JP2019132393A - Motor-operated valve and refrigeration cycle system - Google Patents

Abstract

To provide a motor-operated valve and a refrigeration cycle system capable of properly controlling a flow rate in a small flow rate region, in the motor-operated valve having the flow rate control regions of two stages.SOLUTION: A motor-operated valve 10 includes a main valve element 2, an auxiliary valve element 3, and a driving portion 4, and has flow rate control regions of two stages, that is, a small flow rate control region in which the auxiliary valve element 3 changes an opening of an auxiliary valve port 22, and a large flow rate control region in which the main valve element 2 opens and closes a main valve port 1c. The auxiliary valve element 3 has an auxiliary valve element 31 disposed on its outer peripheral face for changing an opening of an auxiliary valve port 22, and a thrust washer 34 disposed on a tip side with respect to the auxiliary valve port 31. At least one of the main valve element 2 and the auxiliary valve element 3 is provided with a through flow channel 35 as a bypass flow channel R' reaching a tip end portion of the auxiliary valve element 3 while bypassing a contact face of a locked portion 23 and the thrust washer 34.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an electric valve and a refrigeration cycle system.

  Conventionally, as a motor-operated valve provided in a refrigeration cycle of an air conditioner, a sub-flow body is driven back and forth in an axial direction by an electric motor, and a small flow rate control region for controlling a flow rate at a sub-valve port of the main valve body, and a valve chamber Has been proposed which has a two-stage flow rate control region, that is, a large flow rate control region that performs flow control by opening and closing the main valve port of the main valve port (for example, see Patent Document 1).

  The electric valve (electric flow control valve) described in Patent Document 1 includes a main valve element (valve element) that opens and closes a main valve port (valve hole) of a valve chamber, and a main valve element that urges the main valve element in a closing direction. A valve spring (first spring), a sub-valve element that opens and closes a sub-valve port (sub-valve hole) formed in the main valve element, and a sub-valve spring (second spring) that biases the sub-valve element in the closing direction And a drive unit having an electric motor (motor) for driving the auxiliary valve body. In this electric valve, the main valve body biased by the main valve spring sits and closes the main valve port, and the sub valve body biased by the sub valve spring sits and closes the sub valve port, Fully closed state. Further, the auxiliary valve body is pulled up by the drive unit, so that the auxiliary valve port is opened, whereby the small flow rate control is performed. Further, the main valve port is opened when the latched portion (first stopper) of the sub-valve that has been pulled up engages the main valve and the main valve is pulled up, whereby large flow control is performed.

JP 2014-20457 A

  However, in the conventional motor-operated valve described in Patent Document 1, the auxiliary valve port is formed in a long cylindrical shape along the axis, and a long rod-like auxiliary valve body is loosely inserted into the auxiliary valve port. In the small flow rate control, the gap between the inner peripheral surface of the sub valve port and the outer peripheral surface of the sub valve body is a refrigerant flow path. Since the fluid passes through such a long and narrow flow path, in the conventional motor-operated valve, foreign matter flows into the flow path and bites between the sub valve port and the sub valve body, resulting in malfunction of the sub valve body. This may cause problems in the flow control during small flow control.

  An object of the present invention is to provide a motor-operated valve that can appropriately control a flow rate in a small flow rate control region in a motor-operated valve having a two-stage flow rate control region.

  The motor-operated valve of the present invention includes a main valve element that opens and closes a main valve port of a valve chamber, a sub-valve element that makes the opening degree of the sub-valve port provided in the main valve element variable, and the auxiliary valve element that has an axis line A small flow rate control region in which the sub valve body changes the opening degree of the sub valve port, and a large flow rate control region in which the main valve body opens and closes the main valve port. In the small flow rate control region, the sub-valve element has the first position closest to the sub-valve port and the driving force of the driving unit. The secondary valve port is moved in the opening direction to move to a second position that engages with the main valve body, and the main valve body is seated on the main valve port in the large flow rate control region. The main valve port moves together with the sub-valve body moved to the second position by the closed position and the driving force of the drive unit. The main valve body is connected to the sub-valve port on the inner peripheral surface formed in an overall cylindrical shape, and to the main valve port side more than the sub-valve port. And the auxiliary valve body is formed in an overall columnar shape and disposed inside the main valve body, and is provided on the outer peripheral surface of the auxiliary valve body to open the auxiliary valve port. A sub-valve portion that changes the degree of engagement, and a locking portion that is provided on the distal end side of the sub-valve portion and can lock the locked portion, and the main valve body and the sub-valve body At least one of them is characterized in that a bypass flow path that bypasses the contact surface between the locked portion and the locking portion and reaches the tip of the sub-valve element is formed.

  According to the present invention as described above, the sub-valve disposed inside the main valve body has the sub-valve portion and the locking portion, and the locked portion is provided in at least one of the main valve body and the sub-valve body. By forming a bypass flow path that bypasses the contact surface between the valve and the locking portion and reaches the tip of the sub-valve, the fluid at the time of small flow control passes through the bypass flow path and bites foreign matter. Can be prevented. Accordingly, the malfunction of the sub-valve is less likely to occur, and the flow rate in the small flow rate control region can be appropriately controlled. In addition, by providing a bypass flow path, fluid does not pass through the gap between the locking portion of the sub-valve element and the inner peripheral surface of the main valve element, so that this gap can be set small. The locking portion of the valve body and the inner peripheral surface of the main valve body can function as a sliding guide portion that slides and guides each other. As a result, when the sub-valve element moves forward and backward, it is guided to the inner peripheral surface of the main valve element, and when the main valve element moves forward and backward, it is guided to the locking portion of the sub-valve element, The vibration of the body and the auxiliary valve body can be suppressed, and the accuracy of the flow rate control can be improved.

  In this case, the bypass flow path includes a through-flow path that penetrates from a side surface between the sub valve portion and the locking portion to a tip portion of the sub valve body, and an outer periphery including the locking portion of the sub valve body. It is preferable that the main valve body is constituted by at least one of a sub-valve notch portion having a notched surface and a main valve notch portion having an inner peripheral surface of the main valve body notched.

  If the bypass flow path is constituted by a through-flow path, the sliding contact surface where the inner peripheral surface of the main valve body and the outer peripheral surface of the sub-valve element are in sliding contact with each other can be continued all around, and the sliding resistance is constant. Thus, the forward and backward movement of the main valve body and the sub valve body can be further stabilized. Further, if the bypass flow path is constituted by the sub valve notch part or the main valve notch part, the processing becomes simpler and the manufacturing cost can be suppressed as compared with the case where the through flow path is formed.

  At this time, the drive unit includes a screw feeding mechanism having a male screw part integrally connected to the sub-valve body and a female screw part that is screwed into and guided by the male screw part, and drives the drive part. Thus, it is preferable that the auxiliary valve body is driven forward and backward along the axial direction by rotating and guiding the male screw portion to the female screw portion.

  According to this configuration, the sub-valve element can be directly driven by the drive unit by the male screw part integrally connected to the sub-valve element being guided by the female screw part and the sub-valve element being driven forward and backward. In addition, it is possible to improve the accuracy of the flow rate control in the small flow rate control region by suppressing the rattling of the auxiliary valve body.

  Furthermore, it is preferable that the locking portion, the sub valve portion, and the male screw portion are formed so that the diameters are reduced in this order.

  According to this configuration, the locking portion is provided at the distal end portion of the auxiliary valve body, the locking portion is larger in diameter than the auxiliary valve portion and the male screw portion, and the auxiliary valve portion is larger in diameter than the male screw portion. Therefore, the sub-valve body can be assembled so as to be inserted from the male screw portion side into the entire cylindrical main valve body, and the manufacturing efficiency of the electric valve can be improved.

  The valve body further comprises a valve main body, a support member fixed to the valve main body, and a main valve spring that biases the main valve body in a closing direction, and the support member includes the female screw. A resin receiving member having a spring receiving portion that holds the main valve spring in a compressed state and a main valve guide portion that advances and retracts the main valve body in the axial direction between the main valve body and the main valve body It is preferable that it is comprised.

  According to this configuration, the support member fixed to the valve body has the female thread portion, the spring receiving portion, and the main valve guide portion, and the main valve body is guided to advance and retract in the axial direction by the main valve guide portion. The vibration of the valve body can be suppressed, and valve leakage can be prevented by reliably seating on the main valve port. Accordingly, it is possible to appropriately control the flow rate in the small flow rate control region by reducing the influence on the flow rate during the small flow rate control with the sub valve port opened. Moreover, since the support member is made of a resin molded member, wear of the support member and the main valve body can be suppressed, and the durability of the motor-operated valve can be improved.

  The refrigeration cycle system of the present invention is a refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, and any one of the motor-operated valves is used as the expansion valve. It is characterized by.

  According to such a refrigeration cycle system, similarly to the effect of the motor-operated valve described above, the operation of the sub-valve element is less likely to occur by preventing the foreign valve from being caught in the sub-valve port, and the motor-operated valve is used as an expansion valve. The flow rate at the time of small flow rate control in the used refrigeration cycle system can be appropriately controlled.

  According to the motor-operated valve and the refrigeration cycle system of the present invention, in the motor-operated valve having a two-stage flow control region, the flow rate in the small flow control region can be appropriately controlled.

It is a longitudinal cross-sectional view which shows the fully closed state in the motor operated valve of embodiment of this invention. It is a longitudinal cross-sectional view which shows the fully open state in the said motor operated valve. (A), (B) is a longitudinal cross-sectional view which expands and shows a part of said motor operated valve. It is a graph which shows the relationship between the valve opening degree and flow volume in the said motor operated valve. It is a schematic block diagram which shows the refrigerating cycle system of this invention. (A), (B) is the longitudinal cross-sectional view and bottom view which expand and show a part of motor-driven valve of the modification of this invention. (A), (B) is the longitudinal cross-sectional view and bottom view which expand and show a part of motor-driven valve of the other modification of this invention.

  An electric valve according to an embodiment of the present invention will be described with reference to FIGS. As shown in FIGS. 1 and 2, the motor-operated valve 10 of the present embodiment includes a valve housing 1, a main valve body 2, a sub-valve body 3, and a drive unit 4. The concept of “upper and lower” in the following description corresponds to the upper and lower sides in the drawings of FIGS.

  The valve housing 1 has a cylindrical valve body 1a, which is made of brass (made of brass), and a cylindrical valve chamber 1A is formed therein. A primary joint pipe 11 that is connected to the valve chamber 1A from the side surface and into which the refrigerant flows is attached to the valve body 1a, and a secondary joint pipe 12 that is connected to the valve chamber 1A from the bottom side and through which the refrigerant flows out. It is attached. Further, the valve body 1a is formed with a main valve seat 1b at a position where the valve chamber 1A and the secondary joint pipe 12 communicate with each other, and the cross-sectional shape is circular from the main valve seat 1b to the secondary joint pipe 12 side. The main valve port 1c is formed. A support member 13 and a case 15 are fixed to the upper opening of the valve body 1a.

  The support member 13 is a resin molded member formed in a substantially cylindrical shape as a whole, and is fixed to the valve housing 1 via a metal fixing member 14 welded to the upper opening of the valve body 1a. The support member 13 includes a cylindrical main valve guide portion 13a extending downward from the fixing member 14, a female screw portion 13b extending upward from the fixing member 14 and having a female screw formed therein, and a cylindrical inner upper end. And a spring receiving portion 13c provided. The resin material constituting the support member 13 may be any resin material having appropriate hardness and heat resistance, and various engineering plastics can be used. The case 15 is fixed to the upper opening of the valve body 1a by welding or the like, and an airtight space is formed by the valve body 1a and the case 15.

  The main valve body 2 is a stainless steel member formed in a substantially cylindrical shape as a whole, and is supported inside the main valve guide portion 13a of the support member 13 so as to be movable back and forth along the axis L. The main valve body 2 includes a main valve portion 21 that is seated and separated from the main valve seat 1 b, an annular sub-valve port 22 that projects from a cylindrical inner peripheral surface, and a main valve that is more than the sub-valve port 22. It has the to-be-latched part 23 formed in the inner peripheral surface of the port 1c side (lower side) in the shape of a step, and the spring receiving part 24 provided in the upper end part. A sub-valve chamber 2 </ b> A is configured by the internal space above the sub-valve port 22 of the main valve body 2 and the internal space of the support member 13. A through hole 25 is formed in the side surface of the main valve body 2, and the valve chamber 1 </ b> A and the sub valve chamber 2 </ b> A are communicated with each other through the through hole 25. A main valve spring 26 is disposed in a compressed state between the support member 13 and the spring receiving portions 13c, 24 of the main valve body 2, and the main valve body 2 causes the main valve seat 1b to be compressed by the main valve spring 26. It is biased in the direction (closed direction).

  The sub-valve element 3 is a stainless steel member formed in a substantially cylindrical shape as a whole, and is disposed inside the main valve element 2 and integrated with a lower end portion of a rotor shaft (valve shaft) 50 of the drive unit 4 described later. And is driven forward / backward and rotationally by the drive unit 4. The auxiliary valve body 3 includes an auxiliary valve portion 31 provided on the outer peripheral surface thereof for changing the opening degree of the auxiliary valve port 22, and a small diameter portion having a smaller diameter on the distal end side (lower side) than the auxiliary valve portion 31. 32, and a flange portion 33 provided at the tip of the small diameter portion 32 and having a larger diameter than the sub valve portion 31. A thrust washer 34 is provided on the upper side of the flange portion 33. The thrust washer 34 is made of a metal washer having a highly slippery surface, a washer made of highly slippery resin such as fluororesin, or a washer coded with a slippery resin. Is a locking portion capable of locking the locked portion 23 of the main valve body 2. The thrust washer 34 can be brought into contact with the upper surface of the flange portion 33 and the locked portion 23, and the frictional force between the contact surfaces becomes extremely small. Between the side surface of the small-diameter portion 32 between the sub valve portion 31 and the flange portion 33 and the lower surface of the flange portion 33 that is the tip portion of the sub valve body 3, there is a through flow that penetrates the sub valve body 3. A path 35 is provided.

  The drive unit 4 includes a stepping motor 41 as an electric motor, a screw feed mechanism 42 that advances and retracts the sub-valve body 3 by rotation of the stepping motor 41, and a stopper mechanism 43 that restricts rotation of the stepping motor 41.

  The stepping motor 41 includes a magnet rotor 44 whose outer periphery is magnetized in multiple poles, a stator coil 45 disposed on the outer periphery of the case 15, and a rotor shaft 50 that is fixed to the magnet rotor 44 and extends in the axis L direction. It is equipped with. In the stepping motor 41, when a pulse signal is given to the stator coil 45, the magnet rotor 44 is rotated according to the number of pulses.

  The rotor shaft 50 is a long rod-like member fixed to the magnet rotor 44 via a fixing member 50a, and is integrated with the sub-valve element 3 by cutting or rolling a metal material such as stainless steel. Is formed. A male screw portion 50b is formed integrally with the intermediate portion of the rotor shaft 50, and the male screw portion 52b is screwed into the female screw portion 13b of the support member 13, thereby constituting the screw feed mechanism 42. The upper end portion of the rotor shaft 50 is inserted into the guide 46 of the stopper mechanism 43 and is guided in the direction of the axis L. In the integrally formed rotor shaft 50 and auxiliary valve body 3, the diameters of the flange portion 33 and the thrust washer 34, the auxiliary valve portion 31, and the male screw portion 52b become smaller in order, that is, the outer diameter of the thrust washer 34. Is the largest, the outer diameter of the flange portion 33 is next, the outer diameter of the sub-valve portion 31 is next smaller, and the outer diameter of the male screw portion 52b is the smallest.

  When the magnet rotor 44 and the rotor shaft 50 of the drive unit 4 are rotated, the male screw portion 50b is guided by the female screw portion 13b, and the magnet rotor 44 and the rotor shaft 50 are moved in the axis L direction according to the screw pitch. Here, the magnet rotor 44 and the rotor shaft 50 are lowered along with the forward rotation, and the sub-valve element 3 is also lowered along with the lowering. On the other hand, the magnet rotor 44 and the rotor shaft 50 rise with the reverse rotation, and the sub-valve element 3 also rises with this rise.

  The stopper mechanism 43 includes a cylindrical rod-shaped guide 46 suspended from the ceiling of the case 15, a guide screw 47 fixed to the outer periphery of the guide 46, and a movable slider 48 that is guided by the guide screw 47 and can be rotated and moved up and down. And. The movable slider 48 is provided with a claw portion 48a that protrudes radially outward, and the magnet rotor 44 is provided with an extension portion 44a that extends upward and comes into contact with the claw portion 48a, and extends when the magnet rotor 44 rotates. When the portion 44 a pushes the claw portion 48 a, the movable slider 48 rotates and moves up and down following the guide screw 47.

  The guide screw 47 is formed with an upper end stopper 47 a that defines the uppermost position of the magnet rotor 44 and a lower end stopper 47 b that defines the lowermost position of the magnet rotor 44. When the movable slider 48 lowered with the normal rotation of the magnet rotor 44 comes into contact with the lower end stopper 47b, the movable slider 48 cannot rotate at the contacted position, thereby restricting the rotation of the magnet rotor 44 and the subvalve. The descending of the body 3 is also stopped. On the other hand, when the movable slider 48 raised with the reverse rotation of the magnet rotor 44 comes into contact with the upper end stopper 47a, the movable slider 48 becomes unable to rotate at this contacted position, thereby restricting the rotation of the magnet rotor 44, The raising of the auxiliary valve body 3 is also stopped.

  Next, the detailed structure and operation of the motor-operated valve 10 will be described with reference to FIGS. 3 (A) and 3 (B) are longitudinal sectional views showing a part of the motor-operated valve 10 in an enlarged manner, and are longitudinal sectional views showing the distal end portions of the main valve body 2 and the sub-valve body 3 in an enlarged manner. is there. FIG. 4 is a graph showing the relationship between the valve opening and the flow rate in the electric valve 10.

  As shown in FIG. 3, the sub-valve part 31 of the sub-valve element 3 includes a columnar column part 31a, and a truncated cone-shaped cone part 31b whose diameter gradually decreases from the cylinder part 31a toward the tip. , Are formed. The diameter of the cylindrical part 31a is smaller than the inner diameter of the sub valve port 22 of the main valve body 2, and the refrigerant passes through the gap between the outer peripheral surface of the cylindrical part 31a and the conical part 31b and the inner peripheral surface of the sub valve port 22. A flow path R is formed. FIG. 3A shows a position where the cylindrical portion 31 a is located inside the auxiliary valve port 22 corresponding to the lowermost position of the magnet rotor 44, that is, the auxiliary valve body in the first position closest to the auxiliary valve port 22. 3 is shown. FIG. 3B shows a position where the sub-valve element 3 is raised from the first position by the rotation of the magnet rotor 44 and the thrust washer 34 is in contact with the locked portion 23, that is, engaged with the main valve element 2. The secondary valve body 3 in the second position is shown. As the auxiliary valve body 3 rises from the first position toward the second position, the conical portion 31b comes to be located inside the auxiliary valve port 22, and the opening degree of the auxiliary valve port 22 gradually increases. The flow rate of the refrigerant passing through the flow path R increases.

  The above motor operated valve 10 operates as follows. First, in the state of FIG.1 and FIG.3 (A), the main valve part 21 of the main valve body 2 is seated on the main valve seat 1b, and is the valve closed state by which the main valve port 1c was closed. On the other hand, in the auxiliary valve body 3 in the first position, the cylindrical portion 31a is located inside the auxiliary valve port 22, and a flow path R is formed in the gap. Therefore, the refrigerant that flows into the valve chamber 1A from the primary joint pipe 11 and further flows into the sub valve chamber 2A from the through hole 25 flows into the main valve body 2 from the flow path R through the sub valve port 22, It flows out to the front end side of the sub-valve body 3 through the through flow path 35 of the sub-valve body 3, and flows out from the main valve port 1 c toward the secondary joint pipe 12. That is, the bypass passage R ′ that bypasses the contact surface between the thrust washer 34 and the locked portion 23 is configured by the through passage 35 of the sub-valve element 3. As described above, when the refrigerant passes through the flow path R and the bypass flow path R ', a minute flow rate is generated even when the valve opening degree is zero, as shown in FIG.

  Next, the stepping motor 41 of the drive unit 4 is driven to reversely rotate the magnet rotor 44 to raise the subvalve body 3 so that the conical portion 31 b of the subvalve body 3 is positioned inside the subvalve port 22. Thus, the flow path R is formed in the gap. Here, since the diameter of the conical portion 31b is gradually reduced, the gap with the inner peripheral surface of the auxiliary valve port 22 is increased, and the flow path R is enlarged. As shown in FIG. 4, the flow rate is gradually increased. To increase. At this time, since the main valve portion 21 of the main valve body 2 remains seated on the main valve seat 1b, the flow rate increases little until the second position where the sub valve body 3 engages with the main valve body 2. is there. Thus, the control region in which the sub-valve element 3 is moved between the first position and the second position to change the opening degree is the small flow control region, and the sub-valve element 3 is opened in the small flow control region. The change in the flow rate with respect to the degree (the rotation amount of the stepping motor 41) is extremely small.

  Next, when the sub-valve element 3 which is raised to the second position and engaged with the main valve element 2 is further raised, the main valve element 2 is driven by the sub-valve element 3 as shown in FIGS. 2 and 3B. Is pulled up, and the main valve portion 21 is opened away from the main valve seat 1b. Thus, the control region for raising the main valve body 2 from the seating position (closed position) toward the valve open position (open position) is the large flow rate control region, and the main valve body 2 is opened in this large flow rate control region. The change in the flow rate with respect to the degree (the amount of rotation of the stepping motor 41) becomes large. And in the fully open state which raised the main valve body 2 to the valve open position shown in FIG.2 and FIG.3 (B), a flow volume becomes the maximum. Here, as the flow rate in the fully opened state, the opening area of the gap between the main valve portion 21 and the main valve seat 1b is equal to or larger than the opening area of the primary joint pipe 11 and the secondary joint pipe 12, and the main valve portion 21 and The opening is set such that the flow rate is not throttled by the main valve port 1c, that is, the motor-operated valve 10 functions as a simple flow path. Further, by driving the stepping motor 41 of the drive unit 4 to rotate the magnet rotor 44 forward and lowering the sub-valve body 3, the main valve body 2 biased by the main valve spring 26 is also lowered, and the main valve body 2 is lowered. The valve portion 21 is seated on the main valve seat 1b, the main valve port 1c is closed, and a small flow rate control region is established.

  According to the above-described embodiment, the sub-valve element 3 disposed inside the main valve element 2 has the through-flow path 35, and the front end of the sub-valve element 3 passes through the through-flow path 35 during small flow control. When the refrigerant flows to the side, foreign matter can be prevented from being caught between the main valve body 2 and the sub-valve body 3. Accordingly, the malfunction of the sub valve body 3 is less likely to occur, and the flow rate in the small flow rate control region can be appropriately controlled.

  In addition, since the through channel 35 is provided, the refrigerant does not pass through the gap between the thrust washer 34 that is the locking portion of the sub-valve element 3 and the inner peripheral surface of the main valve element 2, so this gap is set small. Thus, the thrust washer 34 and the inner peripheral surface of the main valve body 2 can function as a sliding guide portion that slides and guides each other. Furthermore, by configuring the bypass flow path R ′ with the through flow path 35, the slidable contact surface where the inner peripheral surface of the main valve body 2 and the outer peripheral surface of the sub-valve element 3 are in slidable contact with each other can be continued all around. it can. Thereby, when the subvalve element 3 moves forward and backward, it is guided to the inner peripheral surface of the main valve element 2, so that the subvalve element 3 can be prevented from swinging, and the accuracy of flow control can be improved. Further, even when the main valve body 2 is seated on the main valve seat 1b, the vibration is restricted by the thrust washer 34, so that the valve closing performance can be improved and the valve leakage amount can be reduced.

  Further, the male threaded portion 50b of the rotor shaft 50 that is integrally connected to the subsidiary valve body 3 is guided by the female threaded portion 13b, and the subsidiary valve body 3 is driven forward and backward, so that the subsidiary valve body 3 is directly moved by the drive unit 4. Therefore, it is possible to improve the accuracy of the flow control in the small flow control region by suppressing the backlash of the sub valve body 3.

  In addition, a thrust washer 34 that is a locking portion is provided at the distal end of the sub-valve body 3, and the thrust washer 34, the sub-valve portion 31, and the male screw portion 52b are formed so that the diameter becomes smaller in order, The sub-valve element 3 can be assembled to the cylindrical main valve element 2 by inserting the male screw part 52b, the sub-valve part 31, the thrust washer 34 and the flange part 33 in this order from the upper end side of the rotor shaft 50. The manufacturing efficiency of the electric valve 10 can be improved.

  The support member 13 fixed to the valve body 1 has a main valve guide portion 13a, a female screw portion 13b, and a spring receiving portion 13c. The main valve guide portion 13a guides the main valve body 2 to advance and retreat in the direction of the axis L. Thus, the swing of the main valve body 2 can be suppressed, and valve leakage can be prevented by reliably seating on the main valve seat 1b. Therefore, the influence on the flow rate at the time of the small flow rate control with the sub valve port 22 opened can be reduced, and the flow rate in the small flow rate control region can be controlled appropriately. Moreover, since the support member 13 is comprised by the resin molding member, abrasion of the support member 13 and the main valve body 2 can be suppressed, and durability of the motor operated valve 10 can be improved.

  Further, since the flow path R is formed by the gap between the outer peripheral surface of the cylindrical portion 31a of the sub-valve element 3 in the first position and the inner peripheral surface of the main valve body 2, the flow rate is always secured by the flow path R. The valve-opening type motor-operated valve 10 can be configured. By using such a valve-open type electric valve 10, it can be suitably used for an air conditioner having a dehumidifying function such as a home air conditioner. Furthermore, since the flow path R is formed by the gap between the outer peripheral surface of the cylindrical portion 31a and the inner peripheral surface of the main valve body 2, the opening area of the flow path R can be strictly defined, and the first position A small flow rate when the sub-valve element 3 is present can be appropriately secured.

  Next, the refrigeration cycle system of the present invention will be described based on FIG. The refrigeration cycle system 90 is used in an air conditioner such as a home air conditioner, for example. The motor-operated valve 10 of the embodiment is between the first indoor heat exchanger 91 (acting as a dehumidifying cooler) and the second indoor heat exchanger 92 (acting as a dehumidifying heater) of the air conditioner. The heat pump refrigeration cycle is configured together with the compressor 93, the four-way valve 94, the outdoor heat exchanger 95, and the electronic expansion valve 96. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the electric valve 10 are installed indoors, and the compressor 93, the four-way valve 94, the outdoor heat exchanger 95, and the electronic expansion valve 96 are installed outdoor. It constitutes an air conditioning unit.

  In addition, this invention is not limited to the said embodiment, Including other structures etc. which can achieve the objective of this invention, the deformation | transformation etc. which are shown below are also contained in this invention. For example, in the above-described embodiment, the electric valve 10 used in an air conditioner such as a home air conditioner is illustrated. However, the electric valve of the present invention is not limited to a home air conditioner, and may be a commercial air conditioner. The present invention can be applied not only to air conditioners but also to various refrigerators.

  Moreover, in the said embodiment, although the screw feed mechanism 42 was comprised by the external thread part 50b of the rotor shaft 50, and the internal thread part 13b of the supporting member 13, the structure of the screw feed mechanism which drives the subvalve body 3 forward / backward is described above. Not only the embodiment but also any configuration can be adopted. Furthermore, the mechanism for driving the auxiliary valve element back and forth is not limited to the screw feed mechanism, and an appropriate mechanism can be applied.

  In the above embodiment, the stopper mechanism 43 is constituted by the guide 46, the guide screw 47, and the movable slider 48 provided on the ceiling portion of the case 15. However, as the stopper mechanism, the rotation of the magnet rotor 44 can be restricted. There is no particular limitation on the arrangement position and structure thereof. For example, a stopper mechanism may be provided inside or below the magnet rotor.

  In the above embodiment, the bypass flow path R ′ is constituted by the through flow path 35, but as shown in FIGS. 6 and 7, the bypass flow path R ′ is formed by the auxiliary valve notch 36 or the main valve notch. The through-flow channel 35, the sub-valve notch 36, and the main valve notch 37 may be appropriately combined. Specifically, as shown in FIG. 6, the auxiliary valve notch 36 is formed as a D-cut surface in which a part of the outer peripheral surface is cut from the small diameter portion 32 to the flange portion 33 of the auxiliary valve body 3. . Therefore, the bypass flow path R ′ is provided so as to pass from the small diameter portion 32 to the inside of the thrust washer 34. On the other hand, as shown in FIG. 7, the bypass flow path R ′ is formed by cutting out a part of the inner peripheral surface from the locked portion 23 of the main valve body 2 to the main valve portion 21. Accordingly, the bypass flow path R ′ is provided so as to pass from the small diameter portion 32 of the auxiliary valve body 3 to the outside of the thrust washer 34 and the outside of the flange portion 33.

  As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention.

DESCRIPTION OF SYMBOLS 10 Electric valve 1d Main valve port 2 Main valve body 3 Sub valve body 4 Drive part 13 Support member 13a Main valve guide part 13b Female thread part 13c Spring receiving part 22 Sub valve port 23 Locked part 26 Main valve spring 31 Sub valve part 34 Thrust washer (locking part)
35 Through passage 36 Sub valve notch 37 Main valve notch 42 Screw feed mechanism 50b Male thread 91 First indoor heat exchanger 92 Second indoor heat exchanger 93 Compressor 95 Outdoor heat exchanger R ' Detour channel

Claims (6)

A main valve body that opens and closes a main valve port of the valve chamber, a sub-valve body that makes the opening degree of the sub-valve port provided in the main valve body variable, and a drive unit that drives the sub-valve body to advance and retreat in the axial direction Two-stage flow rate control: a small flow rate control region in which the sub valve body changes the opening degree of the sub valve port, and a large flow rate control region in which the main valve body opens and closes the main valve port A motor-operated valve having a region,
In the small flow rate control region, the sub-valve element is moved in the first position closest to the sub-valve port and in the opening direction to open the sub-valve port by the driving force of the driving unit and is moved to the main valve element. Move between the second position to engage,
In the large flow rate control region, the main valve body moves integrally with the closed position seated on the main valve port and the sub-valve body moved to the second position by the driving force of the driving unit. Move between the open position to open the main valve port,
The main valve body is provided with the sub-valve port on the inner peripheral surface formed in an overall cylindrical shape, and a locked portion closer to the main valve port than the sub-valve port,
The sub-valve element is formed in an overall columnar shape and disposed inside the main valve element, and is provided on the outer peripheral surface of the sub-valve element to change the opening of the sub-valve port; A locking portion that is provided on the tip side of the auxiliary valve portion and can lock the locked portion,
At least one of the main valve body and the sub-valve body is formed with a bypass flow path that bypasses the contact surface between the locked portion and the locking portion and reaches the tip of the sub-valve body. An electrically operated valve characterized by that. The bypass channel is
A through-flow path that penetrates from the side surface between the sub-valve part and the locking part to the tip of the sub-valve element,
A sub-valve notch portion in which an outer peripheral surface including the locking portion of the sub-valve body is cut out, and
2. The motor-operated valve according to claim 1, wherein the motor-operated valve is configured by at least one of main valve notches formed by notching an inner peripheral surface of the main valve body. The drive unit includes a screw feed mechanism having a male screw part integrally connected to the sub-valve body, and a female screw part guided by screwing into the male screw part,
3. The motor-operated valve according to claim 1, wherein the sub-valve body is driven to advance and retract along the axial direction by rotating and guiding the male screw portion to the female screw portion by driving the driving portion. .   The motor-operated valve according to claim 3, wherein the locking portion, the auxiliary valve portion, and the male screw portion are formed so that the diameters are reduced in this order. A valve main body constituting the valve chamber; a support member fixed to the valve main body; and a main valve spring for biasing the main valve body in a closing direction,
The support member includes a spring receiving portion that holds the main valve spring in a compressed state between the female screw portion and the main valve body, and a main valve guide portion that guides the main valve body to advance and retreat in the axial direction. The motor-operated valve according to claim 3, wherein the motor-operated valve is formed of a resin molded member. A refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator,
The refrigeration cycle system, wherein the motor-operated valve according to any one of claims 1 to 5 is used as the expansion valve.

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