WO2015037669A1 - 送水管路系のキャビテーションサージを緩和および防止するための装置および方法 - Google Patents
送水管路系のキャビテーションサージを緩和および防止するための装置および方法 Download PDFInfo
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- WO2015037669A1 WO2015037669A1 PCT/JP2014/074098 JP2014074098W WO2015037669A1 WO 2015037669 A1 WO2015037669 A1 WO 2015037669A1 JP 2014074098 W JP2014074098 W JP 2014074098W WO 2015037669 A1 WO2015037669 A1 WO 2015037669A1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0077—Safety measures
- F04D15/0083—Protection against sudden pressure change, e.g. check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
- F04D29/4293—Details of fluid inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
Definitions
- the present invention relates to a turbo pump that acts on a liquid, and relates to an apparatus and method for suppressing or mitigating cavitation surge, which is a unique phenomenon that occurs in a turbo pump targeting liquid.
- cavitation instability In turbo pumps such as water pumps, a phenomenon called cavitation instability with cavitation may occur, which causes pump shaft vibration, impeller stress fluctuations, and noise.
- the cavitation instability phenomenon includes a phenomenon called cavitation surge, which is a phenomenon in which significant pulsation of the flow rate and pressure of the piping system occurs at a period lower than the rotational speed of the impeller.
- the inventor for example, the periodic behavior of cavitation surge is “spring effect”, the liquid transported by the pump is “inertia element”, the pressure loss of piping and valves is “resistance element”, and the pump is “negative resistance element”
- the present invention was intensively studied as a vibration phenomenon (fluid element fluctuation phenomenon) of the entire system in which each element of the pump system is coupled, and the present invention has been achieved.
- the present invention proposes a cavitation countermeasure as a whole pump system, in particular, an apparatus and method for suppressing or mitigating cavitation surge.
- the first embodiment of the present invention measures and compares the upstream flow rate and the downstream flow rate of the turbo pump that transfers liquid, and the upstream flow rate is smaller than the downstream flow rate.
- the pump suction part is reduced to accelerate the upstream flow rate and the pump discharge part pressure is reduced to reduce the downstream flow rate, and the downstream flow rate is smaller than the upstream flow rate, the pump discharge
- This is a turbo pump cavitation suppression operation method in which the pressure in the pump is increased to increase the downstream flow velocity and the pressure in the pump suction section.
- a turbo pump for transferring the liquid for transferring the liquid, a first damping device that repeatedly pressurizes and depressurizes the upstream liquid so as to attenuate the amplitude of periodic pressure fluctuations of the liquid upstream of the turbo pump, and a turbo pump
- the turbo pump cavitation suppression device includes a second damping device that repeatedly pressurizes and depressurizes the downstream liquid so as to attenuate the periodic pressure fluctuation cycle of the downstream liquid.
- the first damping device performs a depressurization operation when the upstream liquid pressure increases, and performs a pressurization operation when the upstream liquid pressure decreases
- the second damping device Is a cavitation suppression device for a turbo pump that performs a depressurization operation when the pressure of the downstream liquid increases and performs a pressurization operation when the pressure of the downstream liquid decreases.
- a cavitation suppressing device for a turbo pump provided with a control device for performing
- first damping device and the second damping device both comprise a piston and a cylinder, and the piston of the first damping device and the piston of the second damping device are in motion of each other's piston.
- the turbo pump cavitation suppressing device includes a device that brakes the engine and a device that attempts to restore at least one of the pistons to a balanced position.
- both the first damping device and the second damping device comprise a piston and a cylinder, one piston being a cylinder of the first damping device and the second damping device. It is a turbo pump cavitation suppressing device characterized by being fitted together.
- the turbo pump cavitation suppressing device is characterized in that a turbo pump for transferring the liquid and an expander for pushing away the volume of the liquid are connected to a casing or a pipe upstream of the turbo pump. It is.
- the specific operation method is to measure the flow rate or pressure upstream of the turbo pump that transfers liquid, and to expand the expander provided upstream of the turbo pump when a drop in the flow rate or pressure occurs. This is a turbo pump cavitation suppression operation method.
- cavitation surging can be more effectively reduced or suppressed in the entire operating region of the pump.
- pulsation can be more effectively reduced or suppressed throughout the pump system at the upstream, inlet and downstream of the pump, and outlet. it can.
- the pressurizing / depressurizing device separately pressurizes and depressurizes the upstream and downstream in accordance with the periodic pressure state fluctuation compared to the arbitrarily set reference pressure.
- the pressurized downstream flow rate is not returned to the upstream side, and the pump can be efficiently and stably operated without lowering the pump efficiency.
- Fig. 1 is a schematic diagram of a turbo pump system.
- the pump 1 with the impeller 8 built in the casing is a turbo pump, and the rotational force of the external motor 8 rotates the impeller 8 through the shaft.
- a pump upstream pipe 4 is connected to the pump inlet 2 by a flange 10.
- a space (broken line portion) between the pump inlet 2 and the impeller 8 formed in the pump 1 is a pump suction portion 27.
- the pump suction part 27 and the pump upstream pipe 4 are combined to form a pump upstream 29.
- the upstream external device 6 is connected to the pump upstream pipe 4.
- a pump downstream pipe 5 is connected to the pump outlet 3 by a flange 10.
- a space (broken line portion) between the pump outlet 3 and the impeller 8 formed in the pump 1 is a pump discharge portion 28.
- the pump discharge section 28 and the pump downstream pipe 5 are combined to form a pump downstream 30.
- the downstream external device 7 is connected to the pump downstream pipe 5.
- Fig. 2 is a simple reconsideration of what has been described so far as a vibration phenomenon.
- cavitation is called “spring element”
- liquid is “inertia element”
- pressure loss of piping and valves is “resistance element”
- pump is “negative resistance element” or “power source” If we classify and classify the characteristics, we can consider that cavitation surge is a state where power is supplied from a “power source” and vibration continues.
- the present invention aims at stopping or suppressing (relaxing) vibration by changing the characteristics of the pump water supply system by devising a device that changes the state of cavitation and liquid.
- the damping action since the upstream and downstream of the pump are affected by the cavitation state in the pump suction portion, it is desirable that the damping action also acts on both the upstream and downstream.
- FIG. 3 shows a specific embodiment of the invention made based on the above idea.
- a device that acts as a “spring element” and “resistive element” (damper) respectively upstream and downstream of the pump. This is a method of vibration suppression.
- an upstream pressure detector or flow rate detector 13 and an upstream pressurization / decompression device 12 are connected to the pump upstream 29 of the pump 1. These connection positions are connected to the pump suction part 27 or the pump upstream pipe 4 as close to the pump suction part 27 as possible. Separately from these, a downstream pressure detector or flow rate detector 15 and a downstream pressurizing / depressurizing device 14 are connected to the pump downstream 30 of the pump 1. These connection positions are also connected as close as possible to the pump discharge section 28 in the pump discharge section 28 or the pump downstream pipe 5.
- the pressurizing / depressurizing device functions as a pressure pulsation damping device, and specifically, is like an actuator-driven piston as shown in the figure, but is not limited thereto.
- this system there is no bypass system such as a bypass pipe for performing a bypass operation for returning the liquid from the downstream to the upstream, and the bypass operation cannot be performed.
- the periodic pressure fluctuation or flow fluctuation is detected by the upstream and downstream pressure detectors or flow detectors 13 and 15, and the detection information is sent to the controller 16. Based on the information obtained from each detector, the controller 16 gives the upstream and downstream pressurizing / depressurizing devices 12 and 14 timings for convergence of the fluctuations corresponding to the respective cyclic pressure fluctuation phenomena. The operation is instructed to repeat the pressurization and decompression of the liquid.
- the upstream pressurization / decompression device operation corresponds to the pressure and flow rate fluctuation information detected by the upstream detector. If it is downstream, the upstream pressurization / decompression device is operated according to the fluctuation information of the pressure and flow rate detected by the downstream detector, so both upstream and downstream according to each fluctuation state. Independent control can be performed. Note that the cycle of pressurization and pressure reduction applied to the upstream liquid and the cycle of pressurization and pressure reduction applied to the downstream liquid are the same as the basic cycle of the observed pressure fluctuation.
- the pressurization operation is performed so that the pressure in the vicinity of the pump discharge unit 28 is increased from the controller 16 to the pressurization / decompression device 14 on the downstream side. Is instructed. As a result, the liquid flow rate in the pump downstream pipe 5 can be accelerated, and Q2 increases.
- the flow rate that is estimated and corrected based on the measured flow rate is often used in accordance with the performance of the flow rate detector. Therefore, the flow rate includes such a corrected flow rate. .
- the controller 16 when controlling the pressurizing / depressurizing apparatus based on the pressure, the controller 16 tends to increase the pressure of the liquid read by the upstream detector 13 in relation to an arbitrarily set reference pressure.
- the upstream side pressurizing / depressurizing device 12 is instructed to perform an operation of reducing the upward pressure, and conversely, the pressure of the liquid read by the upstream detector tends to decrease further.
- the pressurizing / depressurizing device 12 is instructed to increase the pressure of the decreasing tendency.
- the pressurizing / depressurizing device 14 on the downstream side, and the controller 16 tends to increase the pressure of the liquid read by the downstream detector 15 in relation to the arbitrarily set reference pressure.
- the pressurizing / depressurizing device 14 is instructed to perform an operation of reducing the pressure of the rising tendency, and conversely, the pressure of the liquid read by the downstream detector 15 shows a lower tendency.
- the pressurizing / depressurizing device 14 is instructed to increase the pressure of the decreasing tendency.
- the pump operating area can be operated in a wide range by changing the flow rate Even in this case, cavitation surging can be more effectively mitigated or suppressed in the entire operation region of the pump.
- pulsation can be more effectively reduced or suppressed throughout the pump system at the upstream, inlet and downstream of the pump, and outlet. it can.
- the pressurizing / depressurizing device separately pressurizes and depressurizes the upstream and downstream in accordance with the periodic pressure state fluctuation compared to the arbitrarily set reference pressure. There is no need to return the pressurized downstream flow rate to the upstream side, and it is possible to operate efficiently and stably.
- FIG. 4 shows an embodiment in which the upstream and downstream situations are mainly handled by mechanical control with respect to the upstream and downstream vibration suppression devices.
- An upstream cylinder 18 and an upstream piston 35 fitted to the upstream cylinder 18 are connected to the pump upstream 29 of the pump 1.
- the connection positions in the pump upstream 29 are connected to the pump suction part 27 or the pump upstream pipe 4 as close to the pump suction part 27 as possible.
- a downstream cylinder 19 and a downstream piston 36 fitted thereto are connected to the pump downstream 30 of the pump 1.
- the connection positions in the pump downstream 30 are also connected to the pump discharge section 28 or the pump downstream pipe 5 as close to the pump discharge section 28 as possible.
- a device that is, a piston braking device that mutually brakes the movement of the piston by all or part of the actuator 32, the spring 33, and the dashpot 24.
- the actuator 32, the spring 33, and the dashpot 24 can be adjusted in their elastic coefficients.
- the cross-sectional areas of the pistons 35 and 36 may be equal or different.
- FIG. 5 shows another specific embodiment of the present invention excluding the actuator in FIG. 4 from such a viewpoint.
- the upstream piston 35 and the downstream pressure fluctuation are (1) different in period, (2) if the amplitude is different, or (3) if the phase is the same but the phase is different, the upstream piston 35 and the downstream pressure fluctuation
- the spring 33 and the dashpot 24 connected to the side piston 36 are adjusted so that the operation period, amplitude, and phase of the piston 35 and the piston 36 are appropriate.
- the balance position of the pistons 35 and 36 is an intermediate position between the strokes of the cylinders 18 and 19 when there is no cavitation surge.
- the upstream pressure multiplied by the cylinder cross-sectional area and the downstream pressure x cylinder cross-sectional force are balanced, and the cylinder cross-sectional area required to increase and decrease the upstream pressure x
- the conditions of the piston stroke and the cylinder cross-sectional area ⁇ piston stroke required for increasing and decreasing the pressure on the downstream side do not necessarily match.
- At least one of the pistons 35 and 36 has a “balance position recovery device” configured by a part or all of a spring 23, a dashpot 22, and an actuator 31 connected to an external fixing point. is necessary. By adjusting the spring 23, the dash pot 22, the actuator 31, and the like, the balance positions of the pistons 35 and 36 are determined.
- valves 20 and 21 in the flow path adjust the flow rate flowing into the pistons 35 and 36. You may use for the flow path which connects a pump upstream and downstream flow path by the opening degree adjustment valves 20 and 21 to relieve
- FIG. 6 shows another specific embodiment of the present invention that is more compact.
- the upstream piston 35 in FIG.
- the adjustment device such as the spring 33 and the dashpot 24 that connect between the piston 36 and the downstream piston 36 are unnecessary.
- an upstream cylinder 18 connected to the pump upstream pipe 4 at the pump upstream 29, a downstream cylinder 19 connected to the pump downstream pipe 5 at the pump downstream 30, and a piston 17 fitted to both cylinders are provided. ing.
- the piston 17 may correspond to the cylinders 18 and 19 having the same cross-sectional area, or may correspond to different ones.
- the spring 23, the dashpot 22 and the like can be variably adjusted, and are determined by adjusting the balance position of the piston 17.
- the cavitation compliance ⁇ is the cavitation volume Vc, ⁇ Vc There is a relationship. Therefore, when the cavitation volume Vc is large, the cavitation compliance ⁇ increases and the frequency of the cavitation surge decreases. As the frequency decreases, the frequency of cavitation surge is suppressed.
- the inventor in order to increase the cavitation compliance, the inventor generates a cavitation in the pump in addition to the actual cavitation volume Vc and a dummy volume that behaves as if the cavitation volume has increased simultaneously with the actual cavitation. I came to think that it was generated near the part.
- FIG. 7 shows an example. Specifically, a gas bag (rubber balloon-like) 38 filled with a small amount of gas is developed at the pump suction portion of the turbo pump (or the pump upstream pipe near the pump suction portion). When no cavitation surge is generated, the gas is extracted from the gas bag 38, and the gas bag 38 is installed in a folded state on the inner wall of the pump casing so that the gas bag 38 is deployed when the cavitation surge occurs. May be provided.
- the gas bag 38 expands and contracts during a surge, and the volume of the gas bag 38 that expands and contracts is a dummy volume.
- the volume of the dummy volume When the volume of the dummy volume is Vd, this volume can be treated as an artificial cavitation volume, and the cavitation compliance ⁇ can be considered by combining the actual cavitation volume Vc and the volume Vd of the dummy volume. That means ⁇ (Vc + Vd) Therefore, the value of the cavitation compliance ⁇ can be increased apparently, and the frequency f of the cavitation surge can be decreased. That is, the dummy volume has the effect of reducing the amplitude of the cavitation surge and quickly mitigating the cavitation surge toward convergence.
- FIG. 8 shows a more detailed embodiment.
- the bag 38 is stored in a bag storage groove 25 provided in an annular shape in the upstream casing of the pump 1.
- the bag storage groove 25 preferably has a structure opened in a taper toward the center of the ring.
- the bag 38 Before the cavitation occurs, the bag 38 is stored in the groove 25 (indicated by a solid line).
- the bag 38 may contain gas in advance.
- a pressure detector or a flow rate detector may be disposed as the upstream external device 6 of the pump upstream pipe 4 and gas may be supplied from the gas supply port 26 in response to information that the pressure or flow rate has decreased.
- the bag 38 swells (inflates) in any case, resulting in a state indicated by a broken line.
- the apparent cavitation volume Vc and the expanded volume of the bag 38 reduce the frequency f of the cavitation surge. Become.
- the bag 38 may be unfolded and stored manually by an operator from outside the pump.
- FIG. 9 is the same as the operation used in FIG. 8, but shows a method and apparatus in which an accumulator in which gas is sealed or a spring / mass / dashpot system is directly attached to the pump casing without using a gas bag.
- the cylinder 37 is branched and connected from the upstream casing of the pump 1 or the pump upstream pipe 4, and the piston 17 is fitted thereto.
- a spring 23 and a dashpot 22 are connected to the piston 17.
- the spring 23 corresponds to the bag 38 in FIG. 8.
- the spring 23 extends, and the extension of the spring 23 ⁇ the cross-sectional area of the piston 17 becomes the same as the expanded volume Vd of the bag of FIG.
- Such an apparatus is more rigid than a gas bag and can be expected to have a long life.
- cavitation has been re-examined as a vibration phenomenon, and a method and apparatus for suppressing cavitation surge from two different viewpoints have been shown.
- These two aspects can be implemented not only separately but also in combination with each other.
- it is possible to maintain a stable flow with a wide range of pump operation and to suppress flow fluctuations upstream and downstream of the pump, and at the initial stage of cavitation surge generation.
- the surge frequency can be lowered and the operation can be stably performed.
- the present invention is not limited to the embodiment shown in FIG. 1 and FIG. 7, but can be used for a cavitation surge countermeasure for a turbo pump for transferring a liquid.
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Abstract
Description
本発明は、ポンプシステム全体としてのキャビテーション対策、特にキャビテーションサージを抑制あるいは緩和する装置及び方法を提案するものである。
また、キャビテーションサージの発生時のポンプの上流と下流の圧力や流れを考慮しているので、ポンプ上流、入口とポンプ下流、出口のポンプシステム全てにわたって脈動をより効果的に緩和もしくは抑制することができる。
ここで、キャビテーションが何も発生していない場合には、
Q1=Q2
である。
κ=-∂Vc/∂P1(t)
ここで、κはキャビテーションコンプライアンスという。キャビテーションを前述のバネとして捉えた振動現象としたアナロジーでは、κはバネの弾性定数の逆数にあたるものである。
dVc/dt≒Q2-Q1
である。すなわち流量Q1とQ2は体積Vcの変動に伴い周期的に変動する。
f∝1/κα (αは正の定数)
の関係がある。
また、キャビテーションコンプライアンスκはキャビテーション体積Vcと、
κ∝Vc
の関係がある。
従って、キャビテーション体積Vcが大であると、キャビテーションコンプライアンスκが大きくなり、キャビテーションサージの周波数が小さくなる。周波数が小さくなるほど、キャビテーションサージの頻度が抑制される。
κ∝(Vc+Vd)
となるので、見かけ上キャビテーションコンプライアンスκの値が大きくでき、キャビテーションサージの周波数fを小さくすることができる。即ち、ダミー・ボリュームは、キャビテーションサージの振幅を下げる、速やかにキャビテーションサージを収束に向けて緩和させる効果を持つ。
4 ポンプ上流
5 ポンプ下流
10 フランジ
12 上流側加圧・減圧装置
13 上流側圧力/流量検知器
14 下流側加圧・減圧装置
15 下流側圧力/流量検知器
16 コントローラ
Claims (8)
- 液体を移送するターボポンプの上流の流量と下流の流量を測定して比較し、
該上流の流量が該下流の流量より小さい場合に、ポンプ吸込部の圧力を低減させて該上流の流速を加速させるとともにポンプ吐出部の圧力を低減させて下流の流速を低減させ、
該下流の流量が該上流の流量より小さい場合に、ポンプ吐出部の圧力を増加させて該下流の流速を加速させるとともにポンプ吸込部の圧力を増加させることを特徴とするターボポンプのキャビテーションの抑制運転方法。 - 液体を移送するターボポンプと、
該ターボポンプの上流の液体の周期的な圧力変動の振幅を減衰せしめるように該上流の液体に加圧と減圧を繰り返す第一の減衰装置と、
該ターボポンプの下流の液体の周期的な圧力変動の周期を減衰せしめるように該下流の液体に加圧と減圧を繰り返す第二の減衰装置とを備えたことを特徴とするターボポンプのキャビテーションの抑制装置。 - 前記第一の減衰装置は、前記上流の液体の圧力が上昇するときは減圧動作をし、前記上流の液体の圧力が減少するときは加圧動作をするとともに、
前記第二の減衰装置は、前記下流の液体の圧力が上昇するときは減圧動作をし、前記下流の液体の圧力が減少するときは加圧動作をすることを特徴とする請求項2記載のターボポンプのキャビテーションの抑制装置。 - 該上流に備えられた検知器により得られた情報と、該下流に備えられた検知器により得られた情報から、第一の減衰装置および、第二の減衰装置に動作指示を行う制御機器を備えたことを特徴とする請求項2または3記載のターボポンプのキャビテーションの抑制装置。
- 前記第一の減衰装置と前記第二の減衰装置は、ともにピストンおよびシリンダーからなり、前記第一の減衰装置のピストンと前記第二の減衰装置のピストンは、互いのピストンの動きを制動する装置と、少なくともどちらかのピストンがつりあいの位置に回復しようとする装置を具備することを特徴とする請求項2乃至4のいずれか一項に記載のターボポンプのキャビテーションの抑制装置。
- 前記第一の減衰装置と前記第二の減衰装置は、ともにピストンおよびシリンダーからなり、該ピストンおよびシリンダーは、ひとつのピストンが前記第一の減衰装置と前記第二の減衰装置のシリンダーにともに嵌合することを特徴とする請求項2乃至4のいずれか一項に記載のターボポンプのキャビテーションの抑制装置。
- 液体を移送するターボポンプと、
該ターボポンプの上流側のケーシングまたは配管に、該液体の容積を押しのける膨張器を接続したことを特徴とするターボポンプのキャビテーションの抑制装置。 - 液体を移送するターボポンプの上流の流量または圧力を測定し、
該流量または圧力の低下が発生したときに、該ターボポンプの上流に備えた膨張器を膨張させることを特徴とするターボポンプのキャビテーションの抑制運転方法。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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JP2015536625A JP6590696B2 (ja) | 2013-09-12 | 2014-09-11 | 送水管路系のキャビテーションサージを緩和および防止するための装置および方法 |
US14/917,512 US20160215778A1 (en) | 2013-09-12 | 2014-09-11 | Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system |
US16/690,627 US11378084B2 (en) | 2013-09-12 | 2019-11-21 | Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system |
US17/113,286 US20210088048A1 (en) | 2013-09-12 | 2020-12-07 | Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system |
Applications Claiming Priority (2)
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JP2013-189353 | 2013-09-12 | ||
JP2013189353 | 2013-09-12 |
Related Child Applications (2)
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US14/917,512 A-371-Of-International US20160215778A1 (en) | 2013-09-12 | 2014-09-11 | Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system |
US16/690,627 Division US11378084B2 (en) | 2013-09-12 | 2019-11-21 | Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system |
Publications (1)
Publication Number | Publication Date |
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WO2015037669A1 true WO2015037669A1 (ja) | 2015-03-19 |
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US (3) | US20160215778A1 (ja) |
JP (2) | JP6590696B2 (ja) |
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Cited By (2)
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CN110177927A (zh) * | 2016-12-22 | 2019-08-27 | 赛峰航空器发动机 | 用于调节供给回路的改良方法 |
WO2020042820A1 (zh) * | 2018-08-29 | 2020-03-05 | 华南理工大学 | 一种串联r式汽车减振器的压力损失计算方法 |
Families Citing this family (2)
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US11209842B1 (en) | 2020-06-29 | 2021-12-28 | Saudi Arabian Oil Company | Pressure surge and water hammer mitigation device and method |
CN113007146A (zh) * | 2021-04-16 | 2021-06-22 | 中南大学 | 水泵掺汽超空化防汽蚀及降噪装置 |
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2019
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CN110177927A (zh) * | 2016-12-22 | 2019-08-27 | 赛峰航空器发动机 | 用于调节供给回路的改良方法 |
JP2020514615A (ja) * | 2016-12-22 | 2020-05-21 | サフラン エアークラフト エンジンズ | 供給回路を調整するための改良された方法 |
JP7053626B2 (ja) | 2016-12-22 | 2022-04-12 | サフラン エアークラフト エンジンズ | 供給回路を調整するための改良された方法 |
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Also Published As
Publication number | Publication date |
---|---|
JP6590696B2 (ja) | 2019-10-16 |
US20160215778A1 (en) | 2016-07-28 |
JPWO2015037669A1 (ja) | 2017-03-02 |
US11378084B2 (en) | 2022-07-05 |
US20210088048A1 (en) | 2021-03-25 |
US20200088203A1 (en) | 2020-03-19 |
JP2019105274A (ja) | 2019-06-27 |
JP6741819B2 (ja) | 2020-08-19 |
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