JP2006262699A - Fluid control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To realize the fluid control valve, using an electric motor having an output of different torque. <P>SOLUTION: The electric motor 28 is constituted of a stator 14, having a coil 15, a rotor 16 rotated by magnetization due to current carrying in the coil 15, the rotary shaft 18 of the rotor 16, a first bearing 19 provided to one side of the rotary shaft 18, and a second bearing 22, provided to the other side of the rotary shaft with the material different from that of the first bearing 19; and the rotary shaft 18 is provided with conversion means 34, 42 for converting the rotational motion into rectilinear motion, and by constituting a valve body 33 via the conversion means 34, 42, uses the electric motor 28 as the drive means for an opening/closing valve, so that the output can be selectively utilized as the opening force of the valve element 33. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a fluid cutoff valve that controls opening and closing of a flow of a gas fluid flowing in a flow path.

Conventionally, this type of fluid control valve has been disclosed in Japanese Patent Application Laid-Open No. 9-60752. The configuration will be described below with reference to the drawings. In FIG. 7, reference numeral 1 denotes a valve housing, and a main flow path 2 through which a gas fluid flows is configured in the valve housing 1, and a valve seat 3 is provided in a part thereof. Reference numeral 4 denotes a main flow path opening / closing means, which comprises a conversion means 7 for converting the rotational movement of the rotor 6 of the motor 5 as a drive unit into a vertical movement and a main flow path opening / closing valve 8 connected to the conversion means 7 and moving up and down. Has been. The converting means 7 converts the rotational movement of the rotor 6 into vertical movement of the main flow path opening / closing valve 8 via a screw mechanism (not shown). Reference numeral 9 denotes a magnet fixed to the rotor 6. A bearing 10 supports the rotor 6 at a fixed position. The bearing 10 is fixed to a support plate 11 provided in the main flow path 2. The rotor 6 provided in the main flow path 2 is covered with a cover 12 so that the gas fluid in the main flow path 2 does not leak. Reference numeral 13 denotes a stator that constitutes the motor 5 and is constituted by a coil.
JP-A-9-60752

  However, the conventional fluid control valve does not effectively use the output of the motor 5 as the opening force of the main flow path opening / closing valve 8. That is, when the gas fluid flows in the direction of closing the main flow path opening / closing valve 8 in FIG. 7, the pressure of the gas fluid closes the main flow path opening / closing valve 8 when the closed main flow path opening / closing valve 8 is opened. It is necessary to overcome the gas back pressure and open the valve. When the main flow path opening / closing valve 8 is opened, the rotor 6 is pressed against the lower bearing 10 to raise the main flow path opening / closing valve 8. As a result, the rotational force of the rotor 6 was not effectively obtained as the opening force of the main flow path opening / closing valve 8 due to the influence of frictional resistance caused by the rotor 6 and the lower bearing 10.

  In order to solve the above-described problems, the present invention stores a stator having a coil, a rotor that is excited and rotated by energization of the coil, a rotating shaft of the rotor, and a stator interposed between the stator and the rotor. A bottomed cylindrical hermetic partition that maintains hermeticity with the gas flow path, a second bearing that is provided at the bottom of the hermetic partition and receives one of the rotating shafts, and is inserted into the opening side of the hermetic partition. A bearing support that supports a first bearing that receives the other of the rotating shaft; a seal member that is disposed on an outer periphery of the hermetic partition wall and maintains hermeticity between the base plate; and Conversion means for conversion, a valve body that opens and closes the flow path by contact with and separation from a valve seat disposed in the gas flow path via the conversion means, and biasing that biases the valve body toward the valve seat side And the converting means includes a threaded portion formed on the rotating shaft. Rotation motion is converted into rectilinear motion by engagement of a nut portion formed on the valve body side, and the first bearing and the second bearing are made of different materials and are used during operation from the open state to the closed state. The rotor is prevented from rotating due to the repulsive force of the biasing means in the closed state while ensuring an efficient rotational operation.

  According to the above invention, the two bearings that receive the rotating shaft and the rotor are made of different materials, so that an electric motor having an output with different torque is obtained, and this electric motor is used as the driving means for the on-off valve. Thus, the output can be selectively used as the opening force of the on-off valve.

The fluid control valve of the present invention includes a stator having a coil, a rotor that is rotated by excitation by energization of the coil, a rotating shaft of the rotor, a first bearing provided on one of the rotating shafts, and the other of the rotating shafts. The first bearing and the second bearing made of a different material are used to provide a bearing having a sliding resistance different from that of the rotating shaft and the rotor. Different motor outputs are obtained, and by using this motor as a driving means for the on-off valve, the output can be selectively used as the opening force of the on-off valve.

  A fluid control valve according to a first aspect of the present invention includes a stator having a coil, a rotor that is excited and rotated by energization of the coil, a rotating shaft of the rotor, and the rotor interposed between the stator and the rotor. A bottomed cylindrical hermetic partition that retains airtightness with the gas flow path, a second bearing that is provided at the bottom of the hermetic partition and receives one of the rotating shafts, and on the opening side of the hermetic partition A bearing support portion that supports a first bearing that is inserted and receives the other of the rotating shafts, a sealing material that is disposed on the outer periphery of the hermetic partition wall and maintains hermeticity between the base plate, and a rotor that directly rotates the rotor. Conversion means for converting into motion, a valve body that opens and closes the flow path by contact with and separation from a valve seat disposed in the gas flow path via the conversion means, and biases the valve body toward the valve seat side Biasing means, and the converting means is a screw formed on the rotating shaft. And the nut portion formed on the valve body side converts the rotational motion into a straight motion, and the first bearing and the second bearing are made of different materials and are operated from the open state to the closed state. The rotation of the rotor due to the repulsive force of the urging means in the closed state is prevented while ensuring an efficient rotation operation.

  And, by using different materials, it becomes a bearing having different sliding resistance with respect to the rotating shaft and the rotor, and an electric motor having a motor output with different torque can be realized by the sliding bearing, and the on-off valve can be realized by combining the on-off valve. During the opening and closing operations, fluid control valves having different output characteristics can be realized.

  In the fluid control valve according to the second aspect of the present invention, the first bearing and the second bearing have a radial bearing portion that receives the rotating shaft and a thrust bearing portion that receives the rotor.

  When the valve is opened and closed, the load of the on-off valve acts most on the contact portion between the thrust bearing and the rotor, so that the sliding resistance can be controlled effectively.

  The fluid control valve according to claim 3 is configured such that the thrust bearing portion of the first bearing and the rotor are in contact with each other during the valve opening operation.

  Then, the on / off valve can be efficiently opened and closed by the first bearing having a low sliding resistance for the rotational output of the rotor.

  The fluid control valve according to claim 4 is configured such that the thrust bearing portion of the second bearing and the rotor are in contact with each other when the valve is closed.

  And it can prevent that a rotor rotates by the reaction force of the urging | biasing force of an urging | biasing means.

  Embodiments of the present invention will be described below with reference to the drawings.

Example 1
FIG. 1 is a configuration diagram of an electric motor according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view of the fluid control valve using the same motor when the valve is opened. FIG. 3 is a sectional view of the fluid control valve when the valve is closed. FIG. 4 is a sectional view of the fluid control valve when the valve is completely closed. FIG. 5 is a configuration diagram of a gas flow path using the fluid control valve. FIG. 6 is an electric system diagram of the electric motor.

  In FIG. 1, reference numeral 14 denotes a stator having a coil 15, and reference numeral 16 denotes a rotor that rotates by excitation by energization of the coil 15. The rotor 16 has a cylindrical shape, and a magnet 17 is provided on the outer periphery thereof. The rotor 16 is provided with a rotating shaft 18. One of the rotating shafts 18 includes a bearing 19, and the bearing 19 includes a radial bearing portion 20 that contacts the rotating shaft 18 and a thrust bearing portion 21 that contacts the rotor 16.

  In addition, a bearing 22 is provided on the other side of the rotating shaft, and the bearing 22 includes a radial bearing portion 23 that contacts the rotating shaft 18 and a thrust bearing portion 24 that contacts the rotor 16. The tip end shape of the thrust bearing portion 21 of the bearing 19 is a curved surface shape that can contact the rotor 16. Further, the thrust bearing portion 24 of the bearing 22 has a larger contact area with the rotor 16 than the thrust bearing portion 21 of the bearing 19. This configuration causes a difference in sliding resistance. The bearings 19 and 22 may be made of the same material when the contact areas are different as shown in FIG. However, when the contact area of the bearing 19 and the bearing 22 is the same, for example, when using a bearing (not shown) having the same shape, a material having a small sliding friction resistance is used for a bearing that requires a small sliding resistance. select. For example, in FIG. 1, when it is necessary to reduce the sliding resistance of the bearing 19, a material having a small sliding friction resistance is selected as the material on the bearing 19 side.

  Reference numeral 25 denotes an airtight partition wall formed between the stator 14 and the rotor 16. Reference numeral 26 denotes an O-ring that seals between the airtight partition wall 25 and the base plate 27. The stepping motor 28 which is an electric motor is configured as described above.

  A fluid control valve using the stepping motor 28 will be described with reference to FIGS. In the figure, 14 to 28 are the same as those in FIG. 29 is a fluid control valve, 30 is an inlet, and 31 is an outlet. The fluid control valve 29 includes a flow path 32, a valve body 33 that opens and closes the flow path 32, a nut 34 that is locked to the valve body 33 and that converts conversion of the direct movement of the valve body 33 into rotation, The rotary shaft 18 of the stepping motor 28 connected to the valve 34, the valve seat 35 with which the valve element 33 abuts, and the spring 36 that is an urging means provided between the nut 34 and the valve element 33 are configured. . Reference numeral 37 denotes an anti-rotation pin that prevents the nut 34 from rotating when the rotor 16 rotates. The distal end 38 of the nut 34 and the distal end 39 of the valve body 33 are locked in a state where the spring 36 is compressed, and the nut 34 and the valve body 33 are configured to be slidable in the direction in which the spring 36 is compressed. Reference numeral 40 denotes a valve rubber provided on the valve body 33, and 41 denotes an O-ring. Reference numeral 42 denotes a screw provided on the rotating shaft.

  In FIG. 4, 43 is a gap formed between the tip 38 of the nut 34 and the tip 39 of the valve element 33. Others are the same as FIG. 2 and FIG.

  5 and 6, reference numeral 44 denotes a gas flow path housing, and a flow path 47 that communicates the inlet 45 and the outlet 46 is formed inside the housing 44. Signals from the fluid control valve 29 that opens and closes the flow path 47, the stepping motor 28 that is a driving means for driving the fluid control valve 29, the arithmetic processing unit 48, and the arithmetic processing unit 48 are input to the flow path 47. The drive control means 50 for controlling the output from the drive circuit section 49 to the stepping motor 28 and the battery power supply section 51 are configured. 52 is a flow rate detecting means, 53 is a pressure sensor, and 54 is a seismic sensor.

Next, the operation and action of the above configuration will be described with reference to FIG. The bearing 19 includes a radial bearing portion 20 that contacts the rotating shaft 18 and a thrust bearing portion 21 that contacts the rotor 16. In addition, a bearing 22 is provided on the other side of the rotating shaft, and the bearing 22 includes a radial bearing portion 23 that contacts the rotating shaft 18 and a thrust bearing portion 24 that contacts the rotor 16. The thrust bearing portion 24 of the bearing 22 is compared with the thrust bearing portion 21 of the bearing 19 in comparison with the rotor 16.
The contact area is large. Therefore, when the rotor 16 rotates with the thrust bearing portion 24 and the rotor 16 in contact with each other as shown in FIG. 1, the sliding resistance at the contacted portion increases and the output torque of the rotating shaft 18 decreases. On the other hand, when the rotor 16 moves downward in FIG. 1 (not shown) and the rotor 16 rotates in a state where the thrust bearing 21 and the rotor 16 are in contact with each other, the sliding resistance of the contacted portion is as follows. The output torque of the rotating shaft 18 increases as the torque decreases.

  Further, when the contact areas of the bearings 19 and 22 are different from each other as shown in FIG. However, when the contact areas of the bearing 19 and the bearing 22 are the same, that is, when a bearing having the same shape (not shown) is used, a material having a small sliding friction resistance is required for a bearing that requires a small sliding resistance. Select. For example, in FIG. 1, in order to reduce the sliding resistance of the bearing 19, a material having a small sliding frictional resistance is selected as the material on the bearing 19 side. Conversely, when it is necessary to reduce the sliding resistance of the bearing 22, a material having a low sliding frictional resistance is selected as the material on the bearing 22 side.

  Further, the thrust bearing portion 24 of the bearing 22 has a larger diameter in contact with the rotor 16 than the thrust bearing portion 21 of the bearing 19, and as a result, the thrust bearing portion 24 of the bearing 22 has a larger diameter than that of the bearing 19. Compared to the portion 21, the contact area is configured to be large. This configuration causes a difference in the sliding resistance between the bearing 19 and the bearing 22.

  Next, the valve closing operation of the fluid control valve 28 will be described with reference to FIGS. 2 to 6. Normally, the valve body 33 of the fluid control valve 29 provided in the gas flow path 47 is in an open state as shown in FIG. 2. In this state, gas flows through the flow path 47 and various instruments (not shown) are used. The gas flow rate is detected by the flow rate detection means 52 and compared with the flow rate data registered in advance in the arithmetic processing unit 48. Depending on the result, the stepping motor 28 which is the drive means is operated, and the valve body 33 is closed. Registered flow rate data includes, for example, data on the maximum amount of passage specified by a household gas meter (when this value is exceeded, the gas stopper may be opened), and the elapsed time is specified by the flow rate at a constant flow rate. There is data when the last time is exceeded (forgetting to turn off the appliance). The flow rate detection means 52 may be either an ultrasonic type or a rubber film type.

  As a result of the comparison, for example, when the maximum passage amount data is exceeded, the arithmetic processing unit 48 determines, drives the stepping motor 28 via the drive control means 50 and the drive circuit unit 49 by the cutoff signal, and the valve element 33. Is closed to cut off the gas flow and prevent the outflow of gas. The stepping motor 28 is activated when the activation frequency is input from the drive circuit unit 49 during the valve closing operation. That is, when the rotor 16 rotates in one direction, the output shaft 18 having the screw 42 rotates, and the nut 34 fitted into the screw 42 and prevented from rotating by the rotation preventing pin 37 moves in the valve closing direction. Further, since the tip 38 of the nut 34 and the tip 39 of the valve body 33 are locked in a state where the spring 36 is compressed, the valve body 33 similarly moves in the valve closing direction. The stepping motor 28 can be driven at a high frequency after being started, and is less affected by the pressure of the gas flowing through the flow path 32 to the valve body 33 during the closing operation, so that the closing is faster than the starting frequency. Driven by the frequency at the time of operation, the valve element 33 moves to the state shown in FIG.

  During this operation, the rotor 16 abuts on the thrust bearing portion 21 of the bearing 19 and rotates by its own weight on the valve body 33, so that the rotation of the rotor 16 can be efficiently converted into driving of the valve body 33. After the valve element 33 comes into contact with the valve seat 35, the valve element 33 is driven at a frequency slower than the closing operation frequency, and the valve element 33 moves to the state shown in FIG. That is, the output after the valve element 33 abuts on the valve seat 35 is driven with a torque larger than the closing operation torque.

Further, the frequency after the valve element 33 comes into contact with the valve seat 35 is adjusted so that, after the valve element 33 comes into contact with the valve seat 35, as shown in FIG. By compressing and driving the valve body 33 at a frequency slower than that during the closing operation until the valve body 33 is in a state of urging the valve seat 35, the valve body 33 can be reliably urged to further improve the closing performance of the valve body 33. It is to ensure. The output at this time is a large torque capable of compressing the spring 36 as the biasing means.

  During this operation, the rotor 16 is in contact with the thrust bearing portion 24 of the bearing 22 by the reaction force of the spring 36 by compressing the spring 36. At this time, although the sliding resistance is increased, the spring 36 can be compressed by driving at a driving frequency slower than that in the closing operation. When the energization of the stepping motor 28 is stopped in the valve closed state shown in FIG. 4, the compressed spring 36 acts to push the nut 34 upward in FIG. The force that pushes the nut 34 acts as a force that rotates the rotor 16 in the direction opposite to that during the valve closing operation via the screw 42.

  However, in this embodiment, when the valve is closed, the high-sliding resistance bearing 22 and the rotor 16 are in contact with each other, and the rotor 16 is not rotated by the reaction force of the spring 36. Further, compared to the force that rotates the rotor 16 via the screw 42, the reaction force of the spring 36 that acts to urge the valve body 33 toward the valve seat 35 is a suction force between the rotor 16 and the stator 14 and the bearing. As a result of increasing the sum of the sliding resistances 22, the rotation of the rotor 16 due to the reaction force of the spring 36 can be reliably prevented. Further, the sealing performance of the valve body 33 can be ensured by the urging force of the compressed spring 36.

  In this way, during the valve closing operation, when the maximum passage amount data is exceeded by driving the output at the start, the output at the closing operation, and the spring 36 as the biasing means with a large output capable of being compressed. , Ensuring safety by blocking gas flow and preventing gas outflow.

  After the gas flow is shut off, the valve body 33 is opened when the safety of the gas circuit is confirmed. Next, the valve opening operation will be described. In response to the opening signal, the stepping motor 28 is driven through the drive control means 50 and the drive circuit unit 49 to open the valve body 33 so that the gas flows. In FIG. 4, first, at the time of start-up, the start-up frequency is input, and when the rotor 16 rotates in the opposite direction to that during the valve closing operation, the output shaft 18 having the screw 33 rotates. The nut 34 moves in the valve opening direction. At this time, the tip end 38 of the nut 34 and the tip end 39 of the valve body 33 are formed with a gap 43 in a state where the spring 36 is compressed. The gap 43 is driven at the starting frequency until the state shown in FIG. Since the spring 36 is in a compressed state at the time of starting, the spring 36 pushes the nut 34 upward in FIG. 4, and the groove of the screw 42 has an inclination angle, so that the rotor 16 is connected via the output shaft 18. A force acts in the direction of rotating.

  Therefore, the rotor 16 is easy to start. When the valve body 33 moves to FIG. 3, the tip end 38 of the nut 34 and the tip end 39 of the valve body 33 come into contact with each other, so that the spring 36 does not act as a force for urging the valve body 33 against the valve seat 35. During the valve opening operation from FIG. 3 to FIG. 2, the pressure of the gas flowing through the flow path 32 acts as an urging force that urges the valve body 33, so that the gas overcomes the force that urges the valve body 33. Will be opened. At this time, the valve rubber 40 is driven at a valve opening operation frequency slower than the activation frequency, and the valve rubber 40 provided on the valve body 33 is operated until it is detached from the valve seat 35.

The output at the time of this valve opening operation becomes a larger torque than the output at the time of starting. During this valve opening operation, the rotor 16 moves downward in FIG. 3 to open the valve body 33 in the closed state, and the rotor 16 contacts the thrust bearing portion 21 of the bearing 19 with low sliding resistance. Rotate. Therefore, the rotation of the rotor 16 can be efficiently converted into driving of the valve element 33. Then, after the valve element 33 is detached from the valve seat 35, the valve element 33 is driven at a frequency faster than the frequency at the time of the valve opening operation, and the valve element 33 moves to the state shown in FIG. The output after the valve element 33 is detached from the valve seat 35 is driven with a torque smaller than the torque during the valve opening operation. At this time, since the fluid pressure of the gas flowing through the flow path 32 does not act on the valve body 33, the valve body 33 can be driven with a small torque.

  In this way, the valve is driven with a torque at the time of start-up operation, a torque larger than that at the time of start-up during the valve-open operation, and a torque smaller than the torque at the time of the open operation after the opening.

Sectional drawing which shows the structure of the electric motor of Example 1 of this invention. Sectional drawing which shows the structure at the time of valve opening of the fluid control valve of Example 1 of this invention Sectional view showing the configuration of the fluid control valve when it is closed Sectional view showing the configuration of the fluid control valve when it is completely closed Configuration diagram showing the relationship between the fluid control valve and the control system Electrical diagram of the motor Configuration diagram of conventional fluid control valve

Explanation of symbols

14 Stator 15 Coil 16 Rotor 18 Rotating shaft 19, 22 Bearing 28 Electric motor

Claims (4)

A stator having a coil, a rotor that is excited and rotated by energization of the coil, a rotating shaft of the rotor, and a rotor interposed between the stator and the rotor to store the rotor and maintain gas tightness with the gas flow path A bottomed cylindrical hermetic partition, a second bearing provided at the bottom of the hermetic partition and receiving one of the rotating shafts, and a first bearing inserted on the opening side of the hermetic partition and receiving the other of the rotating shafts A bearing support that supports the seal, a sealing material that is disposed on the outer periphery of the hermetic partition wall and maintains hermeticity between the base plate, a conversion unit that converts the rotation of the rotor into a linear motion, and the conversion unit. A valve body that opens and closes the flow path by contact with and separation from the valve seat disposed in the gas flow path, and a biasing means that biases the valve body toward the valve seat side,
The converting means converts a rotational motion into a straight motion by engagement of a screw portion formed on the rotating shaft and a nut portion formed on the valve body side,
The first bearing and the second bearing are made of different materials, and ensure efficient rotation during the operation from the open state to the closed state, and by the repulsive force of the urging means in the closed state. A fluid control valve designed to prevent rotation of the rotor. The fluid control valve according to claim 1, wherein the first bearing and the second bearing have a radial bearing portion that receives the rotating shaft and a thrust bearing portion that receives the rotor. The fluid control valve according to claim 1, wherein the thrust bearing portion of the first bearing and the rotor are in contact with each other during the valve opening operation. The fluid control valve according to claim 1 or 2, wherein the thrust bearing portion of the second bearing and the rotor are in contact with each other when the valve is closed.

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