JP4975123B2 - Motor driving device, compressor, refrigeration cycle device, washing machine, washing dryer, and blower - Google Patents

Description

  The present invention relates to a motor drive device that suppresses vibration generated in a motor. The present invention also relates to a compressor equipped with the motor driving device, a refrigeration cycle device using the compressor, a washing machine, a washing dryer, and a blower.

  2. Description of the Related Art Conventionally, a washing machine using a motor detects, for example, a vibration of a washing tub with a vibration sensor attached to the upper part of the washing tub, and performs a rotation speed control of the motor by a dehydration process control unit based on the detection signal. However, it only detects the vibration and controls the rotation speed according to the level, and does not actively reduce the vibration by motor control, and the vibration reduction is arranged below the washing tub. However, there is a problem that the vibration of the washing machine cannot be stably reduced.

  Therefore, the vibration state of the receiving cylinder including the washing tub is detected, and the vibration is controlled so that the vibration is reduced to reduce the vibration and noise during dehydration. Washing machine comprising: control means for supporting; support means for supporting the receiving cylinder; vibration sensor for detecting vibration; and vibration control means for inputting an output signal of vibration detected by the vibration sensor to the control means as a motor control signal Has been proposed. This washing machine can detect the vibration state of the receiving cylinder including the washing tub in the washing and dehydrating process, and feedback control the control amount to the motor control current so as to reduce the vibration amount. The vibration can be reduced by controlling the vibration of the casing and the vibration of the housing (see, for example, Patent Document 1).

  Also, in order to reduce undesired vibrations called disturbances in at least one axis rotating at a substantially constant speed, or in a virtual machine axis of the machine, a plurality of axes, particularly in the machine axis of a printing unit or a printing press. In a method for compensating mechanical vibrations, in particular rotational vibrations, having a frequency spectrum that can be approximately represented by a discontinuous frequency part, by at least one actuator acting directly or indirectly on the mechanical axis The at least one moment of the same frequency having a specific amplitude and phase, without depending on at least one of the discontinuous frequency portions of the Compensates for mechanical vibrations characterized by being superimposed by an actuator so that is reduced at that frequency Methods have been proposed (e.g., see Patent Document 2).

  In addition, in order to reliably reduce noise during washing machine dehydration, a vibration detection sensor that detects vibrations in two or more directions is attached to the aquarium, and the horizontal (first direction) vibration and vertical (first By detecting the magnitude of the vibration in the direction (2), it is possible to detect the vibration in the parallel mode and the conical mode of the water tank during dehydration. Then, from the vibration detection result by the vibration detection sensor, the rotation speed and time of the washing tub when the primary resonance rotation speed where the parallel mode vibration appears and when the secondary resonance rotation speed where the conical mode vibration appears are obtained. By controlling, abnormal vibration can be prevented in advance. In addition, noise is predicted by detecting vibrations in the parallel mode and conical mode in the high-speed rotation range of the washing tub, and the rotation speed is controlled based on the predicted noise, so that quiet and short-time dehydration can be performed. Has been proposed (see, for example, Patent Document 3).

  Furthermore, in order to provide a vibration reduction device that can exhibit a good vibration reduction effect even when the rotary compressor is driven by an induction motor, a torque control inverter that controls the generated torque of the motor of the rotary compressor based on a torque command And a torque command generation means for generating a torque command to be applied to the torque control inverter based on the rotation direction acceleration detected by the rotation direction acceleration detection means of the rotary compressor. Of a rotary compressor including a pair of acceleration detection means mounted on the casing at a predetermined position where the angle difference from the center of the motor is 90 °, and a difference calculation means for calculating a difference between output signals from both acceleration detection means A reduction device has been proposed (see, for example, Patent Document 4).

JP 2008-142231 (first page, FIG. 1) Japanese Patent Laid-Open No. 2002-196828 (first page, FIG. 1) JP-A-2006-141556 (first page, FIG. 1) Japanese Patent Laid-Open No. 04-185294 (2nd page, FIG. 4)

  However, although the technology for reducing vibrations and associated noise in the washing machine described in Patent Document 1 is controlled to suppress the vibrations by feeding back the detected vibrations, vibrations other than vibrations generated by the rotation of the motor. If this is detected, vibration cannot be suppressed by the motor, feedback control fails, and there is a problem that vibration is increased.

  Further, the vibration reduction technique in the method of compensating for mechanical vibration described in Patent Document 2 eliminates the influence of disturbance by extracting a specific frequency component from the detected vibration. The vibration that appears in the tangential direction with respect to the rotation axis due to speed pulsation and the vibration that oscillates with respect to the rotation axis due to unbalance of the rotor of the motor, which is difficult to be suppressed by the motor, have the same frequency component. There is a problem that the control breaks down due to the influence of, and the vibration is increased.

  Further, the noise reduction technology of the washing machine described in Patent Document 3 separates the detected vibration into a conical mode and a parallel mode, but the conical mode includes tangential vibration and whirling vibration. There is a problem that the control becomes unstable and the vibration increases due to the influence of the whirling vibration which is difficult to suppress the vibration by the motor.

  Further, the vibration reduction technique in the vibration reduction device for a rotary compressor described in Patent Document 4 uses two acceleration pickups, which is not only disadvantageous in cost, but also increases the power supply lines and signal lines of the acceleration pickups. There are also problems with the mounting surface.

  The present invention has been made to solve the above-described problems, and eliminates the aging of the equipment due to motor vibration, the suppression of vibration while driving the motor, the deterioration of the equipment due to vibration, and the user dissatisfaction due to noise generation. Provided is a motor drive device capable of

  Moreover, the compressor which mounts the motor drive device, the refrigerating-cycle apparatus using the compressor, a washing machine, a washing dryer, and an air blower are provided.

The motor driving device according to the present invention is:
A motor driving the load;
An inverter for applying a voltage to the motor;
Inverter control means for controlling the voltage output by the inverter;
Vibration detecting means attached to a predetermined portion of the motor for detecting the vibration of the motor;
Vibration output correcting means for correcting the output of the vibration detecting means;
Vibration separating means for separating the vibration component in the tangential direction with respect to the rotation axis of the motor from the output of the vibration output correcting means;
Vibration suppression control means for outputting a signal for suppressing vibration based on the output of the vibration separating means,
The inverter control means controls the voltage applied by the inverter based on the output of the vibration suppression control means.

  The motor drive device according to the present invention can correct the automatically detected output even when the vibration detection means for detecting the vibration of the motor is not installed at the ideal installation position and installation angle. Since highly accurate vibration suppression control is performed based on the corrected value, reliability is high and safety can be maintained.

FIG. 3 is a diagram illustrating the first embodiment and is a configuration diagram of a motor drive device 100. FIG. 5 shows the first embodiment and shows the operation of the PWM signal generation means 13. FIG. 5 shows the first embodiment and shows the first operation of the voltage control means 11. FIG. 5 shows the first embodiment, and shows a second operation of the voltage control means 11. FIG. 5 shows the first embodiment and shows the third operation of the voltage control means 11. FIG. 6 is a diagram illustrating the first embodiment, and is a configuration diagram of vibration detection means 5 (acceleration sensor) capable of detecting vibrations in three axial directions (FIG. 6A shows a state in which the vibration detection means 5 is not inclined, FIG. ) Is a state in which the vibration detecting means 5 is inclined). The figure which shows Embodiment 1, The figure which shows the composition of the gravity acceleration of a triaxial direction (FIG. 7 (a) is an inclination angle of 0 deg, FIG. When the inclination of the z axis is inclined to γ, FIG. 7C shows the case where all of the x axis, the y axis, and the z axis are inclined (the inclination α of the x axis, the inclination β of the y axis, the inclination γ of the z axis). ). FIG. 5 shows the first embodiment, and shows an example of vibration of a motor 3. FIG. 8 shows the first embodiment and shows the operation of the vibration separating means 6. FIG. 5 shows the first embodiment, and shows a case of correction coefficients. FIG. 5 shows the first embodiment, and shows the operation of vibration suppression control means 7. FIG. 5 shows the first embodiment, and shows another operation of the vibration suppression control means 7. FIG. 5 is a diagram showing the first embodiment, and is a flowchart showing an operation when the motor drive device 100 is mounted on a device. FIG. 5 shows the first embodiment, and is a configuration diagram of a motor drive device 200 of a first modification. FIG. 9 shows the first embodiment, and shows the operation of the vibration suppression control means 7 of the motor drive device 200 of the first modification. FIG. 10 shows the first embodiment, and shows another operation of the vibration suppression control means 7 of the motor drive device 200 of the first modification. FIG. 5 shows the second embodiment, and is a configuration diagram of a motor driving device 300 that drives the compressor 24; FIG. 5 shows the second embodiment, and is a refrigerant circuit diagram of an air conditioner 400 that uses the compressor 24 in a refrigeration cycle. FIG. 5 shows the second embodiment, and is an exploded perspective view of an outdoor unit 400A of the air conditioner 400. FIG. FIG. 6 is a diagram illustrating the second embodiment, and is a longitudinal sectional view of the compressor 24. AA sectional drawing of FIG. FIG. 5 shows the second embodiment, and is an external view of a compressor 24 to which a compressor terminal protective cover 160 is attached. FIG. 5 shows the second embodiment, and is a top view of a compressor terminal protective cover 160. It is a figure which shows Embodiment 2, and is a side view (a part is shown with a cross section) of the terminal protection cover 160 for compressors. FIG. 5 shows the second embodiment and is a bottom view of the compressor terminal protective cover 160. XX sectional drawing of FIG. The figure which shows the Y part vicinity of FIG. 22, and shows the terminal protective cover 160 for compressors in the XX cross section of FIG. FIG. 6 is a diagram showing the second embodiment, and is a perspective view of an upper surface of a compressor terminal protective cover 160. FIG. 6 is a diagram showing the second embodiment, and is a perspective view of the bottom surface of the compressor terminal protective cover 160 as viewed. FIG. 5 is a diagram illustrating the second embodiment, and is a perspective view of the substrate assembly 270 as viewed from the acceleration sensor 272 side. FIG. 9 is a diagram illustrating the second embodiment, and is an exploded perspective view of the substrate assembly 270 as viewed from the acceleration sensor 272 side. FIG. 9 is a diagram illustrating the second embodiment, and is a perspective view of the substrate assembly 270 as viewed from the opposite side of the acceleration sensor 272; FIG. 9 is a diagram showing the second embodiment, and is a perspective view of the substrate pressing component 280 as viewed from the top surface. FIG. 6 is a diagram showing the second embodiment, and is a top view of a substrate pressing component 280. FIG. 9 shows the second embodiment and is a side view of the board pressing component 280. FIG. 9 is a diagram showing the second embodiment, and is a perspective view of the board pressing component 280 as seen from the bottom surface. FIG. 9 is a diagram showing the second embodiment, and is a bottom view of the board pressing component 280. FIG. 9 is a diagram showing the second embodiment, and is an enlarged perspective view of a first locking portion 281. FIG. 9 is a diagram showing the second embodiment, and is an enlarged perspective view of a second locking portion 284. FIG. 6 shows a second embodiment and is a basic configuration diagram of an acceleration sensor 272; FIG. 5 shows the second embodiment, and is an exploded view showing a state before the molding die 203 of the compressor terminal protective cover 160 is set. The figure which shows Embodiment 2 and the figure which shows the state which set the mold 203 of the terminal protective cover 160 for compressors. FIG. 5 shows the second embodiment, and shows a manufacturing process of the compressor terminal protective cover 160. FIG. 5 shows the third embodiment, and is a configuration diagram of a motor driving device 500 that drives a washing drum 25. FIG. 6 shows the fourth embodiment, and is a configuration diagram of a motor drive device 600 that drives the blower fan 26.

Embodiment 1 FIG.
FIGS. 1 to 13 are diagrams showing the first embodiment, FIG. 1 is a configuration diagram of the motor driving device 100, FIG. 2 is a diagram showing the operation of the PWM signal generating means 13, and FIG. FIG. 4 is a diagram showing a second operation of the voltage control means 11, FIG. 5 is a diagram showing a third operation of the voltage control means 11, and FIG. 6 is capable of detecting vibrations in three axial directions. FIG. 6A is a configuration diagram of the vibration detection means 5 (acceleration sensor) (FIG. 6A shows a state where the vibration detection means 5 is not tilted, FIG. 6B shows a state where the vibration detection means 5 is tilted), and FIG. FIG. 7A shows the composition of gravity acceleration in the direction (FIG. 7A shows the case where the inclination angle is 0 deg. FIG. 7B shows the case where the y axis is fixed and the inclination of the x axis is α and the inclination of the z axis is γ. FIG. 7C shows a case where the x-axis, y-axis, and z-axis are all tilted (x-axis tilt α, y-axis tilt β, z-axis tilt γ), and FIG. FIG. 9 is a diagram showing an example of the vibration of the motor 3, FIG. 9 is a diagram showing the operation of the vibration separating unit 6, FIG. 10 is a diagram showing classification of correction coefficients, and FIG. 11 is a diagram showing the operation of the vibration suppression control unit 7. FIG. 12 is a diagram showing another operation of the vibration suppression control means 7, and FIG. 13 is a flowchart showing the operation when the motor drive device 100 is mounted on a device.

The motor drive device 100 will be described with reference to FIG. The motor drive device 100 shown in FIG. 1 includes the following elements.
(1) DC power source 1: obtained by converting alternating current supplied from commercial power source into direct current;
(2) Inverter 2: has switching elements 14a to 14f, generates AC voltage (pseudo AC voltage) using DC power source 1 as power source, and is electrically connected to motor 3;
(3) Motor 3: For example, brushless DC motor, induction motor, etc .;
(4) Inverter control means 4: Although constituted by a CPU (Central Processing Unit), a microcomputer (microcomputer), a DSP (Digital Signal Processor), etc., it may be constituted by an electronic circuit such as an IC. Although details will be described later, the inverter control means 4 includes a rotation coordinate conversion means 10, a voltage control means 11, a reverse rotation coordinate conversion means 12, and a PWM signal generation means 13 (details will be described later);
(5) Vibration detection means 5: attached to the motor 3, detects the vibration Vib of the motor 3, and can detect gravitational acceleration. The vibration detection means 5 may be any sensor other than a sensor capable of detecting vibration, as long as it can detect vibration, such as a displacement sensor, an acceleration sensor, and a gyro sensor. Further, with respect to the axes for detecting vibrations, at least three vibration directions can be detected. The angle formed by each vibration direction detected by the vibration detection means 5 is 90 degrees. Furthermore, at least two axes of the vibration direction detected by the vibration detection means 5 are for detecting a vibration direction perpendicular to the rotation axis of the motor 3;
(6) Vibration separating means 6: Among the vibration components of the vibration Vib of the motor 3 detected by the vibration detection means 5, only the vibration component Vib_nr in the tangential direction with respect to the rotation axis of the motor 3 is separated and detected (details will be described later). To do). This embodiment is characterized by this vibration separating means 6;
(7) Vibration output correction means 27: Automatically corrects the vibration output value including an error when the vibration detection means 5 is not installed at an ideal installation position and installation angle to an accurate vibration output value. Means;
(8) Vibration suppression control means 7: Calculates a compensation amount Vib_c for suppressing vibration based on the output of the vibration separating means 6 (details will be described later);
(9) Current detection means 8: Detects currents Iu, Iv and Iw flowing through the motor 3. The current detection means 8 can be easily detected by using a Hall sensor such as a DCCT (DC current detector) or an ACCT (AC current transformer) that detects current between the inverter 2 and the motor 3. In FIG. 1, the current between the inverter 2 and the motor 3 is detected. However, the current flows between the DC power source 1 and the inverter 2 and the lower arm (switching elements 14d, 14e, 14f) of the inverter 2. The current may be detected. If at least two phases can be detected, based on Kirchhoff's law, for example, if Iu and Iv can be detected, it is possible to obtain Iw = −Iu−Iv from Iu + Iv + Iw = 0, and the number of sensors can be reduced. Can reduce costs by:
(10) DC voltage detection means 9: detects the voltage Vdc of the DC power supply 1. The DC voltage can be detected by reducing the voltage so that the voltage can be detected by the above-described microcomputer or the like using a voltage dividing resistor connected to both ends of the DC power supply 1, and restoring the voltage based on the voltage dividing ratio inside. Any other means capable of detecting the voltage may be used to detect the voltage.

  Next, the operation of the inverter control means 4 will be described. Using the U-phase, V-phase, and W-phase currents Iu, Iv, and Iw detected by the current detection unit 8 and the rotation phase θ (magnetic pole position) of the motor 3, the rotation coordinate conversion unit 10 uses the following equation (1). Is converted into currents Id and Iq in the rotating coordinate system (dq coordinate system).

振動抑制制御手段７の出力Ｖｉｂ＿ｃと、電流Ｉｄ、Ｉｑを用いて電圧制御手段１１において、ｄｑ座標系の電圧指令Ｖｄ＊、Ｖｑ＊を生成するとともに、磁極位置θの演算を行う。電圧制御手段１１の動作については後述する。ここでは、ｄｑ座標系にて説明するが、ＵＶＷもしくは直交座標系であるαβ座標上で制御を行っても何ら問題ない。

Using the output Vib_c of the vibration suppression control means 7 and the currents Id and Iq, the voltage control means 11 generates voltage commands Vd * and Vq * in the dq coordinate system and calculates the magnetic pole position θ. The operation of the voltage control means 11 will be described later. Here, the dq coordinate system will be described, but there is no problem even if the control is performed on the αβ coordinate which is the UVW or orthogonal coordinate system.

  Thereafter, the Vd * and Vq * obtained by the voltage control means 11 are converted into U-phase, V-phase, and W-phase voltage commands in the reverse rotation coordinate conversion means 12 by the following equation (2) using the magnetic pole position θ Vu *, Vv *, and Vw * are obtained. The method for obtaining the U-phase, V-phase, and W-phase voltage commands Vu *, Vv *, and Vw * was obtained by reverse rotation coordinate transformation this time. However, a method such as two-phase modulation, three-phase modulation, or space vector modulation is used. There is no problem even if is used.

さらに、逆回転座標変換手段１２と電流検出手段８の出力とを用いて、ＰＷＭ信号生成手段１３において、インバータ２内のスイッチング素子１４ａ，１４ｂ，１４ｃ，１４ｄ，１４ｅ，１４ｆを駆動するＰＷＭ信号を生成して、インバータ２が出力する電圧を制御する。

Further, using the reverse rotation coordinate conversion means 12 and the output of the current detection means 8, the PWM signal generation means 13 generates a PWM signal for driving the switching elements 14a, 14b, 14c, 14d, 14e, and 14f in the inverter 2. The voltage generated and controlled by the inverter 2 is controlled.

  A signal generation method of the PWM signal generation means 13 will be described. FIG. 2 is a diagram showing input / output waveforms of the PWM signal generating means 13. Here, the voltage commands Vu *, Vv *, and Vw * can be obtained from the equation (2), but are defined as the following equations (3) to (5) for easy explanation. However, A is the amplitude of the voltage command.

式（３）〜式（５）により得られた電圧指令信号と所定の周波数で振幅Ｖｄｃ／２（ここで、Ｖｄｃは直流電圧検出手段９にて検出した母線電圧）のキャリア信号を比較し、相互の大小関係に基づきＰＷＭ信号ＵＰ，ＶＰ，ＷＰ，ＵＮ，ＶＮ，ＷＮを生成する。

The voltage command signal obtained by the equations (3) to (5) is compared with a carrier signal having a predetermined frequency and an amplitude Vdc / 2 (where Vdc is a bus voltage detected by the DC voltage detecting means 9), PWM signals UP, VP, WP, UN, VN, and WN are generated based on the mutual magnitude relationship.

  Next, the operation of the voltage control unit 11 will be described. FIG. 3 is a diagram showing the first operation of the voltage control means 11 and shows the input / output relationship of the voltage control means 11. The speed controller 15 obtains a q-axis current command Iq * based on the difference between the speed command ω * and the output ω of the speed estimator 18.

  Further, the d-axis current controller 16 obtains the d-axis command voltage Vd * based on the difference between the d-axis current command Id * and the d-axis current Id.

  The q-axis current controller 17 obtains a q-axis voltage command Vq * based on the difference between the q-axis current command Iq * and the q-axis current Iq.

  The speed controller 15, the d-axis current controller 16, and the q-axis current controller 17 can be easily realized by commonly used controllers such as proportional control, integral control, proportional-integral control, and the like. There is no problem using the method.

  For the speed estimator 18, the speed ω can be obtained based on the voltage-current equation of the motor 3 using the d-axis command voltage Vd *, the q-axis voltage command Vq *, the d-axis current Id, the q-axis current Iq, and the like. Is possible. There is no problem even if the speed ω is obtained using a sensor (not shown) for detecting the magnetic pole position θ of the motor 3.

  Further, regarding the position estimator 19, the magnetic pole position θ of the motor 3 can be obtained by integrating the speed ω obtained by the speed estimator 18. Further, there is no problem even if the magnetic pole position θ is directly detected by an encoder or the like.

  In FIG. 3, by adding the output Vib_c of the vibration suppression control means 7 to the speed command ω *, the vibration is controlled by controlling the speed so as to suppress the speed unevenness due to the speed ripple of the motor 3 that is the cause of the vibration. Suppress.

  The speed ripple described above occurs when there is a difference between the load torque τl driven by the motor 3 and the torque τm generated by the motor 3 as in the following equation (6). Here, J is the inertia of the motor 3 and the load.

すなわち、トルクτｍと負荷トルクτｌを一致させることで、速度リップルの発生が抑えられる。そこで、モータ３のトルクτｍは、表面磁石形同期モータの場合には、極対数Ｐｍとモータ３の誘起電圧定数φｆ、ｑ軸電流Ｉｑの積で表される。そのため、図４に示すように、ｑ軸電流指令Ｉｑ＊を、振動を抑制する補償量Ｖｉｂ＿ｃを用いて調整するように構成することで、トルクτｍと負荷トルクτｌを一致させることができる。

That is, by making the torque τm and the load torque τl coincide with each other, the generation of the speed ripple can be suppressed. Therefore, in the case of a surface magnet type synchronous motor, the torque τm of the motor 3 is represented by the product of the number of pole pairs Pm, the induced voltage constant φf of the motor 3 and the q-axis current Iq. Therefore, as shown in FIG. 4, the torque τm and the load torque τl can be matched by configuring the q-axis current command Iq * to be adjusted using the compensation amount Vib_c that suppresses vibration.

  Similarly, as shown in FIG. 5, even if the q-axis voltage command Vq * related to the torque τm is adjusted using the compensation amount Vib_c for suppressing the vibration, the same effect can be obtained. . Here, although not shown, in a control system that directly gives a torque command, the same effect can be obtained by directly operating the torque. The same effect can be obtained with a control system other than those described here.

  Next, the operation of the vibration output correcting means 27 will be described. The vibration output correcting means 27 is a means for automatically correcting the vibration output value including an error when the vibration detecting means 5 is not mounted at an ideal installation position and installation angle to an accurate vibration output value. is there.

  As a specific method, a case is assumed in which vibration detection means 5 (acceleration sensor) capable of detecting vibrations in the three directions of the x-axis, y-axis, and z-axis in which the respective axes are orthogonal as shown in FIG. 6 is used. . However, gravity acceleration can be detected. When this vibration detection means 5 (acceleration sensor) is moved in the x-axis direction, the acceleration Ax in the x-axis direction is detected as shown in FIG.

  Here, when the vibration detection means 5 (acceleration sensor) is tilted, for example, as shown in FIG. 6B, the tilt angle with respect to the x axis is α, the tilt angle with respect to the y axis is β, and the tilt angle with respect to the z axis. Is γ. When the tilted acceleration sensor is moved in the x direction in this state, the value of the acceleration Ax in the x-axis direction cannot be detected as in FIG. 6A, and the detection value Ax corresponding to the tilt angle α is detected. Will be. The detected size of Ax is Ax_t · cos α, where Ax_t is the true x-axis acceleration. That is, if the signals detected by the acceleration sensor are Ax, Ay, and Az, the true accelerations Ax_t, Ay_t, and Az_t on the xyz axis can be obtained by Expression (7).

次に式（７）に示す傾き角α、β、γを求める方法として振動検出手段５（加速度センサ）で検出される重力加速度ｇを用いる方法について説明する。図７（ａ）に示すように、傾き角０ｄｅｇの場合、ｚ軸方向のみ重力加速度１ｇが検出される。

Next, a method of using the gravitational acceleration g detected by the vibration detection means 5 (acceleration sensor) will be described as a method for obtaining the inclination angles α, β, and γ shown in Expression (7). As shown in FIG. 7A, when the tilt angle is 0 deg, the gravitational acceleration 1g is detected only in the z-axis direction.

  However, as shown in FIG. 7B, when the y-axis is fixed and the inclination of the x-axis is α and the inclination of the z-axis is γ, from the x-axis and z-axis of the vibration detecting means 5 (acceleration sensor). Gravitational acceleration corresponding to the tilt angle is detected, and the resultant value is 1 g. At this time, the maximum axis among the detected values of the three axes of the vibration detection means 5 (acceleration sensor) is used for gravity acceleration detection, and output correction can be performed with reference to this axis.

  Similarly, as shown in FIG. 7C, when all of the x-axis, y-axis, and z-axis are tilted, gravitational acceleration corresponding to the tilt angle is detected from all of the x-axis, y-axis, and z-axis, The resultant vector is 1 g. That is, the inclination angle can be obtained by the equation (8) from the acceleration corresponding to the inclination angle and the gravitational acceleration g.

また、振動出力補正手段２７では、振動出力値をもとに振動検出手段５の異常を判断することも可能である。例えば、３軸のうちいずれかの軸もしくは複数の軸の出力値が正規の出力範囲以外となる場合、また３軸の出力の合成値が重力加速度と一致しない場合は、振動検出手段５の異常および故障またはモータ３の動作異常と判断する。このような場合は、後述する振動分離手段６や振動抑制制御手段７を動作させないような対策をするか、もしくはこれらの異常をユーザに知らせるような表示をする対策を施すことで安全性を確保する。

Further, the vibration output correcting means 27 can also determine the abnormality of the vibration detecting means 5 based on the vibration output value. For example, if the output value of any one of the three axes or a plurality of axes is outside the normal output range, or if the combined value of the outputs of the three axes does not match the gravitational acceleration, the vibration detection means 5 is abnormal. Further, it is determined that there is a failure or abnormal operation of the motor 3. In such a case, measures are taken to prevent the vibration separating means 6 and the vibration suppression control means 7 to be described later from being operated, or safety is ensured by taking measures to display these abnormalities to the user. To do.

  As described above, the vibration output correcting unit 27 automatically corrects an output value including an error when the vibration detecting unit 5 is not installed at an ideal installation position and installation angle to an accurate output value. It is possible to perform highly reliable control with high reliability.

  However, when the vibration output correcting means 27 is operated, it is necessary that the motor 3 is not driven or is in a stopped state. If this is not the case, for example, an acceleration other than gravitational acceleration may be detected in a state where the motor 3 is being driven, and there is a possibility that it cannot be corrected accurately.

  Next, the operation of the vibration separating unit 6 will be described. FIG. 8 is a diagram illustrating an example of vibration of the motor 3. The vibration of the motor 3 is divided into vibration in the tangential direction (tangential vibration) with respect to the motor rotation axis due to the generation of speed ripple, and whirling vibration due to mechanical unbalance of the motor 3, and the vibration actually detected is The two (tangential vibration and whirling vibration) are synthesized.

  Since the tangential vibration is generated by the speed ripple of the motor 3, it can be suppressed by the control of the motor 3, whereas the whirling vibration is generated by a mechanical imbalance. It is difficult to suppress. For this reason, even if the control for suppressing the vibration is performed, the whirling vibration component remains, so that the control system for suppressing the vibration may diverge.

  Here, in the xy coordinate system in FIG. 8, the Lissajous waveform of the tangential vibration draws a linear locus, and therefore the vibration Axt in the x direction and the vibration Ayt in the y direction can be expressed by the following equation (9). . Where At is the amplitude of the tangential acceleration, φ is the slope of the tangential acceleration, and α is the phase of the tangential acceleration. Θm is a mechanical rotational position of the motor 3 (rotor), and is obtained by dividing the magnetic pole position θ by the number of pole pairs Pm of the motor 3.

また、振れ回り振動は円軌跡を描くことから、ＡｘｓとＡｙｓは次式（１０）にて表すことが可能である。Ａｓは振れ回り加速度の振幅、βは振れ回り加速度の初期位相である。

Moreover, since the whirling vibration draws a circular locus, Axs and Ays can be expressed by the following equation (10). As is the amplitude of the swing acceleration, and β is the initial phase of the swing acceleration.

よって、合成振動Ｖｉｂ（Ａｘ、Ａｙ）は次式（１１）で表される。

Therefore, the composite vibration Vib (Ax, Ay) is expressed by the following equation (11).

ここで、合成振動Ｖｉｂに含まれる振れ回り振動を除去する方法について、図９を用いて説明する。図９において、式（１１）に示すＡｘ、Ａｙを回転座標変換手段１０を用いて、式（１２）に示すように回転座標上の振動Ａｄ、Ａｑに変換を行う。すると、式（１２）の第一項は接線振動の交流成分、第二項は接線振動の直流成分、第三項は振れ回り振動の直流成分になる。

Here, a method of removing the whirling vibration included in the combined vibration Vib will be described with reference to FIG. In FIG. 9, Ax and Ay shown in Expression (11) are converted into vibrations Ad and Aq on the rotating coordinates as shown in Expression (12) using the rotating coordinate conversion means 10. Then, the first term of equation (12) is the AC component of tangential vibration, the second term is the DC component of tangential vibration, and the third term is the DC component of whirling vibration.

ここで、式（１２）により得られた、Ａｄ、ＡｑをＨＰＦ２０（Ｈｉｇｈ Ｐａｓｓ Ｆｉｌｔｅｒ）において直流成分を除去した信号Ａｄ＿ｈｐｆ、Ａｑ＿ｈｐｆは、式（１３）となる。ＨＰＦ２０を、回転座標変換手段１０の出力の低周波成分を除去する低周波成分除去手段と定義する。

Here, the signals Ad_hpf and Aq_hpf obtained by removing the direct current component from Ad and Aq in the HPF 20 (High Pass Filter) obtained by the equation (12) are represented by the equation (13). The HPF 20 is defined as a low-frequency component removing unit that removes a low-frequency component from the output of the rotating coordinate conversion unit 10.

さらに、式（１３）を式（１４）に示すように、逆回転座標変換手段１２により逆回転座標変換を行うと振幅は１／２になるものの、接線振動成分のみの信号Ｖｉｂ＿ｎｒ（Ａｘ＿ｎｒ、Ａｙ＿ｎｒ）を得ることが可能となる。つまり回転軸方向に対して垂直方向、且つ互いに９０度の角度を持つ２軸以上の振動を検出することにより、接線振動成分のみを分離して検出することが可能となる。

Further, as shown in Expression (14), Expression (13) shows that when reverse rotation coordinate conversion is performed by the reverse rotation coordinate conversion means 12, the amplitude becomes 1/2, but only the signal Vib_nr (Ax_nr, Ay_nr) of the tangential vibration component. ) Can be obtained. That is, by detecting vibrations of two or more axes perpendicular to the rotation axis direction and having an angle of 90 degrees with each other, only the tangential vibration component can be detected separately.

また、振れ回り振動がモータ３の回転に同期しておらず、例えばモータ３の回転の２倍の周波数で変化する場合には、θｍを２×θｍとして、前述の演算を行うことで振れ回り振動を除去することができることは言うまでもない。

In addition, when the whirling vibration is not synchronized with the rotation of the motor 3 and changes at a frequency twice as high as the rotation of the motor 3, for example, the whirling is performed by performing the above calculation with θm being 2 × θm. Needless to say, vibration can be eliminated.

  As described above, the vibration separating means 6 can be separated by detecting biaxial vibrations perpendicular to the rotation axis and having an angle of 90 degrees with each other as shown in FIG. However, if the vibration detection means 5 is not attached at an ideal installation position and installation angle, there is a possibility that the touch-around vibration cannot be accurately separated.

  Therefore, as described above, the output detected using the vibration detecting means 5 (acceleration sensor) capable of detecting vibrations in the three-axis directions is corrected by the vibration output correcting means 27, and then the two axes required by the vibration separating means 6 are corrected. If one of the three axes is selected, accurate whirling vibration can be separated. Therefore, an example of a method for selecting two of the three axes necessary for the vibration separating means 6 will be described below.

  The acceleration component necessary for detecting the vibration generated by the motor 3 with respect to the direction (rotation angle) of each axis is selected by the equation (15) obtained by multiplying the equation (7) by the correction coefficient (Khx, Khy, Khz). To do.

但し、Ｋｈｘは振動検出手段５（加速度センサ）ｘ軸の補正係数、Ｋｈｙは振動検出手段５（加速度センサ）ｙ軸の補正係数、Ｋｈｚは振動検出手段５（加速度センサ）ｚ軸の補正係数である。補正係数は図１０に示すように、傾き角α、β、γの角度に応じて決定する。

Where Khx is the vibration detection means 5 (acceleration sensor) x-axis correction coefficient, Khy is the vibration detection means 5 (acceleration sensor) y-axis correction coefficient, and Khz is the vibration detection means 5 (acceleration sensor) z-axis correction coefficient. is there. As shown in FIG. 10, the correction coefficient is determined according to the inclination angles α, β, and γ.

That is, the correction coefficients Khx, Khy, and Khz are as follows according to the inclination angles α, β, and γ.
(1) The correction coefficient Khx is determined according to the angle of the inclination angle α.

In the range of α = X1 (315 to 45 °), Khx = 1
In the range of α = X2 (45 to 135 °), Khx = 0
In the range of α = X3 (135 to 225 °), Khx = −1
In the range of α = X4 (225 to 315 °), Khx = 0
(2) The correction coefficient Khy is determined according to the angle of the inclination angle β.

In the range of α = Y1 (315 to 45 °), Khy = 1
In the range of α = Y2 (45 to 135 °), Khy = 0
In the range of α = Y3 (135 to 225 °), Khy = −1
In the range of α = Y4 (225 to 315 °), Khy = 0
(3) The correction coefficient Khz is determined according to the angle of the inclination angle γ.

In the range of α = Z1 (315 to 45 °), Khz = 0
In the range of α = Z2 (45 to 135 °), Khz = 1
In the range of α = Z3 (135 to 225 °), Khz = 0
In the range of α = Z4 (225 to 315 °), Khz = −1
Next, the operation of the vibration suppression control means 7 will be described. The vibration suppression control means 7 uses, for example, Ax_nr among the Vib_nr obtained by the equation (12), as shown in FIG. A compensation amount Vib_c is obtained. However, even if Ay_nr is used instead of Ax_nr, it has the same tangential vibration component except that the phase is different by 90 degrees. Therefore, vibration suppression control can be performed using either of them.

  Further, when the control is performed by a microcomputer or the like, since it is affected by a dead time or the like, as shown in FIG. 12, a phase adjustment unit 22 for adjusting the phase is added to the vibration suppression control unit 7 of FIG. Thus, vibration can be reliably suppressed. The amount of phase adjustment by the phase adjusting means 22 may be set to a phase that decreases by detecting increase / decrease in vibration.

  The vibration suppression compensation amount calculation means 21 can be easily realized by a commonly used controller such as proportional control, integral control, proportional integral control, or the like, and there is no problem even if other control methods are used.

  By adding or subtracting Vib_c, which is the output of the vibration suppression control means 7, to ω *, Iq *, Vq *, etc., as described above, vibration can be suppressed.

FIG. 13 is a flowchart of the operation when installed in actual equipment (compressor, refrigeration cycle apparatus (air conditioner, heat pump type water heater, refrigerator, etc.), washing machine, washing dryer, blower, etc.). It explains using.
(1) S1: When the motor driving apparatus 100 is operated, first, initialization processing of the device system is performed;
(2) S2: Output correction of the output obtained from the vibration detection means 5 is performed;
(3) S3: After that, it waits until an activation request for the motor 3 mounted on the device is received;
(4) S4: When a start request for the motor 3 is received, the motor 3 is started to detect vibration of the motor 3;
(5) S5: Based on the detected vibration value, the whirling vibration unnecessary for control is removed;
(6) S6: Thereafter, a compensation amount for performing vibration suppression using the vibration component from which the whirling vibration is removed;
(7) S7: The inverter control means 4 calculates the voltage applied to the motor 3 and operates the inverter 2;
(8) S8: This operation is continued until a stop request is received, and the operation is stopped when a stop request is received.
With the above operation, operation with the vibration of the motor 3 suppressed is possible.

  However, if there is an abnormality in the output obtained from the vibration detection means 5, a failure of the vibration detection means 5 is considered, and therefore a safety measure such as preventing the subsequent operation is required (not shown).

  According to the present embodiment, it is possible to suppress the vibration generated by the rotation of the motor 3 using the vibration detected by the vibration sensor (vibration detecting means 5). Since the vibration to the device connected to is reduced, it is possible to suppress the breakage and the generation of noise due to the vibration, and it is possible to obtain the highly reliable motor drive device 100.

  Since it is possible to remove the whirling vibration that cannot be suppressed by the control of the motor 3 from the output of the vibration detection means 5, it is possible to suppress abnormal vibration due to divergence of the control system. A highly reliable motor driving device 100 can be obtained.

  Further, since the tangential vibration can be detected with high accuracy by only one vibration detection means 5, not only the cost increase by the plurality of vibration detection means 5 can be suppressed, but also the wiring of the vibration detection means 5 can be simplified.

  14 to 16 are diagrams showing the first embodiment. FIG. 14 is a configuration diagram of the motor driving device 200 according to the first modification. FIG. 15 illustrates the operation of the vibration suppression control unit 7 of the motor driving device 200 according to the first modification. FIG. 16 is a diagram illustrating another operation of the vibration suppression control means 7 of the motor driving device 200 according to the first modification.

  The motor drive device 200 of the first modification is the same as the configuration of the motor drive device 100 (FIG. 1) except that the magnetic pole position θ is added to the input of the vibration suppression control means 7. A description will be omitted, and only the changes will be described.

  As shown in FIG. 14, in the motor drive device 200 of the first modification, the magnetic pole position θ is added to the input of the vibration suppression control unit 7 in addition to the tangential vibration component Vib_nr from the vibration separation unit 6.

  As described above, control can be performed using either Ax_nr or Ay_nr of Vib_nr as an input. Here, a case where Ax_nr is input will be described.

  Based on Ax_nr and the magnetic pole position θ, the vibration suppression control unit 7 extracts only a specific frequency component from among the vibrations detected by the specific frequency component extraction unit 23. In FIG. 15, the magnetic rotation position of the motor 3 is obtained by dividing the magnetic pole position θ by the number of pole pairs Pm. When n = 1, the rotation angle is the 1f component, and when n = 2, the rotation angle is the 2f component. Using this rotation angle θn (n is a natural number), Ax_nr is multiplied by sin θn and cos θn, and these are integrated to perform Fourier transform to obtain an and bn.

  By performing proportional integral (PI) control so that the obtained an and bn become 0, and multiplying again by sin θn and cos θn, the vibration compensation amount Vib_c can be obtained (vibration suppression compensation amount calculating means 21). . Here, although proportional integral control is used, there is no problem in using generally used control such as proportional control and integral control.

  Furthermore, although the specific frequency component is extracted using Fourier transform, there is no problem even if means for extracting the frequency such as Fourier series expansion, fast Fourier transform, discrete Fourier transform, wavelet transform or the like is used.

  Further, when control is performed by a microcomputer or the like, it is affected by dead time and the like, and therefore, by providing phase adjusting means 22 for adjusting the phase as shown in FIG. 16, the influence of control delay due to dead time is eliminated. Thus, vibration can be reliably suppressed. The amount of phase adjustment by the phase adjusting means 22 may be set to a phase that decreases by detecting the increase or decrease of vibration.

  According to the motor drive device 200 of the first modification, it is possible to suppress the vibration generated by the rotation of the motor 3 using the vibration detected by the vibration sensor (vibration detection means 5). In addition, since vibrations to the devices connected to the motor are reduced, it is possible to suppress breakage due to vibration and generation of noise, and thus it is possible to obtain a highly reliable motor driving device 200.

  From the output of the vibration detection means 5, it becomes possible to remove the whirling vibration that cannot be suppressed by the control of the motor 3 by the vibration separation means 6, and it is possible to suppress abnormal vibration due to the divergence of the control system. The motor drive device 200 with high performance can be obtained.

  Further, since only the specific frequency component is extracted from the detected vibration, it is possible to eliminate the disturbance vibration component even when the vibration due to the disturbance or the like is detected by the vibration detecting means 5. Therefore, it is possible to minimize the influence on the control system, and it is possible to obtain a highly reliable motor driving device 200.

  Further, since the tangential vibration can be detected with high accuracy by only one vibration detecting means 5, not only the cost increase by the plurality of vibration detecting means 5 can be suppressed, but also the wiring of the vibration detecting means 5 can be simplified.

Embodiment 2. FIG.
FIGS. 17 to 43 are diagrams showing the second embodiment, FIG. 17 is a configuration diagram of a motor driving device 300 that drives the compressor 24, and FIG. 18 is a refrigerant of an air conditioner 400 that uses the compressor 24 in a refrigeration cycle. 19 is an exploded perspective view of the outdoor unit 400A of the air conditioner 400, FIG. 20 is a longitudinal sectional view of the compressor 24, FIG. 21 is a sectional view taken along the line AA in FIG. 20, and FIG. FIG. 23 is a top view of the compressor terminal protective cover 160, FIG. 24 is a side view of the compressor terminal protective cover 160 (part is shown in cross section), FIG. 26 is a bottom view of the compressor terminal protective cover 160, FIG. 26 is a cross-sectional view taken along the line XX in FIG. 23, FIG. 27 shows the vicinity of the portion Y in FIG. Figure showing in cross section, FIG. FIG. 29 is a perspective view of the compressor terminal protective cover 160 as viewed from above, FIG. 29 is a perspective view of the compressor terminal protective cover 160 as viewed from the bottom, and FIG. 30 is a perspective view of the substrate assembly 270 as viewed from the acceleration sensor 272 side. 31 is an exploded perspective view of the substrate assembly 270 as viewed from the acceleration sensor 272 side, FIG. 32 is a perspective view of the substrate assembly 270 as viewed from the opposite side of the acceleration sensor 272, and FIG. 33 is a view of the substrate holding member 280 as viewed from above. 34 is a top view of the board retainer component 280, FIG. 35 is a side view of the substrate retainer component 280, FIG. 36 is a perspective view of the substrate retainer component 280 viewed from the bottom, and FIG. 37 is a bottom view of the substrate retainer component 280. 38 is an enlarged perspective view of the first locking portion 281, FIG. 39 is an enlarged perspective view of the second locking portion 284, FIG. 40 is a basic configuration diagram of the acceleration sensor 272, and FIG. 41 is a compressor terminator. 42 is an exploded view showing a state before the mold 203 of the protective cover 160 is set, FIG. 42 is a view showing a state where the mold 203 of the compressor terminal protective cover 160 is set, and FIG. 43 is a terminal protective cover for the compressor. It is a figure which shows the manufacturing process of 160. FIG.

  A motor driving device 300 shown in FIG. 17 drives a compressor 24 used in a refrigeration cycle such as an air conditioner, a heat pump water heater, and a refrigerator. Note that an air conditioner, a heat pump water heater, a refrigerator, and the like are defined as a refrigeration cycle apparatus.

  First, an electronic component that detects the triaxial acceleration of the compressor using the piezoresistive effect is provided to prevent the terminal that supplies power to the compressor from dust and water, and to prevent contact with conductive foreign objects. Before describing a terminal protective cover manufactured by integrally molding a thermosetting resin so as to embed a substrate on which the vibration detecting means 5 of Embodiment 1) is embedded in the top surface of the terminal protective cover, A refrigerant circuit (refrigeration cycle) using a compressor provided with a terminal and an air conditioner outdoor unit where the compressor is installed will be described.

As shown in FIG. 18, the refrigerant circuit of the air conditioner is mainly composed of the following elements, and these elements are sequentially connected to constitute a refrigeration cycle.
(1) a compressor 24 for compressing refrigerant;
For example, a rotary compressor (single cylinder) is mainly used for the compressor 24 of an air conditioner (small type). In a rotary compressor (single cylinder), the rolling piston rotates eccentrically with respect to the rotating shaft (main shaft), causing unbalanced vibrations that synchronize with the rotational speed, causing whirling vibrations, and load torque during compression. Since the fluctuation occurs in synchronization with the rotation speed, a speed ripple is generated and a tangential vibration is generated. In addition to the rotary compressor, a scroll compressor or the like is also used. R410A is mainly used as the refrigerant. In addition, as the lubricating oil of the compressor 24, incompatible oil, ester oil, ether oil or the like is used.
(2) a four-way valve 32 for switching the flow direction of the refrigerant between the cooling operation and the heating operation;
As shown by the solid line in FIG. 18, the four-way valve 32 is used during the heating operation so that the refrigerant flows from the compressor 24 to the outdoor heat exchanger 33 and from the indoor heat exchanger 35 to the compressor 24 during the cooling operation. 18, the refrigerant 24 operates from the compressor 24 to the indoor side heat exchanger 35 and from the outdoor side heat exchanger 33 to the compressor 24.
(3) Outdoor heat exchanger 33 that operates as a condenser during cooling operation and as an evaporator during heating operation;
(4) A decompression device 34 (for example, an electronically controlled expansion valve) that decompresses the high-pressure liquid refrigerant into a low-pressure gas-liquid two-phase refrigerant;
(5) An indoor heat exchanger 35 that operates as an evaporator during cooling operation and as a condenser during heating operation.

  The solid arrows in FIG. 18 indicate the direction in which the refrigerant flows during the cooling operation. Moreover, the broken line arrow of FIG. 18 shows the direction through which the refrigerant flows during the heating operation.

  The outdoor heat exchanger 33 is provided with an outdoor fan 36 (for example, an axial fan), and the indoor heat exchanger 35 is provided with an indoor fan 37 (for example, a once-through fan).

  During the cooling operation, the compressed high-temperature and high-pressure refrigerant is discharged from the compressor 24 and flows into the outdoor heat exchanger 33 through the four-way valve 32. In the outdoor heat exchanger 33, outdoor air passes between the fins of the outdoor heat exchanger 33 and the tubes (heat transfer tubes) by an outdoor fan 36 (for example, an axial fan) provided in the air passage. While exchanging heat with the refrigerant, the refrigerant is cooled to a high pressure liquid state, and the outdoor heat exchanger 33 acts as a condenser. After that, the pressure is reduced through a decompression device 34 (for example, an electronically controlled expansion valve), and becomes a low-pressure gas-liquid two-phase refrigerant and flows into the indoor heat exchanger 35. In the indoor heat exchanger 35, indoor air passes between the fins of the indoor heat exchanger 35 and the tubes (heat transfer tubes) by driving an indoor blower 37 (for example, a cross-flow fan) attached to the air passage. By exchanging heat with the refrigerant, the air blown into the indoor space is cooled, while the refrigerant receives heat from the air and evaporates into a gaseous state (the indoor heat exchanger 35 acts as an evaporator). Thereafter, the flow returns to the compressor 24. The indoor space is air-conditioned (cooled) by the air cooled by the indoor heat exchanger 35.

  Further, during the heating operation, the four-way valve 32 is inverted, so that the refrigerant flows in the direction opposite to the refrigerant flow during the cooling operation in the refrigeration cycle, and the indoor heat exchanger 35 is used as a condenser to perform outdoor heat exchange. Vessel 33 acts as an evaporator. The indoor space is air-conditioned (heated) by the air heated by the indoor heat exchanger 35.

As shown in FIG. 19, the outdoor unit 400A of the air conditioner 400 is mainly configured by the following elements.
(1) A substantially L-shaped outdoor heat exchanger 33 in plan view;
(2) A bottom plate 38 (base) constituting the bottom of the casing of the outdoor unit 400A;
(3) A flat top panel 39 constituting the top surface of the housing;
(4) a substantially L-shaped front panel 40 in a plan view that constitutes the front surface and one side of the housing;
(5) Side panel 41 constituting the other side of the housing;
(6) Separator 42 that separates the air passage (blower room) and the machine room;
(7) an electrical box 43 for storing electrical products;
(8) a compressor 24 for compressing the refrigerant;
(9) Refrigerant piping / refrigerant circuit components 44 forming a refrigerant circuit;
(10) An outdoor fan 36 that blows air to the outdoor heat exchanger 33.

  Next, the compressor 24 will be described by taking a rotary compressor (single cylinder) as an example with reference to FIGS. 20 to 22. The compressor 24 (rotary compressor (single cylinder)) shown in FIGS. 20 to 22 is a vertical type in which the inside of the hermetic container 170 is high-pressure. A compression element 165 (an example of a load) is housed in the lower part of the hermetic container 170. An electric element 150 (for example, an induction motor) that drives the compression element 165 is accommodated above the compression element 165 in the upper part of the hermetic container 170. Here, although an induction motor is shown as the electric element 150, a brushless DC motor may be used.

  Refrigerating machine oil 190 that lubricates the sliding portions of the compression element 165 is stored at the bottom of the sealed container 170.

  First, the configuration of the compression element 165 will be described. A cylinder 101 in which a compression chamber is formed has a cylinder chamber 101b (see FIG. 21) that is a space having a substantially circular outer periphery in plan view and a substantially circular space in plan view. The cylinder chamber 101b is open at both ends in the axial direction. The cylinder 101 has a predetermined axial height in a side view.

  A parallel vane groove 101a (see FIG. 21) that communicates with a cylinder chamber 101b that is a substantially circular space of the cylinder 101 and extends in the radial direction is provided so as to penetrate in the axial direction.

  Further, a back pressure chamber 101c (see FIG. 21) that is a substantially circular space in plan view communicating with the vane groove 101a is provided on the back surface (outside) of the vane groove 101a.

  A suction port (not shown) through which suction gas from the refrigeration cycle passes through the cylinder 101 penetrates from the outer peripheral surface of the cylinder 101 to the cylinder chamber 101b.

  The cylinder 101 is provided with a discharge port (not shown) in which the vicinity of the edge of the circle forming the cylinder chamber 101b which is a substantially circular space (the end face on the electric element 150 side) is cut out.

  The material of the cylinder 101 is gray cast iron, sintered, carbon steel or the like.

  The rolling piston 102 rotates eccentrically in the cylinder chamber 101b. The rolling piston 102 has a ring shape, and the inner periphery of the rolling piston 102 is slidably fitted to the eccentric shaft portion 50 a of the rotating shaft 50.

  Since the rolling piston 102 is slidably fitted to the eccentric shaft portion 50a of the rotating shaft 50 and rotates eccentrically in the cylinder chamber 101b, unbalanced vibration is generated in synchronization with the rotation speed, and the whirling vibration is generated. appear. Although there is a method of reducing the whirling vibration by attaching a balance weight (not shown) to the rotor 111 of the electric element 150, it is not sufficient.

  The outer periphery of the rolling piston 102 and the inner wall of the cylinder chamber 101b of the cylinder 101 are assembled so that there is always a certain gap.

  The material of the rolling piston 102 is alloy steel containing chromium or the like.

  The vane 103 is accommodated in the vane groove 101a of the cylinder 101, and the vane 103 is always pressed against the rolling piston 102 by the vane spring 108 (see FIG. 20) provided in the back pressure chamber 101c. Since the compressor 24 (rotary compressor) has a high pressure inside the hermetic container 170, when the operation is started, the high pressure in the hermetic container 170 and the pressure in the cylinder chamber 101b are placed on the back surface (back pressure chamber 101c side) of the vane 103. Since the force due to the differential pressure acts, the vane spring 108 mainly moves the vane 103 to the rolling piston when the compressor 24 (rotary compressor) is started (the pressure in the sealed container 170 and the cylinder chamber 101b is not different). Used for the purpose of pressing to 102.

  The shape of the vane 103 is a flat shape (the thickness in the circumferential direction is smaller than the length in the radial direction and the axial direction).

  As the material of the vane 103, high-speed tool steel is mainly used.

  The main bearing 104 is slidably fitted to a main shaft portion 50b (a portion above the eccentric shaft portion 50a and a portion that fits the rotor 111) of the rotating shaft 50, and a cylinder chamber 101b (vane) of the cylinder 101. One end face (including the groove 101a) (on the electric element 150 side) is closed.

  The main bearing 104 includes a discharge valve (not shown). However, it may be attached to either one or both of the main bearing 104 and the sub-bearing 105.

  The main bearing 104 has a substantially inverted T shape when viewed from the side.

  The secondary bearing 105 is slidably fitted to the secondary shaft portion 50c (a portion below the eccentric shaft portion 50a) of the rotating shaft 50, and the other end surface of the cylinder chamber 101b (including the vane groove 101a) of the cylinder 101. (Refrigerating machine oil 190 side) is closed.

  The secondary bearing 105 is substantially T-shaped when viewed from the side.

  The material of the main bearing 104 and the sub bearing 105 is the same as that of the cylinder 101, and is made of gray cast iron, sintered, carbon steel, or the like.

  A discharge muffler 107 is attached to the main bearing 104 on the outer side (the electric element 150 side). The high-temperature and high-pressure discharge gas discharged from the discharge valve of the main bearing 104 enters the discharge muffler 107 at one end, and is then discharged from the discharge muffler 107 into the sealed container 170. However, there may be a discharge muffler 107 on the sub-bearing 105 side.

  A suction muffler 121 is provided beside the hermetic container 170 to suck low-pressure refrigerant gas from the refrigeration cycle and prevent liquid refrigerant from being directly sucked into the cylinder chamber of the cylinder 101 when the liquid refrigerant returns. The suction muffler 121 is connected to the suction port of the cylinder 101 via the suction pipe 122. The main body of the suction muffler 121 is fixed to the side surface of the sealed container 170 by welding or the like.

  A terminal 124 (referred to as a glass terminal) connected to a power source that is a power supply source is fixed to the sealed container 170 by welding. In the example of FIG. 20, the terminal 124 is provided on the upper surface of the sealed container 170. A lead wire 123 from the stator 112 (winding 120) of the electric element 150 is connected to the terminal 124.

  A discharge pipe 125 having both ends opened is inserted into the upper surface of the sealed container 170. The discharge gas discharged from the compression element 165 is discharged from the sealed container 170 through the discharge pipe 125 to the external refrigeration cycle.

  A general operation of the compressor 24 (rotary compressor (single cylinder)) will be described. When electric power is supplied from the terminal 124 and the lead wire 123 to the stator 112 of the electric element 150, the rotor 111 rotates. Then, the rotating shaft 50 fixed to the rotor 111 rotates, and accordingly, the rolling piston 102 rotates eccentrically in the cylinder chamber 101b of the cylinder 101. A space between the cylinder chamber 101 b of the cylinder 101 and the rolling piston 102 is divided into two by a vane 103. As the rotary shaft 50 rotates, the volume of these two spaces changes, the volume gradually increases on one side and the refrigerant is sucked from the suction muffler 121, and the volume gradually decreases on the other side. The refrigerant gas is compressed. The compressed discharge gas is once discharged from the discharge muffler 107 into the sealed container 170, further passes through the electric element 150, and is discharged out of the sealed container 170 through the discharge pipe 125 on the upper surface of the sealed container 170.

  The discharge gas passing through the electric element 150 includes, for example, an air hole portion (through hole, not shown) of the rotor 111 of the electric element 150 and a slot opening (not shown, also referred to as a slot opening portion) of the stator core 112a. It passes through a gap (not shown), a stator notch (not shown) disposed on the outer periphery of the stator core 112a, and the like.

The parts constituting the sliding portion provided in the compression element 165 are collected.
(1) cylinder 101;
(2) rolling piston 102;
(3) Vane 103;
(4) main bearing 104;
(5) Sub bearing 105;
(6) Rotating shaft 50.

  Outside the sealed container 170, the conductive portion is exposed near the terminal 124 (glass terminal) to which a lead wire is connected from an external power source, and when it is directly incorporated into the outdoor unit of the air conditioner, dust, water, There is a risk that the terminal 124 may have poor insulation due to conductive foreign matter or the like.

  Therefore, a compressor terminal protective cover for protecting the portion exposed to the outside of the terminal 124 from dust, water, conductive foreign matter, and the like is necessary.

  As shown in the external view of the compressor 24 in FIG. 22, the compressor terminal protective cover 160 is fixed to the compressor 24 by using a rod 146 erected on the upper surface of the hermetic container 170 of the compressor 24. .

  The nut 147 is fastened to the threaded portion 146 a of the rod 146 to fix the compressor terminal protective cover 160 to the rod 146.

  The compressor terminal protective cover 160 will be described with reference to FIGS. 23 to 26. The compressor terminal protective cover 160 is formed by molding with a thermosetting resin such as BMC (unsaturated polyester).

  As shown in FIGS. 23 to 26, the mold part 161 includes a terminal protection part 163 and a foot part 162. The terminal protector 163 is a part that covers the terminal 124 of the compressor 24 and protects the terminal 124 from dust, water, conductive foreign matter, and the like (see FIG. 27). Further, the compressor terminal protective cover 160 is fixed to the rod 146 of the hermetic container 170 of the compressor 24 by the feet 162.

  Although details will be described later, a board assembly 270 in which a triaxial acceleration sensor is mounted on a board is embedded in the top surface portion of the terminal protection section 163.

  The board assembly 270 in which the 3-axis acceleration sensor is mounted on the board is characterized in that it is embedded in the compressor terminal protective cover 160.

  A screw hole 162 a that is inserted into the rod 146 (see FIG. 22) of the sealed container 170 of the compressor 24 is provided on the upper surface of the foot portion 162.

  FIG. 27 shows the vicinity of the portion Y in FIG. 22 and shows the compressor terminal protective cover 160 in the XX section of FIG. 23. Specifically, as shown in FIG. The screw hole 162a provided in the foot part 162 of the protective cover 160 is passed through the rod 146, and the screw hole 162a is brought into contact with the stepped part 146b of the rod 146 (the part having a diameter larger than the tip part of the rod 146). At this time, the compressor terminal protection cover 160 and the sealed container 170 are configured to have a predetermined gap (several millimeters). Without this predetermined gap, the axial position of the compressor terminal protective cover 160 relative to the hermetic container 170 cannot be determined. If the predetermined gap is too large, dust, water, conductive foreign matter, etc. may enter the terminal 124.

  Further, the nut 147 is fastened to the threaded portion 146 a to fix the compressor terminal protective cover 160 to the rod 146.

  The compressor terminal protective cover 160 will be further described with reference to FIGS. 28 and 29. As described above, the compressor terminal protective cover 160 covers the terminal 124 of the compressor 24 and protects the terminal 124 from dust, water, conductive foreign matter, and the like, and the compressor 24 is hermetically sealed. A substrate assembly 270 is embedded in a mold part 161 including a foot part 162 fixed to the rod 146 of the container 170.

  As shown in FIG. 28, the end surface of the protrusion 285 of the board pressing component 280 described later is exposed on the upper surface of the terminal protection portion 163. This point will be described later.

  As shown in FIG. 29, a protrusion 283 of a board pressing component 280 to be described later protrudes from the bottom surface of the terminal protection part 163. This point will also be described later.

  30 to 32, the board assembly 270 includes a board 271 on which at least the acceleration sensor 272 is mounted, a board-in connector 275 to which a lead wire 274 is connected and soldered to the board 271, and a lead wire. And a lead wire lead part 273 that feeds out 274 and a board pressing part 280 assembled to the board 271.

  Cutouts 276a to which the first locking portions 281 (three) and the second locking portions 284 (one) of the board pressing component 280 are locked are formed on the outer peripheral edge of each side of the substantially square substrate 271. 276b is formed.

  The notches 276a and 276b are substantially square, but are not limited thereto. Any shape is acceptable.

  The two notches 276a are formed at substantially the center of two sides adjacent to the side to which the board-in connector 275 is soldered. The two notches 276a face each other with the acceleration sensor 272 therebetween.

  One first locking portion 281 and one second locking portion 284 are locked to the two notches 276a.

  The notch 276b formed on the side to which the board-in connector 275 is soldered is formed at a position shifted from the center of the side so as not to overlap the board-in connector 275.

  The notch 276b on the opposite side of the side to which the board-in connector 275 is soldered is formed symmetrically with the notch 276b formed on the side to which the board-in connector 275 is soldered.

  Two first locking portions 281 are locked to the two notches 276b.

  The board pressing component 280 will be described in detail with reference to FIGS. As shown in the figure, the board pressing component 280 has a substantially rectangular frame shape as a whole. The substrate pressing component 280 has protrusions 285 (four) standing upright at four corners of the surface of the substrate 271 on the acceleration sensor 272 side.

  The substrate pressing component 280 is formed by injection molding a thermoplastic resin such as PBT (polybutylene terephthalate).

  The four protrusions 285 of the board holding member 280 are positioned in one of the axial directions of the board assembly 270 (axial direction when attached to the compressor 24) when the compressor terminal protective cover 160 is molded. .

  Therefore, as shown in FIG. 28, the end surfaces of the four protrusions 285 of the board pressing component 280 are exposed on the upper surface of the terminal protection part 163 of the compressor terminal protection cover 160.

  The board holding component 280 is formed in the shape of a substantially rectangular frame by the four connecting portions 286.

  The first locking portions 281 (three) and the second locking portions 284 (one) are formed on the surfaces of the four connecting portions 286 opposite to the protrusions 285.

  The first anchoring portion 281 includes a substantially prismatic foot portion 282 extending from the connecting portion 286, and a substantially cylindrical protrusion 283 formed at the tip of the foot portion 282 (see particularly FIG. 38). Further, a step portion 282 a is formed on the foot portion 282 of the first locking portion 281. The foot 282 fits into the notches 276a and 276b of the substrate 271, and the substrate 271 is sandwiched between the connecting portion 286 and the stepped portion 282a, whereby the substrate pressing component 280 is fixed to the substrate 271. However, a second anchoring portion 284 described later also has the same function, and the substrate pressing component 280 is held by the substrate by holding the substrate 271 between the first anchoring portion 281 and the second anchoring portion 284. 271 is fixed.

  Assembling of the substrate holding component 280 and the substrate 271 is performed by fitting the foot portion 282 and the second locking portion 284 of the first locking portion 281 of the substrate pressing component 280 into the notches 276a and 276b of the substrate 271. As much as possible, the positional deviation of the substrate 271 in the horizontal direction and the rotational direction can be prevented.

  The end surface of the first locking portion 281 opposite to the stepped portion 282a of the foot portion 282 is formed in the axial direction of the board assembly 270 (when attached to the compressor 24) when the compressor terminal protective cover 160 is molded. This is a mold installation surface 287 (see FIG. 35) which is the other positioning in the axial direction).

  At the time of molding of the compressor terminal protective cover 160, the mold is molded by sandwiching the four protrusions 285 of the substrate pressing component 280 and the three mold installation surfaces 287, thereby forming the substrate 271. Positioning in the axial direction can be performed.

  At the time of molding of the compressor terminal protective cover 160, substantially cylindrical projections 283 (three) formed at the tip of the foot portion 282 of the first locking portion 281 are formed in corresponding holes (described later) of the mold. ) And molding, it is possible to prevent displacement of the substrate 271 in the horizontal direction and the rotational direction due to the molding pressure during molding.

  The second anchoring portion 284 (having the stepped portion 284a) corresponds to a substantially cylindrical protrusion 283 formed at the tip of the foot portion 282 of the first anchoring portion 281 as shown in FIG. Does not have a part. The reason for this will be described below.

  As shown in FIGS. 35 and 36, the first surface of the board pressing component 280 on the back surface of the terminal protection portion 163 of the compressor terminal protection cover 160 (the surface on the side of the sealed container 170 when attached to the compressor 24). Three substantially cylindrical projections 283 formed at the tip of the foot portion 282 of the anchoring portion 281 are projected.

  The second locking portion 284 is buried in the side wall 163a of the terminal protection portion 163 of the compressor terminal protection cover 160 after molding. As described above, even if the protrusion 283 equivalent part is formed in the second locking part 284, it is buried inside the side wall 163a of the terminal protection part 163 and does not protrude to the outside. Therefore, the second locking part 284 includes A portion corresponding to the substantially cylindrical protrusion 283 formed at the tip of the foot portion 282 of the one locking portion 281 is not formed.

  Here, the acceleration sensor 272 will be described. The acceleration sensor 272 is a small sensor that can detect a physical quantity such as acceleration (in addition, force, magnetism) for each of the three-dimensional components, and forms a gauge resistance on a semiconductor substrate such as silicon so that an external force is applied. Based on this, the mechanical distortion generated in the substrate is converted into an electrical signal using the piezoresistance effect. The basic principle is disclosed, for example, in the international application (WO 93/02342).

  The acceleration sensor 272 shown in FIG. 40 is a triaxial force / moment sensor that detects triaxial force / moment. In the acceleration sensor 272, a Si substrate 292 (a strain body) is fixed to a pedestal 291, and a weight body 293 is bonded to the Si substrate 292 (a strain body).

  The force applied to the Si substrate 292 causes distortion in a piezoresistor (not shown) formed on the Si substrate 292. The electrical resistance of the piezoresistor changes in proportion to the strain based on the piezoresistance effect. The force is detected using this resistance change.

  A diaphragm is formed on the Si substrate 292, and the Si substrate 292 serves as a strain generating body, thereby functioning as a three-axis acceleration sensor.

  Three sets of gauge resistors for detecting triaxial acceleration components are formed on the surface of the Si substrate 292. An annular diaphragm is formed on the back surface of the Si substrate 292, a weight body 293 is joined to the center portion, and a pedestal 291 is joined to the peripheral portion.

  When acceleration in the X or Y axis direction or the Z axis direction acts on the weight body 293, the annular diaphragm is displaced in each direction. At this time, each axis acceleration can be detected independently by connecting a gauge resistor formed on the Si substrate 292 to the bridge circuit.

  As shown in FIGS. 41 and 42, the mold 203 of the compressor terminal protective cover 160 includes an upper mold 201 and a lower mold 202.

  When molding the terminal protective cover 160 for the compressor, the substantially cylindrical projections 283 (three) formed at the tip of the foot 282 of the first locking portion 281 are inserted into the corresponding holes 204 of the mold. Thus, by performing the molding, it is possible to prevent the positional deviation of the substrate 271 in the horizontal direction and the rotation direction due to the molding pressure during molding.

The manufacturing process of the compressor terminal protective cover 160 will be described with reference to FIG.
(1) Step 1: A substrate 271 is manufactured. On the substrate 271, an acceleration sensor 272 for detecting the acceleration of the compressor 24 using the piezoresistance effect is mounted. Further, a lead wire lead-out component 273 that leads out the lead wire 274 is attached to the substrate 271 in the vicinity of the outer peripheral edge thereof. At the same time, the substrate pressing component 280 is manufactured using a thermoplastic resin.
(2) Step 2: The substrate pressing component 280 is fixed to the substrate 271. A substrate pressing component 280 formed by injection molding a thermoplastic resin such as PBT (polybutylene terephthalate) is assembled to the substrate 271 to which the lead wire lead-out component 273 is attached, and the substrate assembly 270 is manufactured.
(3) Step 3: The substrate assembly 270 is molded with a thermosetting resin such as BMC (unsaturated polyester) to manufacture the terminal protective cover 160 for a compressor.

  In the compressor terminal protective cover 160 configured as described above, the rod 146 provided in the compressor 24 is provided via the screw hole 162a provided in the foot portion 162 of the compressor terminal protective cover 160. By screwing and fixing to the screw portion 146a, the acceleration sensor 272 can be assembled to the compressor 24 without increasing the manufacturing process of the compressor 24.

  Further, the first locking portion 281 and the second locking portion 284 of the substrate pressing component 280 are locked and assembled to the substrate 271, and the mold 203 is connected to the protrusion 285 and the first locking portion 281. By sandwiching and molding, the substrate 271 can be positioned in the axial direction.

  Further, by inserting a projection 283 provided at the tip of the first locking portion 281 of the substrate pressing component 280 into the corresponding hole 204 of the mold 203, and molding the substrate, the substrate is formed by the molding pressure at the time of molding. It is possible to prevent the positional deviation of the horizontal direction 271 and the rotational direction.

  Further, the foot holding part 280 and the second locking part 284 of the first locking part 281 provided in the board holding part 280 are fitted into the notches 276a and 276b provided in the board 271, so that the board pressing part 280 and the board 271 are fitted. It is possible to prevent the positional deviation of the substrate 271 in the horizontal direction and the rotational direction by reducing as much as possible the looseness with respect to the assembly.

  The compressor 24 (rotary compressor (single cylinder)) generates whirling vibration and tangential vibration. As described in the first embodiment, the vibration separating means 6 removes the whirling vibration of the compressor 24 (rotary compressor (single cylinder)), extracts only the tangential vibration, and extracts the specific frequency component extracting means 23. Only the vibration component synchronized with the rotation speed is extracted by Fourier transform or the like, and the vibration compensation control means 7 obtains the vibration compensation amount, whereby the vibration caused by the rotation of the compressor 24 can be suppressed.

  According to the present embodiment, the vibration generated by the rotation of the motor 3 (corresponding to the electric element 150) in the compressor 24 is suppressed by using the vibration detected by the vibration detecting means 5 (acceleration sensor 272). Therefore, the vibration of the motor 3 itself, the compressor 24, the piping connected to the compressor 24, and the like is reduced, so that it is possible to suppress the breakdown and the generation of noise due to the vibration. It becomes possible to obtain a high air conditioner or a heat pump type hot water heater (an apparatus using the compressor 24).

  Since it is possible to remove the whirling vibration that cannot be suppressed by the control of the motor 3 from the output of the vibration detection means 5, it is possible to suppress abnormal vibration due to divergence of the control system. A highly reliable compressor 24, an air conditioner using the compressor 24, and a heat pump water heater can be obtained.

  Further, since the tangential vibration can be detected with high accuracy by only one vibration detecting means 5, not only the cost increase by the plurality of vibration detecting means 5 can be suppressed, but also the wiring of the vibration detecting means 5 can be simplified.

  Furthermore, by embedding the vibration detecting means 5 in the resin of the cover (compressor terminal protective cover 160) that protects the terminals of the compressor, insulation can be secured even when attached to the compressor 24 where leakage current occurs. The reliability of the vibration detecting means 5 can be improved.

Embodiment 3 FIG.
FIG. 44 is a diagram showing the third embodiment, and is a configuration diagram of a motor driving device 500 that drives the washing drum 25. Since the motor 3 in FIG. 1 is the same except that the washing drum 25 is replaced, the same portions are denoted by the same reference numerals and the description thereof is omitted.

  44, an oblique drum type washing machine having the largest vibration among the washing machines will be described. The washing drum 25 (an example of a load) of the oblique drum washing machine removes dirt by tapping and washing by lifting clothes from the washing drum 25 and dropping them from the sky. At that time, the load applied to the motor (not shown) increases when the moisture-containing clothes are lifted by the rotation of the washing drum 25, and the load decreases when the clothes are dropped from the sky. In addition, vibrations synchronized with the rotational speed are generated due to speed ripples caused by load torque fluctuations.

  Therefore, as described in the first embodiment, by extracting only the vibration component synchronized with the rotation speed by the specific frequency component extraction means 23 by Fourier transform or the like, the vibration caused by the fall of the moisture-containing clothing is removed. Then, by obtaining the vibration compensation amount by the vibration suppression control means 7, it is possible to suppress the vibration caused by the rotation of the washing drum 25.

  According to the present embodiment, it is possible to suppress vibration generated by rotation of a motor (not shown) that drives the washing drum 25 using vibration detected by the vibration detection means 5. The vibration of the washing drum 25 can be reduced, and a washing / drying machine with high user merit capable of performing washing can be obtained without disturbing other residents even at night.

  In addition, by removing the vibration component from the output of the vibration separating means 6 when the clothes containing moisture at the time of washing, which is a disturbance, are dropped by the specific frequency component extracting means 23, stable vibration can be suppressed. A highly reliable motor driving device 500 can be obtained.

  Further, since the tangential vibration can be detected with high accuracy by only one vibration detecting means 5, not only the cost increase by the plurality of vibration detecting means 5 can be suppressed, but also the wiring of the vibration detecting means 5 can be simplified.

  Further, the vibration output correcting means 27 can automatically correct an output value including an error when the vibration detecting means 5 is not attached at an ideal installation position and installation angle to an accurate output value. Therefore, highly reliable and highly accurate control becomes possible.

Embodiment 4 FIG.
FIG. 45 is a diagram showing the fourth embodiment, and is a configuration diagram of a motor driving device 600 that drives the blower fan 26. Since it is the same except that the blower fan 26 is connected to the motor 3 in FIG. 1, the same reference numerals are given to the same portions, and the description is omitted.

  The motor 3 generates torque pulsation having a frequency n times the rotational speed due to the cogging torque generated structurally, and generates weak vibration. When the motor 3 is applied to the blower fan 26 (an example of a load), weak vibration is transmitted to the blower fan 26 and noise may be generated from the blower fan 26.

  Therefore, as described in the first embodiment, the specific frequency component extraction unit 23 extracts only the vibration component synchronized with n times the rotational speed, which is the cogging torque component, by Fourier transformation or the like, so that the cogging torque component is extracted. , And the vibration suppression control means 7 obtains the vibration compensation amount, so that the vibration due to the cogging torque of the motor 3 can be suppressed and the noise of the blower fan 26 can be suppressed.

  According to the present embodiment, it is possible to suppress the vibration generated by the rotation of the motor 3 that drives the blower fan 26 using the vibration detected by the vibration detecting means 5, so that the motor caused by the vibration generation 3 and the aging deterioration of the blower fan 26 can be suppressed, and noise generated from the blower fan 26 can also be suppressed, so that a highly reliable and low noise blower can be obtained.

  Further, since the tangential vibration can be detected with high accuracy by only one vibration detection means 5, not only the cost increase by the plurality of vibration detection means 5 can be suppressed, but also the wiring of the vibration detection means 5 can be simplified.

  Furthermore, in the case of the resin mold type blower fan 26, the vibration detection means 5 is embedded in the resin mold, thereby ensuring insulation and suppressing the influence of deterioration due to wind and rain, and improving the reliability of the vibration detection means 5. It becomes possible.

  Further, the vibration output correcting means 27 can automatically correct an output value including an error when the vibration detecting means 5 is not attached at an ideal installation position and installation angle to an accurate output value. Therefore, highly reliable and highly accurate control becomes possible.

  Examples of use of the present invention are not limited to refrigeration cycles using motor drive devices such as refrigerators, refrigerators, heat pump water heaters as well as air conditioners, but also home appliances such as hand dryers, vacuum cleaners, ventilation fans, and elevators It can also be applied to railways, vehicles, etc.

  1 DC power supply, 2 inverter, 3 motor, 4 inverter control means, 5 vibration detection means, 6 vibration separation means, 7 vibration suppression control means, 8 current detection means, 9 DC voltage detection means, 10 rotating coordinate conversion means, 11 voltage Control means, 12 Reverse rotation coordinate conversion means, 13 PWM signal generation means, 14a switching element, 14b switching element, 14c switching element, 14d switching element, 14e switching element, 14f switching element, 15 speed controller, 16 d-axis current control 17 q-axis current controller 18 speed estimator 19 position estimator 20 HPF 21 vibration suppression compensation amount calculating means 22 phase adjusting means 23 specific frequency component extracting means 24 compressor 25 washing drum 26 Blower fan, 27 Vibration output correction means, 32 Directional valve, 33 outdoor heat exchanger, 34 decompression device, 35 indoor heat exchanger, 36 outdoor fan, 37 indoor fan, 38 bottom plate, 39 top panel, 40 front panel, 41 side panel, 42 separator, 43 Electrical box, 44 Refrigerant piping / refrigerant circuit parts, 50 Rotating shaft, 50a Eccentric shaft portion, 50b Main shaft portion, 50c Sub shaft portion, 100 Motor drive device, 101 cylinder, 101a vane groove, 101b Cylinder chamber, 101c Back pressure Chamber, 102 Rolling piston, 103 vane, 104 Main bearing, 105 Sub bearing, 107 Discharge muffler, 108 Vane spring, 111 Rotor, 112 Stator, 121 Inhalation muffler, 122 Intake pipe, 123 Lead wire, 124 Terminal, 125 Discharge Tube, 146 rod, 146a Part, 146b step part, 147 nut, 150 electric element, 161 mold part, 162 foot part, 162a screw hole, 163 terminal protection part, 163a side wall, 165 compression element, 170 airtight container, 180 terminal protective cover for compressor, 190 Refrigerating machine oil, 200 Motor drive device, 201 Upper mold, 202 Lower mold, 203 Mold mold, 204 holes, 270 Board assembly, 271 Board, 272 Acceleration sensor, 273 Lead wire lead-out parts, 274 Lead wire, 275 Board-in connector 276a Notch, 276b Notch, 280 Substrate pressing part, 281 First locking part, 282 Foot, 282a Stepped part, 283 Protrusion, 284 Second locking part, 285 Projection, 286 Connecting part, 287 Gold Mold installation surface, 291 pedestal, 292 Si Substrate, 293 weight body, 300 motor driving device, 400 air conditioner, 400A outdoor unit, 500 motor driving device, 600 motor driving device.

Claims (21)

A motor driving the load;
An inverter for applying a voltage to the motor;
Inverter control means for controlling the voltage output by the inverter;
Vibration detecting means attached to a predetermined portion of the motor for detecting vibration of the motor;
Vibration output correcting means for correcting the output of the vibration detecting means;
Vibration separating means for separating a vibration component in a tangential direction with respect to the rotation axis of the motor from the output of the vibration output correcting means;
Vibration suppression control means for outputting a signal for suppressing vibration based on the output of the vibration separating means,
The inverter control means controls the voltage applied by the inverter based on the output of the vibration suppression control means.   The motor drive device according to claim 1, wherein the vibration detection unit can detect gravitational acceleration and can detect vibration directions of at least three axes.   3. The motor driving apparatus according to claim 2, wherein an angle formed by each of the vibration directions detected by the vibration detecting means is 90 degrees.   4. The motor driving apparatus according to claim 1, wherein at least two axes of vibration directions detected by the vibration detection means detect vibration directions perpendicular to a rotation axis of the motor.   5. The motor driving apparatus according to claim 1, wherein the vibration output correcting unit is operated before or when the motor is driven.   6. The vibration suppression control unit according to any one of claims 1 to 5, wherein the vibration suppression control unit does not operate when any output value detected by the vibration detection unit is other than a preset threshold value. The motor drive device described.   7. The vibration output correcting means does not operate the vibration suppression control means when a composite value of at least three axes in the vibration direction detected by the vibration detecting means does not coincide with gravitational acceleration. The motor drive device in any one of.   The vibration output correcting means uses at least one of the three vibration axes detected by the vibration detecting means for detecting the gravitational direction, and outputs the vibration detecting means so that the detected value of this axis coincides with the gravitational acceleration. The motor driving device according to claim 1, wherein the motor driving device is corrected. The vibration separating means includes
Rotational coordinate conversion means for converting the output of the vibration detection means into a rotational coordinate system based on the rotation angle of the motor;
Low frequency component removing means for removing the low frequency component of the output of the rotating coordinate conversion means;
9. The motor driving apparatus according to claim 1, further comprising reverse rotation coordinate conversion means for performing reverse rotation coordinate conversion on the output of the low frequency component removal means based on the rotation angle of the motor. The vibration suppression control means includes
A specific frequency component extracting means for extracting only a specific frequency component from the output of the vibration detecting means;
10. The motor driving apparatus according to claim 1, wherein a signal for suppressing vibration of the motor is output based on an output of the specific frequency component extracting means. The specific frequency component extracting means includes
The motor drive device according to claim 10, wherein a frequency component that is n (n is a natural number) times the rotation angle of the motor is extracted.   The inverter control means adds the output of the vibration suppression control means to the speed command, thereby generating a voltage command of a dq coordinate system for suppressing the vibration of the motor and performing voltage pole calculation. The motor driving apparatus according to claim 1, further comprising means.   The inverter control means is configured to adjust the q-axis current command using the output of the vibration suppression control means, thereby generating a dq coordinate system voltage command for suppressing the vibration of the motor, The motor driving apparatus according to claim 1, further comprising voltage control means for calculating a magnetic pole position.   The inverter control unit is configured to adjust the q-axis voltage command using the output of the vibration suppression control unit, thereby generating a voltage command of a dq coordinate system for suppressing the vibration of the motor, The motor driving apparatus according to claim 1, further comprising voltage control means for calculating a magnetic pole position.   The inverter control means is configured to operate the torque command using the output of the vibration suppression control means, thereby generating a dq coordinate system voltage command for suppressing the vibration of the motor, and the magnetic pole position. The motor drive apparatus according to claim 1, further comprising a voltage control unit that performs the following calculation.   A compressor comprising a compression element and an electric element, wherein the electric element is driven by the motor driving device according to any one of claims 1 to 15.   The compressor according to claim 16, wherein the compressor is a one-cylinder rotary compressor.   A refrigeration cycle apparatus equipped with the compressor according to claim 16 or 17.   A washing machine comprising the motor driving device according to any one of claims 1 to 15.   A washing / drying machine comprising the motor driving device according to any one of claims 1 to 15.   A blower comprising the motor driving device according to claim 1.

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