JP4784484B2 - Electric pump - Google Patents

Electric pump Download PDF

Info

Publication number
JP4784484B2
JP4784484B2 JP2006299057A JP2006299057A JP4784484B2 JP 4784484 B2 JP4784484 B2 JP 4784484B2 JP 2006299057 A JP2006299057 A JP 2006299057A JP 2006299057 A JP2006299057 A JP 2006299057A JP 4784484 B2 JP4784484 B2 JP 4784484B2
Authority
JP
Japan
Prior art keywords
rotor
shaft
rotating shaft
axial direction
electric
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP2006299057A
Other languages
Japanese (ja)
Other versions
JP2008115748A (en
Inventor
俊郎 藤井
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Priority to JP2006299057A priority Critical patent/JP4784484B2/en
Priority to DE102007052275A priority patent/DE102007052275A1/en
Priority to US11/934,290 priority patent/US20080107550A1/en
Publication of JP2008115748A publication Critical patent/JP2008115748A/en
Application granted granted Critical
Publication of JP4784484B2 publication Critical patent/JP4784484B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing 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
    • F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Description

本発明は、回転軸の軸方向において、電動モータと各ロータとの間にタイミングギアが配設された電動ポンプに関する。   The present invention relates to an electric pump in which a timing gear is disposed between an electric motor and each rotor in the axial direction of a rotating shaft.

例えば、電動ポンプとしての特許文献１に開示の流体機械（スクリューポンプ）は、互いに平行に軸支されたロータ軸がタイミングギアを介して同期回転され、各ロータ軸に固定されたスクリューロータが互いに異なる方向へ回転されることにより、流体の吸入及び吐出を行うようになっている。この流体機械は、一方のロータ軸の一端側に電動モータが連結されるとともに、スクリューロータと電動モータの間に前記タイミングギアが配設されている。また、流体機械において、一対のロータ軸はそれぞれその軸方向に沿ってスクリューロータを貫通している。
特開２００２−５４５８７号公報 For example, in a fluid machine (screw pump) disclosed in Patent Document 1 as an electric pump, rotor shafts that are supported in parallel with each other are synchronously rotated via a timing gear, and screw rotors fixed to the rotor shafts are mutually connected. By rotating in different directions, the fluid is sucked and discharged. In this fluid machine, an electric motor is connected to one end side of one rotor shaft, and the timing gear is disposed between the screw rotor and the electric motor. In the fluid machine, each of the pair of rotor shafts penetrates the screw rotor along the axial direction thereof.
JP 2002-54587 A

ところで、特許文献１に開示の流体機械をはじめ電動ポンプは軽量化が望まれている。特許文献１の流体機械において、スクリューロータ及びロータ軸をその軸方向への長さを短くすることで流体機械の体格を小さくし、軽量化を図ることは可能である。しかし、スクリューロータ及びロータ軸をその軸方向への長さを短くすることは、スクリューロータによる流体の移送量が低下してしまい、流体機械の性能が低下して好ましくない。   Incidentally, it is desired to reduce the weight of electric pumps including the fluid machine disclosed in Patent Document 1. In the fluid machine disclosed in Patent Document 1, it is possible to reduce the size of the fluid machine by reducing the length of the screw rotor and the rotor shaft in the axial direction, thereby reducing the weight. However, shortening the length of the screw rotor and the rotor shaft in the axial direction is not preferable because the amount of fluid transferred by the screw rotor is reduced and the performance of the fluid machine is lowered.

本発明は、体格を変えることなく軽量化を図ることができる電動ポンプを提供することにある。   An object of the present invention is to provide an electric pump that can be reduced in weight without changing its physique.

上記問題点を解決するために、請求項１に記載の発明は、電動モータによって駆動される第１の回転軸に第１のロータが一体回転可能に連結されるとともに、タイミングギアを介して前記第１の回転軸と同期回転される第２の回転軸に第２のロータが一体回転可能に連結され、各回転軸の軸方向において、前記電動モータと各ロータとの間に前記タイミングギアが配設された電動ポンプであって、各ロータが各回転軸を形成する材料よりも比重の小さい材料により形成されるとともに、各ロータにおいて、前記回転軸の軸方向における前記タイミングギア側の一方の端面に凹設された凹部に各回転軸のロータ側が圧入されることでロータと回転軸とが連結され、さらに、各ロータにおいて、前記回転軸の軸方向における他方の端面に、各回転軸を形成する材料よりも比重の小さい材料よりなるとともに各ロータに連結された回転軸と同軸に位置する軸部が突設され、該軸部が軸受により回転可能に支持されている。   In order to solve the above problems, the invention according to claim 1 is characterized in that a first rotor is connected to a first rotating shaft driven by an electric motor so as to be integrally rotatable, and the first rotor is connected via a timing gear. A second rotor is coupled to a second rotation shaft that is rotated synchronously with the first rotation shaft so as to be integrally rotatable, and the timing gear is provided between the electric motor and each rotor in the axial direction of each rotation shaft. Each rotor is formed of a material having a specific gravity smaller than the material forming each rotating shaft, and in each rotor, one of the rotors on the timing gear side in the axial direction of the rotating shaft. The rotor and the rotary shaft are connected by press-fitting the rotor side of each rotary shaft into the concave portion provided in the end face. Further, in each rotor, the other end face in the axial direction of the rotary shaft is rotated to the other end face. Shaft unit positioned coaxial with the axis of rotation which is connected to each rotor together made smaller specific gravity material than the material forming the projecting, the shaft portion is rotatably supported by bearings.

この構成によれば、各回転軸において、電動モータの駆動力は各ロータの凹部に圧入された部位を以て各回転軸から各ロータへ伝達される。そして、各回転軸から各ロータへの伝達トルクは、回転軸の軸方向において電動モータ（タイミングギア）に近い程大きく、電動モータ（タイミングギア）から遠ざかる程小さくなる。このため、電動モータ（タイミングギア）から最も遠くなるロータの他方の端面側に掛かる伝達トルクは僅かになる。よって、軸部を支持する軸受が受承する荷重は、前記僅かな伝達トルクとロータ（軸部）からのラジアル荷重となる。したがって、大きな伝達トルクが作用する回転軸の電動モータ（タイミングギア）側のような剛性を軸部に確保する必要が無く、該軸部を回転軸と同じ材料で形成する必要が無くなる。このため、軸部を回転軸を形成する材料より比重の小さい材料で形成することが可能となる。よって、各ロータの他方の端面に軸部を突設するため、各回転軸を各ロータを貫通させる必要が無くなり、回転軸の軸方向への長さを短くすることができる。そして、軸部を形成する材料は、回転軸を形成する材料より比重が小さいため、軸部を設けたとしてもロータの重量が嵩むことを抑えることができる。よって、回転軸を短くするだけで、ロータの体格を変えることなく重量を減らすことができ、電動ポンプの体格を変えることなく軽量化を図ることができる。   According to this configuration, in each rotating shaft, the driving force of the electric motor is transmitted from each rotating shaft to each rotor through a portion press-fitted into the recess of each rotor. And the transmission torque from each rotating shaft to each rotor becomes larger as it is closer to the electric motor (timing gear) in the axial direction of the rotating shaft, and becomes smaller as it is farther from the electric motor (timing gear). For this reason, the transmission torque applied to the other end face side of the rotor farthest from the electric motor (timing gear) is small. Therefore, the load received by the bearing that supports the shaft portion is the slight transmission torque and the radial load from the rotor (shaft portion). Therefore, it is not necessary to secure rigidity in the shaft portion as in the electric motor (timing gear) side of the rotating shaft on which a large transmission torque acts, and it is not necessary to form the shaft portion with the same material as the rotating shaft. For this reason, it becomes possible to form a shaft part with a material whose specific gravity is smaller than the material which forms a rotating shaft. Therefore, since the shaft portion projects from the other end face of each rotor, there is no need to penetrate each rotor shaft through each rotor, and the length of the rotation shaft in the axial direction can be shortened. And since the material which forms a shaft part has a specific gravity smaller than the material which forms a rotating shaft, even if it provides a shaft part, it can suppress that the weight of a rotor increases. Therefore, it is possible to reduce the weight without changing the physique of the rotor and to reduce the weight without changing the physique of the electric pump only by shortening the rotation shaft.

また、前記回転軸の軸方向に沿った前記凹部の深さは、該軸方向に沿ったロータの長さの半分より短くなっていてもよい。この構成によれば、凹部の深さが浅くなれば浅くなる程、言い換えると、凹部に圧入される回転軸の長さが短くなれば短くなるほど回転軸を形成する材料の使用量を減らすことができ、電動ポンプの軽量化に寄与することができる。   Further, the depth of the concave portion along the axial direction of the rotating shaft may be shorter than half the length of the rotor along the axial direction. According to this configuration, as the depth of the concave portion becomes shallower, in other words, as the length of the rotary shaft press-fitted into the concave portion becomes shorter, the use amount of the material forming the rotary shaft can be reduced. This can contribute to weight reduction of the electric pump.

また、前記軸部は前記ロータを形成する材料により形成されていてもよい。この構成によれば、軸部とロータとを同じ材料で形成することができ、例えば、軸部とロータとを別々の材料で形成する場合に比して、電動ポンプの製造コストを抑えることができる。   The shaft portion may be formed of a material that forms the rotor. According to this configuration, the shaft portion and the rotor can be formed of the same material. For example, the manufacturing cost of the electric pump can be reduced as compared with the case where the shaft portion and the rotor are formed of different materials. it can.

また、前記軸部はロータに一体成形されていてもよい。この構成によれば、各回転軸を各ロータを貫通させて軸部をロータに突設する場合に比して各軸部の偏心精度を向上させることができる。   The shaft portion may be integrally formed with the rotor. According to this configuration, the eccentric accuracy of each shaft portion can be improved as compared with the case where each rotor shaft passes through each rotor and the shaft portion projects from the rotor.

本発明によれば、体格を変えることなく軽量化を図ることができる。   According to the present invention, weight reduction can be achieved without changing the physique.

以下、本発明の電動ポンプを電動ルーツ式ポンプに具体化した一実施形態を図１〜図３にしたがって説明する。なお、以下の説明において、電動ルーツ式ポンプの「前」及び「後」は図１の前後方向に延びる矢印Ｙにおける前後に対応している。   Hereinafter, an embodiment in which the electric pump of the present invention is embodied as an electric roots type pump will be described with reference to FIGS. In the following description, “front” and “rear” of the electric roots pump correspond to the front and rear in the arrow Y extending in the front-rear direction of FIG.

図１に示すように、電動ルーツ式ポンプ１０のハウジングは、ロータハウジング１１と、該ロータハウジング１１の前端（先端）に接合固定された軸支部材１２と、該軸支部材１２の前端（先端）に接合固定されたモータハウジング１４とから形成されている。前記ロータハウジング１１と軸支部材１２との間にポンプ室１５が囲み形成されるとともに、軸支部材１２とモータハウジング１４との間にギア室１６が囲み形成されている。また、モータハウジング１４内にはモータ室１７が形成されるとともに、該モータ室１７には電動モータＭが収容されている。   As shown in FIG. 1, the housing of the electric roots pump 10 includes a rotor housing 11, a shaft support member 12 joined and fixed to the front end (tip) of the rotor housing 11, and a front end (tip) of the shaft support member 12. ) And a motor housing 14 bonded and fixed to each other. A pump chamber 15 is formed between the rotor housing 11 and the shaft support member 12, and a gear chamber 16 is formed between the shaft support member 12 and the motor housing 14. A motor chamber 17 is formed in the motor housing 14, and an electric motor M is accommodated in the motor chamber 17.

前記電動モータＭには、該電動モータＭによって駆動される第１の回転軸としての第１回転軸２０の前側（第１の端部側）が連結されるとともに、第１回転軸２０は前記ハウジングに回転可能に支持されている。なお、第１回転軸２０は鉄系材料よりなる。そして、第１回転軸２０は、電動モータＭを貫通した前端部たる第１端部２０ａが第１駆動側軸受３１によってモータハウジング１４に回転可能に支持されている。また、第１回転軸２０は、後端部たる第２端部２０ｂ側が第２駆動側軸受３２によって軸支部材１２に回転可能に支持されている。また、ハウジングには、前記第１回転軸２０と同期回転するとともに、第１回転軸２０対して平行をなす第２の回転軸たる第２回転軸２１が回転可能に支持されている。なお、第２回転軸２１は鉄系材料よりなる。そして、第２回転軸２１は、前端部たる第１端部２１ａ側が第１従動側軸受４１によって軸支部材１２に回転可能に支持されている。   The electric motor M is connected to the front side (first end side) of the first rotating shaft 20 as the first rotating shaft driven by the electric motor M, and the first rotating shaft 20 is The housing is rotatably supported. The first rotating shaft 20 is made of an iron-based material. The first rotating shaft 20 is rotatably supported on the motor housing 14 by a first drive side bearing 31 at a first end 20a that is a front end passing through the electric motor M. The first rotary shaft 20 is rotatably supported on the shaft support member 12 by a second drive side bearing 32 on the second end 20 b side as a rear end. In addition, the housing is rotatably supported by a second rotation shaft 21 that rotates in synchronization with the first rotation shaft 20 and is a second rotation shaft that is parallel to the first rotation shaft 20. The second rotating shaft 21 is made of an iron-based material. The second rotating shaft 21 is rotatably supported on the shaft support member 12 by a first driven side bearing 41 on the first end 21a side which is the front end.

第１回転軸２０において、前記ギア室１６内に位置する部位には第１ギア２８が固定され、第２回転軸２１において、ギア室１６内に位置する部位には第２ギア２９が固定されている。そして、ギア室１６内で第１ギア２８と第２ギア２９とは噛合連結され、タイミングギアＴを構成している。よって、第１回転軸２０と第２回転軸２１とはタイミングギアＴを介して連結され、該タイミングギアＴによって互いに異なる方向へ同期回転するようになっている。   A first gear 28 is fixed to a part of the first rotary shaft 20 located in the gear chamber 16, and a second gear 29 is fixed to a part of the second rotary shaft 21 located in the gear chamber 16. ing. In the gear chamber 16, the first gear 28 and the second gear 29 are meshingly connected to constitute a timing gear T. Therefore, the first rotating shaft 20 and the second rotating shaft 21 are connected via the timing gear T, and the timing gear T rotates synchronously in different directions.

前記ポンプ室１５内において、第１回転軸２０の第２端部２０ｂには、第１のロータとしてのアルミニウム製の第１ロータ２２が連結され、該第１ロータ２２は第１回転軸２０と一体回転可能になっている。また、第２回転軸２１の後端部たる第２端部２１ｂには、第２のロータとしてのアルミニウム製の第２ロータ２３が固定され、該第２ロータ２３は第２回転軸２１と一体回転可能になっている。なお、第１及び第２ロータ２２，２３を形成するアルミニウムは、第１及び第２回転軸２０，２１を形成する鉄系材料より比重が小さいものである。また、第１回転軸２０及び第２回転軸２１の軸方向において、前記第１ロータ２２及び第２ロータ２３と前記電動モータＭとの間に前記タイミングギアＴが配設されている。   In the pump chamber 15, a first rotor 22 made of aluminum as a first rotor is connected to the second end 20 b of the first rotating shaft 20, and the first rotor 22 is connected to the first rotating shaft 20. Integral rotation is possible. A second rotor 23 made of aluminum as a second rotor is fixed to the second end 21 b that is the rear end of the second rotary shaft 21, and the second rotor 23 is integrated with the second rotary shaft 21. It can be rotated. The aluminum forming the first and second rotors 22 and 23 has a lower specific gravity than the iron-based material forming the first and second rotating shafts 20 and 21. The timing gear T is disposed between the first rotor 22 and the second rotor 23 and the electric motor M in the axial direction of the first rotating shaft 20 and the second rotating shaft 21.

図２及び図３に示すように、各ロータ２２，２３は、各回転軸２０，２１の軸方向に直交する断面視が、双葉状（瓢箪状）に形成されたルーツ型のロータである。第１ロータ２２には、第１回転軸２０を挟んで相反する方向へ延びるように山歯２４が形成され、隣り合う山歯２４の間には谷歯２５が形成されている。また、第２ロータ２３には、第２回転軸２１を挟んで相反する方向へ延びるように山歯２６が形成され、隣り合う山歯２６の間には谷歯２７が形成されている。すなわち、第１ロータ２２及び第２ロータ２３は、２つ（複数）の山歯２４，２６を、第１回転軸２０及び第２回転軸２１の周方向へ等間隔をおいて有するとともに隣り合う山歯２４，２６の間に谷歯２５，２７を有する。   As shown in FIGS. 2 and 3, each of the rotors 22 and 23 is a Roots-type rotor in which a cross-sectional view orthogonal to the axial direction of each of the rotation shafts 20 and 21 is formed in a double leaf shape (saddle shape). On the first rotor 22, tooth teeth 24 are formed so as to extend in opposite directions across the first rotation shaft 20, and valley teeth 25 are formed between the adjacent tooth teeth 24. Further, the second rotor 23 is formed with angle teeth 26 extending in opposite directions with the second rotation shaft 21 in between, and valley teeth 27 are formed between the adjacent angle teeth 26. That is, the first rotor 22 and the second rotor 23 have two (plurality) chevron teeth 24 and 26 at equal intervals in the circumferential direction of the first rotary shaft 20 and the second rotary shaft 21 and are adjacent to each other. Valley teeth 25 and 27 are provided between the teeth 24 and 26.

上記構成の第１ロータ２２の山歯２４は第２ロータ２３の谷歯２７に僅かなクリアランスを保って係合するようになっており、第２ロータ２３の山歯２６は第１ロータ２２の谷歯２５に僅かなクリアランスを保って係合するようになっている。そして、ポンプ室１５内において、第１ロータ２２と第２ロータ２３とは、山歯２４と谷歯２７、及び谷歯２５と山歯２６とが僅かなクリアランスを保って互いに係合可能に収容されている。また、図３に示すように、ロータハウジング１１には、流体をポンプ室１５に吸引する吸入口１８と、該吸入口１８の対向位置にポンプ室１５で圧縮された流体を吐出する吐出口１９が形成されている。   The teeth 24 of the first rotor 22 configured as described above are engaged with the valley teeth 27 of the second rotor 23 with a slight clearance, and the teeth 26 of the second rotor 23 are engaged with the teeth of the first rotor 22. It engages with the valley teeth 25 with a slight clearance. In the pump chamber 15, the first rotor 22 and the second rotor 23 are housed so that the teeth 24 and the teeth 27 and the teeth 25 and the teeth 26 can be engaged with each other with a slight clearance. Has been. As shown in FIG. 3, the rotor housing 11 has a suction port 18 that sucks fluid into the pump chamber 15, and a discharge port 19 that discharges the fluid compressed in the pump chamber 15 to a position opposite to the suction port 18. Is formed.

このように構成された電動ルーツ式ポンプ１０では、電動モータＭの駆動力によって第１回転軸２０が回転することにより、第１ギア２８と第２ギア２９との噛合連結を通じて第２回転軸２１が第１回転軸２０とは異なる方向へ同期回転する。すると、ポンプ室１５内では、第１回転軸２０及び第２回転軸２１からの伝達トルクによって第１ロータ２２と第２ロータ２３が同期回転する。第１ロータ２２と第２ロータ２３の同期回転に伴い、流体が吸入口１８からポンプ室１５内へ吸入される。その後、第１ロータ２２と第２ロータ２３の外面と、ポンプ室１５の内面とが協働することにより、ポンプ室１５内に吸引された流体が吐出口１９へ向けて移送され、該吐出口１９からポンプ室１５外へ吐出される。   In the electric roots-type pump 10 configured as described above, the first rotary shaft 20 is rotated by the driving force of the electric motor M, so that the second rotary shaft 21 is engaged through the meshing connection between the first gear 28 and the second gear 29. Rotates synchronously in a direction different from that of the first rotating shaft 20. Then, in the pump chamber 15, the first rotor 22 and the second rotor 23 rotate synchronously by the transmission torque from the first rotating shaft 20 and the second rotating shaft 21. As the first rotor 22 and the second rotor 23 rotate synchronously, fluid is sucked into the pump chamber 15 from the suction port 18. Thereafter, the outer surfaces of the first rotor 22 and the second rotor 23 and the inner surface of the pump chamber 15 cooperate to transfer the fluid sucked into the pump chamber 15 toward the discharge port 19. 19 is discharged out of the pump chamber 15.

次に、第１回転軸２０と第１ロータ２２、及び第２回転軸２１と第２ロータ２３について詳細に説明する。なお、図１に示すように、第１ロータ２２において、第１回転軸２０の軸方向における前記タイミングギアＴ側の一方の端面を前端面２２ａとし、第１ロータ２２において、第１回転軸２０の軸方向における他方の端面を後端面２２ｂとする。また、第２ロータ２３において、第２回転軸２１の軸方向におけるタイミングギアＴ側の一方の端面を前端面２３ａとし、第２ロータ２３において、第２回転軸２１の軸方向における他方の端面を後端面２３ｂとする。   Next, the first rotating shaft 20 and the first rotor 22, and the second rotating shaft 21 and the second rotor 23 will be described in detail. As shown in FIG. 1, in the first rotor 22, one end face on the timing gear T side in the axial direction of the first rotating shaft 20 is a front end face 22 a, and in the first rotor 22, the first rotating shaft 20 The other end face in the axial direction is referred to as a rear end face 22b. Further, in the second rotor 23, one end surface on the timing gear T side in the axial direction of the second rotating shaft 21 is defined as a front end surface 23a, and in the second rotor 23, the other end surface in the axial direction of the second rotating shaft 21 is defined. The rear end face 23b is used.

さて、第１ロータ２２の前端面２２ａには、円穴状の凹部３５が凹設され、この凹部３５はその中心軸Ｍ１が第１回転軸２０の中心軸Ｌ１と同軸に位置するように形成されている。前記凹部３５において、第１回転軸２０の軸方向に沿った深さは、該軸方向に沿った第１ロータ２２の長さ（厚み）の半分より短くなっている。凹部３５には、第１回転軸２０の第２端部２０ｂが圧入固定され、第１回転軸２０に第１ロータ２２が一体回転可能に連結されている。そして、第２端部２０ｂの周面及び端面が凹部３５の周面及び内底面に圧接した圧入部により、第１回転軸２０の回転トルクが第１ロータ２２に伝達される。すなわち、第１回転軸２０からの伝達トルクによって第１ロータ２２が回転する。よって、第１回転軸２０は第１ロータ２２を中心軸Ｍ１に沿った軸方向へ貫通しておらず、貫通した場合に比して第１回転軸２０の軸方向への長さが短くなっている。   The front end surface 22a of the first rotor 22 is provided with a circular hole-shaped concave portion 35, and the concave portion 35 is formed so that the central axis M1 thereof is positioned coaxially with the central axis L1 of the first rotary shaft 20. Has been. In the recess 35, the depth along the axial direction of the first rotating shaft 20 is shorter than half the length (thickness) of the first rotor 22 along the axial direction. The second end 20b of the first rotating shaft 20 is press-fitted and fixed to the recess 35, and the first rotor 22 is connected to the first rotating shaft 20 so as to be integrally rotatable. Then, the rotational torque of the first rotating shaft 20 is transmitted to the first rotor 22 by the press-fitting portion in which the peripheral surface and the end surface of the second end portion 20 b are pressed against the peripheral surface and the inner bottom surface of the recess 35. That is, the first rotor 22 is rotated by the transmission torque from the first rotating shaft 20. Therefore, the first rotating shaft 20 does not penetrate the first rotor 22 in the axial direction along the central axis M1, and the length of the first rotating shaft 20 in the axial direction is shorter than that in the case where it penetrates. ing.

また、凹部３５の深さ、すなわち、凹部３５の深さに合致する第２端部２０ｂの軸方向への長さは、第１回転軸２０（第２端部２０ｂ）を形成する鉄系材料の強度以下の圧入でありながら、前記伝達トルクを第２端部２０ｂから第１ロータ２２に伝達可能とする長さに設定されている。そして、凹部３５の深さ、及び凹部３５への第２端部２０ｂ（圧入部位）の軸方向に沿った長さは、第２端部２０ｂから第１ロータ２２への伝達トルクに安全率を乗じた値と、凹部３５と第２端部２０ｂとの圧入部における締結力とが等しくなる深さ、及び長さに設定されている。このため、第２端部２０ｂの軸方向への長さ（凹部３５の深さ）は、第１回転軸２０が第１ロータ２２を軸方向へ貫通している状態で、伝達トルクを第２端部２０ｂによって伝達可能とするとともに、第２端部２０ｂが凹部３５内で空周りしないような値に設定されている。   Further, the depth of the recess 35, that is, the length in the axial direction of the second end 20 b that matches the depth of the recess 35 is an iron-based material that forms the first rotating shaft 20 (second end 20 b). The transmission torque is set to a length that allows the transmission torque to be transmitted from the second end portion 20b to the first rotor 22 while the press fit is less than the above-described strength. The depth of the concave portion 35 and the length along the axial direction of the second end portion 20b (press-fit portion) to the concave portion 35 give a safety factor to the torque transmitted from the second end portion 20b to the first rotor 22. The depth and length are set such that the multiplied value is equal to the fastening force at the press-fitting portion between the concave portion 35 and the second end portion 20b. For this reason, the length of the second end portion 20b in the axial direction (the depth of the concave portion 35) is set so that the transmission torque is equal to the second torque when the first rotating shaft 20 penetrates the first rotor 22 in the axial direction. The value is set such that transmission is possible by the end portion 20 b and the second end portion 20 b does not idle in the recess 35.

一方、第２ロータ２３の前端面２３ａには、円穴状の凹部３６が凹設され、この凹部３６はその中心軸Ｍ２が第２回転軸２１の中心軸Ｌ２と同軸に位置するように形成されている。前記凹部３６において、第２回転軸２１の軸方向に沿った深さは、該軸方向に沿った第２ロータ２３の長さ（厚み）の半分より短くなっている。凹部３６には、第２回転軸２１の第２端部２１ｂが圧入固定され、第２回転軸２１に第２ロータ２３が一体回転可能に連結されている。そして、第２端部２１ｂの周面及び端面が凹部３６の周面及び内底面に圧接した圧入部により、第２回転軸２１の回転トルクが第２ロータ２３に伝達される。すなわち、第２回転軸２１からの伝達トルクによって第２ロータ２３が回転する。よって、第２回転軸２１は第２ロータ２３を中心軸Ｍ２に沿った軸方向へ貫通しておらず、貫通した場合に比して第２回転軸２１の軸方向への長さが短くなっている。   On the other hand, a circular hole-shaped recess 36 is formed in the front end surface 23 a of the second rotor 23, and the recess 36 is formed such that the central axis M 2 is positioned coaxially with the central axis L 2 of the second rotating shaft 21. Has been. In the concave portion 36, the depth along the axial direction of the second rotating shaft 21 is shorter than half the length (thickness) of the second rotor 23 along the axial direction. The second end 21b of the second rotating shaft 21 is press-fitted and fixed to the recess 36, and the second rotor 23 is connected to the second rotating shaft 21 so as to be integrally rotatable. Then, the rotational torque of the second rotating shaft 21 is transmitted to the second rotor 23 by the press-fitting portion in which the peripheral surface and the end surface of the second end portion 21 b are pressed against the peripheral surface and the inner bottom surface of the recess 36. That is, the second rotor 23 is rotated by the transmission torque from the second rotating shaft 21. Therefore, the second rotating shaft 21 does not penetrate the second rotor 23 in the axial direction along the central axis M2, and the length of the second rotating shaft 21 in the axial direction is shorter than when penetrating. ing.

また、凹部３６の深さに合致する第２端部２１ｂの軸方向への長さは、第２回転軸２１（第２端部２１ｂ）を形成する鉄系材料の強度以下の圧入でありながら、伝達トルクを第２端部２１ｂから第２ロータ２３に伝達可能とする長さに設定されている。そして、凹部３６の深さ、及び凹部３６への第２端部２１ｂ（圧入部位）の軸方向に沿った長さは、第２端部２１ｂから第２ロータ２３への伝達トルクに安全率を乗じた値と、凹部３６と第２端部２１ｂとの圧入部における締結力とが等しくなる深さ、及び長さに設定されている。このため、第２端部２１ｂの軸方向への長さ（凹部３６の深さ）は、第２回転軸２１が第２ロータ２３を軸方向へ貫通している状態で、伝達トルクを第２端部２１ｂによって伝達可能とするとともに、第２端部２１ｂが凹部３６内で空周りしないような値に設定されている。   In addition, the length in the axial direction of the second end portion 21b that matches the depth of the recess 36 is a press fit that is equal to or less than the strength of the iron-based material forming the second rotating shaft 21 (second end portion 21b). The transmission torque is set to a length that allows transmission torque to be transmitted from the second end portion 21b to the second rotor 23. The depth of the concave portion 36 and the length along the axial direction of the second end portion 21b (press-fit portion) to the concave portion 36 give a safety factor to the torque transmitted from the second end portion 21b to the second rotor 23. The depth and length are set such that the multiplied value is equal to the fastening force at the press-fitting portion between the recess 36 and the second end 21b. For this reason, the length of the second end portion 21b in the axial direction (depth of the concave portion 36) is such that the second rotating shaft 21 penetrates the second rotor 23 in the axial direction and the transmission torque is the second. The value is set such that transmission is possible by the end portion 21 b and the second end portion 21 b does not idle in the recess 36.

一方、第１ロータ２２の後端面２２ｂには円柱状の軸部３７が突設され、この軸部３７はその中心軸Ｎ１が第１回転軸２０の中心軸Ｌ１及び凹部３５の中心軸Ｍ１と同軸に位置するように形成されている。軸部３７は第１ロータ２２を型を用いて成形する際に該第１ロータ２２に一体成形されるため、アルミニウムによって形成されている。そして、軸部３７は、第３駆動側軸受３３によってロータハウジング１１に回転可能に支持され、第３駆動側軸受３３は第１ロータ２２のラジアル荷重及び僅かな伝達トルクを受承している。よって、第１ロータ２２は、前端面２２ａ側が第２駆動側軸受３２によって支持され、後端面２２ｂ側が第３駆動側軸受３３によって支持され、両持ち支持状態となっている。   On the other hand, a cylindrical shaft portion 37 protrudes from the rear end surface 22b of the first rotor 22. The shaft portion 37 has a central axis N1 that is a central axis L1 of the first rotating shaft 20 and a central axis M1 of the recess 35. It is formed so as to be located on the same axis. Since the shaft portion 37 is integrally formed with the first rotor 22 when the first rotor 22 is formed using a mold, the shaft portion 37 is formed of aluminum. The shaft portion 37 is rotatably supported by the rotor housing 11 by the third drive side bearing 33, and the third drive side bearing 33 receives the radial load and a slight transmission torque of the first rotor 22. Therefore, the first rotor 22 is supported at the front end surface 22a side by the second drive side bearing 32, and the rear end surface 22b side is supported by the third drive side bearing 33, and is in a both-end supported state.

第２ロータ２３の後端面２３ｂには円柱状の軸部３８が突設され、この軸部３８はその中心軸Ｎ２が第２回転軸２１の中心軸Ｌ２及び凹部３６の中心軸Ｍ２と同軸に位置するように形成されている。この軸部３８は第２ロータ２３を型を用いて成形する際に該第２ロータ２３に一体成形されるため、アルミニウムによって形成されている。そして、軸部３８は、第２従動側軸受４２によってロータハウジング１１に回転可能に支持され、第２従動側軸受４２は第２ロータ２３のラジアル荷重及び僅かな伝達トルクを受承している。よって、第２ロータ２３は前端面２３ａ側が第１従動側軸受４１によって支持され、後端面２３ｂ側が第２従動側軸受４２によって支持され、両持ち支持状態となっている。   A cylindrical shaft portion 38 protrudes from the rear end surface 23b of the second rotor 23. The shaft portion 38 has a central axis N2 coaxial with the central axis L2 of the second rotating shaft 21 and the central axis M2 of the recess 36. It is formed to be located. The shaft portion 38 is formed of aluminum because it is integrally formed with the second rotor 23 when the second rotor 23 is formed using a mold. The shaft portion 38 is rotatably supported by the rotor housing 11 by a second driven side bearing 42, and the second driven side bearing 42 receives the radial load and a slight transmission torque of the second rotor 23. Therefore, the front end surface 23a side of the second rotor 23 is supported by the first driven side bearing 41, and the rear end surface 23b side is supported by the second driven side bearing 42.

上記実施形態によれば、以下のような効果を得ることができる。
（１）各回転軸２０，２１は、それぞれ連結された各ロータ２２，２３を軸方向へ貫通しておらず、貫通する場合に比して軸方向への長さが短くなっている。また、軸部３７，３８は各ロータ２２，２３と同じ材料（アルミニウム）で形成されている。このため、各ロータ２２，２３に各回転軸２０，２１を貫通させて軸部３７，３８を突設する場合に比して、各ロータ２２，２３の体格を同じとしながらも軽量化を図ることができる。その結果として、電動ルーツ式ポンプ１０の体格を変えることなく、該電動ルーツ式ポンプ１０の軽量化を図ることができる。 According to the above embodiment, the following effects can be obtained.
(1) The rotating shafts 20 and 21 do not penetrate the connected rotors 22 and 23 in the axial direction, respectively, and the length in the axial direction is shorter than when they penetrate. The shaft portions 37 and 38 are made of the same material (aluminum) as the rotors 22 and 23. For this reason, compared with the case where each rotary shaft 20 and 21 is penetrated to each rotor 22 and 23 and the shaft parts 37 and 38 project, the weight of each rotor 22 and 23 is made the same. be able to. As a result, the weight of the electric roots pump 10 can be reduced without changing the physique of the electric roots pump 10.

（２）各軸部３７，３８は各ロータ２２，２３の成形時に一体成形される。このため、各ロータ２２，２３に各回転軸２０，２１を貫通させて軸部３７，３８を突設する場合に比して、各ロータ２２，２３に対する軸部３７，３８の偏心精度を向上させることができ、該偏心に起因した各回転軸２０，２１の振動を低減させることができる。   (2) The shaft portions 37 and 38 are integrally formed when the rotors 22 and 23 are formed. For this reason, the eccentric accuracy of the shaft portions 37 and 38 with respect to the rotors 22 and 23 is improved as compared with the case where the shaft portions 37 and 38 protrude from the rotors 22 and 23 through the rotary shafts 20 and 21. The vibrations of the rotary shafts 20 and 21 due to the eccentricity can be reduced.

（３）また、各軸部３７，３８と各ロータ２２，２３がアルミニウムによって同時に成形される。このため、軸部３７，３８とロータ２２，２３とが異なる材料で別々に製造され、さらに、それらを一体化して各ロータ２２，２３に軸部３７，３８を設ける場合に比して、電動ルーツ式ポンプ１０の製造コストを抑え、さらに、生産性を向上させることができる。   (3) Moreover, each shaft part 37 and 38 and each rotor 22 and 23 are shape | molded simultaneously with aluminum. For this reason, the shaft portions 37 and 38 and the rotors 22 and 23 are manufactured separately from different materials, and are further integrated with each other to provide the shaft portions 37 and 38 on the rotors 22 and 23. The manufacturing cost of the Roots pump 10 can be reduced, and the productivity can be improved.

（４）各凹部３５，３６の深さ及び該凹部３５，３６に圧入される各第２端部２０ｂ，２１ｂの長さは、各回転軸２０，２１の軸方向に沿ったロータ２２，２３の長さ（厚み）の半分以下となっている。そして、各第２端部２０ｂ，２１ｂの長さが短くなればなるほど鉄系材料を減らすことができ、電動ルーツ式ポンプ１０の軽量化に寄与することができる。   (4) The depth of each recess 35, 36 and the length of each second end 20b, 21b press-fitted into the recess 35, 36 are the rotors 22, 23 along the axial direction of each rotary shaft 20, 21. It is less than half of the length (thickness). And, as the length of each of the second end portions 20b and 21b becomes shorter, the iron-based material can be reduced, and the electric roots pump 10 can be reduced in weight.

（５）各ロータ２２，２３の成形と同時に、各凹部３５，３６及び各軸部３７，３８が形成される。このため、各回転軸２０，２１を各ロータ２２，２３に貫通させて連結する場合のように、該ロータ２２，２３を軸方向に貫通する貫通孔を加工する必要が無くなる。よって、各ロータ２２，２３の加工時間を短縮することができ、結果として電動ルーツ式ポンプ１０の生産性を向上させることができる。   (5) Simultaneously with the molding of the rotors 22 and 23, the concave portions 35 and 36 and the shaft portions 37 and 38 are formed. For this reason, it is not necessary to process a through-hole penetrating the rotors 22 and 23 in the axial direction as in the case where the rotary shafts 20 and 21 are connected to the rotors 22 and 23. Therefore, the processing time of each rotor 22 and 23 can be shortened, and as a result, the productivity of the electric roots type pump 10 can be improved.

なお、上記実施形態は以下のように変更してもよい。
○ 実施形態において、凹部３５，３６の深さ、及び凹部３５，３６に圧入される第２端部２０ｂ，２１ｂの長さは任意に変更してもよい。 In addition, you may change the said embodiment as follows.
In the embodiment, the depths of the recesses 35 and 36 and the lengths of the second end portions 20b and 21b press-fitted into the recesses 35 and 36 may be arbitrarily changed.

○ 各ロータ２２，２３と同じ材料（アルミニウム）よりなる軸部３７，３８を、各ロータ２２，２３とは別体形成し、該軸部３７，３８を各ロータ２２，２３に圧入等によって一体に設けてもよい。   ○ Shaft portions 37 and 38 made of the same material (aluminum) as the rotors 22 and 23 are formed separately from the rotors 22 and 23, and the shaft portions 37 and 38 are integrated into the rotors 22 and 23 by press fitting or the like. May be provided.

○ 軸部３７，３８を各回転軸２０，２１より比重の小さい材料（例えば、チタン、合成樹脂）によって形成し、その軸部３７，３８を各ロータ２２，２３に圧入等によって一体に設けてもよい。   ○ Shaft portions 37 and 38 are formed of a material having a specific gravity smaller than that of each rotary shaft 20 or 21 (for example, titanium or synthetic resin), and the shaft portions 37 and 38 are integrally provided in the rotors 22 and 23 by press fitting or the like. Also good.

○ 実施形態において、第１ロータ２２及び第２ロータ２３を合成樹脂材料により形成し、第１回転軸２０及び第２回転軸２１を合成樹脂材料より比重の大きい金属材料（例えば、鉄系材料）により形成してもよい。   In the embodiment, the first rotor 22 and the second rotor 23 are formed of a synthetic resin material, and the first rotating shaft 20 and the second rotating shaft 21 are metal materials (for example, iron-based materials) having a specific gravity greater than that of the synthetic resin material. May be formed.

○ 実施形態において、例えば、三葉型といった複数葉型の第１ロータ２２及び第２ロータ２３を用いた電動ルーツ式ポンプ１０としてもよい。
○ 実施形態では、第１及び第２のロータをルーツ型に具体化した電動ルーツ式ポンプとしたが、第１及び第２のロータを、スクリュー型に具体化した電動スクリュー式ポンプとしてもよい。 In embodiment, it is good also as the electric roots type pump 10 using the 1st rotor 22 and the 2nd rotor 23 of multiple leaf type, such as a trilobal type, for example.
In the embodiment, the first and second rotors are electric root pumps embodied in a root type, but the first and second rotors may be electric screw pumps embodied in a screw type.

次に、上記実施形態及び別例から把握できる技術的思想について以下に追記する。
（１）前記回転軸における前記凹部への圧入部位の軸方向に沿った長さは、該圧入部位からロータへの伝達トルクに安全率を乗じた値と、凹部と圧入部位における締結力とが等しくなる長さに設定されている請求項１〜請求項４のうちいずれか一項に記載の電動ポンプ。 Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(1) The length along the axial direction of the press-fitted portion into the concave portion on the rotating shaft is determined by the value obtained by multiplying the torque transmitted from the press-fitted portion to the rotor by the safety factor and the fastening force at the concave portion and the press-fitted portion. The electric pump according to any one of claims 1 to 4, wherein the electric pump is set to an equal length.

実施形態の電動ルーツ式ポンプを示す平断面図。The plane sectional view showing the electric roots type pump of an embodiment. 図１の２−２線断面図。FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. 図１の３−３線断面図。FIG. 3 is a sectional view taken along line 3-3 in FIG. 1.

符号の説明Explanation of symbols

Ｍ…電動モータ、Ｔ…タイミングギア、２０…第１の回転軸としての第１回転軸、２１…第２の回転軸としての第２回転軸、２２…第１のロータとしての第１ロータ、２２ａ，２３ａ…一方の端面としての前端面、２２ｂ，２３ｂ…他方の端面としての後端面、２３…第２のロータとしての第２ロータ、３５，３６…凹部、３７，３８…軸部、３３…第３駆動側軸受、４２…第２従動側軸受。   M ... electric motor, T ... timing gear, 20 ... first rotating shaft as a first rotating shaft, 21 ... second rotating shaft as a second rotating shaft, 22 ... first rotor as a first rotor, 22a, 23a ... front end face as one end face, 22b, 23b ... rear end face as the other end face, 23 ... second rotor as the second rotor, 35, 36 ... recess, 37, 38 ... shaft part, 33 ... 3rd drive side bearing, 42 ... 2nd driven side bearing.

Claims (4)

電動モータによって駆動される第１の回転軸に第１のロータが一体回転可能に連結されるとともに、タイミングギアを介して前記第１の回転軸と同期回転される第２の回転軸に第２のロータが一体回転可能に連結され、各回転軸の軸方向において、前記電動モータと各ロータとの間に前記タイミングギアが配設された電動ポンプであって、
各ロータが各回転軸を形成する材料よりも比重の小さい材料により形成されるとともに、各ロータにおいて、前記回転軸の軸方向における前記タイミングギア側の一方の端面に凹設された凹部に各回転軸のロータ側が圧入されることでロータと回転軸とが連結され、さらに、各ロータにおいて、前記回転軸の軸方向における他方の端面に、各回転軸を形成する材料よりも比重の小さい材料よりなるとともに各ロータに連結された回転軸と同軸に位置する軸部が突設され、該軸部が軸受により回転可能に支持されている電動ポンプ。 A first rotor is coupled to a first rotating shaft driven by an electric motor so as to be integrally rotatable, and a second rotating shaft is rotated in synchronization with the first rotating shaft via a timing gear. Each of the rotors is connected so as to be integrally rotatable, and in the axial direction of each rotating shaft, the timing gear is disposed between the electric motor and each rotor,
Each rotor is formed of a material having a specific gravity smaller than that of the material forming each rotating shaft, and each rotor rotates in a recess formed in one end surface on the timing gear side in the axial direction of the rotating shaft. The rotor and the rotary shaft are connected by press-fitting the rotor side of the shaft. Further, in each rotor, the other end surface in the axial direction of the rotary shaft is made of a material having a specific gravity smaller than that of the material forming each rotary shaft. An electric pump in which a shaft portion that is coaxial with a rotation shaft connected to each rotor is projected and the shaft portion is rotatably supported by a bearing. 前記回転軸の軸方向に沿った前記凹部の深さは、該軸方向に沿ったロータの長さの半分より短くなっている請求項１に記載の電動ポンプ。 The electric pump according to claim 1, wherein the depth of the concave portion along the axial direction of the rotation shaft is shorter than half of the length of the rotor along the axial direction. 前記軸部は前記ロータを形成する材料により形成される請求項１又は請求項２に記載の電動ポンプ。 The electric pump according to claim 1, wherein the shaft portion is formed of a material forming the rotor. 前記軸部はロータに一体成形されている請求項３に記載の電動ポンプ。 The electric pump according to claim 3, wherein the shaft portion is integrally formed with the rotor.
JP2006299057A 2006-11-02 2006-11-02 Electric pump Expired - Fee Related JP4784484B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2006299057A JP4784484B2 (en) 2006-11-02 2006-11-02 Electric pump
DE102007052275A DE102007052275A1 (en) 2006-11-02 2007-11-02 Electric pump
US11/934,290 US20080107550A1 (en) 2006-11-02 2007-11-02 Eletric pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006299057A JP4784484B2 (en) 2006-11-02 2006-11-02 Electric pump

Publications (2)

Publication Number Publication Date
JP2008115748A JP2008115748A (en) 2008-05-22
JP4784484B2 true JP4784484B2 (en) 2011-10-05

Family

ID=39265178

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2006299057A Expired - Fee Related JP4784484B2 (en) 2006-11-02 2006-11-02 Electric pump

Country Status (3)

Country Link
US (1) US20080107550A1 (en)
JP (1) JP4784484B2 (en)
DE (1) DE102007052275A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3308001A4 (en) * 2015-06-11 2019-03-13 Eaton Corporation Supercharger having rotor with press-fit stub shafts
DE102019100404B4 (en) * 2018-01-22 2023-06-22 Kabushiki Kaisha Toyota Jidoshokki Motor-driven Roots pump
US11174858B2 (en) * 2018-01-26 2021-11-16 Waterblasting, Llc Pump for melted thermoplastic materials
US11668304B2 (en) 2020-02-27 2023-06-06 Gardner Denver, Inc. Low coefficient of expansion rotors for vacuum boosters
US11746782B2 (en) * 2020-04-03 2023-09-05 Gardner Denver, Inc. Low coefficient of expansion rotors for blowers

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2014932A (en) * 1933-03-17 1935-09-17 Gen Motors Corp Roots blower
US3644071A (en) * 1970-11-18 1972-02-22 Us Navy Pump fluid motor with pressurized bearing lubrication system
FR2530742B1 (en) * 1982-07-22 1987-06-26 Dba VOLUMETRIC SCREW COMPRESSOR
US4504203A (en) * 1983-01-18 1985-03-12 Delta Screw Nederland B.V. Apparatus adapted for use as a screw compressor for motor
US4595349A (en) * 1983-06-20 1986-06-17 Eaton Corp. Supercharger rotor, shaft, and gear arrangement
US4797078A (en) * 1986-06-11 1989-01-10 Wankel Gmbh Bearing arrangement of an external-axial rotary piston blower
DE3775553D1 (en) * 1987-05-15 1992-02-06 Leybold Ag TWO SHAFT PUMP.
EP0666422B1 (en) * 1994-02-05 1997-10-22 MAN Gutehoffnungshütte Aktiengesellschaft Bearings and drive connection for the rotors of a screw compressor
SE9603878L (en) * 1996-10-22 1997-08-11 Lysholm Techn Ab Shaft pin for light metal rotor
JP3941452B2 (en) * 2001-10-17 2007-07-04 株式会社豊田自動織機 Operation stop control method and operation stop control device for vacuum pump
US6969242B2 (en) * 2003-02-28 2005-11-29 Carrier Corpoation Compressor
JP2006125251A (en) * 2004-10-27 2006-05-18 Toyota Industries Corp Roots-type compressor

Also Published As

Publication number Publication date
US20080107550A1 (en) 2008-05-08
DE102007052275A1 (en) 2008-05-08
JP2008115748A (en) 2008-05-22

Similar Documents

Publication Publication Date Title
JP4784484B2 (en) Electric pump
JP5622033B2 (en) Fluid pump
JPH05256268A (en) Gear-type machine
JP2008196390A (en) Variable volume fluid machine
JP2006161616A (en) Tandem type trochoid pump and method of assembling same
CN105143673A (en) Trochoid pump for transferring high-viscosity liquid under high pressure
KR20160144948A (en) Gerotor Pump with double rotor assembly
TWI579474B (en) Eccentric rocking gear device
JP4215160B2 (en) Internal gear pump and manufacturing method thereof
JP2011032892A (en) Trochoid type rotary pump
JP2008115747A (en) Electric pump
KR101943674B1 (en) Oil pump rotor
JP2007218128A (en) Gear pump
JP6664316B2 (en) Trochoid pump
JP6642061B2 (en) Motor with reduction mechanism and power seat device
JP2016200127A5 (en)
WO2013132748A1 (en) Eccentric oscillation-type gear device
KR101044590B1 (en) Oil pump rotor
JP6836922B2 (en) Oil pump
JP5465248B2 (en) Gear pump
JP6745132B2 (en) Compound pump
JP6661529B2 (en) Trochoid pump
JP5257342B2 (en) Rotary pump
JP6187127B2 (en) Internal gear pump
JP4920971B2 (en) Tandem trochoid pump

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20090908

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20110609

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20110614

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20110627

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140722

Year of fee payment: 3

LAPS Cancellation because of no payment of annual fees