JP4546751B2 - Rotating motorized valve - Google Patents

Description

  The present invention relates to a rotary motor-operated valve, and more particularly to a direct-acting rotary motor-operated valve.

  As a rotary electric valve, the rotor of an electric motor such as a stepping motor and the valve body are directly connected in a torque transmission relationship, and the valve body is driven to rotate by the electric motor, so that valve operations such as flow path switching and flow control are performed. A direct-acting rotary motor-operated valve that performs the above is known (for example, Patent Documents 1 and 2).

  In a direct-acting rotary motor-operated valve, the connection between the rotor and the valve body for torque transmission is the engagement between the concave portion formed in one of the rotor and the valve body and the convex portion formed in the other Is done.

  In the case of such a connection structure, an inevitable gap (in the case of a resin molded product, 0 in the rotational direction) is formed in the engaging portion between the concave portion and the convex portion integrally formed with the rotor and the valve body by resin molding. .About 0.05 mm), and when the rotor and the valve body rotate, a rattling noise is generated in the gap described above, which causes a large amount of noise during valve operation.

That is, if there is a gap in the rotational direction at the engaging part between the concave part and the convex part, when the rotational direction of the rotor is reversed, the convex part and the concave part are relatively displaced in the rotational direction by the gap, and the concave part and the convex part Collision occurs at the opposite surface portion to produce a collision sound. In addition, even when rotating in one direction, with a rotational drive by a stepping motor, if viewed from a microscopic viewpoint, damping is performed one pulse at a time (the operation of returning to the reverse direction after overshoot is repeated several times to the target value) Since it is moving while being converged, a rattling sound is produced.
JP 2002-122366 A JP 2001-187777 A

  The problem to be solved by the present invention is to avoid the generation of rattling noise caused by the gap in the rotational direction existing in the engaging portion between the concave portion and the convex portion for torque transmission between the rotor and the valve body, It is to improve the quietness during valve operation.

  A rotary electric valve according to the present invention has a valve body directly connected in a torque transmission relationship with a rotor of an electric motor, and the rotary electric valve performs valve operation when the valve body is rotationally driven by the electric motor. In connection, the connection between the rotor and the valve body for torque transmission is performed by engagement of a concave portion formed in one of the rotor and the valve body and a convex portion formed in the other, One of the side surfaces of the convex portion in the rotational direction of the rotor and the valve body facing each other in the engaged state of the concave portion and the convex portion and the corresponding inner side surface of the concave portion are opposed to each other. An elastic member is provided between the side surface and the inner side surface to relatively bias the valve body and the rotor in the rotational direction in a direction in which the other side surface and the inner side surface facing each other are in close contact with each other. Has been

  The valve operation referred to here is a rotation operation of a valve body for flow rate control including flow path switching such as a three-way valve and a four-way valve or a variable throttle operation.

The rotary type electric valve according to the present invention, prior Symbol elastic member is given a preload compressive deformation are those wherein the spring member disposed between the side surface and the inner surface of one face each other.

The rotary type electric valve according to the present invention, prior Symbol spring member, and the rotor and the ring-shaped portion for positioning fitted to a hub portion formed on the center of rotation concentric to any one of the valve body, wherein An extending portion extending in a radial direction from the ring-shaped portion; and a spring piece bent at a distal end of the extending portion, wherein the spring piece has one of the side surface and the inner side surface facing each other. It is sandwiched between them with a preload for compression deformation.

  The rotary electric valve according to the present invention further includes the hub portion of the spring member in the direction of the rotation axis of the rotor and the valve body on either one of the side surface and the inner side surface facing each other. An overhanging stopper portion for preventing the spring piece from being formed is formed, and the compression deformation of the spring piece is limited by the stopper portion.

  The rotary electric valve according to the present invention is one of the side surfaces of the convex portion in the rotation direction of the rotor and the valve body and the corresponding inner side surfaces of the concave portion, which are opposed in the engaged state between the concave portion and the convex portion. The valve member, the concave portion and the convex portion of the rotor are relatively biased in the rotational direction by an elastic member such as a spring provided between the side surface and the inner side surface facing each other, and the other side surface and inner side surface facing each other. Adhere to each other.

  As a result, a gap like a backlash is maintained between the one side surface and the inner side surface that are opposed to each other even when the direction of rotation is reversed, so that no rattling noise is generated and quietness during valve operation is improved. The

  A motor-driven valve according to Embodiment 1 of the present invention will be described with reference to FIGS. The electric valve of Embodiment 1 is an electric switching valve.

  As shown in FIG. 1, the electric switching valve 10 includes a disk-shaped bottom lid member 11 that is a stationary member, and a can-like case 12 that is airtightly welded onto the bottom lid member 11. is doing. The case 12 cooperates with the bottom lid member 11 to form a valve chamber 13 having an airtight chamber structure inside.

  As shown in FIG. 4, through holes 11B, 11C, and 11D for inserting pipe joints are punched and formed in required portions (three locations) of the bottom cover member 11, respectively. The through holes 11C and 11D are at positions separated by a predetermined rotation angle on the same arc line concentric with the central axis. One end portions of the pipe joints 14, 15, and 16 are inserted into the through holes 11B, 11C, and 11D, respectively. The pipe joints 14, 15, and 16 are each fixed to the bottom lid member 11 by brazing with a ring braze, and extend outside (downward) the bottom lid member 11.

  As shown in FIG. 1, an intermediate plate (base plate) 17 is fixed to the upper surface portion of the bottom cover member 11 by brazing. A shaft support hole 17F is punched and formed in the center of the intermediate plate 17. On the lower surface side of the intermediate plate 17, there is an annular protrusion 17A formed around the shaft support hole 17F by burring when the shaft support hole 17F is punched, as shown in FIG. Is fitted in a central recess 11E embossed at the center of the bottom lid member 11.

  The central recess 11E of the bottom cover member 11 has a sufficient depth D, acts as a brazing material reservoir, and prevents the brazing material from flowing into the shaft support hole 17F. Further, the central recess 11E also functions as a relief for variation in the axial length of the central shaft 21 described later.

  The intermediate plate 17 and the bottom lid member 11 are brazed by brazing the pipe joints 14, 15, and 16 to the bottom lid member 11 by the ring brazing described above. This brazing will be described with reference to FIG. When brazing the intermediate plate 17 to the bottom lid member 11 and the pipe joints 14, 15, 16, the direction of the intermediate plate 17, the bottom lid member 11, the pipe joints 14, 15, 16 in the brazed set state is reversed (pipe joints 14, 15, 16 are facing upward), and the ring braze 29 is passed through each of the pipe joints 14, 15, 16, and each ring braze 29 is disposed at a position in contact with the bottom lid member 11. In order to maintain this state, the parts are fixed by a jig (not shown) and brazed in the furnace.

  In the furnace, the ring braze 29 melts and the melted braze flows through the gaps between the through holes 11B, 11C, 11D of the bottom lid member 11 and the pipe joints 14, 15, 16 and the bottom lid member 11 and the intermediate plate. The contact surface (joint surface) with 17 penetrates in the outer peripheral direction and the center direction by capillary action. When brazing has penetrated to the center side, even if brazing is performed under the same conditions, there are cases where the brazing portion (the central concave portion 11E) of the bottom lid member 11 flows out and does not flow out due to variations such as subtle temperature changes. Arise.

  The brazing reservoir portion of the bottom cover member 11 is formed for the purpose of preventing the brazing from flowing into the shaft support hole (shaft hole) 17F of the intermediate plate 17. However, the brazing reservoir portion is too large due to part size and processing restrictions. The part cannot be formed. For this reason, if there is a large amount of brazing into the brazing reservoir due to brazing variation, brazing will flow up to the shaft support hole 17F of the intermediate plate 17, and the center shaft 21 may not be normally inserted into the shaft support hole 17F. There is.

  In contrast, in this embodiment, the burring portion of the intermediate plate 17, that is, the digging groove 17 </ b> H (see FIG. 2) is formed around the outer periphery of the annular convex portion 17 </ b> A, thereby weakening the penetration of the capillary phenomenon. At the same time, since it also functions as a wax pool, it prevents the wax from flowing to the wax pool portion of the bottom cover member 11 and reliably prevents the wax from flowing into the shaft support hole 17F of the intermediate plate 17.

  The intermediate plate 17 is formed with a notch 17C that opens the through hole (inlet port) 11B to the valve chamber 13. The intermediate plate 17 is formed with communication openings (communication openings) 17D and 17E communicating with the through holes (exit ports) 11C and 11D, respectively. Each of the communication openings 17D and 17E is formed by a long hole having substantially the same longitudinal dimension as the diameter of the corresponding through hole 11C and 11D, as well shown in FIG. Hereinafter, the through hole 11B may be referred to as A port, the through hole 11C as B port, and the through hole 11D as C port.

  As shown in FIG. 2, a lower end of a later-described center shaft 21 is fitted into a shaft support hole 17 </ b> F punched and formed at the center of the intermediate plate 17.

  As shown in FIG. 4, the intermediate plate 17 is formed with a base-pointing stopper piece 17 </ b> G that bends a protruding piece 20 </ b> F of a valve body 20 described later. A rubber buffering O-ring 18 having a refrigerant resistance such as HNBR is attached to the stopper piece 17G so as to surround the stopper piece 17G.

  A valve seat (valve seat member) 19 is attached to the upper surface of the intermediate plate 17. In the valve seat 19, valve ports 19 </ b> C and 19 </ b> D communicating with the communication openings 17 </ b> D and 17 </ b> E of the intermediate plate 17 and a central hole 19 </ b> E through which the central shaft 21 passes are formed. The valve seat 19 is provided with a notch 19F that opens the through hole (inlet port) 11B to the valve chamber 13 in the same manner as the notch 17C of the intermediate plate 17. The valve seat 19 is joined to the intermediate plate 17 by adhesion / sealant, brazing, soldering, thermocompression bonding, welding, or the like.

  The valve ports 19C and 19D are at positions separated by a predetermined rotation angle on the same arc line concentric with the center axis of the center hole 19E through which the center shaft 21 passes.

  To summarize the bottom structure of the valve chamber 13, the bottom of the valve chamber 13 includes a bottom cover member 11 to which pipe joints 14, 15 and 16 are connected, and valve ports 19 C and 19 D, as well shown in FIG. Is opened and the end face (lower bottom surface 20A, see FIG. 9) of the valve body 20 is slidably in contact with the valve seat sheet 19, the bottom cover member 11 and the valve seat sheet 19, and the pipe joints 15 and 16 and the valve port 19C. It is configured by a three-layer laminated structure including an intermediate plate 17 having communication openings 17D and 17E, which are communication openings that communicate with 19D.

  The valve ports 19 </ b> C and 19 </ b> D are biased toward the rotation center side of the valve body 20 from the center position of the pipe joints 15 and 16. The intermediate plate 17 having long hole-like communication openings 17D and 17E communicates the valve ports 19C and 19D with the pipe joints 15 and 16.

  The upper surface of the valve seat 19 in the valve chamber 13 is a valve seat surface 19G, and the valve body 20 is disposed on the valve seat surface 19G. The valve body 20 is an integrally molded product made of a resin material considering sliding and refrigerant resistance. The valve body 20 is in sliding contact with the valve seat surface 19G of the valve seat 19 at the lower bottom surface 20A and passes through the center hole 20D. , The center of rotation is set, guided by the center axis 21 and rotated around the center axis, and the flow path switching and opening / closing control of the A port, B port, and C port are performed.

  As shown in FIG. 4, the valve body 20 is integrally formed with two projecting pieces 20 </ b> F and 20 </ b> G projecting radially outward at a small interval in the circumferential direction. The two projecting pieces 20F and 20G define a recess 28 between them for connecting the valve body 20 and a rotor 31 of a stepping motor 30 described later in a torque transmission relationship. A protruding piece (convex portion) 39 integrally formed with the rotor 31 is engaged with the concave portion 28. By this engagement, the rotor 31 and the valve body 20 are connected in a torque transmission relationship, and the valve body 20 is rotationally driven by the stepping motor 30 about the central shaft 21 as a rotation center.

  The two projecting pieces 20F and 20G of the valve body 20 and the projecting piece 39 of the rotor 31 are made such that the lateral width (rotational direction width) Wa of the recess 28 is larger than the lateral width Wb of the projecting piece 39 in the same direction ( A leaf spring structure 40 that constitutes an elastic member is provided at the engaging portion between the recess 28 and the protruding piece 39.

  As shown in FIGS. 7 to 10, the leaf spring structure 40 is formed by pressing a spring material of stainless steel or copper alloy, and the valve body 20 has a rotation center of the valve body 20 and A ring-shaped portion 40A that is positioned and fitted to the hub portion 20K formed concentrically, an extended portion 40B that extends in the radial direction from the ring-shaped portion 40A, and a spring that is bent at the tip of the extended portion 40B As shown in FIG. 10, the spring piece 40 </ b> C has an inner side surface 28 </ b> A of one of the two protruding pieces 20 </ b> F and 20 </ b> G constituting the recess 28, and the rotor 31. Between the side surfaces 39A and 39B of the projecting piece 39 and the side surface 39A facing the inner surface 28A of the projecting piece 20G in the rotational direction of the rotor 31 and the valve body 20, a preload for compressive deformation is applied and sandwiched. Yes.

  Thus, the spring piece 40C is located between one inner side surface 28A of the concave portion 28 and one side surface 39A of the protruding piece 39, and the valve body 20 and the rotor 31 are connected to the other inner side surface 28B of the concave portion 28 and the protruding piece. The other side surface 39B of 39 is urged in the direction in which they are brought into close contact with each other. By this urging (spring force), the other inner side surface 28B of the recess 28 and the other side surface 39B of the protruding piece 39 are always in close contact. As shown in FIG. 7, the spring piece 40C is formed with a bent upper piece 40D that is joined to the upper surface of the protruding piece 20G.

  Guide piece portions 20H and 20J are integrally formed at the upper part of the base side of the protruding pieces 20F and 20G of the valve body 20. The guide pieces 20H and 20J guide the engagement of the protruding piece 39 of the rotor 31 shown in FIG. 4 between the protruding pieces 20F and 20G of the valve body 20 when the rotor 31 is assembled to the valve body 20. To do. In other words, the protruding piece 39 is prevented from coming off between the protruding pieces 20F and 20G.

  As shown in FIG. 7, an overhang-like stopper portion 20L is formed on the guide piece portion 20J. As shown in FIG. 8, the stopper portion 20L is engaged with the upper end 40E of the spring piece 40C of the leaf spring structure 40 in a state where the ring-like portion 40A is positioned and fitted to the hub portion 20K of the valve body 20. The structure 40 is prevented from coming off in the axial direction, and at the same time, the compression deformation of the spring piece 40C is limited. That is, the leaf spring structure 40 moves in the axial direction in the valve body 20 by the engagement between the bent upper piece 40D and the upper surface of the protruding piece 20G and the upper edge 40E of the spring piece 40C and the stopper portion 20L. It is stopped and attached.

  As shown in FIG. 10, the lateral width Wc of the stopper portion 20L and the opposing surface 28B in the rotational direction is larger than the lateral width Wb of the protruding piece 39 in the same direction and smaller than the lateral width Wa of the concave portion 28 in the same direction. Thus, the compression deformation of the spring piece 40C is limited, and the excessive deformation of the spring piece 40C is prevented.

  As shown in FIG. 2, the center shaft 21 is rotatably supported by the intermediate plate 17 at its lower end by fitting with the shaft support hole 17F. As shown in FIG. 1, the upper end of the central shaft 21 is rotatably fitted in a bearing hole 22 </ b> A of the bearing member 22. The bearing member 22 is made of a highly slippery resin material, and is engaged with the bearing engaging recess 12C of the case 12 by the upper center protrusion 22B. Thereby, the central shaft 21 is supported so that the upper end can rotate from the case 12.

  A rotor 31 of a stepping motor 30 is rotatably provided in the valve chamber 13. The rotor 31 is a plastic magnet having a multi-pole magnetized outer peripheral portion 31B. As described above, the rotor 31 is connected in a torque transmission relationship with the valve body 20 by the protruding piece 39, and rotationally drives the valve body 20.

  As shown in FIG. 4, the boss portion 31C of the rotor 31 is formed with a through hole 31D through which the central shaft 21 passes, and the rib-shaped portion 31E connecting the outer peripheral portion 31B and the boss portion 31C communicates with pressure equalization. A hole 31F is provided.

  Between the lower end of the boss portion 31 </ b> C of the rotor 31 and the upper surface portion of the valve body 20, a holding spring 23 by a compression coil spring is sandwiched. The holding spring 23 presses the lower bottom surface 20A (see FIGS. 9 and 10) of the valve body 20 against the valve seat surface 19G (see FIGS. 5 and 6) to ensure the stability of the valve seal in a low differential pressure state. . At the same time, the holding spring 23 urges the rotor 31 and the bearing member 22 upward, and presses the upper center protrusion 22B of the bearing member 22 against the bearing engaging recess 12C of the case 12.

  As shown in FIG. 1, the stator assembly 32 of the stepping motor 30 is positioned and fixed to the outer periphery of the case 12. The stator assembly 32 includes upper and lower two-stage stator coils 33, a plurality of magnetic pole teeth 34, an electrical connector portion 35, and the like, and is liquid-tightly sealed with a sealing resin 36. The stepping motor 30 drives the valve body 20 to be divided and rotated by energization control (pulse control) to the stator coil 33.

  The valve body 20 is configured to open both valve ports 19C and 19D to the valve chamber 13 by split rotation driving by the stepping motor 30, and the A port (inlet port) communicates with the two outlet ports (B port and C port). 1 switching position (0 pulse = base point position), a second switching position where the valve port 19D is closed, only the valve port 19C is opened to the valve chamber 13, and the A port (inlet port) communicates only with the B port ( 18 pulse), the valve ports 19C and 19D are closed together, the A port (inlet port) is not connected to any outlet port, the third switching position (36 pulses = fully closed position), and the valve port 19C is closed. Only the valve port 19D is opened to the valve chamber 13, and the switching operation is performed between the A port (inlet port) and the fourth switching position (54 pulses) communicating only with the C port to obtain 4 positions.

  If a more detailed explanation is required for this switching operation, refer to the specification and drawings of Japanese Patent Application No. 2003-37315 by the same applicant as the present applicant.

  In the switching operation (valve operation) described above, even if the rotation direction of the rotor 31 is reversed or the stepping motor 30 is damped one pulse at a time, one of the inner surface 28A of the recess 28 and one of the protruding pieces 39 The other inner side surface 28B of the recess 28 and the other side surface 39B of the projecting piece 39 are brought into close contact with each other by the spring force of the spring piece 40C sandwiched between the side surface 39A and a preload of compression deformation. The valve body 20 and the rotor 31 are urged to each other, and by this urging, the other inner side surface 28B of the concave portion 28 and the other side surface 39B of the protruding piece 39 are always in close contact with each other. No noise is generated in the gap between the two and the quietness during valve operation is improved.

  A motor-driven valve according to a second embodiment of the present invention will be described with reference to FIGS. 11 and 12, portions corresponding to those in FIGS. 1 to 10 are denoted by the same reference numerals as those in FIGS. 1 to 10, and description thereof is omitted.

  As shown in FIG. 11, the electric switching valve 10 according to the second embodiment includes pipe joints at required portions (two locations) of the bottom cover member 111 instead of the bottom cover member 11 of the motor operated valve according to the first embodiment. Through holes 111B and 111C for insertion are formed by punching. One end portions of pipe joints 114 and 115 are inserted into the through holes 111B and 111C, respectively. The pipe joints 114 and 115 are each fixed to the bottom lid member 111 by brazing with a ring brazing and extend outward (downward) from the bottom lid member 111.

  As shown in FIG. 12, an intermediate plate 117 is fixed to the upper surface portion of the bottom cover member 111 by brazing. The intermediate plate 117 is formed with a notch 117C that opens the through hole (inlet port) 111B to the valve chamber 13. The intermediate plate 117 has a communication opening (not shown) communicating with the through hole (exit port) 111C. This communication opening is formed as a long hole having a dimension in the longitudinal direction substantially the same as the diameter of the through hole 111C. As with the intermediate plate 17 of the first embodiment, the intermediate plate 117 is also formed with a bent-out stopper piece 117G with which the protruding piece 20F of the valve body 20 abuts, and the stopper piece 117G has a bent shape. A rubber buffering O-ring 18 having a refrigerant resistance such as HNBR is attached so as to surround the stopper piece 117G.

  A valve seat (valve seat member) 119 is attached to the upper surface of the intermediate plate 117. In the valve seat 119, a fully open port 119C communicating with a communication opening (not shown) of the intermediate plate 117 and a center hole 119E through which the center shaft 21 passes are formed by etching. A concave groove 116 for variably setting the throttle flow rate is formed in the valve seat surface 119G of the valve seat 119 by half etching or the like. The concave groove 116 extends in an arc shape in the same direction as the rotation direction of the valve body 20, that is, extends in a rotation angle range of about 270 degrees around the central axis, and has a uniform depth and a groove in the extending direction. The width is gradually changed. The concave groove 116 communicates with the fully opened port 119C at the maximum width portion (groove width maximum side) at one end, and the groove width gradually decreases as it proceeds in the clockwise direction in the figure, and the other end becomes the minimum width portion. ing.

  Of the valve seat surface 119G, the central portion where the lower bottom surface 20A of the valve body 20 is actually opposed has a concave groove 116 formed by half etching or the like, leaving a contour demarcating portion 116C demarcating the contour of the concave groove 116 in a band shape having a predetermined width. It becomes the hollow 119H of the depth equivalent to. As a result, the contour defining portion 116C that defines the contour of the concave groove 116 becomes a belt-like protrusion.

  The valve seat 119 is formed with a notch 119F that opens the through hole (inlet port) 111B to the valve chamber 13 in the same manner as the notch 117C of the intermediate plate 117.

  The upper surface of the valve seat 119 in the valve chamber 13 is a valve seat surface 119G, and the valve body 20 is disposed on the valve seat surface 119G. The valve body 20 is an integrally molded product made of a resin material considering sliding and refrigerant resistance, and a central shaft 21 that is in sliding contact with the valve seat surface 119G of the valve seat 119 at the lower bottom surface 20A and penetrates the central hole 20D. , The center of rotation is set, and the valve body 20 is guided in the center axis 21 to close the entire groove 116 and the fully open port 119C (0 pulse = base position), and the valve body 20 is counterclockwise from the fully closed position. Rotate between the control range (10 to 54 pulses) for quantitatively determining the throttle flow rate by the concave groove 116 according to the rotation position and the fully open position (64 pulses) for opening the fully open port 119C, Perform flow control and open / close control.

  If a more detailed explanation is necessary for the operation of the flow rate control, refer to the specification and drawings of Japanese Patent Application No. 2003-37314 by the same applicant as the present applicant.

  Also in the second embodiment, as in the first embodiment, the valve body 20 is integrally formed with two protruding pieces 20F and 20G protruding outward in the radial direction at a small interval in the circumferential direction. The two projecting pieces 20F and 20G define a recess 28 between them for connecting the valve body 20 and a rotor 31 of a stepping motor 30 described later in a torque transmission relationship. A protruding piece (convex portion) 39 integrally formed with the rotor 31 is engaged with the concave portion 28. By this engagement, the rotor 31 and the valve body 20 are connected in a torque transmission relationship, and the valve body 20 is rotationally driven by the stepping motor 30 about the central shaft 21 as a rotation center.

  The two projecting pieces 20F and 20G of the valve body 20 and the projecting piece 39 of the rotor 31 are made such that the lateral width (rotational direction width) Wa of the recess 28 is larger than the lateral width Wb of the projecting piece 39 in the same direction ( A leaf spring structure 40 that constitutes an elastic member is provided at the engaging portion between the recess 28 and the protruding piece 39.

  The leaf spring structure 40 is the same as that of the first embodiment, and is formed by pressing a spring material of stainless steel or copper alloy as shown in FIGS. A ring-shaped portion 40A that is positioned and fitted to a hub portion 20K formed concentrically with the rotation center of the valve body 20, an extended portion 40B that extends in the radial direction from the ring-shaped portion 40A, and the extended portion 40B The spring piece 40C is bent at the tip, and the spring piece 40C is, as shown in FIG. 10, one of the two protruding pieces 20G of the two protruding pieces 20F and 20G constituting the recess 28. Preload of compression deformation between the side surface 28A and the side surface 39A of the both side surfaces 39A, 39B of the protruding piece 39 of the rotor 31 that faces the inner side surface 28A of the protruding piece 20G in the rotational direction of the rotor 31 and the valve body 20 Given and pinched To have.

  Thus, the spring piece 40C is located between one inner side surface 28A of the concave portion 28 and one side surface 39A of the protruding piece 39, and the valve body 20 and the rotor 31 are connected to the other inner side surface 28B of the concave portion 28 and the protruding piece. The other side surfaces 39B of 39 are biased to each other in a direction in which they are brought into close contact with each other. By this urging (spring force), the other inner side surface 28B of the recess 28 and the other side surface 39B of the protruding piece 39 are always in close contact. As shown in FIG. 7, the spring piece 40C is formed with a bent upper piece 40D that is joined to the upper surface of the protruding piece 20G.

  Guide piece portions 20H and 20J are integrally formed at the upper part of the base side of the protruding pieces 20F and 20G of the valve body 20. The guide pieces 20H and 20J guide the engagement of the protruding piece 39 of the rotor 31 shown in FIG. 4 between the protruding pieces 20F and 20G of the valve body 20 when the rotor 31 is assembled to the valve body 20. To do. In other words, the protruding piece 39 is prevented from coming off between the protruding pieces 20F and 20G.

  Also in the second embodiment, as shown in FIG. 7, the guide piece 20J is formed with an overhanging stopper 20L. The stopper portion 20L is engaged with the upper end 40E of the spring piece 40C of the leaf spring structure 40 in a state where the ring-like portion 40A is positioned and fitted to the hub portion 20K of the valve body 20, and the axial direction of the leaf spring structure 40 In addition, the compression deformation of the spring piece 40C is limited. That is, the leaf spring structure 40 moves in the axial direction in the valve body 20 by the engagement between the bent upper piece 40D and the upper surface of the protruding piece 20G and the upper edge 40E of the spring piece 40C and the stopper portion 20L. It is stopped and attached.

  Also in the second embodiment, as shown in FIG. 10, the lateral width Wc of the stopper portion 20L and the facing surface 28B in the rotational direction is larger than the lateral width Wb of the protruding piece 39 in the same direction, and By being smaller than the lateral width Wa in the same direction, compression deformation of the spring piece 40C is limited, and excessive deformation of the spring piece 40C is prevented.

  Therefore, even in the second embodiment, in the switching operation (valve operation) described above, even if the rotation direction of the rotor 31 is reversed or the stepping motor 30 is damped one pulse at a time, one inner surface of the recess 28 The other inner side surface 28B of the recess 28 and the other side surface of the projecting piece 39 are caused by the spring force of the spring piece 40C sandwiched between 28A and one side surface 39A of the projecting piece 39 by applying a preload for compressive deformation. The valve body 20 and the rotor 31 are urged to each other in the direction in which 39B is in close contact with each other, and by this urging, the other inner side surface 28B of the recess 28 and the other side surface 39B of the protruding piece 39 are always in close contact. No collision noise is generated in the gap between the recess 28 and the protruding piece 39, and the quietness during the valve operation is improved.

  In any of the above-described embodiments, the concave portion 28 is provided on the rotor 31 side, and the protruding piece 39 is provided on the valve body 20 side. In this case, the plate is the same as in the above-described embodiment. By providing the spring structure 40, operations and effects equivalent to those of the above-described embodiment can be obtained.

It is sectional drawing which shows Embodiment 1 of the motor operated valve by this invention. It is a partial expanded sectional view of FIG. It is sectional drawing which shows the brazing operation state of the bottom cover member of the motor operated valve of Embodiment 1, an intermediate plate, and a pipe joint. FIG. 3 is an exploded perspective view of a main part of the electric valve according to the first embodiment. FIG. 3 is an enlarged plan view showing an arrangement relationship between a through hole and a valve port of the electric valve according to the first embodiment. FIG. 3 is an enlarged cross-sectional view showing the positional relationship between the through hole and the valve port of the electric valve according to the first embodiment. (A) is an expansion perspective view which shows one embodiment of the spring member used for the motor operated valve by this invention, (b) is an expansion perspective view which similarly shows one embodiment of the valve body. It is an expansion perspective view of the principal part (valve body with which the spring member was equipped) of the motor operated valve by this invention. It is a B arrow view of FIG. It is an enlarged view of the principal part (engagement part of the valve body with which the spring member was mounted | worn, and a rotor) of the motor operated valve by this invention. It is sectional drawing which shows Embodiment 2 of the motor operated valve by this invention. It is a disassembled perspective view of the principal part of the motor operated valve of Embodiment 2.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Electric switching valve 11, 111 Bottom cover member 12 Case 14, 15, 16, 114, 115 Pipe joint 17, 117 Intermediate plate 19, 119 Valve seat 20 Valve body 20F, 20G Protruding piece 20K Hub part 20L Stopper part 21 Central shaft 23 Pressing spring 28 Recessed portion 30 Stepping motor 31 Rotor 32 Stator assembly 39 Projection piece 40 Leaf spring structure 40A Ring-shaped portion 40C Spring piece

Claims (2)

In a rotary electric valve having a valve body directly connected in a torque transmission relationship with a rotor of an electric motor, and performing valve operation by the valve body being rotationally driven by the electric motor,
Connection between the rotor and the valve body for torque transmission is performed by engagement of a concave portion formed in one of the rotor and the valve body and a convex portion formed in the other,
One of the side surfaces of the convex portion in the rotational direction of the rotor and the valve body facing each other in the engaged state of the concave portion and the convex portion and the corresponding inner side surface of the concave portion are opposed to each other. An elastic member is provided between the side surface and the inner side surface to relatively bias the valve body and the rotor in the rotational direction in a direction in which the other side surface and the inner side surface facing each other are in close contact with each other. It is,
The elastic member, Ri said side surfaces and a spring member der disposed between the inner surface opposite to each other in one and preloaded compressive deformation,
The spring member includes a ring-shaped portion that is positioned and fitted to a hub portion formed concentrically with the rotation center of one of the rotor and the valve body, and an extension that extends in the radial direction from the ring-shaped portion. And a spring piece that is bent at the tip of the extension part, and the spring piece is sandwiched by applying a preload of compressive deformation between the one side surface and the inner side surface facing each other. rotary type electric valve that it is characterized in that it is. An overhang-like stopper portion for preventing the spring member from coming off from the hub portion in the rotational axis direction of the rotor and the valve body is provided on one of the side surface and the inner side surface facing each other. The rotary electric valve according to claim 1 , wherein the rotary electric valve is formed, and the compression deformation of the spring piece is limited by the stopper portion.

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