JPS60234092A - Automatic following type vibration arrester - Google Patents

Abstract

PURPOSE:To improve the following performance to vibration arrest by driving a vibration arrester by an electric motor and directly controlling the speed of the electric motor, in the captioned apparatus for arresting the abnormal vibration of a hull which is caused by the vibration of a main engine in a vessel. CONSTITUTION:A vibration arrester 1 is constituted from a pair of discs 4 and 5 which have gears 2 and 3 meshing each other on the outer periphery and have disequillibrium weights 6 and 7 having an equal weight at symmetrical positions, and said vibration arrester 1 is directly driven by an electric motor 8 through a driving gear 9 meshed with one disc 4. The electric motor 8 controls the frequency of the electric power supplied into the electric motor 8 by a frequency converter 11 controlled by a balance controller 19. Said balance controller 19 inputs each output of a main-machine speed detector 11, main-machine phase detector 14, vibration-arrester speed detector 16, and a vibration-arrester phase detector 17, and the above-described electric-power frequency is varied according to the revolution speed relation and the revolution phase relation between a main engine 12 and the vibration arrester 1.

Description

[Detailed Description of the Invention] [Technical Field of the Invention] The present invention eliminates or eliminates abnormal vibrations of a ship's hull caused by vibrations of reciprocating engines (hereinafter referred to as main engines) mounted on two ship C towers. The present invention relates to an automatic follow-up type vibration damping device.

[Technical background of the invention and its problems]

General C=The main engine of a ship generates unbalanced couples of first, second, etc. order when it is operated.

For this reason, this first-order, second-order... m-order unbalanced couple is
It resonates with the natural frequency m number of nodes 1 to n of the ship's hull, causing significant abnormal vibrations in the rotation of the main engine (corresponding nodes 1, 2, ... n nodes), which adversely affects the ship's hull. This often results in poor livability.

Therefore, the applicant has installed a vibration damper that generates vibrations as shown in Figure 1 at an appropriate location within the ship, such as the wheelhouse, which is known as a location suitable for canceling hull vibrations. (and increase this by +61 ja) Second, an automatic follow-up vibration damping device that eliminates or reduces abnormal vibrations of the hull is proposed in Japanese Patent Publication No. 52-30079 or Publication No. 56-44
It was proposed as Publication No. 296.

That is, FIG. 1 shows a vibration damper (1) that constitutes a part of an automatic follow-up vibration damping device. Figure 1 (2, (4)
) and (5) are the teeth (2) and (3) provided on the outer periphery, respectively (=therefore, they can engage with each other and rotate in opposite directions (=the provided disks, (
6).

(The force is exerted by two unbalanced weights of the same weight attached to the pair of discs 14) and +5) at symmetrical positions.

In this way (=configured vibration damper zl) is a disk t4),
When (5) is rotated, the unbalanced weight t61. Since the unbalanced force in the horizontal direction caused by the force is mutually canceled and only the vertical direction is added, the location where the vibration damper (1) is installed (=vertical direction and disk 14), The direction of the vibration generated from the force of the vibration damper (1) is not limited to the vertical direction (2), but the mounting position of to change (
It goes without saying that the vibration can be generated in any direction and can be matched to the vibration direction of the ship.

By the way, the vibration generated in the hull is canceled by the vibration damping + iA (1) configured in this way (= means that the discs (4) and (5) of the vibration damper (1) are equal to the number of revolutions of the main engine. For example, to cancel the vibrations of nodes 1 to n of the hull caused by the secondary unbalanced couple of the main engine, the main engine should be rotated at twice the rotational speed and the vibrations of the same frequency as that generated in the hull would be canceled. Damping flA (1
2) The rotation phase of the vibration damper (1) is adjusted so that the vibration generated from the vibration damper (1) is in opposite phase with the vibration generated from the ship body (2). It is necessary to control the phase relationship to minimize undesired vibrations of the hull.

Therefore, conventional automatic follow-up type vibration damping devices, for example, control the primary side manual pressure (by providing a magnetic motor (induced magnetic motion d&) that enables speed control directly at vibration damping@I'knee). ,
The input voltage of the magnetic motor was appropriately controlled according to the rotational speed relationship and rotational phase relationship (==) between the vibration absorber and the vibration absorber.

However, as mentioned above, the method of controlling the speed of the It had the following drawbacks: 1) The power factor and efficiency were poor, and the magnetic current flowing through the engine became very large.

■ For this reason, the capacity of the magnetic motor, the onboard magnet generator that supplies magnetic force, and the magnetic wiring are larger than necessary, which is a problem that rarely occurs as ships (2) are becoming lighter. It had become.

Therefore, in order to eliminate these drawbacks, the present applicant has developed a system in which the output rotation of the magnetic motor driven at a constant speed is controlled by a vortex flow joint and a vortex magnetic flow brake (two-way rotation i61), and the rotation drives the vibration damper. We have proposed a configuration in which the whirlpool joint and the whirlpool brake are appropriately controlled according to the rotational speed relationship and rotational phase relationship between the main engine and the vibration damper.

However, the above-mentioned vibration damping device also had the following drawbacks: ■ There were some problems with response due to the use of a thin first-flow joint with a large time constant and a whirlpool first-flow brake. When the rotational speed of the main engine suddenly changed due to such disturbances (the second vibration damper was sometimes unable to follow it).

■ As a result, not only was the vibration damping effect not achieved, but in the worst case, the vibration damper that was supposed to cancel the vibrations turned into a dual vibration exciter, which had an adverse effect on the ship's hull and livability.

Since a vibration damper generates vibration, bearings (= fretting) are likely to occur.For this reason, if a 9Z magnetic coupling, a 4# spiral, and a brake are used as vibration dampers, the number of bearings will increase accordingly. , there is a disadvantage that there are many failure points due to fretting.

■ Machinery losses will also increase.

[Purpose of the invention]

The present invention has good followability even if the rotational speed of the 4iA valve changes rapidly, and has a good power factor and efficiency.
It is an object of the present invention to provide an automatic follow-up type vibration damping device which can reduce the capacity of dJ iso, on-board eruption, and wax vapor, has fewer failure points and mechanical losses due to fretting, and is light in weight as a whole.

[Summary of the invention]

The automatic follow-up type erasing S device according to the present invention (2) directly transmits the erasure is 4
It is configured to be driven by a 1IJ machine (2. The 4m
The frequency converter changes the magnetic frequency that supplies power to the machine according to the rotational speed relationship and rotational phase relationship between the main engine and the fkR model. The Ir1J machine is characterized by being configured to directly control speed and voltage.

[Embodiments of the invention]

Hereinafter, one embodiment of the present invention will be explained with reference to FIGS. 2 and 3, taking as an example the case where vibrations of the hull caused by the unbalanced couple C2 of the υ main engine are cancelled. (The second one is given the same reference numeral and the explanation is omitted.

In Figure 2, (8) is an electric motor that drives one disc (4) of the vibration damper (1) via a drive gear (9), and 4 is a paper feed to the electric motor (8) (force frequency This is a frequency conversion device controlled by a balance control device which will be explained later.

(lυ is the main shaft of the main engine @2 fixed toothed discs (13
1 + 2 is a main engine speed detector that outputs a signal according to the rotational speed of the main engine (1 + 2), and 4 is a main engine speed detector that outputs a signal according to the rotational speed of the main engine (2).
! 19 + phase detector, which is provided oppositely and detects the rotational phase of the main engine gear, and two protrusions u! on the main shaft with an interval of 180°. 9 was provided in the main engine tta 2.
This is to cancel the vibrations caused by the second unbalanced couple (2, hence the ship body C) (to rotate the second vibration damper (1) at twice the speed of the main engine u4).

(tl is the vibration damper C1) rotation shaft (= vibration damper speed detector installed and detects the rotation speed, Uη is the vibration damper 11). A vibration damper phase detector 11 is provided to face the vibration damper (1) and detects the rotational phase of the vibration damper (1); 11 is a balance control device that controls the frequency converter (11); By inputting the valley detection signals of the main engine phase detector I, the waster speed detector tte, and the damper phase detector 17), the main engine u3 and the damper (1
) rotational speed relationship and rotational phase relationship (= outputting the corresponding detection No. 16 to the frequency converter (2), and controlling the frequency converter (= controlling the input frequency of the electric motor (8)) Then, the speed of the DJ machine (8) is controlled to cancel the vibrations of the hull generated by the vibration damper 11).

Figure 3 shows the balance control device 1 field and the frequency conversion device.
In the circuit diagram 69, the same parts as in FIG. 2 are given the same reference numerals. Although the frequency conversion device is an example of a PWM transistor inverter device, it is not necessarily limited to this. First, in the balancer control device 11 in FIG. is a frequency-voltage conversion circuit, which inputs the signal output from the main engine speed detector μυ and converts it into a voltage, that is, outputs a voltage proportional to the rotational speed of the main engine @.(21) is a flip-flop The circuit is reset by the output pulse C2 of the main engine phase detector I (set by 2, and the damper phase detector 7).S4 is a conversion circuit, for example 7.
Lip-flop circuit - When power is 1” (2 to 1
When the voltage is 0V, and when the voltage is 0'' (-1Ov), the integrator integrates the output of the conversion circuit t, !-. The output of the vibration damper (to) is connected in such a way that it is added to the output of the frequency type-voltage conversion circuit.In addition, the output of the vibration damper speed detector 4, that is, the rotational speed of the vibration damper (1) (= The corresponding output voltage is connected to the polarity that reduces the output of the frequency-voltage conversion circuit (a). (to) is an amplifier.

Next (in the two-frequency converter tH, (to) is a converter that is made up of diodes and converts the constant frequency AC voltage inside the ship into DC power ζ2, (to) is a converter that is made up of transistors, and is a converter (c). An inverter converts the converted DC power into an AC force of a predetermined frequency, and η is an inverter that converts the converted DC power into an AC force of a predetermined frequency. This is an inverter control device that controls each transistor.

Next, the operation of the automatic follow-up type vibration damping device of the present invention will be explained. First, frequency −1 positive conversion times iN! If the output voltage of I- is still higher than the output voltage of the damper speed detector ul, the positive voltage of the difference is input to the input of the amplifier.

The positive voltage of this difference is appropriately amplified by an amplifier (to) and inputted to the inverter control device. Here, the inverter control device I2η controls each transistor so that the frequency corresponding to the positive voltage ζ2 amplified by the amplifier (2) is output from the inverter, so that the output frequency of the inverter (2) is The input power frequency of (8) increases, resulting in the rotational speed of the RiUh machine (8) increasing and speeding up the damper (1).

If the output voltage of the next C2 frequency-voltage conversion circuit (to) is lower than the output voltage of the damper speed detector cl, the above is reversed;
= Since a negative voltage is input to the amplifier (to), the rotational speed of the 7I&# machine (8) decreases and the damper 11) is decelerated.

Therefore, by appropriately selecting the output level of the frequency-voltage conversion circuit (7), the output level of the vibration damper speed detector inclination, the reduction ratio of the drive gear (9) and the disc rod 4), etc., vibration can be suppressed. machine (1
) can be made to follow twice the speed of the main engine 1, and the vibration damper t1) can generate the same number of vibrations in the main engine 4 as the vibrations of the hull caused by the main engine 4.

In order to reduce the excitation caused by the quadratic inequitable couple of the main engine u4 (l excitation is less than 1),
The condition for this is to maintain the vibration phase of the vibration damper <1) and the vibration phase of the hull generated by the main engine U area to be correctly opposite in phase. Therefore, when the main engine phase detector IC2 detects the rotational phase of the main engine (scrolling) and obtains two pulse signals for each revolution of the ball shaft, the main engine phase detector The rotational phase of the vibrator (1) is detected, and the rotation phase of the disc (4) is detected.
One pulse signal is obtained for every rotation of 1 g. here,
The relative position of the protrusion 1 and the protrusion (to) is the main engine @ because the vibration damper (1) is rotating at twice the speed of the main engine.
4. When the vibration phase of the hull caused by 2 and the vibration phase of the vibration damper 11) are correctly opposite in phase, each pulse output from each phase detector (L4.αη) occurs alternately with equal time. We have a relationship like that.

Therefore, for example, the vibration phase of the vibration damper (1) and the main engine u3 (
- Therefore, if the vibration excitation phases with the hull are correctly opposite to each other (=correctly opposite phases), from the 7-rig flop circuit υ, the time in the ``1'' state and the time in the 0'' state will be the same length. A waveform is output. This pulse waveform is applied to the next conversion circuit, and from the conversion circuit j16t, a pulse waveform in which the time at +10V is equal to the time at -10V is output.At this time, If the time constant of the integrator (to) is chosen to be sufficiently large, the output will contain some triangular waveform pulsations, but will be substantially constant (= is almost constant, and the output voltage of the frequency-voltage conversion circuit (4) will be Second, no modifications can be made.

However, if the vibration phase of the vibration absorber ζl) lags slightly behind the vibration phase of the hull generated by the main engine 0, the pulse intervals output from the 7 rip-flops will be unequal (2 rip-flop times 1 l). The set time, that is, the time in the 1'' state is longer than the time in the 10'' state. Therefore, the time of +lOv, which is the input signal of the integrator (c), is -
Since the time is longer than lOV, the output of PI 4- slowly increases in the positive direction while including triangular waveform pulsations.

This output is the output (=
When added up, it becomes one song as if a strange speed increase command had been issued, so the output frequency of the inverter (1) is slightly increased, and the speed of the vibration damper (1) is slightly increased (2 speeds are accelerated and the phase is delayed). is recovered. Opposite (= When the vibration phase of the vibration damper (1) slightly advances the vibration phase of the hull caused by the main engine, the output of the integrator (c) increases in the negative direction, so it disappears. The speed of the shaker (1) is small (2) and the phase delay is recovered.

Therefore, the rotational speed relationship and rotational phase relationship between the main engine q4 and the vibration damper <1) are detected, and the vibration phase of the vibration damper <1) is detected. A phase relationship (2) can be maintained that minimizes undesired vibrations of the hull caused by the main engine.

Up to now, we have explained the case of canceling the vibrations of nodes 1 to n of the hull caused by the secondary unbalanced couple of the main engine.
1 to nl of the hull caused by the m-order unbalanced couple of the main engine
It goes without saying that similar control can be performed when canceling the swing 741i17 of i. In this case, the disc of the vibration damper is driven at a speed m times the number of rotations IKct of the main engine, and the two protrusions provided on the ball shaft (2) are It is only necessary to perform ≦2 control so that the excitation and the excitation produced by the ship (2) are in opposite phases.

〔Effect of the invention〕

As described above (the second invention), the vibration damper can be directly connected to the center of the invention.
In order to GM with machine B (if configured with two configurations, the power frequency that will be sent to the sea will be changed by the frequency converter according to the rotational speed relationship and rotational phase relationship between the main engine and the vibration damper (=) 2. Therefore, since the IJJJ machine is configured to directly control the speed, there is no need to use a whirlpool streamline hand and a whirlpool flow brake with a large time constant as in the past.
Trackability becomes extremely good. Therefore, even if the rotational speed of the main engine suddenly changes due to some kind of disturbance, it is followed without any delay, and has an excellent effect of not adversely affecting the hull 42 or impairing the comfort of the ship.

In addition, since the extremely inefficient 4A joint and eddy current brake are not used, the efficiency of the device increases, and since the device is designed to operate continuously for long periods of time, the energy saving effect is also significant. By changing the frequency of the power supplied to the motive power and directly controlling the speed of the motive power, we can reduce the power factor and efficiency of 9 moving rocks, 4 onboard engines, and 6 layers of power wiring, and reduce the overall You can lighten your own weight.

Furthermore, since an eddy current joint and an eddy current brake are not used, the number of bearings can be reduced accordingly, and the number of failure points and mechanical losses due to fretting can be reduced accordingly.

[Brief explanation of the drawing]

Fig. 1 is a schematic configuration diagram showing the main parts of the vibration damper, Fig. 2 is a connection configuration diagram showing an embodiment of the automatic follow-up vibration damping device according to the present invention, and Fig. 3 is a control diagram used in the present invention. 1... Vibration damper 8... Drive ring motor 10... Frequency converter 11... Gray machine speed detector 12... Main engine 14...・Main engine phase detector 16...
・Vibration machine speed detector 17...Vibration machine phase/director 1
9... Balance control device W... Frequency-to-city pressure converter 21... Flip-flop circuit n... Conversion circuit n... Integrator M... Amplifier 5... Converter 26... Inverter n...
Inverter control device (8733) Agent: Yoshiaki Inomata, patent attorney (and 1 others)
Figure 1 Figure 2

Claims (1)

[Claims] 11) An automatic tracking type vibration damping device installed at a suitable location inside the ship, which eliminates or reduces undesirable vibrations of the hull caused by the unbalanced couple C2 of the main engine mounted inside the ship (1). The speed of the turtle machine is controlled by changing the magnetic frequency that supplies power to the electric motor (the damper that is directly driven by the second motor and generates a 7ζ vibration according to its rotational speed, and the 4IIdJ machine that drives this damper). a frequency converter, and the frequency converter is configured such that the rotational speed of the vibration damper is a constant integer with respect to the rotational speed of the previous ml earth engine according to the rotational speed relationship and rotational phase relationship between the main engine and the vibration damper. Ratio (two thrusts, and said extinguishing fR4I
and a balance control device (a) for controlling the rotational phase of the main engine so that the rotational phase of the main engine has a phase relationship that minimizes undesired vibrations of the hull. Device.