WO2007026618A1 - 内接型ギヤポンプ - Google Patents
内接型ギヤポンプ Download PDFInfo
- Publication number
- WO2007026618A1 WO2007026618A1 PCT/JP2006/316755 JP2006316755W WO2007026618A1 WO 2007026618 A1 WO2007026618 A1 WO 2007026618A1 JP 2006316755 W JP2006316755 W JP 2006316755W WO 2007026618 A1 WO2007026618 A1 WO 2007026618A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear pump
- teeth
- tooth
- rotor
- angle
- Prior art date
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
- 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
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
-
- 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
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
-
- 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
-
- 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
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps 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
Definitions
- the present invention relates to an internal gear pump that sucks and discharges fluid by changing the volume of a cell formed between an inner rotor and an outer rotor.
- the inscribed gear pump shown in Patent Document 1 has an inner rotor with n (n is a natural number) outer teeth and an outer rotor with n + 1 inner teeth that mesh with these outer teeth.
- a rotor and a casing formed with a suction port through which fluid is sucked and a discharge port through which fluid is discharged are formed, and when the inner rotor rotates, the outer teeth mesh with the inner teeth and the outer mouth rotates. Then, fluid is sucked and discharged by changing the volume of a plurality of cells formed between the rotors.
- the cells are individually partitioned by the contact between the outer teeth of the inner rotor and the inner teeth of the outer rotor on the front and rear sides in the rotational direction, and both sides are partitioned by a casing. This constitutes an independent fluid transfer chamber.
- Each cell is in the middle of the process of meshing the external teeth and the internal teeth! Then, after the volume reaches the maximum, when moving along the discharge port, the volume is reduced and the fluid is discharged.
- Patent Document 1 Japanese Patent Laid-Open No. 2003-328959
- the rear ends of the rotors of the suction port in the rotational direction and the front ends of the discharge port in the rotational direction are Distance, that is, the partition width force of the port is larger than the width at the meshing portion of the external teeth along the rotation direction.
- the distance between the suction port and the discharge port of the casing at the position where the cell volume is minimum is larger than the width of the cell having the minimum volume. Therefore, among the plurality of cells, the so-called fluid confinement, in which the cells of the minimum volume located at the meshing position where the rotors mesh with each other and transmit the rotational driving force from the outer teeth to the inner teeth is sealed. This was a factor that reduced the transfer efficiency (ratio between the discharge rate and the suction rate) of the inscribed gear pump.
- the present invention has been made in view of such problems, and an object of the present invention is to provide an internal gear pump that prevents the occurrence of fluid confinement and has improved conveyance efficiency. Means for solving the problem
- the inscribed gear pump according to the present invention is configured so that the teeth of both rotors are rotated when the inner rotor and the outer rotor rotate together.
- An internal gear pump that conveys fluid by sucking and discharging fluid by changing the volume of cells formed between the faces: an inner rotor with n (n is a natural number) external teeth; An outer rotor formed with n + 1 internal teeth that mesh with the outer teeth; a casing formed with a suction port for sucking fluid and a discharge port for discharging fluid;
- a first angle formed by a first straight line connecting the rotation center and the tooth tip of the external tooth and a second straight line connecting the rotation center and the meshing part of the external tooth is the first angle.
- a third straight line connecting the bottom of the external teeth and the second straight line There second angle of 1.4 times or more forms 1. than 8 times.
- both rotors in the tooth tip portion including the meshing portion of the external teeth The width along the rotation direction of the suction port is widened, and this width can be made closer to the distance between the front end of the suction port in the rotation direction and the rear end of the discharge port in the rotation direction, that is, the partition width of the port. Therefore, among the plurality of cells, so-called fluid confinement occurs, in which the cells with the smallest volume located at the meshing position where the rotors mesh together to transmit the rotational driving force from the outer teeth to the inner teeth are sealed. Can be prevented, and the conveying efficiency of the inscribed gear pump can be improved.
- the first angle is smaller than 1.4 times the second angle, the above-described effect is not achieved, and the transfer efficiency of the internal gear pump cannot be improved. If the first angle is larger than 1.8 times the second angle, the tooth surface of the inner teeth of the outer rotor is likely to wear, and the durability of the internal gear pump is reduced.
- the distance between the rear end of the suction port in the rotation direction of both rotors and the front end of the discharge port in the rotation direction is equal to the width along the rotation direction of the outer teeth. It may be.
- the width force is equal to the partition width of the port along the rotation direction in the meshing portion of the external teeth, the fluid is confined as described above in the cell having the minimum volume.
- the first angle is not less than 1.4 times and not more than 1.8 times the second angle
- the rotational directions of both rotors in the tooth tip portion including the meshing portion of the external teeth are met.
- the width is equal to the port partition width. Therefore, it is possible to reliably avoid the occurrence of the backflow even if the port partition width is not reduced and the current equivalent.
- FIG. 1 is a plan view of an essential part showing an inscribed gear pump in an embodiment according to the present invention.
- FIG. 2 is an enlarged view showing the meshing and part of the internal gear pump shown in FIG. 1.
- FIG. 3 is a view showing a result of a first test for verifying an operation effect of the internal gear pump according to the present invention.
- FIG. 4 is a diagram showing the results of a second test for verifying the function and effect of the internal gear pump according to the present invention.
- the casing 50 is housed inside.
- the rotation center O of the outer rotor 30 is the rotation of the inner rotor 20.
- Eccentricity e is eccentric with respect to rolling center O.
- the rotation center of the drive shaft 60 and the rotation center Ol of the inner rotor 20 coincide.
- the rotation driving force is transmitted to the mounting hole 22, and the inner rotor 20 also rotates about the rotation center O.
- the rotational driving force of the inner rotor 20 is transmitted to the outer rotor 30 when the outer teeth 21 mesh with the inner teeth 31, and the outer rotor 30 rotates around the rotation center O.
- inner surface 50a of casing 50, end surface 20a of inner rotor 20, end surface 30a of outer rotor 30, and outer rotor 30 Slidably contact with the outer peripheral surface 30b.
- a plurality of cells C are formed between the tooth surfaces of the inner rotor 20 and the tooth surfaces of the outer rotor 30 along the rotational direction F of the inner rotor 20 and the outer rotor 30.
- Each cell C is individually partitioned by the contact between the outer teeth 21 of the inner rotor 20 and the inner teeth 31 of the outer rotor 30 on the front side and the rear side in the rotational direction F, and both side surfaces of the casing 50 are It is partitioned by an inner surface 50a, thereby forming an independent fluid transfer chamber.
- the cell C rotates with the rotation of the inner rotor 20 and the outer rotor 30 and repeats increasing and decreasing in volume with one rotation as one cycle.
- the rotational driving force of the inner rotor 20 is such that the outer teeth 21 are applied to the inner teeth 31 at the position where the cell C having the smallest volume is formed.
- the casing 50 is provided with an arcuate suction port 51 in plan view that communicates with the cell C when the volume increases, and an arcuate discharge port 52 that communicates with the cell C when the volume decreases.
- the fluid sucked into the cell C from the suction port 51 is conveyed along with the rotation of the inner rotor 20 and the outer port 30 and is discharged from the discharge port 52.
- the illustrated inner rotor 20 has an abduction cycloid curve created by a first abduction circle that circumscribes the first basic circle di and rolls without slipping, and has a shape of a tooth tip portion 21b of the outer tooth 21.
- An addendum cycloid curve created by the first addendum circle inscribed in the basic circle di and slipping is formed as the shape of the tooth gap portion 21c of the outer tooth 21.
- the outer rotor 30 has an abduction cycloid curve created by a second abduction circle that circumscribes the second basic circle do and slides in a shape of the tooth groove portion 31b of the inner tooth 31.
- An addendum cycloid curve created by a second addendum circle inscribed in the basic circle do and slips is formed as the shape of the tip portion 31c of the inner tooth 31.
- the first angle ⁇ 1 formed by the second straight line L2 connecting O and the meshing portion 21a of the external tooth 21 is the third straight line L3 connecting the rotation center O and the root 21e of the external tooth 21;
- the second angle L2 formed by the second straight line L2 is 1. 4 times or more and 1. 8 times or less of 0 2.
- the meshing portion 21a of the external tooth 21 is an intersection of the tooth surface of the external tooth 21 and the first basic circle di.
- the circumferential distance between the rear end 51a of the suction port 51 in the rotational direction F and the front end 52a of the discharge port 52 in the rotational direction F is a meshing portion of the external teeth 21 along the rotational direction F. It is equivalent to the width in 21a.
- the distance between the intersection of the rear end 51a of the suction port 51 with the first basic circle di and the intersection of the front end 52a of the discharge port 52 and the first basic circle di is the external tooth along the rotation direction F. This is equivalent to the width of the 21 staggered portion 21a.
- the rotation direction F of the inner rotor 20 and the outer rotor 30 in the tooth tip portion 21b including the meshing portion 21a of the outer tooth 21 is The width along the line can be made closer to the distance between the front end 51a of the suction port 51 and the rear end 52a of the discharge port 52, that is, the partition width of the port. Accordingly, among the plurality of cells C, the inner volume 20 and the outer rotor 30 are squeezed together to transmit the rotational driving force from the outer teeth 21 to the inner teeth 31. Occurrence of the so-called fluid confinement that is sealed can be prevented, and the conveying efficiency of the internal gear pump 10 can be improved.
- the width force along the rotational direction F in the meshing portion 21a of the external tooth 21 is equal to the partition width of the port, so that the fluid is confined as described above in the cell C having the minimum volume.
- the first angle ⁇ 1 is set to be not less than 1.4 times and not more than 1.8 times the second angle ⁇ 2, and the rotational direction F in the tooth tip portion 21 b including the meshing portion 21 a of the external tooth 21 is determined.
- this width is equal to the partition width of the port. Therefore, the port partition width is not narrowed and can be maintained at the same level as the current one, and the occurrence of the backflow can be surely avoided.
- a force indicating a configuration in which the shapes of the outer teeth 21 and the inner teeth 31 are formed based on a cycloid curve instead, for example, a tooth based on a trochoid curve.
- a surface shape may be formed.
- the rotation direction F in the tooth tip portion 21b including the meshing portion 21a of the external tooth 21 is increased. If the width along the width is increased, the width along the rotation direction F at the meshing portion 21a of the external tooth 21 should not be equal to the partition width of the port.
- an internal gear pump that prevents the occurrence of fluid confinement and has improved transport efficiency.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Gears, Cams (AREA)
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2006800259698A CN101223362B (zh) | 2005-08-31 | 2006-08-25 | 内接型齿轮泵 |
US11/996,643 US7819645B2 (en) | 2005-08-31 | 2006-08-25 | Internal gear pump |
KR1020087001696A KR100932406B1 (ko) | 2005-08-31 | 2006-08-25 | 내접형 기어 펌프 |
EP06783044.8A EP1921316B1 (en) | 2005-08-31 | 2006-08-25 | Internal gear pump |
ES06783044.8T ES2535539T3 (es) | 2005-08-31 | 2006-08-25 | Bomba de engranaje interior |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005252374A JP4889981B2 (ja) | 2005-08-31 | 2005-08-31 | 内接型ギヤポンプ |
JP2005-252374 | 2005-08-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007026618A1 true WO2007026618A1 (ja) | 2007-03-08 |
Family
ID=37808712
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/316755 WO2007026618A1 (ja) | 2005-08-31 | 2006-08-25 | 内接型ギヤポンプ |
Country Status (8)
Country | Link |
---|---|
US (1) | US7819645B2 (ja) |
EP (1) | EP1921316B1 (ja) |
JP (1) | JP4889981B2 (ja) |
KR (1) | KR100932406B1 (ja) |
CN (1) | CN101223362B (ja) |
ES (1) | ES2535539T3 (ja) |
MY (1) | MY143546A (ja) |
WO (1) | WO2007026618A1 (ja) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9624929B2 (en) * | 2012-12-21 | 2017-04-18 | Lg Innotek Co., Ltd. | Electric pump |
JP6599181B2 (ja) * | 2015-09-07 | 2019-10-30 | アイシン機工株式会社 | ギヤポンプ |
KR102008612B1 (ko) * | 2018-02-19 | 2019-08-09 | 주식회사 바디프랜드 | 마사지 모듈 및 이를 포함하는 마사지 장치 |
CN111425391B (zh) * | 2020-05-08 | 2022-08-05 | 潍柴动力股份有限公司 | 转子泵 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60195989U (ja) * | 1984-06-07 | 1985-12-27 | 株式会社不二越 | 内接ギヤポンプ |
JPS6456589U (ja) * | 1987-10-05 | 1989-04-07 | ||
JPH04179880A (ja) * | 1990-11-13 | 1992-06-26 | Matsushita Electric Ind Co Ltd | 冷媒ポンプ |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB233423A (en) * | 1924-02-07 | 1925-05-07 | Hill Compressor & Pump Co Inc | Improvements in or relating to rotary pumps or the like |
GB958779A (en) * | 1960-05-19 | 1964-05-27 | Robert Wesley Brundage | Improvements in gear type hydraulic pumps and motors |
GB2085969B (en) * | 1980-10-17 | 1984-04-26 | Hobourn Eaton Ltd | Rotary positive-displacement pumps |
JPS60195989A (ja) * | 1984-03-19 | 1985-10-04 | 株式会社日立製作所 | 樹脂コ−テイング装置 |
JPS61108884A (ja) * | 1984-10-31 | 1986-05-27 | Aisin Seiki Co Ltd | トロコイド型オイルポンプ |
JPS62151641A (ja) | 1985-12-23 | 1987-07-06 | Toyota Motor Corp | 自動車構成部品の振動防止方法 |
JPS6456589A (en) * | 1987-08-28 | 1989-03-03 | Mitsubishi Rayon Co | Optical recording material |
ATE247778T1 (de) * | 1997-09-04 | 2003-09-15 | Sumitomo Electric Industries | Innenzahnradpumpe |
JP4823455B2 (ja) * | 1999-06-14 | 2011-11-24 | ウェイ ショウーン | ギヤとこのギヤによる一対の係合ギヤを備えた流体機械 |
JP3917026B2 (ja) * | 2002-07-10 | 2007-05-23 | アイシン精機株式会社 | オイルポンプロータ |
US6652253B1 (en) * | 2002-07-15 | 2003-11-25 | General Motors Corporation | Hydraulic pump having a noise reduction recess |
MY141586A (en) * | 2002-07-18 | 2010-05-14 | Mitsubishi Materials Pmg Corp | Oil pump rotor |
JP3906806B2 (ja) * | 2003-01-15 | 2007-04-18 | 株式会社日立プラントテクノロジー | スクリュウ圧縮機およびそのロータの製造方法と製造装置 |
JP2004245151A (ja) * | 2003-02-14 | 2004-09-02 | Hitachi Unisia Automotive Ltd | オイルポンプ |
JP2003328959A (ja) | 2003-06-13 | 2003-11-19 | Hitachi Unisia Automotive Ltd | オイルポンプ |
-
2005
- 2005-08-31 JP JP2005252374A patent/JP4889981B2/ja not_active Expired - Fee Related
-
2006
- 2006-08-25 EP EP06783044.8A patent/EP1921316B1/en not_active Not-in-force
- 2006-08-25 WO PCT/JP2006/316755 patent/WO2007026618A1/ja active Application Filing
- 2006-08-25 CN CN2006800259698A patent/CN101223362B/zh not_active Expired - Fee Related
- 2006-08-25 MY MYPI20080128A patent/MY143546A/en unknown
- 2006-08-25 ES ES06783044.8T patent/ES2535539T3/es active Active
- 2006-08-25 US US11/996,643 patent/US7819645B2/en not_active Expired - Fee Related
- 2006-08-25 KR KR1020087001696A patent/KR100932406B1/ko not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60195989U (ja) * | 1984-06-07 | 1985-12-27 | 株式会社不二越 | 内接ギヤポンプ |
JPS6456589U (ja) * | 1987-10-05 | 1989-04-07 | ||
JPH04179880A (ja) * | 1990-11-13 | 1992-06-26 | Matsushita Electric Ind Co Ltd | 冷媒ポンプ |
Non-Patent Citations (1)
Title |
---|
See also references of EP1921316A4 * |
Also Published As
Publication number | Publication date |
---|---|
US7819645B2 (en) | 2010-10-26 |
CN101223362B (zh) | 2010-09-22 |
KR100932406B1 (ko) | 2009-12-17 |
MY143546A (en) | 2011-05-31 |
ES2535539T3 (es) | 2015-05-12 |
JP2007064122A (ja) | 2007-03-15 |
CN101223362A (zh) | 2008-07-16 |
EP1921316A1 (en) | 2008-05-14 |
EP1921316B1 (en) | 2015-02-18 |
EP1921316A4 (en) | 2013-10-30 |
KR20080022584A (ko) | 2008-03-11 |
US20100158734A1 (en) | 2010-06-24 |
JP4889981B2 (ja) | 2012-03-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5353383B2 (ja) | ルーツ式流体機械 | |
WO2007026618A1 (ja) | 内接型ギヤポンプ | |
JP4650180B2 (ja) | オイルポンプロータ | |
JPWO2004044430A1 (ja) | 内接型オイルポンプロータ | |
JP2004044436A (ja) | オイルポンプロータ | |
JP4485770B2 (ja) | オイルポンプロータ | |
JP4675809B2 (ja) | 内接型ギヤポンプロータおよび内接型ギヤポンプ | |
JP3734617B2 (ja) | オイルポンプロータ | |
JP4255798B2 (ja) | 内接型ギヤポンプロータおよび内接型ギヤポンプ | |
JP6011297B2 (ja) | 内接ギヤポンプ | |
JP4393943B2 (ja) | オイルポンプロータ | |
JP3860125B2 (ja) | オイルポンプロータ | |
JP3132631B2 (ja) | 内接型オイルポンプロータ | |
JP4255768B2 (ja) | オイルポンプロータ | |
JP4255771B2 (ja) | オイルポンプロータ | |
JPH09256965A (ja) | オイルポンプロータ | |
JP4255770B2 (ja) | オイルポンプロータ | |
JP4255769B2 (ja) | オイルポンプロータ | |
WO2005064163A1 (ja) | 内接型ギアポンプ | |
KR20060038368A (ko) | 오일펌프 로터 | |
JP4961624B2 (ja) | 内接歯車ポンプ | |
JP2004197670A (ja) | 内接型オイルポンプ | |
JP6503855B2 (ja) | トロコイド型ポンプ | |
JP2004150295A (ja) | 内接ヘリカル型のオイルポンプロータおよびオイルポンプ | |
JP2006200418A (ja) | 内接型ギヤポンプ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200680025969.8 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 211/KOLNP/2008 Country of ref document: IN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020087001696 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2006783044 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 11996643 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |