WO2016158186A1 - Centrifugal pump device - Google Patents

Centrifugal pump device Download PDF

Info

Publication number
WO2016158186A1
WO2016158186A1 PCT/JP2016/056567 JP2016056567W WO2016158186A1 WO 2016158186 A1 WO2016158186 A1 WO 2016158186A1 JP 2016056567 W JP2016056567 W JP 2016056567W WO 2016158186 A1 WO2016158186 A1 WO 2016158186A1
Authority
WO
Grant status
Application
Patent type
Prior art keywords
impeller
chamber
centrifugal pump
magnetic
unit
Prior art date
Application number
PCT/JP2016/056567
Other languages
French (fr)
Japanese (ja)
Inventor
山田 裕之
顕 杉浦
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date

Links

Images

Classifications

    • AHUMAN NECESSITIES
    • A61MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61MDEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M1/00Suction or pumping devices for medical purposes; Devices for carrying-off, for treatment of, or for carrying-over, body-liquids; Drainage systems
    • A61M1/10Blood pumps; Artificial hearts; Devices for mechanical circulatory assistance, e.g. intra-aortic balloon pumps
    • A61M1/101Non-positive displacement pumps, e.g. impeller, centrifugal, vane pumps
    • A61M1/1012Constructional features thereof
    • A61M1/1013Types of bearings
    • A61M1/1015Magnetic bearings
    • AHUMAN NECESSITIES
    • A61MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61MDEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M1/00Suction or pumping devices for medical purposes; Devices for carrying-off, for treatment of, or for carrying-over, body-liquids; Drainage systems
    • A61M1/10Blood pumps; Artificial hearts; Devices for mechanical circulatory assistance, e.g. intra-aortic balloon pumps
    • A61M1/1086Regulating or controlling systems therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00Pumping installations or systems
    • F04D13/02Units comprising pumps and their driving means
    • F04D13/06Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0666Units comprising pumps and their driving means the pump being electrically driven the motor being of the plane gap type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/04Shafts or bearings, or assemblies thereof
    • F04D29/041Axial thrust balancing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/04Shafts or bearings, or assemblies thereof
    • F04D29/041Axial thrust balancing
    • F04D29/0413Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/04Shafts or bearings, or assemblies thereof
    • F04D29/046Bearings
    • F04D29/047Bearings hydrostatic; hydrodynamic
    • F04D29/0473Bearings hydrostatic; hydrodynamic for radial pumps
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02PCONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P21/00Arrangements or methods for the control of electric machines by vector control, e.g. by control of field orientation
    • H02P21/06Rotor flux based control involving the use of rotor position or rotor speed sensors
    • AHUMAN NECESSITIES
    • A61MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61MDEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M1/00Suction or pumping devices for medical purposes; Devices for carrying-off, for treatment of, or for carrying-over, body-liquids; Drainage systems
    • A61M1/10Blood pumps; Artificial hearts; Devices for mechanical circulatory assistance, e.g. intra-aortic balloon pumps
    • A61M1/101Non-positive displacement pumps, e.g. impeller, centrifugal, vane pumps
    • AHUMAN NECESSITIES
    • A61MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61MDEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M1/00Suction or pumping devices for medical purposes; Devices for carrying-off, for treatment of, or for carrying-over, body-liquids; Drainage systems
    • A61M1/10Blood pumps; Artificial hearts; Devices for mechanical circulatory assistance, e.g. intra-aortic balloon pumps
    • A61M1/101Non-positive displacement pumps, e.g. impeller, centrifugal, vane pumps
    • A61M1/1012Constructional features thereof
    • A61M1/1013Types of bearings
    • A61M1/1017Hydrodynamic bearings

Abstract

At least one drive unit among a first drive unit (9) and a second drive unit (9D) maintains an impeller (10) at a position in the center of the movement range of the impeller (10) inside a pump chamber (7) in a direction along the rotation axis by adjustment, through vector control, of an attractive force acting on the corresponding magnetic body among permanent magnet (17) and permanent magnet (17D). Consequently, even in the event of changes in flow velocity, rotation speed, pressure, and the like, the position of the impeller (10) in the axial direction can be adjusted while changes in rotation torque of the motor are suppressed. Consequently, a centrifugal pump device with improved impeller stability during floating rotation can be provided.

Description

Centrifugal pump device

The present invention relates to a centrifugal pump device, in particular, it relates to a centrifugal pump device which includes an impeller to send the liquid by centrifugal force upon rotation.

Recently, canned motor structure separated in the motor driving chamber and the rotor chamber is often used by the partition wall. Such motors are, for example, and transport pump chemical liquid or pure water for semiconductor manufacturing lines used in an environment averse dust, have been used to pump to transport biological fluids.

The JP 2010-261394 (Patent Document 1), a non-contact levitation of the impeller by the fluid dynamic bearing, the axial gap type centrifugal pump, characterized in canned motor structure is described. The axial gap type centrifugal pump, wherein the non-contact levitation of the impeller by the fluid dynamic bearing, so as to offset the axial direction attraction force acting between the impeller and the motor is disposed on the opposite side of the impeller and balancing the suction force of the axial direction by the ring-shaped permanent magnet or the like has.

However, the suction force due to such these permanent magnets, the impeller approaches in one direction, a component of the negative stiffness (uncertainties) to approaching more in that direction.

Further, for example, when the flow rate is large, the impeller pressure difference is generated in the circumferential direction under the influence of the position of the fluid outlet, eccentric in the radial direction. As a result, the difference between the suction force decrease amount of the ring-shaped magnet attraction force of the side decreased amount and the motor side is generated, and changes the balance of axial direction attraction, floating position of the axial direction of the impeller is offset from the center there has been a problem to put away.

Furthermore, often the fluid inlet is disposed on one side in the vicinity of the impeller center in centrifugal pumps. Floating position of the impeller there is a problem that deviates from the steady levitated position in the fluid force Again.

Thus, as a method for controlling the axial attractive force which is changed by eccentricity of the impeller, JP At 2010-261394 (Patent Document 1), so that the motor side suction force is balanced with the attraction force changes of the ring-like magnet portion the corresponded by adjusting the motor current phase. Thus, the impeller is also eccentric in the radial direction, it was possible to maintain stable rotation without changing the floating position of the axial direction of the impeller due to a disturbance, the operating condition.

JP 2010-261394 JP

As described above, the centrifugal pumps as described in JP-A-2010-261394, even eccentric impeller in the radial direction by the disturbance or operating conditions, stable without changing the floating position of the axial direction of the impeller to maintain the rotation, the motor side suction force is made to take measures such as adjusting the motor current phase to balance the attractive force variation of the ring-shaped permanent magnet portion.

But the fact that varying the motor current phase, there is a possibility that various problems occur. For example, when the current phase from the situation that has to operate the motor at the maximum efficiency point is changed, which may lead to decrease in the motor efficiency. Further, for example, varying the current phase from a situation that was operated at the maximum torque point, generated torque was a possibility of reduced degradation or motor step-out of the pump output.

In pump applications clean state is essential, the generation of pollutants by contact or the like between the inner wall of the impeller and the pump chamber, and its incorporation is required to reliably prevented. On the other hand, it decreases and the pump output reduction efficiency of the motor should be avoided as much as possible.

The present invention was made to solve the above problems, its object is to provide a centrifugal pump apparatus which can achieve both the prevention of reduction of pollution and efficiency and performance .

The invention comprises in summary, a centrifugal pump device, the housing including a first, second and third chamber. The second chamber is provided is sandwiched between the first chamber and the third chamber. The first chamber and the second chamber are partitioned by the first partition wall. The second chamber and the third chamber is partitioned by the second partition wall.

Centrifugal pump device further rotatably provided an axis intersecting the first and second partitions in the second chamber as a rotating shaft, an impeller sending a liquid by centrifugal force upon rotation, the first chamber provided, a first driving unit for rotationally driving the impeller through the first partition wall, provided in the third chamber, and a second drive unit for rotationally driving the impeller through the second partition wall, comprising a first magnetic body provided on one side face of the impeller opposite to the first partition, and a second magnetic body provided on the other side of the second partition wall opposed to the impeller. First dynamic pressure groove is formed on the wall surface of the first partition wall to one surface or opposite to that of the impeller. Second dynamic pressure grooves are formed on the wall surface of the second partition to the other side or opposite to that of the impeller. At least one of the first driving unit and the second driving portion is adjusted by the vector control, by the suction force acting on the magnetic material corresponding one of the first magnetic body and second magnetic body, the position of the impeller It is maintained in the middle of the movable range in the direction of the impeller along the rotation axis in the second chamber.

Preferably, the first drive unit, when the position of the impeller is changed in a direction away from the first partition wall from the center of the movable range increases the magnetic flux current in the vector control.

More preferably, the second drive unit, when the position of the impeller is changed in a direction away from the second partition wall from the center of the movable range increases the magnetic flux current in the vector control.

Preferably, during normal rotation of the impeller, when the first driving unit and the second driving portion is a high-efficiency drive acts between the first magnetic body and the first drive unit a first suction force, and a second magnetic body and the second suction force acting between the second drive unit, when the impeller in the center of the movable range of impeller in the second chamber is located balance.

Preferably, the centrifugal pump device further includes a phase estimator for estimating the rotation angle of the impeller for use in vector control.

More preferably, the centrifugal pump device, the fluid force acting on the impeller, the rotational speed of the impeller, the flow rate, discharge pressure, and at least one previously measured and stored and used as a parameter of the physical properties of the fluid further comprising a storage unit, a drive control unit for the storage unit to control the first suction force in response to values ​​stored to.

Preferably, a centrifugal pump apparatus further comprises a rotation detector for detecting the rotation angle of the impeller for use in vector control.

More preferably, the rotation detector is a magnetic sensor, detects the floating position of the impeller by the magnetic sensor.

Preferably, the third dynamic pressure grooves are formed on the side surface of the outer peripheral side of the impeller.
Preferably, a wall surface of the second chamber, the third dynamic pressure grooves are formed on the side surface opposite to the wall surface of the outer peripheral side of the impeller.

Preferably, a centrifugal pump device is used to circulate the food.
Preferably, a centrifugal pump device is used for circulating the pharmaceutical.

In the conventional configuration, the suction force of the drive motor side or a negative stiffness component of the axial direction of the suction force of the ring magnet side to offset it, had become unstable cause the impeller behavior.

In the present invention, separated into a torque current component electromagnetic force (Iq component) and the field current component (Id component) generated by the motor and (vector control), by actively changing the Id component, acting on the impeller make it possible to control the axial direction attraction, it is possible to enhance the stability during levitation rotation of the impeller.

It is an electric circuit diagram of a motor drive system of the centrifugal pump apparatus according to the present embodiment. It is a waveform diagram for explaining an output signal outputted from the PWM driver inverter. Is a control block diagram showing a motor control unit 324 a peripheral construction thereof in the motor drive system. A modification of FIG. 3 is a control block diagram showing a motor control unit 324A and its peripheral structure in the motor drive system when using the sensorless angle detection processing on the motor drive. It is a block diagram of a voltage equation of the motor. It is a vector diagram of a motor control. The appearance of the pump unit 1 of the centrifugal pump apparatus according to an embodiment of the present invention is a front view showing. It is a side view of the pump unit 1 shown in FIG. It is a sectional view taken along line IX-IX of Figure 8. It is a sectional view taken along line X-X of Figure 9. Is a sectional view showing a state in which removal of the impeller from FIG. Is a sectional view showing a state in which removal of the impeller from the sectional view taken along line XII-XII of Figure 9. Is a sectional view taken along line XIII-XIII of FIG. The size of the resultant force of the attraction force F2 between the attraction force F1 and the permanent magnet 17 and the magnetic body 18 between the permanent magnets 17D and the magnetic 18D is a position other than the center position of the movable range in the pump chamber 7 of the impeller 10 P1 in is a diagram showing the forces acting on impeller 10 when adjusted to zero. The size of the resultant force of the attraction force F2 between the attraction force F1 and the permanent magnet 17 and the magnetic body 18 between the permanent magnets 17D and the magnetic 18D is zero at the center position P0 of the movable range in the pump chamber 7 of the impeller 10 when adjusted to a diagram showing the forces acting on the impeller 10. It shows an arrangement of the magnetic sensor S for detecting the rotational speed during sectional view shown in FIG. 13. Is a time chart showing the output signal of the magnetic sensor shown in FIG. 16. It is a diagram showing a modification of the arrangement of the magnetic sensor. The output of the magnetic sensor is a diagram for explaining a control of feeding back the current in the coil. It is a waveform diagram for explaining a process for estimation of the angle from the magnetic sensor output. It is a schematic block diagram for explaining the process for performing sensorless control in the motor drive unit. Is a diagram showing the relationship between the flow rate and the floating position during rotation of the impeller. Is a diagram showing the relationship between the discharge pressure and the floating position during rotation of the impeller. It is a diagram showing a relationship between the engine speed and the raised position. Is a diagram showing the relationship between the current Id and the suction force. It is a diagram showing a modification of the configuration shown in FIG. It is a cross-sectional view taken along XXVII-XXVII in FIG. 26. It is a diagram showing a modified example further provided with a radial dynamic pressure groove on the outer peripheral surface of the impeller 10. It is a diagram showing a modified example further provided with a radial dynamic pressure groove in the pump chamber periphery. It is a diagram showing a first example of the formed dynamic pressure grooves on the outer circumferential surface of the shroud. It is a diagram showing a second example of the dynamic pressure grooves formed on the outer circumferential surface of the shroud. It is a diagram showing a first example of a specific configuration of the radial dynamic pressure groove formed in the pump chamber periphery. It is a diagram showing a second example of a specific configuration of the radial dynamic pressure groove formed in the pump chamber periphery. Is a diagram showing the detailed arrangement of the buried magnet shroud of the impeller 10. It is a first modification of the arrangement of the permanent magnets shown in FIG. 34. It is a second modification of the arrangement of the permanent magnets shown in FIG. 34. It is a third modification of the arrangement of the permanent magnets shown in FIG. 34. A fourth modification of the arrangement of the permanent magnets shown in FIG. 34. A fifth modification of the arrangement of the permanent magnets shown in FIG. 34.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Incidentally, the description thereof will not be repeated like reference numerals denote the same or corresponding portions in the drawings.

[Overview of the motor control circuit]
Figure 1 is an electric circuit diagram of a motor drive system of the centrifugal pump apparatus according to the present embodiment. 1, a motor drive system 300 includes a battery unit 310, an inverter device 320, and a motor section 331.

Motor unit 331, three-phase synchronous motor, for example SPM type (surface permanent magnet) synchronous motor, the rotor 332 includes a permanent magnet, and a stator including a stator coil of 3-phase. Rotation angle of the rotor 332 is detected by the angle detector 334.

The inverter device 320 includes a smoothing unit 328 for smoothing the DC voltage supplied from the battery unit 310, a three-phase inverter 330, and an arithmetic unit 322. Computing unit 322 includes a motor control unit 324, and a PWM driver 326.

3-phase inverter 330 is composed of six driving elements are semiconductor switching elements, and outputs the phase of the driving current of the three-phase motor (U, V, W-phase) in the pulse waveform.

Figure 2 is a waveform diagram for explaining the output signal outputted from the PWM driver inverter. For example, as shown in FIG. 2, PWM driver 326, a three-phase inverter 330 so that the current output to drive a sine wave is obtained by pulse width modulating the current command input, give off command to the six driving elements .

1, in the PWM driver 326 and the motor control unit 324, operation unit 322 is constituted a weak electric circuit portion of the inverter device 320. Calculation unit 322 is constituted by a computer and a program executed thereto, and electronic circuitry.

Figure 3 is a control block diagram showing a motor control unit 324 and its peripheral structure in the motor drive system. Referring to FIG. 3, the motor control unit 324 includes a current command calculation unit 340, a torque current control unit 341, a magnetic flux current controller 343, the αβ coordinate converting unit 350, a 2-phase / 3-phase conversion unit 352 includes a 3-phase / 2-phase conversion unit 354 of the detection side, and a rotation coordinate conversion unit 356.

Current calculation unit 340 includes a torque current command unit 362, and a flux current setting unit 364. Torque current command unit 362, in accordance with the torque command given from the host control means outputs a command value Iqref the torque current. The torque command is calculated by the rotational speed or the torque command or the like from the outside. Flux current setting unit 364 outputs a command value Idref defined magnetic flux current. Command value Idref flux current is appropriately set according to the characteristics of the motor or the like, normally is set to "0".

The torque current, hereinafter referred to as "q-axis current". In addition, the flux current, hereinafter referred to as "d-axis current". The flux current is also referred to as the excitation current or field current. For the voltage, the torque voltage referred to as "q-axis voltage", the magnetic flux voltage referred to as "d-axis voltage". Note that the q-axis is an axis that indicates the component of the motor rotational direction, d-axis is the direction of the axis orthogonal to the q-axis.

Torque current control unit 341 includes a subtraction unit 342 subtracts the q-axis current detection value Iq from the q-axis current command value Iqref, the arithmetic processing unit 346 for performing arithmetic processing determined for the output of the subtraction unit 342. Processing unit 346 performs a proportional integral processing in the example shown in FIG.

Torque current control unit 341, to the q-axis current command value Iqref given from the torque current command unit 362 of the specified current calculation unit 340 performs control to q-axis current detection value Iq to follow. q-axis current detection value Iq, the detection value Iu of the current detector 336, 337 for detecting the driving current of the motor, from Iv, obtained through the 3-phase / 2-phase conversion unit 354 and the rotating coordinate converter 356. Torque current control unit 341 outputs the q-axis voltage instruction value Vq.

Flux current control unit 343 includes a subtraction unit 344 subtracts the d-axis current detection value Id from the d-axis current command value Idref, and an arithmetic processing unit 348 for performing arithmetic processing determined for the output of the subtraction unit 344 . Processing unit 348 performs a proportional integral processing in the example shown in FIG.

Flux current control unit 343, to the d-axis current command value Idref given from the flux current setting unit 364 of the specified current calculation unit 340 is controlled so as to follow the d-axis current detection value Id. d-axis current detection value Id, the detection value Iu of the current detector 336, 337 for detecting the driving current of the motor, from Iv, obtained through the 3-phase / 2-phase conversion unit 354 and the rotating coordinate converter 356. Flux current control unit 343 outputs the d-axis voltage command value Vd.

3-phase / 2-phase conversion unit 354, the motor of the U-phase, V-phase, out of the current flowing through the W-phase, two, or three phases of current, for example, the current Iu of the U phase, the V phase current Iv the detected value, the detected value of (actual current on the actual current, and β axes on α-axis) the actual current of the stationary orthogonal two-phase coordinate components I.alpha, converted to I beta.

Rotation coordinate conversion unit 356, based on the motor rotor angle θmea detected by the angle detector 334, the detection value Iα of the actual current of the stationary orthogonal two-phase coordinate components, the I beta, q, detected value of the d-axis Iq, Id to convert to.

αβ coordinate converting unit 350, a q-axis voltage command value Vq and d-axis voltage instruction value Vd, motor rotor angle θ detected by the motor angle detector, that is based on the motor rotor phase, the command of the actual voltage of the stationary 2-phase coordinate components the conversion value Vα, to Vβ.

2-phase / 3-phase coordinate conversion unit 352, a command value of the actual voltage output from the αβ coordinate converting unit 350 V.alpha, the V?, The motor of the U-phase, V-phase voltage command value of three-phase AC to control the W-phase Vu , to convert Vv, to Vw.

PWM driver 326 and the three-phase inverter 330, the voltage command value output from the 2-phase / 3-phase coordinate conversion unit 352 as described above Vu, Vv, and power conversion and Vw motor driving currents Iu, Iv, and Iw Output.

Figure 4 is a modification of FIG. 3 is a control block diagram showing a motor control unit 324A and its peripheral structure in the motor drive system when using the sensorless angle detection processing on the motor drive.

4 shows a state of performing control using the motor rotor angle θest phase estimator 358 outputs are shown.

Hereinafter, perform equations described phase estimator 358 estimates the angle.
Equivalent motor equations shown in the following equation (1), in the d-q coordinate system is represented by the formula shown in equation (2). Formula shown is converted into more alpha-beta coordinate system equation shown in equation (2) (Equation 3) is obtained.

Figure JPOXMLDOC01-appb-M000001

Figure JPOXMLDOC01-appb-M000002

Figure JPOXMLDOC01-appb-M000003

Here, the resulting expression shown below (Expression 4) and expressed by using Iq the equation shown in equation (3). Phase estimator 358 based on this equation, an estimate of the angle of the motor rotor (phase theta).

Figure JPOXMLDOC01-appb-M000004

In the above formulas, R is armature winding resistance, Ld is a d-axis inductance, Lq is q-axis inductance, KE represents the induced voltage constant. R, Ld, Lq, KE is a known value, I.alpha, I beta is detected values, V.alpha, V? When is position estimation arithmetic value when the vector control is known. Therefore, it is possible to estimate the angle (phase) of the motor rotor.

Wherein for formula (Equation 1), it shows a block diagram and a vector diagram. Figure 5 is a block diagram of a voltage equation of the motor. Figure 6 is a vector diagram of a motor control.

In FIG. 6, d-axis and q-axis represents the magnetic pole direction of the permanent magnet. Armature flux linkage φa is on the d-axis. Further, Ldid and Lqiq the flux linkage components of the respective axes, the total flux linkage of the motor is found to be in FIGS. 6 .phi.0. Here, the input current ia is the combined current id and iq. Further, representative of the phase angle between the q-axis input current ia in beta. β denotes a current phase difference relative to the induced voltage ωφa without load.

Terminal voltage Va becomes a voltage obtained by adding the voltage drop Raia with an armature winding resistance Ra to V0. V0 is a voltage obtained by adding the electric reaction voltage ωLdid of each axis, the ωLqiq the induced voltage Omegafaiei. Phase difference between the voltage V0 and φ0 is 90 degrees.

From the vector diagram of FIG. 6, a field magnetic flux of the armature interlinkage magnetic flux φa is a permanent magnet, the magnetic flux of the armature reaction that influence the magnitude of the field flux is found to be Ldid. Since d-axis component affects the attraction force, controlling the id to zero will suppress the change in suction force. β is a zero, it would cause the phase of the current phase is matched with the induced voltage ωφa without load. In this case, the current vector ia will move the q-axis according to the load condition.

It can be seen that it is possible to vary the suction force by varying the d-axis component. Here dare controls the d-axis component, controls the suction force of the axial direction.

Before describing the details of control of the suction force, previously described basic structure of the pump unit below.

Description of the basic configuration of the pump unit]
By Figures 1 to 6 has been described motor control of the centrifugal pump apparatus of this embodiment. Next, a description will be given of a basic configuration of a pump unit of a centrifugal pump apparatus of this embodiment. Pump unit, as described below, since the install two motors, at least one motor, vector control of the motor described by Figures 1-6 is applied.

Figure 7 is a front view showing an appearance of a pump unit 1 of the centrifugal pump device according to the embodiment of this invention. Figure 8 is a side view of the pump unit 1 shown in FIG. Figure 9 is a sectional view taken along line IX-IX of Figure 8. Figure 10 is a sectional view taken along line X-X of Figure 9.

Referring to FIGS. 7 to 10, the pump unit 1 of the centrifugal pump device comprises a housing 2 made of a nonmagnetic material. The housing 2 includes a cylindrical body portion 3, a cylindrical inlet port 4 provided upright in the center of one end face of the main body portion 3, a cylindrical outlet port 5 provided on the outer peripheral surface of the main body portion 3 including the door. Outlet port 5 extends in a tangential direction of the outer peripheral surface of the body portion 3.

In the housing 2, as shown in FIG. 9, the pump chamber 7 and the motor chamber 8 and 8D partitioned by partition walls 6 and 6D are provided. The pump chamber 7, as shown in FIGS. 9 and 10, disc-shaped impeller 10 having a center through hole 10a is rotatably provided.

The impeller 10 includes a two shrouds 11 and 12 of the donut-shaped, and a vane 13 of a plurality formed between the two shrouds 11 and 12 (e.g., six). The shroud 11 is disposed on the partition wall 6D side inlet port 4 is formed, the shroud 12 is disposed on the partition wall 6 side. The shroud 11, 12 and vanes 13 are formed of a nonmagnetic material.

Between the two shrouds 11 and 12, the liquid passage 14 is formed of a plurality of partitioned by a plurality of vanes 13 (in this case six). Liquid passages 14, as shown in FIG. 10, is in fluid center communicates with the through hole 10a of the impeller 10, and the through hole 10a of the impeller 10 and the starting end and extends gradually broadening to the outer peripheral edge. In other words, the vanes 13 between two adjacent liquid passages 14 are formed. In this embodiment, a plurality of vanes 13 are provided at equal angular intervals, and formed in the same shape. Therefore, a plurality of liquid passages 14 is provided at equal angular intervals, and formed in the same shape.

When the impeller 10 is rotated, the liquid flowing from the inlet port 4 is sent to the outer periphery of the impeller 10 through the fluid passage 14 from the through hole 10a by centrifugal force, and flows out from the outlet port 5.

<Description of the dynamic pressure grooves>
Figure 11 is a sectional view showing a state in which removal of the impeller from FIG. Figure 12 is a sectional view showing a state in which removal of the impeller from the sectional view taken along line XII-XII of Figure 9.

11, as shown in FIG. 12, the surface of the partition wall 6 facing the shroud 12 of the impeller 10 a plurality of dynamic pressure grooves 21 are formed, a plurality of dynamic pressure grooves on the surface of the partition wall 6D facing the shroud 11 22 is formed. When the rotational speed of the impeller 10 exceeds a predetermined rotational speed, a hydrodynamic bearing effect generated between each impeller 10 of the dynamic pressure grooves 21 and 22. Thus, the dynamic pressure grooves drag is generated from each of the 21, 22 with respect to the impeller 10, the impeller 10 rotates without contacting a pump chamber 7. That is, the axial position of the impeller 10 is supported by the dynamic pressure grooves 21 and the dynamic pressure grooves 22.

In detail, a plurality of dynamic pressure grooves 21, as shown in FIG. 11, is formed in a size corresponding to the shroud 12 of the impeller 10. Respective dynamic pressure grooves 21 has one end from the center of the partition wall 6 on the peripheral edge slightly spaced circular portion (circumference), the vortex (in other words, curved with) to the vicinity of the outer edge of the partition wall 6, the width It extends so as to expand gradually. The plurality of dynamic pressure grooves 21 is substantially the same shape, and are disposed at substantially the same spacing. Dynamic pressure grooves 21 are concave, the depth of the dynamic pressure grooves 21 is preferably about 0.005 ~ 0.4 mm. The number of dynamic pressure grooves 21 is preferably 6 to 36 or so.

In Figure 11, 10 of the dynamic pressure grooves 21 are arranged at equal angles with respect to the center axis of the impeller 10. Dynamic pressure groove 21, since a so-called inward spiral groove shape, the impeller 10 rotates in the clockwise direction, the pressure of the liquid is increased toward the inner diameter from the outer diameter portion of the dynamic pressure grooves 21. Accordingly, repulsive force is generated between the impeller 10 and the partition wall 6, which is the dynamic pressure.

Thus, the hydrodynamic bearing effect formed between the impeller 10 and a plurality of dynamic pressure grooves 21, the impeller 10 is separated from the partition 6, to rotate in a non-contact state. Therefore, the liquid flow path is secured between the impeller 10 and the partition wall 6. Further, in the normal state, by the stirring action and the flow of liquid by the pressure difference between the impeller and outside diameter resulting in pump operation between the impeller 10 and the partition wall 6 by the dynamic pressure grooves 21 (leak rate), partially between them occurrence of liquid retention can be prevented such.

Further, a corner portion of the dynamic pressure grooves 21 are preferably rounded to have at least 0.05mm or more R.

The plurality of dynamic pressure grooves 22, as shown in FIG. 12, similar to the plurality of dynamic pressure grooves 21 are formed in a size corresponding to the shroud 11 of the impeller 10. Respective dynamic pressure grooves 22 has one end from the center of the inner wall of the pump chamber 7 on the periphery (circumference) of slightly spaced circular portion (in other words, curved with) the spiral inner wall of the pump chamber 7 to the vicinity of the outer edge, and it extends so that the width is widened gradually. The plurality of dynamic pressure grooves 22 is substantially the same shape, and are disposed at substantially the same intervals. Dynamic pressure grooves 22 are concave, the depth of the dynamic pressure grooves 22 is preferably in the order of 0.005 ~ 0.4 mm. The number of dynamic pressure grooves 22 is preferably 6 to 36 or so. In Figure 12, 10 of the dynamic pressure grooves 22 are arranged equiangularly with respect to the center axis of the impeller 10.

The portion of the corner of the dynamic pressure grooves 22 are preferably rounded to have at least 0.05mm or more R.

Thus, the hydrodynamic bearing effect formed between the impeller 10 and a plurality of dynamic pressure grooves 22, the impeller 10 is spaced from the inner wall of the pump chamber 7, rotates in a non-contact state. Further, and when the pump unit 1 is subjected to external impact, when the dynamic pressure by the dynamic pressure grooves 21 has become excessive, it is possible to prevent adhesion to the inner wall of the pump chamber 7 of the impeller 10. Dynamic pressure generated by the dynamic pressure and the dynamic pressure grooves 22 generated by the dynamic pressure grooves 21 may be made different.

However, the gap between the shroud 12 and the partition wall 6 of the impeller 10, it is preferred that the impeller 10 rotates at substantially the same state with a gap of the shroud 11 and the partition wall 6D of the impeller 10. Large disturbance such as fluid force acting on the impeller 10, when one of the gaps is narrower, greater than the dynamic pressure dynamic pressure due to the narrow side of the dynamic pressure grooves by the other of the dynamic pressure grooves, both gaps for substantially the same, it is preferable to vary the shape of the dynamic pressure grooves 21 and 22.

In FIG. 11 and FIG. 12, although the respective dynamic pressure grooves 21 and 22 inward spiral groove shape, it is also possible to use the dynamic pressure grooves 21 and 22 of other shapes.

<Description of the arrangement of the permanent magnets and coils>
With reference to FIGS. 9 and 10 again, the permanent magnet 17 of the plurality (e.g., eight) is embedded in the shroud 12. A plurality of permanent magnets 17, as adjacent magnetic poles are different from each other, are disposed with a gap at equal angular intervals along the same circle. In other words, the permanent magnet 17 with its N pole on the motor chamber 8 side, a gap is provided alternately along the same circle a permanent magnet 17 transgression equal angular intervals toward an S-pole in the motor chamber 8 side It is located.

Figure 13 is a sectional view taken along line XIII-XIII of FIG. Referring to FIGS. 9 and 13, the motor chamber 8, the coil 20 of a plurality (e.g., nine) is provided. A plurality of coils 20, in opposition sandwiching the partition wall into a plurality of permanent magnets 17 of the impeller 10, at equal angular intervals are arranged along the same circle. Coil 20, the coil wire around a core portion, magnetic bodies are disposed (the magnetic body 18) is wound.

However, the coils inside the magnetic body 13 may be a laminated steel plates, it may be a powder magnetic core and other magnetic material.

Further, although not shown, the core portion may be air core.
On the opposite side of the partition wall 6 of the plurality of coils 20 arranged magnetic body 19 serving as a back yoke, it is increasingly flux of the coil 20. It should be noted that the back yoke may be omitted.

The nine coils 20, a voltage is applied, for example, 120-degree energization method. That is, nine coils 20 are grouped three by three. The first to third coils 20 of each group, U-phase, V-phase, three-phase voltage VU of W-phase, VV, VW is applied. The first coil 20, 0 in a period of ~ 120 ° positive voltage is applied, the 0V is applied to the period of 120 to 180 degrees, a negative voltage is applied to a period of 180-300 degrees, 300-360 degrees 0V is applied to the period. Therefore, the end surface of the first coil 20 (the end surface of the impeller 10 side) becomes the N pole in a period of 0 to 120 degrees, the S pole in a period between 180 and 300 degrees. Phase voltage VV is delayed 120 degrees than the voltage VU, the phase of the voltage VW is delayed 120 degrees than the voltage VV. Thus, each voltage VU to the first to third coil 20, VV, by applying the VW, it is possible to form a rotating magnetic field, the attraction force between the plurality of permanent magnets 17 of the plurality of coils 20 and the impeller 10 and by the repulsive force, it is possible to rotate the impeller 10.

A plurality of permanent magnets 17D are provided in the shroud 11, the motor chamber 8D is also provided on the shroud 11 side of the housing 2. Motor chamber 8D and the pump chamber 7 is partitioned by a partition wall 6D. The motor chamber 8D, plurality of coils 20D are provided to face the plurality of permanent magnets 17D. A plurality of coils 20D, each is wound around the magnetic body 18D. The opposite side of the partition wall 6D of the plurality of coils 20D disposed magnetic 19D serving as a back yoke, are increasingly flux of the coil 20D. It should be noted that the back yoke may be omitted.

The arrangement of the arrangement and a plurality of coils 20D of the plurality of permanent magnets 17D are not repeated basically detail because it is similar to the arrangement of the permanent magnets 17 and the coil 20 shown in FIGS. 9 and 10 described.

14, the magnitude of the resultant force of the attraction force F2 between the attraction force F1 and the permanent magnet 17 and the magnetic body 18 between the permanent magnets 17D and the magnetic 18D is a central position of the movable range of the pump chamber 7 of the impeller 10 is a diagram illustrating the forces acting on impeller 10 when adjusted to zero at the position P1 outside. However, the rotational speed of the impeller 10 is maintained at the rated value.

The horizontal axis of FIG. 14 shows the position of the impeller 10 (the left side partition wall 6 side in the figure), the vertical axis represents the force acting against the impeller 10. When the force acting on the impeller 10 acts on the partition wall 6 side to the acting force negative. The acting force against the impeller 10, a suction force F1 between the permanent magnets 17D and the magnetic 18D, and the suction force F2 between the permanent magnets 17 and the magnetic body 18, a hydrodynamic pressure F3 of the dynamic pressure grooves 21, the dynamic pressure grooves 22 a hydrodynamic pressure F4 of showed "net force acting on the impeller F5" is their force.

Suction force F1 between the permanent magnets 17D and the magnetic 18D is set smaller than the suction force F2 between the permanent magnets 17 and the magnetic body 18, floating position of the impeller 10 that their resultant force is zero than the middle of the impeller the movable range It assumed to be in the partition wall 6 side. The shape of the dynamic pressure grooves 21 and 22 are the same.

As it can be seen from Figure 14, at a position where the net force F5 acting on impeller 10 becomes zero, floating position of the impeller 10 is deviated from the center position of the movable range of impeller 10. As a result, the distance between the impeller 10 and the partition wall 6 during rotation narrows, the impeller 10 also act small disturbance force to the impeller 10 would be in contact with the partition wall 6.

Figure 15 contrast, the magnitude of the resultant force of the attraction force F2 between the attraction force F1 and the permanent magnet 17 and the magnetic body 18 between the permanent magnets 17D and the magnetic 18D is movable in the pump chamber 7 of the impeller 10 when adjusted to the range zero at the center position P0 of a diagram showing the forces acting on the impeller 10. Again, the rotational speed of the impeller 10 is maintained at the rated value.

That is set substantially the same as the suction force F2 between the attraction force F1 and the permanent magnet 17 and the magnetic body 18 between the permanent magnets 17D and the magnetic 18D. The shape of the dynamic pressure grooves 21 and 22 are the same. The case shown in FIG. 15, as compared with the case of FIG. 14, the support rigidity for the floating position of the impeller 10 is increased. Further, since the net force F5 acting on impeller 10 has a zero at the center of the movable range, if the relative impeller 10 disturbance force does not act on the impeller 10 floats at a central location.

Thus, floating position of the impeller 10, a suction force F1 between the permanent magnets 17D and the magnetic 18D, and the suction force F2 between the permanent magnets 17 and the magnetic body 18, movement during rotation of the impeller 10 grooves 21, 22 in determined by the balance between the dynamic pressure F3, F4 generated. Substantially the same west of F1 and F2, by the same shape of the dynamic pressure grooves 21 and 22, it is possible to float the impeller 10 in a substantially central portion of the pump chamber 7 during rotation of the impeller 10. As shown in FIGS. 9 and 10, the impeller 10 because it has a shape forming a blade between the two disks, it can be the two surfaces facing the inner wall of the housing 2 in the same shape and the same dimensions. Therefore, it is possible to provide a dynamic pressure grooves 21 and 22 having substantially the same dynamic pressure performance on both sides of the impeller 10.

In this case, the impeller 10 is so floats at the center position of the pump chamber 7, the impeller 10 is held in equally distant from the partition wall 6 and 6D of the pump chamber 7 of the housing 2. As a result, the disturbance force is applied to the impeller 10 during floating of the impeller 10, be varied floating position of the impeller 10 is a possibility that the inner wall of the impeller 10 and the housing 2 are in contact decreases.

Control of the impeller position of the pump unit]
Then, having a structure as described above, it will be described the application of vector control for adjusting the axial position of the impeller of the pump that the dynamic pressure grooves are formed on the inner wall of the pump room.

Figure 16 is a view showing the arrangement of the magnetic sensor S for detecting the rotational speed during sectional view shown in FIG. 13. Figure 17 is a time chart showing an output signal of the magnetic sensor shown in FIG. 16.

Referring to FIG. 16, it is provided between the three of the four magnetic bodies 18 which three magnetic sensor S adjacent the nine magnetic body 18. Three magnetic sensors S are placed opposite the passage path of the plurality of permanent magnets 17 of the impeller 10. When the impeller 10 passes near the magnetic sensor S alternately S and N poles of the plurality of permanent magnets 17 rotates, the level of the output signal of the magnetic sensor S, as shown in FIG. 17, varies sinusoidally to. Therefore, by detecting the time variation of the output signal of the magnetic sensor S, it is possible to detect the positional relationship between the plurality of permanent magnets 17 and a plurality of magnetic bodies 18, and when current flows into a plurality of coils 20, it can be determined rotational speed of the impeller 10.

Further, when the gap between the impeller 10 and the partition wall 6 is wide, the amplitude A1 of the output signal of the magnetic sensor S and the magnetic field in the vicinity of the magnetic sensor S becomes weak decreases. If the gap between the impeller 10 and the partition wall 6 is narrow, the amplitude A2 of the output signal of the magnetic sensor S and the magnetic field in the vicinity of the magnetic sensor S becomes stronger the greater.

Therefore, by detecting the amplitude of the output signal of the magnetic sensor S, it is possible to detect the position of the impeller 10 within the movable range of the axial direction of the impeller 10.

Figure 18 is a diagram showing a modification of the arrangement of the magnetic sensor. In this modification, nine coils 20 are divided into three by three groups, three magnetic sensors S are disposed respectively between the three three groups. Thus, the mechanical angle between the three magnetic sensors S, since the respective 120 degrees, can easily be calculated the floating posture of the impeller 10 in rotation. The timing to flow a current into nine coils 20 is calculated based on the output signal of one of the magnetic sensors S of the three magnetic sensors S.

By placing the magnetic sensor as shown in FIG. 18, to separate the translation (parallel movement) and rotation of the impeller (tilt), can be detected more accurately floating position.

Figure 19 is a diagram for explaining the control for feeding back the output of the magnetic sensor to the current in the coil. For simplicity of understanding, it is also shown in cross-sectional view of the pump in FIG. 19 to simplify the Figure 3. The controller 42 includes a position calculator 49, a rotational speed calculator 50, a position determining unit 51, a rotation angle estimator 48, and a motor control circuit 43,43D, a power amplifier 44,44D. Rotational speed calculator 50 calculates the rotational speed of the impeller 10 on the basis of the output signals of three magnetic sensors S, and outputs a signal φR indicating the rotational speed. Position determining unit 51, based on a signal φP indicating the position of the impeller 10 generated by the position calculator 49, and a signal φR indicating the rotational speed of the impeller 10 generated by the rotational speed calculation unit 50, the position of the impeller 10 it is determined whether or not within the normal range, and outputs a signal φD indicating the determination result. To refer to rotational speed of the impeller 10 during determination, dynamic pressure bearing effect of the dynamic pressure grooves 21 and 22 vary with the rotational speed of the impeller 10, the position of the impeller 10 is changed, and generates the impeller by rotational speed fluid force is because changes. In the case where the rotation speed is fixed, the rotation speed calculation unit 50 may be removed.

Further, if the position of the impeller 10 to determine whether the normal range, instead rotational speed of the impeller 10, or in addition to the rotational speed of the impeller 10, may refer to viscosity data of the liquid. This dynamic pressure bearing effect of the dynamic pressure grooves 21 and 22 vary with the viscosity of the liquid is because the position of the impeller 10 is changed.

Further, since the centrifugal pump device, hydrodynamic bearing effect of the case where the impeller 10 is not rotating dynamic pressure groove 21, 22 is not generated, the suction force F1 between the permanent magnets 17D and the magnetic 18D, the permanent magnet We are in contact with the inner wall of the impeller 10 and the housing 2 by the suction force F2 between 17 and magnetic body 18. Therefore, in the starting rotation and at low-speed rotation, the impeller 10 is not rotating in the normal axial position. Therefore, if you do not use a signal φR indicating the rotational speed position determination for a predetermined time with the start of rotation to reach the rated speed, it is normal position of forcibly impeller 10 an output signal φD position determinator 51 it may be a signal indicating that.

Figure 20 is a waveform diagram for explaining a process for estimation of the angle from the magnetic sensor output. Rotation angle estimator 48 shown in FIG. 19, specifically includes a multiplication processing section, using at least one or more output signals of the magnetic sensors, for example based on the zero cross position of the magnetic sensor output signal 20 It generates a rotational synchronization pulse, performs estimation of the angle of the motor rotor which was generating a multiplied pulse by multiplying.

Then, based on the relationship shown in FIG. 17, estimates the axial position of the impeller 10 from the amplitude of the magnetic sensor output signals, in accordance with the axial position, the suction force using a motor control circuit 43 or the motor control circuit 43D adjust. Note the adjustment of the suction force is believed to control the following three patterns.

The first is a control to lower the suction force or by changing the Id component of only one of the motor control circuit 43,43D. The second is a control to increase the suction force by changing either Id component of only one of the motor control circuit 43,43D. Third, along with by changing either Id component of the motor control circuit 43,43D lowering the suction force is controlled to increase the attraction force by changing the other Id component of the motor control circuit 43,43D.

Figure 21 is a schematic block diagram for explaining the process for performing sensorless control in the motor drive unit. For simplicity of understanding, it is also shown in cross-sectional view of the pump in FIG. 21 to simplify the drawing 4. Referring to FIG. 21, the impeller attitude determination unit 70 rotational speed N of the controller 42A, flow J, enter at least one or more information of the discharge pressure P, and the fluid information (physical property values) Y. The storage unit 71, an impeller behavior measured in advance under various conditions are stored. Based on the information stored in the storage unit 71, controls the Id component of the motor drive current to rotate by floating the impeller in a substantially central position.

When starting the pump operation the impeller acts fluid force. In the configuration shown in FIGS. 7 to 9, to the inlet (entrance) is axially, in the form asymmetry due to a side one position, the flow rate, the rotational speed is increased impeller moves to the inlet side.

The pressure balance around the impeller outlet (opening 7a) is due to asymmetry of the shape which is one position in the circumferential direction as shown in FIG. 10, the impeller 10 is moved to the outlet (opening 7a) side. At this time, if the suction force in the axial directions are different due to the eccentricity of the impeller 10, the impeller is displaced in the axial direction.

Figure 22 is a diagram showing a relationship between the flow rate and the floating position during rotation of the impeller. Previously, if examine such a relationship can flow J1 is to obtain a shift amount d1 of floating position if known. Figure 23 is a diagram showing the relationship between the discharge pressure and the floating position during rotation of the impeller. Previously, if examine this relationship can be the discharge pressure P2 to obtain a displacement amount d2 of floating position if known. It should be noted that on the experience, greater than the impact effect on the flow rate to the discharge pressure. Figure 24 is a diagram showing a relationship between the engine speed and the floating position. When rotation is stopped does not have dynamic pressure generation, the impeller is in contact with either the partition wall, the impeller by the balance of the upper and lower dynamic pressure and the magnetic attraction force between the impeller starts rotating floats in a central position. The rotation speed increases again, the flow rate or discharge pressure increases impeller is displaced axially. Previously, if examine such a relationship, it is possible rotational speed N3 is to obtain a displacement amount d3 of floating position if known.

Figure 25 is a diagram showing the relationship between the attraction force and the current Id. A pump device of the present embodiment, low flow time when Id component is zero, the impeller take a vertical force balance flies in a central position. In Id component zero state, the motor drive unit are generated magnetic attraction force. As the flow rate increases, if the impeller levitation position is shifted, by increasing and decreasing the Id component, it is possible to change the suction force of the motor drive unit. From the relationship of FIGS. 22 to 24, amount of displacement of the impeller levitation position, this to vary the suction force so as to correspond, it is sufficient to increase or decrease the Id component according to the relationship of FIG. 25.

[Various Modifications]
Figure 26 is a diagram showing a modification of the configuration shown in FIG. Figure 27 is a cross-sectional view taken along XXVII-XXVII in FIG. 26. In this variation, the teeth 18A on the tip of the core (magnetic body 18,18D), 18B are arranged. Figure 26 is the side that the rotor facing the stator in FIG. 9, there is shown a configuration in which is arranged as a magnetic material spread area. Thus since the opposing area between the rotor of the permanent magnet can be widely ensured, the motor output, the improvement of the motor efficiency can be improved.

Figure 28 shows a further modified embodiment in FIG. 29 (add radial dynamic pressure groove). Figure 28 is a diagram showing a modified example in which a further radial dynamic pressure groove on the outer peripheral surface of the impeller 10. Figure 29 is a diagram showing a modified example further provided with a radial dynamic pressure groove in the pump chamber periphery. Thus, it is possible to secure the resistance to outer disturbance property, it becomes possible to stabilize rotation of the impeller. Processability than processing for forming a dynamic pressure grooves 161 and 162 to the inner peripheral surface of the pump chamber 7 as shown in FIG. 29 to form a dynamic pressure grooves 61 and 62 on the outer peripheral surface of the impeller 10 as shown in FIG. 28 good. Example shown in FIG. 28 can be further ensured example as well as resistance to outer disturbance resistance shown in FIG. 29, it is possible to stabilize rotation of the impeller.

<Configuration Example of the radial dynamic pressure groove provided in the shroud outer peripheral surface of the impeller>
Figure 30 is a diagram showing a first example of the dynamic pressure grooves formed on the outer circumferential surface of the shroud. Figure 31 is a diagram showing a second example of the dynamic pressure grooves formed on the outer circumferential surface of the shroud.

Referring to FIG. 30, the dynamic pressure grooves 61 and 62 are formed on the outer peripheral surface of the shroud 11, 12, respectively. The tip of the dynamic pressure grooves 61 and 62 is directed in the direction of the rotational direction opposite to the impeller 10. When the impeller 10 rotates in the direction of the arrow, the pressure of the liquid is increased toward the tip portion of the dynamic pressure grooves 61 and 62. Accordingly, repulsive force is generated between the impeller 10 and the inner peripheral surface of the pump chamber 7, which is the dynamic pressure.

In the second example shown in FIG. 31, the dynamic pressure grooves 64 and 65 rather than the inner peripheral surface of the pump chamber 7, are formed on the outer peripheral surface of each shroud 11, 12. Each of the depth of the dynamic pressure grooves 64 and 65, is gradually shallower toward a rotational direction opposite to the direction of the impeller 10. In this modification, when the impeller 10 rotates in the direction of the arrow, the pressure of the liquid is increased toward the tip portion of the dynamic pressure grooves 64 and 65. Accordingly, repulsive force is generated between the impeller 10 and the inner peripheral surface of the pump chamber 7, which is the dynamic pressure.

<Configuration Example of the radial dynamic pressure groove provided in the pump chamber circumference>
Figure 32 is a diagram showing a first example of a specific configuration of the radial dynamic pressure groove formed in the pump chamber periphery. In Figure 32, the region facing the outer circumferential surface of the shroud 11 of the inner peripheral surface of the pump chamber 7, V-shaped dynamic pressure grooves 161 are formed at a predetermined pitch in the rotating direction of the impeller 10. The tip of the V-shaped dynamic pressure grooves 161 (acute angle portion) is oriented in the direction of rotation of the impeller 10. Similarly, the region facing the outer circumferential surface of the shroud 12 of the inner peripheral surface of the pump chamber 7, the dynamic pressure grooves 162 of the V-shape is formed at a predetermined pitch in the rotating direction of the impeller 10. The tip of the V-shaped dynamic pressure grooves 162 (acute angle portion) is oriented in the direction of rotation of the impeller 10. The region facing the gap of the shroud 11, 12 of the inner peripheral surface of the pump chamber 7, a groove 63 having a predetermined depth is formed in a ring shape. When the impeller 10 rotates in the direction of the arrow, the pressure of the liquid is increased toward the tip portion of the dynamic pressure grooves 161 and 162. Accordingly, repulsive force is generated between the impeller 10 and the inner peripheral surface of the pump chamber 7, which is the dynamic pressure.

Figure 33 is a diagram showing a second example of a specific structure of the radial dynamic pressure groove formed in the pump chamber periphery. In the modification shown in FIG. 33, the dynamic pressure grooves 161 and 162 are replaced by each dynamic pressure generating grooves 164, 165. Each of the dynamic pressure grooves 164 and 165 are formed in a band shape and extends in the direction of rotation of the impeller 10. Each of the depth of the dynamic pressure grooves 164 and 165 are gradually shallower toward the rotational direction of the impeller 10. In this modification, when the impeller 10 rotates in the direction of the arrow, the pressure of the liquid is increased toward the tip portion of the dynamic pressure grooves 164 and 165. Accordingly, repulsive force is generated between the impeller 10 and the inner peripheral surface of the pump chamber 7, which is the dynamic pressure.

Finally, again summarized with reference to the drawings this embodiment. Referring mainly to FIG. 9, a centrifugal pump device according to the present embodiment includes a housing containing a pump chamber 7 and the motor chamber 8,8D. The pump chamber 7 is provided sandwiched motor chamber 8 and the motor chamber 8D. Motor chamber 8 and the pump chamber 7 partitioned by the partition walls 6. Pump chamber 7 and the motor chamber 8D is partitioned by the partition wall 6D.

Centrifugal pump device further rotatably provided an axis intersecting the first and the partition wall 6D in the pump chamber 7 as a rotation axis, the impeller 10 sends the liquid by centrifugal force upon rotation, the motor chamber 8 provided, a first drive unit 9 the impeller 10 is rotated through the septum 6 (coil 20), provided in the motor compartment 8D, a second drive unit for rotatably driving the impeller 10 through the partition wall 6D comprises a 9D (coil 20D), a permanent magnet 17 provided on one side face of the impeller 10 facing the partition wall 6, and a permanent magnet 17D provided on the other surface of the impeller 10 facing the partition wall 6D.

The first dynamic pressure groove (dynamic pressure grooves 21) are formed on the wall surface of the partition walls 6 to one surface or opposite to that of the impeller 10. Second dynamic pressure grooves (dynamic pressure grooves 22) are formed on the wall surface of the partition wall 6D of the other side or opposite to that of the impeller 10.

At least one of the first driving member 9 and the second drive unit 9D is adjusted by the vector control, suction force acting on the corresponding magnetic of the permanent magnet 17 and the permanent magnet 17D (e.g. F2 in FIG. 15) by maintaining the position of the impeller 10 in the center of the movable range in the direction of the impeller 10 along the rotary shaft in the pump chamber 7. Thus, the flow rate, rotational speed, even if such pressure is changed, while suppressing the variation of the rotational torque of the motor, it is possible to adjust the position of the axial direction of the impeller 10.

Preferably, as explained in FIGS. 22 to 25, the first drive unit 9, when the position of the impeller 10 is changed in a direction away from the partition wall 6 from the center of the movable range, the magnetic flux current Id in the vector control increase.

More preferably, the second driving unit. 9D, when the position of the impeller 10 is changed in a direction away from the partition wall 6D from the center of the movable range increases the magnetic flux current Id in the vector control.

Note that when increasing the magnetic flux current Id in the first driving portion 9, such as to reduce the magnetic flux current Id in the second driving portion 9D, complementary to the first drive unit 9 relative to the second drive unit 9D it may be performed Do not control.

Thus, the axial position of the impeller 10 since the suction force of the driving section 9,9D increases back to the center.

Preferably, as shown in FIG. 15, during normal rotation of the impeller 10, when the drive unit 9,9D is a high-efficiency drive, between the permanent magnet 17D and the second driving portion 9D first suction force F1 acting, the permanent magnet 17 and the second suction force F2 acting between the first driving unit 9, the center (point of the movable range of impeller 10 in pump chamber 7 P0 ) the balance when the impeller 10 is located.

Preferably, as shown in FIG. 4, a centrifugal pump device further includes a phase estimator 358 for estimating the rotation angle of the impeller 10 for use in vector control.

Preferably, as shown in FIG. 21, a centrifugal pump device, the fluid force acting on the impeller 10, the rotational speed N of the impeller 10, the flow rate J, the discharge pressure P, and the fluid of the fluid information Y, such as physical properties of at least one of a storage unit 71 for storing the results of previously measured using as a parameter, the drive control unit which controls the second suction force (Id component command generated according to the value storage unit 71 stores the out further comprising a section 74) and.

Preferably, a centrifugal pump apparatus further comprises a rotation detector for detecting the rotation angle of the impeller 10 for use in vector control. As shown in FIGS. 16 to 18, more preferably, the rotation detector is a magnetic sensor S, for detecting the floating position of the impeller 10 by the magnetic sensor.

Preferably, as shown in FIGS. 28 to 29, on the side surface of the outer peripheral side of the impeller 10, the dynamic pressure grooves 61 and 62 or the dynamic pressure grooves 64 and 65 are formed.

Preferably, 30, 32, as shown in FIG. 33, a wall surface of the pump chamber 7, on the outer peripheral side surface opposite to the wall surface of the impeller 10, the dynamic pressure grooves 161 and 162, or the dynamic pressure grooves 164 , 165 are formed.

<Configuration example of an arrangement of permanent magnets>
Figure 36 is a diagram showing a first example of a specific configuration of the arrangement of the permanent magnets. Referring to FIG. 36, the permanent magnets 17 of the plurality (e.g., eight) is embedded in the shroud 12. A plurality of permanent magnets 17, as adjacent magnetic poles are different from each other, are disposed with a gap at equal angular intervals along the same circle. In other words, the permanent magnet 17 with its N pole on the motor chamber 8 side, a gap is provided alternately along the same circle a permanent magnet 17 transgression equal angular intervals toward an S-pole in the motor chamber 8 side It is located.

In the modification of FIG. 37 (a) (b), a plurality of permanent magnets 17 and a plurality of permanent magnets 67 are provided in the impeller 10. The number of the permanent magnets 67 is the same as the number of the permanent magnets 17. Permanent magnets 67 are magnetized in the circumferential direction (rotational direction of the impeller 10). The plurality of permanent magnets 17 and a plurality of permanent magnets 67 are arranged in a Halbach array structure along the same circle at equal angular intervals alternately one by one. In other words, the permanent magnet 17 with its N pole on the partition wall 6 side, are alternately arranged along the same circle a gap of a permanent magnet 17 transgression equal angular intervals toward an S-pole on the partition wall 6 side there. N pole of the permanent magnet 67 is disposed toward the permanent magnet 17 with its N pole on the partition wall 6 side, the S pole of the permanent magnet 67 is directed toward the permanent magnet 17 with its S pole on the partition wall 6 side It is. Between the shape of the plurality of permanent magnets 17 have the same shape between the plurality of permanent magnets 67 are the same. Shape between the permanent magnets 67 of the permanent magnets 17 may be the same or may be different. In this modification, it is possible to suppress the suction force of the permanent magnet 17 and the coil 20, it is possible to enhance the magnetic flux as a result of the torque, it is possible to reduce the size of the most permanent magnet. In other words, it is possible to most lightweight impeller 10, and it is possible to enhance the energy efficiency, even if the motor gap is wide.

In another modification shown in FIG. 38, (shroud 12 of the impeller 10) rotor includes a permanent magnet 17A magnetized in the rotation axis direction, the circumferential direction magnetized permanent magnet 67A and the magnetic body 70A They are out. Permanent magnets 17A are arranged so that the direction of the magnetic poles of the adjacent magnets are different, is further arranged such permanent magnets 67A approaches the same magnetic poles of the permanent magnet 17A in the partition wall 6 side end face of the permanent magnet 17A.

Permanent magnets 17A and the permanent magnet 67A is the same number. Magnetizing direction length of the permanent magnet 67A is shorter than the width of the permanent magnet 17A, a gap a central magnetizing direction length of the permanent magnet 67A when the circumferential direction coincide with the boundaries of the magnet adjacent permanent magnets 17A It can, placing a magnetic body 70A in the gap. In this case, it is the magnetic flux is focused on the magnetic body 70A, as compared with the configuration of the structure (FIG. 37) in the absence of magnetic material and conventional Halbach array, achieving high torque stronger field magnetic flux can be obtained. In still arrangement of FIG. 38, it is possible to suppress the permanent magnets 17A, a decrease in permeance coefficients of 67A.

Figure 39 is in the configuration of FIG. 38, it is arranged magnetic body 72 on the end face of the partition wall 6 of the permanent magnets 17A opposite. It can be strengthened further flux by the effect of the magnetic body 72.

Figure 40 shows another magnet arrangement. In canned motor having a partition wall 6 between the stator and the rotor, the rotor and the permanent magnets 17B, which are magnetized in the rotation axis direction, consists circumferentially magnetized permanent magnet 67B and the magnetic body 70B, permanent magnet 17B have different orientations of the magnetic poles of the adjacent magnets are arranged with a gap, the permanent magnet 67B is arranged partition wall 6 side into the gap. When placing a magnet in a limited space, the structure can be greater than 38 permeance coefficient for flattening of the permanent magnet 17B is reduced. Permanent magnet 17B and the permanent magnet 67B is the same number. Permanent magnets 67B are magnetized in the circumferential direction (rotational direction of the rotor). The plurality of permanent magnets 17B and a plurality of permanent magnets 67B, are arranged in a Halbach array structure along the same circle at equal angular intervals alternately one by one. In other words, the permanent magnet 17B with its N pole on the partition wall 6 side, are alternately arranged along the same circle a gap in the permanent magnet 17B Hitoshi Toga angular intervals toward an S-pole on the partition wall 6 side there. N pole of the permanent magnet 67B is arranged toward the permanent magnet 17B with its N pole on the partition wall 6 side, the S pole of the permanent magnet 67B is arranged toward the permanent magnet 17B with its S pole on the partition wall 6 side It is. A shape among a plurality of permanent magnets 17B identical shape between the plurality of permanent magnets 67B are the same. The axial length of the permanent magnet 17B is shorter than the width of the permanent magnet 67B, when placed, to allow a step on the partition wall 6 side, placing a magnetic body 70B to the step portion. In this case also focused magnetic flux in the magnetic 70B, configuration in the absence of magnetic material and conventional Halbach array compared with (FIG. 36), a stronger field magnetic flux can be made high torque obtained. Further permanent magnets 17B, it is possible to suppress the reduction of the permeance coefficient of 67B.

Configuration shown in FIG. 41, in the configuration of FIG. 40, it is arranged magnetic body 72 on the end face of the partition wall 6 of the permanent magnet 17B opposite. It can be strengthened further flux by the effect of the magnetic body 72.

Further, a plurality of permanent magnets 17 which are embedded in the shroud 12, as adjacent magnetic poles are different from each other, may be arranged without providing the gap at equal angular intervals along the same circle.

As described above, in this embodiment, in the axial gap type centrifugal pump, wherein the non-contact levitation of the impeller by the fluid dynamic bearing, the use of vector control as a motor driving method, torque current component ( was separated into Iq component) field current component and (Id component).

Then, while the field current component to maintain the rotational torque of the motor only (Id component) to be changed aggressively, and controls the axial direction attracting force exerted on the impeller. Thus, it is possible to control the floating position of the impeller can always be stabilized floating near the center of the movable range.

In the above embodiment, since the two driving units 9,9D is arranged so as to sandwich the impeller, when the drive unit is compared with what is only one, it is possible to generate a larger torque. Further, by magnetic material opposed to the first drive unit 9 the second driving unit 9D and each of the constitution (permanent magnet) in the same, it is easy to balance the magnetic attraction force.

Incidentally, the centrifugal pump device in the above embodiment may be used to circulate the food. Further, centrifugal pump device of the above embodiment may be used to circulate a medicament.

The embodiments disclosed herein are to be considered as not restrictive but illustrative in all respects. The scope of the invention is defined by claims rather than the above description, it is intended to include any modifications within the meaning and range of equivalency of the claims.

1 pump, 2 housing, 3 main body, 4 inlet ports, 5 outlet port, 6,6D partition wall, 7 the pump chamber, 7a opening, 8,8D motor chamber, 10 an impeller, 10a through hole, 11 the shroud, 13 vane, 14 a liquid path, 17,17D permanent magnets, 18,18D, 19,19D magnetic, 18A, 18B teeth, 20,20D coil, 21,22,61,62,64,65,161,162,164 , 165 dynamic pressure grooves, 42, 42A controller, 43,43D motor control circuit, 44,44D power amplifier, 48 a rotation angle estimator 49 position calculator, 50 rpm calculator, 51 position determinator, 63 groove, 70 impeller attitude determination unit, 71 storage unit, 74 component command generation unit, 300 a motor drive system, 310 battery unit, 320 inverter Location, 322 operation unit, 324 a motor control unit, 326 PWM driver, 328 a smoothing unit, 330 inverter, 331 motor unit, 332 rotor, 334 angle detector, 336 and 337 the current detector, 340 current calculation unit, 341 a torque current control unit, 342, 344 subtraction unit, 343 a magnetic flux current controller, 346 processing unit, 350 coordinate conversion unit, 352, 354 conversion unit, 356 rotating coordinate conversion unit, 358 a phase estimator, 362 torque current command unit, 364 flux current setting unit, S magnetic sensor.

Claims (12)

  1. A housing comprising a first, second and third chamber, the second chamber is provided in sandwiched between the first chamber and the third chamber, the first chamber and the second chamber partitioned by the first partition wall, said second chamber and said third chamber are partitioned by a second partition,
    Rotatably provided an axis intersecting the first and second partitions in the second chamber as a rotating shaft, an impeller sending a liquid by centrifugal force upon rotation,
    A first driving portion to which the first provided in the indoor, rotatably driving the impeller through the first partition wall,
    A second driving unit for the third provided in the indoor, rotatably driving said impeller through said second partition wall,
    A first magnetic body provided on one surface of the impeller opposite to the first partition wall,
    And a second magnetic body provided on the other surface of the impeller opposite to the second partition,
    First dynamic pressure groove is formed on the wall surface of the first partition wall facing the one surface or that of the impeller, the second dynamic on the wall surface of the second partition to the other side or opposite to that of the impeller pressure groove is formed,
    Wherein the first at least one drive unit and the second driving unit, which is adjusted by the vector control, by the suction force acting on the corresponding magnetic of the first magnetic body and the second magnetic body , to maintain the position of the impeller in the center of the movable range of the impeller in a direction along the rotation axis in the second chamber, a centrifugal pump device.
  2. The first drive unit, when the position of the impeller is changed in a direction away from said first partition wall from the center of the movable range increases the magnetic flux current in the vector control, according to claim 1 centrifugal pump device.
  3. The second drive unit, when the position of the impeller is changed in a direction away from said second partition wall from the center of the movable range increases the magnetic flux current in the vector control, according to claim 2 centrifugal pump device.
  4. During normal rotation of the impeller, the first when the driving portion and said second driving portion is a high-efficiency drive, between the first magnetic member and the first drive unit a first suction force acting, said second suction force acting between the second magnetic member and the second driving portion, in the center of the movable range of the impeller in the second chamber the impeller is balanced when the position, the centrifugal pump according to claim 1.
  5. Further comprising a phase estimator for estimating the rotational angle of the impeller for use in the vector control, centrifugal pump device according to any one of claims 1-4.
  6. A storage unit for the fluid force acting on the impeller, the rotational speed of the impeller, the flow rate, measured in advance and stored using at least one or more of the physical property values ​​of the discharge pressure, and fluid as a parameter,
    Further comprising a drive control unit for controlling said first suction force in response to the value of the storage unit stores, centrifugal pump device according to claim 4.
  7. Further comprising a rotation detector for detecting the rotation angle of the impeller for use in the vector control, centrifugal pump device according to any one of claims 1-4.
  8. The rotation detector is a magnetic sensor, detects the floating position of the impeller by the magnetic sensor, a centrifugal pump apparatus of claim 7.
  9. The third dynamic pressure grooves on the side surface of the outer peripheral side of the impeller is formed, centrifugal pump device according to any one of claims 1-8.
  10. A wall of the second chamber, the third dynamic pressure grooves on the outer peripheral side surface opposite to the wall surface of the impeller is formed, centrifugal pump according to any one of claims 1 to 8 apparatus.
  11. The centrifugal pump apparatus is used to circulate the food, centrifugal pump device according to any one of claims 1 to 10.
  12. The centrifugal pump apparatus is used to circulate the pharmaceutical, centrifugal pump device according to any one of claims 1 to 10.
PCT/JP2016/056567 2015-03-30 2016-03-03 Centrifugal pump device WO2016158186A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2015-069407 2015-03-30
JP2015069407A JP2016188618A5 (en) 2015-03-30

Publications (1)

Publication Number Publication Date
WO2016158186A1 true true WO2016158186A1 (en) 2016-10-06

Family

ID=57005698

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/056567 WO2016158186A1 (en) 2015-03-30 2016-03-03 Centrifugal pump device

Country Status (1)

Country Link
WO (1) WO2016158186A1 (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010101107A1 (en) * 2009-03-06 2010-09-10 Ntn株式会社 Centrifugal pump device
JP2012062790A (en) * 2010-09-14 2012-03-29 Ntn Corp Centrifugal pump unit
US20140241904A1 (en) * 2013-02-27 2014-08-28 Thoratec Corporation Startup sequence for centrifugal pump with levitated impeller

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010101107A1 (en) * 2009-03-06 2010-09-10 Ntn株式会社 Centrifugal pump device
JP2012062790A (en) * 2010-09-14 2012-03-29 Ntn Corp Centrifugal pump unit
US20140241904A1 (en) * 2013-02-27 2014-08-28 Thoratec Corporation Startup sequence for centrifugal pump with levitated impeller

Also Published As

Publication number Publication date Type
JP2016188618A (en) 2016-11-04 application

Similar Documents

Publication Publication Date Title
US6846168B2 (en) Pump with an electrodynamically supported impeller and a hydrodynamic bearing between the impeller and the stator
US6879074B2 (en) Stator field providing torque and levitation
US6707200B2 (en) Integrated magnetic bearing
US7885785B1 (en) Rotor position sensing apparatus and method using piezoelectric sensor and hall-effect sensor
EP1973217A2 (en) Electromagnetic steel plate lamination; electromagnetic core, rotor and permanent magnet type synchronous rotating electric machine provided with the same
US20110243759A1 (en) Centrifugal pump apparatus
Raggl et al. Robust angle-sensorless control of a PMSM bearingless pump
US20130170970A1 (en) Centrifugal pump apparatus
US7474029B2 (en) Rotor magnet placement in interior permanent magnet machines
US20100013332A1 (en) Magnetic radial bearing and magnetic bearing system having a three-phase controller
US20120130152A1 (en) Rotation drive device and centrifugal pump apparatus using the same
US20080024082A1 (en) Controller for motor
JP2007089972A (en) Centrifugal blood pump apparatus
JPH08308286A (en) Angular velocity of rotation detector for synchronous motor, angle velocity of rotation and controller and controlling method for the motor
Ooshima et al. Magnetic suspension performance of a bearingless brushless DC motor for small liquid pumps
EP2405140A1 (en) Centrifugal pump device
US6473562B1 (en) Method for low-speed operation of brushless DC motors
CN101188398A (en) Online recognition method for asynchronous electromotor rotor resistance
Shen et al. A novel compact PMSM with magnetic bearing for artificial heart application
JPH10150755A (en) Radial force generator, rotary machine with winding, and turning equipment
JP2010136863A (en) Centrifugal type pump apparatus
WO2011092011A2 (en) Method for improving efficiency in a multiphase motor, and motor for implementing such a method
US20100013333A1 (en) Magnetic radial bearing having permanent-magnet generated magnetic bias, and a magnetic bearing system having a magnetic radial bearing of this type
Asama et al. Development of a compact centrifugal pump with a two-axis actively positioned consequent-pole bearingless motor
Nguyen et al. Analysis and control of nonsalient permanent magnet axial gap self-bearing motor

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16772070

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase in:

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16772070

Country of ref document: EP

Kind code of ref document: A1