JP4580673B2 - Measuring instrument - Google Patents

Description

The present invention relates to a measuring instrument, for example, it relates to a measuring instrument or the like having a braking device of a spindle for braking the descent speed of the spindle.

Conventionally, a dial gauge is known as a measuring instrument having a spindle that moves up and down through the main body case, and in order to avoid the probe provided at the tip of the spindle from colliding strongly with the object to be measured, A dial gauge provided with a braking means (spindle braking device) for preventing the fall is known (for example, Patent Document 1).
FIG. 8 is a view showing a braking means 700 of a conventional dial gauge 800.
In FIG. 8, a dial gauge 800 includes a spindle 300 penetrating the main body case 200 so as to be movable up and down, a bushing 212 as a guide means for guiding the upper end side of the spindle 300, and a braking means for braking the spindle 300. 700.
The spindle 300 is urged downward by urging means (not shown).
The braking means 700 includes a long cylindrical cylinder 610 that is fitted on the upper end side of the bush 212, and a movable member 710 that is slidably provided in the cylinder 610.

The bush 212 is press-fitted to the cylinder 610 so as to maintain airtightness.
On the upper end side of the cylinder 610, a partition body 740 and a cap 760 for defining a valve chamber between the partition body 740 are provided.
The partition body 740 has a through hole 742 that communicates the inside of the cylinder 610 with the valve chamber, and the partition body 740 has a tapered valve seat 741 that increases in diameter at the upper end side opening of the through hole 742. A ball 750 is seated on the valve seat 741, and the through hole 742 is closed.
The cap 760 has a vent hole 761 that allows the valve chamber to communicate with the outside.

  The movable member 710 defines a first partition chamber 616 between the bushing 212 and the cylinder 610, and defines a second partition chamber 617 between the partition 740 and the cylinder 610. The outer diameter of the movable member 710 is slightly smaller than the inner diameter of the cylinder 610, and a predetermined gap exists between the movable member 710 and the inner wall of the cylinder 610. A through hole 711 is formed in the movable member 710, and a stop screw 720 and a mounting screw 730 are sequentially screwed onto the upper end of the spindle 300, and a head 731 of the mounting screw 730 is inserted into the through hole 711 of the movable member 710. The movable member 710 and the spindle 300 are integrated by engaging with the inner wall surface. The through hole 711 of the movable member 710 is sealed with a cap 712.

In such a configuration, the first compartment 616 and the second compartment 617 are substantially hermetic chambers except for the gap between the movable member 710 and the cylinder inner wall surface. When the movable member 710 descends downward, the pressure in the first compartment 616 increases and the pressure in the second compartment 617 decreases. As a result, the movable member 710 floats against the gravity within the cylinder 610 to some extent, and the spindle 300 is braked by the buoyancy acting on the movable member 710.
Incidentally, the ball body 750 seated on the valve seat 741 of the partition wall body 740 corresponds to a decrease in gravity (in the axial direction) acting on the spindle 300 and the movable member 710 when the dial gauge 800 is tilted sideways. The dial gauge 800 is provided to open the through-hole 742 and reduce the braking force when the dial gauge 800 falls sideways.

Japanese Patent Publication No. 3-70761

  However, in the configuration disclosed in Patent Document 1, it is necessary to ensure the airtightness of the first compartment 616 and the second compartment 617. For this reason, problems such as an increase in the number of components for liquid-tightly closing the openings at both ends of the cylinder 610 and an increase in the number of assembly steps are given as an example.

An object of the present invention is to provide a measuring instrument having a simple configuration and including a spindle braking device that improves the operability of the spindle.

The measuring instrument of the present invention includes a main body case, a spindle that passes through the main body case and is movable in the axial direction, a cylindrical bush that is provided in the main body case and guides the spindle, display means for displaying the displacement amount, a measuring device and a braking device for braking the movement speed of the spindle, the spindle is arranged to be reciprocated in the axial direction in a state of being inserted into said bush It is have a feeler at one end movement, wherein the braking device includes a cylinder having a space in which one end the spindle with mounted reciprocates in the bush, in the cylinder together with the spindle in the other end side of the front Symbol spindle A piston provided in a possible manner, and a first series defined by the piston on the bush side in the cylinder. And Dialog chamber, a second cylinder chamber which is partitioned at the opposite side to the manual said first cylinder chamber to said piston in said cylinder, fluid is communicated with said second cylinder chamber and the first cylinder chamber A main flow path provided to be able to flow, a fine flow path that allows the relatively small amount of fluid to flow through the first cylinder chamber and the second cylinder chamber, and an opening / closing means for opening and closing the main flow path. The opening / closing operation of the opening / closing means is linked to the movement of the spindle, and when the spindle moves to one end side, the opening / closing means closes the main flow path and the spindle moves to the other end side. wherein the interlocking means the to open the main flow path opening and closing means, Bei example to, the primary flow passage is constituted by a through hole formed through said piston, said opening and closing means, the provided main channel valves Seat and this valve And a valve body seated so as to be able to come into contact with and separate from the valve seat from the opposite side of the spindle, and the interlocking means connects the spindle and the valve body in a state of being inserted into the through hole. The measuring device is configured by a valve stem having a length that secures a predetermined gap between the spindle and the piston in a state where the valve body is seated on the valve seat, and the measuring instrument has one end. A lifter portion is provided which is attached to the valve body and is provided in a state where the other end protrudes from the opening on the other end side of the cylinder .

In this configuration, when the spindle moves to one end side, the piston also moves in the cylinder to one end side. At this time, since the main flow path is closed by the opening / closing means, a small amount of fluid flows into the second cylinder chamber from only the fine flow path. Then, a negative pressure is generated in the second cylinder chamber by moving the piston to one end side. As a result, when the spindle moves toward one end, a large braking effect can be obtained by the internal pressure (negative pressure) in the second cylinder chamber.
When the spindle moves to the other end side, the piston also moves in the cylinder to the other end side. At this time, since the main flow path is opened by the opening / closing means, the second cylinder chamber communicates with the first cylinder chamber not only by the fine flow path but also by the main flow path. Then, fluid flows out from the second cylinder chamber from the fine flow path and the main flow path. As a result, the positive pressure in the second cylinder chamber is suppressed, and the braking effect is reduced when the spindle moves toward the other end side.
That is, a braking effect can be obtained only when the spindle moves to one end side, and no braking effect can be generated when the spindle moves to the other end side. That is, it is possible to prevent inconveniences such as the spindle suddenly moving (for example, dropping) to one end side and causing the probe to crash into the object to be measured, while the spindle can be easily moved (for example, lifted) to the other end side. Therefore, the operability of the spindle is improved.
Further, according to this configuration, since the braking effect is obtained only by the internal pressure of the second cylinder chamber, the first cylinder chamber may be opened. As a result, the step of sealing the first cylinder chamber is not necessary as compared with the conventional case.

Further , the main flow path is constituted by a through-hole formed through the piston, and the opening / closing means is provided from a side opposite to the spindle between the valve seat provided in the main flow path and the valve seat. A valve body seated on and away from the valve seat, the interlocking means connecting the spindle and the valve body in a state of being inserted into the through hole, and the valve body is the valve body that is composed of a valve stem in a state of sitting on the seat has a length to secure a predetermined gap between the spindle and the piston.

In this configuration, when the spindle moves to one end side, the movement of the spindle is transmitted to the valve body by a valve rod provided in a state of passing through the through hole, and the valve body moves to one end side together with the spindle and is seated on the valve seat. To do. That is, when the spindle moves to one end side, the main flow path is closed by the valve body.
On the other hand, when the spindle moves to the other end side, the valve element is pushed to the other end side by the valve rod and leaves the valve seat. Then, the main flow path is opened.
According to this configuration, the spindle and the valve body are integrally moved by the valve rod, and the opening / closing operation of the valve is interlocked with the movement of the spindle.
Then, the valve body is seated from the opposite side of the spindle with the valve seat in between, and this valve body is pulled by the spindle through the valve rod, so that the valve body is moved when the spindle moves to one end side. The main flow path is more reliably closed by seating on the valve seat more strongly. That is, when the spindle moves to one end side, the main flow path is completely closed, and the airtightness of the second cylinder chamber (excluding the fine flow path) is improved.
Further, when the valve body is moved integrally with the spindle to the one end side via the valve rod, at this time, the piston is also pulled together with the spindle to the one end side by the engagement between the valve seat and the valve body. Then, since it is not necessary to separately provide a means for engaging the spindle and the piston, a simple configuration can be achieved.
The display means for displaying the displacement of the spindle may display the detected value by detecting the amount of displacement of the spindle with an encoder (for example, photoelectric type, capacitance type, magnetic type encoder), for example. Alternatively, the displacement amount of the spindle may be enlarged and displayed by a gear mechanism.
For example, when measuring the depth of a hole, etc., the lower end side of the spindle cannot be held by hand. A lifting operation can be performed.

In the present invention, the switching means is arranged before Symbol valve seat, the valve member and the valve body is the valve seat and the valve seat is held between said valve body when seated on the valve seat preferably includes a resilient member that seals between.

  According to this configuration, when the valve body is seated on the valve seat, the elastic member is elastically deformed so that the gap between the valve seat and the valve body is completely sealed, and the second cylinder chamber (excluding the fine flow path) is sealed. ) Airtightness is improved.

Here, in the present invention, the fine flow path is formed by a groove that is cut along the axial direction on the outer peripheral surface of the piston and communicates the first cylinder chamber and the second cylinder chamber. It is preferable.
According to this configuration, minute communication between the first cylinder chamber and the second cylinder chamber is ensured by the minute flow path regardless of the position of the piston and regardless of the open / closed state of the main flow path.

Further, in the present invention, a communication path for communicating the main flow path with the first cylinder chamber is ensured in a state where the spindle moves to the other end side and the end face of the spindle contacts the end face of the piston. It is preferable.
According to this configuration, when the spindle moves to the other end side and the valve element is separated from the valve seat, the first cylinder chamber is communicated with the second cylinder chamber via the main flow path.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be illustrated and described with reference to reference numerals attached to respective elements in the drawings.
(First embodiment)
1st Embodiment which concerns on the measuring device of this invention is described with reference to FIGS.
FIG. 1 is an overall view of the measuring instrument, and FIG. 2 is an internal configuration diagram of the measuring instrument. FIG. 3 is an enlarged sectional view showing the configuration of the upper end of the spindle and the braking means.
The measuring instrument according to the first embodiment is a dial gauge (indicator) 100, and a main body case 200 having a storage space therein, and a spindle 300 provided so as to be slidable in the axial direction through the main body case 200. The biasing means 400 (see FIG. 2) for biasing the spindle 300 toward one end side (lower end side) in the axial direction, the displacement detection means 500 for detecting the displacement amount of the spindle 300, and the descent speed of the spindle 300 are braked. Braking means (spindle braking device) 600.

The main body case 200 includes guide means 210 for guiding the moving direction of the spindle 300 and a display unit 220 as output means for displaying the displacement amount of the spindle 300.
The guide unit 210 includes a stem 211 that guides the lower end side (one end side) of the spindle 300 and a bush 212 that guides the upper end side (the other end side) of the spindle 300.
As shown in FIG. 2, the stem 211 and the bush 212 are cylindrical members that are attached to the side walls of the main body case 200 with their axes aligned at the opposing positions. 300 is slidably fitted.
The bush 212 is a short cylindrical member, and has a flange portion 213 that protrudes in a flange shape from the outer peripheral surface at substantially the center in the axial direction. As shown in FIG. 3, a lower end side large diameter portion 217 that increases in diameter by sandwiching the reduced diameter portion 216 between the flange portion 213 on one end side (lower end side) on the outer peripheral surface of the bush 212. Is formed. Further, an upper end side large diameter portion 215 is formed on the outer peripheral surface of the bush 212. The upper end side large diameter portion 215 is formed between the flange 213 and the flange portion 213 on the other end side (upper end side).
The bush 212 is attached to the main body case 200 by press-fitting the lower end side (the reduced diameter portion 216 and the lower end side large diameter portion 217) of the flange portion 213 into the side wall of the main body case 200.

  The spindle 300 includes a measuring element 310 having a predetermined rigidity at one end (lower end), and has a female screw portion 320 at the upper end.

  The biasing means 400 includes a guide rod 410 fixed in parallel with the spindle 300 in the housing space of the main body case 200, one end slidable along the guide rod 410, and the other end fixed to the spindle 300. A guide piece 420 and a coil spring 440 that is provided by being extrapolated to the guide rod 410 and biases one end of the guide piece 420 downward.

  The displacement detection unit 500 includes an index scale 510 provided in parallel to the spindle 300 via an attachment member 520, and a detection unit 530 that is fixed to the main body case 200 and detects the amount of displacement of the index scale 510. The detection value detected by the detection unit 530 is displayed on the display unit 220.

The braking means 600 will be described.
The braking means 600 is provided with a long cylindrical cylinder 610 attached to the upper end of the bush 212, and the cylinder 610 can be moved up and down together with the spindle 300. The cylinder 610 includes a first cylinder chamber 611 and a second cylinder chamber 612. The piston 620 that forms the partition, the flow path 630 that ventilates the first cylinder chamber 611 and the second cylinder chamber 612, the opening and closing means 660 that opens and closes the flow path 630, and the opening and closing operation of the opening and closing means 660 is the vertical movement of the spindle 300. And interlocking means 670 for interlocking with.

  The inner wall of the cylinder 610 is smoothly finished with high accuracy, and a bush 212 is press-fitted into the lower end thereof. That is, the upper end (the reduced diameter portion 214, the upper end side large diameter portion 215) of the bush 212 from the flange portion 213 is fitted in the lower end side opening of the cylinder 610 without a gap. A cylinder cap 613 is fitted to the upper end of the cylinder 610, and the upper end side opening of the cylinder 610 is sealed in a liquid-tight manner.

The piston 620 has a cylindrical shape whose outer diameter is substantially equal to the inner diameter of the cylinder 610.
The piston 620 defines a first cylinder chamber 611 between the bushing 212 and the spindle 300 on the lower end side, and forms a second cylinder chamber 612 between the piston cap 623 and the cylinder cap 623 on the upper end side of the piston 620. To do.
On the lower end surface of the piston 620, an outer edge wall 621 that stands up as compared with the central portion is provided upright.

The flow path 630 communicates with the first cylinder chamber 611 and the second cylinder chamber 612 so as to flow a relatively large amount of gas, and the main flow path 640, the first cylinder chamber 611, and the second cylinder chamber 612. And a fine channel 650 serving as a channel through which a relatively small amount of gas is circulated.
The main flow path 640 is formed by a through hole 641 that is formed to penetrate the piston 620 and communicates the first cylinder chamber 611 and the second cylinder chamber 612. A diameter-reduced portion (valve seat) 642 is formed on the inner wall of the through-hole 641 on the way from the upper end side to the lower end side, and the through-hole 641 is formed by a step of the diameter-reduced portion 642 on the way from the upper end side to the lower end side. Reduce diameter. Further, a tapered surface 643 that increases the diameter of the opening of the through hole 641 is formed on the lower end surface of the piston 620. The tapered surface 643 has a different slope depending on the location, and a steep slope 644 is provided depending on the location.
The micro flow path 650 is configured by several grooves 651 engraved along the axial direction on the outer peripheral surface of the piston 620.

The opening / closing means 660 is inserted into the O-ring 662 as a ring-shaped elastic member placed on the reduced diameter portion 642 in the through hole 641 of the main channel 640 and the through hole 641 of the main channel 640 from the upper end side opening. And a valve head (valve element) 661 that is slidably seated through an O-ring 662 on a reduced diameter portion 642 of the reference numeral 641.
The valve head 661 can move up and down on the upper end side of the reduced diameter portion 642 in the through hole 641, and the diameter of the valve head 661 is at least larger than the diameter of the lower end side of the through hole 642. When the valve head 661 descends downward and the O-ring 662 is sandwiched between the valve head 661 and the reduced diameter portion 642, the main flow path 640 is closed.
On the other hand, when the valve head 661 moves upward and the valve head 661 is separated from the reduced diameter portion 642, the main flow path 640 is opened, and the first cylinder chamber 611 and the second cylinder chamber 612 are communicated.

The interlocking means 670 is constituted by a valve rod 671 extending from the valve head (opening / closing means) 661 and passing through the through hole 641 and connected to the upper end of the spindle 300.
A male screw 672 that engages with the female screw 320 of the spindle 300 is provided at the lower end of the valve rod 671.
Here, the valve stem 671 has such a length that the lower end of the valve stem 671 protrudes from the lower end side opening of the through hole 641 in a state where the valve head 661 is seated on the reduced diameter portion 642 of the through hole 641. A predetermined gap G exists between the spindle 300 (the upper end) and the piston 620 (the lower surface).

The operation of the first embodiment having such a configuration will be described with reference to FIGS.
FIG. 4 is a diagram illustrating a state where the spindle 300 is lifted and the spindle 300 moves upward. FIG. 5 is a diagram illustrating how the spindle 300 is lowered.
First, the case where the spindle 300 moves upward will be described with reference to FIG.
When the spindle 300 moves upward, the valve rod 671 and the valve head 661 move together with the spindle 300. When the valve head 661 moves upward, the valve head 661 moves away from the O-ring 662 provided in the reduced diameter portion 642. Then, the main channel 640 is opened.
When the spindle 300 further rises, the upper end of the spindle 300 comes into contact with the lower end surface of the piston 620, and the piston 620 is pushed up by the upper end of the spindle 300.
When the upper end surface of the spindle 300 and the lower end surface of the piston 620 come into contact with each other, the tapered surface 643 formed at the opening of the through hole 641 and the steep slope 644 formed at a part of the tapered surface 643 cause the piston 620. A predetermined gap (communication path) is formed between (the lower end face of) and the spindle 300 (the upper end face thereof), and the communication of the main flow path 640 is ensured.

When the piston 620 moves upward, a positive pressure is generated in the second cylinder chamber 612 (a negative pressure is generated in the first cylinder chamber 611). At this time, since the first cylinder chamber 611 and the second cylinder chamber 612 are communicated with each other by the main flow path 640 in addition to the fine flow path 650, the second cylinder chamber 612 passes through the fine flow path 650 and the main flow path 640. Air (fluid) flows into the first cylinder chamber 611. Then, generation of positive pressure in the second cylinder chamber 612 (and generation of negative pressure in the first cylinder chamber 611) is suppressed to a predetermined level or less.
Thereby, the piston 620 together with the spindle 300 moves upward in the cylinder 610 without receiving a large resistance.

Next, a case where the spindle 300 is lowered will be described with reference to FIG.
For example, when the spindle 300 moves downward due to the biasing force of the coil spring 440 and the weight of the spindle 300, the valve head 661 moves downward via the valve rod 671.
When the valve head 661 moves downward, the O-ring 662 is sandwiched between the valve head 661 and the reduced diameter portion 642, and the O-ring 662 is elastically deformed. Then, the main flow path 640 is closed by the valve head 661 and the O-ring 662. At this time, the first cylinder chamber 611 and the second cylinder chamber 612 are communicated with each other only by the micro flow path 650.
When the spindle 300 moves further downward, the valve head 661 moves downward through the valve rod 671, and the piston 620 faces downward by the engagement between the valve head 661 and the reduced diameter portion 642 through the O-ring 662. Be lowered.
When the piston 620 moves downward, a negative pressure is generated in the second cylinder chamber 612 (a positive pressure is generated in the first cylinder chamber 611).
Since the first cylinder chamber 611 and the second cylinder chamber 612 are communicated with each other through the micro flow path 650, gas (fluid) flows from the first cylinder chamber 611 into the second cylinder chamber 612 through the micro flow path 650. .
Here, since the flow rate through the micro flow path 650 is very small, the negative pressure in the second cylinder chamber 612 is buffered little by little. As a result, the lowering speed of the piston 620 is decelerated by the negative pressure in the second cylinder chamber 612. (Braking). And the descent speed of the spindle 300 is braked by braking the descent speed of the piston 620.

According to such 1st Embodiment, there can exist the following effects.
(1) When the spindle 300 moves downward, the main flow path 640 is closed by the valve head 661 (opening / closing means), and when the spindle 300 moves upward, the main flow path 640 is opened. Therefore, a braking effect can be obtained only when the spindle 300 moves downward, and no braking effect can be generated when the spindle 300 moves upward. That is, it is possible to prevent inconveniences such as the spindle 300 suddenly dropping downward and causing the probe 310 to collide with an object to be measured (not shown), while the spindle can be easily lifted upward.

(2) Since only the second cylinder chamber 612 needs to be substantially liquid-tightly partitioned by the piston 620, the first cylinder chamber 611 may be opened. Therefore, the process of sealing the first cylinder chamber 611 is not necessary as compared with the conventional case. As a result, the assembly process can be simplified and the production efficiency can be improved.

(3) Since the interlocking means 670 is constituted by the valve rod 671 that connects the spindle 300 and the valve head 661, a very simple configuration can be achieved.
When the valve head 661 seated on the reduced diameter portion 642 is pulled by the spindle 300 via the valve rod 671, the main flow path 640 is strongly blocked by the valve head 661. That is, that is, when the spindle 300 moves downward, the main flow path 640 is completely closed, and the airtightness of the second cylinder chamber 612 (excluding the fine flow path 650) is improved. As a result, the braking force is surely applied to the spindle 300 when the spindle 300 moves downward.

(4) The valve head 661 is moved downward integrally with the spindle 300 via the valve rod 671. At this time, the piston 620 is also lowered downward together with the spindle 300 by the engagement of the valve head 661 and the reduced diameter portion 642. Be drawn to. Therefore, it is not necessary to separately provide means for engaging the spindle 300 and the piston 620, so that the configuration can be simplified.

(5) The O-ring 662 is disposed in the reduced diameter portion 642, and the valve head 661 and the reduced diameter portion are elastically deformed when the O ring 662 is sandwiched between the valve head 661 and the reduced diameter portion 642. The gap with 642 is completely sealed. As a result, the airtightness of the second cylinder chamber 612 (excluding the micro flow path 650) is enhanced, and the braking effect is enhanced.

(6) On the lower end surface of the piston 620, a steep slope 644 is provided on a tapered surface 643 that increases in diameter downward from the through hole 641. Therefore, in a state where the spindle 300 is moved upward and the upper end surface of the spindle 300 is in contact with the lower end surface of the piston 620, the communication path that communicates the main channel 640 with the first cylinder chamber 611 is at least the steep slope 644 and the spindle 300. Secured during. Therefore, when the spindle 300 moves upward and pushes up the piston 620 with the spindle 300, the first cylinder chamber 611 and the second cylinder chamber 612 are always communicated with each other via the main flow path 640. As a result, when the spindle 300 moves upward, no braking force is applied, and the spindle 300 can be easily lifted.

(Modification 1)
Next, Modification 1 according to the measuring instrument of the present invention will be described with reference to FIG.
The basic configuration of Modification 1 is the same as that of the first embodiment, but is characterized in that a lifter portion is attached.
In FIG. 6, a lifter unit 900 is provided.
The lifter unit 900 includes a shaft body 910 and an outer cylinder portion 920.
The shaft body 910 is inserted into the cylinder 610 from the opening on the upper end side of the cylinder 610, the lower end (one end) is screwed to the valve head 661, and the upper end (the other end) protrudes to the outside of the cylinder 610.
The outer cylinder portion 920 is attached to the upper end (the other end) of the shaft body 910 and covers the cylinder 610 so as to cover the outside of the cylinder 610.
A cylinder cap 613 that closes the upper end of the cylinder 610 is not provided.

  In such a configuration, when the outer cylinder portion 920 of the lifter portion 900 is lifted upward, the valve head 661 is lifted upward together with the shaft body 910. Further, when the valve rod 671 is lifted together with the valve head 661, the spindle 300 is pulled up via the valve rod 671, and the piston 620 is pushed up by the upper end of the spindle 300.

  On the other hand, when the spindle is biased downward by the coil spring 440, the operation when the spindle 300 moves downward is the same as in the first embodiment.

According to such a structure, in addition to the effect of the said embodiment, there can exist the following effect.
(7) The lifter unit 900 can perform an operation of lifting the spindle 300 upward. For example, the spindle 300 can be lifted upward by the lifter unit 900 even when it is impossible to manually hold the lower end side of the spindle 300 when measuring the depth of the hole. Further, in providing the lifter unit 900, it is only necessary to remove the cylinder cap 613 from the configuration of the first embodiment and attach the lifter unit 900 to the valve head 661. Therefore, the attachment of the lifter unit 900 is very simple.

  The gap d between the outer cylinder part 920 and the cylinder 610 of the lifter part 900 is not particularly limited, but it is desirable to narrow the gap d between the outer cylinder part 920 and the cylinder 610. If the gap between the outer cylinder portion 920 and the cylinder 610 is small, the airtightness of the second cylinder chamber 612 is enhanced, and the braking effect of the spindle 300 is obtained by the second cylinder chamber 612.

It should be noted that the present invention is not limited to the above-described embodiment, and modifications, improvements, and the like within the scope that can achieve the object of the present invention are included in the present invention.
The cylinder 610 only needs to contain air, but the cylinder 610 may be filled with a fluid such as oil (for example, a viscous fluid).

The main flow path 640 and the fine flow path 650 may be formed anywhere.
Although the micro flow path 650 is a groove formed on the outer peripheral surface of the piston 620, a fine hole penetrating the piston 620 may be formed as the micro flow path 650.
Furthermore, a flow path (for example, a tube or the like) that connects the first cylinder chamber 611 and the second cylinder chamber 612 may be provided outside the cylinder 610. A check valve may be provided in the main channel.
Alternatively, when the valve head 661 is seated on the reduced diameter portion (valve seat) 642, the fine flow path 650 may be secured by leaving a gap for the fine flow path 650.
The area ratio between the fine channel 650 and the main channel 640 is not particularly limited, but it is exemplified that the main channel is made larger.

In attaching the lifter unit 900, for example, as shown in FIG. 7, the lifter unit 900 may be provided after the cylinder 610 is removed.
In addition, the shape of the lifter unit 900 is not particularly limited, and the lifter unit 900 may include only the shaft body 910 without the outer cylinder unit 920.

  The present invention can be used as a brake device for a spindle in a measuring instrument having a spindle such as a dial gauge.

The front view of 1st Embodiment of this invention. The figure which shows the internal structure of a measuring device in 1st Embodiment. The expanded sectional view which shows the structure of the upper-end part of a spindle and a braking means in 1st Embodiment. The figure which shows a mode that a spindle moves upwards in 1st Embodiment. The figure which shows a mode that a spindle falls in 1st Embodiment. The figure which shows a mode that the lifter part was attached in the modification 1 which concerns on the measuring device of this invention. The figure which shows a mode that a cylinder is removed and a lifter part is attached as a modification. The figure which shows the braking means of a spindle in the conventional measuring device.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 ... Dial gauge (measuring instrument), 200 ... Main body case, 210 ... Guide means, 211 ... Stem, 212 ... Bush, 213 ... Flange part, 214 ... Reduced diameter part, 215 ... Upper end side large diameter part, 216 ... Reduced diameter Part, 217 ... large diameter at the lower end side, 220 ... display part, 300 ... spindle, 310 ... measuring element, 320 ... female thread part, 400 ... biasing means, 410 ... guide rod, 420 ... guide piece, 440 ... coil spring, 500 ... Displacement detection means, 510 ... Index scale, 520 ... Mounting member, 530 ... Detection section, 600 ... Brake means (spindle braking device), 610 ... Cylinder, 611 ... First cylinder chamber, 612 ... Second cylinder chamber, 613 ... Cylinder cap, 616 ... First compartment, 617 ... Second compartment, 620 ... Piston, 621 ... Outer edge wall, 623 ... Cylinder cap 630 ... channel, 640 ... main channel, 641 ... through hole, 642 ... reduced diameter portion (valve seat), 642 ... through hole, 643 ... tapered surface, 644 ... steep slope, 650 ... fine channel, 651 ... groove 660 ... opening and closing means, 661 ... valve head (valve element), 662 ... O-ring, 670 ... interlocking means, 671 ... valve rod, 700 ... braking means, 710 ... movable member, 711 ... through hole, 712 ... cap, 731 ... Head, 740 ... Partition body, 741 ... Valve seat, 742 ... Through hole, 750 ... Ball body, 760 ... Cap, 761 ... Vent hole, 800 ... Dial gauge, 900 ... Lifter part, 910 ... Shaft body, 920 ... outer cylinder part, d ... gap, G ... gap.

Claims (2)

A main body case, a spindle that passes through the main body case and is provided so as to be movable in the axial direction, a cylindrical bush that is provided in the main body case and guides the spindle, and a display means for displaying a displacement amount of the spindle And a braking device for braking the moving speed of the spindle,
The spindle is to have a measuring element at one end is provided to be reciprocated in the axial direction in the insertion state into the bush,
The braking device is:
A cylinder having one end attached to the bush and a space in which the spindle reciprocates ;
A piston in the cylinder is movable together with the spindle in the other end side of the front Symbol spindle,
A first cylinder chamber defined by the piston on the bush side in the cylinder;
A second cylinder chamber which is partitioned at the opposite side to the manual said first cylinder chamber to said piston in said cylinder,
A main channel provided in fluid communication with the first cylinder chamber and the second cylinder chamber;
A microchannel provided in a manner that allows a relatively small amount of fluid to flow through the first cylinder chamber and the second cylinder chamber;
Opening and closing means for opening and closing the main flow path;
The opening / closing operation of the opening / closing means is interlocked with the movement of the spindle, and when the spindle moves to one end side, the opening / closing means closes the main flow path, and when the spindle moves to the other end side, e Bei and a interlocking means to open the main flow path opening and closing means,
The main flow path is constituted by a through hole formed through the piston,
The opening / closing means includes a valve seat provided in the main flow path, and a valve body that is slidably seated on the valve seat from the opposite side of the spindle with the valve seat interposed therebetween,
The interlocking means connects the spindle and the valve body in a state of being inserted through the through hole, and has a predetermined gap between the spindle and the piston in a state where the valve body is seated on the valve seat. Consists of a valve stem having a length to ensure
The measuring instrument, the measuring instrument, characterized in that one end provided with a lifter which is the other end from the other end side opening provided in the state of protrusion of said cylinder with mounted on the valve body. The measuring instrument according to claim 1, wherein
The opening / closing means is disposed on the valve seat, and is sandwiched between the valve seat and the valve body when the valve body is seated on the valve seat to seal between the valve seat and the valve body. A measuring instrument comprising an elastic member for stopping .

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