JPH0334011B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention This invention relates to an improved structure of a valve mechanism for gas distribution in a gas meter, particularly a dry gas meter.

BACKGROUND ART Conventionally, the two-membrane four-measuring-chamber type dry gas meter has been most commonly put into practical use. Such gas meters generally have 4 gas meters in pairs.
Each pair of measuring chambers is separated by a membrane, and the movement of each membrane is controlled by the gas pressure flowing into each measuring chamber in a predetermined order. Converts to rotational drive of a pair of blade shafts, and uses this driving force to operate a sliding valve belonging to a distributor placed above the metering chamber to control the distribution of gas to each metering chamber. It is also used to operate the counter.

Problems to be Solved by the Invention Incidentally, there has been a strong demand for miniaturization of gas meters. Recently, various structural modifications have been attempted for this purpose, but one of the major factors hindering the demand for miniaturization is that the distribution valve mechanism, including the distributor, has become smaller due to the gas flow resistance. This is because the current mechanism is reaching its limit in reducing the size of the current mechanism. In other words, in the conventional valve mechanism of a distributor, the sliding valve, which controls the opening and closing of the gas inlet and outlet of the distributor, almost continuously slides on the valve seat by the driving force based on the rotation of the blade shaft. Therefore, each gas inlet in the distributor is gradually opened and then gradually closed by the valve. For this reason, the effective opening area of the valve seat during the entire process of actual gas flow must be considerably small compared to the wide opening area of the valve seat. For this reason, the smaller the valve mechanism is made, the more gas flow resistance increases, making it difficult to maintain the desired meter driving force, causing performance problems, and ultimately reducing the valve mechanism. The current situation is that we have no choice but to make it relatively large.

On the other hand, the crank mechanism for driving the valves in the conventional two-membrane four-chamber gas meter has a pair of blade shafts 101, 101, as shown in FIG.
From large elbow 102, 102 and small elbow 103, 1
A single crank 104 is rotationally driven through a single crank 104, and a fan-shaped valve 10 is driven from an eccentric position of this crank through a pair of crank rods 105, 105.
6, 106 are reciprocated in an oscillating manner. With this mechanism, crank 1
In order to obtain continuous rotation of 04, the crank ₁ must be connected between the connection position P1 of the small armrest 103 and the connection position of the crank rod 105 for driving the valve.
A phase angle θ of 90° must be set strictly in the rotation direction of 04. For this reason, manufacturing and assembling the crank mechanism was somewhat troublesome, and there were also problems in that it was difficult to achieve sufficient accuracy.

The present invention provides a valve mechanism based on a completely original idea that can solve the above-mentioned problems all at once, thereby making it possible to realize further miniaturization of gas meters.

Means for Solving the Problems In order to achieve the above-mentioned object, the present invention comprises four measuring chambers each forming a pair of two measuring chambers, and a membrane that partitions the two measuring chambers forming the pair. Based on the rotation of a pair of blade shafts that are rotationally driven by the action of each membrane, a crank is continuously rotated in one direction via a large arm and a small arm, and the crank is further rotated in one direction. In a two-membrane, four-chamber gas meter, a sliding valve is made to slide on a valve seat of a distributor based on the rotation of the crank. A power storage drive mechanism that repeatedly stores and releases power based on motion is interposed, and the mechanism allows
In the middle between the timing points of the flow path switching operation of the valve, the valve is held stationary at the extreme position of the reciprocating operation, accumulating force, and at the timing of the switching operation, the accumulated force is released all at once. The valve is actuated instantaneously from one extreme position to the other extreme position, and a connecting point of the small armrest to the crank and a connecting point of a valve driving crank rod extending from the crank, Set on the same radius line with a phase difference in the direction of rotation of the cranks as zero, and the rotation angle of the cranks is 90°.
The object of the present invention is to provide a gas meter characterized in that the valve is activated instantaneously at each time.

Specific embodiments of the above-mentioned force storage drive mechanism include one that utilizes the tensile force or compressive repulsive force of a spring such as a coil spring or a leaf spring, or one that utilizes one or more pairs of springs, as shown in the examples below. Various embodiments have been proposed, such as those that utilize magnetic attraction or repulsion of permanent magnets placed opposite each other.

Embodiments Hereinafter, various embodiments of the present invention will be divided into the basic operating principle mechanism of the meter and the instantaneous valve actuation mechanism, that is, the power storage drive mechanism, which is an important part of the present invention, based on the attached drawings. This will be explained below.

[Gas meter operating principle mechanism]

In FIGS. 1 to 3, a meter casing 1 is a main body 1a having a substantially H-shaped cross section and made of a die-cast molded product of a light metal alloy such as an aluminum alloy.
and abdominal plates 1b, 1b that close both sides, and the interior is divided into two chambers. Each chamber is further divided equally into two chambers each by a pair of membranes 2, 2 arranged vertically, and from the front side of the meter, the first measuring chamber, the second measuring chamber, and the third measuring chamber. It is divided into a measuring chamber and a fourth measuring chamber. Gas is introduced into these four measuring chambers in a predetermined order, and the discharge is controlled.
By causing the membranes 2, 2 to move in the left-right direction in FIG. 12, 12 to cause reciprocating rotational movement within a predetermined rotational angle range.

On the other hand, a distributor 3 is arranged on the casing body 1a toward one side on the right side. This distributor 3 has first to fourth measuring chambers corresponding to the first to fourth measuring chambers, as shown in FIGS. 4 and 5.
gas inlets a, a, a, a are provided, and first and second gas inlets a, a
Common gas exhaust ports X ₁ and X ₂ are provided between the two chambers and between the third and fourth gas inlets a and a, respectively (see FIGS. 4 and 5). As shown in FIGS. 1 and 2, on the distributor 3, two fan-shaped valves 5, 5 at the front and rear, which slide on the valve seats 4, 4 on the upper surface thereof, connect one point of the base end to the distributor. 3 by pivots 6, 6, and each gas inlet port a, a,
a and a are opened and closed in a predetermined order to control the inflow of gas into each of the measuring chambers, .

The reciprocating sliding movement of the valves 5, 5 is caused by the reciprocating rotational movement of the blade shafts 12, 12, and therefore, the two are connected by a crank-type interlocking mechanism. There is. This interlocking mechanism, as shown in FIG.
One crank 15 is continuously driven to rotate in one direction via large armrests 13, 13, one end of which is fixed to 2, and small armrests 14, 14', one end of which is pivotally connected to the other end. has. And this crank 1
Based on the continuous rotation of the valve 5, both the front and rear valves 5, 5 are actuated via an instantaneous valve drive mechanism, that is, a force storage drive mechanism 20, which will be described later. Through this, a counter 18 in a counter case 17 attached to the front side of the upper cover 16 of the casing 1 is operated. 21 is a connecting shaft of a small armrest to the crank 15, and 22 is a crankshaft.

[Power storage drive mechanism]

As described above, the power storage drive mechanism instantaneously operates the valves 5, 5 at the timing of switching the flow paths based on the continuous rotation of the crank 15, and does not operate the valves on the way up to the timing. It functions to store the force for performing the instantaneous operation while remaining stationary at a position in front of one extreme point of the operating stroke. Therefore, as long as such a function can be realized, various embodiments may be adopted in terms of design, and the specific structure is not particularly limited. As preferred embodiments of the force storage drive mechanism, a spring-type one using a spring for the force storage device and one using magnetic force of a permanent magnet are proposed. Among these two methods,
The former can be classified into those that utilize the compressive repulsive force of a coil spring or leaf spring, and those that similarly utilize the tensile force of a spring.The latter utilize the magnetic attraction force of a magnet, and those that utilize the repulsive force. It can be categorized into those used.

Next, specific embodiments of each of the above systems will be described with reference to the drawings.

(a) Compression spring method The force storage drive mechanism described below with reference to FIGS. 1 to 11 shows an example in which a leaf spring is used as an example of the compression spring method. be.

As shown in FIG. 1, the crank 15 included in the interlocking mechanism between the blade shafts 12, 12 and the front and rear valves 5, 5 includes a pair of crank rods 23 for driving the valves in an eccentric position. 2
3 is pivoted at one end. As shown in FIG. 7, the connecting point P ₂ of the crank rods 23, 23 to the crank 15
For connection point P ₁ to crank 15 of 4,
It is set at a position where the phase difference is zero in the rotational direction of the crank 15. That is, both connection points P ₁ , P ₂
are set on the same radius line of the crank 15. In conventional valve mechanisms, unless a 90° phase difference is provided between the two connection points as described above, if the two connection points stop in a straight line (the so-called dead center position), the Although it was not possible to cause the crank 15 to rotate, in this invention, by adopting the power storage drive mechanism 20, it is possible to set the positions of both connection points with the phase difference as described above being zero, This makes it possible to further simplify the design, manufacture, and assembly of the crank part, and to improve assembly accuracy.

On the other hand, as shown in FIGS. 1 and 6, the pivot shafts 6, 6 of the valves 5, 5 are extended upwardly so that their extensions are directed upwardly toward their free ends. A pair of valve arms 24, 24 extending toward the valve are each pivotally connected at one end. A connecting pin 2 is attached to the intermediate portion of the valve arms 24, 24 in the longitudinal direction.
5, the tip of the crank rod 23 is pivotally connected. Furthermore, valve arm 2
An arcuate compression-type leaf spring 26 is installed between the tip of the bulb 4 and the upper surface of the valve 5 at a proper position in the widthwise intermediate portion near the tip. Further, on the side of the distributor 3, a stopper 2 is provided for accurately stopping the valves 5, 5 at the extreme positions of their reciprocating strokes.
7 and 27 are erected, one pair each.

Therefore, as the crank rod 23 moves in the direction of the arrow in FIG. 6 due to the rotation of the crank 15, the valve arm 24 continuously moves about the pivot shaft 6 in the direction of the arrow in the figure. However, between the tip and the valve 5, the leaf spring 26
Therefore, when the valve arm 24 rotates counterclockwise in the figure with the valve 5 positioned at one of the extreme positions as shown in FIG. (See Figure A), the compression deformation of the leaf spring 26 applies a repulsive force to it until it reaches the dead center position where the connecting fulcrums at both ends of the leaf spring 26 and the center of the pivot shaft 6 of the valve 5 are aligned. While accumulating force, keep the valve 5 in its original position in a stationary state (see Figure 11B). and,
When the leaf spring connecting point at the tip of the valve arm 24 exceeds the dead center position, the force stored in the leaf spring 26 is released all at once due to the compression of the leaf spring 26, and the valve 5 rapidly moves to the valve arm. 24
The stopper 2 is momentarily oscillated in a direction opposite to the direction of movement of the stopper 2, that is, clockwise in FIG.
7, it is stopped at the other stroke pole position (see FIG. 11C). After that, the valve arm 24 continues to rotate counterclockwise for a while, and then reverses itself and rotates clockwise. It remains stationary in position.

The relationship between the above-mentioned operation of the valve 5 and the flow path switching operation by the distributor 3 will be explained next.

7 to 10 sequentially show the relationship between the rotation angle of the crank 15 and the positions of the front and rear valves 5, 5 at each rotation angle of the crank 15 of 90 degrees. As can be understood from these figures, in the two-membrane four-chamber gas meter, either the front or rear valve 5 is activated momentarily every 90° rotation angle of the crank 15, and the gas flow path is switched.
That is, the distribution of gas to each metering chamber is changed. In addition, in FIGS. 7 to 10, the portion shown with a chain line indicates the portion where the valve 5 substantially covers the gas inlet and outlet of the valve seat 4 of the distributor 3.

In the state shown in Fig. 7, the first gas inlet a
The first metering chamber continues to take in air through the air. Then, when the crank 15 rotates 90 degrees from this state and reaches the valve switching timing shown in FIG. Operate. Therefore, by this, the second
The gas inlet a opens, allowing gas to enter the second metering chamber. At this time, the first measuring chamber has completed intake, so as gas flows into the second lightweight chamber, gas flows from the first measuring chamber through the recess on the bottom of the valve 5 and the gas outlet _X1 . It is discharged. Furthermore, at the time of the above switching of the front valve 5, the third metering chamber on the rear side is at the midpoint of the intake stroke through the third gas inlet a, and even if the state shown in FIG. 8 is reached, the rear valve 5 is Remain stationary. Therefore, the intake of air into the third measurement chamber and the exhaustion of air from the fourth measurement chamber continue, so the rotation of the crank 15 continues.

When the crank 15 further rotates 90 degrees and reaches the state shown in FIG. 9, the rear valve 5 is instantaneously activated, closing the third gas inlet a and opening the fourth gas inlet a. At this time, since the intake of air into the third measuring chamber has been completed, air intake into the fourth measuring chamber a is started instead, and exhaust is performed from the third measuring chamber, and based on this intake and exhaust, the crank
5 is still driven in rotation. At the time of switching of the rear valve 5 shown in FIG. 9, the second metering chamber is exactly at the midpoint of the intake stroke.

Subsequently, by further rotating the crank 15 by 90 degrees, when the state shown in FIG. 10 is reached, the front valve 5 is instantaneously switched again. Therefore, intake of air into the first measurement chamber is started, exhaustion of air is started from the second measurement chamber, and the rotation of the crank 15 is thereby continued. At the switching timing of the front valve 5 in FIG. 10, the fourth metering chamber is in the middle of the intake stroke, and the intake continues while the rear valve 5 is kept stationary.

Gas metering is performed by repeating the steps shown in FIGS. Since the switching action is instantaneously performed from the pole position to the other unknown pole position, each of the first to fourth measuring chambers...
During the intake process, the corresponding first to fourth gas inlets a, a, a,
The opening area of a is maintained at a substantially fully open state corresponding to the opening area of the valve seat 4. That is, the gas inlet is not gradually opened and gradually closed as in the conventional case. Therefore, the gas flow path resistance can be significantly reduced.

In the above embodiment, the leaf spring 26 is used as an example of using a compression type spring, but it goes without saying that a compression coil spring may be used instead.

(b) Tension spring system For the force storage drive mechanism 20', a tension coil spring 36 is used as shown in FIG. 12 in place of the compression spring of the previous embodiment. In addition, in relation to the use of a tension spring, the force storage drive mechanism 2
0' also has a long hole 30 formed along its length at the tip of the valve arm 24' extending from the pivot 6 of the valve 5, while one end is pivotally connected to the free end of the valve 5. The slide pin 3 has a tip of the valve link 31 loosely fitted into the elongated hole 30.
2 to the tip of the valve arm 24', and a coil spring 36 is tensioned so as to apply a tensile force between the slide pin 32 and the pivot shaft 6.

In this embodiment as well, the tensile force of the coil spring 36 causes the pivot 6, the pivot point 37 at the base end of the valve link 31, and the slide pin 32 to be aligned in a straight line, with the dead center position being defined as the dead center position of the valve arm 24'. When the valve 5 is turned in either the left or right direction past the dead center position, the valve 5 is momentarily operated in the opposite direction, and the gas flow path is switched.

Since this is the same as in the other embodiments described above, detailed explanation will be omitted. It goes without saying that even in the case of the tension spring system, a belt-shaped plate spring formed into an arc shape or the like can be used in place of the coil spring 36.

(c) Repulsion permanent magnet method This embodiment is shown in FIGS. 13 and 14, and a modification thereof is shown in FIG. 15.

Power storage drive mechanism 2 shown in FIGS. 13 and 14
0'', the leaf spring 26 of the above-mentioned mechanism shown in FIGS. 1 to 11 is constantly extended using the magnetic repulsion force generated by a pair of permanent magnets MG ₁ and MG ₂ arranged with the same poles facing each other. This is installed in place of the telescopic connecting rod 46 that is biased in the direction.
consists of a cylindrical female rod 47 with one permanent magnet MG ₁ fixed to its tip, and a rod-shaped male rod 48 into which the tip is loosely inserted. Another permanent magnet MG ₂ whose mounting position can be slid in the axial direction is
It was installed with the same poles facing MG ₁ .

Therefore, during the switching operation timing of the valve 5, as the telescoping link 46 shortens, the permanent magnets MG ₁ and MG ₂ are brought close to each other by their magnetic fields, thereby accumulating repulsive force. Then, at the switching timing, the valve 5 is extended to release the stored force at once, causing an instantaneous switching operation of the valve 5. Other configurations and operations are similar to those of the compression spring type embodiment.

In the modification shown in FIG. 15, in order to increase the range of elastic expansion/contraction behavior of the telescopic connecting rod 46' caused by the magnet, a permanent magnet MG ₁ on the cylindrical female rod 47 side,
Between the permanent magnet MG ₂ on the side of the rod-shaped male rod 48, one or more permanent magnets Gn) can be slid onto the male rod 48 in order so that the same-named poles of the adjacent ones face each other. It was established in The rest is the same as the embodiment shown in FIG.

(d) Attraction permanent magnet system The force storage drive mechanism 20'' of this embodiment is shown in FIG. 16 and uses a tension spring system instead of the tension cork spring 36 of the embodiment shown in FIG. 12.
The telescopic link 56 is always elastically biased in the shortening direction by the attraction force, that is, the magnetic attraction force, caused by one or more pairs of permanent magnets MG ₁ and MG ₂ .
It uses In this embodiment, during the switching operation timing of the valve 5,
With the extension behavior of the telescopic link 56, both permanent magnets
When MG ₁ and MG ₂ are separated in their magnetic fields, they accumulate attractive force, and at the above-mentioned switching timing, they act shortened to release this accumulated force at once, thereby causing an instantaneous switching operation of valve 5. It is something that causes it. Other structures and functions are similar to those of the tension spring type embodiment.

Although the present invention has been described above using specific examples, the present invention is not limited to the above-mentioned examples. In particular, the present invention applies to a two-curtain, four-chamber type gas meter, which is equipped with a so-called parallel sliding type or rotary type valve in which the valve slides linearly on a valve seat to switch gas inflow. The same applies.

Effects of the Invention As described above, the present invention includes four measuring chambers arranged in pairs of two, and a membrane that partitions the two measuring chambers, each of the membranes being separated from each other. Based on the rotation of a pair of blade shafts that are rotationally driven by the operation, a crank is continuously rotated in one direction via a large armrest and a small armrest, and further based on the rotation of the crank. In a two-membrane, four-chamber type gas meter in which a sliding valve is slid on a valve seat of a distributor, storage is generated between the crank and the sliding valve based on the continuous rotational movement of the crank. A power storage drive mechanism that repeatedly generates and releases force is interposed,
The mechanism stores power while holding the valve stationary at the extreme position of reciprocating operation in the middle between the timings of the flow path switching operation of the valve, and stores the stored power all at once at the timing of the switching operation. Since it is designed to instantaneously operate the valve from one extreme position to the other extreme position, during the intake process of each metering chamber whose intake and exhaust are controlled by the valve, The effective opening area of the gas inlet of the distributor belonging to the metering chamber is calculated throughout the entire process from the initial stage to the completion of intake.
Almost 100% corresponding to valve seat opening area
It is possible to maintain the valve in a nearly fully open state. In other words, it is possible to effectively utilize nearly 100% of the opening area of the valve seat of the distributor. Therefore, the flow path resistance applied to the gas flow entering the metering chamber from the gas inlet can be significantly and significantly reduced compared to the conventional structure. By the way, when using a conventional continuous sliding valve mechanism, the gas inlet gradually opens and closes as the valve moves, so the total maximum opening area of the valve seat (opening area x time) Only about 70% of the effective opening area can be secured, and about 30% becomes dead space, and this dead space also causes pressure loss to increase in proportion to the square of the flow rate as the meter rotation speed increases. In practice, the pressure loss is not limited to 30%, but synergistically causes a negative effect of 50 to 60% or more. However, depending on the application of this invention, the above pressure loss can be reduced to the minimum. As a result, in a gas meter that generates the same differential pressure at the same flow rate, it is possible to reduce the size of the valve mechanism by about 2/3 to 1/2 of that of conventional products. This also means that the area of the sliding contact area of the valve can be reduced, so the required valve driving force can be obtained even if the amount of membrane required is reduced, which greatly contributes to the miniaturization of the entire gas meter. can make a contribution.

Furthermore, as shown in the examples, the present invention provides two
In a membrane four-chamber type gas meter, the connecting point of the small armrest to the crank in the interlocking mechanism that transmits power from the blade shaft to the valve, and the connecting point of the crank rod for driving the valve extending from the crank, are connected to each other by the rotation of the crank. The valves are set on the same radius line with a phase difference of zero, and the valves are instantaneously activated every 90 degrees of rotation of the crank, so that the small armrest for the crank is not required as in the past. There is no need to arrange the connection point on the drive side of the valve and the connection point on the driving side of the valve with a strict 90° phase difference in the direction of rotation of the crank, making it easier to achieve precision when assembling the transmission system, and resulting in higher accuracy. This not only makes it easier to assemble a high-precision gas meter, but also eliminates the pulsation in gas flow rate caused by gas being discharged from each metering chamber in a sine curve with the crank angle out of phase by approximately 90 degrees. This does not occur, and the discharge gas flow rate can be stabilized.

[Brief explanation of the drawing]

Figures 1 to 11 show an embodiment of the present invention using a compression type spring-based power storage drive mechanism. Figure 1 is a plan view of the distribution chamber of the gas meter, and Figure 2 is the entire gas meter. 3 is a sectional view taken along the line A-A in FIG. 2, FIG. 4 is a plan view of the distributor, FIG. 5 is a sectional view taken along the line B-B in FIG. 4, and FIG. A perspective view of the power storage drive mechanism, and FIGS. 7 to 10 are valve diagrams sequentially showing the opening and closing states of the valve by the power storage drive mechanism as the crank changes its rotation angle by 90 degrees. A, B, and C in Figure 11 also indicate the opening/closing status of the valve.
FIG. 7 is a valve diagram sequentially shown with the rotation angle changed by 45°. Fig. 12 is a perspective view of the main parts of a valve mechanism equipped with a force storage drive mechanism using a tension spring type, Fig. 13 is a plan view of main parts of a valve mechanism equipped with a force storage drive mechanism using a repulsion permanent magnet type, and Fig. 14 15 is a vertical sectional view showing a modified example of the telescopic linking rod in the embodiment shown in FIG. 3, and FIG. 16 is a valve equipped with a force storage drive mechanism using an attractive permanent magnet system. FIG. 3 is a perspective view of the main parts of the mechanism. FIG. 17 is a valve diagram of a valve mechanism in a conventional two-membrane four-chamber gas meter. 1... Casing, 2... Capsule, 3... Distributor, 4... Valve seat, 5... Valve, 6...
Axis, 12... wing axis, 13... large elbow, 14...
Kojigane, 15... Crank, 20, 20', 2
0'', 20''...Power storage drive mechanism, 23...Crank rod, 24, 24'...Valve arm, 26...
...Plate spring, 30...Elongated hole, 31...Valve link, 32...Slide pin, 36...Coil spring, 46, 46', 56...Telescopic link, MG ₁ ,
MG ₂ , MGn...Permanent magnet,...First measuring chamber,
...Second measuring chamber, ...Third measuring chamber, ...Fourth measuring chamber, a...First gas inlet, a...Second gas inlet, a...Third gas inlet, a...
... Fourth gas inlet, X ₁ , X ₂ ... Gas outlet.

Claims (1)

[Scope of Claims] 1. Comprising four measuring chambers arranged in pairs of two, and a membrane that partitions the two measuring chambers, which are rotated by the movement of each of the membranes. Based on the rotation of the pair of driven blade shafts, the crank is continuously rotated in one direction via the large and small armrests, and further based on the rotation of the crank, the valve of the distributor is driven. In a two-membrane, four-chamber type gas meter in which a sliding valve is slid on a seat, an electric power is stored and released between the crank and the sliding valve based on the continuous rotational movement of the crank. A repetitive force storage drive mechanism is interposed, and the mechanism
In the middle between the timing points of the flow path switching operation of the valve, the valve is held stationary at the extreme position of the reciprocating operation, accumulating force, and at the timing of the switching operation, the accumulated force is released all at once. The valve is actuated instantaneously from one extreme position to the other extreme position, and a connecting point of the small armrest to the crank and a connecting point of a valve driving crank rod extending from the crank, Set on the same radius line with a phase difference in the direction of rotation of the cranks as zero, and the rotation angle of the cranks is 90°.
A gas meter characterized in that the valve is instantaneously activated every time the gas meter is used. 2. The power storage drive mechanism connects one end to the crank,
Claim 1: The crank rod comprises a crank rod whose other end is connected to an intermediate portion of a valve arm extending from the pivot of the valve, and a compression type spring installed between the tip of the valve arm and a proper position of the valve.
Gas meter as described in section. 3. The power storage drive mechanism connects one end to the crank,
a crank rod whose other end is connected to the middle part of a valve arm extending from the pivot of the valve; and a valve link whose one end is connected to the valve and the other end to the tip of the valve arm so as to be slidable in the length direction of the arm. 2. The gas meter according to claim 1, further comprising a tension spring stretched between the tip of the link and the pivot of the valve. 4. The power storage drive mechanism connects one end to the crank,
A crank rod whose other end is connected to the middle part of a valve arm extending from the pivot of the valve, and one or more pairs of permanent magnets installed between the tip of the valve arm and the appropriate position of the valve are used to make use of the repulsive force. 2. The gas meter according to claim 1, wherein the gas meter comprises a telescoping link that is always biased in the direction of extension. 5. The power storage drive mechanism includes a crank rod having one end connected to an intermediate portion of a valve arm extending from the pivot of the crank, one end to the valve, and the other end to the tip of the valve arm so as to be slidable in the length direction of the arm. It is composed of a connected valve link and an extensible link that is installed between the link and the pivot of the valve and is constantly biased in the direction of contraction using the attractive force of one or more pairs of permanent magnets. A gas meter according to claim 1.