JP2010174714A - Electric pump, and electric pump for brake - Google Patents

Electric pump, and electric pump for brake Download PDF

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JP2010174714A
JP2010174714A JP2009017532A JP2009017532A JP2010174714A JP 2010174714 A JP2010174714 A JP 2010174714A JP 2009017532 A JP2009017532 A JP 2009017532A JP 2009017532 A JP2009017532 A JP 2009017532A JP 2010174714 A JP2010174714 A JP 2010174714A
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pump
motor
electric
frequency
brake
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JP5208004B2 (en
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Michihide Saito
倫英 齊藤
Keigo Kajiyama
径吾 梶山
Chiharu Nakazawa
千春 中澤
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Hitachi Astemo Ltd
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Hitachi Automotive Systems Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric pump capable of restricting the noise and vibration at low costs without increasing dimensions of the pump. <P>SOLUTION: The electric pump is set so that the a value obtained by multiplying the number of slots of a rotor of the motor and the minimum common multiple of the number of discharge per revolution of the pump by a primary number of revolution frequency corresponding to the lowest number of revolution of the motor becomes a predetermined frequency or more. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、電動モータにより駆動されるポンプの技術分野に関する。   The present invention relates to the technical field of pumps driven by electric motors.

従来、電動モータにより駆動されるポンプとして特許文献１に記載の技術が開示されている。この特許文献１に記載のポンプでは、電動モータの回転力変動やポンプの吐出脈動に起因する音や振動を低減するために、モータ出力軸とポンプ駆動軸との噛み合い部分の一方に凸部を、他方に凹部を形成し、モータとポンプの脈動を周波数整合させると共に逆位相へ移相することで脈動成分を相殺し、音や振動を低減している。   Conventionally, the technique of patent document 1 is disclosed as a pump driven by an electric motor. In the pump described in Patent Document 1, in order to reduce noise and vibration caused by fluctuations in the rotational force of the electric motor and discharge pulsation of the pump, a convex portion is provided on one of the meshing portions of the motor output shaft and the pump drive shaft. A recess is formed on the other side, and the pulsation of the motor and the pump are frequency matched and phase-shifted to the opposite phase to cancel out the pulsation component and reduce sound and vibration.

特開２００１−１９９３５５号公報JP 2001-199355 A

しかしながら、上記従来技術にあっては、特殊な継ぎ手を供える必要があり、部品点数の増加やコストアップを招き、また大型化を招く。更に、周波数整合を図るためにモータのコギング回数とポンプギヤ数を一致させる必要があり、設計自由度が低下する問題があった。   However, in the above prior art, it is necessary to provide a special joint, which causes an increase in the number of parts, an increase in cost, and an increase in size. Furthermore, in order to achieve frequency matching, it is necessary to match the number of cogging of the motor and the number of pump gears, which causes a problem that the degree of freedom in design is reduced.

本発明は、上記問題に着目してなされたもので、大型化を招くことなく低コストで音や振動を抑制できる電動式ポンプを提供することにある。   The present invention has been made paying attention to the above problems, and it is an object of the present invention to provide an electric pump that can suppress noise and vibration at low cost without causing an increase in size.

上記目的を達成するため、本発明では、モータの回転子のスロット数とポンプ一回転あたりの吐出回数の最小公倍数にモータの最低回転数に対応する一次回転数周波数を乗算した値が、所定の周波数以上となるように設定した。   In order to achieve the above object, according to the present invention, a value obtained by multiplying the number of slots of the rotor of the motor and the least common multiple of the number of discharges per one rotation of the pump by the primary rotational speed frequency corresponding to the minimum rotational speed of the motor is a predetermined value. It set so that it might become more than a frequency.

よって、共振周波数が高いため人に聞こえることがなく、また、高周波であることから振動も小さくなり、大型化を招くことなく低コストで音や振動を抑制した電動式ポンプを提供できる。   Therefore, since the resonance frequency is high, it cannot be heard by humans, and since it is a high frequency, vibration is reduced, and an electric pump that suppresses sound and vibration at a low cost without causing an increase in size can be provided.

実施例１の電動式ポンプを表す断面図である。1 is a cross-sectional view illustrating an electric pump according to a first embodiment. 実施例１に適用されたギヤポンプを表す断面図である。It is sectional drawing showing the gear pump applied to Example 1. FIG. 実施例１に適用された電動モータを表す断面図である。1 is a cross-sectional view illustrating an electric motor applied to Example 1. FIG. 実施例１の最小公倍数と一次モータ回転数との関係を表す特性図である。It is a characteristic view showing the relationship between the least common multiple of Example 1, and the primary motor rotation speed. 実施例２のモータトルクとポンプ脈動との関係を表すタイムチャートである。It is a time chart showing the relationship between the motor torque of Example 2, and pump pulsation.

以下、本発明の実施形態について図面に基づいて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１はブレーキユニットのポンプ及びモータ部の概要を表す部分断面図である。アルミブロックから形成された略直方体のハウジング１内にはギヤポンプ２が収装され、ハウジング１の一側面にはモータ３がボルトにより取り付けられている。ギヤポンプ２の駆動軸であるポンプシャフト２ａには凸型の２面幅が形成され、モータ３の駆動軸であるモータシャフト３ａには凹型の２面幅が形成され、それらが互いに直接嵌合している。ギヤポンプ２は、１つのポンプシャフト２ａにより駆動される二つのギヤポンプ２１，２２が設けられ、二系統を有するブレーキ装置にあっては、一つのギヤポンプで独立して一系統に油圧を供給可能に構成される。ブレーキの系統とは、例えばＸ配管がなされたブレーキ装置の場合、右前輪と左後輪の組み合わせを一系統と言い、左前輪と右後輪の組み合わせを他の一系統と言う。実施例１では、これら二つのギヤポンプ２１，２２のギヤ位置は一致されており、一方のギヤの位相に着目して設定することで両ギヤの位相が調整される。   FIG. 1 is a partial cross-sectional view illustrating an outline of a pump and a motor unit of a brake unit. A gear pump 2 is housed in a substantially rectangular parallelepiped housing 1 formed of an aluminum block, and a motor 3 is attached to one side of the housing 1 with bolts. The pump shaft 2a, which is the drive shaft of the gear pump 2, has a convex two-surface width, and the motor shaft 3a, which is the drive shaft of the motor 3, has a concave two-surface width, which are directly fitted to each other. ing. The gear pump 2 is provided with two gear pumps 21 and 22 driven by a single pump shaft 2a, and in a brake device having two systems, a single gear pump can independently supply hydraulic pressure to one system. Is done. In the brake system, for example, in the case of a brake device having X piping, a combination of the right front wheel and the left rear wheel is referred to as one system, and a combination of the left front wheel and the right rear wheel is referred to as another system. In the first embodiment, the gear positions of the two gear pumps 21 and 22 are coincident with each other, and the phases of both gears are adjusted by setting focusing on the phase of one gear.

図２はギヤポンプ２１の軸直角方向の断面図である。このギヤポンプ２は外接ギヤポンプであり、ポンプシャフト２ａと一体に回転するドライブギヤ４と、このドライブギヤ４と同一の歯数を有するドリブンギヤ５とが互いに噛み合っている。また、両ギヤの外周側にはシールブロック６が配置され、吸入ポートを形成すると共に、ギヤ歯先とシールブロック内周とでシール面を形成する。作動時には、シールブロック６内の吸入ポートからブレーキ液を吸い込み、両ギヤにより圧縮されたブレーキ液が吐出される。このとき、一回転あたり歯数分の噛み合いと吐出脈動を原因とする音や振動が発生する。   FIG. 2 is a cross-sectional view of the gear pump 21 in the direction perpendicular to the axis. The gear pump 2 is an external gear pump, and a drive gear 4 that rotates integrally with the pump shaft 2 a and a driven gear 5 having the same number of teeth as the drive gear 4 mesh with each other. A seal block 6 is disposed on the outer peripheral side of both gears to form a suction port, and a seal surface is formed by the gear tooth tip and the inner periphery of the seal block. During operation, the brake fluid is sucked from the suction port in the seal block 6, and the brake fluid compressed by both gears is discharged. At this time, sound and vibration are generated due to meshing and discharge pulsation for the number of teeth per rotation.

図３にモータ軸直角方向の断面図を示す。モータ３は回転子であるモータコア３１と、モータハウジング７内壁に固定された永久磁石９とを有する。モータコア３１は複数のスロット１０（図３には９つのスロット）が形成されている。各スロット１０にはそれぞれコイル８が巻回されており、これら各コイル８に図外の整流子を介して次々に電流を印加することにより永久磁石との間で電磁力による吸引反発力を発生させ、回転力を得て作動を行う。分割されているスロット１０に電流を印加する際、各スロットの間においては一瞬電流の流れは遮断され、回転力を失い、その後次のスロットに電流が流れた際、再び回転力を得る。つまり、電動モータにおいては一回転あたりにスロットの数だけ回転数および回転力変動を原因とする音や振動が発生する。   FIG. 3 shows a cross-sectional view in the direction perpendicular to the motor shaft. The motor 3 has a motor core 31 that is a rotor, and a permanent magnet 9 fixed to the inner wall of the motor housing 7. The motor core 31 has a plurality of slots 10 (9 slots in FIG. 3). Each slot 10 has a coil 8 wound around it. By applying a current to each of the coils 8 via a commutator (not shown), an attractive repulsion force is generated between the permanent magnet and an electromagnetic force. To obtain a rotational force. When a current is applied to the slot 10 that is divided, the current flow is interrupted between the slots for a moment and the rotational force is lost. Then, when the current flows to the next slot, the rotational force is obtained again. That is, in the electric motor, sound and vibration due to fluctuations in the rotation speed and rotational force are generated by the number of slots per rotation.

（音，振動の特性）
音や振動は波動であり、別々の起震源から発生する音や振動の周波数成分同士が一致した場合、波の重ね合わせの原理により、振動が増幅され、周波数分析結果において鋭いピークを示す。このピークが音や振動としては問題となる。人間の可聴域は数十Ｈｚから２０ＫＨｚ程度までとされており、この範囲の周波数は人に何らかの違和感を与えるおそれがある。ただし、２ＫＨｚ以上の高周波領域では、振幅が非常に小さくなるため実質的には気にならないことが多い。例えば、自動車に搭載されるブレーキユニットにおいては車室内において２ＫＨｚ以下の周波数帯の音や振動が問題とされることが多く、周波数成分同士の一致点を２ＫＨｚ以上に設定することが望ましい。また、音や振動の性質として、基本周波数の２倍，３倍，・・Ｎ倍の次数成分を持ち、次数成分同士が一致した場合においても波の重ね合わせ原理が適用できる。 (Sound and vibration characteristics)
Sounds and vibrations are waves, and when the frequency components of sounds and vibrations generated from different earthquake sources coincide with each other, the vibrations are amplified by the principle of wave superposition and show a sharp peak in the frequency analysis results. This peak becomes a problem as sound and vibration. The human audible range is set to several tens Hz to about 20 KHz, and the frequency in this range may give the person some sense of incongruity. However, in the high frequency region of 2 KHz or higher, the amplitude is very small, so there are many cases that the user is not substantially concerned. For example, in a brake unit mounted on an automobile, sound and vibration in a frequency band of 2 KHz or less are often a problem in the passenger compartment, and it is desirable to set the coincidence point of frequency components to 2 KHz or more. In addition, as a property of sound and vibration, the wave superposition principle can be applied even when the order components have twice, three times,... N times the fundamental frequency and the order components coincide with each other.

（ポンプ歯数とスロット数の最適な組み合わせ）
上記課題に鑑み、実施例１では起震源であるギヤポンプ２の歯数及びモータ３のスロット数の組み合わせについて以下のように設定することとした。まず、ギヤポンプ２とモータ３の最初の周波数一致点は、ギヤポンプ２の歯数とモータ３のスロット数の最小公倍数（以下、LCMと記載）である。次に、あるモータ一次回転数（rpm）を考えたとき、このモータ一次回転数は一分間当たりの回転数であるため、６０で割って（一分は６０秒だから）周波数に直す。これをモータ一次周波数と定義する。次に、モータ一次周波数にLCMを乗じることにより共振周波数を算出する。この共振周波数が２ＫＨｚ以上であれば、車の乗員にはほとんど違和感を与えることがないのである。図４は、モータ一次周波数と、モータ一次回転数と、LCMとの関係を表す表及び特性図である。すなわち、モータ３を作動させるときのモータ一次回転数に対し、LCMを斜線領域となるように設定すれば２ＫＨｚ以上の共振周波数を得ることができる。 (Optimal combination of pump teeth and slots)
In view of the above-mentioned problems, in Example 1, the combination of the number of teeth of the gear pump 2 and the number of slots of the motor 3 as the earthquake source is set as follows. First, the first frequency coincidence point between the gear pump 2 and the motor 3 is the least common multiple (hereinafter referred to as LCM) of the number of teeth of the gear pump 2 and the number of slots of the motor 3. Next, when a certain motor primary rotational speed (rpm) is considered, since this motor primary rotational speed is the rotational speed per minute, it is divided by 60 (since 1 minute is 60 seconds), and is converted to the frequency. This is defined as the motor primary frequency. Next, the resonance frequency is calculated by multiplying the motor primary frequency by LCM. If this resonance frequency is 2 KHz or more, the vehicle occupant is hardly given a sense of incongruity. FIG. 4 is a table and a characteristic diagram showing the relationship between the motor primary frequency, the motor primary rotation speed, and the LCM. That is, if the LCM is set so as to be in a hatched region with respect to the motor primary rotation speed when the motor 3 is operated, a resonance frequency of 2 KHz or more can be obtained.

例えば、モータ３を作動させるときに最も低い作動回転数は１２００rpm程度と考えられるとする。これは、ポンプを作動させてホイルシリンダを加圧して制動力を得るブレーキ装置において、通常ブレーキ相当の減速を得られる程度である。この場合、モータ一次周波数は２０Ｈｚである。今、共振周波数を２ＫＨｚ以上に設定したいのだから、２０Ｈｚ×LCM≧２０００Ｈｚとなればよい。よって、LCMを１００以上に設定すれば、全ての作動回転数領域で共振周波数を２ＫＨｚ以上に設定することができる。実施例１ではギヤポンプ２の歯数を１９とし、スロット数を９とすると、LCMは１７１となり、共振周波数は３４２０Ｈｚとなり、２ＫＨｚ以上に設定できる。一方、ギヤポンプ２の歯数を１８とすると、LCMは１８となり、共振周波数が３６０Ｈｚとなって２ＫＨｚ未満となってしまうため、乗員に違和感を与えることになる。この場合は、スロット数を１６に設定することで、共振周波数が２ＫＨｚ以上とできる。   For example, it is assumed that the lowest operating rotational speed when the motor 3 is operated is considered to be about 1200 rpm. This is such that a deceleration equivalent to a normal brake can be obtained in a brake device that operates a pump to pressurize a wheel cylinder to obtain a braking force. In this case, the motor primary frequency is 20 Hz. Now, since it is desired to set the resonance frequency to 2 KHz or higher, 20 Hz × LCM ≧ 2000 Hz may be satisfied. Therefore, if the LCM is set to 100 or more, the resonance frequency can be set to 2 KHz or more in all operating rotational speed regions. In Example 1, when the number of teeth of the gear pump 2 is 19 and the number of slots is 9, the LCM is 171 and the resonance frequency is 3420 Hz, which can be set to 2 KHz or more. On the other hand, if the number of teeth of the gear pump 2 is 18, the LCM will be 18, and the resonance frequency will be 360 Hz and less than 2 KHz, which will give the passenger a sense of incongruity. In this case, by setting the number of slots to 16, the resonance frequency can be 2 KHz or more.

次に、ギヤポンプ２の歯数とモータ３のスロット数をどのように設定してLCMを最適な値に設定するかについて説明する。図５は、モータが回転しているときの１つのスロットに着目したとき、モータ側でのトルク変化と、ポンプ側で発生する脈動との関係を表すタイムチャートである。１つのスロットが回転移動する間、その回転速度やモータトルクは一定値を取る。そこで、１つのスロットに対してより多くの歯数を設定すれば、脈動が小さく安定した吐出圧を得ることができる。これにより、音や振動の発生を抑制することができる。   Next, how to set the number of teeth of the gear pump 2 and the number of slots of the motor 3 to set the LCM to an optimum value will be described. FIG. 5 is a time chart showing the relationship between torque change on the motor side and pulsation generated on the pump side when focusing on one slot when the motor is rotating. While one slot rotates, its rotational speed and motor torque take a constant value. Therefore, if a larger number of teeth is set for one slot, a stable discharge pressure with small pulsation can be obtained. Thereby, generation | occurrence | production of a sound and a vibration can be suppressed.

以上説明したように、実施例１の電動式ポンプにあっては、下記に列挙する作用効果を得ることができる。
(1)永久磁石９を用いた回転式の電動モータ３と、該電動モータ３の回転軸により回転駆動されるポンプ２とから構成される電動式ポンプにおいて、LCM（モータ３のスロット数とポンプ一回転あたりの吐出回数の最小公倍数）にモータ３の最低回転数に対応する一次周波数を乗算した値が、ブレーキ制御に許容される２ＫＨｚ以上となるように設定した。よって、共振周波数が高いため人に聞こえることがなく、また、高周波であることから振動も小さくなり、大型化を招くことなく低コストで音や振動を抑制した電動式ポンプを提供できる。尚、実施例１では車両に搭載されるブレーキユニットに適用する例であり、ブレーキユニットに許容される周波数が２ＫＨｚであるため、そのように設定したが、車両以外に適用されるような電動式ポンプであっても、人の可聴領域の上限である４ＫＨｚ以上となるように設定すれば、いずれにせよ音や振動が違和感となることはない。すなわち適用箇所において許容される周波数以上にLCMを設定すれば発明の目的は達成される。また、LCMの組み合わせを検討するに当たり、スロット数よりも歯数が多くなるように設定することが好ましい。これにより、更に音や振動を抑制することができる。 As described above, in the electric pump according to the first embodiment, the following effects can be obtained.
(1) In an electric pump composed of a rotary electric motor 3 using a permanent magnet 9 and a pump 2 driven to rotate by the rotary shaft of the electric motor 3, an LCM (the number of slots in the motor 3 and the pump The value obtained by multiplying the least common multiple of the number of discharges per revolution) by the primary frequency corresponding to the minimum revolution number of the motor 3 was set to be 2 KHz or more allowed for brake control. Therefore, since the resonance frequency is high, it cannot be heard by humans, and since it is a high frequency, vibration is reduced, and an electric pump that suppresses sound and vibration can be provided at low cost without causing an increase in size. In addition, in Example 1, it is an example applied to the brake unit mounted in a vehicle, and since the frequency permitted to a brake unit is 2 KHz, it set so, it is an electric type which is applied other than a vehicle. Even if it is a pump, if it sets so that it may become 4 KHz or more which is the upper limit of a person's audible area, a sound and a vibration will not become uncomfortable anyway. That is, the object of the invention can be achieved if the LCM is set higher than the frequency allowed at the application location. Further, when considering the combination of LCM, it is preferable to set the number of teeth to be larger than the number of slots. Thereby, sound and vibration can be further suppressed.

１ ハウジング
２ ギヤポンプ
３ モータ
４ ドライブギヤ
５ ドリブンギヤ
１０ スロット 1 Housing 2 Gear Pump 3 Motor 4 Drive Gear 5 Driven Gear 10 Slot

Claims (2)

永久磁石を用いた回転式の電動モータと、該電動モータの回転軸により回転駆動されるポンプとから構成される電動式ポンプにおいて、
前記モータの回転子のスロット数と前記ポンプ一回転あたりの吐出回数の最小公倍数に前記モータの最低作動回転数に対応する一次回転数周波数を乗算した値が、所定の周波数以上となるように設定したことを特徴とする電動式ポンプ。 In an electric pump composed of a rotary electric motor using a permanent magnet and a pump driven to rotate by the rotating shaft of the electric motor,
A value obtained by multiplying the least common multiple of the number of slots of the rotor of the motor and the number of discharges per one rotation of the pump by the primary rotational frequency corresponding to the minimum operating rotational speed of the motor is set to be equal to or higher than a predetermined frequency. An electric pump characterized by that. 永久磁石を用いた回転式の電動モータと、該電動モータの回転軸により回転駆動されるポンプとから構成されるブレーキ用電動式ポンプにおいて、
前記モータの回転子のスロット数と前記ポンプ一回転あたりの吐出回数の最小公倍数に前記モータの最低作動回転数に対応する一次周波数を乗算した値が、ブレーキ制御に許容される２ＫＨｚ以上となるように設定したことを特徴とするブレーキ用電動式ポンプ。 In a brake electric pump composed of a rotary electric motor using a permanent magnet and a pump driven to rotate by the rotary shaft of the electric motor,
The value obtained by multiplying the least common multiple of the number of slots of the rotor of the motor and the number of discharges per one rotation of the pump by the primary frequency corresponding to the minimum operating rotational speed of the motor is 2 KHz or more allowed for brake control. Electric brake pump, characterized in that it is set to
JP2009017532A 2009-01-29 2009-01-29 Electric pump for brake Expired - Fee Related JP5208004B2 (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012097585A (en) * 2010-10-29 2012-05-24 Hitachi Automotive Systems Ltd Electric pump
JP2012097586A (en) * 2010-10-29 2012-05-24 Hitachi Automotive Systems Ltd Electric pump
JP2014036533A (en) * 2012-08-10 2014-02-24 Hitachi Automotive Systems Ltd Brushed dc motor and vehicle brake system using the same
JP2018165136A (en) * 2017-03-28 2018-10-25 株式会社アドヴィックス Brake control device
WO2018206189A1 (en) * 2017-05-08 2018-11-15 Robert Bosch Gmbh External gear machine, and exhaust gas heat recovery system having an external gear machine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1113643A (en) * 1997-06-23 1999-01-19 Koyo Seiko Co Ltd Gear pump
JP2001182670A (en) * 1999-12-24 2001-07-06 Koyo Seiko Co Ltd Gear pump
JP2002171721A (en) * 2000-12-01 2002-06-14 Nidec-Shimpo Corp Rotating drive unit
JP2005273667A (en) * 2002-05-21 2005-10-06 Shimadzu Corp Hydraulic device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1113643A (en) * 1997-06-23 1999-01-19 Koyo Seiko Co Ltd Gear pump
JP2001182670A (en) * 1999-12-24 2001-07-06 Koyo Seiko Co Ltd Gear pump
JP2002171721A (en) * 2000-12-01 2002-06-14 Nidec-Shimpo Corp Rotating drive unit
JP2005273667A (en) * 2002-05-21 2005-10-06 Shimadzu Corp Hydraulic device

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012097585A (en) * 2010-10-29 2012-05-24 Hitachi Automotive Systems Ltd Electric pump
JP2012097586A (en) * 2010-10-29 2012-05-24 Hitachi Automotive Systems Ltd Electric pump
JP2014036533A (en) * 2012-08-10 2014-02-24 Hitachi Automotive Systems Ltd Brushed dc motor and vehicle brake system using the same
JP2018165136A (en) * 2017-03-28 2018-10-25 株式会社アドヴィックス Brake control device
WO2018206189A1 (en) * 2017-05-08 2018-11-15 Robert Bosch Gmbh External gear machine, and exhaust gas heat recovery system having an external gear machine

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