JPH08312460A - Vibration regulating mechanism of stirling engine - Google Patents

Abstract

PURPOSE: To regulate a large vibration generated at the starting time and the stopping time of a Stirling engine. CONSTITUTION: The vibration generated in the operation of a Stirling engine is received by a base board 4. A shape memory alloy 7 is contacted with the base board 4 between a seat 5, a vibration isolating rubber 6, and a pedestal 8, installed on the base board 4, by making a fixed base plate 11 as a standard, and regulates the vibration. Consequently, the vibration is regulated by the vibration isolating rubber and the attached shape memory alloy, and this vibration regulating mechanism absorbes the vibration as well as protects the piping apparatus.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration regulation mechanism for a Stirling engine supported by a mount.

[0002]

2. Description of the Related Art Conventionally, various anti-vibration mechanisms have been proposed for a base supporting a reciprocating engine with large vibration and have already been put to practical use. However, in the Stirling engine which has been put into practical use in recent years, the vibration at the time of starting and stopping is larger than that of the conventional engine (the vibration frequency is also low), and the conventional vibration isolation mechanism cannot obtain a sufficient effect.

FIG. 28 is a sectional view showing an example of a conventional vibration isolation mechanism. In the figure, 1 is a piston, 2 is a connecting rod, 3 is a crankshaft, 4 is a base (also referred to as a vibration base), and 5 is A seat, 6 is an anti-vibration rubber, 8 is a base, 11 is a base plate, and 30 is an engine. 29 and 30 are shown in FIG.
As an example of the anti-vibration rubber 6, the receiving seat 5, and the pedestal 8 of JP-A-1-
FIG. 10 is a cross-sectional view of a conventional engine vibration-damping rubber disclosed in Japanese Patent No. 105035. In the figure, 53 is a spring made of a shape memory alloy, 50 is an opening provided in the seat 5, 51 is an upper plate that receives the upper end of the spring 53, and 52 is a small opening provided in the upper plate 51. .

Reference numeral 30 denotes an engine, which is composed of a piston 1, a connecting rod 2 and a crankshaft 3. As is well known, the engine 30 is composed of more elements, but here, only the elements having many points that contribute to vibration generation are illustrated.

Next, the operation will be described. The piston 1 descends, the rotation is transmitted to the crankshaft 3 by the connecting rod 2, and a rotational movement is generated, and an output is taken out.
The vibration generated at this time is received by the base 4, and the base 4
When the vibration is transmitted between the receiving seat 5, the anti-vibration rubber 6, and the pedestal 8 attached to the, the vibration is prevented (reduced) with reference to the base plate 11 fixed to the floor.

When the engine 30 is in the idling state (low rotational speed), the vibration-proof rubber 6 does not have the shape memory alloy spring 53 reaching the seat 5, as shown in FIG.
Only the anti-vibration rubber 6 receives the load. When the engine 30 is rotated at high speed, the spring 53 is heated by a warm air device (not shown) to return to the memorized shape, and the upper plate 51 opens the seat 5 as shown in FIG. Part 50
Touch

As a result, the size of the hole of the opening 50 is changed to the small opening 52, and the force of the spring 53 is added to the force of the antivibration rubber 6, so that the spring constant is increased as a whole and the vibration damping effect is also increased. .

That is, in the conventional engine vibration isolating mechanism as shown in FIGS. 28 to 30, basically, the resonance frequency of the vibration isolating mechanism is increased at high speed rotation and is lowered at low rotation speed, so that The vibration frequency of the engine is set to be higher than the resonance frequency, and due to this characteristic, the vibration of the engine is designed not to be transmitted to the base plate 11.

By the way, since the Stirling engine produces little noise and vibration during steady operation, it is used especially for applications requiring quietness. Therefore, the resonance frequency of the vibration isolator used for the pedestal is lower. There is a request to set the frequency (that is, to set it softer).

As described above, the vibration frequency when the Stirling engine is started and stopped is extremely low and the amplitude is large. Therefore, based on the design concept of the conventional vibration isolation mechanism, the resonance frequency of the vibration isolation mechanism at low speed is set to the vibration frequency of the engine. However, it is practically impossible to make it even lower. Therefore, at low speed, the entire engine resonates with the base 4, and a violent vibration state is exhibited with respect to the base plate 11. Therefore, the conventional one is not useful. . That is, there is a limit to the permissible frequency and range of the vibration isolating mechanism made up of the anti-vibration rubber and the like, and it is not possible to follow the vibration due to a large imbalance during start and stop, and the vibration base 4 shakes greatly. Since such a phenomenon occurs, flexible pipes and joints are required for the pipes or joints between the engine and the fixed part, and the start and stop due to the stress applied at each start and stop Depending on the number of times, the parts may be broken or loosened due to fatigue, etc., and the engine must be stopped or repaired.

[0011]

Since the conventional antivibration mechanism is constructed as described above, (1) it is difficult to obtain an antivibration mechanism that matches the vibration characteristics of the Stirling engine.

Further, in the system in which the vibration characteristic is changed, (2) the warm air for warming the spring 53 made of the shape memory alloy also acts on the antivibration rubber 6 to accelerate the deterioration of the antivibration rubber 6. .

(3) The temperature of the warm air cannot be increased in order to prevent the deterioration of the vibration-proof rubber 6, and therefore the deformation speed of the shape memory alloy is slow, so that there is no quick response to changes in the spring constant. (4) When the temperature rises, the inside of the anti-vibration rubber 6 becomes close to a seal,
When you want to lower the temperature, it is difficult to lower the temperature.

(5) Therefore, the spring constant of the anti-vibration rubber 6 cannot be set too small so that a large problem does not occur even if the follow-up change of the spring constant is delayed. There was such a problem.

The present invention has been made to solve the above-mentioned problems, and impedes the operation of the Stirling engine in which the vibration state greatly changes, both in the normal operation state and in the start / stop state. It is an object of the present invention to obtain an anti-vibration mechanism that does not cause such vibration and resonance.

Further, by obtaining a quick response to the change of the spring constant of the anti-vibration mechanism, the vibration at the time of starting and stopping the engine (in particular, the Stirling engine which has a large vibration at the time of starting and stopping) can be regulated and the fatigue of other parts due to the shaking The purpose is to obtain a vibration control mechanism that can prevent breakage and improve reliability, and that that can control the degree of vibration so that the vibration is below a certain level during steady operation. .

[0017]

A vibration control mechanism for a Stirling engine according to a first aspect of the present invention comprises a vibration damping rubber for supporting a base of the Stirling engine, and an actuator arranged on a base plate for supporting the vibration damping rubber. A switch for controlling the drive / stop of the actuator is provided, and the movement of the base is restricted by the actuator.

A vibration control mechanism for a Stirling engine according to a second aspect of the present invention is provided with a vibration damping rubber for supporting a base of the Stirling engine, a shape memory alloy arranged on a base plate for supporting the vibration damping rubber, and the shape memory alloy. And an electric heater and a switch for turning on and off the electric heater.

The vibration regulation mechanism for a Stirling engine according to the third aspect of the present invention is, in addition to the means of the first or second aspect,
A punch is used that is pushed toward the seat by an actuator. The tip of the punch and the seat to which the tip is pressed have a conical shape.

In the fourth invention, the ball-shaped projection restrains only the movement of the base in the horizontal plane.

In addition to the means of the first invention, the vibration regulating mechanism according to the fifth invention has a spline shaft provided on the base and one end inserted into the spline shaft and the other end fixed to the base plate. And a ring provided outside the universal joint and driven by an actuator.

According to the sixth aspect of the invention, the acceleration detector detects the vibration of the base, and the controller automatically controls the actuator.

In the seventh invention, the piezo element operates as an actuator.

In addition to the means of the first to third inventions, the vibration regulation mechanism for a Stirling engine according to the eighth invention has a vibration energy absorbing material at the tip of an actuator or a punch driven by the actuator.

A vibration regulating mechanism for a Stirling engine according to a ninth aspect of the invention is the vibration regulating mechanism of the first or second aspect of the invention.
The driving directions of the actuators are different from each other.

The vibration regulating mechanism for a Stirling engine according to the tenth aspect of the invention is different from the means of the first or second aspect of the invention in that the driving direction of one actuator is different from the driving directions of the other actuators.

The eleventh invention is, in addition to the means of the fifth invention, provided with only one spline shaft immediately below the Stirling engine.

The twelfth invention has a displacement speed detecting means and an amplifier in addition to the means of any one of the first to fifth inventions.

A thirteenth invention has, in addition to the means of any one of the first to fifth inventions, a plurality of angles which are made of a damping steel plate and to which an actuator is attached.

The fourteenth invention comprises a base, a distance sensor, a power source, an electromagnetic coil and a magnet.

In the fifteenth invention, in addition to the means of the fourteenth invention, the power supply has a level judging circuit.

A sixteenth invention uses a rotation angle sensor of a Stirling engine instead of the distance sensor used in the means of the fourteenth invention.

[0033]

In the first to eighth aspects of the present invention,
Anti-vibration rubber absorbs vibrations at normal Stirling engine operating speeds. When the actuator operates, the base has a total of six degrees of freedom of the base plate in the directions of the X, Y, and Z axes and the rotation about the X, Y, and Z axes, respectively. Losing at least one degree of freedom,
The movement is restrained.

When the Stirling engine is in the low rotation range during starting and stopping, the actuator operates and the movement of the base is restricted, so that the base does not resonate and move violently.

In the second aspect of the invention, the shape memory alloy is heated by the heater when the amplitude at the time of starting / stopping the engine is large, and the shape is deformed so that the pedestal and the pedestal are directly connected structurally. Since this heater is directly wound around the shape memory alloy, the vibration-proof rubber is not heated by the heater.

According to the third aspect of the invention, the punch is pushed into the punch insertion hole provided in the seat by the deformation of the shape memory alloy, whereby the seat moves in the horizontal plane and the seat moves downward. Movement is restricted.

The vibration control mechanism of the Stirling engine according to the fourth invention has a punch having a ball-shaped projection at the tip instead of the conical projection of the means of the third invention, and a hemispherical hole provided in the base. Have.

In the fifth or eleventh aspect of the invention, the ring eliminates the degree of freedom in the bending direction of the universal joint, so that vibration is restricted.

A vibration regulating mechanism for a Stirling engine according to a sixth aspect of the invention has an acceleration detector and a control device in addition to the means of any of the first to fifth aspects of the invention.

The vibration regulation mechanism of the Stirling engine according to the seventh aspect of the invention has a piezo element as an actuator.

In the eighth aspect of the invention, the vibration energy absorbing material absorbs minute vibrations of the engine.

In the ninth, tenth, or thirteenth aspect of the invention, since the actuators having different driving directions regulate vibrations in different directions, the vibration regulating effect becomes large.

In the twelfth aspect of the invention, the displacement velocity detecting means and the amplifier act so that the vibration regulating mechanism works only when the vibration amplitude exceeds a certain value.

In the fourteenth and fifteenth aspects of the invention, the distance sensor and the power source act so that the vibration regulation mechanism works only when the vibration amplitude exceeds a certain value.

In the sixteenth aspect of the invention, the circuit angle sensor outputs an output that matches the cycle of vibration, and the vibration regulation mechanism operates at a timing corresponding to this output, so the vibration amplitude does not increase.

[0046]

【Example】

Example 1. FIG. 1 shows a structural example of a vibration isolation mechanism for a Stirling engine according to the first and second aspects of the present invention. In FIG. 1 and the subsequent drawings, the same reference numerals indicate the same or corresponding portions as those of the conventional one, and thus detailed description thereof will be omitted. A piston 1 reciprocating in the cylinder and a connecting rod 2 for converting the reciprocating motion of the piston 1 into a rotary motion,
In a Stirling engine 18 having a crankshaft 3, a plurality of cylindrical anti-vibration rubbers 6 supporting the engine, and a shape memory alloy 7 arranged at the center of the cylindrical anti-vibration rubber 6,
Electric heater 10 for heating the shape memory alloy 7
And a switch 60 and a power source 9 for the electric heater 10. 61 is a hole provided in the center of the seat 5. 2 and 3 are cross-sectional explanatory views showing in detail the essential parts of the vibration isolation mechanism of FIG.

The shape memory alloy 7 has one end fixed to the pedestal 8 and the other end inserted into the hole 61.
The diameter of the hole 61 is larger than the outer diameter of the shape memory alloy 7, and there is a gap between them that is not in contact with the Stirling engine 18 at a normal operating speed. Note that, for convenience of description below, the directions of the movements X, Y, and Z are shown in FIG.
It shall be determined as shown in FIG.

Next, the operation will be described. When the switch 60 is turned on before starting the Stirling engine 18, a current flows from the power source 9 to the heater 10 and the heater temperature rises. When the temperature rises, the shape memory alloy 7 tries to return to its original shape as shown in FIG. At this time, the left and right movements of the receiving seat 5 are restricted, and large vibrations in the horizontal plane at the time of starting and stopping are restricted. Vertical movement is also constrained by friction.

Although only two shape memory alloys 7 are shown in FIG. 1, three or more shape memory alloys 7 are provided, and the bending directions of the shape memory alloys 7 are arranged in the respective holes 61 so as to be different from each other. Vibration can be regulated more reliably. In this case, if a plurality of shape memory alloys 7 are installed at a sufficient distance from each other, not only the movement of the base in the horizontal plane but also the rotational movement can be restricted.

The shape memory alloys of the two seats 5 in FIG. 1 may press the seats in opposite directions. After the start of the Stirling engine 18, when the rotation speed becomes sufficiently high, the switch 60 is opened and the operation is performed in the state of FIG. When the Stirling engine 18 is stopped, the switch 60 is first turned on and then the stop operation is performed in the same manner as when starting the engine.

Here, the shape memory alloy 7 and the electric heater 10 are used.
Acts as a kind of actuator, so that instead of the combination of the shape memory alloy 7 and the electric heater 10, an electromagnetic solenoid is used, an electric motor, or pneumatic pressure,
For example, a hydraulic actuator may be used. However,
The vibration force of a large Stirling engine is strong, a sufficient force is required for an actuator for controlling this vibration, and it must be small. The method of using the shape memory alloy described above meets such a demand.

The heater 10 is directly wound around the shape memory alloy via an insulator (not shown).
0 and the anti-vibration rubber 6 have a sufficient gap, so that the heat of the heater 10 is less likely to deteriorate the anti-vibration rubber 6.
Further, although the shape memory alloy 7 is shown inside the antivibration rubber 6 in the figure, it may be outside the antivibration rubber, and the contact surface of the shape memory alloy 7 is a vertical part, but a horizontal part. (For example, the lower part of the seat 5), the vertical movement of the base can be restrained. The base plate 11 is not always necessary, and the base 8 may be directly installed on the floor or a beam (not shown) of the vehicle.

Since the main purpose of the present invention is to prevent vibration of large amplitude due to resonance of the base, X, Y, Z
6 of vibration in the direction and rotational movement around the X, Y and Z axes
Even if you do not constrain all the four degrees of freedom, depending on how the engine is installed, constraining at least one shaft is sufficient.

Example 2. In the case of FIG. 1, since the direction of the regulated vibration is small, the invention for more reliable regulation is shown below. 4 and 5 show other examples of detailed cross-sectional views of the essential parts of the vibration-proof mechanism according to the third invention. In the figure, 7b is a shape memory alloy whose tip bends up and down depending on the memory temperature, 16 is a punch that moves up and down by the shape memory alloy 7b, and the tip of the punch is conical as shown. Reference numeral 61b is a hole provided in the seat 5 and has a concave shape that is the same as the conical shape of the tip of the punch 16. Further, the pedestal 8 has a cylindrical surrounding portion, in which the punch 16 is slidably accommodated.

FIG. 4 shows a state in which the switch 60 is not closed and the punch 16 is penetrated from the hole 61b. FIG. 5 shows that the temperature of the shape memory alloy 7b rises when the switch 60 is turned on and the shape thereof is restored. As a result, the punch 16 is shown inserted into the hole 61b. The lower end of the punch 16 is always in the cylindrical enclosure portion 33 of the pedestal 8 and has a structure that does not move left and right.

Next, the operation will be described. When starting the Stirling engine 18, turn on the switch 60,
A current flows from the power supply 9 to the heater 10, and the heater temperature rises. When the temperature rises, the shape memory alloy 7b tries to return to its original shape. At this time, by pushing up the punch 16 and fitting it into the hole 61b of the seat 5, the rotation of the pedestal 8 and the seat 5 in the X and Y axes and the downward and horizontal movements are restricted, and a large vibration is generated at the time of starting. Regulate.

Example 3. FIG. 6 shows an anti-vibration mechanism according to the fourth aspect of the invention, and FIG. 7 shows an enlarged main part thereof. In the figure, 2
Reference numeral 8 is a punch having a ball (spherical) tip shape, and a high damping material is used as its material.

Engine, especially Stirling engine 18
When starting or stopping, the vibration of the pedestal 4 of the engine
In some cases, it is necessary to restrict only horizontal vibration while allowing the pedestal 4 to tilt. FIG. 6 is characterized in that the gap can be reduced while following the vibration (tilting) of the vibration base 4. When the vibration base 4 vibrates while vibrating, the ball-shaped shape has an advantage that a combination of a male and a female machined on the spherical surface R can follow the inclination of the vibration base while keeping a gap. If necessary, when the punch 28 rises, the male and female contacts at the point and the ring.

Example 4. 8 and 9 show another example of the vibration preventing mechanism according to the fifth invention. In the figure, 12 is a spline shaft that is vertically attached to the seat 5, 13 is a cross free joint that is inserted into the spline shaft 12 on one side and is freely movable up and down. It is fixed to the upper end of a shaft 34 that stands vertically from the base 8. That is, the pedestal 5 is usually above and below the pedestal 8,
You can move left, right, front and back.

Reference numeral 14 is a ring which is fitted completely onto the outside of the cross joint 13, and this ring is a base 8
Since the shape memory alloy 7 is fixed on the upper end of the shape memory alloy 7 installed above, the shape memory alloy 7 moves up and down as the shape of the shape memory alloy 7 changes.

When the ring 14 moves upward to the position where the cross free joint 13 is encased, the bending of the cross free joint 13 is restricted, so that the seat 5 cannot move in the horizontal direction. . Of course, the rotation of the pedestal is also restricted.

Example 5. FIG. 10 shows the structure of the vibration damping mechanism of the sixth embodiment of the present invention, and FIG. 11 shows the operation explanatory diagram thereof. FIG.
At 0, 20 is an accelerometer, and 19 is a control device that determines the magnitude of the signal of the accelerometer 20 and gives an output command to the power supply 9 when the vibration is above a certain level.

FIG. 11 shows the relationship between the output of the power source 9 and the magnitude of the signal from the accelerometer 20. In FIG. 10, the vibration base 4
The accelerometer 20 is attached to the power source 9, and the power source 9 is activated by the signal of the accelerometer generated by the magnitude of the vibration to heat the heater 10 and the shape memory alloy 7 regulates the vibration. It can be automatically turned off. It is possible to perform real-time control of the vibration having a relatively slow cycle, which occurs when accelerating and decelerating during normal operation as well as when starting and stopping the Stirling engine 18.

Example 6. A vibration preventing mechanism according to a seventh aspect of the present invention is shown in FIGS. In the figure, 23 is a piezo element, 24 is a link mechanism, and 49 is a piezo power source for driving the piezo element 23.

Since the piezo element 23 is used, the heater 10 shown in FIG. 1 is not necessary, and the piezo element 23 is deformed by pushing a current with the power source 49 to push up the punch 16. By using the piezo element 23, the capacity of the power supply 49 and the shape of the vibration damping mechanism become compact. It is characterized by utilizing a large force due to the deformation of the piezo element.

Since the piezo element 23 increases the amount of driving deformation,
A plurality of layers may be stacked and used. Alternatively, as shown in FIG. 13, by incorporating a link mechanism 24, the movement amount (movement) of the piezo element 23 can be expanded to expand the control range of the vibration amplitude. The link mechanism 24 has a triangular shape if the ratio of the action point, the force point, and the operation point can be obtained.
The shape does not matter, such as a half circle or an ellipse.

Example 7. FIG. 14 shows another structural example of the vibration prevention mechanism according to the eighth aspect of the present invention. In the figure 54
Is a vibration energy absorbing material, such as a damping steel plate, attached to the conical surface in contact with the hole 61b at the tip of the punch 16 and the surface in contact with the pedestal 8.

Next, the operation will be described. When the shape memory alloy 7b returns to its original shape and pushes up the punch 16, the punch 16 and the pedestal 5 and the pedestal 8 are in strong contact with each other with the vibration energy absorbing material 54 interposed therebetween, so that the vibration plate The vibration applied to 4 is absorbed and the vibration transmitted to the base plate 11 is reduced. This vibration energy absorbing material is applied to both the tip of the shape memory alloy of FIG. 1 and the tip of the punch 28 of FIG.
It can also be used for the ring 14 of FIG.

The inventions shown in Examples 1 to 7 can be used in combination with each other, and the details can be modified according to the combination.

Example 8. In the case of FIG. 1 of the first embodiment, it is necessary to use a plurality of pairs of anti-vibration rubbers including the shape memory alloy 7, the heater 10 and the like (both feet or feet on the depth direction side not shown in the drawings). There is a drawback that the structure becomes complicated.

A vibration regulating mechanism for a Stirling engine that can solve this drawback is shown in FIGS. FIG.
Is a perspective external view, FIG. 17 is a cross-sectional view as seen from the front (X direction), and FIG. 18 is a cross-sectional view as seen from the lateral direction (Y direction).

In the figure, the vibration-proof rubber 6, the seat 5, and the pedestal 8 are the same as in the conventional case, and the center of the base 4 (just below the vibration weight of the engine) is shown in FIGS. One vibration restricting body 26 including the cross free joint 13, the spline shaft 12, and the ring 14 fitted in the cross free joint 13 is attached.

The operation of the vibration regulator 26 is shown in FIG.
The description is omitted because it is as described in FIG. 8.
Since the vibration regulation mechanism 26 is mounted immediately below the mechanism portion that causes the vibration of the Stirling engine 18, the vibration regulation mechanism 26 has a great effect of regulating the vibration, and the effect that only one vibration regulation mechanism is used can be obtained.

Example 9. Another embodiment of the present invention is shown in FIG.
It shows in FIG. FIG. 19 is a sectional view of the vibration regulation mechanism, and FIG.
FIG. 6 is a voltage waveform diagram for explaining the operation. FIG.
The horizontal axis represents time and the vertical axis represents voltage.

In the figure, reference numeral 48 is a movable iron core having a permanent magnet attached to the base 4. Reference numeral 27 denotes a coil, and the movable iron core 48 vibrates (moves) inside the coil 27 due to the vibration of the base 4. An amplifier 31 is connected to the coil 27 and amplifies the output voltage waveform 35 of the coil 27.

Reference numeral 29 shows an output voltage waveform of the amplifier 31.
Reference numeral 32 is an explanation auxiliary line, which shows a constant level of the voltage waveform 35. Reference numeral 23 denotes a piezo element, which is a means for driving the punch 16 by stacking one or a plurality of piezo elements.

Next, the operation will be described. When the base 4 vibrates, the movable iron core 48 moves inside the coil 27 in accordance with the vibration. The magnetic flux density of the coil 27 fluctuates due to the horizontal component of the movement (horizontal direction toward the drawing), so that a voltage waveform such as 28 in FIG. 20B is generated in the coil 27.

The amplifier 31 receives the voltage waveform 35 and amplifies and outputs the absolute value of the voltage waveform 35 only when the absolute value of this voltage exceeds a certain value (shown by 30 in FIG. 20B). This is shown by the waveform 29 in FIG. The waveform 29 has a peak when the speed of vibration is high. The voltage waveform 29 is applied to the piezo element 23, and the piezo element 23 deforms in accordance with the cycle of vibration and presses the punch 16 against the pedestal 5.

As a result, the vibration is suppressed only when the vibration of the base 4 exceeds a certain range and becomes large. It is easy to make the voltage level 32 variable (including the zero level). In addition, the movable iron core 48 and the coil 27
Although the mounting direction of is horizontal in FIG. 19, it can be mounted in any direction. Further, the movable iron core 48 and the coil 27 are respectively directed in the directions of two or more axes of X, Y and Z.
Can be provided, and the outputs thereof can be combined and input to the amplifier 31.

The amplifier 31 is not always necessary if the piezoelectric element has sufficient sensitivity. Piezo element 23
Alternatively, an electromagnetic solenoid or a pneumatic actuator can be used.

In this embodiment, the vibration regulation mechanism works only when the vibration speed of the base 4 exceeds a certain range, and the regulation does not work when the speed is low, so that the vibration absorption mechanism is effective. .

The movable iron core 48 and the coil 27 are the displacement speed detecting means of the base.

Example 10. Another embodiment of the present invention is shown in FIG.
~ 28. In the figure, 38 is a mounting angle and 39 is a shape memory alloy plate. The shape memory alloy plate 39 is the heater 1
The actuators 36 and 37 are configured with 0.

The mounting angles 38 are mounted on the base plate 11 at different angles. 36 is a left side actuator and 37 is a right side actuator. When the left actuator 36 and the right actuator 37 are in contact with the base 4 to regulate their vibrations, the vibration directions that can be regulated are different from each other.

Although only two actuators are shown in the figure, the effect becomes high relative to the number of actuators if at least three sets of actuators installed in directions orthogonal to each other are used.

Such effects can be similarly obtained for any actuators of Embodiments 1 to 9 as well as the shape of the actuator of FIG.

22 and 23 show the mounting angle 38 of FIG.
Is a high damping material mounting angle 40 configured by using a high damping material.

Example 11. Another embodiment of the present invention is shown in FIG.
~ 27. 24: is a figure which shows the structure of the vibration control mechanism of the Stirling engine of Example 11. FIG. In the figure, 41 is a column fixed to the base plate 11. 45 is pillar 4
Distance sensor fixed at 1 (also called proximity sensor)
And the metal fitting 46 attached to the base 4 and the distance sensor 4
5 outputs a signal according to the distance between the two. That is, the base plate 1
A signal corresponding to the lateral displacement of the base 4 with respect to 1 is output.

Reference numerals 43 and 44 denote permanent magnets attached to the metal fitting 46, which are attached in opposite directions to each other as shown in the figure. Reference numeral 47 is a function generating circuit which receives the output signal of the distance sensor 45 and outputs a predetermined signal, and the characteristic of the function is as shown in FIG. 31, for example.

Reference numeral 42 is an electromagnet fixed between the two pillars 41, which is located between the two permanent magnets 43 and 44. Reference numeral 58 is a coil wound around the electromagnet 42, and 57 is a power supply device that supplies a current to the coil 58 and controls the current.

FIG. 25 is a diagram for explaining the operation of force between the electromagnet 42 and the permanent magnets 43 and 44, FIG. 26 is a characteristic diagram of the function generating circuit 47, FIG. 27 is a distance sensor 45,
It is a block diagram explaining the flow of the control signal between the function generation circuit 47, the power supply device 57, the coil 58, the electromagnet 42, and the permanent magnet 43 (or 44).

Next, the operation will be described. The distance between the distance sensor 42 and the metal fitting 46 facing the distance sensor 42 is L.
It is assumed that L is 0 when the base 4 is at the center (not laterally displaced due to vibration) with respect to the base plate 11, and the value increases to + or − as it shifts to the right or left.

Now, the base 4 vibrates, and the output of the distance sensor 45 is output as an AC signal according to the change of the base,
When the amplitude increases, the function generator 47 outputs an AC output having an amplitude according to the characteristic curve shown in FIG.

An alternating current corresponding to this output is the power supply device 4.
8 to the coil 58. This current is naturally synchronized with the vibration of the base 4. When an alternating current synchronized with the vibration flows through the coil 58, the electromagnet 42 is pushed rightward or leftward according to the direction of the current and receives a pulling force, as shown in FIGS.

Here, the moving direction of the base 4 and the electromagnet 52
The vibration of the base 4 is regulated by setting the direction of the current so that the direction in which the force is applied is opposite to the direction in which the force is applied, that is, the direction in which the electromagnet 42 regulates the movement of the base 4. It

The characteristic curve of FIG. 26 can be set in any way by electronic circuit means. As shown in FIG. 26, the characteristic that the output is output only when the vibration amplitude becomes a certain value or more is a characteristic that is convenient for suppressing the large amplitude when the Stirling engine is started, but it is not necessary to use the function generator. However, the same function can be achieved by using, for example, a level determination circuit in combination with a relay. It is also possible to insert an appropriate lead-lag circuit in the block diagram of FIG. 27 to further enhance the vibration suppressing effect. In FIG. 24, although it is described that two distance sensors 45 are used,
It may be one.

Two permanent magnets 43 and 44 are not always required. Further, although the permanent magnets 43 and 44 and the electromagnet 52 are installed in the space below the base 4, they may be provided inside the cylinder of the vibration-proof rubber 6.

24 to 27, only the vibration in the lateral direction has been described for convenience of explanation, but it is clear that it can be used in all the X, Y, and Z directions, and even if it is used in a plurality of directions at the same time. Good.

Also, instead of using the distance sensor 45,
By using a signal accompanying the rotation of the Stirling engine 18 (for example, a crankshaft angle signal (not shown)), a substantially similar vibration regulation effect can be obtained.

[0100]

As described above, the first to eighth aspects of the present invention are as follows.
According to the invention, when the Stirling engine is started or stopped, the actuator moves in at least 1 direction of the movement of the base.
Since the shaft is restrained, the base does not resonate and violent vibration does not occur.

Further, during normal operation, the vibration of the engine is absorbed by the anti-vibration rubber. Therefore, the vibration of the piping system can be minimized, the effect of preventing breakage of the pipes and fittings is remarkable, and the effect of preventing the shaking of the entire apparatus can be exerted. In addition, since there is no large shaking at the start, there is an effect that the start can be smoothly performed.

According to the second invention, since the shape memory alloy is used as the actuator, the reliability can be improved. Further, since only the shape memory alloy is warmed by the electric heater, deterioration of the anti-vibration rubber can be prevented, heating deformation is fast, and response can be improved.

According to the third aspect of the present invention, the punch restrains the vibrations of the pedestal in the X and Y directions and the rotational movement about the X and Y axes, thereby more reliably preventing the resonance of the base. can do.

According to the fourth invention, only the horizontal vibrations of the base in the X and Y directions can be restrained by the ball-shaped projections.

According to the fifth aspect of the invention, all the movements of the base other than the movement in the Z-axis direction can be restrained, and a more reliable resonance preventing effect can be obtained.

According to the sixth aspect of the invention, the actuator O
It is possible to automate the N-OFF control without the need for a person to perform it.

According to the seventh aspect of the invention, the response can be made faster by using the piezo element.

According to the eighth aspect of the present invention, vibration can be absorbed even when the actuator is operating.

The vibration regulation mechanism for a Stirling engine according to the ninth aspect of the present invention has a substantially uniform vibration damping effect against vibrations in all directions or rotational vibrations having axes in all directions.

The vibration regulation mechanism of the Stirling engine according to the tenth aspect of the invention has an effect that the direction of vibration to be regulated is not limited to one direction.

The vibration regulation mechanism of the Stirling engine according to the eleventh aspect of the invention has the effect of reducing the number of vibration damping mechanisms.

The vibration regulating mechanism of the Stirling engine according to the twelfth, fourteenth and fifteenth aspects of the invention has an effect that it can be operated only when the displacement speed of vibration becomes large.

In the vibration regulation mechanism for the Stirling engine according to the thirteenth invention, the actuator mounting angle made of the vibration damping steel plate absorbs the vibration of the engine transmitted to the actuator, and the vibration damping effect is further enhanced.

The vibration regulating mechanism for a Stirling engine according to the sixteenth invention can obtain the same effect as that of the fourteenth invention with a simpler structure.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a vibration regulation mechanism according to a first embodiment of the present invention.

FIG. 2 is an explanatory view of a main part of the image stabilization mechanism of FIG.

FIG. 3 is an explanatory view of a main part of the image stabilization mechanism of FIG.

FIG. 4 is an explanatory view of a main part of a vibration regulation mechanism according to a second embodiment.

FIG. 5 is an explanatory diagram of a main part of a vibration regulation mechanism according to a second embodiment.

FIG. 6 is an explanatory view of a main part of a vibration regulation mechanism according to a third embodiment.

7 is an enlarged view of a main part of the vibration regulation mechanism of FIG.

FIG. 8 is a configuration diagram of a vibration regulation mechanism according to a fourth embodiment.

9 is an explanatory diagram of the operation of FIG.

FIG. 10 is an explanatory view of a main part of a vibration regulation mechanism according to a fifth embodiment.

FIG. 11 is an operation explanatory view of the vibration regulation mechanism of FIG.

FIG. 12 is an explanatory diagram of a main part of a vibration regulation mechanism according to a sixth embodiment.

13 is an operation explanatory view of the vibration regulation mechanism of FIG.

FIG. 14 is an explanatory diagram of a main part of a vibration regulation mechanism according to a seventh embodiment.

FIG. 15 is a diagram illustrating directions of axes for explanation.

FIG. 16 is a perspective external view of a vibration regulation mechanism of Example 8.

17 is a cross-sectional view of the vibration regulation mechanism of FIG.

18 is a vertical cross-sectional view of the vibration regulation mechanism of FIG.

FIG. 19 is a cross-sectional view of a vibration regulation mechanism of Example 9.

FIG. 20 is an explanatory diagram of voltage waveforms.

FIG. 21 is a cross-sectional view of the vibration regulation mechanism of Example 10.

FIG. 22 is a sectional view showing another example of the tenth embodiment.

23 is an operation explanatory view of the vibration regulation mechanism of FIG.

FIG. 24 is a cross-sectional view of the vibration regulation mechanism of Example 11.

FIG. 25 is an operation explanatory view of the vibration regulation mechanism of FIG. 24.

FIG. 26 is a characteristic diagram of a function generating circuit.

FIG. 27 is a control block diagram of the vibration regulation mechanism of FIG. 24.

FIG. 28 is a configuration diagram of a conventional anti-vibration mechanism of a Stirling engine.

FIG. 29 is an explanatory diagram of a vibration-proof rubber of the vibration-proof mechanism of FIG. 28.

30 is an explanatory diagram of a vibration-proof rubber of the vibration-proof mechanism of FIG.

[Explanation of symbols]

1 Piston 2 Connecting Rod 3 Crankshaft 4 Base (Vibration Base) 5 Seat 6 Vibration Damper 7 Shape Memory Alloy 7b Shape Memory Alloy 8 Base 9 Power 10 Heater 11 Base 12 Spline Shaft 13 Universal Joint 14 Ring 16 Punch 19 Control device 20 Accelerometer 23 Piezo element 24 Link mechanism 27 Coil 28 Ball-shaped high damping material punch 29 Waveform 31 Amplifier 33 Cylindrical enclosure 35 Voltage waveform 36 Left side actuator 37 Right side actuator 38 Mounting angle 39 Shape memory alloy plate 40 High Damping material Angle 41 Column 42 Electromagnet 43, 44 Permanent magnet 45 Distance sensor 46 Metal fitting 47 Function generating circuit 48 Iron core 49 Power source for piezo element 50 Opening 51 Upper plate 52 Small opening 53 Shape memory alloy spring 54 High damping material pon Conical bore hole 61b seat 57 power supply 58 coil 60 switch 61 receiving seat

Claims (16)

[Claims] 1. A vibration control mechanism of a base for supporting a Stirling engine having a piston and a crankshaft, the vibration control rubber having a lower end fixed to a floor or a base plate installed on the floor, and an upper end of the vibration control rubber. A base having the Stirling engine supported thereon, an actuator fixed to the floor or the base plate and having a movable end, and a switch for controlling driving and stopping of the actuator. When the actuator is driven, A vibration regulation mechanism for a Stirling engine, wherein the movable end of the actuator is configured to come into contact with the base. 2. The actuator is made of a shape memory alloy in which one end is fixed to a floor or a base plate and an electric heater is wound around an insulator, and the shape memory alloy is heated by the electric heater to a storage temperature. 2. The vibration regulation mechanism for a Stirling engine according to claim 1, wherein the vibration regulation mechanism is configured so that when the temperature becomes low, the other end comes into contact with the base. 3. An actuator vertically drives a punch having a conical projection at its tip, which is vertically inserted in and supported by a cylindrical enclosure provided on a floor or a base plate.
The vibration regulation mechanism for a Stirling engine according to claim 1 or 2, wherein the base has a conical hole that fits into the conical protrusion. 4. A punch having a ball-shaped projection at the tip is used instead of the punch having a conical projection at the tip, and is provided at the base instead of the conical hole provided at the base. The vibration regulation mechanism for a Stirling engine according to claim 3, wherein a hemispherical hole that fits into the ball-shaped protrusion is used. 5. A spline shaft fixed downward from a base, a universal joint having one end slidably inserted in the spline shaft and the other end fixed to a base plate, and an outer side of the universal joint. And a ring configured to slide so as to lose the flexibility of the universal joint, driven by an actuator provided on the base plate parallel to the spline shaft. Claim 1
The vibration regulation mechanism of the Stirling engine described in. 6. An acceleration detector provided on a base, and a control device which is connected to a switch circuit of the actuator and turns on the switch of the actuator when an output signal of the acceleration detector exceeds a predetermined constant value. The vibration regulation mechanism for a Stirling engine according to any one of claims 1 to 5, further comprising: 7. The vibration regulation mechanism for a Stirling engine according to claim 1, wherein the actuator comprises a piezo element and a power source for applying a voltage to the piezo element. . 8. A vibration energy absorbing material is attached to a portion of the tip of the actuator which is in contact with the base or a portion of the tip of the punch driven by the actuator which is in contact with the base or a hole provided in the base. The vibration regulation mechanism for a Stirling engine according to any one of claims 1 to 4. 9. The vibration regulation mechanism for a Stirling engine according to claim 1, wherein a plurality of actuators are used, and the driving methods of all the actuators are set in directions different from each other. 10. A plurality of actuators are used, and at least one of the plurality of actuators is installed so that its driving direction is different from the driving directions of other actuators. The vibration regulation mechanism for a Stirling engine according to claim 1. 11. The vibration regulation mechanism for a Stirling engine according to claim 5, wherein one spline shaft is provided on the lower surface of the base immediately below the Stirling engine installed on the base. 12. Displacement speed detecting means for outputting the displacement speed of a base provided on the base as an electric signal, and driving the actuator when the displacement speed exceeds a predetermined constant value in response to the electric signal. The vibration regulation mechanism for a Stirling engine according to any one of claims 1 to 5, further comprising: 13. The actuator is made of a damping steel plate and is attached to a floor or a plurality of angles attached to a base plate at a predetermined angle, and the vibration directions regulated by the plurality of actuators are mutually opposite. The vibration regulation mechanism for a Stirling engine according to any one of claims 1 to 4, which is different. 14. A vibration control mechanism for a base, which supports a Stirling engine having a piston and a crankshaft, comprising:
Anti-vibration rubber whose lower end is fixed to the floor or a base plate installed on the floor, a base on which the Stirling engine is installed supported by the upper end of the anti-vibration rubber, the floor or the base of the base fixed to the base plate. A distance sensor that outputs a signal according to the vibration amplitude, a power source that outputs a current according to the signal of the distance sensor, an electromagnetic coil that is maintained by this power source and is provided on the floor or the base plate, and is provided on the base. A vibration regulation mechanism for a Stirling engine, comprising: a magnet that generates an electromagnetic force between the electromagnetic coil and the electromagnetic coil. 15. The power supply has a function characteristic circuit or a level determination circuit that outputs a current only when the signal amplitude from the distance sensor is equal to or more than a predetermined constant value. Vibration control mechanism for the described Stirling engine. 16. The vibration regulation mechanism for a Stirling engine according to claim 14, wherein a rotation angle sensor that outputs a signal according to a rotation angle of the Stirling engine is used instead of the distance sensor.