JP2006038193A - Electric control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To finely and highly accurately control a flow rate, without requiring large motor torque, in a rotary electric control valve. <P>SOLUTION: A first inlet-outlet flow port 11 and a second inlet-outlet flow port 12 are arranged in a valve housing 10. The inside of the valve housing 10 is provided with a rotary valve element 30 having a flows rate control shape part (a first flow rate control recessed groove 31, and a second flow rate control recessed groove 32), and controlling a flow rate of fluid flowing between the first inlet-outlet flow port 11 and the second inlet-outlet flow port 12, by increasing-decreasing the effective communicating area between the first inlet-outlet flow port 11 and the second inlet-outlet flow port 12 by the flow rate control shape part in response to a turning angle. A bevel gear type speed reduction gear device is arranged between a rotary valve element 30 and a rotor shaft 43 of a stepping motor 40 installed in the valve housing 10. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an electric control valve, and more particularly to a rotary electric control valve used in a heat pump type air conditioner or the like.

  As the flow control valve, a rotary electric control valve that quantitatively controls the flow rate according to the rotation angle (rotation position) of the valve body by rotating the valve body by an electric motor such as a stepping motor is provided. is there. This rotary electric control valve uses a cross-sectional shape for controlling the flow rate, a cylindrical or disk-shaped valve body having a concave groove, and the valve body is directly connected to the rotor and output shaft of the electric motor. The linearly rotated type (for example, Patent Documents 1, 2, 3, and 4) and the rotation of the electric motor are transmitted to the plate-like valve body by a spur gear train for reduction, and the valve body There are deceleration types that directly increase or decrease the effective opening area of the port according to the rotational displacement position (for example, Patent Documents 5, 6, and 7).

  In direct-acting rotary electric control valves, the torque required for driving the valve is directly affected by the operating pressure differential acting on the valve body. The higher the high-pressure specification, the greater the motor torque required for driving the valve. Therefore, it is necessary to increase the size and output of the electric motor.

  In addition, since the direct-acting rotary electric control valve controls the flow rate by the rotational displacement of the valve body within one rotation, the flow rate is reduced by increasing or decreasing the passage cross-sectional area by the cross-sectional shape or concave groove of the valve body. Even if the control is attempted, since the motor resolution is poor, the stepping motor has a large flow rate change amount for one pulse, and fine high-precision flow rate control cannot be performed.

  The reduction-type rotary electric control valve can reduce the motor torque required to drive the valve according to the reduction ratio, but the plate-like valve element directly increases or decreases the effective opening area of the port to control the flow rate. It is difficult to perform fine high-accuracy flow rate control, and since a spur gear train is used as a speed reducer, the radial dimension becomes large and a large space is required for installation.

Further, the conventional rotary electric control valve lacks the ease of incorporating a stopper mechanism for setting the maximum valve closing position and the maximum valve opening position of the valve body.
Japanese Patent No. 3454603 JP 2001-187777 A JP 2002-295694 A JP 2003-278934 A Japanese Patent No. 329589 JP 2001-56060 A JP 2004-28176 A

  The problem to be solved by the present invention is to perform fine and highly accurate flow rate control in a rotary electric control valve without requiring a large motor torque.

  An electric control valve according to the present invention includes a valve housing having a first inlet / outlet port and a second inlet / outlet port, a valve housing rotatably provided in the valve housing, a flow rate control shape portion, and a rotation angle. Accordingly, the effective communication area between the first inlet / outlet port and the second inlet / outlet port is increased / decreased by the flow rate control shape portion, and the first inlet / outlet port and the second inlet / outlet port are A rotary valve body that controls the flow rate of the fluid flowing between the electric motor, an electric motor attached to the valve housing, and an output shaft of the electric motor and the rotary valve body. A reduction gear device that transmits the reduction valve to the rotary valve body.

  The electric control valve according to the present invention preferably has a pair of input gear and output gear with which the reduction gear device meshes, the input gear is drivingly connected to the output shaft, and the output gear is rotated. It is integrally formed with the valve body.

  In the electric control valve according to the present invention, preferably, the reduction gear device is a cross shaft gear.

  In the electric control valve according to the present invention, it is preferable that a C-shaped arc-shaped stopper groove is formed concentrically with the rotation center of the rotary valve body, and the stopper recess is formed in the valve housing. A stopper projection that engages with the groove is provided, and the stopper projection selectively abuts on both ends in the arc direction of the concave groove for stopper, thereby restricting the rotation angle range of the rotary valve body to within 360 degrees. Then, the maximum valve closing position and the maximum valve opening position of the rotary valve body are set by the restriction.

  In the electric control valve according to the present invention, preferably, a valve seat surface having the first inlet / outlet port or the second inlet / outlet port opened is formed in the valve housing, and the valve seat of the rotary valve body is formed. As the flow control shape portion, a C-shaped arc-shaped flow control groove is formed concentrically with the rotation center of the rotary valve body on the surface facing the surface, and the flow control groove is displaced in the arc direction. A groove shape that changes the groove cross-sectional area for each position, and the first inlet / outlet port or the second inlet / outlet port that opens to the valve seat surface, and the rotation angle of the rotary valve body The effective communication area between the first inlet / outlet port and the second inlet / outlet port is increased / decreased according to the determined positional relationship in the arc direction of the concave groove for flow control, and the first inlet / outlet port and the second inlet / outlet port are increased or decreased. Flows between two incoming and outgoing ports To control the flow rate of the body.

  In the electric control valve according to the present invention, preferably, the valve housing has a first valve seat surface in which the first inlet / outlet port is opened and a second valve seat in which the second inlet / outlet port is opened. The valve seat surface is formed in a state of being opposed to the valve seat surface at a predetermined interval, and the rotary valve body is rotated as the flow control shape portion on one of the disk surfaces facing the first valve seat surface of the rotary valve body. A C-shaped arc-shaped first flow control concave groove is formed concentrically with the center, and another flow control shape portion is formed on the other disk surface of the rotary valve body facing the second valve seat surface. C-shaped arc-shaped second flow rate control groove is formed concentrically with the rotation center of the rotary valve body, and the first flow rate control groove and the second flow rate control groove are respectively A groove shape that changes the groove cross-sectional area for each position displaced in the arc direction, and The valve body is provided with a through hole that communicates the first flow rate control groove and the second flow rate control groove with each of the maximum groove cross-sectional areas, and the first valve seat surface For the first flow rate control determined by the first inlet / outlet port opened to the second valve, the second inlet / outlet port opened to the second valve seat surface, and the rotation angle of the rotary valve body The effective communication area between the first inlet / outlet port and the second inlet / outlet port is increased / decreased according to the positional relationship in the arc direction of each of the concave groove and the second groove for controlling flow rate. The flow rate of the fluid flowing between the inlet / outlet port and the second inlet / outlet port is controlled.

  The electric control valve according to the present invention is preferably provided on each of the disk surface facing the first valve seat surface of the rotary valve body and the disk surface facing the second valve seat surface of the rotary valve body. A pressure relief pocket is formed.

  In the electric control valve according to the present invention, the rotation of the output shaft of the electric motor is decelerated and transmitted to the rotary valve body by the reduction gear device, and the flow control shape part formed in the rotary valve responds to the rotation angle of the rotary valve body. The effective communication area between the first inlet / outlet port and the second inlet / outlet port is increased / decreased, and the flow rate of the fluid flowing between the first inlet / outlet port and the second inlet / outlet port is controlled. Fine and highly accurate flow rate control can be performed without requiring a large motor torque.

  One embodiment of an electric control valve according to the present invention will be described with reference to FIGS.

  The electric control valve has a valve housing 10 as shown in FIG. The valve housing 10 is formed with a first inlet / outlet port 11, a second inlet / outlet port 12, and joint connecting portions 15, 16 that connect the joints 13, 14 to these ports.

  The valve housing 10 is formed with a substantially semicircular valve chamber 20. Of the opposite side surfaces of the valve chamber 20, one side surface is a first valve seat surface 21 with the first inlet / outlet port 11 opened, and the other side surface is the second inlet / outlet port 12. The second valve seat surface 22 is opened. The first inlet / outlet port 11 and the second inlet / outlet port 12 open toward the valve chamber 20 at the same corresponding positions of the first valve seat surface 21 and the second valve seat surface 22. , Opposite each other with the valve chamber 20 in between.

  The valve chamber 20 has a rotary valve body 30 under a rotary valve body 30 formed with a thickness slightly smaller than a separation dimension (valve chamber width dimension) between the first valve seat surface 21 and the second valve seat surface 22 of the valve chamber 20. Half (substantially lower half) is housed.

  A valve rotation center shaft 18 is loosely inserted in the center through-hole 33 of the rotary valve body 30, and the valve rotation center shaft 18 includes an upper bearing member 17 fixed to the upper portion of the valve housing 10, the valve housing 10, and Thus, the rotary valve body 30 can be rotated around the valve rotation center axis 18 in the valve chamber 20.

  The rotary valve body 30 has one panel surface 30A facing the first valve seat surface 21 and the other panel surface 30B facing the second valve seat surface 22, and FIGS. As shown in b), a first flow control concave groove 31 having a C-shaped arc shape is formed on one panel surface 30A as a flow control shape portion concentrically with the rotation center of the rotary valve body 30. Yes. Further, as shown in FIGS. 10B and 10C, a C-shaped arc-shaped second concentric with the rotation center of the rotary valve body 30 is provided on the other panel surface 30B as another flow control shape portion. Two flow control concave grooves 32 are formed.

  As shown in FIGS. 5A and 5B, the first flow rate control groove 31 and the second flow rate control groove 32 have the same shape at the same position on the front and back of the rotary valve body 30. The arc radius of the same dimension as the deviation size of the first inlet / outlet flow port 11 and the second inlet / outlet port 12 with respect to the rotation center of the rotary valve body 30 is formed over a rotation angle range of 270 degrees. .

  The first flow control groove 31 and the second flow control groove 32 have maximum groove width portions (maximum groove cross-sectional area portions) 31A and 32A for obtaining a maximum flow rate at one end and a minimum flow rate at the other end. It has a minimum groove width portion (minimum groove cross-sectional area portion) 31B, 32B, and the groove width is from the maximum groove width portion 31A, 32A toward the minimum groove width portion 31B, 32B (clockwise as viewed from the panel surface 30A) Ii) Gradually and continuously decreasing. Thereby, the groove | channel cross-sectional area changes for every position where the 1st groove | channel 31 for flow control, and the 2nd groove | channel 32 for 2nd flow control have displaced in the circular arc direction.

  The rotary valve body 30 is formed with a through-hole 34 through which the first flow rate control groove 31 and the second flow rate control groove 32 communicate with each other at the maximum groove width portions 31A and 32A. Further, the portions of the disk surfaces 30A and 30B of the rotary valve body 30 that are displaced in the clockwise direction from the minimum groove width portions 31B and 32B as viewed on the disk surface 30A have no groove recesses and are completely closed with the disk surfaces 30A and 30B. Portions 31C and 32C are formed.

  On the disk surface 30B of the rotary valve body 30, a C-shaped arc-shaped stopper groove 35 is formed concentrically with the rotation center of the rotary valve body 30. The stopper groove 35 has a larger arc radius than the second flow rate control groove 32 and has a fully closed valve portion via the minimum groove width portion 32B rather than the maximum groove width portion 32A of the second flow rate control groove 32. It is formed over the same rotation angle range (about 315 degrees) as the rotation angle range reaching 32C.

  As shown in FIG. 1, a stopper pin (stopper protrusion) 19 that engages with a stopper groove 35 is integrally formed on the upper bearing member 17 fixed to the valve housing 10. The stopper pin 19 selectively contacts the one end 35A and the other end 35B in the arc direction of the stopper groove 35 shown in FIG. Is within 360 degrees (in this embodiment, 315 degrees which is the rotation angle range of the stopper groove 35), and the maximum valve closing position and the maximum valve opening position of the rotary valve body 20 are set by this restriction.

  That is, as shown in FIG. 8, when the stopper pin 19 comes into contact with the one end portion 35A of the stopper groove 35, the first flow control groove 31 as shown in FIG. The maximum groove width portion 31A and the maximum groove width portion 32A of the second flow control concave groove 32 are disposed at the rotational positions facing the first inlet / outlet port 11 and the second inlet / outlet port 12. The valve opening position is mechanically set in a door-to-door manner.

  On the contrary, as shown in FIG. 2, the stopper pin 19 abuts against the other end 35 </ b> B of the stopper groove 35, thereby causing the first pin as shown in FIG. 1. The fully closed valve portion 31C of the flow rate controlling groove 31 and the fully closed valve portion 32C of the second flow rate controlling groove 32 are opposed to the first inlet / outlet port 11 and the second inlet / outlet port 12, respectively. The maximum valve closing position (fully closed position) arranged at the rotational position is mechanically set to a door-to-door type.

  The rotary valve body 30 is formed with a bevel gear tooth portion 36 on an outer peripheral surface inclined at 45 degrees, and the rotary valve body 30 itself forms a driven side bevel gear.

  A hermetically sealed rotor case 41 of a stepping motor 40 that is an electric motor is airtightly attached to the upper portion of the valve housing 10. In the sealed rotor case 41, a rotor 42 whose outer peripheral portion is alternately magnetized with SN alternately is arranged in a state of being rotatably supported by the rotor shaft (motor output shaft) 43 from the upper bearing member 17 and the sealed rotor case 41. Has been. A cylindrical stator coil unit 44 having a multipolar tooth structure is detachably attached to the outside of the hermetic rotor case 41. In the drawing, the rotor shaft 43 is a vertical axis orthogonal to the valve rotation center shaft 18.

  A drive-side bevel gear 45 is mounted on the rotor shaft 43 in a torque transmission relationship. The drive side bevel gear 45 is formed with a bevel gear tooth portion 46 on an outer peripheral surface portion inclined at 45 degrees, and meshes with the tooth portion 36 of the rotary valve body 30. The ratio of the number of teeth of the rotary valve body 30 forming the driving side bevel gear 45 and the driven side bevel gear is set to about 1: 2 to 1: 3. As a result, the drive-side bevel gear 45 is a small bevel gear, the rotary valve body 30 that is a driven-side bevel gear is a large bevel gear, and the drive-side bevel gear 45 and the rotary valve body 30 that is a driven-side bevel gear are crossed axes. A reduction gear device using gears is configured.

  Next, the operation of the electric control valve configured as described above will be described in the case where the first inlet / outlet port 11 is on the high pressure side and the second inlet / outlet port 12 is on the low pressure side. When the first inlet / outlet port 11 is on the high pressure side and the second inlet / outlet port 12 is on the low pressure side, the disk surface 30B of the rotary valve body 30 is pressed against the second valve seat surface 22 due to the pressure difference. A minute gap t is formed between the opposite board surface 30A and the first valve seat surface 21 (see FIGS. 1, 3, and 7).

  As an example of the initial state, the fully closed state will be described first. As shown in FIG. 2, when the rotary valve body 30 is in the rotational position where the stopper pin 19 contacts the other end 35 </ b> B of the stopper groove 35, the rotation is performed as shown in FIG. 1. The fully closed valve portions 31C and 32C of the valve body 30 face the first inlet / outlet port 11 and the second inlet / outlet port 12, and the first inlet / outlet port 11 and the second inlet / outlet port 12 communicate with each other. Completely shut off and a fully closed state with zero flow is set.

  When the pulse signal for driving the valve opening is given to the stator coil unit 44 of the stepping motor 40 from the fully closed state described above, the rotor 42 rotates in the valve opening direction. The rotation of the rotor 42 is transmitted to the rotary valve body 30 by the meshing of the teeth 46 of the drive side bevel gear 45 and the teeth 36 of the rotary valve body 30 that forms the driven side bevel gear. When viewed from the side of the board surface 30A shown in (a), it rotates at a reduced speed in the counterclockwise direction.

  As a result, as shown in FIGS. 3 to 5A and 5B, the minimum groove width portion 31B and the maximum groove width portion 31A of the first flow control concave groove 31 of the rotary valve body 30 are provided. Or the intermediate portion between the minimum groove width portion 32B and the maximum groove width portion 32A of the second flow control concave groove 32 is opposed to the first input / output flow port 11 and the second input / output flow port 12. The fluid flows from the first inlet / outlet port 11 to the second inlet / outlet port 12 through the first flow control concave groove 31, the through hole 34, and the second flow control concave groove 32.

  The effective communication area between the first inlet / outlet port 11 and the second inlet / outlet port 12 at this time is shown in FIG. 6 at the portion facing the second inlet / outlet port 12. The groove cross-sectional area S (see FIG. 6) determined by the groove width and groove depth of the flow-control-use concave groove 32 and the first area which is not shown in FIG. The groove sectional area determined by the groove width and the groove sectional area determined by the groove depth and the groove depth of the first flow control concave groove 31 at the portion facing the inlet / outlet flow port 11 of the first flow control groove 11. The flow rate of the fluid flowing from the first inlet / outlet port 11 to the second inlet / outlet port 12 is metered and controlled using S and the groove cross-sectional area on the first flow rate control groove 31 (not shown).

  That is, the first flow control concave groove 31 and the second flow control concave groove 32 determined by the rotation angle of the rotary valve body 30 with respect to each of the first inlet / outlet port 11 and the second inlet / outlet port 12. The effective communication area between the first inlet / outlet port 11 and the second inlet / outlet port 12 increases or decreases depending on the positional relationship in the arc direction, and the second inlet / outlet flow from the first inlet / outlet port 11 accordingly. The flow rate of the fluid flowing to the port 12 is quantitatively controlled.

  Since the rotary valve body 30 is decelerated and rotated by the reduction gear device including the drive side bevel gear 45 and the rotary valve body 30 that forms the driven side bevel gear, the valve rotation resolution is reduced by the reduction ratio, that is, the stepping motor 40 The rotation angle of the rotary valve body 30 for each pulse is reduced, and fine flow rate control can be performed with high accuracy.

  Moreover, the motor torque can be reduced by reducing the rotational speed of the rotary valve body 30 regardless of the maximum operating pressure difference between the first inlet / outlet flow port 11 and the second inlet / outlet flow port 12. Thereby, size reduction of the stepping motor 40 and reduction of a motor output are achieved.

  Further, since the reduction gear device is of a cross-shaft gear type using bevel gears, the radial dimension of the reduction gear device (rotational radial dimension of the stepping motor 40) is smaller than that of a reduction gear device using a spur gear train. This makes it possible to reduce the size of the electric control valve. Thereby, the space required for installation of the electric control valve can be reduced.

  Further, since the driven bevel gear of the reduction gear device is integrally formed with the rotary valve body 30, that is, the rotary valve body 30 also serves as the driven bevel gear of the reduction gear device. The reduction gear device can be miniaturized, and the electric control valve can be further miniaturized. Thereby, the space required for installation of the electric control valve can be further reduced.

  By rotation of the rotary valve body 30, as shown in FIG. 7, the maximum groove width portions 31A and 32A of the first flow control concave groove 31 and the second flow control concave groove 32 of the rotary valve body 30 are provided. Is opposed to the first inlet / outlet port 11 and the second inlet / outlet port 12, a maximum valve open state is set in which a maximum flow rate of fluid flows from the first inlet / outlet port 11 to the second inlet / outlet port 12. .

  In this maximum valve open state, as shown in FIG. 8, the stopper pin 19 comes into contact with the one end portion 35 </ b> A of the stopper groove 35 in a door-to-door manner, and the maximum valve open position (rotation position) of the rotary valve body 30. ) Is reliably set with high precision in the mechanical type.

  The operation from the maximum valve open state to the fully closed state is performed in the same manner as during the valve opening operation by driving the stepping motor 40 in the valve closing direction. As shown in FIG. When 19 contacts the other end 35B of the stopper groove 35 in a door-to-door manner, the fully closed position (rotational position) of the rotary valve body 30 is reliably set mechanically with high accuracy.

  Each rotation position of the rotary valve body 30 during the opening / closing operation of the electric control valve described above is shown in FIGS. 11 to 16 each show an intermediate valve open state from a fully closed state to a fully open state. In this embodiment, the first flow rate control groove 31 and the second flow rate control groove 32 gradually and continuously change between the maximum groove width portions 31A and 32A and the minimum groove width portions 31B and 32B. 17, the proportional flow rate control characteristic is obtained in which the flow rate changes in a proportional relationship with respect to the pulse position of the stepping motor 40, in other words, the rotation angle of the rotary valve body 30, as shown in FIG. 17. .

  In FIG. 17, the pulse position A is the rotational position of the rotary valve body 30 shown in FIG. 2, the pulse positions B to G are the rotational position of the rotary valve body 30 shown in FIGS. It corresponds to the rotational position of the rotary valve body 30 shown.

  Incidentally, in contrast to what has been described above, when the second inlet / outlet port 12 is on the high pressure side and the first inlet / outlet port 11 is on the low pressure side, as shown in FIG. Due to the pressure difference, the disc surface 30A of the rotary valve body 30 is pressed against the first valve seat surface 21, and a minute gap t is created between the disc surface 30B opposite to the first valve seat surface 22 and the second valve seat surface 22. The flow direction is the same as that when the first inlet / outlet port 11 is on the high pressure side and the second inlet / outlet port 12 is on the low pressure side. The effect is obtained.

  Thereby, in the use of a heat pump type air conditioner or the like, even if the refrigerant flow direction is reversed during cooling operation and heating operation, the same flow rate control characteristics can be obtained and excellent bidirectionality is exhibited.

  The flow control characteristic of the electric control valve according to the present invention is such that the first flow control concave portion 32 is representatively shown in FIGS. 18 (a) and 18 (b). By setting the relative positional relationship in the rotational direction between the groove 31 and the second flow control concave groove 32 and the stopper concave groove 35, as shown in FIG. It is also possible to obtain a valve opening / closing characteristic that provides a fully closed state at both pulse positions.

  Further, as shown in FIGS. 19A and 19B, the second flow control groove 32 is representatively shown, the first flow control groove 31 and the second flow control groove 32. By changing the condition of the change in the groove width of 32, it is possible to obtain the flow control characteristic of the quadratic curve by the equal percentage as shown in FIG. 19 (c), and FIG. 20 (a), ( As shown in FIG. 21 (a) and FIG. 21 (b), the second flow rate control groove 32 is representatively shown, and the first flow rate control groove 31 and the second flow rate control groove 32 are shown. By giving a step to the change in the groove width of the groove 32, it is possible to obtain a flow rate control characteristic having an inflection point as shown in FIG. 20 (c) and FIG. 21 (c).

  18 to 21, (a) shows the most valve closed side state, (b) shows the most valve open side state, and in the characteristic diagram of (c), the pulse position A is (a). The rotation position and the pulse position H of the rotary valve body 30 in the most valve-closed state shown in FIG. 6 respectively correspond to the rotation position of the rotary valve body 30 in the most valve-opened state shown in FIG.

  Moreover, it is shown in FIGS. 23A to 23F which are sectional views taken along lines connecting the point O in FIG. 22 which is a plan view of the rotary valve body 30 viewed from the board surface 30B side and the respective positions A to F. As described above, the groove shape of the first flow rate control groove 31 and the second flow rate control groove 32 in which the groove cross-sectional area changes with the displacement in the arc direction is the groove depth regardless of the groove width change. You may change like d1-d6. Further, a change in groove width and a change in groove depth can be combined.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIGS. 24 and 25, parts corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1, and description thereof is omitted.

  In this embodiment, the rotary valve body 30 is provided on each of the disc surface 30A facing the first valve seat surface 21 of the rotary valve body 30 and the disc surface 30B where the rotary valve body 30 faces the second valve seat surface 22. A plurality of annular pressure relief pockets 37 and 38 are formed concentrically with the center of rotation.

  The plate thickness of the rotary valve body 30 is such that the first valve seat surface 21 and the second valve seat surface 22 of the valve chamber 20 are separated from each other so that the rotary valve body 30 can rotate in the valve chamber 20 (valve chamber width). Is slightly smaller than the dimension), between the panel surface 30A of the rotary valve body 30 and the first valve seat surface 21, and between the panel surface 30B of the rotary valve body 30 and the second valve seat surface 22. However, there are inevitable gaps Ta and Tb.

  For this reason, there is a gap flow that flows through the gaps Ta and Tb in addition to the regular metering flow that flows through the first flow rate control groove 31, the second flow rate control groove 32, and the through hole 34. This gap flow causes a decrease in flow rate control accuracy.

  On the other hand, by providing the pressure relaxation pockets 37 and 38, a pressure relaxation action is obtained, and the gap flow flowing through the gaps Ta and Tb is reduced. Thereby, the fall of the flow control accuracy by a gap flow can be stopped to the minimum.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. Also, in FIG. 26, the parts corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1, and the description thereof is omitted.

  In this embodiment, tooth portions 36A and 36B for bevel gears are formed on both sides of the outer peripheral portion of the rotary valve body 30, respectively, and the rotary valve body 30 is a double bevel gear on the driven side.

  For this reason, the board surface 30B of the rotary valve body 30 is pressed against the second valve seat surface 22 because the first inlet / outlet port 11 is on the high pressure side and the second inlet / outlet port 12 is on the low pressure side. In this case, the tooth portion 36B is not engaged with the tooth portion 46 of the driving side bevel gear 45, and the tooth portion 36A is engaged with the tooth portion 46 of the driving side bevel gear 45. On the other hand, because the second inlet / outlet port 12 is on the high pressure side and the first inlet / outlet port 11 is on the low pressure side, the disc surface 30A of the rotary valve body 30 is pressed against the first valve seat surface 21. In this case, the tooth portion 36A is not engaged with the tooth portion 46 of the driving side bevel gear 45, and the tooth portion 36B is engaged with the tooth portion 46 of the driving side bevel gear 45.

  Thereby, in any state, the meshing state between the driving side bevel gear 45 and the rotary valve body 30 forming the driven side bevel gear is maintained in an appropriate state.

  In the above-described embodiment, a reduction gear device using a bevel gear is used. However, the electric control valve according to the present invention is not limited to this, and as shown in FIG. It may be of the face gear type by meshing the tooth portion 48 of the attached drive side face gear 47 and the tooth portion 49 formed on the outer peripheral portion of the rotary valve body 30 forming the driven face gear.

  The reduction gear device may use a spur gear, a helical gear, a worm gear, a hypoid gear, or the like.

It is a longitudinal cross-sectional view which shows the fully closed state of one Embodiment of the electrically driven control valve by this invention. It is a front view of the rotary valve body which shows the fully closed state of the electrically driven control valve by one Embodiment. It is a longitudinal cross-sectional view which shows the intermediate valve open state of one Embodiment of the electrically driven control valve by this invention. (A) is a front view which shows one board surface of the rotary valve body of the intermediate valve open state of the electrically driven control valve by one Embodiment, (b) is a front view which similarly shows the other board surface. (A) is a perspective view which shows one board surface of the rotary valve body of the intermediate valve open state of the electrically driven control valve by one Embodiment, (b) is a perspective view which similarly shows the other board surface. It is a perspective view which shows the rotary valve body of the intermediate valve open state of the electrically driven control valve by one Embodiment. It is a longitudinal cross-sectional view which shows the fully open state of one Embodiment of the electrically driven control valve by this invention. It is a front view of the rotary valve body which shows the fully open state of the electrically driven control valve by one Embodiment. It is a longitudinal cross-sectional view which shows the fully open state at the time of the reverse flow of one Embodiment of the electrically driven control valve by this invention. (A) is the front view of one board surface of the electrically driven control valve by one Embodiment, (b) is the longitudinal cross-sectional view similarly, (c) is the front view of the other board surface similarly. FIG. 2 is a front view of a rotary valve body showing an intermediate valve open state of an electric control valve according to one embodiment. FIG. 2 is a front view of a rotary valve body showing an intermediate valve open state of an electric control valve according to one embodiment. FIG. 2 is a front view of a rotary valve body showing an intermediate valve open state of an electric control valve according to one embodiment. FIG. 2 is a front view of a rotary valve body showing an intermediate valve open state of an electric control valve according to one embodiment. FIG. 2 is a front view of a rotary valve body showing an intermediate valve open state of an electric control valve according to one embodiment. FIG. 2 is a front view of a rotary valve body showing an intermediate valve open state of an electric control valve according to one embodiment. It is a graph which shows the flow control characteristic of the electric control valve by one embodiment. (A) is a front view of a rotary valve body showing a maximum valve closed state of another embodiment of the electric control valve according to the present invention, and (b) is a fully open side of another embodiment of the electric control valve according to the present invention. The front view of the rotary valve body which shows a valve closed state, (c) is a graph which shows the flow control characteristic of the electrically driven control valve by this embodiment. (A) is a front view of a rotary valve body showing a maximum valve closed state of another embodiment of the electric control valve according to the present invention, and (b) is a maximum valve opening of another embodiment of the electric control valve according to the present invention. The front view of the rotary valve body which shows a state, (c) is a graph which shows the flow control characteristic of the electric control valve by this embodiment. (A) is a front view of a rotary valve body showing a maximum valve closed state of another embodiment of the electric control valve according to the present invention, and (b) is a maximum valve opening of another embodiment of the electric control valve according to the present invention. The front view of the rotary valve body which shows a state, (c) is a graph which shows the flow control characteristic of the electric control valve by this embodiment. (A) is a front view of a rotary valve body showing a maximum valve closed state of another embodiment of the electric control valve according to the present invention, and (b) is a maximum valve opening of another embodiment of the electric control valve according to the present invention. The front view of the rotary valve body which shows a state, (c) is a graph which shows the flow control characteristic of the electric control valve by this embodiment. It is a front view which shows the panel surface of the rotary valve body of other embodiment of the electrically driven control valve by this invention. 22A is a cross-sectional view taken along the line OA in FIG. 22, FIG. 22B is a cross-sectional view taken along the line OB in FIG. 22, FIG. 22C is a cross-sectional view taken along the line O-C in FIG. FIG. 22E is a cross-sectional view taken along the line OE in FIG. 22, and FIG. 22F is a cross-sectional view taken along the line FF in FIG. It is a longitudinal cross-sectional view which shows other embodiment of the electrically driven control valve by this invention. It is an expanded vertical sectional view of the principal part of the electrically driven control valve by other embodiment. It is a longitudinal cross-sectional view which shows other embodiment of the electrically driven control valve by this invention. It is a longitudinal cross-sectional view which shows other embodiment of the electrically driven control valve by this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Valve housing 11 1st inlet / outlet port 12 2nd inlet / outlet port 17 Upper bearing member 18 Valve rotation center axis | shaft 19 Stopper pin 20 Valve chamber 21 1st valve seat surface 22 2nd valve seat surface 30 Rotary valve body 31 First groove for controlling flow rate 32 Second groove for controlling flow rate 34 Through hole 35 Groove for stopper 36, 36A, 36B Teeth 37, 38 Pressure relief pocket 40 Stepping motor 42 Rotor 44 Stator coil unit 45 Drive side bevel gear 46 Tooth part 47 Drive side face gear 48, 49 Tooth part

Claims (7)

A valve housing having a first inlet / outlet port and a second inlet / outlet port;
The valve housing is rotatably provided, has a flow rate control shape portion, and effective between the first input / output flow port and the second input / output flow port by the flow rate control shape portion according to a rotation angle. A rotary valve body that increases or decreases the communication area and controls the flow rate of the fluid flowing between the first inlet / outlet port and the second inlet / outlet port;
An electric motor attached to the valve housing;
A reduction gear device that is provided between the output shaft of the electric motor and the rotary valve body and transmits the rotation of the output shaft to the rotary valve body at a reduced speed;
Electric control valve with   2. The reduction gear device includes a pair of input gear and output gear that mesh with each other, the input gear is drivingly connected to the output shaft, and the output gear is integrally formed with the rotary valve body. The electric control valve described.   3. The electric control valve according to claim 1, wherein the reduction gear device is a cross shaft gear.   The rotary valve body is formed with a C-shaped arc-shaped stopper concave groove concentrically with the rotational center of the rotary valve body, and the valve housing is provided with a stopper projection for engaging with the stopper concave groove, The stopper projection selectively contacts both ends in the arc direction of the concave groove for stopper, thereby restricting the rotation angle range of the rotary valve body to within 360 degrees, and by the restriction, the maximum valve of the rotary valve body is controlled. The electric control valve according to claim 1, wherein a closed position and a maximum valve open position are set. A valve seat surface in which the first inlet / outlet port or the second inlet / outlet port is opened is formed in the valve housing,
On the surface of the rotary valve body facing the valve seat surface, as the flow control shape portion, a C-shaped arc-shaped flow control concave groove is formed concentrically with the rotation center of the rotary valve body. The concave groove has a groove shape that changes the groove cross-sectional area for each position displaced in the arc direction,
The first inlet / outlet port or the second inlet / outlet port opened to the valve seat surface and the positional relationship in the arc direction of the concave groove for flow rate control determined by the rotation angle of the rotary valve body. The effective communication area between the first inlet / outlet port and the second inlet / outlet port is increased / decreased to control the flow rate of the fluid flowing between the first inlet / outlet port and the second inlet / outlet port. The electric control valve according to claim 1. In the valve housing, a first valve seat surface in which the first inlet / outlet port is opened and a second valve seat surface in which the second inlet / outlet port is opened are opposed to each other at a predetermined interval. Formed,
A first groove for flow rate control having a C-shaped arc concentric with the center of rotation of the rotary valve body as the flow rate control shape portion on one panel surface of the rotary valve body facing the first valve seat surface. Is formed on the other disc surface facing the second valve seat surface of the rotary valve body as another flow control shape portion, and a C-shaped arc-shaped second concentric with the rotation center of the rotary valve body. The first flow rate control groove and the second flow rate control groove each have a groove shape whose groove cross-sectional area changes at each position displaced in the arc direction. Have
Furthermore, the rotary valve body is formed with a through-hole that communicates the first groove for controlling flow rate and the second groove for controlling flow rate with each other at each maximum groove cross-sectional area portion,
It is determined by the first inlet / outlet port opened to the first valve seat surface, the second inlet / outlet port opened to the second valve seat surface, and the rotation angle of the rotary valve body. The effective communication area between the first inlet / outlet port and the second inlet / outlet port is determined by the positional relationship in the arc direction of each of the first groove for controlling flow rate and the second groove for controlling flow rate. The electric control valve according to claim 1, wherein the flow rate of the fluid flowing between the first inlet / outlet port and the second inlet / outlet port is controlled.   The pressure relaxation pocket is formed in each of the board surface facing the said 1st valve seat surface of the said rotary valve body, and the board surface facing the said 2nd valve seat surface of the said rotary valve body. Electric control valve.

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