EP1722104A2 - Rotors pour un compresseur à vis - Google Patents

Rotors pour un compresseur à vis Download PDF

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Publication number
EP1722104A2
EP1722104A2 EP06008149A EP06008149A EP1722104A2 EP 1722104 A2 EP1722104 A2 EP 1722104A2 EP 06008149 A EP06008149 A EP 06008149A EP 06008149 A EP06008149 A EP 06008149A EP 1722104 A2 EP1722104 A2 EP 1722104A2
Authority
EP
European Patent Office
Prior art keywords
profile
rotors
screw
rotor pair
screw 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.)
Granted
Application number
EP06008149A
Other languages
German (de)
English (en)
Other versions
EP1722104B1 (fr
EP1722104A3 (fr
Inventor
Harald Martin
Ronald Dr. Sachs
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.)
Pfeiffer Vacuum GmbH
Original Assignee
Pfeiffer Vacuum 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
Application filed by Pfeiffer Vacuum GmbH filed Critical Pfeiffer Vacuum GmbH
Publication of EP1722104A2 publication Critical patent/EP1722104A2/fr
Publication of EP1722104A3 publication Critical patent/EP1722104A3/fr
Application granted granted Critical
Publication of EP1722104B1 publication Critical patent/EP1722104B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04C18/14—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 toothed rotary pistons
    • F04C18/16—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 toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • 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
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum

Definitions

  • the invention relates to a pair of rotors for a screw compressor, wherein the rotors are in meshing, non-contact engagement, the rotors each having at least one gear and a steady change in pitch, wherein the shape of the rotors is determined by a screw profile.
  • Screw compressors have been used successfully for some years on the one hand in compressor construction and on the other hand for the production of vacuum. In them rotate synchronously and in opposite directions two rotors, which mesh with each other without contact. These rotors have screw threads with opposite directions of rotation, often referred to as left and right. There is no use of sealants and lubricants such as oil in the working space of the machines, which explains part of the success.
  • a change in the pitch of the threads causes a change in the volume trapped between the rotors and the housing and thus creates a corresponding compression of the gas trapped in the volume.
  • a pressure gradient forms, i. Distributed over the axial length different pressures occur.
  • the characteristics of the compressors and the effort required to manufacture the rotors are largely determined by the design of the screw rotors. This shape is characterized by the screw profile. This can be described by the profile outline, which results, for example, in the axis or in the face section.
  • the DE-OS 199 41 787 looks at the profile outline of the tooth, which results in the axial section. It proposes to provide an area along the contour line with a straight section in which a left-handed and a right-handed Facing the rotor. This area is also called profile intervention.
  • the proposed measure does away with undercuts that make the production complex and expensive. However, this must be compromised in the tightness to be accepted, ie the vacuum technical properties are worse than the ideal.
  • the tooth profiles proposed and cited in this document are based on the gearing law.
  • the invention is therefore based on the object to eliminate the disadvantages of the prior art, to develop a relation to the characteristics of the compressor improved screw rotor pair and to create a design flexibility that goes beyond the prior art.
  • the object is achieved by a pair of rotors for a screw compressor, which is characterized in that the profile type of the screw is different at least two axially spaced locations along the rotors and that the adapted to the respective pressure range profile types continuously merge into each other.
  • Screw profiles can not only be characterized by the profile outline as in the prior art. In the context of the invention, it proved to be advantageous to classify the screw profiles in profile types. This arrangement takes place via the sealing effect on the profile engagement, which results from the respective profile type. Different profiles produce the sealing effect at radially different locations of the rotor. There are those which achieve the optimum sealing effect in the circumferential direction at an outer radial region (for example so-called Quimby profiles). Other profiles seal almost completely in the radial direction but over a small part of the circumference. The distance between the two rotors in the axial direction at these sealing points, also referred to as gap height, determines the quality of the seal, but not the basic type.
  • the presented measures make it possible to change the shape of the gap, which exists on the profile engagement between the rotors, along the rotor axis and in each case to optimally adapt to the pressure conditions and tightness requirements.
  • Basis of the design is thus the gap type and not the gearing law as in the prior art.
  • the rotors Due to the continuous transition from one profile type to the next, the rotors can be manufactured in one piece. Above all, there are no steps and edges in the interior of the screw threads, which would adversely affect their gas-promoting and -compacting performance.
  • the change in pitch of the screw threads takes place in such a way that it is zero in certain areas. This allows an adaptation of the compression curve along the rotor axis to the flow or printing area. Since the compaction is controlled, among other things, via the slope and heat is generated during the compression of gases, the change in slope can influence the heat balance of the compressor.
  • the steady change in slope is such that the slope progression is described by a third degree curve. This allows the simplest possible transition from one pitch to the next.
  • a further advantage results if the change in pitch and the profile change at least in sections along the axis are not simultaneous. This measure results in a partial decoupling of the change in compression from the change in slope.
  • the profile type can be constant over an axial region, whereby a plurality of such regions can be present over the rotor length. This represents a further simplification of the production without having to forego the advantages that result from the combination of the profile types.
  • FIG. 1 shows the rotor pair in a view of the plane spanned by the rotor axes.
  • the rotor pair is formed by a left rotor 1 and a right rotor 2, these each having a shaft 3, 4.
  • On this wave screw flights are applied as pump-active structures, which are formed in the right-hand 5 and left-hand 6.
  • a compression of the pumped medium for example a gas mixture, can be achieved.
  • the rotors are in meshing, non-contact engagement. At this engagement is located between the rotors of the profile engagement gap.
  • the medium is conveyed in the figure from bottom to top and compacted. This is indicated by the block arrow.
  • FIG. 2a shows the partial frontal section through the rotor pair at height I-I '.
  • the rotors 1 and 2 mesh with each other, ie in this sight, the screw threads overlap 5 and 6 and each push close to the shaft 3 or 4.
  • Dark colored and marked 8 is the area of the highest sealing effect between the rotors.
  • the designated 9 area has only a small sealing effect, which is indicated by the two broad arrows that symbolize gas flow.
  • the shape of the high sealing area is characteristic of the profile type.
  • the shown shape of the region 8 is almost exclusively radially between the two waves.
  • the high sealing effect in this area is paid for by a stronger overflow at the areas 9.
  • Such a type of profile is simple and inexpensive to manufacture. It is used in the embodiment at a point of high pressure, where the overflow 9 leads to a distribution of the gas heated by the compression. This influences the heat balance of the vacuum pump.
  • the axial section shown in Figure 3 illustrates the importance of profile type and gap height.
  • the curves 10 and 11 describe the helical profile of the rotors 1 and 2.
  • the curves 10 'and 11' are shown, which correspond to a different design of the rotors. Due to the higher distance of the curves results in a larger gap width S '. Although this deteriorates the quality of the gasket, in both cases it is the same type of profile.
  • FIG. 2b shows, in a section on the rotor height II-II ', an "S" -shaped course of the region of highest sealing effect 8 while there are two regions 9 in which gas can flow over between the rotors.
  • This type of profile represents a compromise of manufacturing and vacuum requirements.
  • Figure 2c as a section through the rotors at height III-III 'shows a transitional shape or mixed shape between the profile types 2b and 2d.
  • the sealing area 8 is formed predominantly along the circumference (as in FIG. 2d), but also has an extent in the radial direction, the latter not lying directly between the shaft axes (therefore, as in FIG. 2b).
  • FIG. 2d as a section through the rotors at height IV-IV 'again shows a profile type with a sealing region 8 divided into two partial regions. It is formed along the contacting circumferential lines of the rotors.
  • the shown shape of the region 8 is generated by a so-called Quimby curve in the profile of the tooth on the engagement gap. The occurring gaps are small, the sealing effect is altogether high, which is why this profile type is very well suited for high pressures.
  • this type of profile is comparatively complicated and expensive to manufacture.
  • the four profile types shown in FIGS. 2a to 2d continuously merge into one another, so that different profile types are present at at least two axial locations of the rotors.
  • a profile type can be constant over a longer axial section before the transition to another profile type begins.
  • the continuous transition of the profile types results in mixed variants of the profile types.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP06008149.4A 2005-05-14 2006-04-20 Paire de rotors pour un compresseur à vis Not-in-force EP1722104B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510022470 DE102005022470B4 (de) 2005-05-14 2005-05-14 Rotorpaar für Schraubenverdichter

Publications (3)

Publication Number Publication Date
EP1722104A2 true EP1722104A2 (fr) 2006-11-15
EP1722104A3 EP1722104A3 (fr) 2014-01-01
EP1722104B1 EP1722104B1 (fr) 2016-04-13

Family

ID=36699179

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06008149.4A Not-in-force EP1722104B1 (fr) 2005-05-14 2006-04-20 Paire de rotors pour un compresseur à vis

Country Status (2)

Country Link
EP (1) EP1722104B1 (fr)
DE (1) DE102005022470B4 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104454523A (zh) * 2014-11-25 2015-03-25 巫修海 一种螺杆真空泵的螺杆

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19941787A1 (de) * 1999-09-02 2001-03-08 Leybold Vakuum Gmbh Schraubenvakuumpumpe mit Schraubengängen mit sich verändernder Steigung
WO2002057044A1 (fr) * 2001-01-19 2002-07-25 Ralf Steffens Contour profile d'une pompe a broche helicoidale
WO2002103205A1 (fr) * 2001-06-19 2002-12-27 Ralf Steffens Contour profile des rotors helicoidaux d'une pompe a vis
US20030152475A1 (en) * 2000-07-25 2003-08-14 Becher Ulrich F. Twin screw rotors and displacement machines containing the same

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2329800A1 (de) * 1972-07-06 1974-01-17 H & H Licensing Corp Verfahren und vorrichtung zum verdichten von gasfoermigen medien in schraubenkompressoren
KR0133154B1 (ko) * 1994-08-22 1998-04-20 이종대 무단 압축형 스크류식 진공펌프
KR100386753B1 (ko) * 1998-03-23 2003-06-09 다이코 기카이 고교 가부시키가이샤 드라이 진공펌프
DE10334484A1 (de) * 2003-07-29 2005-03-24 Steffens, Ralf, Dr. Trockenverdichtende Spindelvakuumpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19941787A1 (de) * 1999-09-02 2001-03-08 Leybold Vakuum Gmbh Schraubenvakuumpumpe mit Schraubengängen mit sich verändernder Steigung
US20030152475A1 (en) * 2000-07-25 2003-08-14 Becher Ulrich F. Twin screw rotors and displacement machines containing the same
WO2002057044A1 (fr) * 2001-01-19 2002-07-25 Ralf Steffens Contour profile d'une pompe a broche helicoidale
WO2002103205A1 (fr) * 2001-06-19 2002-12-27 Ralf Steffens Contour profile des rotors helicoidaux d'une pompe a vis

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104454523A (zh) * 2014-11-25 2015-03-25 巫修海 一种螺杆真空泵的螺杆

Also Published As

Publication number Publication date
DE102005022470B4 (de) 2015-04-02
DE102005022470A1 (de) 2006-11-16
EP1722104B1 (fr) 2016-04-13
EP1722104A3 (fr) 2014-01-01

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