JP2011215845A - Pressure controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pressure controller allowing minute detection of a rotation position of a rotary output shaft by improving reliability of the rotation position detection while simplifying a configuration.SOLUTION: This pressure controller includes: a first rotation position detection sensor 27 detecting a rotation position of a first deceleration rotary shaft J3 transmitted with rotation of the rotary output shaft J2 in a state that the rotation is decelerated by a deceleration mechanism S2 for a reference; a second rotation position detection sensor 26 detecting a rotation position of the rotary output shaft J2 or a rotation position of a second deceleration rotary shaft transmitted with the rotation of the rotary output shaft J2 in a state that the rotation is decelerated by a deceleration mechanism for a low deceleration rate having a lower deceleration rate than the deceleration mechanism S2 for the reference; and a rotation position arithmetic means obtaining a rotation number of the rotary output shaft J2 based on detection information of the first rotation position detection sensor 27, obtaining a rotation angle of the rotary output shaft J2 based on detection information of the second rotation position detection sensor 26, and obtaining the rotation position of the rotary output shaft J2 from the obtained rotation number and rotation angle of the rotary output shaft J2.

Description

  The present invention is provided with a pressure control valve that adjusts the secondary pressure of the fluid flow path to a set pressure, and a pressure setting unit that changes and sets the set pressure of the pressure control valve, and the pressure setting unit includes a spring A pressure setting spring capable of changing and setting the set pressure by adjusting a load, a rotation output shaft capable of rotating a pressure adjusting screw capable of adjusting a spring load applied to the pressure setting spring, and a drive for rotating the rotation output shaft The pressure control apparatus provided with the part.

The pressure control device as described above is provided in a fluid flow path such as a gas conduit for supplying city gas to each consumer, and adjusts the secondary side pressure to a desired set pressure. When city gas is supplied to each consumer through the gas conduit, the set pressure is set according to the load so that the pressure of the city gas supplied to each consumer is within a desired range even if the load fluctuates. It is required to change settings.
Therefore, the pressure setting unit of the pressure control device adjusts the spring load applied to the pressure setting spring by driving the rotation output shaft to rotate by the drive unit, thereby adjusting the spring load applied to the pressure setting spring. It is configured to automatically change settings.

  For example, since the set pressure of the pressure control valve needs to be changed and set to a target set pressure according to a load or the like, a potentiometer has conventionally been provided as a rotation position detection sensor for detecting the rotation position of the rotation output shaft. A control unit that controls the operation of the drive unit is provided so that the rotational position detected by the potentiometer is a target rotational position corresponding to the target set pressure (see, for example, Patent Document 1).

JP 2001-134323 A

  The apparatus described in Patent Document 1 includes one potentiometer that can detect a rotational position of 360 degrees or more as a rotational position detection sensor. For example, for a 360 degree that can detect only 360 degrees, such as a resolver. Since the sensor is generally highly durable, the reliability of rotational position detection can be improved by using such a 360-degree sensor as the rotational position detection sensor.

  When a 360-degree sensor is used as the rotational position detection sensor, the rotational range detected by the sensor must be kept within 360 degrees. Therefore, the rotational output shaft is decelerated at a large deceleration rate to reduce the output. It is necessary to provide a speed reduction mechanism that transmits to the shaft. As described above, when the rotation of the rotation output shaft is decelerated at a large deceleration rate by the reduction mechanism, the resolution is greatly reduced, and the rotation position of the rotation output shaft cannot be detected in detail. For this reason, there is a possibility that the set pressure of the pressure control valve cannot be accurately changed to a desired set pressure such as a target set pressure.

  On the other hand, if the integration means capable of integrating the number of times that the rotation output shaft passes through the 360 degree rotation position is provided, the rotation speed of the rotation output shaft can be obtained from the integration count of the integration means. As a result, a 360-degree sensor can be used without a reduction mechanism as described above. However, in this case, since it is necessary for the integrating means to store the number of times of integration even at the time of a power failure or the like, a storage means for storing the number of times of integration must be separately provided, resulting in a complicated configuration. It will be.

  The present invention has been made paying attention to such a point, and its object is to improve the reliability of rotational position detection and to precisely detect the rotational position of the rotational output shaft while simplifying the configuration. It is in the point which provides the pressure control apparatus which can do.

In order to achieve this object, the characteristic configuration of the pressure control device according to the present invention includes a pressure control valve that adjusts the secondary side pressure of the fluid flow path to a set pressure, and changes and sets the set pressure of the pressure control valve. The pressure setting unit rotates a pressure setting spring capable of changing and setting the set pressure by adjusting a spring load and a pressure adjusting screw capable of adjusting a spring load applied to the pressure setting spring. In a pressure control device comprising a free rotation output shaft and a drive unit that rotationally drives the rotation output shaft,
A rotation position of the rotation output shaft, a rotation position of the rotation output shaft, or a rotation position of the rotation output shaft. A second rotational position detection sensor for detecting a rotational position of the second reduction rotational shaft transmitted by being reduced by a reduction speed rate reduction mechanism whose rotation rate is lower than that of the reference reduction mechanism; and the first rotational position detection The rotation speed of the rotation output shaft is obtained based on the detection information of the sensor, and the rotation angle of the rotation output shaft is obtained based on the detection information of the second rotation position detection sensor. Rotational position calculation means for obtaining the rotational position of the rotational output shaft from the rotational speed and the rotational angle.

According to this characteristic configuration, when the rotation output shaft makes one rotation, the rotation of the rotation output shaft can be decelerated by the reference reduction mechanism so that the first reduction rotation shaft rotates by a predetermined angle. The rotation position of the first reduction rotation shaft detected by the first rotation position detection sensor is obtained by reducing the rotation of the rotation output shaft by the reference reduction mechanism. Therefore, the reduction rate of the reference reduction mechanism is used. The rotation speed of the rotation output shaft can be obtained from the rotation position of the first reduction rotation shaft detected by the first rotation position detection sensor. Therefore, the rotation speed of the rotation output shaft can be obtained without providing an integration means capable of integrating the number of times that the rotation output shaft passes through the 360 degree rotation position.
Further, when the rotation position of the rotation output shaft is detected by the second rotation position detection sensor, the rotation angle of the rotation output shaft can be directly obtained from the rotation position of the rotation output shaft. When the rotational position of the second reduction rotational shaft is detected, the rotational output shaft is detected from the rotational position of the second reduction rotational shaft detected by the second rotational position detection sensor by using the deceleration rate of the speed reduction mechanism. Can be obtained.

  Thus, the rotational position calculation means can obtain the rotational speed of the rotational output shaft based on the detection information of the first rotational position detection sensor, and also the rotational output shaft based on the detection information of the second rotational position detection sensor. Therefore, the rotational position of the rotation output shaft can be determined finely and appropriately from the determined rotation speed and rotation angle of the rotation output shaft. Therefore, the control unit controls the operation of the drive unit so that the rotation position of the rotation output shaft obtained in this way by the rotation position calculation means becomes the target rotation position, thereby setting the set pressure of the pressure control valve to the target. The set pressure can be accurately changed.

  Since the rotation of the rotation output shaft is decelerated and transmitted by the reference deceleration mechanism, the rotation speed of the first deceleration rotation shaft is adjusted by adjusting the deceleration rate of the reference deceleration mechanism. It can be suppressed within 360 degrees, and as the first rotational position detection sensor, a generally highly durable sensor such as a sensor for 360 degrees can be used. Further, since the second rotational position detection sensor is used for obtaining the rotational angle of the rotational output shaft within 360 degrees, the second rotational position detection sensor is generally highly durable like the 360 degree sensor. A sensor can be used.

  And although the rotation of the rotation output shaft is decelerated, the second decelerating rotation shaft is decelerated by the reduction speed rate reduction mechanism having a lower deceleration rate than the reference deceleration mechanism, and the rotation of the rotation output shaft is transmitted. Therefore, not only when the rotation position of the rotation output shaft is detected as it is by the second rotation position detection sensor, but also when the rotation position of the second reduction rotation shaft is detected by the second rotation position detection sensor, the resolution is greatly reduced. The rotation angle of the rotation output shaft can be detected without any problem.

  From the above, it is not necessary to provide an integration means capable of integrating the number of times that the rotation output shaft passes through the 360-degree rotation position, the configuration can be simplified, and more durable than conventional potentiometers and the like. Using the first rotational position detection sensor and the second rotational position detection sensor, which are superior in terms of performance, improve the reliability of rotational position detection, finely detect the rotational position of the rotational output shaft, and set the pressure control valve A pressure control device capable of accurately changing and setting the pressure to a desired set pressure can be realized.

  A further characteristic configuration of the pressure control device according to the present invention is that the second rotational position detection sensor is attached to the rotational output shaft.

  According to this feature configuration, the rotation position of the rotation output shaft can be detected as it is with the second rotation position detection sensor attached to the rotation output shaft, and the rotation angle of the rotation output shaft can be detected without reducing the resolution. can do. In addition, the rotation angle of the rotation output shaft can be detected simply by attaching the second rotation position detection sensor to the rotation output shaft without providing a speed reduction mechanism that transmits the rotation of the rotation output shaft by decelerating. Therefore, it is possible to simplify the configuration for detecting the rotation angle of the rotation output shaft.

  In a further characteristic configuration of the pressure control device according to the present invention, the deceleration rate of the reference deceleration mechanism is such that the rotation range of the first reduction rotation shaft is within 360 degrees with respect to the rotation range of the rotation output shaft. The second rotational position detection sensor is attached to the rotational output shaft, and is configured to be able to detect the rotational angle of the rotational output shaft within 360 degrees.

  According to this feature configuration, the deceleration rate of the reference speed reduction mechanism is set so that the rotation range of the first reduction rotation shaft is within 360 degrees with respect to the rotation range of the rotation output shaft. The rotation range of the shaft can be reliably suppressed within 360 degrees, and a generally highly durable sensor such as a 360-degree sensor can be reliably applied as the first rotational position detection sensor. Since the second rotational position detection sensor is attached to the rotational output shaft, the rotational angle of the rotational output shaft can be detected simply by attaching the second rotational position detection sensor to the rotational output shaft, and the configuration is simple. Can be achieved. In addition, since the rotation angle of the rotation output shaft within 360 degrees may be detected as the second rotation position detection sensor, the second rotation position detection sensor is generally highly durable like the sensor for 360 degrees. The sensor can be reliably applied.

  A further characteristic configuration of the pressure control device according to the present invention is that the reference deceleration mechanism is constituted by a worm deceleration mechanism.

  According to this characteristic configuration, the reference speed reduction mechanism is configured by the worm speed reduction mechanism, so that the installation space for the reference speed reduction mechanism can be reduced, and the space can be saved as the apparatus.

Overall schematic diagram of pressure control device Schematic perspective view of pilot valve and pressure setting unit Schematic sectional view of pilot valve and pressure setting part Perspective view showing a part of the pressure setting section Perspective view showing a part of the pressure setting section Perspective view showing a part of the pressure setting section Sectional view showing part of the pressure setting section The figure which shows a state when switching a clutch mechanism to a transmission state The figure which shows the state in the middle of switching a clutch mechanism from the transmission state to the interruption | blocking state The figure which shows the state when the clutch mechanism is switched to the disengaged state

[First Embodiment]
An embodiment of a pressure control device according to the present invention will be described with reference to the drawings.
As shown in FIG. 1, the pressure control device includes a pressure control valve 2 that adjusts the secondary pressure of the fluid flow path 1 to a set pressure, and a pressure setting unit 3 that changes and sets the set pressure of the pressure control valve 2. And is configured. The pressure control device is provided with a pilot valve 4 that supplies a drive pressure to the pressure control valve 2 so that the secondary pressure of the fluid flow path 1 becomes a set pressure. By adjusting 4, the set pressure of the pressure control valve 2 is changed and set.

  Here, although illustration is omitted, for example, by branching the downstream side of the pressure control valve 2 of the fluid flow path 1 into a plurality of branch paths and connecting each of the plurality of branch paths to each consumer, It is configured to supply a fluid such as natural gas to a plurality of consumers. The secondary pressure on the downstream side of the pressure control valve 2 is adjusted to a set pressure lower than the primary pressure on the upstream side.

  The pressure control valve 2 includes a first diaphragm D1, and the internal space is partitioned into a first chamber H1 and a second chamber H2 by the first diaphragm D1. The pressure control valve 2 includes a first valve body B1 that opens and closes the fluid flow path 1, and the first valve body B1 is configured to be opened and closed by a first diaphragm D1. The first chamber H1 is provided with a first biasing spring G1 that biases the first diaphragm D1 toward the valve closing direction of the first valve body B1.

  The pilot valve 4 includes a second diaphragm D2 and a third diaphragm D3, and the internal spaces of the second diaphragm D2 and the third diaphragm D3 are the third chamber H3, the fourth chamber H4, and the fifth chamber H5. It is divided into. The third chamber H3 is communicatively connected to the secondary side of the fluid flow path 1 (downstream side from the pressure control valve 2) by the first secondary pressure introduction path 5, and the second secondary pressure The introduction path 6 is connected to the first chamber H1 of the pressure control valve 2 in communication. The fourth chamber H4 is connected to the primary side (upstream side of the pressure control valve 2) of the fluid flow path 1 by the primary pressure introduction path 7 and is connected to the pressure control valve 2 by the driving pressure introduction path 8. The two rooms H2 are connected in communication. Although not shown, the second diaphragm D2 and the third diaphragm D3 are connected by a connecting portion or the like, and are configured to be integrally displaceable up and down. A second urging spring G2 is disposed in the fifth chamber H5. The second urging spring G2 urges the third diaphragm D3 toward the fourth chamber H4, whereby the second diaphragm D2 is urged toward the third chamber H3 side.

  A second valve body B2 is provided at the distal end of the primary pressure introduction path 7, and the second valve body B2 is configured to be opened and closed by a second diaphragm D2. That is, when the second diaphragm D2 is displaced toward the third chamber H3, the second valve body B2 is opened, and the fluid on the primary side of the fluid flow path 1 passes through the primary pressure introduction path 7 to the fourth chamber H4. be introduced. On the other hand, the displacement of the second diaphragm D2 toward the fourth chamber H4 moves the second valve body B2 toward the valve closing side, thereby reducing the amount of primary fluid introduced into the fourth chamber H4.

The operation when the secondary pressure is adjusted to the set pressure will be described.
When the secondary pressure of the fluid flow path 1 falls below the set pressure, the third chamber H3 of the pilot valve 4 that is connected to the secondary side of the fluid flow path 1 through the first secondary pressure introduction path 5 And the second diaphragm D2 is displaced toward the third chamber H3 by the biasing force of the second biasing spring G2. As a result, the second valve body B2 of the pilot valve 4 is operated to the open side, and the primary side pressure of the fluid flow path 1 is introduced into the fourth chamber H4 through the primary side pressure introduction path 7, and the pressure in the fourth chamber H4 Rises. Then, the increased pressure in the fourth chamber H4 is supplied as the driving pressure to the second chamber H2 of the pressure control valve 2 through the driving pressure introduction path 8, and the pressure in the second chamber H2 also increases, and the first chamber H1. The first diaphragm D1 is displaced toward the first chamber H1 due to the pressure difference between the first chamber H2 and the second chamber H2. Therefore, the first valve body B1 of the pressure control valve 2 is operated to the open side, and the secondary side pressure of the fluid flow path 1 is increased to adjust the secondary side pressure to the set pressure.

  On the other hand, when the secondary side pressure rises higher than the set pressure, the pressure in the third chamber H3 of the pilot valve 4 rises, and the second diaphragm D2 resists the biasing force of the second biasing spring G2, and the second diaphragm D2 moves into the fourth chamber H4. Displace to the side. As a result, the second valve body B2 of the pilot valve 4 is operated to the closed side, and there is no fluid supply source to the fourth chamber H4. Then, the fluid in the second chamber H2 is discharged to the secondary side via the orifice U, the second secondary pressure introduction path 6, the third chamber H3, and the first secondary pressure introduction path 5, and the second chamber H2 is discharged to the secondary side. The pressure in the two chambers H2 decreases, and the first diaphragm D1 is displaced toward the second chamber H2 due to the pressure difference between the first chamber H1 and the second chamber H2. Accordingly, the first valve body B1 of the pressure control valve 2 is operated to the closed side, and the secondary side pressure of the fluid flow path 1 is reduced to adjust the secondary side pressure to the set pressure.

  The set pressure of the pressure control valve 2 is not always a constant pressure, but the set pressure is adjusted to the target set pressure that is changed according to the load or the like by providing the pressure setting unit 3. For example, in the fluid flow path 1, the load becomes large during a time period in which much demand is expected, so the pressure setting unit 3 adjusts the set pressure to a high target set pressure, and the load is set in other time periods. Therefore, the set pressure is adjusted to the low target set pressure.

  As described above, in the pilot valve 4, the driving pressure corresponding to the magnitude relationship between the urging force of the second urging spring G <b> 2 and the secondary side pressure supplied through the first secondary side pressure introduction path 5 is the pilot valve 4. To the pressure control valve 2, and the secondary pressure is adjusted to the set pressure by the pressure control valve 2. Therefore, the pressure setting unit 3 changes and sets the set pressure of the pressure control valve 2, but the second biasing spring G2 is configured as a pressure setting spring 9 that sets the set pressure of the pressure control valve 2. By adjusting the spring load of the pressure setting spring 9 (second biasing spring G2), the set pressure of the pressure control valve 2 can be changed and set.

  As shown in FIGS. 2 and 3, the pressure setting unit 3 rotates the pressure adjusting screw 10 that can adjust the spring load applied to the pressure setting spring 9 in addition to the pressure setting spring 9 described above. And a control unit (not shown) for changing and setting the set pressure by controlling the operation of the drive unit 11. The pressure setting unit 3 is provided with a pressure setting spring 9 and a pressure adjusting screw 10 inside a pilot valve forming unit 14 that forms the pilot valve 4, and a drive unit 11 and a control unit ( The pilot valve forming portion 14 and the storage case 15 are connected to each other so that the spring load of the pressure setting spring 9 can be adjusted.

  As shown in FIG. 3, the pressure setting spring 9 of the pressure setting unit 3 is disposed in the fifth chamber H5 of the pilot valve 4, its upper end is in contact with the third diaphragm D3, and its lower end is It is in contact with the spring receiver 13. And in the lower part which forms the 5th chamber H5 among pilot valve formation parts 14, the 1st screw part N1 is formed in the inner wall part, and spring receiving part 13 was formed in the outer peripheral part. The second screw portion N2 and the first screw portion N1 formed on the pilot valve forming portion 14 are provided in a screwed state. In the fifth chamber H5 of the pilot valve 4, a first rotating shaft J1 is disposed in a state of penetrating the spring receiving portion 13 in the vertical direction. 1 rotation axis J1 and the spring receiving part 13 rotate integrally, and the spring receiving part 13 is comprised so that it may move up and down. The spring receiving portion 13 is moved up and down by integral rotation of the first rotating shaft J1 and the spring receiving portion 13, and the spring load applied to the pressure setting spring 9 is adjustable. Thereby, the first rotating shaft J1 and the spring receiving portion 13 are configured as the pressure adjusting screw 10. Further, the first rotating shaft J1 is disposed in a state where the lower end portion having a small diameter penetrates the pilot valve forming portion 14 and protrudes downward.

  On the other hand, as shown in FIG. 3, the drive unit 11 and the control unit of the pressure setting unit 3 are disposed inside the storage case 15 together with the second rotation shaft J <b> 2 that is rotationally driven by the drive unit 11. The second rotating shaft J2 is disposed in a state where the upper end side portion protrudes upward from the storage case 15. And the lower end side part of the 1st rotating shaft J1 and the upper end side part of the 2nd rotating shaft J2 are connected by the rotating shaft connection part 16, and the 1st rotating shaft J1 and the 2nd rotating shaft J2 are integrated. It is configured to be freely rotatable. As a result, the second rotating shaft J2 is rotationally driven by the drive unit 11, whereby the second rotating shaft J2 and the first rotating shaft J1 are integrally rotated to move the spring receiving portion 13 up and down, and the pressure setting spring. Adjust the spring load applied to 9.

  As for the connection between the pilot valve forming portion 14 and the storage case 15, as shown in FIGS. 2 and 3, in addition to the rotating shaft connecting portion 16 that connects the first rotating shaft J1 and the second rotating shaft J2, the pilot valve forming portion 14 and the storage case 15 are connected. A connecting member 22 that connects the plate-like first connecting portion K1 fixed to the valve forming portion 14 and the plate-like second connecting portion K2 fixed to the upper end side portion of the storage case 15 is provided. The connecting member 22 is formed in a columnar shape, and a plurality (four in this embodiment) are provided, and the first connecting portion K1 and the second connecting portion K2 are connected at a plurality of locations. In order to electrically insulate the pilot valve 4 and the storage case 15, for example, an insulating member is interposed between the second connecting portion K2 and the connecting member 22 is connected to the second connecting portion K2. The connecting member 22 itself is made of an insulating material.

As shown in FIG. 4, the drive unit 11 includes an electric drive motor 23 and a drive speed reduction mechanism S <b> 1 that rotates the second rotary shaft J <b> 2 by the rotational driving force of the drive motor 23. The drive reduction mechanism S1 includes a drive gear 24 fixed to the output shaft of the drive motor 23, and a first gear F1 externally fixed to the second rotating shaft J2. The first gear F1 is a drive gear. The drive gear 24 and the first gear F1 are engaged with each other. As a result, the rotation of the drive motor 23 is decelerated by the drive speed reduction mechanism S1 and then transmitted to the second rotation axis J2. The drive motor 23 rotates the second rotation axis J2.
As described above, when the second rotating shaft J2 is rotationally driven by the drive motor 23, the second rotating shaft J2 and the first rotating shaft J1 are integrally rotated to move the spring receiving portion 13 up and down as described above. The set pressure of the pressure control valve 2 can be changed and set by adjusting the spring load applied to the pressure setting spring 9 (see FIG. 3).

  The control unit of the pressure setting unit 3 monitors the rotation position of the second rotation axis J2 (corresponding to the rotation output shaft), and the rotation position of the second rotation axis J2 corresponds to the target set pressure. By controlling the operation of the drive motor 23 so as to be in the rotational position, the set pressure of the pressure control valve 2 is changed to the target set pressure. Therefore, as shown in FIGS. 4 and 5, the pressure setting unit 3 is provided with a rotation position detection sensor 25 that detects the rotation position of the second rotation axis J <b> 2, and the control unit detects the rotation position detection sensor 25. Based on the 25 detection information, the rotation position of the second rotation axis J2 is monitored.

(Rotation position detection sensor)
In the pressure control device according to the present invention, as shown in FIG. 5, as the rotational position detection sensor 25, a rotational angle detection sensor 26 (second rotational position) for detecting the rotational angle of the second rotational axis J <b> 2 within 360 degrees. Two rotation position detection sensors, which correspond to a detection sensor) and a rotation speed detection sensor 27 (corresponding to a first rotation position detection sensor) for detecting the rotation speed of the second rotation shaft J2. .

  The rotation angle detection sensor 26 is disposed at the lower end portion of the second rotation axis J2 (corresponding to the rotation output axis), and is directly connected to the second rotation axis J2 that is a rotation angle detection target within 360 degrees. It is attached. Therefore, the rotation angle detection sensor 26 is configured to be able to detect the rotation position of the second rotation axis J2 within 360 degrees as the rotation angle of the second rotation axis J2 within 360 degrees.

  The rotation speed detection sensor 27 transmits a third rotation shaft J3 (corresponding to the first reduction rotation shaft) transmitted by the reference deceleration mechanism S2 with the rotation of the second rotation shaft J2 (corresponding to the rotation output shaft) being reduced. It is comprised so that the rotation position of may be detected. The third rotation axis J3 is arranged in a state extending in a direction orthogonal to the second rotation axis J2. The reference speed reduction mechanism S2 is in a state in which the second gear F2 formed on the outer peripheral portion of the second rotating shaft J2 and the third gear F3 fixed to the third rotating shaft J3 mesh with each other below the first gear F1. It is comprised with the worm reduction mechanism provided in. Here, the second rotation axis J2 has a rotation range from the lower limit target rotation position corresponding to the minimum value of the target set pressure to the upper limit target rotation position corresponding to the maximum value of the target set pressure. The deceleration rate is set so that the rotation range of the third rotation axis J3 is within 360 degrees with respect to the rotation range of the second rotation axis J2.

  The control unit of the pressure setting unit 3 obtains the rotation position of the second rotation axis J2 within 360 degrees detected by the rotation angle detection sensor 26 as the rotation angle P1 of the second rotation axis J2 within 360 degrees. Further, the control unit of the pressure setting unit 3 obtains the rotation speed P2 of the second rotation shaft J2 from the rotation position of the third rotation shaft J3 detected by the rotation speed detection sensor 27 and the deceleration rate of the reference deceleration mechanism S2. Yes. Then, the control unit of the pressure setting unit 3 performs the second rotation using the following [Equation 1] from the obtained rotation angle P1 of the second rotation axis J2 and the obtained rotation speed P2 of the second rotation axis J2. The rotational position P3 of the axis J2 is obtained. Thereby, a control part is equivalent to a rotation position calculating means.

[Equation 1]
P3 = P1 + 360 × P2
Here, P1 is the rotation angle of the second rotation axis J2, P2 is the rotation speed of the second rotation axis J2, and P3 is the rotation position of the second rotation axis J2.

  The control unit of the pressure setting unit 3 determines the magnitude relationship between the rotation position of the second rotation axis J2 and the set pressure of the pressure control valve 2 (for example, the pressure position of the pressure control valve 2 increases as the rotation position of the second rotation axis J2 increases). The relationship between the set pressure and the like is stored in advance, and the rotation of the second rotary shaft J2 is performed using the stored magnitude relationship so that the set pressure of the pressure control valve 2 becomes the target set pressure. The operation of the drive motor 23 is controlled to adjust the position. That is, the control unit 12 obtains the target rotational position of the second rotational axis J2 corresponding to the target set pressure from the stored magnitude relationship, and the rotational position of the second rotational axis J2 obtained in the above [Equation 1] is obtained. The operation of the drive motor 23 is controlled so as to reach the target rotation position.

(Clutch mechanism)
As described above, the controller can automatically change and set the set pressure of the pressure control valve 2 to the target set pressure by controlling the operation of the drive motor 23. For example, the pressure control can be performed manually by the operator. The set pressure of the valve 2 can be changed and set.
That is, as shown in FIGS. 6 to 10, the pressure setting unit 3 adjusts the rotational driving force of the driving unit 11 by engaging the first gear F <b> 1 on the pressure adjusting screw 10 side and the driving gear 24 on the driving unit 11 side. A clutch mechanism that can be switched between a transmission state transmitted to the screw 10 and a cut-off state that releases the meshing of the first gear F1 and the drive gear 24 and blocks the transmission of the rotational driving force of the drive unit 11 to the pressure adjusting screw 10. 30. Here, FIG. 6 shows an exploded perspective view when each member of the clutch mechanism 30 is disassembled, and FIG. 7 shows a cross-sectional view of the clutch mechanism 30. 8 shows a state in which the clutch mechanism 30 is switched to the transmission state, FIG. 9 shows a state in the middle of switching the clutch mechanism 30 from the transmission state to the cutoff state, and FIG. The state which has switched the mechanism 30 to the interruption | blocking state is shown.

  As described above, by providing the clutch mechanism 30, when the set pressure of the pressure control valve 2 is changed to the target set pressure, the operation of the drive motor 23 is controlled by the control unit, and the first rotation shaft J1 and the second rotation are controlled. In the case of automatically rotating the shaft J2, the clutch mechanism 30 is switched to the transmission state, and the first rotating shaft J1 and the first rotating shaft J1 and the second rotating shaft 16 are manually operated by the manual operation member 20 (see FIG. 3) provided in the rotating shaft connecting portion 16. When the two-rotation shaft J2 is rotated, the clutch mechanism 30 is switched to the disconnected state.

  The clutch mechanism 30 is manually operated so as to be swingable between a first position (see FIG. 8) and a second position (see FIG. 10) around the vertical axis along the axial direction of the first gear F1 and the drive gear 24. The drive gear 24 is arranged in the radial direction at an engagement position (see FIG. 8) where the operation lever 31, the first gear F1 and the drive gear 24 are engaged, and an engagement release position where the engagement between the first gear F1 and the drive gear 24 is released. The first plate-like body Q1 that is freely movable, and the manual operation lever 31 so as to move the drive gear 24 to the meshing position and the meshing release position by swinging the manual operation lever 31 between the first position and the second position. And a linkage mechanism 32 that links the operation of the drive gear 24 with each other. In this way, the clutch mechanism 30 meshes with the meshing position by moving the first gear F1 as a stationary gear and the driving gear 24 as a moving gear and moving the driving gear 24 as a moving gear in the radial direction thereof. The drive gear 24 is moved to the release position so that it can be switched between a transmission state and a cutoff state.

  The manual operation lever 31 is fitted into a rotating body 46 whose one end portion protrudes upward from the upper surface portion of the cylindrical support portion 34, and has a first position around the vertical axis with the one end portion as a fulcrum (see FIG. 8) and a second position (see FIG. 10). As shown in FIGS. 6 and 7, a disc-shaped second plate-like body Q2 is fitted on the outer periphery of the support portion 34, and the upper surface of the second plate-like body Q2 is on the upper side. An extending standing wall portion 35 is provided. And this standing wall part 35 is formed in circular arc shape by planar view so that it may extend along the external shape of the 2nd plate-shaped body Q2, and the 1st recessed part formed in the lower surface part of the manual operation lever 31 The standing wall portion 35 is fitted to R1. Thereby, the manual operation lever 31 is configured to be swingable between the first position and the second position while being guided by the rising wall 35 by fitting the first recess R1 and the rising wall 35. ing.

  The first plate-like body Q1 is composed of a convex plate-like body whose central portion protrudes from both end portions in plan view, and is provided so as to be swingable around the vertical axis with its one end portion as a fulcrum. It has been. A drive motor 23 is attached to the lower side of the central portion of the first plate-like body Q1. The output shaft extending upward from the drive motor 23 penetrates the first plate Q1 in the vertical direction, and the drive gear 24 provided on the output shaft is more than the first plate Q1. It is arranged on the upper side. As a result, the first plate-like body Q1, the drive motor 23, and the drive gear 24 can move integrally as a result of the first plate-like body Q1 swinging around the vertical axis with one end portion as a fulcrum. It is configured.

  The linkage mechanism 32 includes an engagement pin 41 that is movable integrally with the manual operation lever 31, and an elongated engagement groove 42 formed at the other end portion of the first plate-like body Q1. By engaging the engagement pin 41 with the engagement groove 42, the operation of the manual operation lever 31 and the operation of the drive gear 24 are linked. Inside the support portion 34 that supports the manual operation lever 31, a rotating body 46 that is rotatably supported around the vertical axis is disposed. The rotating body 46 is manually operated by a fastener T such as a bolt. Fastened to the operation lever 31. Therefore, when the manual operation lever 31 is swung, the rotating body 46 is configured to rotate along with the swing operation. An engaging pin 41 is provided at the lower end of the rotating body 46 so as to extend downward, and the engaging pin 41 is disposed at a position eccentric from the rotational axis of the rotating body 46. Thus, when the manual operation lever 31 is swung around the vertical axis, the rotating body 46 rotates with the swinging operation, and the engagement pin 41 rotates around the rotation axis of the rotating body 46. . Since the engaging pin 41 rotates while being engaged with the engaging groove 42, the engaging pin 41 moves while pressing the side wall portion of the engaging groove 42. The body Q1 is swung around the vertical axis. In this way, the linkage mechanism 32 links the operation of the manual operation lever 31 and the operation of the first plate Q1, and the manual operation lever 31 swings to the first position as shown in FIG. When operated, the first plate Q1 is swung so that the drive gear 24 moves to the meshing position, and when the manual operation lever 31 is swung to the second position as shown in FIG. The first plate member Q1 is swung so that 24 moves to the mesh release position.

  The meshing position (see FIG. 8) and the meshing release position (see FIG. 10) are set as positions that are spaced apart in the radial direction of the first gear F1. Then, the drive gear 24 is moved to the mesh release position by swinging the first plate-like body Q1 having the drive gear 24 in the meshing position in the radial direction away from the first gear F1. Thereby, the drive gear 24 can be moved to the meshing release position while preventing the sliding between the drive gear 24 and the first gear F1 and reducing the sliding resistance. As a result, it is possible to reduce the operating force required when swinging the manual operation lever 31 from the first position to the second position, and to improve the operability. Further, the drive gear 24 is moved to the meshing position by swinging the first plate-like body Q1 having the drive gear 24 in the meshing release position so as to approach the first gear F1 in the radial direction. Thereby, even if it does not have a guide means etc., the drive gear 24 is appropriately bitten with respect to the first gear F1 by utilizing the mountain-shaped tooth shape of both the drive gear 24 and the first gear F1. Therefore, the configuration can be simplified.

  A first elastic body C1 such as a compression spring for returning and energizing the drive gear 24 is provided on the meshing position side of the meshing position and the meshing release position. The first elastic body C1 has one end connected to the other end of the first plate Q1 opposite to the one end serving as the swing fulcrum of the first plate Q1, and the other end of the first plate Q1. The drive gear 24 is urged to return to the meshing position side by urging the portion toward the first gear F1 in the radial direction.

(Lock mechanism)
In addition, a lock mechanism 33 that holds the drive gear 24 at each of the meshing position and the meshing release position is provided. The lock mechanism 33 is configured to hold the driving gear 24 in the meshing position and the meshing release position by holding the manual operation lever 31 in the first position and the second position, respectively.

  Hereinafter, the configuration of the lock mechanism 33 will be described with reference to FIGS. 7A shows a state where the lock mechanism 33 holds the position of the manual operation lever 31. FIG. 7B shows a state where the lock mechanism 33 holds the position of the manual operation lever 31. Indicates the state in which is released. FIG. 8 shows a state where the lock mechanism 33 holds the position of the manual operation lever 31 at the first position (that is, a state where the drive gear 24 is held at the meshing position). 9 shows a state in which the lock mechanism 33 releases the position holding of the manual operation lever 31 in the first position (that is, a state in which the position holding of the drive gear 24 to the meshing position is released). FIG. The state where the mechanism 33 holds the manual operation lever 31 at the second position (that is, the state where the drive gear 24 is held at the mesh release position) is shown.

  As shown in FIG. 7, the manual operation lever 31 includes a columnar exit / retreat button 36 that can be retracted along the horizontal direction on the side protruding to the outside of the manual operation lever 31 and on the side retracting inward. Is provided. A second elastic body C <b> 2 such as a compression spring that presses and urges the retracting button 36 outward from the manual operation lever 31 is provided inside the manual operation lever 31. The exit / retreat button 36 is provided with a second recess R2 similarly to the first recess R1 provided on the manual operation lever 31, and the upright wall 35 is fitted into the second recess R2. Further, as shown in FIGS. 8 to 10, an arc-shaped protrusion 37 protruding in the horizontal direction is formed on the side wall portion of the second recess R <b> 2 of the exit / exit button 36. An arc-shaped recessed groove 38 that is recessed in the horizontal direction is formed. As shown in FIGS. 8 and 10, a protrusion 37 is configured to be freely fitted into the recessed groove 38. The recessed groove 38 is formed at a position corresponding to the first position of the manual operation lever 31 and a position corresponding to the second position of the manual operation lever 31. As a result, the lock mechanism 33 includes the protrusion 37 and the recessed groove 38, and the protrusion 37 fits into the recessed groove 38, so that the manual operation lever 31 can be moved in each of the first position and the second position. Hold position.

  Thereby, when the manual operation lever 31 is located at the first position, the projection 37 is fitted into the recessed groove portion 38, the manual operation lever 31 is held at the first position, and the manual operation lever 31 is moved to the second position. Even when positioned, the protrusion 37 is fitted into the recessed groove 38, and the manual operation lever 31 is held in the second position. Therefore, when swinging the manual operation lever 31 located at the first position or the second position, first, the operator pushes the retract button 36 toward the side where the manual operation lever 31 is retracted. After the fitting of the projection 37 and the recessed groove 38 is released to release the position of the manual operation lever 31, the manual operation lever 31 is swung.

  As described above, the clutch mechanism 30 swings the manual operation lever 31 to the first position and the second position to move the drive gear 24 to the meshing position and the meshing release position, so that the transmission state and the cutoff state are established. It is configured to be switchable. Here, the change setting of the set pressure of the pressure control valve 2 is normally performed automatically by the control unit controlling the operation of the drive motor 23, so that the clutch mechanism 30 is in the transmission state as shown in FIG. It has been switched to. When the set pressure of the pressure control valve 2 is changed and set by a manual operation by the operator, the operator pushes the retract button 36 toward the side of retraction inside the manual operation lever 31 as shown in FIG. Thus, after the position holding of the manual operation lever 31 is released, the manual operation lever 31 is swung to switch the clutch mechanism 30 to the disconnected state as shown in FIG.

  Then, in order to change and set the set pressure of the pressure control valve 2 by manual operation by the operator, as shown in FIG. 3, the rotary shaft connecting portion 16 is provided with a manual operation member 20. When the manual operation member 20 is rotated by manual operation, the first rotation axis J1 and the second rotation axis J2 are rotated in accordance with the rotation operation. Thus, after the clutch mechanism 30 is switched to the disconnected state, the operator rotates the manual operation member 20 to rotate the first rotating shaft J1 and the second rotating shaft J2 to move the spring receiving portion 13 up and down. The set pressure of the pressure control valve 2 is changed and set by adjusting the spring load applied to the pressure setting spring 9. In this way, the pressure setting unit 3 is configured to be able to change and set the set pressure of the pressure control valve 2 by an operator's manual operation.

  Here, in the pressure control device according to the present invention, as described above, when the control unit automatically changes the set pressure of the pressure control valve 2 by controlling the operation of the drive motor 23, the pressure setting unit 3 obtains the rotation angle P1 of the second rotation axis J2 within 360 degrees from the detection information of the rotation angle detection sensor 26, and calculates the rotation speed P2 of the second rotation axis J2 from the detection information of the rotation speed detection sensor 27. The rotation position P3 of the second rotation axis J2 is obtained from the obtained rotation angle and rotation number of the second rotation axis J2 using the above [Equation 1]. Therefore, even when the set pressure of the pressure control valve 2 is changed and set, the rotational position of the second rotary shaft J2 can be obtained.

  That is, when the set pressure of the pressure control valve 2 is changed and set by the manual operation of the operator, the pressure control is performed by rotating the manual operation member 20 by the operator after switching the clutch mechanism 30 to the disconnected state. Change and set the set pressure of valve 2. At this time, since the second rotation axis J2 is rotated by the rotation operation of the manual operation member 20, the third rotation axis J3 is also rotated by the reference speed reduction mechanism S2 along with the rotation of the second rotation axis J2. Thereby, the control unit of the pressure setting unit 3 can obtain the rotation angle P1 of the second rotation axis J2 within 360 degrees from the information of the rotation angle detection sensor 26, and the detection information of the rotation number detection sensor 27 The rotation speed P2 of the two rotation axis J2 can be obtained. Therefore, the control unit of the pressure control unit 3 obtains the rotational position P3 of the second rotational axis J2 from the obtained rotational angle and rotational speed of the second rotational axis J2 using the above [Equation 1]. Can do. Therefore, for example, the control unit of the pressure control unit 3 displays the obtained rotation position of the second rotation axis J2 on the display unit or the like, so that the operator can recognize the rotation position of the second rotation axis J2 while The set pressure of the control valve 2 can be changed and set, and the operator can easily change and set the set pressure of the pressure control valve 2 to a desired set pressure.

[Second Embodiment]
The second embodiment is another embodiment of the configuration of the second rotational position detection sensor in the first embodiment. Hereinafter, the configuration of the second rotational position detection sensor will be described, but the other configuration is the same as that of the first embodiment, and thus the description thereof is omitted.

In the first embodiment, the rotation angle detection sensor 25 as the second rotation position detection sensor is attached to the second rotation axis J2 (corresponding to the output rotation axis), and the rotation angle of the second rotation axis J2 is detected as the rotation angle. The sensor 25 detects it as it is.
In the second embodiment, although not shown, a reduction speed rate reduction mechanism is provided separately from the reference reduction mechanism S2 to reduce the rotation of the second rotation shaft J2 and transmit it to the second reduction rotation shaft. The deceleration rate of the deceleration mechanism for low deceleration rate is set to a deceleration rate lower than that of the reference deceleration mechanism S2. Then, a rotation position detection sensor as a second rotation position detection sensor is attached to the second reduction rotation axis, and the rotation position of the second reduction rotation axis is detected by the second rotation position detection sensor.

  As a result, the rotational position of the second reduction rotation shaft detected by the second rotation position detection sensor is the rotation speed of the second rotation shaft J2 (corresponding to the rotation output shaft) reduced by the reduction speed rate reduction mechanism. Therefore, the control unit of the pressure setting unit uses the deceleration rate of the reduction mechanism for the reduced speed rate to rotate the second rotation axis J2 from the rotation position of the second deceleration rotation axis detected by the second rotation position detection sensor. The angle can be determined. Thus, although the rotation of the second rotating shaft J2 is decelerated, the second decelerating rotating shaft is decelerated by the decelerating speed reduction mechanism having a lower decelerating rate than the reference decelerating mechanism, and the second rotating shaft J2 Since the rotation is transmitted, even if the rotation angle of the second rotation axis J2 is obtained by detecting the rotation position of the second reduction rotation axis by the second rotation position detection sensor, the resolution is not greatly reduced. The rotation angle of the two rotation axis J2 can be detected.

In addition, as described above, a reduction speed rate reduction mechanism can be provided separately from the reference speed reduction mechanism S2 in providing the reduction speed rate reduction mechanism, but instead of this configuration, a part of the reference speed reduction mechanism S2 is provided. However, it can also serve as a reduction mechanism for a reduced speed rate.
Although not shown in the drawings, when the rotation of the second rotation shaft J2 (corresponding to the rotation output shaft) is transmitted to the third rotation shaft J3 (corresponding to the first reduction rotation shaft), the transmission of the rotation is relayed. A first reference speed reduction mechanism (for example, a parallel shaft gear) that decelerates the rotation of the second rotation shaft J2 (corresponding to the rotation output shaft) and transmits it to the relay rotation shaft. A reduction mechanism) and a second reference reduction mechanism (for example, a worm reduction mechanism) that reduces the rotation of the relay rotation shaft and transmits it to the third rotation shaft J3 (corresponding to the first reduction rotation shaft). Then, the first rotational position detection sensor is attached to the third rotational axis J3 to detect the rotational position of the third rotational axis J3, the second rotational position detection sensor is attached to the relay rotational axis, and the relay rotational axis of the relay rotational axis is detected. Detect the rotational position. As described above, when the reference deceleration mechanism S2 includes the first reference deceleration mechanism and the second reference deceleration mechanism, the first reference deceleration mechanism that is a part of the reference deceleration mechanism S2 reduces the reduction rate reduction. The mechanism can also be used.

[Another embodiment]
(1) In the first and second embodiments, the reference speed reduction mechanism S2 is configured by a worm speed reduction mechanism, but the speed reduction mechanism configured by the reference speed reduction mechanism S2 is appropriately changed. Is possible.

  The present invention is provided with a pressure control valve that adjusts the secondary pressure of the fluid flow path to a set pressure, and a pressure setting unit that changes and sets the set pressure of the pressure control valve, and the pressure setting unit includes a spring A pressure setting spring capable of changing and setting the set pressure by adjusting a load, a rotation output shaft capable of rotating a pressure adjusting screw capable of adjusting a spring load applied to the pressure setting spring, and a drive for rotating the rotation output shaft And improving the reliability of rotational position detection while simplifying the configuration, and can be applied to various pressure control devices capable of finely detecting the rotational position of the rotational output shaft.

DESCRIPTION OF SYMBOLS 1 Fluid flow path 2 Pressure control valve 3 Pressure setting part 9 Pressure setting spring 10 Pressure adjusting screw 11 Drive part 26 2nd rotation position detection sensor (rotation angle detection sensor)
27 First rotational position detection sensor (rotational speed detection sensor)
J2 Rotation output shaft (second rotation shaft)
J3 First reduction rotation axis (third rotation axis)
S2 Reference deceleration mechanism

Claims (4)

A pressure control valve for adjusting the secondary pressure of the fluid flow path to a set pressure and a pressure setting unit for changing and setting the set pressure of the pressure control valve are provided, and the pressure setting unit is configured by adjusting a spring load. A pressure setting spring capable of changing and setting the set pressure; a rotation output shaft capable of rotating a pressure adjusting screw capable of adjusting a spring load applied to the pressure setting spring; and a drive unit for rotating the rotation output shaft. A pressure control device comprising:
A rotation position of the rotation output shaft, a rotation position of the rotation output shaft, or a rotation position of the rotation output shaft. A second rotational position detection sensor for detecting a rotational position of the second reduction rotational shaft transmitted by being reduced by a reduction speed rate reduction mechanism whose rotation rate is lower than that of the reference reduction mechanism; and the first rotational position detection The rotation speed of the rotation output shaft is obtained based on the detection information of the sensor, and the rotation angle of the rotation output shaft is obtained based on the detection information of the second rotation position detection sensor. A pressure control device comprising: a rotational position calculating means for obtaining a rotational position of the rotational output shaft from a rotational speed and a rotational angle.   The pressure control device according to claim 1, wherein the second rotation position detection sensor is attached to the rotation output shaft.   The deceleration rate of the reference deceleration mechanism is set so that the rotation range of the first reduction rotation shaft is within 360 degrees with respect to the rotation range of the rotation output shaft, and the second rotation position detection sensor is The pressure control device according to claim 1, wherein the pressure control device is attached to the rotation output shaft so as to be capable of detecting a rotation angle of the rotation output shaft within 360 degrees.   The pressure control device according to claim 1, wherein the reference speed reduction mechanism is configured by a worm speed reduction mechanism.

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