EP3134649A2 - Paire de rotors pour bloc de compresseur d'une visseuse - Google Patents

Paire de rotors pour bloc de compresseur d'une visseuse

Info

Publication number
EP3134649A2
EP3134649A2 EP15736405.0A EP15736405A EP3134649A2 EP 3134649 A2 EP3134649 A2 EP 3134649A2 EP 15736405 A EP15736405 A EP 15736405A EP 3134649 A2 EP3134649 A2 EP 3134649A2
Authority
EP
European Patent Office
Prior art keywords
rotor
tooth
profile
main
secondary rotor
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
EP15736405.0A
Other languages
German (de)
English (en)
Other versions
EP3134649B9 (fr
EP3134649B1 (fr
EP3134649B2 (fr
Inventor
Gerald WEIH
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.)
Kaeser Kompressoren AG
Original Assignee
Kaeser Kompressoren 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=53541638&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3134649(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Kaeser Kompressoren AG filed Critical Kaeser Kompressoren AG
Priority to EP19190907.6A priority Critical patent/EP3597920B1/fr
Priority to EP18163593.9A priority patent/EP3358189B9/fr
Priority to EP23198449.3A priority patent/EP4273403A3/fr
Publication of EP3134649A2 publication Critical patent/EP3134649A2/fr
Publication of EP3134649B1 publication Critical patent/EP3134649B1/fr
Publication of EP3134649B9 publication Critical patent/EP3134649B9/fr
Application granted granted Critical
Publication of EP3134649B2 publication Critical patent/EP3134649B2/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines 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
    • F01C1/16—Rotary-piston machines or engines 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
    • 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
    • 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
    • F04C18/20—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 dissimilar tooth forms
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the invention relates to a rotor pair for a compressor block a
  • a screw machine wherein the rotor pair consists of a main rotor rotating about a first axis and a secondary rotor rotating about a second axis according to the features of claim 1, 15 or 29. Furthermore, the invention relates to a compressor block with a corresponding pair of rotors.
  • Screw machines whether as screw compressors or as screw expanders, have been in practical use for several decades. Designed as screw compressors, they have forced reciprocating compressors as compressors in many areas. With the principle of the intermeshing screw pair not only gases can be compressed by applying a certain amount of work. The use as a vacuum pump also opens up the use of screw machines to achieve a vacuum. Finally, by passing pressurized gases the other way around, a workload can be generated, so that from pressurized gases by means of the principle of the screw machine and mechanical energy can be obtained.
  • Screw machines generally have two shafts arranged parallel to one another, on which, on the one hand, a main rotor and, on the other hand, a secondary rotor are seated. Main rotor and secondary rotor engage with corresponding helical Dovetailing into each other. Between the teeth and a compressor housing, are included in the main and secondary rotor, a compression space (working chambers) is formed by the tooth space volumes.
  • the working chamber is first closed and then continuously reduced in volume as the main and secondary rotor rotate, so that a compression of the medium occurs. Finally, as the rotation progresses, the working chamber is opened to a pressure window and the medium is ejected into the pressure window.
  • typical pressure ratios may be between 1, 1 and 20, the pressure ratio being the ratio of
  • Compression end pressure to suction pressure is.
  • the compression can be done in one or more stages.
  • Achievable ultimate pressures can be, for example, in the range 1, 1 bar to 20 bar.
  • Screw machines can, in addition to the already mentioned function as
  • Vacuum pump or used as a screw expander in various fields of technology as a compressor is particularly preferred.
  • Refrigeration applications use. In the compression of gases, especially at higher pressure conditions is usually worked with a fluid-injected compression, in particular an oil-injected compression; but it is also possible to operate a screw machine on the principle of dry compression. In the low pressure range screw compressors are sometimes referred to as a screw blower. There have been considerable successes in recent decades in terms of manufacturability, reliability, smoothness and efficiency of
  • Incident cut of the secondary rotor find its equivalent in the frontal section of the main rotor.
  • the profile of the rotor is referred to in a plane perpendicular to the axis of the rotor.
  • different types of face cutting production such as rotor or rack-based face cutting production methods, are known from the prior art.
  • a first design frontal incision is created in a first step. This is conventionally further optimized in several subsequent (revision) steps according to various criteria.
  • the energy efficiency of compressor blocks can be advantageously influenced in a known manner by minimizing the internal leakage in the compressor block and in particular by reducing the gap between the main rotor and secondary rotor.
  • blow hole results from the Kopfud ndu ng the profiles, in particular the profile of the secondary rotor.
  • Pressure-side working chambers are connected to the respectively adjacent working chambers via pressure-side blades, suction-side
  • blow hole is to be understood in the following text as "pressure-side blowing hole”.
  • a short profile gap length should be combined with a small (pressure side) blow hole to minimize internal leakage.
  • the two sizes behave in opposite directions. Ie. the smaller the blow hole is modeled, the larger the profile gap length inevitably becomes. Conversely, the shorter the profile gap length, the larger the blow hole becomes. This is illustrated, for example, by Helpertz in his thesis “Method for stochastic optimization of screw rotor profiles", Dortmund, 2003 on page 162.
  • Pressure-side blowholes must not be made too large, as described above, in order to prevent the backflow of already compressed medium
  • blowing hole area can be kept small by making the head roundings of the profiles small in the face cut. Specifically, this can be due to a strong curvature in the
  • Head region of the leading tooth flank of the secondary rotor and in the head region of the trailing tooth flank of the main rotor can be effected.
  • the stronger this curvature is, however, the sooner one gets into production technology
  • Boundary areas as this leads, for example, to high wear on profile cutters and profile grinding wheels in the production of main rotor and secondary rotor.
  • Chamber gusset volume between the two rotors and the pressure-side housing end wall is a first chamber gusset volume between the two rotors and the pressure-side housing end wall.
  • incompressible oil is additionally present in the chamber gusset and is squeezed.
  • the object of the present invention is to provide a pair of rotors for a compressor block of a screw machine, which is characterized by high operational reliability and reasonable manufacturing costs by high smoothness and a special energy efficiency.
  • the rotor geometry is essentially characterized by the shape of the front section and by the rotor length and the wrap angle,
  • secondary rotor or main rotor have a predetermined, often different number per rotor of identically designed teeth.
  • the outermost circle drawn through the axis Cl or C2 via the vertices of the teeth is referred to as the tip circle.
  • a foot circle is defined in the end section.
  • the ribs are referred to as teeth of the rotor.
  • the grooves (or recesses) are referred to as tooth gaps.
  • the area of the tooth at and above the root defines the tooth profile.
  • the contour of the ribs defines the course of the tooth profile. For the tooth profile, foot points Fl and F2 and a vertex F5 are defined.
  • the vertex F5 or H5 is defined by the radially outermost point of the tooth profile. If the tooth profile has a plurality of points with the same maximum radial distance from the center defined by the axis C1 or C2, then the tooth profile at its radially outer end follows a circular arc on the top circle, then the vertex F5 lies exactly in the middle of this circular arc. Between two adjacent vertices F5, a tooth space is defined.
  • the points closest to the axis Cl or C2 between a considered and the adjacent tooth define foot points Fl and F2. Again, in the case that several points of the axis Cl or C2 come close, so that the tooth profile follows the root circle in sections at its lowest point, the corresponding foot point Fl or F2 then lies on half of this circular arc lying on the root circle ,
  • a pitch circle is defined by the meshing of the main rotor and the secondary rotor both for the secondary rotor and for the main rotor.
  • the pitch circle diameters of the main rotor and secondary rotor can be determined with the help of the center distance and the number of teeth ratios.
  • tooth space areas between the teeth and the respective top circle KK are defined, namely tooth space area A6 between the profile profile of the secondary rotor NR between two adjacent vertices F5 and the tip circle KKi or a surface A7 as the tooth gap area between the teeth
  • the tooth profile of the secondary rotor (but also of the main rotor) has a respective tooth flank leading in the direction of rotation and a tooth flank trailing in the direction of rotation.
  • the secondary rotor (NR) is the leading
  • the trailing tooth flank F N forms a point in its section between tip circle and root circle in which the curvature of the profile of the tooth profile changes. This point is referred to below as F8 and divides the trailing tooth flank F N into a convexly curved portion between F8 and the tip circle and a concavely curved portion between the root circle and F8. Small profile changes, such as by sealing strips or by other local profile transformations, are considered in the consideration of the above
  • a wrap angle ⁇ is defined. This wrap angle is the angle by which the end cut is twisted from the suction side to the pressure side rotor end face, cf. See also the detailed explanations in connection with FIG. 8.
  • the main rotor has a rotor length L HR , which is defined as the distance of a suction-side main rotor rotor end face to a pressure-side main rotor rotor face.
  • the distance of the mutually parallel first axis Cl of the secondary rotor to the second axis C2 of the main rotor is referred to below as the axial distance a.
  • the length of the main rotor L H R corresponds to the length of the secondary rotor L NR , whereby the length of the secondary rotor is also the distance of a suction side
  • Secondary rotor rotor face is understood to a pressure side secondary rotor rotor face.
  • a rotor length ratio L / a is defined, ie a ratio of the rotor length of the main rotor to the axial distance.
  • the ratio L / a is a measure of the axial dimensioning of the rotor profile.
  • the engagement line is as follows: The tooth flanks of the main rotor and secondary rotor touch each other with backlash-free teeth depending on the angular position of the rotors in certain points. These points are called engagement points.
  • the geometrical location of all engagement points is called the engagement line and can already be calculated in two-dimensional terms based on the end section of the rotors, cf. FIG.
  • the engagement line is divided into two sections in the front-sectional view through the connecting line between the two center points C1 and C2, into a (comparatively short) suction-side section and a (comparatively long) pressure-side section.
  • the engagement line can also be extended three-dimensionally and corresponds to the contact line of the main rotor and the secondary rotor.
  • the profile engagement gap is defined as follows: In the real compressor block of a screw machine clearance between the two rotors is present at installation axis distance of main rotor and side rotor.
  • the gap between the main rotor and the secondary rotor is referred to as the profile engaging gap and is the locus of any point where the two paired rotors are in contact with each other or the least spaced apart.
  • the profile engagement gap Through the profile engagement gap, the compressing and ejecting working chambers are connected to chambers which are still in contact with the suction side. At the profile ei ngriffsspalt thus the entire maximum pressure ratio. Due to the profile engagement gap, already compressed working fluid is transported back to the suction side, thus reducing the efficiency of compaction. Since it would act at the Profilein grip gap with backlash-free teeth around the engagement line, the profile engagement gap is also referred to as a "quasi-intervention line".
  • Blowholes between working chambers are created by head rounding of the teeth of the profile.
  • About blowholes are the working chambers with leading and connected subsequent working chambers, so that (in contrast to
  • Tooth pairings common, for example, a pair of rotors, in which the main rotor 3 and the side rotor 4 teeth or a rotor pairing, in which the main rotor 4 teeth and the secondary rotor 5 teeth or further a rotor pair geometry, in which the main rotor 5 teeth and the secondary rotor has 6 teeth.
  • a pair of rotors in which the main rotor 3 and the side rotor 4 teeth or a rotor pairing, in which the main rotor 4 teeth and the secondary rotor 5 teeth or further a rotor pair geometry, in which the main rotor 5 teeth and the secondary rotor has 6 teeth.
  • pair-of-rotor 4/5 (4-tooth main rotor, 5-tooth sub rotor) rotor pair assemblies are considered suitable mating for oil-injected compression applications in moderate pressure ranges.
  • the number of teeth or the number of teeth gives different types of rotor pairings and, as a result, also different types of screw machines, in particular screw compressors.
  • PTrel - where PT r ei is at least 0.5, preferably at least 0.515, and at most 0.65, preferably at most 0.595, where PT re i to the relative tread depth, at rk ! is a tip circle radius drawn around the outer circumference of the secondary rotor and, at rfi, it is a root circle radius which adjoins the base of the profile.
  • the ratio of the axial distance ⁇ of the first axis Cl to the second axis C2 and the tip circle radius rki set so that- at least 1.636 and at most 1.8, preferably at most 1,733, weight, wherein the main rotor preferably with a looping angle 0 H R is formed, for which applies 240 ° ⁇ 0 R H 360 °, and wherein preferably a rotor length ratio L H R / a applies:
  • PT r ei is at least 0.5, preferably at least 0.515 and at most 0.58, wherein PT re i is the relative tread depth, rki is a tip radius drawn around the outer circumference of the sub rotor, and rfi is a profile ground Root radius is.
  • the ratio of the axial distance a of the first axis Cl to the second axis C2 and the tip circle radius rk ! a is set so that - is at least 1.683 and at most 1.836, preferably at most 1.782, wherein preferably the main rotor with a
  • Wrapping angle 0 H R is formed, for which applies 240 ° ⁇ 0 H R 360 °, and wherein preferably for a rotor length ratio L H R / a applies:
  • PT r ei at least 0.44 and at most 0.495, preferably at most 0.48, which is accreting at PT rel the relative profile depth at rki to a drawn around the outer circumference of the secondary rotor tip circle radius and rfi one on the profile base Root radius is.
  • the ratio of the axial distance a of the first axis Cl to the second axis C2 and the tip circle radius rki a is set so that - is at least 1.74, preferably at least 1.75 and at most 1.8, preferably at most 1.79, wherein preferably the
  • Main rotor is formed with a wrap angle H R, for which applies 240 ° ⁇ 0 H R ⁇ 360 °, and wherein preferably for a rotor length ratio L H R / a applies:
  • the relative tread depth of the secondary rotor is a measure of how deep the profiles are cut. As the tread depth increases, for example, the
  • the values given for the rotor length ratio L H R / a and the wrap angle H R represent advantageous or expedient values for the respectively indicated tooth-number ratio in order to determine an advantageous rotor pairing in the axial dimension.
  • the goal is to combine a small blow hole with a short length of the profile engagement gap.
  • the two parameters behave in opposite directions, d. H. the smaller the blow hole is modeled, the greater the inevitable length of the profile engagement gap. Conversely, the shorter the length of the profile engagement gap, the larger the blow hole becomes.
  • a particularly favorable combination of the two parameters is achieved. At the same time a sufficiently high bending stiffness of the secondary rotor is ensured.
  • Cross-sectional view between the considered tooth of the sub rotor (NR) and the adjacent tooth of the sub rotor foot points Fl and F2 at the root circle and the radially outermost Pu nkt of the tooth a vertex F5 are defined, wherein by Fl, F2 and F5, a triangle D z is defined u nd wherein in a radially outer region of the tooth with its formed between F5 and F2 leading tooth flank F v with a surface AI and with its trailing formed between Fl and F5 tooth flank F N with a surface A2 on the triangle D z and 8 ⁇ A2 / A1 ⁇ 60 is maintained.
  • the tooth surface area AI on the leading tooth flank F v of the secondary rotor has a significant influence on the blow hole area.
  • the tooth part surface A2 on the trailing tooth flank F N of the secondary rotor has a significant influence on the length of the profile engagement gap, the Kammerausschu b and the
  • the pair of rotors has a secondary rotor, in which, in a cross-sectional view, between the considered tooth of the secondary rotor (NR) and the respective adjacent tooth of the Maurotorsdorfsetting Fl and F2 and at the radially outermost point of the tooth a vertex F5 are defined, wherein by Fl, F2 and F5, a triangle D z is defined and wherein the formed between F5 and F2 leading
  • Vertex are defined F5 being defined by Fl, F2 and F5, a triangle D z, and wherein said formed between F5 and F2 leading
  • FIGS. 7d and 7e With regard to the illustration of the parameters, reference is additionally made to FIGS. 7d and 7e.
  • the offset angle is always always positive, ie always the offset in the direction of the direction of rotation is given and not contrary.
  • the tooth of the secondary rotor is curved in this respect to the direction of rotation of the secondary rotor.
  • the offset should be in the range indicated to be advantageous to provide a favorable compromise between the blow hole area, the shape of the line of action, the length and shape of the profile engagement gap, the minor rotor torque, the
  • the trailing tooth flank F N of a tooth of the secondary rotor (NR) formed between Fl and F5 has a convex length portion of at least 45% to at most 95%.
  • Preferred dimensions of the secondary rotor is designed such that in one
  • trailing tooth flank F N associated area ratio is limited A4 then the one hand by the radial ray R and in sections, between the two points of intersection of the leading tooth flank F v with the radial R, on the other hand by the leading tooth flank F v.
  • volume ratio of the print window area can be made larger. In addition, this also shortens the axial extension of the sketchschiebenden
  • a rotor pair is provided, which is designed and cooperates with each other such that a blow hole factor ⁇ ⁇ ⁇ is at least 0.02% and at most 0.4%, preferably at most 0.25%,
  • Tooth gaps surfaces of the secondary rotor (NR) and the main rotor (HR) denote, wherein the area A6 in a cross-sectional view, the between the
  • Enclosed surface and the surface A7 in an end-sectional view denote between the profile profile of the main rotor (HR) points between two adjacent vertices H5 and the tip circle KK 2 enclosed area.
  • the pressure-side blow hole surface can thus be displayed independently of the size of the screw machine.
  • a rotor pair is designed and matched to each other such that for a blow hole / profile gap length factor ⁇ * ⁇ ⁇ ⁇
  • Tooth gaps surfaces of the secondary rotor (NR) and the main rotor (HR) denote, wherein the area A6 in a cross-sectional view, the between the
  • ⁇ denotes a profile gap length factor, wherein the length of the profile engagement gap of a tooth gap is set in relation to the profile depth PTi. This can be a measure of the length of the professional leingriffspalts set regardless of the size of the screw machine. The smaller the numerical value of the characteristic ⁇ is, the shorter is the profile gap of a tooth pitch and thus the lower the leakage volume flow back to the suction side at the same profile depth. From the factor ⁇ * ⁇ ⁇ ⁇ results in the goal to combine a small pressure-side blow hole with a cool profile gap. However, the two ratios behave, as already mentioned, but in opposite directions.
  • main rotor (HR) and secondary rotor (NR) are designed and matched to one another such that a dry compression with a pressure ratio ⁇ of up to 3, in particular with a pressure ratio ⁇ of greater than 1 and up to 3 , is obtainable, wherein the pressure ratio refers to the ratio of compression end pressure to suction pressure.
  • a further preferred embodiment provides a rotor pair, such that the main rotor (HR) with respect to a tip circle KK 2 with a
  • Circumferential speed is operable in a range of 20 to 100 m / s.
  • a diameter ratio defined by the ratio of the head circle radii of the main rotor (HR) and the secondary rotor (NR)
  • Dki is the diameter of the tip circle KKi of the minor rotor (NR) and Dk 2 is the diameter of the tip circle KK 2 of the main rotor (HR).
  • the goal is to combine a small blow hole with a short length of the profile engagement gap.
  • the two parameters behave in opposite directions, d. H. the smaller the blow hole is modeled, the greater the inevitable length of the profile engagement gap. Conversely, the shorter the length of the profile engagement gap, the larger the blow hole becomes.
  • a particularly favorable combination of the two parameters is achieved. At the same time a sufficiently high bending stiffness of the secondary rotor is ensured.
  • the tooth surface area AI on the leading tooth flank F v of the secondary rotor has a significant influence on the blow hole area.
  • the tooth part surface A2 on the trailing tooth flank F N of the secondary rotor has a significant influence on the length of the profile engagement gap, the Kammerausschu b and the
  • the pair of rotors has a secondary rotor, in which, in an end-sectional view, between the considered tooth of the secondary rotor (NR) and the adjacent tooth of the secondary rotor (NR), points F1 and F2 are defined and at the radially outermost point of the tooth a vertex F5 are, where by Fl, F2 and F5, a triangle D z is defined and wherein formed between F5 and F2 vorlufende tooth flank F v in a radially outer region of the tooth with an area AI over the triangle D z and in a radially inner Area with respect to the triangle D z recedes with an area A3 and where 9.0 ⁇ A3 / A1 ⁇ 18 is maintained.
  • Vertex F5 are defined, wherein by Fl, F2 and F5, a triangle D z is defined and wherein the trained between F5 and F2 leading
  • FIGS. 7d and 7e With regard to the definition of the parameters, reference is made to FIGS. 7d and 7e.
  • a vertex F5 are defined, wherein the running between Fl and F2 circular arc B to the du rch the axis Cl defined center defined a tooth pitch angle ⁇ corresponding to 360 ° / number of teeth of the minor rotor NR, wherein on the half circular arc B A point F1 is defined between F1 and F2, wherein a radial ray R drawn from the center point of the secondary rotor (NR) defined by the axis C1 intersects the circular arc B at a point F12, wherein an offset angle ⁇ is determined by the direction of rotation Secondary rotor (NR) considered offset from F1 to F12 is defined and wherein
  • the offset angle is always always positive, that is to say always the offset in the direction of the direction of rotation is given and not contrary.
  • the tooth of the secondary rotor is curved in this respect to the direction of rotation of the secondary rotor.
  • the offset should be in the range indicated to be favorable to provide a favorable compromise between the blow hole area, the shape of the line of action, the length and shape of the profile engagement gap, the minor rotor torque, the
  • the trailing tooth flank F N of a tooth of the secondary rotor (NR) formed between Fl and F5 has a convex length portion of at least 55% to at most 95%.
  • Preferred dimensions of the secondary rotor is designed so that in a
  • Cross-sectional view of the drawn from the axis Cl of the secondary rotor (NR) by F5 radial beam R divides the tooth profile in one of the leading tooth flank F v associated surface portion A5 and the trailing tooth flank F N associated surface portion A4 and
  • A4 is of the trailing tooth flank F N associated area rate then the one hand by the radial ray R in sections, namely, confined between the two points of intersection of the leading tooth flank F v with the radial R, on the other hand by the leading tooth flank F v.
  • a further preferred embodiment has a rotor pair, which is characterized in that the main rotor HR is formed with a wrap angle 0 H R, for which applies: 320 ° ⁇ 0 H R 360 °, preferably 330 ° ⁇ 0 H R
  • volume ratio of the print window area can be made larger. In addition, this also shortens the axial extension of the sketchschiebenden
  • Tooth gaps surfaces of the secondary rotor NR and the main rotor (HR) denote, wherein the area A6 in an end-sectional view, the between the Profile profile of the secondary rotor (NR) between two adjacent vertices F5 and the tip circle KKi enclosed area and the surface A7 in a cross-sectional view the points between the profile of the main rotor (HR) between two adjacent vertices points H5 and the tip circle KK 2 enclosed area.
  • a rotor pair is designed and matched to one another such that for a blow hole / profile gap length factor ⁇ * ⁇ ⁇ ⁇
  • Tooth gaps surfaces of the secondary rotor (NR) and the main rotor (HR) denote, wherein the area A6 in a cross-sectional view, the between the
  • ⁇ denotes a profile gap length factor, wherein the length of the profile engagement gap of a tooth gap is set in relation to the profile depth PTi. This can be a measure of the length of the professional leingriffspalts set regardless of the size of the screw machine.
  • main rotor (HR) and secondary rotor (NR) are designed and matched to one another such that a dry compression with a pressure ratio of up to 5, in particular with a pressure ratio ⁇ of greater than 1 and up to 5 , or alternatively, a fluid-injected compression with a pressure ratio of up to 16, in particular with a pressure ratio greater than 1 and up to 16, can be achieved, wherein the pressure ratio, the ratio of compression end pressure to
  • a further preferred embodiment provides a pair of rotors, such that in the case of a dry Verdichtu ng the main rotor with respect to a tip circle KK 2 with a peripheral speed in a range of 20 to 100 m / s and in the case of a fluid-injected compression of the main rotor with a peripheral speed is designed to be operable in a range of 5 to 50 m / s.
  • a diameter ratio defined by the ratio of the head circle radii of the main rotor (HR) and the secondary rotor (NR)
  • the goal is to combine a small blow hole with a short length of the profile engagement gap.
  • the two parameters behave in opposite directions, i. the smaller the blow hole is modeled, the greater the inevitable length of the profile engagement gap. Conversely, the shorter the length of the profile engagement gap, the larger the blow hole becomes.
  • a particularly favorable combination of the two parameters is achieved. At the same time a sufficiently high bending stiffness of the secondary rotor is ensured.
  • the tooth surface area AI on the leading tooth flank F v of the secondary rotor has a significant influence on the blow hole area.
  • the tooth part surface A2 on the trailing tooth flank F N of the secondary rotor has a significant influence on the length of the profile engagement gap, the Kammerausschu b and the
  • the rotor pair has a secondary rotor, in which, in a front-sectional view, between the
  • FIG. 7d With regard to the illustration of the parameters, reference is additionally made to FIG. 7d.
  • Vertex F5 are defined, wherein by Fl, F2 and F5, a triangle D z is defined and wherein the trained between F5 and F2 leading
  • FIGS. 7d and 7e With regard to the illustration of the parameters, reference is additionally made to FIGS. 7d and 7e.
  • a vertex F5 are defined, wherein the running between Fl and F2 circular arc B to the by Axis Cl defined center defined a tooth pitch angle ⁇ corresponding to 360 ° / number of teeth of the secondary rotor NR, wherein on the half circular arc B between Fl and F2 a point Fl l is defined, wherein a defined by the axis Cl center of the secondary rotor (NR) Radial beam R drawn through the vertex F5 intersects the arc B at a point F12, an offset angle ⁇ being defined by the offset of F1 to F12 considered in the direction of rotation of the minor rotor (NR), and
  • the offset angle is always always positive, that is to say always the offset in the direction of the direction of rotation is given and not contrary.
  • the tooth of the secondary rotor is curved in this respect to the direction of rotation of the secondary rotor.
  • the offset should be in the range indicated to be favorable to provide a favorable compromise between the blow hole area, the shape of the line of action, the
  • a further preferred embodiment has a rotor pair, which is characterized in that the main rotor HR is formed with a wrap angle 0 H R, for which applies: 320 ° ⁇ 0 H R 360 °, preferably 330 ° ⁇ 0 H R
  • Tooth gaps surfaces of the secondary rotor NR and the main rotor (HR) denote, wherein the area A6 in an end-sectional view, the between the
  • the pressure-side blow hole surface can thus be independent of the size of the screw compressor.
  • a rotor pair is designed and matched to one another such that for a blow hole / profile gap length factor ⁇ * ⁇ ⁇ ⁇
  • Tooth gaps surfaces of the secondary rotor (NR) and the main rotor (HR) denote, wherein the area A6 in a cross-sectional view, the between the
  • ⁇ denotes a profile gap length factor, wherein the length of the profile engagement gap of a tooth gap is set in relation to the profile depth PTi. This can be a measure of the length of the professional leingriffspalts set regardless of the size of the screw machine. The smaller the numerical value of the characteristic ⁇ is, the shorter is the profile gap at the same profile depth and thus the lower the leakage volume flow back to the suction side. From the factor ⁇ * ⁇ ⁇ ⁇ results in the goal to combine a small pressure-side blow hole with a cool profile gap. However, the two ratios behave, as already mentioned, but in opposite directions.
  • main rotor (HR) and secondary rotor (NR) are designed and matched to one another such that a dry compression with a pressure ratio of up to 5, in particular with a pressure ratio ⁇ of greater than 1 and up to 5 , or alternatively, a fluid-injected compression with a pressure ratio of up to 20, in particular with a pressure ratio ⁇ of greater than 1 and up to 20, achievable where the pressure ratio is the ratio of the discharge pressure to the suction pressure.
  • a further preferred embodiment provides a rotor pair, such that the main rotor (HR) with respect to a tip circle KK 2 in the case of a dry compression at a peripheral speed in a range of 20 to 100 m / s and in the case of a fluid-injected compression with a
  • a diameter ratio defined by the ratio of the helix radii of the main rotor (HR) and the secondary rotor (NR)
  • the teeth of the sub rotor taper outwardly, i.e., outwardly. all arcs of a circle extending perpendicularly from the center point defined by the axis Cl and passing through the point F5
  • trailing tooth flank F N to the leading tooth flank F v from Fl to F2 decrease in the sequence radially outwards (or at least remain the same in sections).
  • each by the leading tooth flank F v and the trailing tooth flank F N are limited so that the arc lengths b (r) monotonously decrease with increasing radius r.
  • the teeth of the secondary rotor are thus formed in this preferred embodiment so that no constrictions arise, so the width of a tooth of the secondary rotor increases at any point, but decreases radially outward or remains the same maximum. This is considered useful in order to achieve on the one hand a small pressure-side blowing hole with a short profile engagement gap length.
  • the front section design of the secondary rotor (NR) is made such that the effective direction of the torque, which consists of a
  • Reference pressure on the working chamber limiting partial surface of the secondary rotor results, is directed against the direction of rotation of the secondary rotor.
  • Rotorklappern is understood to mean a uniform rotational movement superimposed advancing and lagging of the secondary rotor about its axis of rotation, which with a rapidly changing impact of the trailing secondary rotor edges on the leading main rotor edges and then the leading
  • Gas forces along with other moments (e.g., from bearing friction) on the sub rotor are undefined (e.g., near zero), which is advantageous
  • main rotor (HR) and secondary rotor (NR) for conveying air or inert gases, such as helium or nitrogen, are designed and matched to one another.
  • the profile of a tooth of the sub-rotor is asymmetrical with respect to the radial ray R drawn from the center defined by the axis Cl through the vertex F5.
  • the secondary rotor are thus leading tooth flank and
  • Trailing tooth flank of each tooth formed asymmetrically to each other. This asymmetrical design is already known per se for screw compressors. But it contributes significantly to an efficient compaction.
  • Rolling circles WKi of the secondary rotor (NR) and WK 2 of the main rotor (HR) touch that K5 intersects the root circle FK ! of the minor rotor (NR) is defined with the link C1C2, where ri measures the distance between K5 and C, and that K4 denotes the point of the suction side of the engagement line furthest from the link C1C2 between C1 and C2, where r 2 measures the distance between K4 and C and where:
  • Line of action can be based on the radii ratio ri / r 2 of two
  • the rotor pair is designed and configured such that the following applies for a rotor length ratio L HR / a:
  • the flexural rigidity of the rotors is sufficiently high that the rotors do not appreciably deflect during operation and therefore the gaps (between the rotors or between the rotors and the compressor housing) can be made relatively narrow without risking that the rotors start under unfavorable operating conditions (high temperatures and / or high pressures) together or start in the compressor housing.
  • Narrow gaps offer the advantage of low backflow and thus contribute to energy efficiency. At the same time, the operational reliability is guaranteed despite small gaps. Also in the rotor manufacturing a high bending stiffness of the rotors to comply with the high demands on the shape tolerances is advantageous.
  • Tooth flank F N on the circular arc with radius rki are about the center defined by the axis Cl, wherein preferably the circular arc ARCi an angle with respect to the axis Cl between 0.5 ° and 5 °, further
  • the above-described embodiment of the tooth profile of the secondary rotor is relevant above all for a tooth-number ratio of 3/4 or 4/5. With such a teeth number ratio, by keeping to the above-mentioned condition, the blow hole area can be reduced. When teeth number ratio 5/6 an aforementioned point of contact or aforementioned intersections with the leading tooth flank F v, however, not desirable, since the teeth of the secondary rotor may then be too thin and consequently too flexible.
  • a compressor block comprising a compressor housing and a pair of rotors as described above as claimed invention, wherein the rotor pair comprises a main rotor HR and a secondary rotor NR, which are each rotatably mounted in the compressor housing.
  • the compressor block is designed such that the endcut design is made such that the working chamber formed between the tooth profiles of main rotor (HR) and secondary rotor (NR) can be pushed out substantially completely into the pressure window.
  • Chamber gape volume between the two rotors forms.
  • the compression can be done very efficiently, since there is no backflow from already
  • Oil-injected compressors prevent squeezing of the oil, thus improving the smoothness of the compressor, reducing the load on the rotor bearings and reducing the stress on the oil.
  • a shaft end of the main rotor is led out of the compressor housing and formed for connection to a drive, wherein preferably both shaft ends of the secondary rotor are completely accommodated within the compressor housing.
  • FIG. 1 shows an end section of a first embodiment with a tooth
  • Figure 2 is a front section of a second embodiment with a
  • FIG. 3 shows an end section of a third embodiment with a
  • FIG. 4 shows a fourth exemplary embodiment in a cross-sectional view with a teeth number ratio 5/6.
  • Figure 5 is an illustration of the isentropic block efficiency for the second embodiment for the 3/4 teeth number ratio compared to the prior art.
  • FIGS. 7a-7k show diagrams illustrating the different parameters of the geometry of the secondary rotor or of the rotor pair, comprising a main rotor and secondary rotor.
  • FIG. 8 shows an illustration of the wrap angle in FIG.
  • Figure 9 is a schematic sectional view of an embodiment of a
  • Figure 10 shows an embodiment of an intermeshed rotor pair consisting of a main rotor and a side rotor in three-dimensional representation.
  • Figure 11 is a perspective view of an embodiment of a
  • Figures 12a, 12b is an illustration of the relevant for the torque effects surfaces or partial surfaces of a working chamber of an embodiment of the secondary rotor.
  • Figure 13 shows the end section of the embodiment of Figure 1 for
  • Figure 14 shows the end section of the embodiment of Figure 2 for
  • Figure 15 shows the end section of the embodiment of Figure 3 for
  • FIG. 16 shows the end section of the embodiment according to FIG.
  • the isentropic block efficiency compared to the prior art is illustrated for the second embodiment for the 3/4 teeth number ratio in FIG. There are two curves with the same pressure ratio.
  • the concrete reproduced pressure ratio is 2.0 (ratio
  • FIG. 6 shows the isentropic block efficiency in comparison with the prior art in the fourth exemplary embodiment (5/6 teeth number ratio).
  • the delivery quantity indicated in each case in FIGS. 5 and 6 corresponds to the delivery volume flow of the compressor block relative to the intake state.
  • FIG. 7 a shows a front view of an embodiment of FIG.
  • the direction of rotation 24 of the secondary rotor and the inevitably resulting direction of rotation of the main rotor when operating as a compressor.
  • the leading tooth flank F v and the trailing tooth flank F N are marked on a secondary rotor tooth.
  • a tooth gap 23 is marked.
  • the profile profile of the leading tooth flank F v and the trailing tooth flank F N illustrated with reference to FIG. 7 a corresponds to that explained with reference to FIG. 4 for a tooth ratio of 5/6
  • FIG. 7b shows in an end view the tooth gap surfaces A6 and A7 as well as a side view of a blow hole.
  • the profile profiles shown in FIG. 7b for explaining the tooth gap surfaces A6 and A7 correspond to those illustrated for a tooth ratio of 3/4 on the basis of FIG.
  • FIG. 7b shows the position of the coordinate system of the blow hole area A B i shown in FIG. 7 k in relation to the rotor pair.
  • the coordinate system is spanned by the u-axis parallel to the rotor end faces along the pressure-side intersection edge 11.
  • the pressure-side blowing hole lies in the described coordinate system and quite concretely in a plane perpendicular to the rotor end faces between the pressure-side intersection edge 11 and an engagement line point K2 of the pressure-side part of the engagement line.
  • K2 denotes the point of the pressure-side part of the engagement line 10 which is furthest from the straight line through Cl and C2.
  • the u-axis is a parallel to the rotor end faces and corresponds in an end-sectional view to the vector from the engagement line point K2 to the pressure-side intersection edge 11.
  • FIG. 7k Further details on the pressure-side blow hole area A B i are shown in FIG. 7k.
  • FIG. 7c shows, in an end-sectional view, a tooth of the secondary rotor with the concentric arcs B 25 , B 50 , B 75 running around the rotor tooth around the center Cl with the associated radii r 2 5, r 50 , r 75 and the associated arc lengths b 2 5 , b 5 o, b 75 .
  • the circular arcs B 2 5, B 50 , B 75 are each bounded by the leading tooth flank F v and the trailing tooth flank F N.
  • the profile profile of the leading tooth flank F v and the trailing tooth flank F N shown on the basis of FIG. 7 c corresponds to the exemplary embodiment explained with reference to FIG. 4 for a tooth number ratio of 5/6.
  • FIG. 7 d shows, in an end-sectional view, between the viewed tooth of the secondary rotor and the respectively adjacent tooth of the secondary rotor, base points F 1 and F 2 at the root circle and at the radially outermost point of the tooth
  • Vertex F5 Furthermore, the triangle D z defined by the points Fl, F2 and F5 is shown.
  • FIG. 7d shows the following (tooth part) surfaces:
  • Part tooth surface AI corresponds to the surface with which the tooth under consideration with its leading tooth flank F v formed between F5 and F 2 projects beyond the triangle D z in a radially outer region.
  • Part tooth surface A2 corresponds to the surface with which the tooth under consideration with its trailing tooth flank F N formed between F5 and Fl projects beyond the triangle D z in a radially outer region.
  • Area A3 corresponds to the area at which the tooth in question recedes with respect to the triangle D z with its leading tooth flank formed between F5 and F2.
  • tooth pitch angle ⁇ corresponding to 360 ° / number of teeth of the sub rotor.
  • the profile profile of the leading tooth flank F v and the trailing tooth flank F N shown on the basis of FIG. 7 d corresponds to that explained with reference to FIG. 4 for a tooth number ratio of 5/6
  • FIG. 7e shows, in an end-sectional view, the cross-sectional area AO of a tooth of the secondary rotor, which extends through the one between Fl and F2
  • Arc B is bounded by the center point Cl.
  • the profile profile of the leading tooth flank F v and the trailing tooth flank F N shown on the basis of FIG. 7e corresponds to the exemplary embodiment explained with reference to FIG. 4 for a tooth number ratio of 5/6.
  • FIG. 7f shows the offset angle ⁇ in a cross-sectional view. This is defined by the offset from point F1 to point F12 considered in the direction of rotation of the secondary rotor.
  • Fl l is a point on the half circular arc B between Fl and F2 around the center point Cl and accordingly corresponds to the intersection of the bisector of the tooth pitch angle ⁇ with the
  • Circular arc B Circular arc B.
  • FIG. 7g shows, in an end-sectional view, the point of inflection F8 on the trailing tooth flank F N of the secondary rotor, in which the curvature of the profile of the tooth profile between head and root circle changes.
  • the trailing tooth flank F N of the secondary rotor is formed by the point F8 in a substantially convexly curved portion between F8 and
  • FIG. 7h shows in a cross-sectional view two points of intersection of FIG
  • FIG. 7i shows, in an end-sectional view, the tooth profile divided by the radial jet R drawn from C1 to F5.
  • the tooth profile is divided into a surface portion A4 associated with the trailing tooth flank F N and an area portion A 5 assigned to the leading tooth flank F v .
  • the profile profiles of the leading tooth flank F v and the trailing tooth flank F N explained with reference to FIG. 7i correspond to the exemplary embodiment according to FIG. 4 described for a tooth number ratio of 5/6.
  • FIG. 7j shows, in an end-sectional view, the engagement line 10 between the main rotor and the secondary rotor and the two concentric circles about the point C with the radii ri and r 2 for describing the characteristic features of the profile of the suction-side part of the engagement line.
  • the engagement line 10 is divided into two sections by the connection path between the first axis Cl and the second axis C2.
  • the suction-side part of the engagement line is shown below, the pressure-side part above the connection path C1C2.
  • Point C is the point of contact of the pitch circle WK ! of the secondary rotor with the pitch circle WK 2 of the main rotor.
  • K4 denotes the point of the suction-side part of the engagement line, which is furthest from the connection path between C1 and C2.
  • Radius ⁇ " ! Is the distance between K5 and C, radius r 2 denotes the distance between K4 and C.
  • FIG. 7k is a diagrammatic representation of FIG. 7k.
  • FIG. 7k shows a pressure-side blow hole area A B i of a working chamber, specifically in a sectional view perpendicular to the rotor end faces.
  • the limitation of the blow hole area A B i arises from the section line 27 of the above-described imaginary flat surface with the leading secondary rotor edge F v , the section line 26 of the plane with the trailing HR edge and a
  • the coordinate system of the pressure-side blow hole is in the in Fig. 7b described flat surface and is spanned by
  • the already repeatedly addressed wrap angle ⁇ is illustrated again pictorially. Specifically, it is the angle ⁇ , around which the endcut is twisted from the suction side to the pressure side rotor end face. This is illustrated by the rotation of the profile between a pressure-side end face 13 and a suction-side end face 14 by the angle OHR in the main rotor HR.
  • Figure 9 shows a schematic sectional view of a compressor block 19 comprising a housing 15 and stored therein two mutually paired rotors, namely a main rotor HR and a secondary rotor NR.
  • Main rotor HR and secondary rotor NR are each rotatably supported in the housing 15 via suitable bearings 16.
  • a drive power can be applied to a shaft 17 of the main rotor HR, for example with a motor (not shown) via a coupling 18.
  • the compressor block shown is an oil-injected screw compressor in which the torque transmission between the main rotor HR and the secondary rotor NR takes place directly over the rotor flanks. In contrast to can be avoided in a dry screw compressor touching the rotor edges by means of a synchronization gear (not shown).
  • Secondary rotor NR shown in a perspective view.
  • FIG. 11 shows the spatial engagement line 10 exactly one tooth gap 23.
  • the profile gap length l sp is the length of the spatial engagement line exactly one
  • Gap gap 23 This therefore corresponds to the profile gap length of exactly one tooth pitch.
  • Partial surfaces of the secondary rotor In Fig. 12a, such, a working chamber limiting partial surface (22) of the secondary rotor is shown by hatching example.
  • FIG. 12b shows the division of the partial surface (22) delimiting a working chamber shown in FIG. 12a into a dotted area (28) and a cross-hatched area (29). Only the cross hatch rt
  • the sub-surface (22) results from the actual Stirnroughmony and the slope of the secondary rotor.
  • the slope of the secondary rotor refers to the pitch of the helical toothing of the secondary rotor.
  • Fig. 12a the partial surface limiting three-dimensional
  • Engagement line (10) is also determined by the front section design of the secondary rotor and the slope.
  • Partial surface (22) is also limited by section line (27). Details of section line (27) have already been shown and described in the context of FIGS. 7b and 7k. The same applies to the engagement point K2. The dependent on the angular position of the secondary rotor to the main rotor concrete length of a working chamber in the direction of the rotor axis between the
  • the three-dimensional line of action (10) and cutting line (27) on the other hand does not play a significant role because - as described in the relevant literature - the gas pressures on areas of the rotor surface, in a sectional plane perpendicular to the axis of the rotor complete tooth gaps
  • profile profiles can also be generated by means of publicly available computer programs, as is well known to the person skilled in the art.
  • SV_Win a project of the Vienna University of Technology
  • An alternative, publicly accessible computer program also includes the DISCO software and, in particular, the SCORPATH module of the City University of London (Center for Positive Displacement Compressor Technology).
  • DISCO software and, in particular, the SCORPATH module of the City University of London (Center for Positive Displacement Compressor Technology).
  • ScrewView Another alternative software is the software ScrewView, which is also mentioned in the thesis “Directed Evolutionary Algorithms” by Stefan Berlik, Dortmund 2006 (pp. 173 f.) On the website http: //pi.informatik / Screwdriver / projects / will use the ScrewView software in the
  • a tooth with trailing rotor flank F N and leading rotor flank F v is generated concretely as follows:
  • the section S1 to S2 results from a circular arc on the secondary rotor NR about the center point C1 generated by the circular arc section T1 to T2 around the center C2 on the main rotor HR.
  • the section S2 to S3 results from a Hüllku rve to a trochoid generated by arc section T2 to T3 about the center M4 on the main rotor HR.
  • the section S3 to S4 is surrounded by a circular arc defines the center M l.
  • the section S4 to S5 is given by a circular arc around the center M2.
  • the section S5 to S6 is defined by a circular arc around the center point Cl.
  • the subsequent section S6 to S7 is replaced by a
  • section S7 to Sl is characterized by an envelope to a trochoids, generated by the
  • the profile profile of the teeth of the main rotor HR is also briefly explained below for the exemplary embodiment according to FIGS. 1 to 4 with reference to FIGS. 13 to 16.
  • the section T1-T2 results from a circular arc on the main rotor HR about the center C2 on the main rotor HR.
  • the section T2 - T3 is defined by the circular arc on the main rotor HR around the center M4.
  • the section T3-T4 results from an envelope to a trochoid generated by the section S3-S4 on the sub rotor NR.
  • the section T4-T5 is given by an envelope to a trochoid generated by the section S4-S5 on the sub rotor.
  • the section T5-T6 is defined by a circular arc around the center C2 generated by the circular arc section S5-S6 around the center point Cl on the sub rotor NR.
  • the section T6-T7 results from an envelope to a trochoid generated from the section S6-S7 on the sub rotor NR.
  • section T7-T1 is surrounded by a circular arc
  • Main rotor HR are of course matched and thus the envelopes correspond to a trochoid each circular arc sections on the counter rotor.
  • a tangential transition from one section to the next is ensured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une paire de rotors destinée à un bloc de compresseur d'une visseuse. Selon l'invention, la paire de rotors est constituée d'un rotor secondaire (NR) tournant sur un premier axe (C1) et d'un rotor principal (RS) tournant sur un second axe (C2), le nombre de dents (Z2) du rotor principal (RS) étant de 3 et le nombre de dents (Z1) du rotor secondaire (NR) étant de 4, le profil de profondeur relative du rotor secondaire (formule (I)) étant de 0,5 minimum, de préférence de 0,515 minimum, et de 0,65 maximum, de préférence de 0,595 minimum, rk1 étant le rayon du cercle de tête tracé sur la périphérie extérieure du rotor secondaire (NR) et rf1 étant le rayon du cercle de pied rapporté à la base du profil du rotor secondaire, le rapport entre l'écartement des axes (a), entre le premier axe (C1) et le second axe (C2), et le rayon du cercle de tête rk1 (formule (II)) étant de 1,636 minimum et de 1,8 maximum, de préférence de 1,733 maximum.
EP15736405.0A 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse Active EP3134649B2 (fr)

Priority Applications (3)

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EP19190907.6A EP3597920B1 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP18163593.9A EP3358189B9 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP23198449.3A EP4273403A3 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014105882.8A DE102014105882A1 (de) 2014-04-25 2014-04-25 Rotorpaar für einen Verdichterblock einer Schraubenmaschine
PCT/EP2015/059070 WO2015162296A2 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse

Related Child Applications (5)

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EP19190907.6A Division EP3597920B1 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP19190907.6A Division-Into EP3597920B1 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP18163593.9A Division-Into EP3358189B9 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP18163593.9A Division EP3358189B9 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP23198449.3A Division EP4273403A3 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse

Publications (4)

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EP3134649A2 true EP3134649A2 (fr) 2017-03-01
EP3134649B1 EP3134649B1 (fr) 2018-04-04
EP3134649B9 EP3134649B9 (fr) 2019-02-27
EP3134649B2 EP3134649B2 (fr) 2022-12-14

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EP18163593.9A Active EP3358189B9 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP19190907.6A Active EP3597920B1 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP15736405.0A Active EP3134649B2 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP23198449.3A Pending EP4273403A3 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse

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EP18163593.9A Active EP3358189B9 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse
EP19190907.6A Active EP3597920B1 (fr) 2014-04-25 2015-04-27 Paire de rotors pour bloc de compresseur d'une visseuse

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US (4) US10400769B2 (fr)
EP (4) EP3358189B9 (fr)
JP (1) JP6545787B2 (fr)
CN (1) CN106536933B (fr)
DE (2) DE102014105882A1 (fr)
ES (3) ES2668317T5 (fr)
WO (1) WO2015162296A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3358189A1 (fr) 2014-04-25 2018-08-08 Kaeser Kompressoren SE Paire de rotors pour bloc de compresseur d'une visseuse
WO2019044390A1 (fr) 2017-09-04 2019-03-07 株式会社日立産機システム Compresseur à vis

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016011436A1 (de) 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Anordnung von Schrauben für einen Schraubenkompressor für ein Nutzfahrzeug
CA3060013A1 (fr) * 2017-04-20 2018-10-25 Cogenergy Suisse Sa Reducteur de pression pour moteur a combustion interne rotatif
DE102020103384A1 (de) 2020-02-11 2021-08-12 Gardner Denver Deutschland Gmbh Schraubenverdichter mit einseitig gelagerten Rotoren

Family Cites Families (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR953057A (fr) 1946-07-18 1949-11-30 Ljungstroms Angturbin Ab Perfectionnements aux compresseurs et aux moteurs à roue hélicoïdale
GB627162A (en) 1946-07-18 1949-07-29 Ljungstroms Angturbin Ab Improvements in rotary devices of the helical screw wheel type
IT454201A (fr) * 1947-07-16
US3138110A (en) 1962-06-05 1964-06-23 Joseph E Whitfield Helically threaded intermeshing rotors
US3282495A (en) 1964-04-29 1966-11-01 Dresser Ind Sealing arrangement for screw-type compressors and similar devices
DE1428265A1 (de) * 1964-05-22 1969-01-16 Svenska Rotor Maskiner Ab Schraubenrotormaschine
US3275226A (en) 1965-02-23 1966-09-27 Joseph E Whitfield Thrust balancing and entrapment control means for screw type compressors and similardevices
US3437263A (en) * 1966-06-22 1969-04-08 Atlas Copco Ab Screw rotor machines
DE2911415C2 (de) 1979-03-23 1982-04-15 Karl Prof.Dr.-Ing. 3000 Hannover Bammert Parallel- und außenachsige Rotationskolbenmaschine mit Kämmeingriff
US4412796A (en) 1981-08-25 1983-11-01 Ingersoll-Rand Company Helical screw rotor profiles
SE429783B (sv) * 1981-12-22 1983-09-26 Sullair Tech Ab Rotorer for en skruvrotormaskin
US4583927A (en) * 1983-03-16 1986-04-22 Kabushiki Kaisha Kobe Seiko Sho Screw rotor mechanism
JPH079239B2 (ja) * 1984-04-11 1995-02-01 株式会社日立製作所 スクリュー真空ポンプ
US4527967A (en) * 1984-08-31 1985-07-09 Dunham-Bush, Inc. Screw rotor machine with specific tooth profile
US4643654A (en) * 1985-09-12 1987-02-17 American Standard Inc. Screw rotor profile and method for generating
US5018953A (en) * 1989-05-18 1991-05-28 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Rotor with eccentrically positioned retainer pin
US5624250A (en) * 1995-09-20 1997-04-29 Kumwon Co., Ltd. Tooth profile for compressor screw rotors
AU720108B2 (en) * 1995-12-11 2000-05-25 Ateliers Busch S.A. Twin feed screw
KR100313638B1 (ko) 1998-05-06 2001-12-12 최성규 자동차용스크류형수퍼차져로타의치형
KR100425414B1 (ko) * 2002-01-25 2004-04-08 이 재 영 스크류 압축기용 로우터의 치형
US7163387B2 (en) * 2002-12-16 2007-01-16 Carrier Corporation Meshing helical rotors
JP2007146659A (ja) * 2005-11-24 2007-06-14 Hitachi Industrial Equipment Systems Co Ltd 油冷式圧縮機
JP4951571B2 (ja) * 2008-03-31 2012-06-13 株式会社日立産機システム スクリュー圧縮機
IT1394590B1 (it) * 2009-05-21 2012-07-05 Robuschi S P A Compressore a vite
CN102052322B (zh) 2010-12-23 2012-10-31 上海耐浦流体机械科技有限公司 一种双螺杆压缩机转子型线
CN102352840B (zh) 2011-09-29 2013-08-28 陕西丰赜机电科技有限公司 螺杆转子端面廓形副及其构造方法
GB2501302B (en) * 2012-04-19 2016-08-31 The City Univ Reduced noise screw machines
CN103195716B (zh) 2013-05-07 2015-09-02 巫修海 一种新型齿形螺杆型线
DE102014105882A1 (de) 2014-04-25 2015-11-12 Kaeser Kompressoren Se Rotorpaar für einen Verdichterblock einer Schraubenmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3358189A1 (fr) 2014-04-25 2018-08-08 Kaeser Kompressoren SE Paire de rotors pour bloc de compresseur d'une visseuse
WO2019044390A1 (fr) 2017-09-04 2019-03-07 株式会社日立産機システム Compresseur à vis

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CN106536933A (zh) 2017-03-22
EP3134649B9 (fr) 2019-02-27
US11248606B2 (en) 2022-02-15
DE202015009525U1 (de) 2018-02-15
EP4273403A3 (fr) 2024-04-03
EP3597920B1 (fr) 2023-09-06
JP2017514069A (ja) 2017-06-01
EP3134649B1 (fr) 2018-04-04
US20240175436A1 (en) 2024-05-30
US20200040894A1 (en) 2020-02-06
WO2015162296A3 (fr) 2015-12-23
EP3597920A3 (fr) 2021-03-24
US20220136504A1 (en) 2022-05-05
US20170045050A1 (en) 2017-02-16
US20180112663A2 (en) 2018-04-26
EP3358189B1 (fr) 2023-10-11
EP3358189A1 (fr) 2018-08-08
EP3358189B9 (fr) 2024-01-03
WO2015162296A2 (fr) 2015-10-29
US10400769B2 (en) 2019-09-03
ES2668317T5 (es) 2023-04-10
EP4273403A2 (fr) 2023-11-08
ES2668317T3 (es) 2018-05-17
ES2967470T3 (es) 2024-04-30
JP6545787B2 (ja) 2019-07-17
EP3134649B2 (fr) 2022-12-14
CN106536933B (zh) 2019-07-12
DE102014105882A1 (de) 2015-11-12
EP3597920A2 (fr) 2020-01-22
ES2963314T3 (es) 2024-03-26

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