JP5328921B2 - Valve opening / closing mechanism - Google Patents

Description

  The present invention relates to a valve opening / closing mechanism that controls opening and closing of two or more valves asynchronously with one power source (actuator).

  Conventionally, there is Patent Document 1 that opens and closes two or more passages by controlling two or more valves with one power source. The device described in Patent Document 1 uses a gear for the power transmission mechanism, and the gear and the output shaft are fixed. Patent Document 2 discloses that two or more passages are controlled to be opened and closed asynchronously. What is described in Patent Document 2 is only the application of pressure to the output shaft, and does not directly apply pressure to the gear.

JP 2002-298528 A FR2926126

  However, in the configuration described in Patent Document 1, the gear connected to one power source and each output shaft cannot be moved individually. Therefore, in the EGR system that returns exhaust gas from the engine to the intake side, there is a problem that two valves and power sources having different types of the EGR valve that controls the exhaust gas flow rate and the switching valve that switches the passage are necessary.

  Further, in the configuration described in Patent Literature 2, two or more passages can be controlled to open and close asynchronously, but since no pressure is applied to the gear, the power transmission member is caused by vibration or the like. Backlash and backlash of the link will occur, causing wear and abnormal noise. In addition, when a position sensor is provided in one power transmission member and the position of another output shaft is detected, there is a problem that accurate position detection cannot be performed if there is play.

  The present invention has been made to solve the above-described problems. In a valve opening / closing mechanism that asynchronously controls opening / closing of two or more valves with one power source, wear and noise are suppressed, and a sensor is installed. It is intended to enable accurate position detection by being installed on a power transmission member.

The valve opening / closing mechanism according to the present invention includes an input shaft, two or more output shafts each having a valve, a power transmission member that transmits the power of the input shaft to each of the output shafts while changing the phase, and the output A first pressure applying member that applies pressure to the shaft; and a second pressure applying member that applies pressure in a direction opposite to the first pressure applying member to the power transmission member. Yes.

According to this invention, the opening patterns of the valves provided on the respective output shafts can be variously set by transmitting the power of the input shafts to the output shafts while changing the phase. Further, since each output shaft is separated from the power transmission member, there is an effect that heat transfer can be relaxed when the flow rate of the high-temperature gas is controlled.
And since the pressurization is given to the output shaft, the valve can be returned to an arbitrary position (initial position) at the time of failure. The effect of vibration and gas pressure pulsation is suppressed, and the valve can be stably held at the initial position even when no current is applied.

  In addition, since the pressure applied to the power transmission member in the opposite direction to the pressure applied to the output shaft is applied, the backlash of the gear due to vibration and the vibration of the power transmission member due to the backlash of the link are suppressed, and abnormal noise and friction are suppressed. Suppression is possible. Since the power transmission member cannot swing with respect to the output shaft, the position can be accurately measured even if the sensor magnet is installed on the power transmission member. When a sensor magnet is installed on the power transmission member, the positions of other output shafts can be measured with the same sensor magnet.

It is the front view which cut through a part which shows the valve opening and closing mechanism of this invention. FIG. 2 is a cross-sectional bottom view taken along line 2-2 of FIG. It is a schematic block diagram which shows the valve | bulb opening / closing mechanism of this invention. It is a longitudinal cross-sectional view of the principal part which shows the structure which gives the pressurization of the opposite direction to the pressurization of each output shaft to a gear. It is a partial longitudinal cross-sectional view which shows the state which installed the sensor facing the magnet of a gear head. It is the figure which showed the valve opening with respect to operation | movement of a gear according to the state at the time of normal time and valve | bulb fixation, and the spring load seen from the motor. It is a flowchart explaining lock detection and lock release operation | movement. It is a figure which shows the modification 1 of the contact part of a gear and an arm member, (a) is a top view, (b) is a cross-sectional view which follows the 8-8 line. It is a figure which shows the modification 2 of the contact part of a gear and an arm member, (a) is a top view, (b) is a cross-sectional view which follows the 9-9 line. It is a block diagram using a link as a transmission member. It is a block diagram which shows the other modification using a link as a transmission member. It is a longitudinal cross-sectional view of the principal part which shows the modification of the structure which gives the pressurization of the direction opposite to the pressurization of each output shaft to the gear shown in FIG. FIG. 13 is a plan view of FIG. 12 with the valve housing removed. It is a longitudinal cross-sectional view of the principal part which shows the other structure which gives the pressurization of the opposite direction to the pressurization of each output shaft to a gear. FIG. 15 is a plan view of FIG. 14 with the valve housing removed.

Hereinafter, in order to explain the present invention in more detail, modes for carrying out the present invention will be described with reference to the accompanying drawings.
Embodiment 1 FIG.
FIG. 1 is a partially cutaway configuration diagram showing a valve opening / closing mechanism according to Embodiment 1 of the present invention, and FIG. 2 is a transverse bottom view taken along line 2-2 of FIG. This valve opening / closing mechanism includes a motor 1 as a power source, an input shaft 2 for inputting power from the motor 1 to the valve side, and an output shaft 5 having valves 3 and 4 for supplying the power of the input shaft 2 respectively. Gears 7 and 8 that transmit to 6 and a valve housing 9 that houses them are provided.

  The valve housing 9 is formed with a passage 9a that passes through the cooler in parallel and a passage 9b that does not pass through the cooler. The output shafts 5 and 6 pass through the passages 9a and 9b through the bearings 10 and 11, respectively. It is supported freely. A mounting substrate 12 of the motor 1 is attached to the upper end of the peripheral side wall of the recess provided in the upper part of the valve housing 9 with a packing 13 interposed therebetween, and the recess is formed as a gear housing chamber 14.

  The input shaft 2 is rotatably supported on the substrate 12 via a bearing 15, and a pinion via 16 is attached to the tip portion thereof. Gears 7 and 8 are rotatably attached to the distal end portions of the output shafts 5 and 6 that have entered the gear housing chamber 14, and the gears 7 and 8 mesh with the pinion gear 16, respectively. The gears 7 and 8 are respectively formed with fan-shaped holes 7a and 8a.

  Further, cylinders 17 and 18 are attached to the output shafts 5 and 6 in the vicinity of the gears 7 and 8, and arm members 17 a and 18 a provided on the cylinders 17 and 18 are attached to the holes 7 a of the gears 7 and 8. , 8a and abuts against the hole surface. Coil springs 19 and 20 as pressurizing members are wound around the outer circumferences of the cylinders 17 and 18, and the output shafts 5 and 6 are constantly pressurized in the valve closing direction by the coil springs 19 and 20. In order to seal the lower ends of the output shafts 5 and 6, sealing members 21 and 22 are provided on the valve housing 9 so as to face the lower ends. A power transmission member between the input shaft 2 and the output shaft 5 (6) is constituted by the pinion gear 16, the gear 7 (8), the hole 7a (8a), the arm member 17a (18a), and the cylindrical body 17 (18). Is configured.

  Hereinafter, the operation of the valve opening / closing mechanism according to the first embodiment will be described with reference to FIGS. 1 and 2. 1 and 2 show a state in which the valves 3 and 4 attached to the output shafts 5 and 6 are closed. In this state, the pinion gear 16 integrated with the input shaft 2 of the motor 1 is When rotated counterclockwise (broken line arrow in the figure), the gears 7 and 8 engaged with the pinion gear 16 rotate in the right direction. For this reason, the hole surface 7a-1 of the gear 7 abuts on the arm member 17a, rotates the output shaft 5 in the right direction via the cylindrical body 17, and opens the valve 3. On the other hand, since the gear 8 rotates in the direction in which the hole surface 8a-1 moves away from the arm member 18a, the output shaft 6 cannot rotate, and the valve 4 maintains the valve closed state.

  1 and 2, when the pinion gear 16 integrated with the input shaft 2 of the motor 1 rotates to the right (solid arrow in the figure), the gears 7 and 8 meshed with the pinion gear 16 are respectively left Rotate in the direction. For this reason, since the gear 7 rotates in the direction in which the hole surface 7a-1 moves away from the arm member 18a, the output shaft 6 cannot rotate, and the valve 4 maintains the closed state. On the other hand, the gear 8 has the hole surface 8 a-1 in contact with the arm member 17 a, rotates the output shaft 5 through the cylindrical body 17, and opens the valve 3. At this time, the flow rate of the exhaust gas flowing through the passage 9a or the passage 9b can be controlled by controlling the opening degree of the valves 3 and 4 according to the energization amount to the motor 1.

  As described above, according to the valve opening / closing mechanism according to Embodiment 1 of the present invention, the valves 3 and 4 provided on the output shafts 5 and 6 can be asynchronously controlled by the rotation direction of the input shaft. At the same time, various valve opening patterns can be set. Moreover, since each output shaft 5 and 6 is isolate | separated from the arm members 17a and 18a, when controlling the distribution | circulation amount of high temperature gas, heat transfer can be eased. Further, since the output shafts 5 and 6 are pressurized in the valve closing direction by the coil springs 19 and 20, the valve can be closed, the position when the actuator 1 is not energized is regulated, and the touch due to vibration is suppressed. Can do.

  Further, by arbitrarily setting the distance between the arm members 17a, 18a and the hole surfaces 7a-1, 8a-1 in the valve open state, that is, by making the reduction ratio of the power transmission member variable, the operating range of the output shaft can be increased. It can be arbitrarily set for each valve, and the distance between the valves can also be changed. Further, by making the axial arrangement of the power transmission members variable, interference between the power transmission members can be avoided even when the distance between the valves is reduced.

  FIG. 3 shows a comparison between the valve opening / closing mechanism according to the first embodiment of the present invention and the passage through which the cooler passes and the passage through which the cooler does not pass, and the flow rate is controlled in comparison with the conventional example. FIG. In the EGR system that returns exhaust gas from the engine to the intake side, a cooler 31 is installed to lower the gas temperature and increase the EGR effect. However, when the gas temperature is low, such as when the engine is started, the gas temperature decreases. Too much. Therefore, a passage 32 that passes through the cooler 31 and a passage 33 that does not pass through the cooler 31 are provided. Therefore, in the conventional configuration shown in FIG. 3 (a), it is necessary to install an EGR-valve 35 for controlling the gas flow rate and a switching valve 34 for switching the passage 32 passing through the cooler 31 and the passage 33 not passing through the cooler 31. It was.

  On the other hand, when the valve opening / closing mechanism according to Embodiment 1 of the present invention is used as the EGR valve 36, the gas flow rate can be controlled and the passage can be switched by one EGR valve 36, which is necessary in the conventional configuration. The switching valve 34 is not required, and the configuration can be simplified and the cost can be reduced. In addition, since the switching valve 34 and the EGR valve 35 provided at two locations in the gas flow passage can be shared by one EGR valve 36, the pressure loss can be reduced to ½.

Embodiment 2. FIG.
FIG. 4 is a structural view in which a part of a valve opening / closing mechanism according to Embodiment 2 of the present invention is vertically cut. This valve opening / closing mechanism serves as a pressure applying member for each of the gears 7 and 8 so as to give the gears 7 and 8 a pressurizing force in a direction opposite to the pressurizing force applied to the output shafts 5 and 6 by the coil springs 19 and 20. The coil springs 23 and 24 are mounted. In this case, one end of the coil springs 23 and 24 is fixed to the gears 7 and 8 and the other end is fixed to the valve housing 9, and when the motor 1 is not energized and when the holes 7a-1 and 8a-1 of the gears 7 and 8 and the arm Even when the members 17a and 18a are not in contact with each other, the gears 7 and 8 can be prevented from being shaken by the pressurization of the coil springs 23 and 24, so that the wear of the gears 7 and 8 can be suppressed.

Embodiment 3 FIG.
FIG. 5 is a structural view in which a part of a valve opening / closing mechanism according to Embodiment 3 of the present invention is vertically cut. In this valve opening / closing mechanism, in order to increase the resolution, a sensor 26 is installed facing the magnet 25 on the gear head, and the gear keeps moving even when the one-side valve is not operating. However, since the gear cannot swing with respect to the output shaft, it is possible to detect the positions of the valves on both sides only by installing the sensor 26 facing the magnet 25 on the gear head on one side. However, the position of the gear may not match the position of the valve when the valve is fixed, etc., so it is possible to install the sensor 26 on the output shaft or arm member on both sides facing the magnet installed on the gear. To do.

Embodiment 4 FIG.
FIG. 6 shows a valve opening / closing mechanism according to Embodiment 4 of the present invention by displaying the valve opening with respect to the operation of the gears 7 and 8 and the spring load as viewed from the motor 1 according to the normal state and the state when the valve is fixed. It is a figure. In this valve opening / closing mechanism, the contact portions of the arm members 17a, 18a and the output shafts 5, 6 are provided in the direction opposite to the driving direction, and the driving force of the motor 1 is forcibly used even when the valve is fixed. It can be closed. Note that the horizontal axis of the drawing showing the valve opening is the position of the motor 1, and a step sensor is integrated with the motor 1 every 10 °, and the initial position (1), (2), fully open position. (1) and (2) are intended for the output of the step sensor.

  During normal operation, when the motor 1 is not energized, the valves 3 and 4 are held in the closed state by the valve preload springs (center view in FIG. 6). In this state, when the pinion gear 16 is rotated counterclockwise, the gears 7 and 8 are rotated clockwise. For this reason, the arm member 18a is pushed by the hole surface 8a-1 of the gear 8 and rotated clockwise, and the valve 4 is opened according to this rotation. On the other hand, the gear 7 does not open the valve 3 because the hole surface 7a-1 rotates in a direction away from the arm member 17a.

  Further, when the pinion gear 16 is rotated in the clockwise direction with the valves 3 and 4 being closed, the gears 7 and 8 are rotated in the counterclockwise direction. For this reason, the arm member 17a is pushed by the hole surface 7a-1 of the gear 7 and rotated counterclockwise, and the valve 3 is opened according to this rotation. On the other hand, the gear 8 does not open the valve 4 because the hole surface 8a-1 rotates in a direction away from the arm member 18a.

  Accordingly, the valves 3 and 4 open and close asynchronously with the counterclockwise and clockwise rotation of the pinion gear 16. Here, the driving force supplied to the motor 1 when the valves 3 and 4 are closed is the lock detection driving force (A) setting range, the closed region of the valves 3 and 4 is the lock detection determination width (B), The movable range 4 is the cleaning operation determination width (C).

  Next, the time when the valve is fixed will be described. The illustrated example shows a state in which the valve 3 is not closed by the valve preload spring when the motor 3 is not in operation when the valve 3 is not energized due to foreign matter mixed in during the opening.

  In such a state, when the pinion gear 16 is rotated clockwise, the gears 7 and 8 are rotated counterclockwise, and the arm member 17a is pushed by the hole surface 7a-1 of the gear 7 to rotate counterclockwise. Since the arm member 17a does not return to the predetermined position due to the valve 3 being fixed, the spring force applied to the gear 7 is small and is rotated by a small driving force supplied to the motor 1, so this small By the driving force, the sticking, that is, the lock of the valve 3 is detected.

  FIG. 7 is a flowchart for explaining the lock detection and release operation of the valve 3 or the valve 4. First, when the lock detection of the valves 3 and 4 is started (step ST1), the motor 1 is driven with the driving force (A) (step ST2), and it is determined whether the specified time has passed (step ST3). For example, it is determined whether there is a position change <sensor output change> (step ST4). If NO, the process returns to step ST3 to continue the above operation.

  If the determination in step ST3 and step ST4 is YES, the position is set to the initial position (1) (step ST5), the motor is driven in the reverse direction with the driving force (A) (step ST6), and the specified time has elapsed. If NO (NO in step ST7), it is determined whether or not there is a position change <sensor output change> (step ST8). If NO, the process returns to step ST7 to continue the above operation. On the other hand, if the determination in step ST7 and step ST8 is YES, the position is set to the initial position (2) (step ST9), and | initial position (1) −initial position (2) | <lock detection determination width ( B) is determined. If YES, the valve opening / closing is determined to be normal and the lock detection is terminated (step ST11).

  If the determination in step ST10 is NO, for example, it is determined whether the number of retries <3 (step ST12). If NO, it is determined that the valve is abnormal and the lock detection is terminated (step ST25). On the other hand, if the determination in step ST12 is YES, the motor is driven with full power (step ST13), it is determined whether the specified time has elapsed (step ST14), and if NO, the position change <sensor output change> is If it is NO, the process returns to step ST14 and the above operation is continued.

  If the determination in step ST14 and step ST15 is YES, the position is set to the fully open position (1) (step ST16), the motor is driven in the reverse direction with full power (step ST17), and it is determined whether the specified time has elapsed. If it is NO (NO in step ST18), it is determined whether there is a change in position <sensor output change> (step ST19). If NO, the process returns to step ST18 and the above operation is continued. In this way, the fixed valve can be forcibly closed by driving the motor in the reverse direction with full power. On the other hand, if the determination in step ST18 and step ST19 is YES, the position is set to the fully open position (2) (step ST20), and | initial position (1) −initial position (2) | <cleaning operation determination width ( C) is determined (step ST21).

If the determination in step ST21 is YES, a lock detection count is performed (step ST23), and then it is determined whether lock detection count> 3 (step ST24). If YES, the process proceeds to step ST25 to determine that the valve is abnormal. To end lock detection. If the determination in step ST21 or step ST24 is NO, the number of retries is counted and the process returns to step ST1.
Note that (1) and (2) given to the initial position and the fully opened position correspond to circles 1 and 2 attached to the initial position and fully opened position in FIG.

  As described above, according to the fourth embodiment, lock detection is performed, and the motor is driven in a direction opposite to the valve opening control, so that the hole surfaces 7a-2 and 8a-2 opposite to those at the time of valve opening are formed. Since the valve is operated in the valve closing direction by abutting against the arm members 17a and 18a, the valve can be forcibly closed even if the valve is stuck or locked in the middle of opening due to foreign matter or the like being mixed. The inconvenience associated with can be avoided.

Embodiment 5 FIG.
In each of the above embodiments, the gear and the arm member are configured such that the arm member is placed in a hole provided in the gear and the arm member is brought into contact with the edge of the hole. FIG. 9 is a view showing a modification of the contact portion between the gear and the arm member according to the fifth embodiment, wherein the gears 7 and 8 are provided with convex portions 7b and 8b, and the convex portions 7b and 8b are in contact with the arm members 17a and 18a. It can also be set as the structure which touches. With this configuration, as shown in the first to fourth embodiments, the gears 7 and 8 can be downsized compared to the case where the holes 7a and 8a are provided in the gears 7 and 8. In addition, FIG.8 (b) is a longitudinal cross-sectional view which follows the 8-8 line | wire of Fig.8 (a).

Embodiment 6 FIG.
FIGS. 9A and 9B are diagrams showing a modification of the contact portion between the gear and the arm member according to the sixth embodiment. The gears 7 and 8 are provided with pin insertion holes 17c and 18c. The protrusions shown in the fifth embodiment can be obtained by press-fitting pins 27 and 28 into 17c and 18c. With such a configuration, the same gear can be used on both the left and right sides by changing the positions of the holes into which the pins 27 and 28 are inserted. In addition, FIG.9 (b) is a longitudinal cross-sectional view which follows the 9-9 line | wire of Fig.9 (a).

Embodiment 7.
FIG. 10 is a view showing a valve opening / closing mechanism according to Embodiment 7 of the present invention. In the first to sixth embodiments, a gear is used as a power transmission member for transmitting the power of the input shaft 2 to the output shafts 5 and 6. In this seventh embodiment, a link is used as the power transmission member. The intermediate portion of the lever 41 is attached to the input shaft 2, the ends of the links 42 and 43 are connected to both ends of the lever 41 by connecting pins 44 and 45, and attached to the output shafts 5 and 6. The pins 48 and 49 at the tips of the crank levers 46 and 47 are engaged with elongated holes 42a and 43a formed in the links 42 and 43, respectively.

  With this configuration, when the input shaft 2 rotates in the direction of the solid arrow as in the illustrated example, the lever 41 rotates counterclockwise, pulling down the link 42 and pushing up the link 43 in the drawing. For this reason, the hole edge 43 a-1 of the elongated hole 43 a of the link 43 rotates the crank lever 47 in the clockwise direction via the pin 49. That is, the power of the input shaft 2 is transmitted to the output shaft 6. At this time, the hole edge 42 a-1 of the elongated hole 42 a of the lowered link 42 is only moved away from the pin 48 of the crank lever 46, and the power of the input shaft 2 is not transmitted to the output shaft 5.

  On the other hand, contrary to the above, when the input shaft 2 rotates in the direction of the dotted arrow, the lever 41 rotates in the clockwise direction, pushing up the link 42 and pulling down the link 43 in the figure. Therefore, the hole edge 42 a-1 of the long hole 42 a of the link 42 rotates the crank lever 46 counterclockwise via the pin 48. That is, the power of the input shaft 2 is transmitted to the output shaft 5. At this time, the hole edge 43 a-1 of the elongated hole 43 a of the link 43 that has been pulled down merely moves away from the pin 49 of the crank lever 47, and the power of the input shaft 2 is not transmitted to the output shaft 6.

  As described above, also in the seventh embodiment in which a link is used as a power transmission member, power can be transmitted in the same manner as in each embodiment in which a gear is used as a power transmission member, and the same effect can be obtained. .

Embodiment 8 FIG.
FIG. 11 is a view showing a valve opening / closing mechanism according to Embodiment 8 of the present invention, which is a modification of Embodiment 7 in which a link is used as a power transmission member. In the eighth embodiment, a crank lever 51 is attached to the input shaft 2, the ends of the links 52, 53 are connected to the end of the lever 51 by a connecting pin 54, and the crank is attached to the output shafts 5, 6. The pins 57 and 58 at the tips of the levers 55 and 56 are engaged with elongated holes 52a and 53a formed in the links 52 and 53, respectively.

  With this configuration, when the input shaft 2 rotates in the direction of the solid arrow as in the illustrated example, the lever 51 rotates counterclockwise, and in the figure, the links 52 and 53 are moved to the right. For this reason, the hole edge 53 a-1 of the long hole 53 a of the link 53 rotates the crank lever 56 clockwise via the pin 58. That is, the power of the input shaft 2 is transmitted to the output shaft 6. At this time, the hole edge 52 a-1 of the long hole 52 a of the link 52 only moves away from the pin 57 of the crank lever 55 and does not transmit the power of the input shaft 2 to the output shaft 5.

  On the other hand, contrary to the above, when the input shaft 2 rotates in the direction of the dotted arrow, the lever 51 rotates in the clockwise direction and moves the links 52 and 53 in the left direction in the figure. Therefore, the hole edge 52 a-1 of the long hole 52 a of the link 52 rotates the crank lever 55 counterclockwise via the pin 57. That is, the power of the input shaft 2 is transmitted to the output shaft 5. At this time, the hole edge 53 a-1 of the long hole 53 a of the link 53 only moves away from the pin 58 of the crank lever 56 and does not transmit the power of the input shaft 2 to the output shaft 6.

  As described above, also in the eighth embodiment, which is a modification of the seventh embodiment using a link as a power transmission member, power can be transmitted in the same manner as each embodiment using a gear as a power transmission member. The same effect can be obtained.

Embodiment 9 FIG.
12 and 13 are a longitudinal sectional view and a plan view of a main part showing a modification of the configuration in which the gear according to the second embodiment is applied with a pressurization in the direction opposite to the pressurization of each output shaft. 6 are used as plate bodies 27 and 28, and end bent portions 27a and 28a of the plate bodies 27 and 28 are engaged with holes 7a and 8a provided with gears 7 and 8, respectively. One end of 24 is fixed to the gears 7 and 8 and the other end is fixed to the valve housing 9.

  When the coil springs 23 and 24 are provided between the valve housing 9 and the gears 7 and 8 as the components of the power transmission member as in this configuration, A is the spring load direction of the coil spring 19 acting on the left output shaft 5 and B Is the spring load direction of the coil spring 23 acting on the left power transmission member, C is the spring load direction of the coil spring 24 acting on the right power transmission member, and D is the spring load direction of the coil spring 20 acting on the right output shaft 6.

  When the pinion gear 16 is rotated in the direction (1), the right output shaft 6 rotates in the clockwise direction together with the gear 8, and the plate body 28 is connected via the end bent portion 28 a engaged with the hole 8 a provided in the gear 8. When is pushed, the output shaft 6 integrated with the plate 28 is also rotated in the clockwise direction. For this reason, the coil spring 24 provided between the valve housing 9 and the gear 8 rotates so as to release the pressurization. However, since the coil spring 24 needs to secure a necessary pressure even at the end of rotation of the plate body 28 shown by hatching, the pressure applied at the illustrated position of the coil spring 24 is applied with an application force released by the rotation. A large pressure is required. As a result, in order to ensure the self-returning property, it is necessary to apply a pressure that overcomes the pressure applied to the output shaft 6, and the pressure applied to the coil spring 20 that applies pressure in the opposite direction to the coil spring 24 also increases. It will be. When the pinion gear 16 is rotated in the direction (2), the same thing as described above occurs in the coil springs 23 and 19.

  FIGS. 14 and 15 are a longitudinal sectional view and a plan view of the main part of the configuration for applying a pressure in the direction opposite to the pressure applied to each output shaft to the gear according to the ninth embodiment. In order to improve the point that requires a large pressurizing force due to the configuration, the coil springs 23 and 24 for applying a pressurizing force to the gears 7 and 8 are arranged, one end 23a and 24a are gears 7 and 8 and the other end 23b and 24b are plate bodies. This configuration is fixed to the output shafts 5 and 6 via 28.

  When the coil springs 23 and 24 are provided between the output shafts 5 and 6 and the gears 7 and 8 that are components of the power transmission member as in this configuration, A is the spring load direction of the coil spring 19 acting on the left output shaft 5. , B is the spring load direction of the coil spring 23 acting on the left power transmission member, C is the spring load direction of the coil spring 24 acting on the right power transmission member, and D is the spring load direction of the coil spring 20 acting on the right output shaft 6. .

  In the state shown in the drawing, when the pinion gear 16 is rotated in the direction (1), the right output shaft 6 rotates in the clockwise direction together with the gear 8, and the end bent portion 28a engaged with the hole 8a provided in the gear 8 is moved. When the plate body 28 is pushed through, the output shaft 6 integrated with the plate body 28 also rotates in the clockwise direction. However, one end 24 a of the coil spring 24 moves to the oblique line position together with the gear 8, but the other end 24 b also moves to the oblique line position together with the plate body 28 integrated with the output shaft 6, so that the coil spring 24 is released from the applied pressure. Rotational force does not work. As a result, the coil spring 24 only needs to have a minimum required pressure at the illustrated position, so that the pressure of the coil spring 20 for ensuring the self-returning property can be kept small, and the load for valve operation is reduced. This makes it possible to drive the valve with quick response even with less power. When the pinion gear 16 is rotated in the direction (2), the applied pressure of the coil springs 23 and 19 can be reduced by the same operation as described above.

Claims (9)

An input shaft driven by the power source, and two or more output shaft having a valve, respectively, the power of the input shaft, a power transmission member for transmitting to each of said output shaft by changing the phase, given to the output shaft A first pressurizing member for applying pressure; and a second pressurizing member for applying a pressure in the direction opposite to the first pressurizing member to the power transmission member. The valve opening and closing mechanism. The valve opening / closing mechanism according to claim 1, wherein the second pressurizing member is disposed between the output shaft and the power transmission member.   2. The valve opening / closing mechanism according to claim 1, wherein a reduction ratio of each power transmission member is variable.   The valve opening / closing mechanism according to claim 1, wherein the axial arrangement of each power transmission member is variable.   The valve opening / closing mechanism according to claim 1, wherein a sensor for detecting a position is provided in one power transmission member to detect the position of each output shaft.   2. The valve opening / closing mechanism according to claim 1, wherein a sensor for detecting the position of the valve is provided on each output shaft.   2. The valve opening / closing mechanism according to claim 1, wherein a contact portion between the output shaft and the power transmission member is provided on the side opposite to the driving direction.   2. The valve opening / closing mechanism according to claim 1, wherein each power transmission member is a gear.   2. The valve opening / closing mechanism according to claim 1, wherein each power transmission member is a link.

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