04022170A EP1640613B1 (de) 2004-09-17 2004-09-17 Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters
AT04022170T ATE347036T1 (de) 2004-09-17 2004-09-17 Drehkolbenverdichter und verfahren zum betreiben eines drehkolbenverdichters
ES04022170T ES2276204T3 (es) 2004-09-17 2004-09-17 Compresor de embolo giratorio y procedimiento para el funcionamiento de un compresor de embolo giratorio.
PL04022170T PL1640613T3 (pl) 2004-09-17 2004-09-17 Sprężarka z obrotowym tłokiem i sposób eksploatacji sprężarki z obrotowym tłokiem
DK04022170T DK1640613T3 (da) 2004-09-17 2004-09-17 Rotationskompressor og fremgangsmåde til drift af en rotationskompressor
US11/228,238 US20060067835A1 (en) 2004-09-17 2005-09-19 Rotary compressor and method of operating a rotary compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04022170A EP1640613B1 (de) 2004-09-17 2004-09-17 Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters

Publications (3)

Publication Number Publication Date
EP1640613A1 EP1640613A1 (de) 2006-03-29
EP1640613A8 EP1640613A8 (de) 2006-07-05
EP1640613B1 true EP1640613B1 (de) 2006-11-29

Family

ID=34926581

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04022170A Expired - Lifetime EP1640613B1 (de) 2004-09-17 2004-09-17 Drehkolbenverdichter und Verfahren zum Betreiben eines Drehkolbenverdichters

Country Status (7)

Country Link
US (1) US20060067835A1 (es)
EP (1) EP1640613B1 (es)
AT (1) ATE347036T1 (es)
DE (1) DE502004002191D1 (es)
DK (1) DK1640613T3 (es)
ES (1) ES2276204T3 (es)
PL (1) PL1640613T3 (es)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9127694B2 (en) 2011-09-09 2015-09-08 Woodward, Inc. High-flow electro-hydraulic actuator
WO2015109048A1 (en) * 2014-01-15 2015-07-23 Eaton Corporation Method of optimizing supercharger performance
US11009034B2 (en) 2014-01-15 2021-05-18 Eaton Intelligent Power Limited Method of optimizing supercharger performance
WO2016109551A1 (en) * 2014-12-30 2016-07-07 Eaton Corporation Optimal expander outlet porting
US10119478B2 (en) 2015-06-25 2018-11-06 Woodward, Inc. High reliability high flow redundant trip block

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3141604A (en) * 1962-09-26 1964-07-21 Gardner Denver Co Compressor supercharging system
DD209880A1 (de) * 1982-08-27 1984-05-23 Halle Maschf Veb Anordnung und gestaltung der aufladeeinlassoeffnungen an einem schraubenverdichter
SE457822B (sv) * 1986-11-28 1989-01-30 Svenska Rotor Maskiner Ab Foerfarande foer aastadkommande av selektivt styrda tryckpulser i en gasmassa samt anordning foer genomfoerande av foerfarandet
US5131829A (en) * 1991-06-19 1992-07-21 Eaton Corporation Trapped volume vent means for meshing lobes of roots-type supercharger
US5320508A (en) * 1993-08-05 1994-06-14 Eaton Corporation Rotary pump and rotor-shaft subassembly for use therein
DE19819538C2 (de) * 1998-04-30 2000-02-17 Rietschle Werner Gmbh & Co Kg Druck-Saug-Pumpe
EP1357275A1 (en) * 2002-04-26 2003-10-29 Visteon Global Technologies, Inc. Modelling of the thermal behaviour of a switched reluctance motor driving a supercharger of an internal combustion engine
US6732595B2 (en) * 2002-07-18 2004-05-11 Panametrics, Inc. Method of and system for determining the mass flow rate of a fluid flowing in a conduit
US6884050B2 (en) * 2003-04-16 2005-04-26 General Motors Corporation Roots supercharger with extended length helical rotors

Also Published As

Publication number Publication date
ES2276204T3 (es) 2007-06-16
EP1640613A1 (de) 2006-03-29
US20060067835A1 (en) 2006-03-30
DE502004002191D1 (de) 2007-01-11
PL1640613T3 (pl) 2007-04-30
EP1640613A8 (de) 2006-07-05
DK1640613T3 (da) 2007-03-26
ATE347036T1 (de) 2006-12-15

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