CN1334904A - Twin delivery screws provided for installation in positive-displacement machines, especially pumps - Google Patents
Twin delivery screws provided for installation in positive-displacement machines, especially pumps Download PDFInfo
- Publication number
- CN1334904A CN1334904A CN99816093.8A CN99816093A CN1334904A CN 1334904 A CN1334904 A CN 1334904A CN 99816093 A CN99816093 A CN 99816093A CN 1334904 A CN1334904 A CN 1334904A
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- China
- Prior art keywords
- tooth
- screws provided
- delivery screws
- twin delivery
- flank
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- 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.)
- Pending
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Classifications
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- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
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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)
Abstract
Prior art multithread twin delivery screws comprise point-symmetric profiles , small inclines, and very large angles of wrap and, due to the residual blow-hole losses between the working cells, have to be operated in a high-speed manner. Prior art single-thread and multi-thread embodiments seal-off work cells without the use of blow-hole connections and produce a good vacuum and a good level of efficiency when operated at average and low rotational speeds, but don't suit at high rotational speeds. The invention eliminates this deficiency and combines the advantages of both aforementioned embodiments. The invention provides a uniform solution for a broad range of rotational speeds by using delivery screws (1, 2) which are not point-symmetric and which comprises multithread front profiles with a centrical center-of-gravity. Delivery screws of this type function without blow-hole losses, are also suited for high-speed operation, and, due to the lack of balancing cavities with average inclines, can be equipped with channels f or inner cooling. These favorable adaptations possibilities with regard to process control permit the invention to be used in the fields of medicine, chemicals and semiconductor technology.
Description
The present invention relates to a kind of especially pump twin delivery screws provided of positive-displacement machine that be used for being installed in, be particularly useful for the reverse outer gearing with＞720 ° looping angle of parallel axes, and it is identical to be embodied as end profile, the hollow flank of tooth that respectively has a cycloidal, this pair screw thread constitute an axial chamber order that does not have the good bulkhead of pore connection in housing.
Known various types of twin delivery screws provided and characteristic is described below.
In first kind of so two screw thread, each carries screw thread that a plurality of threaded bodies that axial front and back are arranged on a common shaft are arranged respectively.
Disclosed pair of screw thread has the different threaded body of looping direction in document EP 0496170 A2 and DE 4316735 A1.Here divide volume flowrate, thereby saved critical dynamic seal (packing).Even the non-point symmetry section to single head also guarantees transient equiliblium in addition.
It is right that document JP 63-36086 and DE 19522559 A1 show this screw thread of first type equally, but the threaded body of arranging here has different pitch.Make the compressing area axial expansion thus, thereby the heat exchange area of housing increases, cause external refrigeration to be improved.
Combine above-mentioned two features in DE 19614562 A1 in the disclosed volute pump (Schraubenpumpe), promptly the threaded body that front and back are arranged on an axle has different looping directions and different pitch.
The shortcoming of above-mentioned first kind of two screw thread is that especially each screw rod has a threaded body has relatively increased expense.In addition, except patent application DE 19522559 A1, all aforementioned publications all are the single head rotors, although complete equilibrium, strong tendency is in flexure vibrations because its length is very long, and this is not suitable for high-revolving pump.
Second kind twin delivery screws provided in, screw thread is a bull, and the section point symmetry.Particularly, the SRM section of " Svenska Rotor Maskiner Aktiebolag " company promptly belongs to this type of, and wherein, two rotors have the different numbers of teeth, in the rotor with individual be " protrusion ", another is " being recessed into ".In these known sections, there is not imbalance problem, because they are point-symmetric.This not only relates to " symmetry " section that has the mirror image flank of tooth, and relates to " asymmetric " section that has the different flank of tooth.
The shortcoming of this second kind two screw threads is that they can not constitute an axial chamber order in a pump case, because be positioned at the housing seamed edge place on the line of cut of two housing bores, has formed a so-called pore.Screw thread has the large screw pitch parcel and twines the angle, even also obtain good limiting vacuum and good efficiency thus under high rotating speed.This is external to have visual function in the compressor of this pair of screw thread and the end cap of provisioning request end face side.
Cooling off the possibility of this rotor, can be " liquid discharging " of known and extensive use on the one hand, but this be unsuitable for all applications, is an inner cooling system on the other hand, and wherein cooling medium imports by rotor.Patent documentation DE 914886, US 2714314 and US 2441771 disclose the cooling system of one type of back.
Following the third pair screw thread belongs to point symmetry equally.
The two screw threads that have two rectangular cross section are disclosed among patent application DE 19522559 A1 and DE 19522560 A1.After complete understanding, the pump design liaison of realizing with this conveying screw thread present most advanced design flexible.Two rectangular cross section allows high rotating speed not have flexure vibrations, and the not end cap work of band edge face side.Exactly because this but then rectangular cross section, only make very little pitch and very big looping angle in conjunction with high rotating speed (8000 seconds-1) thus condition under could form enough well bulkhead leakage axial chamber order seldom, that is to say that the operation in the slow-speed of revolution and medium speed range causes very poor limiting vacuum and very poor efficient.The cooling of pump herein is to realize by cooling liquid by the numbers on standing part.The cooling of rotor realizes at the heat radiation principle of basis coaxial aperture on the pressure side.For the effective inner cooling system with the cooling medium that flows, the geometrical construction of this rotor does not have the space.
In patent documentation DE 4224969 C1, have identical height of thread, identical number of starts and monosymmetric flank of tooth profile in the disclosed pair of screw thread, by proofreading and correct the flank of tooth profile slit of reducing the loss.But for not having information by the improvement that this measure obtained.
The 4th kind that describes below also is that last a kind of pair of screw thread has the single head section.
Known a kind of pump that has this type rotor is made by Kashiyama, has the rotor of a side bearing, and described rotor has the single head rectangular cross section.Aspect geometrical shape, rotating speed, leakage, limiting vacuum and efficient, this pump and above-mentionedly same problem is arranged by DE 19522559 A1 and the disclosed two of DE 19522560 A1 rectangular cross section.Additional equilibrium problem is solved by the depression in distolateral center portion.In MANUFACTURER, it is unnecessary that strong limited application area and very little size become cooling.
Document GB 112104, GB 670395, disclose two screw threads of the single head section that has the hollow flank of tooth among GB 746628 and the WO 97/21926.By the cycloid (the hollow flank of tooth) that each flank of tooth with the single head section is designed to prolong, alternately form the line of contact of symmetry, this line of contact is extended from seamed edge in the housing to the core circle along the screw thread external frame.This line of contact is divided into the working room that moves arranged superposed vertically with the inner chamber of pump, and the length of working room doubles pitch.Big looping angle (＞720 °) can obtain good bulkhead does not have pore fully, and can reach high efficiency and good limiting vacuum for medium rotating speed (3000 seconds-1) and little rotating speed yet.Output control is not to force to carry out by an end cap; Screw thread itself can work separately.Balance method importantly when realizing that this single head is carried screw thread.By forming cavity end face and/or inner, cut away outside unessential threaded piece, adopting the material of different densities and change looping angle to reach static equilibrium and transient equiliblium.The document of representing the prior art of this method is JP 62291486, and WO 97/21925, JP 0,230 5393 and WO 98/11351.
Can not realize not having the operation of flexure vibrations, especially under the situation of high rotating speed and elongate rotor.Can not realize effective internal rotor cooling in addition, because require significant balance re-entrant portion for this reason.
From these prior aries, task of the present invention provides a kind of conveying screw thread and pays, its can be in very wide speed range the operation of (about 1000-8000 second-1) no problem ground, even and pay the operation that can both obtain good vacuum and not have flexure vibrations up to higher scope in the slow-speed of revolution by this conveying screw thread.In addition, carry screw thread that an effective internal rotor cooling system can be installed, this is especially more meaningful to bigger pump (＞200 meters 3/ hour).
Here the scheme that it shall yet further be noted that some proposition is imaginary scheme.For example at the point symmetry section rotor that has a plurality of hollow flank of tooth described in document US 4224016 and the AU 261792.Although can constitute screw rotor by this section, these rotors can not constitute axial chamber order in a housing, and opposite be that all partial volumes all interconnect, thereby can't realize positive-displacement machine.
In order to solve above-mentioned task, according to twin delivery screws provided being characterised in that of the present invention, end profile be bull but be not point-symmetric, firm what a flank of tooth of a tooth is designed to the hollow flank of tooth of cycloidal, other geared surface is convex curved substantially, makes the profile center of gravity consistent with rotating center by correspondingly constituting a unique end profile boundary curve.
According to a kind of design proposal, at the tooth position of internal rotor, be provided with the passage of thread-shaped, cooling medium flows through this passage.
Describe embodiments of the invention with reference to the accompanying drawings in detail.Accompanying drawing is represented:
Fig. 1 is twin delivery screws provided pair in a housing, corresponding to the cross section of the I-I line among Fig. 3,
Fig. 2 is a twin delivery screws provided pair different cross section of tip circle camber line,
Fig. 3 is have internal cooling channel twin delivery screws provided, along the partial sectional view of arrow III direction among Fig. 1.
Fig. 1 has schematically illustrated the cross section with the housing of 3 expressions, and twin delivery screws provided 1 and 2 of first embodiment according to the invention is arranged in this housing.The view of Fig. 1 is that the I-I line in Fig. 3 dissects, but the passages of 11 expressions among Fig. 3 wherein are not shown.Each shown screw thread has a same threaded body that is associated, and preferably is used to have the dried process pump of external synchronizer.The section of screw thread is made up of following boundary curve: a hollow flank of tooth 6 carries out the transition to a tip circle camber line K in its radial outer end portion through a seamed edge 7.The hollow flank of tooth 6 of cycloidal tangentially carries out the transition to root circular arc line F at its radial inner end.The other end at the root circular arc line is connected to first convex side 8 through a knuckle radius, is connected to another tip circle camber line K in the radial outer end portion of this flank of tooth 8.The other end at this another tip circle camber line is second convex side 9, and this flank of tooth 9 itself carries out the transition to another root circular arc line F through a knuckle radius.At the other end of this another root circular arc line, profile carries out the transition to the 3rd convex side 10 through a knuckle radius again, and this flank of tooth 10 is received the tip circle of having addressed in its radial outer end portion.The shape and the mutual alignment of above-mentioned boundary curve are selected like this, and promptly the plane center of gravity of the cross section of end profile just overlaps with the rotating shaft of relevant conveying screw thread.Thus balanced measure become unnecessary, carrying threaded interior that the cooling channel can be set, shown in Fig. 3 reference character 11.
Fig. 2 shows twin delivery screws provided according to second embodiment of the invention, and in order to follow above-mentioned condition, promptly profile section center of gravity overlaps with rotating center, and each carries two tip circle arc bK1 of screw thread and the radius r K1 of bK2, and rK2 needn't be identical as shown in Figure 1.According to Fig. 2, rK1＞rK2, thereby and convex side 8 and 9 adjacent tip circle arc K and inner walls between tangible gap is arranged.But this gap does not have any meaning to the bulkhead of working room, because this finishes at seamed edge 7 and adjacent with it tip circle arc place.Different Root radius rF1, rF2 is by wheelbase and tip circle radius r K1, rK2 generation of forced.By this embodiment, increased and formed the housing 3 of active chamber and the surface of rotor 1,2, this combines very favourable with the interior cooling of rotor.
Fig. 3 illustrates the twin delivery screws provided of Fig. 1 with the broken section along arrow III direction among Fig. 1.The design of two head rotor mirror images also is meshing with each other.There is the passage 11 of a thread-shaped in portion within it, and cooling medium flows through this passage during work.Each rotor design becomes monomer.Can certainly be assembled by a rotor shaft 4 and a threaded body 5 by each rotor, they can be with identical or different made.Because favourable end profile shape also can be used the material than small intensity in this case.If cooling also can be used not pourable special material in the cancellation rotor.
Claims (11)
1. be used for being installed in positive-displacement machine especially pump twin delivery screws provided (1,2), be particularly useful for the reverse outer gearing with＞720 ° looping angle of parallel axes, and it is identical to be embodied as end profile, the hollow flank of tooth that respectively has a cycloidal, this pair screw thread constitutes an axial chamber order that does not have the good bulkhead of pore connection in a housing (3), it is characterized in that, end profile be bull but be not point-symmetric, firm what a flank of tooth of a tooth is designed to the hollow flank of tooth (6) of cycloidal, all other at least three flank of tooth (8,9,10) basic convex curved makes the profile center of gravity consistent with rotating center by correspondingly constituting a unique end profile boundary curve.
2. according to claim 1 twin delivery screws provided, it is characterized in that end profile has two teeth, by the hollow flank of tooth of so-called cycloidal (6), three convex sides (8,9,10), two identical tip circle camber lines (K) of radius constitute with two identical root circular arc lines (F) of radius.
3. according to claim 2 twin delivery screws provided, it is characterized in that, with the hollow flank of tooth (6) be connected on the same circular arc line (F) first convex side (8) and with the 3rd convex side (10) that the hollow flank of tooth (6) is connected on the same tip circle camber line (K) be congruent.
4. according to claim 3 twin delivery screws provided, it is characterized in that second convex side (9) and first (8) becomes the mirror image design with the 3rd convex side (10).
5. according to claim 1 twin delivery screws provided, it is characterized in that, be not all tip circle camber lines (K) thereby be not all root circular arc lines (F) be that radius is identical, the maximum tip circle corresponding with housing bore belongs to the tooth that has the hollow flank of tooth (6).
6. described twin delivery screws provided according to one of claim 1 to 5, it is characterized in that each screw thread all is designed to monomeric form (Monobloc-Bauweise).
7. described twin delivery screws provided according to one of claim 1 to 5, it is characterized in that each screw thread is assembled by polylith.
8. according to claim 7 twin delivery screws provided, it is characterized in that rotor shaft (4) and threaded body (5) are by different made.
9. described twin delivery screws provided according to one of claim 1 to 8, it is characterized in that at the tooth position of threaded interior, be provided with spirality channel (11), it is used to make cooling medium to flow through.
10. described twin delivery screws provided according to one of claim 1 to 9, it is characterized in that pitch changes along axis.
11. according to claim 10 twin delivery screws provided, it is characterized in that profile changes along axis.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP99810101.8 | 1999-02-08 | ||
| EP99810101A EP1026399A1 (en) | 1999-02-08 | 1999-02-08 | Twin feed screw |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1334904A true CN1334904A (en) | 2002-02-06 |
Family
ID=8242666
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99816093.8A Pending CN1334904A (en) | 1999-02-08 | 1999-12-07 | Twin delivery screws provided for installation in positive-displacement machines, especially pumps |
Country Status (6)
| Country | Link |
|---|---|
| EP (2) | EP1026399A1 (en) |
| JP (1) | JP2002536593A (en) |
| CN (1) | CN1334904A (en) |
| AU (1) | AU1371400A (en) |
| CA (1) | CA2362075A1 (en) |
| WO (1) | WO2000047897A1 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100538078C (en) * | 2005-02-16 | 2009-09-09 | 阿特里尔斯布希股份有限公司 | Volumetric rotary machine with asymmetric profile rotor |
| CN1904365B (en) * | 2005-07-29 | 2010-06-16 | 良峰塑胶机械股份有限公司 | Designing method of claw type rotor |
| CN101963153A (en) * | 2009-07-22 | 2011-02-02 | 株式会社丰田自动织机 | Screw rotor |
| CN102678542A (en) * | 2011-03-11 | 2012-09-19 | 株式会社丰田自动织机 | Screw pump |
| CN103452846A (en) * | 2013-10-08 | 2013-12-18 | 李锦上 | Plug rod compressor |
| CN107882735A (en) * | 2017-11-02 | 2018-04-06 | 西安交通大学 | A kind of strict closed type bidentate Twin-screw vacuum pump molded lines of rotor |
| CN111396311A (en) * | 2020-04-26 | 2020-07-10 | 陕西理工大学 | Hollow screw rotor and processing method thereof |
| CN111779676A (en) * | 2020-07-15 | 2020-10-16 | 西安交通大学 | Double-tooth rotor compressor rotor profile, double-tooth rotor and compressor |
| CN111828327A (en) * | 2020-07-15 | 2020-10-27 | 高秀峰 | Multi-tooth rotor compressor rotor molded line, multi-tooth rotor and compressor |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH694339A9 (en) | 2000-07-25 | 2005-03-15 | Busch Sa Atel | Twin screw rotors and those containing Ve rdraengermaschinen. |
| DE10300203A1 (en) * | 2003-01-08 | 2004-07-22 | Pfeiffer Vacuum Gmbh | Twin-shaft vacuum pump and method for manufacturing a twin-shaft vacuum pump |
| DE102011118050A1 (en) | 2011-11-05 | 2013-05-08 | Ralf Steffens | Spindle compressor profile contour for two-shaft positive displacement rotary engine, has head arc with force groove, which is provided in such manner that overall profile centroid lies as close to rotor pivot point |
| US10495090B2 (en) | 2015-08-27 | 2019-12-03 | Ingersoll-Rand Company | Rotor for a compressor system having internal coolant manifold |
| US9683569B2 (en) | 2015-08-27 | 2017-06-20 | Ingersoll-Rand Company | Compressor system having rotor with distributed coolant conduits and method |
| JP7096044B2 (en) * | 2018-03-30 | 2022-07-05 | 株式会社日立産機システム | Screw rotor and fluid machine body |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB112104A (en) | 1917-07-05 | 1917-12-27 | Edward Nuebling | Improvements in or relating to Rotary Meters, Pumps and Motors. |
| GB527339A (en) * | 1939-04-06 | 1940-10-07 | Paul Leistritz | Improvements in screw pumps or screw motors |
| US2441771A (en) | 1941-05-31 | 1948-05-18 | Jarvis C Marble | Yieldable drive for rotors |
| DE914886C (en) | 1949-09-15 | 1954-07-12 | Svenska Rotor Maskiner Ab | Cooling device for multi-part housings or runners, especially of rotary piston machines with helical wheels |
| GB670395A (en) | 1950-01-16 | 1952-04-16 | Roots Connersville Blower Corp | Improvements in or relating to rotary screw-pumps and motors |
| US2714314A (en) | 1951-05-15 | 1955-08-02 | Howden James & Co Ltd | Rotors for rotary gas compressors and motors |
| GB746628A (en) | 1953-04-06 | 1956-03-14 | Dresser Ind | Improvements in pumps or motors of the meshing screw type |
| DE1289433B (en) * | 1960-07-08 | 1969-02-13 | Prinz Fritz | Screw rotor for screw pumps or the like with hollow screw threads |
| US4224016A (en) | 1978-09-27 | 1980-09-23 | Brown Arthur E | Rotary positive displacement machines |
| JPS62291486A (en) | 1986-06-12 | 1987-12-18 | Taiko Kikai Kogyo Kk | Screw compressor |
| JPS6336086A (en) | 1986-07-30 | 1988-02-16 | Taiko Kikai Kogyo Kk | Multi-stage screw type vacuum pump |
| JPH02305393A (en) | 1989-05-19 | 1990-12-18 | Hitachi Ltd | Screw rotor and screw vacuum pump |
| CA2058325A1 (en) | 1990-12-24 | 1992-06-25 | Mark E. Baran | Positive displacement pumps |
| DE4224969C1 (en) | 1992-07-29 | 1993-09-30 | Heinrich Moeller | Feed screw pair for rotating positive displacement pumps |
| DE4316735C2 (en) | 1993-05-19 | 1996-01-18 | Bornemann J H Gmbh & Co | Pumping method for operating a multi-phase screw pump and pump |
| JP2904719B2 (en) * | 1995-04-05 | 1999-06-14 | 株式会社荏原製作所 | Screw rotor, method for determining cross-sectional shape of tooth profile perpendicular to axis, and screw machine |
| DE19614562A1 (en) | 1995-04-13 | 1996-10-17 | Ingersoll Dresser Pump Co | Screw pump |
| DE19522560A1 (en) | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Vacuum pump with pair of helical inter-meshing displacement rotors |
| DE19522559A1 (en) | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Axial delivery compressor, especially screw compressor |
| ES2186785T3 (en) | 1995-12-11 | 2003-05-16 | Busch Sa Atel | DOUBLE SCREW SYSTEM. |
| DE59604068D1 (en) | 1995-12-11 | 2000-02-03 | Busch Sa Atel | TWIN CONVEYOR SCREWS |
| JP4307559B2 (en) | 1996-09-12 | 2009-08-05 | アトリエール ブッシュ ソシエテ アノニム | Screw rotor device |
-
1999
- 1999-02-08 EP EP99810101A patent/EP1026399A1/en not_active Withdrawn
- 1999-12-07 WO PCT/CH1999/000587 patent/WO2000047897A1/en not_active Application Discontinuation
- 1999-12-07 EP EP99973677A patent/EP1151199A1/en not_active Withdrawn
- 1999-12-07 CN CN99816093.8A patent/CN1334904A/en active Pending
- 1999-12-07 AU AU13714/00A patent/AU1371400A/en not_active Abandoned
- 1999-12-07 JP JP2000598773A patent/JP2002536593A/en active Pending
- 1999-12-07 CA CA002362075A patent/CA2362075A1/en not_active Abandoned
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100538078C (en) * | 2005-02-16 | 2009-09-09 | 阿特里尔斯布希股份有限公司 | Volumetric rotary machine with asymmetric profile rotor |
| CN1904365B (en) * | 2005-07-29 | 2010-06-16 | 良峰塑胶机械股份有限公司 | Designing method of claw type rotor |
| CN101963153A (en) * | 2009-07-22 | 2011-02-02 | 株式会社丰田自动织机 | Screw rotor |
| CN101963153B (en) * | 2009-07-22 | 2013-09-11 | 株式会社丰田自动织机 | Screw rotor |
| CN102678542A (en) * | 2011-03-11 | 2012-09-19 | 株式会社丰田自动织机 | Screw pump |
| CN103452846B (en) * | 2013-10-08 | 2016-08-03 | 李锦上 | Plug rod compressor |
| CN103452846A (en) * | 2013-10-08 | 2013-12-18 | 李锦上 | Plug rod compressor |
| CN107882735A (en) * | 2017-11-02 | 2018-04-06 | 西安交通大学 | A kind of strict closed type bidentate Twin-screw vacuum pump molded lines of rotor |
| CN107882735B (en) * | 2017-11-02 | 2019-05-24 | 西安交通大学 | A kind of bidentate Twin-screw vacuum pump with stringent closed type rotor line |
| CN111396311A (en) * | 2020-04-26 | 2020-07-10 | 陕西理工大学 | Hollow screw rotor and processing method thereof |
| CN111779676A (en) * | 2020-07-15 | 2020-10-16 | 西安交通大学 | Double-tooth rotor compressor rotor profile, double-tooth rotor and compressor |
| CN111828327A (en) * | 2020-07-15 | 2020-10-27 | 高秀峰 | Multi-tooth rotor compressor rotor molded line, multi-tooth rotor and compressor |
| CN111779676B (en) * | 2020-07-15 | 2021-11-19 | 西安交通大学 | Double-tooth rotor compressor rotor profile, double-tooth rotor and compressor |
| CN111828327B (en) * | 2020-07-15 | 2021-11-30 | 高秀峰 | Multi-tooth rotor compressor rotor molded line, multi-tooth rotor and compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2000047897A1 (en) | 2000-08-17 |
| EP1151199A1 (en) | 2001-11-07 |
| CA2362075A1 (en) | 2000-08-17 |
| EP1026399A1 (en) | 2000-08-09 |
| JP2002536593A (en) | 2002-10-29 |
| AU1371400A (en) | 2000-08-29 |
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| AD01 | Patent right deemed abandoned | ||
| C20 | Patent right or utility model deemed to be abandoned or is abandoned |