JPS6343594B2 - - Google Patents
Info
- Publication number
- JPS6343594B2 JPS6343594B2 JP58117196A JP11719683A JPS6343594B2 JP S6343594 B2 JPS6343594 B2 JP S6343594B2 JP 58117196 A JP58117196 A JP 58117196A JP 11719683 A JP11719683 A JP 11719683A JP S6343594 B2 JPS6343594 B2 JP S6343594B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- motors
- motor
- output
- rotation speed
- 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
Links
- 239000012530 fluid Substances 0.000 description 4
- 238000005452 bending Methods 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/008—Prime movers
-
- 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
- F04C2/18—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 with similar tooth forms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
- F04C2240/402—Plurality of electronically synchronised motors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
【発明の詳細な説明】
本発明は歯車ポンプに関する。このポンプはケ
ーシングを有し、ケーシングの中では２つの歯車
が互いに噛合いながら支承されている。またこの
歯車ポンプは、歯車用の駆動装置をも有してい
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gear pump. This pump has a casing in which two gear wheels are mounted in mesh with each other. The gear pump also has a drive for the gear.
公知の歯車ポンプでは、歯車の１つが駆動モー
タと結合され、この歯車と噛合つた他の歯車に必
要な駆動力が伝達される。この歯車には、伝達さ
れるトルクと流体の圧力とによつて、曲げ荷重が
負荷される。従つてこの歯車の歯は、大きな曲げ
荷重にさらされる。また、互いに噛合つている両
歯車の歯面には、伝達トルクにより発生する周期
的押圧力と直線荷重、および流体の圧力により生
じる表面圧力と直線荷重が加えられる。これらの
荷重により、差圧と流体の粘度とか大きい場合に
は、全歯丈を相応に小さくしなければならない。
このため、所定の送出し効率を得るためには、歯
車の厚さおよび／または直径を大きくしなければ
ならず、そのため歯車のかさが相当に大きくな
る。さらに、歯車１回転当りの送出し流量に比べ
てケーシングの内部空間が非常に大きく、従つて
それに応じてケーシングの全容積も大きくしなけ
ればならない。その上に、摩擦力が増大するので
ポンプの効率が低下する。従つて、公知の歯車ポ
ンプで達成できる送出し効率および送出し圧力に
は限界があり、それを越えようとすると動作に支
障が生じた。 In known gear pumps, one of the gears is connected to a drive motor, which transmits the necessary driving force to the other gears meshing with this gear. A bending load is applied to this gear due to the transmitted torque and the pressure of the fluid. The teeth of this gear are therefore exposed to large bending loads. Furthermore, periodic pressing force and linear load generated by transmitted torque, and surface pressure and linear load generated by fluid pressure are applied to the tooth surfaces of both gears that mesh with each other. Due to these loads, if the differential pressure and fluid viscosity are large, the total tooth height must be reduced accordingly.
Therefore, in order to obtain a given delivery efficiency, the thickness and/or diameter of the gear must be increased, which increases the bulk of the gear considerably. Furthermore, the internal space of the casing is very large compared to the delivery flow rate per revolution of the gear, and the total volume of the casing must therefore be correspondingly large. Additionally, the efficiency of the pump decreases due to increased frictional forces. Therefore, there are limits to the delivery efficiency and delivery pressure that can be achieved with known gear pumps, and attempts to exceed these limits result in operational problems.
発明の目的
本発明の課題は、冒頭に述べた歯車ポンプを次
のよう改良することである。つまりこの歯車ポン
プは、与えられた規格の歯車において有効寿命を
縮めずに、送出し効率および／または送出し圧力
を公知の歯車ポンプよりも大きくできなければな
らない。Object of the invention The object of the invention is to improve the gear pump mentioned at the beginning as follows. This means that the gear pump must be able to have a higher delivery efficiency and/or delivery pressure than known gear pumps without reducing the useful life for a given specification gear.
発明の構成と効果
本発明によればこの課題は、各歯車にそれぞれ
専用のモータを配属することにより解決される。Structure and Effects of the Invention According to the present invention, this problem is solved by assigning a dedicated motor to each gear.
また本発明によれば、各歯車に配属された２つ
のモータは共通の制御装置によつて制御される。
この制御装置の第１の入力側には、２つのモータ
の出力比を決定する入力信号が加わる。また２つ
のモータの各々に回転数設定値発信器が配属さ
れ、一方のモータに配属された回転数設定値発信
器の入力側に、外部から入力される回転数設定値
が加わり、他方のモータに配属された回転数設定
値発信器の入力側には制御装置の出力が加わる。
さらに、２つの回転数設定値発信器の出力側がそ
れぞれ出力増幅器と接続され、該出力増幅器が電
源測定器を介して２つのモータに駆動電流を供給
する。そして、電流測定器の出力側が、それぞれ
制御装置の第２または第３の出力側と接続されて
いる。 Further, according to the present invention, the two motors assigned to each gear are controlled by a common control device.
At a first input of this control device, an input signal is applied which determines the output ratio of the two motors. In addition, a rotation speed set value transmitter is assigned to each of the two motors, and the rotation speed set value input from the outside is added to the input side of the rotation speed set value transmitter assigned to one motor, and The output of the control device is applied to the input side of the rotational speed setpoint transmitter assigned to .
Furthermore, the output sides of the two rotational speed setpoint transmitters are each connected to an output amplifier, which supplies drive current to the two motors via a power supply measuring device. The output side of the current measuring device is then connected to the second or third output side of the control device, respectively.
本発明によれば、２つの歯車のどちらにも、そ
の歯みぞ内の流体を吸入口から吐出口まで移送す
るのに必要な駆動力を与えるだけでよい。たとえ
２つの歯車間で力の伝達があつても、それは両モ
ータ間の電力消費量の差に相当する小さなものに
限られる。従つて本発明の歯車ポンプによれば、
従来のものより大きな送出し効率ないし送出し圧
力が得られる。 According to the invention, it is only necessary to provide both of the two gears with the driving force necessary to transfer the fluid in their tooth spaces from the suction port to the discharge port. Even if there is a transmission of force between the two gears, it is limited to a small amount corresponding to the difference in power consumption between the two motors. Therefore, according to the gear pump of the present invention,
A greater delivery efficiency or delivery pressure than before can be achieved.
モータの出力差がごくわずかで、補償用の歯車
がこの差出力をもう１つの歯車に伝達できるよう
にすると有利である。そうすれば、両歯車の歯車
がいつも所定通りに接触するようになる。 It is advantageous if the difference in the output of the motors is negligible and the compensating gear is able to transmit this differential output to the other gear. By doing so, the gears of both gears will always come into contact as specified.
しかしまた、所定の微小出力差の範囲内で、あ
る時には１つの歯車、別の時には別の歯車を駆動
歯車とし、それにより両歯車の全歯面を均一に接
触させることもできる。 However, within a predetermined minute output difference range, it is also possible to use one gear at some times and another gear at other times as the drive gear, thereby bringing all tooth surfaces of both gears into uniform contact.
また、２つのモータは直流モータとするのが有
利である。 It is also advantageous for the two motors to be direct current motors.
本発明の歯車ポンプでも、公知のものと同じよ
うに、モータは歯車と同軸的に連結され、ケーシ
ングの一端面に取付けられる。この場合、もう１
つのモータも他の歯車と同軸的に連結され、ケー
シングの他の端面に取付けられると有利である。 In the gear pump of the present invention as well, the motor is coaxially connected to the gear and attached to one end surface of the casing, as in the known gear pump. In this case, one more
Advantageously, the two motors are also coaxially connected to the other gears and mounted on the other end face of the casing.
この場合２つのモータは、連結部材を囲繞する
中間支持部材を介してケーシングにフランジ付け
される。 In this case, the two motors are flanged to the casing via an intermediate support element that surrounds the coupling element.
実施例の説明
次に図面を参照しながら本発明の実施例につい
て詳しく説明する。DESCRIPTION OF EMBODIMENTS Next, embodiments of the present invention will be described in detail with reference to the drawings.
第１図は、本発明による歯車ポンプの軸方向の
縦断面図であり、第２図は第１図の―線に沿
つた横断面図である。 FIG. 1 is a vertical cross-sectional view in the axial direction of a gear pump according to the present invention, and FIG. 2 is a cross-sectional view taken along the line -- in FIG.
歯車ポンプはケーシング１０を有し、それには
吸入口１２と吐出口１４とが設けられている。ケ
ーシング１０は、上部軸２０のための一対の上部
軸受ブツシユ１６と、下部軸２２のための下部軸
受ブツシユ１８を有している。軸２０，２２は互
いに平行であり、この実施例では上下に並んで配
置されている。軸２０には歯車２４が支持され、
それは軸受ブツシユ１６の間に配置されている。
同じく軸２２には歯車２６が支持され、軸受ブツ
シユ１８間に位置している。２つの歯車は、それ
ぞれの軸と一体に形成されているか、あるいはそ
れに取付けられている。 The gear pump has a casing 10, which is provided with an inlet 12 and an outlet 14. The casing 10 has a pair of upper bearing bushes 16 for the upper shaft 20 and a lower bearing bush 18 for the lower shaft 22. The axes 20, 22 are parallel to each other and are arranged one above the other in this embodiment. A gear 24 is supported on the shaft 20,
It is arranged between the bearing bushes 16.
A gear 26 is also supported on the shaft 22 and is located between the bearing bushes 18. The two gears are integrally formed with or attached to the respective shafts.
ケーシングは、対向する２つの端面を有し、そ
れには側壁部材２８ないし３０が取付けられてい
る。上部軸２０は、第１図で右側にある側壁部材
２８を突抜けて延在し、下部軸２２は左側壁部材
３０を突抜けて延在している。２つの軸２０，２
２は、それぞれの側壁部材２８，３０の中でパツ
キン３２ないし３４によつて密封されている。さ
らに、軸２０は連結部材３６によつてモータ４０
と連結され、軸２２は連結部材３８によつてモー
タ４２と連結されている。モータ４０ないし４２
は軸２０ないし２２と同軸的に配置され、それぞ
れ中間保持部材４４または４６にフランジ付けさ
れている。中間保持部材４４，４６も、側壁部材
２８ないし３０にフランジ付けされている。これ
らの部材４４と４６、および２８と３０とは、そ
れぞれ全く同じ形状をしている。 The casing has two opposite end faces to which side wall members 28 to 30 are attached. The upper shaft 20 extends through the side wall member 28 on the right side in FIG. 1, and the lower shaft 22 extends through the left wall member 30. two axes 20,2
2 are sealed within their respective side wall members 28, 30 by packings 32-34. Further, the shaft 20 is connected to the motor 40 by the connecting member 36.
The shaft 22 is connected to the motor 42 by a connecting member 38. motor 40 to 42
are arranged coaxially with shafts 20-22 and flanged to intermediate retaining members 44 or 46, respectively. Intermediate retaining members 44, 46 are also flanged to sidewall members 28-30. These members 44 and 46 and 28 and 30 have exactly the same shape.
第３図は、この歯車ポンプを制御する電気回路
を示している。この図ではモータ４０，４２は直
流分巻電動機として構成されている。その励磁電
流路には電流測定器５２ないし５４が配置され、
それらは共通の制御装置５０の入力側と接続され
ている。制御装置５０の出力側は回転数設定値発
信器５８と接続され、それは出力増幅器６２を介
してモータ４２の電流測定器５４と接続されてい
る。制御装置５０には、制御線路６４を介して入
力信号Ｘが供給される。この入力信号Ｘは２つの
モータ４０，４２の出力比を決定し、それを0.5
〜１の間で調整する。モータ４０，４２には、別
の回転数設定値発信器５６を配属されている。こ
の回転数設定値発信器５６は、モータ４０と接続
された回転数発信器６６の発生する実際値を、入
力される設定回転数と比較し、必要に応じて、補
正された制御量を出力増幅器６０に供給する。 FIG. 3 shows the electrical circuit that controls this gear pump. In this figure, the motors 40, 42 are configured as DC shunt motors. Current measuring devices 52 to 54 are arranged in the excitation current path,
They are connected to the input side of a common control device 50. The output of the control device 50 is connected to a rotational speed setpoint transmitter 58 , which is connected via a power amplifier 62 to a current measuring device 54 of the motor 42 . An input signal X is supplied to the control device 50 via a control line 64 . This input signal X determines the output ratio of the two motors 40, 42 and sets it to 0.5
Adjust between ~1. A further rotational speed setpoint transmitter 56 is assigned to the motors 40 , 42 . This rotation speed set value transmitter 56 compares the actual value generated by the rotation speed transmitter 66 connected to the motor 40 with the input set rotation speed, and outputs a corrected control amount as necessary. Amplifier 60 is supplied.
モータの出力を制御する際には、出力増幅器６
０は、設定回転数の入力量に対応して、電流I40
をモータ４０に供給する。電流測定器５２はこの
電流を測定し、測定量Ｋ・I40の信号を制御装置
５０に供給する。制御装置５０は、入力信号Ｘお
よび測定Ｋ・I40に応じて、回転数設定値発信器
５８を介して出力増幅器６２を制御し、それはモ
ータ４２に電流I42を供給する。電流測定器５４
は電流I42を測定し、測定量Ｋ・I42を制御装置５
０にフイードバツクする。制御装置５０は測定量
Ｋ・I42を設定量Ｋ・I42 SOLLと比較し、必要に
応じて、出力増幅器６２に加えられる制御量を補
正する。 When controlling the output of the motor, the output amplifier 6
0 corresponds to the input amount of the set rotation speed, and the current I 40
is supplied to the motor 40. A current measuring device 52 measures this current and supplies a signal of the measured quantity K·I 40 to the control device 50. Depending on the input signal X and the measurement K·I 40 , the control device 50 controls an output amplifier 62 via a rotational speed setpoint transmitter 58, which supplies the motor 42 with a current I 42 . Current measuring device 54
measures the current I 42 and transmits the measured quantity K・I 42 to the control device 5.
Feedback to 0. The control device 50 compares the measured quantity K·I 42 with the set quantity K·I 42 SOLL and corrects the control quantity applied to the output amplifier 62 if necessary.
第１図は本発明による歯車ポンプの実施例を軸
方向に沿つて示す縦断面図、第２図は第１図の
―線に沿つて示す横断面図、第３図はこの歯車
ポンプを制御する電気回路のブロツク図である。
１０…ケーシング、１２…吸入口、１４…吐出
口、１６，１８…軸受ブツシユ、２０，２２…歯
車軸、２４，２６…歯車、２８，３０…側壁部
材、３２，３４…パツキング、３６，３８…連結
部材、４０，４２…モータ、４４，４６…中間支
持部材、５０…制御装置、５２，５４…電流測定
器、５６，５８…回転数設定値発信器、６０，６
２…出力増幅器、６４…制御線路、６６…回転数
発信器。
Fig. 1 is a longitudinal sectional view showing an embodiment of the gear pump according to the present invention along the axial direction, Fig. 2 is a transverse sectional view taken along the line - - in Fig. 1, and Fig. 3 is a control of this gear pump. FIG. 2 is a block diagram of an electric circuit. DESCRIPTION OF SYMBOLS 10... Casing, 12... Suction port, 14... Discharge port, 16, 18... Bearing bushing, 20, 22... Gear shaft, 24, 26... Gear, 28, 30... Side wall member, 32, 34... Packing, 36, 38 ...Connecting member, 40, 42... Motor, 44, 46... Intermediate support member, 50... Control device, 52, 54... Current measuring device, 56, 58... Rotation speed setting value transmitter, 60, 6
2... Output amplifier, 64... Control line, 66... Rotation speed transmitter.
Claims (1)
互いに噛合つた２つの歯車２４，２６が支承さ
れ、また該歯車用の駆動装置を有する歯車ポンプ
において、各歯車２４，２６にそれぞれ固有のモ
ータ（４０ないし４２）が配属されていることを
特徴とする歯車ポンプ。 ２ ２つのモータ４０，４２の出力がごく僅かだ
け異なつている特許請求の範囲第１項記載の歯車
ポンプ。 ３ モータ４０が歯車２４と同軸的に連結され、
かつケーシング１０の端面に取付けられ、また他
のモータ４２がもう１つの歯車２６と同軸的に連
結され、かつケーシング１０のもう一方の端面に
取付けられている特許請求の範囲第１項記載の歯
車ポンプ。 ４ ケーシング１０を有し、該ケーシングの中で
互いに噛合つた２つの歯車２４，２６が支承さ
れ、また該歯車用の駆動装置を有する歯車ポンプ
において、各歯車２４，２６にそれぞれ固有のモ
ータ（４０ないし４２）が配属されており、該２
つのモータ４０，４２が共通の制御装置５０によ
つて制御され、該制御装置の第１の入力側に、２
つのモータ４０，４２の出力比を決定する入力信
号Ｘが加わり、 ２つのモータの各々に回転数設定値発信器５
６；５８が配属され、一方のモータに配属された
回転数設定値発信器５６の入力側に、外部から入
力される回転数設定値が加わり、他方のモータに
配属された回転数設定値発信器５８の入力側には
制御装置５０の出力が加わり、 ２つの回転数設定値発信器５６，５８の出力側
が、それぞれ出力増幅器６０，６２と接続され、
該出力増幅器が電流測定器５２，５４を介して２
つのモータに駆動電流を供給し、 電流測定器５２，５４の出力側が、それぞれ制
御装置５０の第２または第３の出力側と接続され
ている、 ことを特徴とする歯車ポンプ。[Scope of Claims] 1. A gear pump having a casing 10, in which two gears 24, 26 meshing with each other are supported, and a drive device for the gears, in which each gear 24, 26 has a A gear pump, characterized in that each is assigned its own motor (40 to 42). 2. The gear pump according to claim 1, wherein the outputs of the two motors 40, 42 differ only slightly. 3. The motor 40 is coaxially connected to the gear 24,
The gear according to claim 1, which is attached to an end face of the casing 10, and another motor 42 is coaxially connected to another gear 26, and is attached to the other end face of the casing 10. pump. 4. A gear pump having a casing 10, in which two gears 24, 26 meshing with each other are supported, and a drive for the gears, each gear 24, 26 having its own motor (40 2 to 42) are assigned, and
The two motors 40, 42 are controlled by a common control device 50, at a first input of which two motors 40, 42 are connected.
An input signal X that determines the output ratio of the two motors 40 and 42 is applied, and a rotation speed set value transmitter 5 is applied to each of the two motors.
6; 58 is assigned, and the rotation speed setting value inputted from the outside is added to the input side of the rotation speed setting value transmitter 56 assigned to one motor, and the rotation speed setting value assigned to the other motor is transmitted. The output of the control device 50 is added to the input side of the generator 58, and the output sides of the two rotation speed set value transmitters 56 and 58 are connected to output amplifiers 60 and 62, respectively.
The output amplifier is connected to two
A gear pump characterized in that a drive current is supplied to two motors, and the output sides of current measuring devices 52 and 54 are connected to the second or third output side of a control device 50, respectively.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH4164/82A CH659290A5 (en) | 1982-07-08 | 1982-07-08 | GEAR PUMP. |
| CH4164/82-3 | 1982-07-08 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5920590A JPS5920590A (en) | 1984-02-02 |
| JPS6343594B2 true JPS6343594B2 (en) | 1988-08-31 |
Family
ID=4270990
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58117196A Granted JPS5920590A (en) | 1982-07-08 | 1983-06-30 | Gear pump |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS5920590A (en) |
| CH (1) | CH659290A5 (en) |
| DE (1) | DE3230550C2 (en) |
| FR (1) | FR2529964A1 (en) |
| GB (1) | GB2123089B (en) |
| IT (1) | IT1163629B (en) |
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| FR2580339B1 (en) * | 1985-04-16 | 1989-06-16 | Sagem | ELECTROPNEUMATIC CONVERTER |
| CH664604A5 (en) * | 1985-11-25 | 1988-03-15 | Cerac Inst Sa | ROTARY MACHINE. |
| JPS639691A (en) * | 1986-06-27 | 1988-01-16 | Mitsubishi Electric Corp | Scroll type fluid machinery |
| SE466167B (en) * | 1990-05-16 | 1992-01-07 | Johnson Pump Ab | PUMP MOUNTING TYPE OF DEPLACEMENT METHOD INCLUDING TWO INDIVIDUAL ELECTRIC MOTOR DRIVES WITH EACH INTERACTIVE PUMP ENGINES, WHERE ANOTHER MOTOR ROTARY AND RELATED PUMP ROTOR MOVES A PUMP HOUSING INTEGRATOR MOTOR ROTOR |
| US5354179A (en) * | 1990-08-01 | 1994-10-11 | Matsushita Electric Industrial Co., Ltd. | Fluid rotating apparatus |
| EP0472933B2 (en) * | 1990-08-01 | 2003-12-03 | Matsushita Electric Industrial Co., Ltd. | Fluid rotating apparatus |
| JP3049793B2 (en) * | 1991-03-04 | 2000-06-05 | 松下電器産業株式会社 | Fluid rotating device |
| JPH055492A (en) * | 1991-06-28 | 1993-01-14 | Matsushita Electric Ind Co Ltd | Fluid rotary device |
| JP3074829B2 (en) * | 1991-09-05 | 2000-08-07 | 松下電器産業株式会社 | Fluid rotating device |
| JP3074845B2 (en) * | 1991-10-08 | 2000-08-07 | 松下電器産業株式会社 | Fluid rotating device |
| JPH05195957A (en) * | 1992-01-23 | 1993-08-06 | Matsushita Electric Ind Co Ltd | Vacuum pump |
| JPH05202855A (en) * | 1992-01-29 | 1993-08-10 | Matsushita Electric Ind Co Ltd | Hydraulic rotating device |
| KR960009860B1 (en) † | 1992-01-31 | 1996-07-24 | 다니이 아끼오 | Synchronous rotating apparatus for rotating a plurality of shafts |
| KR960009861B1 (en) * | 1992-01-31 | 1996-07-24 | 다니이 아끼오 | Fluid rotating apparatus |
| JPH05272478A (en) * | 1992-01-31 | 1993-10-19 | Matsushita Electric Ind Co Ltd | Vacuum pump |
| US5374173A (en) * | 1992-09-04 | 1994-12-20 | Matsushita Electric Industrial Co., Ltd. | Fluid rotating apparatus with sealing arrangement |
| DE4318707A1 (en) * | 1993-06-04 | 1994-12-08 | Sihi Gmbh & Co Kg | Displacement machine with electronic motor synchronization |
| US6241486B1 (en) | 1998-03-18 | 2001-06-05 | Flowserve Management Company | Compact sealless screw pump |
| EP0886068B1 (en) | 1998-08-25 | 2003-10-08 | Maag Pump Systems Textron AG | Gear pump with multiple driven shafts |
| DE19859287A1 (en) * | 1998-12-22 | 2000-03-09 | Bosch Gmbh Robert | Electrohydraulic arrangement, esp. for mobile applications, e.g. for motor vehicle steering systems has drive system with number of motors corresp. to number of displacement devices |
| EP1249608A1 (en) | 2001-10-24 | 2002-10-16 | Maag Pump Systems Textron AG | Device, like an extrusion machine, comprising a direct driven gear pump |
| GB0203071D0 (en) * | 2002-02-09 | 2002-03-27 | Lucas Industries Ltd | Control system |
| EP1270946B1 (en) | 2002-09-17 | 2006-10-18 | Maag Pump Systems Textron AG | Device, like an extrusion machine, comprising a direct driven gear pump |
| GB2432631A (en) * | 2005-11-24 | 2007-05-30 | Timothy John Sweatman | Meshing gear type pump controlled by phase adjustment |
| DE102005061673A1 (en) | 2005-12-21 | 2007-07-05 | Rolls-Royce Deutschland Ltd & Co Kg | Leading edge formation for the compressor blades of gas turbine engines |
| EP2275683B1 (en) | 2009-06-18 | 2017-01-11 | Maag Pump Systems AG | Method for controlling a gear pump |
| EP2275684A1 (en) | 2009-06-18 | 2011-01-19 | Maag Pump Systems AG | Assembly with a gear pump |
| KR102252260B1 (en) * | 2014-02-28 | 2021-05-13 | 프로젝트 피닉스, 엘엘씨 | Pump integrated with two independently driven prime movers |
| EP3123029B1 (en) | 2014-03-25 | 2024-03-20 | Project Phoenix, LLC | System to pump fluid and control thereof |
| WO2015164453A2 (en) | 2014-04-22 | 2015-10-29 | Afshari Thomas | Fluid delivery system with a shaft having a through-passage |
| JP2015220905A (en) * | 2014-05-20 | 2015-12-07 | 株式会社荏原製作所 | Pump including electric motor and control method of the same |
| EP3149342B1 (en) | 2014-06-02 | 2020-04-15 | Project Phoenix LLC | Linear actuator assembly and system |
| US10544861B2 (en) | 2014-06-02 | 2020-01-28 | Project Phoenix, LLC | Hydrostatic transmission assembly and system |
| JP6742299B2 (en) | 2014-07-22 | 2020-08-19 | プロジェクト・フェニックス・エルエルシー | Pump and method for transferring fluid |
| SG11201702336RA (en) * | 2014-09-23 | 2017-04-27 | Project Phoenix Llc | System to pump fluid and control thereof |
| US10072676B2 (en) | 2014-09-23 | 2018-09-11 | Project Phoenix, LLC | System to pump fluid and control thereof |
| US10539134B2 (en) | 2014-10-06 | 2020-01-21 | Project Phoenix, LLC | Linear actuator assembly and system |
| EP3209885A1 (en) | 2014-10-20 | 2017-08-30 | Project Phoenix LLC | Hydrostatic transmission assembly and system |
| US10865788B2 (en) | 2015-09-02 | 2020-12-15 | Project Phoenix, LLC | System to pump fluid and control thereof |
| US11085440B2 (en) | 2015-09-02 | 2021-08-10 | Project Phoenix, LLC | System to pump fluid and control thereof |
| GB201518619D0 (en) * | 2015-10-21 | 2015-12-02 | Rolls Royce Controls & Data Services Ltd | Gear Pump |
| CN105805528A (en) * | 2016-03-16 | 2016-07-27 | 哈尔滨宏万智科技开发有限公司 | Gear oil pump with double transmission gear shafts |
| CN107246386A (en) * | 2017-08-10 | 2017-10-13 | 青岛科技大学 | A kind of dual drive rubber teeth wheel pump filter glue device |
| CN108150412B (en) * | 2017-12-28 | 2024-07-23 | 重庆川仪自动化股份有限公司 | Differential gear pump controlled by manual and electric combination |
| CN109854498A (en) * | 2019-03-06 | 2019-06-07 | 郑州沃华机械有限公司 | A kind of double driving shafts Melt Pump and its control method |
| US20230250820A1 (en) * | 2020-07-08 | 2023-08-10 | Project Phoenix, LLC | Dynamic control of gears in a gear pump having a drive-drive configuration |
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|---|---|---|---|---|
| GB809445A (en) * | 1954-02-27 | 1959-02-25 | Heraeus Gmbh W C | Improvements in or relating to rotary high vacuum pumps |
| US2918209A (en) * | 1957-05-14 | 1959-12-22 | Schueller Otto | Motor-compressor unit |
| DE1628368A1 (en) * | 1967-06-28 | 1971-07-22 | Rietschle Masch App | Rotary lobe compressors |
| US3484823A (en) * | 1967-12-15 | 1969-12-16 | Cornell Aeronautical Labor Inc | Multirecompression heater and/or high temperature compressor |
| DE2049116A1 (en) * | 1970-10-06 | 1972-04-13 | Leningradskij nautschno-issledowatelskij i konstruktorskij institut chimitsches kowo matschinostrojenija, Leningrad (Sowjetunion) | Device for the continuous conveyance and mixing of liquids |
| CH592249A5 (en) * | 1975-12-11 | 1977-10-14 | Maag Zahnraeder & Maschinen Ag | |
| JPS5387408U (en) * | 1976-12-20 | 1978-07-18 | ||
| DE2736222C3 (en) * | 1977-08-11 | 1980-04-10 | Fischer, Peter, 8741 Salz | Lift catch |
| GB2019493A (en) * | 1978-04-19 | 1979-10-31 | Compair Ind Ltd | Positive Displacement Compressors |
-
1982
- 1982-07-08 CH CH4164/82A patent/CH659290A5/en not_active IP Right Cessation
- 1982-08-17 DE DE3230550A patent/DE3230550C2/en not_active Expired
-
1983
- 1983-06-30 JP JP58117196A patent/JPS5920590A/en active Granted
- 1983-06-30 IT IT21861/83A patent/IT1163629B/en active
- 1983-07-08 FR FR8311440A patent/FR2529964A1/en active Pending
- 1983-07-08 GB GB08318588A patent/GB2123089B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| DE3230550C2 (en) | 1984-11-22 |
| GB2123089A (en) | 1984-01-25 |
| GB2123089B (en) | 1985-05-30 |
| DE3230550A1 (en) | 1984-01-12 |
| FR2529964A1 (en) | 1984-01-13 |
| JPS5920590A (en) | 1984-02-02 |
| IT8321861A0 (en) | 1983-06-30 |
| CH659290A5 (en) | 1987-01-15 |
| IT1163629B (en) | 1987-04-08 |
| GB8318588D0 (en) | 1983-08-10 |
| IT8321861A1 (en) | 1984-12-30 |
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