JPH08136311A - Vibration-type measuring instrument - Google Patents
Vibration-type measuring instrumentInfo
- Publication number
- JPH08136311A JPH08136311A JP27163594A JP27163594A JPH08136311A JP H08136311 A JPH08136311 A JP H08136311A JP 27163594 A JP27163594 A JP 27163594A JP 27163594 A JP27163594 A JP 27163594A JP H08136311 A JPH08136311 A JP H08136311A
- Authority
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- Japan
- Prior art keywords
- measuring
- vibration
- pipe
- amplitude
- measuring tube
- 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.)
- Granted
Links
Landscapes
- Measuring Volume Flow (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、加振される少なくと
も１本の測定管を有し、この測定管内を流れる流体の質
量流量にもとづき発生するコリオリ力を利用して質量流
量を測定する質量流量計、または上記測定管内の流体の
密度変化に応じて変化する測定管の共振周波数の変化に
より流体密度を測定する振動式の密度計、もしくは両方
の機能を持つ振動型測定器、特に流体温度，周囲温度や
軸力（応力）によって変化する測定値を補正することが
可能な振動型測定器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mass for measuring a mass flow rate by using Coriolis force generated based on a mass flow rate of a fluid flowing in the measurement tube, which has at least one vibrating measurement tube. A flow meter, a vibrating density meter that measures the fluid density by changing the resonance frequency of the measuring tube that changes according to the density change of the fluid in the measuring tube, or a vibrating measuring instrument that has both functions, especially the fluid temperature. The present invention relates to a vibration-type measuring instrument that can correct measured values that change due to ambient temperature and axial force (stress).
【０００２】[0002]
【従来の技術】図５は直管式質量流量計の従来例を示す
構成図である。検出部１は１本の直管状測定管２と、こ
の測定管２の振動の節部ａ，ｂを固定する左右の固定材
３ａ，３ｂと、固定材３ａ，３ｂの振動を互いにキャン
セルするよう、ネジ止めまたは溶接等の手段により固定
材３ａ，３ｂに固定されたり、または固定材３ａ，３ｂ
と一体的に成形された支持部４ａおよび４ｂ（４ａのみ
図示）と、アダプタ７ａによりそれぞれ支持部４ａ，４
ｂに固定されたコイルおよび測定管２の中央部に固定さ
れたマグネットにより構成され、測定管２をその共振周
波数で振動させる（加振する）振動発生器５とを有して
いる。2. Description of the Related Art FIG. 5 is a block diagram showing a conventional example of a straight pipe type mass flow meter. The detection unit 1 cancels the vibrations of one straight tubular measuring pipe 2, the left and right fixing members 3a and 3b for fixing the vibration nodes a and b of the measuring pipe 2, and the fixing members 3a and 3b. , Fixed to the fixing members 3a, 3b by means such as screwing or welding, or the fixing members 3a, 3b
And supporting portions 4a and 4b (only 4a is shown) integrally molded with the supporting portions 4a and 4b, respectively.
It has a coil fixed to b and a magnet fixed to the central portion of the measuring tube 2, and has a vibration generator 5 for vibrating (exciting) the measuring tube 2 at its resonance frequency.
【０００３】検出部１はさらに、振動発生器５と同じく
アダプタ７ｂ，７ｃにより支持部４ａ，４ｂに固定され
たコイルに対し、測定管２上の振動発生器５を中心とす
るほぼ対称な位置にそれぞれ固定されたマグネットによ
り構成され、測定管２の振動を検出する速度検出センサ
（または変位センサ，加速度センサ）６ａ，６ｂと、速
度検出センサ６ａからの出力を受けてその信号振幅が一
定となるよう、振動発生器５に対して駆動信号を出力す
る駆動回路８と、速度検出センサ６ａ，６ｂからの信号
の位相差（時間差）にもとづき質量流量信号Ｑｍを出力
する信号処理回路９とから構成されている。The detection unit 1 further has a substantially symmetrical position about the vibration generator 5 on the measuring tube 2 with respect to the coil fixed to the support units 4a and 4b by the adapters 7b and 7c like the vibration generator 5. Speed detection sensors (or displacement sensors, acceleration sensors) 6a and 6b for detecting the vibration of the measuring tube 2 and a signal amplitude that is constant when receiving the output from the speed detection sensor 6a. As described above, the drive circuit 8 that outputs a drive signal to the vibration generator 5 and the signal processing circuit 9 that outputs the mass flow rate signal Qm based on the phase difference (time difference) of the signals from the speed detection sensors 6a and 6b. It is configured.
【０００４】ここで、以上の如く構成された検出部１に
おいて、流体の流量がゼロの場合について考える。すな
わち、測定管２は速度検出センサ６ａ、振動発生器５お
よび駆動回路８により、その共振周波数で加振されてい
る。また、速度検出センサ６ａ，６ｂは測定管２の中央
部に対して対称な位置に取り付けられているため、これ
らのセンサ６ａ，６ｂからは互いに位相差のない同じ振
幅の信号が得られる。Now, let us consider a case where the flow rate of the fluid is zero in the detecting section 1 constructed as described above. That is, the measuring tube 2 is vibrated at its resonance frequency by the speed detection sensor 6a, the vibration generator 5, and the drive circuit 8. Further, since the speed detection sensors 6a and 6b are mounted at symmetrical positions with respect to the central portion of the measuring tube 2, the sensors 6a and 6b can obtain signals having the same amplitude but no phase difference.
【０００５】これに対し、流れが生じて振動する測定管
２内を流体が流れると、測定管２の節ａから測定管２の
中央部に向かうに従い、図６に示されるように振動方向
の速度成分が増加するため、測定管２内を流れる流体に
は振動方向に測定管２から正の加速度が作用する。した
がって、その反作用として測定管２には流体から反力が
作用するため、図７に示されるように測定管２の節ａか
ら測定管２の中央部では、振動の位相が遅れる方向に変
形する。また、測定管２の中央部から節ｂに向かうに従
い、振動方向の速度成分は減少するため、測定管２内を
流れる流体には振動方向に測定管２から負の加速度が作
用する。したがって、その反作用として測定管２には流
体からの反力が作用し、図７のように測定管２の中央部
から節ｂでは振動の位相が進む方向の変形力を受ける。On the other hand, when a fluid flows in the measuring tube 2 where a flow is generated and vibrates, the direction of vibration is changed from the node a of the measuring tube 2 toward the center of the measuring tube 2, as shown in FIG. Since the velocity component increases, a positive acceleration acts on the fluid flowing in the measuring pipe 2 from the measuring pipe 2 in the vibration direction. Therefore, as a reaction, a reaction force acts on the measuring tube 2 from the fluid, and as shown in FIG. 7, in the center part of the measuring tube 2 from the node a of the measuring tube 2, the vibration phase is deformed in a direction in which the phase of the vibration is delayed. . Further, since the velocity component in the vibration direction decreases from the central portion of the measurement pipe 2 toward the node b, a negative acceleration from the measurement pipe 2 acts on the fluid flowing in the measurement pipe 2 in the vibration direction. Therefore, as a reaction thereof, a reaction force from the fluid acts on the measurement pipe 2, and as shown in FIG. 7, the deformation force in the direction in which the phase of vibration advances from the central portion of the measurement pipe 2 to the node b.
【０００６】以下、変形を数式を用いて説明する。い
ま、変位センサ６ａの変位は、共振による測定管の横振
動の変位から、 Ｙａ＝η（ａ）ｓｉｎωｔ …（１） と表わされる。 η（ａ）：測定管の長手方向の位置ａにおける振幅を表
わす関数 ω ：測定管の共振周波数The transformation will be described below by using mathematical expressions. Now, the displacement of the displacement sensor 6a is expressed as Ya = η (a) sinωt (1) from the displacement of the lateral vibration of the measuring pipe due to resonance. η (a): Function that represents the amplitude at the position a in the longitudinal direction of the measuring tube ω: Resonant frequency of the measuring tube
【０００７】また、変位センサ６ａにおける流体からの
反力による測定管のたわみ形状は、下記（２）式とな
る。 ｙａ＝−２Ｌ3 ωＱｍηｃ（ａ）ｃｏｓωｔ／ＥＩ …（２） Ｌ ：測定管の長さ Ｅ ：測定管のヤング率 Ｉ ：測定管の断面２次モーメント Ｑｍ ：測定管内を流れる流体の質量流量 ηｃ（ａ）：測定管の長手方向の位置ａにおける流体か
らの反力による測定管の変形振幅を与える関数The deflection shape of the measuring tube due to the reaction force from the fluid in the displacement sensor 6a is given by the following equation (2). ya = -2L 3 ωQm ηc (a) cos ωt / EI (2) L: Length of measuring pipe E: Young's modulus of measuring pipe I: Second moment of area of measuring pipe Qm: Mass flow rate of fluid flowing in measuring pipe ηc (A): A function that gives the deformation amplitude of the measuring pipe due to the reaction force from the fluid at the position a in the longitudinal direction of the measuring pipe.
【０００８】実際の測定管のたわみ形状は（１）式の共
振による測定管のたわみに、（２）式の測定管の変形が
重畳して振動する。つまり、測定管のたわみ形状は
（１），（２）式を合成して（３）式のようになる。 ξａ＝Ｙａ＋ｙａ＝Ａｓｉｎ（ωｔ−α） …（３） ここに、 Ａ＝［η（ａ）2 ＋｛２Ｌ3 ωＱｍηｃ（ａ）／ＥＩ｝2 ］1/2 …（４） α＝２Ｌ3 ωＱｍηｃ（ａ）／ＥＩη（ａ） …（５）In the actual bending shape of the measuring pipe, the deformation of the measuring pipe of the formula (2) is superimposed on the bending of the measuring pipe due to the resonance of the formula (1) and vibrates. That is, the deflection shape of the measuring tube is expressed by the formula (3) by combining the formulas (1) and (2). ξa = Ya + ya = Asin (ωt−α) (3) where A = [η (a) 2 + {2L 3 ωQmηc (a) / EI} 2 ] 1/2 (4) α = 2L 3 ωQmηc (A) / EIη (a) (5)
【０００９】変位センサ６ｂにおける測定管の横振動の
変位は、これが測定管の中央部に関し変位センサ６ａと
対称な位置に取り付けられているため、変位センサ６ａ
の変位と同じになる。すなわち、 Ｙｂ＝Ｙａ＝η（ａ）ｓｉｎωｔ …（６） また、変位センサ６ｂにおける流体からの測定管への反
力は、変位センサ６ａにおける流体からの反力と大きさ
は同じで方向は反対であるから、 ｙｂ＝−ｙａ＝２Ｌ3 ωＱｍηｃ（ａ）ｃｏｓωｔ／ＥＩ …（７） となる。The displacement of the lateral vibration of the measuring pipe in the displacement sensor 6b is attached at a position symmetrical to the displacement sensor 6a with respect to the central portion of the measuring pipe.
Becomes the same as the displacement of. That is, Yb = Ya = η (a) sinωt (6) Further, the reaction force from the fluid in the displacement sensor 6b to the measuring pipe has the same magnitude as the reaction force from the fluid in the displacement sensor 6a, but the direction is opposite. Therefore, yb = −ya = 2L 3 ωQmηc (a) cosωt / EI (7)
【００１０】したがって、変位センサ６ｂにおける測定
管のたわみ形状は、 ξｂ＝Ｙａ−ｙａ＝Ａｓｉｎ（ωｔ＋α） …（８） となる。上記（３），（８）式より、変位センサ６ａ，
６ｂの信号間には２αの位相差があることが分かり、こ
の位相差２αは（５）式より質量流量Ｑｍに比例するこ
とが分かる。よって、変位センサ６ａ，６ｂの信号間の
時間差は、 Δｔ＝２α／ω＝２Ｌ3 Ｑｍηｃ（ａ）／ＥＩη（ａ） …（９） となる。Therefore, the deflection shape of the measuring tube in the displacement sensor 6b is ξb = Ya-ya = Asin (ωt + α) (8) From the equations (3) and (8), the displacement sensor 6a,
It can be seen that there is a phase difference of 2α between the signals of 6b, and this phase difference 2α is found to be proportional to the mass flow rate Qm from equation (5). Therefore, the time difference between the signals of the displacement sensors 6a and 6b is Δt = 2α / ω = 2L 3 Qmηc (a) / EIη (a) (9).
【００１１】また、測定管の共振周波数は次の（１０）
式で与えられる。 ω＝λ2 ／Ｌ2 ・（ＥＩ／ρ）1/2 …（１０） λ：測定管の境界条件と振動モードで決定される定数 ρ：測定管と測定管内の流体を含めた線密度 ところで、測定管の温度が変化すると、（５）または
（９）式より、ヤング率Ｅの温度依存性から、質量流量
Ｑｍが一定でもセンサ出力信号の位相差や時間差が変化
することが分かる。同様にして、測定流体に密度変化が
ない場合でも、（１０）式の共振周波数ωも変化するこ
とが分かる。Further, the resonance frequency of the measuring tube is (10)
Given by the formula. ω = λ 2 / L 2 · (EI / ρ) 1/2 (10) λ: Constant determined by the boundary condition and vibration mode of the measuring tube ρ: Linear density including the measuring tube and the fluid in the measuring tube As the temperature of the measuring tube changes, it can be seen from the equation (5) or (9) that the phase difference and time difference of the sensor output signal change from the temperature dependence of the Young's modulus E even if the mass flow rate Qm is constant. Similarly, it can be seen that the resonance frequency ω of the equation (10) also changes even when the density of the measurement fluid does not change.
【００１２】これまでは、測定管に作用する軸力（応
力）の影響を無視したが、軸力の影響を考慮すると、測
定管の振幅を示す定数ηは測定管の位置だけでなく軸力
Ｔの関数ともなることから、先の（１）式は次の（１
１）式のようになる。 Ｙａ＝η（ａ，Ｔ）ｓｉｎωｔ …（１１） したがって、先の（５）式，（９）式は下記の（１
２），（１３）式のようになる。 α＝２Ｌ3 ωＱｍηｃ（ａ，Ｔ）／ＥＩη（ａ，Ｔ） …（１２） Δｔ＝２α／ω＝２Ｌ3 Ｑｍηｃ（ａ，Ｔ）／ＥＩη（ａ，Ｔ） …（１３）Up to now, the influence of the axial force (stress) acting on the measuring pipe is neglected. However, considering the influence of the axial force, the constant η indicating the amplitude of the measuring pipe is not only the position of the measuring pipe but also the axial force. Since it is also a function of T, the above equation (1) is
It becomes like the formula 1). Ya = η (a, T) sinωt (11) Therefore, the above equations (5) and (9) are
It becomes like the formulas (2) and (13). α = 2L 3 ωQmηc (a, T) / EIη (a, T) (12) Δt = 2α / ω = 2L 3 Qmηc (a, T) / EIη (a, T) (13)
【００１３】すなわち、質量流量に比例して発生する位
相差や時間差は、測定管に作用する軸力によっても変化
することが分かる。このときの測定管の共振周波数ω
は、 ω＝λn （Ｔ）2 ／Ｌ2 ・（ＥＩ／ρ）1/2 …（１４） となり、測定管の共振周波数ωも測定管に作用する軸力
の関数であることを示している。That is, it is understood that the phase difference and the time difference generated in proportion to the mass flow rate also change depending on the axial force acting on the measuring tube. Resonance frequency ω of the measuring tube at this time
Is ω = λ n (T) 2 / L 2 · (EI / ρ) 1/2 (14), showing that the resonance frequency ω of the measuring tube is also a function of the axial force acting on the measuring tube. There is.
【００１４】一般的に、測定管を振動させ、測定管内を
流れる流体の質量流量にもとづいて発生するコリオリ力
を利用して質量流量を測定する質量流量計では、測定流
体の温度変化や周囲温度の変化によって測定管の温度が
変化した場合、測定管のヤング率の温度依存性により測
定管の剛性が変化し、コリオリ力に対する感度が変化し
て流量測定値が変化する。また、直管状の測定管を有す
るコリオリ式の質量流量計の場合、上述のように温度な
どの変化による測定管や支持部の膨張，収縮によって測
定管に作用する軸力が変化し、この軸力の変化にて質量
流量の 感度が変化することになる。Generally, in a mass flow meter that vibrates a measuring pipe and uses a Coriolis force generated based on the mass flow rate of a fluid flowing in the measuring pipe to measure the mass flow rate, the temperature change of the measuring fluid and the ambient temperature are measured. When the temperature of the measuring tube changes due to the change of, the rigidity of the measuring tube changes due to the temperature dependence of the Young's modulus of the measuring tube, the sensitivity to Coriolis force changes, and the flow rate measurement value changes. Further, in the case of a Coriolis mass flowmeter having a straight tubular measuring tube, the axial force acting on the measuring tube changes due to the expansion and contraction of the measuring tube and the supporting part due to the change in temperature as described above, and this axis The change in force changes the sensitivity of mass flow rate.
【００１５】また、振動式の密度計においても同様に、
測定流体の温度変化や周囲温度の変化によって測定管の
温度が変化すると、測定管のヤング率の温度依存性によ
り共振周波数が変化し、測定誤差が発生する。特に、直
管状の測定管を有するものでは、測定管に作用する軸力
の変化に伴って共振周波数が変化するため、測定値に誤
差が生じるわけである。Similarly, in a vibration type density meter,
When the temperature of the measuring tube changes due to the temperature change of the measurement fluid or the ambient temperature, the resonance frequency changes due to the temperature dependence of the Young's modulus of the measuring tube, causing a measurement error. Particularly, in the case of having a straight tube-shaped measuring tube, the resonance frequency changes with the change of the axial force acting on the measuring tube, so that an error occurs in the measured value.
【００１６】以上のように、温度環境の変化に伴って質
量流量計の感度や測定値に変動が生じた場合の補正方式
としては、例えば特公平５−６９４５２号公報，特開平
６−９４５０１号公報に示すものなどがある。前者によ
れば、２つの温度センサを支持部と実質的に測定管の温
度に等しい位置に、それぞれ取り付け、この２つの温度
センサからの信号を補正回路に導くとともに、２つの振
動センサから導かれた流量信号も同様に補正回路に入力
して、補正を実施するようにしている。As described above, as a correction method when the sensitivity or the measured value of the mass flowmeter fluctuates due to the change of the temperature environment, for example, Japanese Patent Publication No. 5-69452 and Japanese Patent Laid-Open No. 6-94501. There are those shown in the official gazette. According to the former, the two temperature sensors are mounted at positions substantially equal to the temperature of the support portion and the measuring tube, and the signals from the two temperature sensors are guided to the correction circuit and the two vibration sensors. Similarly, the flow rate signal is also input to the correction circuit to perform the correction.
【００１７】一方、後者では、流量測定値を測定管の温
度に対応して補正するため、測定管の温度を検出する温
度センサと、測定値を測定管の長さおよび応力に依存し
て補正するための長さ変化センサ（例えばストレインゲ
ージなどのひずみゲージ）とを設け、それぞれの信号を
補正回路に導いて補正するようにしている。On the other hand, in the latter, since the flow rate measurement value is corrected according to the temperature of the measuring pipe, the temperature sensor for detecting the temperature of the measuring pipe and the measured value are corrected depending on the length and stress of the measuring pipe. A length change sensor (for example, a strain gauge such as a strain gauge) is provided to guide each signal to a correction circuit for correction.
【００１８】[0018]
【発明が解決しようとする課題】前者のように、測定管
と支持部の温度測定を行ない、ヤング率の変化に伴う変
化と、間接的に測定管の軸力を推定する場合、温度安定
時でも流体の温度と環境温度の差により、各部での温度
勾配が異なる場合がある。また、流体温度や環境温度が
変化する過渡的な状態においては、各部の温度勾配は当
然安定しない。したがって、上記のような各状態におい
ては測定管や支持部の平均温度を評価できる温度の測定
位置が常に変化するため、或る特定位置の温度測定では
正確な測定値の補正ができない場合が生じる。As in the former case, when the temperature of the measuring tube and the supporting portion is measured and the change due to the change of the Young's modulus and the axial force of the measuring tube are indirectly estimated, when the temperature is stable. However, the temperature gradient in each part may differ due to the difference between the fluid temperature and the environmental temperature. Further, in a transient state in which the fluid temperature and the environmental temperature change, the temperature gradient of each part is naturally not stable. Therefore, in each of the above-mentioned states, the temperature measurement position at which the average temperature of the measurement pipe and the support portion can be evaluated is constantly changing, so that it may not be possible to accurately correct the measurement value by measuring the temperature at a specific position. .
【００１９】一方、後者のように直接測定管の歪みを測
定するものでは、前者の方式に比べ歪みを直接測定して
いることから、正確な補正が可能となる点で優れている
が、測定管に直接ストレインゲージ等を取り付ける必要
があるため、測定管の振動特性に悪影響を及ぼし、測定
の安定性に問題が生じる。このような影響を避けるた
め、発明者は質量体を測定管の両側に取り付け、その外
側にストレインゲージを貼り付ける構成を提案してい
る。このとき、測定管の振動を安定化するため、質量体
の質量を測定管に対して充分に大きくする必要があり、
質量計が大型化し重くなるという別の問題が発生する。On the other hand, in the latter case in which the strain of the measuring tube is directly measured, the strain is directly measured as compared with the former method, so that it is excellent in that accurate correction is possible. Since it is necessary to directly attach a strain gauge or the like to the pipe, this adversely affects the vibration characteristics of the measuring pipe and causes a problem in measurement stability. In order to avoid such an influence, the inventor has proposed a configuration in which the mass body is attached to both sides of the measuring tube and the strain gauge is attached to the outside thereof. At this time, in order to stabilize the vibration of the measuring tube, it is necessary to make the mass of the mass body sufficiently large with respect to the measuring tube.
Another problem occurs that the mass meter becomes large and heavy.
【００２０】また、支持部にストレインゲージを貼り付
ける別の構成も提案しているが、測定管を安定に振動さ
せるには、支持部の剛性を充分に大きくする必要がある
ため、測定管の断面積は支持部の断面積に比較してかな
り小さく、支持部に発生する歪みは測定管の歪みに比べ
てかなり小さくなるため、支持部の歪みから測定管の歪
みを推定する方式は、誤差が大きくなるという問題が生
じる。さらに長さ変化スロットを設け、測定管の長さを
測定する実施例も開示されているが、構造が複雑でコス
トアップになるという問題もある。したがって、この発
明の課題は測定精度の向上を、特に構造を複雑化するこ
となく安価に実現可能とすることにある。Another structure has been proposed in which a strain gauge is attached to the supporting portion. However, in order to vibrate the measuring tube stably, the rigidity of the supporting portion needs to be sufficiently large. Since the cross-sectional area is much smaller than the cross-sectional area of the support part and the strain generated in the support part is much smaller than the strain of the measuring pipe, the method of estimating the strain of the measuring pipe from the strain of the supporting part is an error. Becomes large. Further, an example in which a length changing slot is provided to measure the length of the measuring tube is also disclosed, but there is a problem that the structure is complicated and the cost is increased. Therefore, an object of the present invention is to improve the measurement accuracy at low cost without complicating the structure.
【００２１】[0021]
【課題を解決するための手段】このような課題を解決す
るため、請求項１の発明では、加振される少なくとも１
本の直管状測定管内を流れる流体の質量流量または密度
の少なくとも一方の測定が可能な振動型測定器におい
て、前記測定管の第１部分とその他の第２部分との振動
振幅比（または差）を求め、その結果にもとづき測定値
の補正を行なうことを特徴としている。この請求項１の
発明では、前記測定管の第１部分を、測定管の振幅が最
大となる部分とすることができる（請求項２の発明）。In order to solve such a problem, in the invention of claim 1, at least one vibration is applied.
In a vibration type measuring instrument capable of measuring at least one of mass flow rate and density of a fluid flowing in a straight measuring tube of a book, a vibration amplitude ratio (or a difference) between a first part and another second part of the measuring tube. Is obtained, and the measured value is corrected based on the result. In the invention of claim 1, the first portion of the measuring tube can be a portion where the amplitude of the measuring tube is maximum (invention of claim 2).
【００２２】また、請求項３の発明では、加振される少
なくとも１本の直管状測定管内を流れる流体の質量流量
または密度の少なくとも一方の測定が可能な振動型測定
器において、前記測定管を加振する振動発生器と、測定
管の第１部分の振動振幅を測定する第１のセンサと、測
定管の第２部分の振動振幅を測定する第２のセンサと、
測定管の温度を測定する温度センサと、前記測定管，振
動発生器，第１，第２のセンサを支持する支持部と、前
記測定管の第１部分と第２部分との振動振幅比（または
差）を演算する振幅演算手段と、この振幅演算手段から
の出力により測定値の補正演算を行なう補正演算手段と
を設けたことを特徴としている。Further, in the invention of claim 3, in the vibration type measuring instrument capable of measuring at least one of the mass flow rate and the density of the fluid flowing in the at least one straight tubular measuring tube to be vibrated, the measuring tube is provided. A vibration generator that vibrates, a first sensor that measures the vibration amplitude of the first portion of the measuring tube, and a second sensor that measures the vibration amplitude of the second portion of the measuring tube;
A temperature sensor for measuring the temperature of the measuring pipe, a supporting portion for supporting the measuring pipe, the vibration generator, and the first and second sensors, and a vibration amplitude ratio of the first portion and the second portion of the measuring pipe ( Alternatively, it is characterized in that an amplitude calculation means for calculating the difference) and a correction calculation means for correcting the measurement value by the output from the amplitude calculation means are provided.
【００２３】上記請求項３の発明では、前記測定管の第
１部分を、測定管の振幅が最大となる部分とすることが
できる（請求項４の発明）。さらに、請求項３または４
の発明では、前記第２のセンサ（第１のセンサ）の出力
が一定となるように測定管を駆動する一方、前記第１の
センサ（第２のセンサ）の出力を前記補正演算手段に直
接導入して補正演算することにより、前記振幅演算手段
を省略することができる（請求項５の発明）。In the invention of claim 3, the first portion of the measuring tube can be a portion where the amplitude of the measuring tube is maximum (invention of claim 4). Further, claim 3 or 4
In the invention, while driving the measuring tube so that the output of the second sensor (first sensor) becomes constant, the output of the first sensor (second sensor) is directly output to the correction calculation means. By introducing and performing the correction calculation, the amplitude calculating means can be omitted (the invention of claim 5).
【００２４】[0024]
【作用】測定管の１次のたわみ振動によるたわみ形状は
軸力の有無によって変化し、例えば図４のようになる。
これは、測定管に或る軸力が加わった場合（実線）と、
軸力が作用していない場合（点線）のたわみ形状を示し
ている。なお、このたわみ形状は測定管の中央に対して
対称となるから、図４では固定点から中央までの形状を
示している。The flexure shape of the measuring tube due to the primary flexural vibration changes depending on the presence / absence of the axial force, for example, as shown in FIG.
This is when a certain axial force is applied to the measuring tube (solid line),
The flexure shape when no axial force is acting (dotted line) is shown. Since this flexure shape is symmetrical with respect to the center of the measuring tube, FIG. 4 shows the shape from the fixed point to the center.
【００２５】このことから、測定管の第１部分（例えば
振幅が最大となる中央部）の振動振幅を測定する第１の
センサと、その他の部分（第２部分）の振動振幅を測定
する第２のセンサを設け、測定管の第１部分とその他の
第２部分の振動振幅との比（または差）を測定すること
により、測定管の軸力を直接知ることができることが分
かる。そこで、この振動振幅比（差）にもとづき、測定
信号の感度補正を行なうようにする。なお、密度測定値
についても同様に、振動振幅比（差）に応じて補正す
る。From this, the first sensor for measuring the vibration amplitude of the first portion (for example, the central portion where the amplitude is maximum) of the measuring pipe and the first sensor for measuring the vibration amplitude of the other portion (second portion). It can be seen that the axial force of the measuring tube can be directly known by providing two sensors and measuring the ratio (or difference) between the vibration amplitude of the first part of the measuring tube and the vibration amplitude of the other second part. Therefore, the sensitivity of the measurement signal is corrected based on this vibration amplitude ratio (difference). The density measurement value is similarly corrected according to the vibration amplitude ratio (difference).
【００２６】なお、測定管の振動振幅比の計測は、原理
的には任意の２点間とすることができるが、測定管を１
次モードで加振する場合は、その中央部とその他の部分
の振幅を測定し、測定管を高次モードで加振する場合
は、振幅が最大となる腹の部分とその他の部分の振幅を
測定するのが便利である。In principle, the measurement of the vibration amplitude ratio of the measuring tube can be performed between any two points, but one measuring tube is used.
When oscillating in the next mode, measure the amplitude of the central part and other parts.When oscillating the measuring tube in the higher mode, measure the amplitude of the antinode part and other parts where the amplitude is maximum. It is convenient to measure.
【００２７】[0027]
【実施例】図１はこの発明の実施例を説明するための構
成図である。同図からも明らかなように、この実施例の
特徴は検出部１に速度検出センサ６ｃおよび温度センサ
１０を付加した点、さらに、信号処理回路９に振幅比演
算部９１，温度演算部９３および補正演算部９４などを
付加した点にあり、その他は図５に示すものと同様であ
る。したがって、ここではこれらの相違点を中心に説明
する。1 is a block diagram for explaining an embodiment of the present invention. As is apparent from the figure, the feature of this embodiment is that the speed detection sensor 6c and the temperature sensor 10 are added to the detection unit 1, and the signal processing circuit 9 further includes an amplitude ratio calculation unit 91, a temperature calculation unit 93, and The point is that a correction calculation unit 94 and the like are added, and the other points are the same as those shown in FIG. Therefore, these differences will be mainly described here.
【００２８】先の（５），（９）式または（１２），
（１３）式に示すように、質量流量に比例して発生する
速度センサ６ａ，６ｂからの出力信号の位相差または時
間差が、ヤング率Ｅおよび軸力Ｔの関数であることか
ら、まず、温度センサ１０からの出力を、温度演算部９
３で温度信号に変換する。次に、速度検出センサ６ａ，
６ｂからの各出力を振幅比演算部９１に導き、検出部１
の構成と現在の駆動条件とから決まる振動振幅比（また
は差）を演算する。The above equations (5) and (9) or (12),
As shown in the equation (13), the phase difference or time difference between the output signals from the speed sensors 6a and 6b, which is generated in proportion to the mass flow rate, is a function of the Young's modulus E and the axial force T. The output from the sensor 10 is used as the temperature calculation unit 9
Convert to a temperature signal at 3. Next, the speed detection sensor 6a,
Each output from 6b is led to the amplitude ratio calculation unit 91, and the detection unit 1
The vibration amplitude ratio (or difference) determined by the above configuration and the current driving condition is calculated.
【００２９】補正演算部９４は振幅比演算部９１，位相
差演算部９２，温度演算部９３および速度検出センサ６
ａからの出力を受け、位相差演算部９２からの位相差信
号を、ここでは速度検出センサ６ａから得られる測定管
の共振周波数によって補正し、時間差信号に変換する。
この時間差信号は、補正演算部９４で温度演算部９３か
らの温度信号と、振幅比演算部９１からの振幅比信号に
よる測定管の軸力変化にともなう感度補正信号とによっ
て補正が行なわれる。The correction calculation unit 94 includes an amplitude ratio calculation unit 91, a phase difference calculation unit 92, a temperature calculation unit 93, and a speed detection sensor 6.
Upon receiving the output from a, the phase difference signal from the phase difference calculator 92 is corrected by the resonance frequency of the measuring tube obtained from the speed detection sensor 6a, and converted into a time difference signal.
The time difference signal is corrected by the correction calculation unit 94 by the temperature signal from the temperature calculation unit 93 and the sensitivity correction signal due to the change in the axial force of the measuring pipe due to the amplitude ratio signal from the amplitude ratio calculation unit 91.
【００３０】なお、上記では、補正演算部９４に速度検
出センサ６ａからの出力を導入するようにしたが、速度
検出センサ６ｂまたは６ｃからの出力も導入するように
しても良い。また、密度計における密度測定値について
も上記と同様に、温度と振動振幅比に応じた補正が行な
われることになるのはいうまでもない。In the above description, the output from the speed detection sensor 6a is introduced into the correction calculation unit 94, but the output from the speed detection sensor 6b or 6c may be introduced. Needless to say, the density measurement value in the densitometer is also corrected in accordance with the temperature and the vibration amplitude ratio, as described above.
【００３１】図２はこの発明の他の実施例を示す構成図
である。これは、駆動回路８から振動発生器５に供給さ
れる信号によって、速度検出センサ６ａの出力を一定と
なるようにしていることから、測定管の一方の位置での
振動振幅を既知として扱い、測定管の他方の位置での振
動振幅としては速度検出センサ６ｃからの出力を利用
し、補正演算部９４によって測定管の軸力変化にともな
う感度補正を行なうことにより、振幅比演算部９１を省
略可能としたものである。なお、その他の点は図１と同
様である。FIG. 2 is a block diagram showing another embodiment of the present invention. This is because the output of the speed detection sensor 6a is made constant by the signal supplied from the drive circuit 8 to the vibration generator 5, so that the vibration amplitude at one position of the measuring tube is treated as known, The output from the speed detection sensor 6c is used as the vibration amplitude at the other position of the measuring tube, and the correction calculating section 94 performs sensitivity correction according to the axial force change of the measuring tube, thereby omitting the amplitude ratio calculating section 91. It was possible. The other points are the same as in FIG.
【００３２】図３に図２の変形例を示す。これは、振幅
比演算部９１を省略可能とした点は図２の場合と同じで
あるが、測定管の中央部の振幅を一定、つまり速度検出
センサ６ｃの出力を一定（既知）となるように制御し、
速度検出センサ６ａ（または６ｂ）からの出力を補正演
算部９４に導入して両者の振幅比を求めるようにした点
で異なっている。その他は図２と同じである。FIG. 3 shows a modification of FIG. This is the same as the case of FIG. 2 in that the amplitude ratio calculation unit 91 can be omitted, but the amplitude of the central portion of the measuring tube is constant, that is, the output of the speed detection sensor 6c is constant (known). Control to
The difference is that the output from the speed detection sensor 6a (or 6b) is introduced into the correction calculation unit 94 to obtain the amplitude ratio of the two. Others are the same as in FIG.
【００３３】なお、以上では測定管を１次のたわみ振動
で加振する場合について説明してきたが、この発明は高
次モードで加振する場合にも適用することができる。そ
の場合は、例えば振動の腹の部分と他の部分の振動振幅
比（または差）に応じて補正を行なう。すなわち、測定
管の異なる２点間の振動振幅比（または差）に応じて補
正がなされるわけである。Although the case where the measuring tube is vibrated by the first-order flexural vibration has been described above, the present invention can be applied to the case where the measuring tube is vibrated in the higher-order mode. In that case, for example, the correction is performed according to the vibration amplitude ratio (or difference) between the antinode portion of the vibration and the other portion. That is, the correction is made according to the vibration amplitude ratio (or difference) between two different points on the measuring tube.
【００３４】[0034]
【発明の効果】この発明によれば、測定管の或る位置の
振動振幅と、その他の位置での振動振幅との比（または
差）を求め、測定管に作用する軸力変化にともなう感度
変化の補正を、温度補正に加えて行なうようにしたの
で、検出部の構成を特に複雑化せず、かつ振動型測定器
の安定性を損なうこともなく、さらには過渡的な温度変
化時にも正確な測定が可能になる、などの利点がもたら
される。According to the present invention, the ratio (or difference) between the vibration amplitude at a certain position of the measuring pipe and the vibration amplitude at other positions is obtained, and the sensitivity due to the change in the axial force acting on the measuring pipe is obtained. Since the change is corrected in addition to the temperature correction, the structure of the detection unit is not particularly complicated, the stability of the vibration type measuring device is not impaired, and even when there is a transient temperature change. This brings advantages such as accurate measurement.
【図１】この発明の実施例を示す構成図である。FIG. 1 is a configuration diagram showing an embodiment of the present invention.
【図２】この発明の他の実施例を示す構成図である。FIG. 2 is a configuration diagram showing another embodiment of the present invention.
【図３】図２の変形例を示す構成図である。FIG. 3 is a configuration diagram showing a modified example of FIG.
【図４】測定管の軸力による変形形状例を説明するため
の説明図である。FIG. 4 is an explanatory diagram for explaining an example of a deformed shape of a measuring tube due to an axial force.
【図５】従来例を示す構成図である。FIG. 5 is a configuration diagram showing a conventional example.
【図６】流体に作用する加速度を説明するための説明図
である。FIG. 6 is an explanatory diagram for explaining acceleration acting on a fluid.
【図７】測定管に作用する流体反力の影響を説明するた
めの説明図である。FIG. 7 is an explanatory diagram for explaining the influence of a fluid reaction force acting on the measuring tube.
１…検出部、２…測定管、３ａ，３ｂ…固定材、４ａ，
４ｂ…支持部、５…振動発生器、６ａ，６ｂ，６ｃ…速
度検出センサ、７ａ，７ｂ，７ｃ…アダプタ、８…駆動
回路、９…信号処理回路、１０…温度センサ、９１…振
幅比演算部、９２…位相差演算部、９３…温度演算部、
９４…補正演算部。DESCRIPTION OF SYMBOLS 1 ... Detection part, 2 ... Measuring tube, 3a, 3b ... Fixing material, 4a,
4b ... Support part, 5 ... Vibration generator, 6a, 6b, 6c ... Speed detection sensor, 7a, 7b, 7c ... Adapter, 8 ... Drive circuit, 9 ... Signal processing circuit, 10 ... Temperature sensor, 91 ... Amplitude ratio calculation Part, 92 ... phase difference calculating part, 93 ... temperature calculating part,
94 ... Correction calculation unit.
Claims (5)
管内を流れる流体の質量流量または密度の少なくとも一
方の測定が可能な振動型測定器において、 前記測定管の第１部分とその他の第２部分との振動振幅
比（または差）を求め、その結果にもとづき測定値の補
正を行なうことを特徴とする振動型測定器。1. A vibration-type measuring instrument capable of measuring at least one of a mass flow rate and a density of a fluid flowing in at least one straight tubular measuring pipe to be vibrated, the first portion of the measuring pipe and the other portion. A vibration-type measuring instrument characterized by obtaining a vibration amplitude ratio (or difference) between two parts and correcting the measured value based on the result.
が最大となる部分とすることを特徴とする請求項１に記
載の振動型測定器。2. The vibration measuring instrument according to claim 1, wherein the first portion of the measuring pipe is a portion where the amplitude of the measuring pipe is maximum.
管内を流れる流体の質量流量または密度の少なくとも一
方の測定が可能な振動型測定器において、 前記測定管を加振する振動発生器と、測定管の第１部分
の振動振幅を測定する第１のセンサと、測定管の第２部
分の振動振幅を測定する第２のセンサと、測定管の温度
を測定する温度センサと、前記測定管，振動発生器，第
１，第２のセンサを支持する支持部と、前記測定管の第
１部分と第２部分との振動振幅比（または差）を演算す
る振幅演算手段と、この振幅演算手段からの出力により
測定値の補正演算を行なう補正演算手段とを設けたこと
を特徴とする振動型測定器。3. A vibration type measuring instrument capable of measuring at least one of a mass flow rate and a density of a fluid flowing in at least one straight tubular measuring pipe to be vibrated, wherein a vibration generator vibrates the measuring pipe. A first sensor for measuring the vibration amplitude of the first portion of the measuring pipe, a second sensor for measuring the vibration amplitude of the second portion of the measuring pipe, a temperature sensor for measuring the temperature of the measuring pipe, and the measurement A support part for supporting the pipe, the vibration generator, the first and second sensors, an amplitude calculation means for calculating a vibration amplitude ratio (or a difference) between the first part and the second part of the measuring pipe, and the amplitude. A vibration-type measuring instrument comprising: a correction calculation unit that performs a correction calculation of a measured value based on an output from the calculation unit.
が最大となる部分とすることを特徴とする請求項３に記
載の振動型測定器。4. The vibration measuring instrument according to claim 3, wherein the first portion of the measuring pipe is a portion where the amplitude of the measuring pipe is maximum.
力が一定となるように測定管を駆動する一方、前記第１
のセンサ（第２のセンサ）の出力を前記補正演算手段に
直接導入して補正演算することにより、前記振幅演算手
段を省略可能にしたことを特徴とする請求項３または４
のいずれかに記載の振動型測定器。5. The measuring tube is driven so that the output of the second sensor (first sensor) becomes constant while the first sensor
5. The amplitude calculation means can be omitted by directly introducing the output of the sensor (second sensor) of the above into the correction calculation means and performing correction calculation.
The vibration type measuring instrument according to any one of 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27163594A JP3565588B2 (en) | 1994-11-07 | 1994-11-07 | Vibration type measuring instrument |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27163594A JP3565588B2 (en) | 1994-11-07 | 1994-11-07 | Vibration type measuring instrument |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08136311A true JPH08136311A (en) | 1996-05-31 |
| JP3565588B2 JP3565588B2 (en) | 2004-09-15 |
Family
ID=17502817
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27163594A Expired - Fee Related JP3565588B2 (en) | 1994-11-07 | 1994-11-07 | Vibration type measuring instrument |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3565588B2 (en) |
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| DE102009012474A1 (en) | 2009-03-12 | 2010-09-16 | Endress + Hauser Flowtec Ag | Measuring system with a vibration-type transducer |
| DE102009028007A1 (en) | 2009-07-24 | 2011-01-27 | Endress + Hauser Flowtec Ag | Measuring transducer of the vibration type and measuring device with such a transducer |
| DE102009028006A1 (en) | 2009-07-24 | 2011-01-27 | Endress + Hauser Flowtec Ag | Vibration-type transducers and measuring instrument with such a transducer |
| WO2011080173A2 (en) | 2009-12-31 | 2011-07-07 | Endress+Hauser Flowtec Ag | Measuring system comprising a vibration-type transducer |
| WO2011080172A1 (en) | 2009-12-31 | 2011-07-07 | Endress+Hauser Flowtec Ag | Measuring system comprising a vibration-type transducer |
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