Electric valve and refrigeration cycle system using the same

Abstract

The present application provides an electric valve having a driving shaft with a radial movement suppression member that can achieve low operating noise, and a refrigeration cycle system using the electric valve. The electric valve (100a) has a support member (20) that moves a driving shaft (30) in the axial direction (L) by a thread feed mechanism portion that converts rotational motion into linear motion by thread coupling of an external thread portion (31a) and an internal thread portion (23a), and a bearing portion (24) that guides the driving shaft (30) in the axial direction (L) by engaging with a guide portion (32) of the driving shaft (30); a valve core (42) that is connected to the guide portion (32) of the driving shaft, and adjusts the opening of a valve port (11a) and a valve seat; and a radial movement suppression member (70a) that applies force to one of the external thread portion and the internal thread portion in the direction orthogonal to the axis, and suppresses the relative radial movement of the external thread portion and the internal thread portion. Thus, the problem of collision in the thread feed mechanism portion can be eliminated, and low operating noise can be achieved.

Description

Technical Field

[0001] The present invention relates to an electric valve having a radial movement inhibition member with a drive shaft, and a refrigeration circulation system using the electric valve. Background Technology

[0002] In the existing electric valve 1500, such as Figure 15 As shown in (a), a first connector pipe 1501 communicating with the valve chamber 1512 is installed on the side of the valve body 1510. A second connector pipe 1502 and a valve seat component 1511 are installed at the lower end of the valve body 1510, and a valve port 1511a centered on the axis L is formed on the valve seat component 1511. Furthermore, a support component 1520 is installed on the upper part of the valve body 1510, and an internal thread portion 1523a is formed on the support component 1520. Furthermore, a drive shaft 1530 connected to the magnetic rotor 1562 of the stepper motor 1560 is threaded into the internal thread portion 1523a by the external thread portion 1531a. In addition, a valve core portion 1540 is installed at the lower part of the drive shaft 1530. Furthermore, the valve core 1540 moves along the axis L together with the drive shaft 1530 via the threaded feed mechanism of the external threaded portion 1531a and the internal threaded portion 1523a formed by the rotation of the drive shaft 1530, thereby opening and closing the valve port 1511a.

[0003] Due to its structure, the thread feed mechanism is located in the axial L direction and the radial direction (see reference) between the internal thread portion 1523a and the external thread portion 1531a. Figure 15(b) has a tiny gap (hereinafter referred to as "thread loosening"). Therefore, when adjusting the opening of the valve port 1511a, the external thread portion 1531a of the drive shaft 1530 fixed to the magnetic rotor 1562, due to the characteristics of the stepper motor 1560, performs a complex helical motion relative to the internal thread portion 1523a, rotating and oscillating in a way that causes the axis to be misaligned while moving along the axis L. When this helical motion is performed, since a centrifugal force always acts on the external thread portion 1531a as a radial component, the tooth flanks of the external thread portion 1531a and the internal thread portion 1523a are subjected to a relatively strong force in the radial direction. However, since this centrifugal force is unstable, the external thread portion 1531a frequently and repeatedly moves in the radial direction relative to the internal thread portion 1523a. At this time, the contact area of ​​the tooth flanks (the inclined surfaces of the external and internal thread portions) of the thread feed mechanism changes continuously. Therefore, an unstable radial force is applied to the external thread portion 1531a via the tooth flanks, while an unstable axial force also acts. As a result, a problem arises where the tooth flanks of the thread feed mechanism momentarily approach and recede from each other in the radial and axial directions, i.e., they collide (hereinafter referred to as "existing problem point (collision in the thread feed mechanism)"). The resulting vibrations and collisions are propagated to the outside as operating noise.

[0004] Furthermore, since this electric valve is located inside the indoor unit of an air conditioner, low operating noise is required. In addition, in recent years, due to changes in refrigerant and improved oil separator capacity in air conditioners, the amount of lubricating materials such as refrigerant oil returning to the electric valve has sometimes decreased. Therefore, the electric valve must maintain low operating noise even in a dry (oil-depleted) state.

[0005] Correspondingly, Patent Document 1 describes the following: An electric valve in which a helical spring always presses the drive shaft in the axial direction through a small gap relative to the axial direction between the internal thread and the external thread, so that the internal thread and the external thread are always in contact in the axial direction.

[0006] However, in Patent Document 1, since the drive shaft is pressed by a helical spring in the axial direction, space is required in the axial direction, making it larger in the axial direction. Furthermore, the external thread portion still performs a complex helical motion relative to the internal thread portion, which cannot eliminate the existing problem (collision in the thread feed mechanism portion).

[0007] Furthermore, Patent Document 2 describes the following: A control valve, which serves as a sway prevention mechanism for a valve core connected to the lower end of a drive shaft, has a steel ball inserted into a through hole formed in a support member in a movable manner, and a force-applying member engaged in a circumferential groove formed in the support member, the force-applying member applying force to the steel ball in a direction orthogonal to the axis.

[0008] However, regarding the detailed connection structure between the drive shaft and the valve core in Patent Document 2, as described in Patent Document 3, the valve core has a clearance in the radial direction relative to the drive shaft, allowing for a movable connection. Therefore, similarly in Patent Document 2, since the force applied to the valve core does not act on the drive shaft, the external thread portion still undergoes a complex helical motion relative to the internal thread portion, failing to eliminate the existing problem (collision in the thread feed mechanism).

[0009] Existing technical documents

[0010] Patent documents

[0011] Patent Document 1: Japanese Patent Application Publication No. 2017-145923

[0012] Patent Document 2: Japanese Patent Application Publication No. 2000-120883

[0013] Patent Document 3: Japanese Patent Application Publication No. 10-2450 Summary of the Invention

[0014] The problem that the invention aims to solve

[0015] The object of the present invention is to provide an electric valve having a radial movement suppression member for a drive shaft capable of achieving low operating noise, and a refrigeration circulation system using the electric valve.

[0016] Solution for solving the problem

[0017] To address the aforementioned issues, an electric valve is provided, comprising: a support member having a drive shaft and a bearing portion; the drive shaft moving along an axial direction via a threaded feed mechanism that converts rotary motion into linear motion through an external thread and an internal thread; the bearing portion engaging with a guide portion of the drive shaft to guide the drive shaft along the axial direction; a valve core connected to the guide portion of the drive shaft to adjust the opening degree between the valve port and the valve seat; and a radial movement suppression member that applies force to one of the external thread and the internal thread in a direction orthogonal to the axial direction to suppress relative radial movement of the external thread and the internal thread.

[0018] Furthermore, in the aforementioned electric valve, it is preferable that the radial movement suppression member is disposed between the bearing portion and the guide portion.

[0019] Furthermore, in the aforementioned electric valve, it is preferable that the radial movement suppression member has an abutment member that contacts the aforementioned drive shaft, and force is applied to one of the aforementioned external thread portion and the aforementioned internal thread portion in the orthogonal direction of the axis via the aforementioned abutment member.

[0020] Furthermore, in the aforementioned electric valve, it is preferable that the contact state between the drive shaft of the radial movement suppression member and the abutting member is at least one line contact extending along the axial direction of the drive shaft.

[0021] Furthermore, in the aforementioned electric valve, it is preferable that the drive shaft of the radial movement suppression member and the abutting member are in at least one point contact.

[0022] Furthermore, in the aforementioned electric valve, it is preferable that the aforementioned abutting member and the outer peripheral surface of the aforementioned drive shaft are arranged facing each other, and the aforementioned radial movement suppression member also has a force-applying member that applies force to the aforementioned abutting member.

[0023] Furthermore, in the aforementioned electric valve, the aforementioned abutting member is preferably in a generally L-shaped form, having an abutting portion that abuts against the aforementioned drive shaft, and a force-applying portion that extends along the outer peripheral surface of the aforementioned support member and abuts against the aforementioned force-applying member in a manner that departs from the axis of the aforementioned abutting portion.

[0024] Furthermore, in the aforementioned electric valve, it is preferable that the force-applying portion extends along the axial direction of the outer peripheral surface of the aforementioned support member.

[0025] Furthermore, in the aforementioned electric valve, the force-applying component is preferably C-shaped with a slit, and anti-rotation engaging portions are provided at a pair of ends of the force-applying component that are directly or indirectly held in the aforementioned support component.

[0026] Furthermore, in the aforementioned electric valve, it is preferable to provide an anti-rotation portion on the radially outer side of the abutting member. By engaging the anti-rotation engagement portion of the force-applying member with the anti-rotation engagement portion of the force-applying member, the force-applying member is held in the support member via the abutting member.

[0027] Furthermore, in the aforementioned electric valve, it is preferable that a circumferential mounting groove is formed on the outer peripheral surface of the aforementioned support member, and an anti-rotation portion is provided on the aforementioned support member in such a discontinuous manner as the circumferential mounting groove. The anti-rotation portion engages with the anti-rotation engagement portion of the aforementioned force-applying member, thereby holding the aforementioned force-applying member on the aforementioned support member.

[0028] Furthermore, in the aforementioned electric valve, it is preferable that a continuous circumferential mounting groove is formed on the outer peripheral surface of the aforementioned support member, and an anti-rotation portion is provided that is continuously connected to the aforementioned circumferential mounting groove in the radially inner direction or in the axial direction. The anti-rotation portion engages with the aforementioned anti-rotation engagement portion of the aforementioned force-applying member, thereby holding the aforementioned force-applying member on the aforementioned support member.

[0029] Furthermore, in the aforementioned electric valve, it is preferable that the radial movement suppression member also has a retaining member that clamps the force-applying member between itself and the abutting member.

[0030] Furthermore, in the aforementioned electric valve, the abutting member is preferably composed of an annular elastic member, and also has a retaining member that clamps the abutting member between itself and the drive shaft when it is deformed in the orthogonal direction of the axis.

[0031] Furthermore, in the aforementioned electric valve, it is preferable that the abutting member is composed of an annular elastic member, which is arranged in the circumferential groove of the drive shaft in a state of deformation along the orthogonal direction of the axis.

[0032] Furthermore, in the aforementioned electric valve, it is preferable that the valve core is connected to the drive shaft in a manner that allows for radial relative displacement, and the radial movement suppression member applies force to the drive shaft.

[0033] Furthermore, a preferred refrigeration cycle system includes a compressor, a condenser, an expansion valve, and an evaporator, using the aforementioned electric valve as the expansion valve.

[0034] The effects of the invention are as follows.

[0035] According to the present invention, an electric valve having a radial movement suppression member for a drive shaft capable of achieving low operating noise and a refrigeration circulation system using the electric valve can be provided. Attached Figure Description

[0036] Figure 1 The diagram shows a cross-sectional view of an electric valve according to a first embodiment of the present invention. (a) shows a longitudinal cross-sectional view of the electric valve, (b) shows an enlarged cross-sectional view of (a) along the Ib-Ib line, (c) shows an enlarged cross-sectional view of (b) after the force-applying component has been removed, and (d) shows an explanatory diagram of the rotation axis movement using the enlarged cross-sectional view of (a) along the Id-Id line.

[0037] Figure 2 This is an enlarged cross-sectional view of a radial movement suppression member (using an abutment member to stop the rotation of a force-applying member) of a first embodiment of the present invention, in variation 1-1. (a) shows variation 1-1 (1) (using a protrusion of the abutment member), (b) shows variation 1-1 (2) (using a recess of the abutment member), and (c) shows variation 1-1 (3) (using a straight portion of the abutment member).

[0038] Figure 3This is an enlarged view showing the radial movement suppression member (using a bracket to stop the rotation of the force-applying component) of the first embodiment of the present invention, in variations 1-2. (a), (c), (e), and (g) are enlarged cross-sectional views, (b), (d), (f), and (h) are enlarged side views. (a) and (b) represent variations 1-2(1) (using the protrusion of the bracket), (c) and (d) represent variations 1-2(2) (using a limiting pin engaged with the bracket), (e) and (f) represent variations 1-2(3) (using the radial groove of the bracket), and (g) and (h) represent variations 1-2(4) (using the axial groove of the bracket).

[0039] Figure 4 This is an enlarged view showing a radial movement suppression member (a stable support provided by the contact portion of the abutment member) of a modified example 2-1 of the first embodiment of the present invention. (a) and (c) show the contact state of the abutment member and the guide portion, (b) and (d) show the contact area of ​​the abutment member, and (a) and (b) show the modified example 2-1 (1) (a reverse arc-shaped contact portion), and (c) and (d) show the modified example 2-1 (2) (a conical contact portion).

[0040] Figure 5 express Figure 4 A schematic diagram of the contact state between the cylindrical guide and the conical contact part in (c).

[0041] Figure 6 This is an enlarged view showing a radial movement suppression member (in a manner that reduces sliding resistance by utilizing the contact portion of the abutment member) of a variation 2-2 of the first embodiment of the present invention. (a) and (c) show the contact state of the abutment member and the guide portion, (b) and (d) show the contact area of ​​the abutment member, and (a) and (b) show variation 2-2 (1) (spherical contact portion), and (c) and (d) show variation 2-2 (2) (contact portion composed of multiple spherical shapes).

[0042] Figure 7 This is an enlarged cross-sectional view showing a radial movement suppression member (a means of suppressing circumferential loosening of the abutment portion) of a modified example 3-1 of the first embodiment of the present invention.

[0043] Figure 8 This is a cross-sectional view of an electric valve having a radial movement suppression member (in a manner that suppresses loosening of the abutment portion in the axial direction) of a modified example 3-2 of the first embodiment of the present invention. (a) shows a longitudinal cross-sectional view of the electric valve, (b) shows an enlarged view of the dashed area VIIIb in (a), and (c) shows an enlarged cross-sectional view of VIIIc-VIIIc in (a).

[0044] Figure 9 It is shown Figure 8 The above perspective view of the supporting member and the abutting member, (a) shows the supporting member as viewed from the anti-rotation part side of the force-applying member, (b) shows the supporting member as viewed from the abutting part side of the force-applying member, and (c) shows the abutting member as viewed from the abutting part side.

[0045] Figure 10 The diagram shows a cross-sectional view of the electric valve according to the second embodiment. (a) shows a longitudinal cross-sectional view of the electric valve, and (b) shows an enlarged cross-sectional view of (a) along the Xb-Xb line.

[0046] Figure 11 The diagram shows a cross-sectional view of the electric valve according to the third embodiment. (a) shows a longitudinal cross-sectional view of the electric valve, and (b) shows an enlarged cross-sectional view of (a) along the XIb-XIb line.

[0047] Figure 12 The diagram shows a cross-sectional view of the electric valve according to the fourth embodiment. (a) shows a longitudinal cross-sectional view of the electric valve, and (b) shows an enlarged cross-sectional view of (a) along line XIIb-XIIb.

[0048] Figure 13 The diagram shows a cross-sectional view of the electric valve according to the fifth embodiment. (a) shows a longitudinal cross-sectional view of the electric valve, and (b) shows an enlarged cross-sectional view of (a) along line XIIIb-XIIIb.

[0049] Figure 14 This is a diagram illustrating the refrigeration cycle system of the present invention.

[0050] Figure 15 The diagram shows a cross-sectional view of a prior art electric valve, (a) is a longitudinal cross-sectional view of the electric valve, and (b) is an explanatory diagram of the helical motion using the enlarged cross-sectional view XVb-XVb of (a).

[0051] In the picture:

[0052] 100a~100e, 100a”—Electric valve, 10—Valve body, 20, 20”—Support component, 21—Bracket part, 21a—Radial groove (anti-rotation part), 21a”—Radial groove, 21b, 21b”—Protrusion (anti-rotation part), 21c—Pin hole, 21d—Limit pin (anti-rotation part), 21e—Axial direction groove (anti-rotation part), 21f—Anti-disengagement claw part, 22—Fixing part, 23—Threaded hole, 23a—Internal thread part (thread feed mechanism part), 24—Bearing hole (bearing part), 25—Sliding hole, 30—Drive shaft, 31—Threaded part, 31a—External thread part (thread feed mechanism part), 32—Guide part, 40—Valve core part, 50— Coil components, 60—Stepper motor, 70a~70e, 70a1~70a9—Radial movement suppression components, 71a~71e, 71a1~71a3, 71a1-1~71a1-4, 71a', 71a”—Abutting components, 71a1c-1~71a1c-4—Contact parts, 71a1p—Protrusions (anti-rotation parts), 71a2d—Recesses (anti-rotation parts), 71a3s—Straight parts (anti-rotation parts), 71a'1, 71a”1—Abutting parts, 71a'2, 71a”2—Force-applying parts, 71a”21—Circumferential mounting groove, 72a~72c, 72a1~72a7, 72a9—Force-applying components, 72a1 n—A pair of cut-out ends (anti-rotation engaging parts) (a pair of ends), 72a2f—A pair of radially bent-back ends (anti-rotation engaging parts) (a pair of ends), 72a3b—A pair of straight-line bent ends (anti-rotation engaging parts) (a pair of ends), 72a4n—A pair of cut-out ends (anti-rotation engaging parts) (a pair of ends), 72a5n—A pair of cut-out ends (anti-rotation engaging parts) (a pair of ends), 72a6f—A pair of radially bent-back ends (anti-rotation engaging parts) (a pair of ends), 72a7b—A pair of axially bent ends (anti-rotation engaging parts) (a pair of ends), 72a9n—A pair of cut-out ends (anti-rotation engaging parts) (a pair of ends), 73c—Retaining member, 75a~75 c、75a”—Mounting hole; 76a、76a4、76a”、76b—Circumferential mounting groove; 77c—Outer mounting groove in the axial direction; 78d—Inner mounting groove in the axial direction; 79e—Circumferential groove; A1—Gap between the guide and the bearing hole; B—Protrusion of the abutting part into the mounting groove; C1、C2—Gap between the external thread and the internal thread; Ca-1、Ca-2—Line contact; Ca-3、Ca-4—Point contact; Da—Diameter of the guide; F1~F5—Force; L—Axis; L71a'、L71a”—Axis of the abutting part; Lb—Width of the contact part; M1、M2—Torque; Oa—Center position of the force-applying part; θ—Cone angle. Detailed Implementation

[0053] Reference Figures 1 to 14The embodiments of the present invention will be described in detail below. Furthermore, while electric valves will be described below, the radial movement suppression member of the present invention is not limited to electric valves; for example, it can also be applied to other devices and systems such as linear actuators.

[0054] <Regarding terminology>

[0055] In this specification and claims, "line contact" and "point contact" do not refer to the surface irregularities during microscopic observation, but rather to the contact state during macroscopic observation (in a geometric manner).

[0056] (First Implementation)

[0057] <About the structure of electric valves>

[0058] use Figure 1 The electric valve 100a according to the first embodiment of the present invention will be described. The electric valve 100a is mainly composed of a valve body 10, a support member 20, a drive shaft 30, a valve core 40, a coil member 50, a stepper motor 60, and a radial movement suppression member 70a. Hereinafter, each structure of the electric valve 100a will be described in turn. Here, the electric valve 100a of this embodiment is an electric valve that uses a radial movement suppression member 70a of the drive shaft 30, which will be described in detail below. This radial movement suppression member 70a suppresses the movement of the external thread portion (thread feed mechanism portion) 31a relative to the internal thread portion (thread feed mechanism portion) 23a in the radial direction by applying force to the external thread portion 31a in the orthogonal direction of the axis L, thereby eliminating the existing problem point (collision in the thread feed mechanism portion) and achieving low operating noise.

[0059] The valve body 10 is formed into a cylindrical shape, for example, using a metal such as stainless steel. A valve seat component 11, formed separately from the valve body 10 to seal the lower end, is provided on the valve body 10. A valve port 11a is opened in the center of the valve seat component 11. A valve chamber 12 is formed on the inner side of the valve body 10.

[0060] A first connector pipe 1, serving as a flow path for fluids such as refrigerant, is connected to one side of the outer periphery of the valve body 10. This first connector pipe 1 communicates with the valve chamber 12. Furthermore, a second connector pipe 2, which abuts against the valve seat component 11, is connected to the bottom surface of the valve body 10. This second connector pipe 2 communicates with the valve chamber 12 via the valve port 11a. Both the first connector pipe 1 and the second connector pipe 2 are constructed of materials such as copper or stainless steel and are fixed to the valve body 10 by brazing or the like.

[0061] The support member 20 includes: a generally cylindrical support portion 21 made of a resin-based material such as polyphenylene sulfide (PPS); and a stainless steel fixing portion 22 integrally formed on the end of the support portion 21 near the valve body 10 by inlay molding. The support member 20 is welded and fixed to the valve body 10 by the fixing portion 22.

[0062] The support portion 21 is configured such that its axis overlaps with the axis L of the shaft passing through the valve port 11a. At the center of the support portion 21, threaded holes 23, bearing holes (bearing portions) 24, and sliding holes 25 are formed concentrically in the direction of axis L, penetrating the support portion 21. An internal thread portion 23a is formed on the inner circumferential surface of the threaded hole 23 for threaded engagement with the external thread portion 31a of the drive shaft 30 described below. The guide portion 32 of the drive shaft 30 described below is engaged with the inner circumferential surface of the bearing hole 24 in a slidable manner. The sliding hole 25 is positioned close to the valve port 11a and is formed with an inner diameter larger than the inner diameter of the bearing hole 24. The valve core portion 40 described below is engaged with the sliding hole 25 in a slidable manner.

[0063] A guide rail 26, consisting of spiral protrusions, is integrally formed on the outer peripheral surface of the support portion 21. Adjacent wound portions of the guide rail 26 are spaced apart. The guide rail 26 is configured such that its axis overlaps with axis L, allowing for threaded engagement with the coil portion 51 of the coil component 50 described below, and guiding each wound portion of the coil portion 51 from one or both sides in a manner that allows the coil component 50 to rotate circumferentially.

[0064] The drive shaft 30 is formed into a cylindrical rod shape, for example, using a metal such as stainless steel. The drive shaft 30 has a threaded portion 31, a guide portion 32, and a flange portion 33 disposed at the end of the guide portion 32 near the valve port 11a, arranged in the direction of the axis L. An external threaded portion 31a is formed in the threaded portion 31a, and by threading this external threaded portion 31a with the internal threaded portion 23a of the support portion 21, the rotational motion of the drive shaft 30 is converted into linear motion. The guide portion 32 guides the movement of the drive shaft 30 in the direction of the axis L by engaging with the inner circumferential surface of the bearing hole 24 in a sliding manner. The drive shaft 30 is positioned at an offset position O1 (see reference) offset in the orthogonal direction of the axis L by a radial movement suppression member 70a provided in the bearing hole 24. Figure 1 (d) and moves along the axis L by means of a rotation-based threaded feed action, which will be described in detail below. The flange portion 33 locks the valve core portion 40 described below so that it can rotate. In this embodiment, the internal thread portion 23a and the external thread portion 31a are right-hand threads.

[0065] The valve core 40 includes a valve holder 41, a valve core 42, a washer 43, a spring seat 44, and a compression coil spring 45.

[0066] The valve holder 41 is formed into a cylindrical shape with an outer diameter that is approximately the same as the inner diameter of the sliding hole 25 of the support portion 21. The valve holder 41 engages along the sliding hole 25 in a manner that allows it to slide in the direction of the axis L.

[0067] The valve core 42 is formed in the shape of a needle and is fixed to the lower end 41a of the valve port 11a side in the valve holder 41 with its needle-shaped front end facing the valve port 11a. The valve core 42 regulates the flow rate by adding or subtracting the opening between the valve port 11a and the valve seat between the maximum opening degree and the minimum opening degree (or the fully closed state) of the valve.

[0068] On the upper end 41b of the valve holder 41, opposite to the valve port 11a, a flange 33 of the drive shaft 30 is rotatably engaged. Specifically, a washer 43 is inserted between the flange 33 of the drive shaft 30 and the upper end 41b of the valve holder 41, and the flange 33 rotatably engages the drive shaft 30 with the upper end 41b of the valve holder 41. Through this engagement, the drive shaft 30 supports the valve holder 41 so that it can move along the axis L and rotate about the axis L. Furthermore, an opening larger than the radial range of motion of the drive shaft 30 is formed on the upper end 41b of the valve holder 41. A spring seat 44 is provided inside the valve holder 41 so that it can move along the axis L. A compression coil spring 45 is installed between the spring seat 44 and the valve core 42 under a predetermined load. As a result, the spring seat 44 is pushed to the side of the drive shaft 30 and abuts against the flange portion 33 of the drive shaft 30.

[0069] In this embodiment, since the valve core 40 is connected to the drive shaft 30 in a manner that allows for radial relative displacement, when the radial movement suppression member 70a applies force to the external thread 31a in the orthogonal direction of the axis L, its influence can be reliably reduced and transmitted to the valve core 40. This will be explained in detail below.

[0070] The coil component 50 integrally comprises a coil portion 51 in the shape of a helical spring and a claw portion 52 protruding radially outward from one end of the coil portion 51. The coil portion 51 is threadedly engaged with the guide rail 26 of the support portion 21 in a circumferentially rotatable manner. The claw portion 52 can abut against the protrusion 67 of the magnetic rotor 62 described below, and by the rotation of the magnetic rotor 62, the coil component 50 is pushed back circumferentially via the claw portion 52. As a result, the coil component 50 encounters an upper limit stop (not shown) or a lower limit stop (not shown), limiting the rotation of the coil component 50 and also limiting the rotation of the magnetic rotor 62. Therefore, the movement of the valve core portion 40 is limited beyond the position of maximum opening or minimum opening (or closed state). This coil component 50 can be easily manufactured by forming a metal wire such as stainless steel.

[0071] The stepper motor 60 includes a housing 61, a magnetic rotor 62, and stator coils (not shown).

[0072] The housing 61 is formed in a generally cylindrical shape with the upper end sealed, for example, using a metal such as stainless steel. The lower open end of the housing 61 is airtightly fixed to the upper end of the valve body 10 by welding or the like.

[0073] The magnetic rotor 62 integrally comprises a cylindrical magnet portion 64 that magnetizes its outer periphery into multiple poles and a disk portion 65 that seals one end of the disk portion 64. The magnetic rotor 62 is fixed to the drive shaft 30 via a metal part 66 integrally formed in the center of the disk portion 65. Thus, the magnetic rotor 62 is disposed within the housing 61 in a manner that allows it to rotate about the axis L of the drive shaft 30. The drive shaft 30 is the axis of rotation of the magnetic rotor 62.

[0074] The stator coil is disposed on the outer peripheral surface of the housing 61. By applying a pulse signal to the stator coil, the magnetic rotor 62 rotates according to the number of pulses. The stator coil is equivalent to a stepper motor 60.

[0075] If the magnetic rotor 62 rotates, the drive shaft 30 rotates together with the magnetic rotor 62. Through the threaded feed action based on the external thread 31a and the internal thread 23a (threaded feed mechanism), the drive shaft 30 moves along the axis L, and the valve core 40 moves forward and backward relative to the valve port 11a. As a result, the opening degree of the valve port 11a relative to the valve seat changes, controlling the flow rate of the fluid flowing from the first connector pipe 1 to the second connector pipe 2 (or from the second connector pipe 2 to the first connector pipe 1).

[0076] <Regarding radial movement suppression components>

[0077] like Figure 1 As shown in (b), the radial movement suppression member 70a includes: an abutment member 71a made of a resin-based material with high sliding properties; a force-applying member 72a made of a C-shaped ring; a mounting hole 75a that connects the inner and outer peripheral surfaces of the support portion 21 in the orthogonal direction of the axis L via a stepped portion; and a circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. When viewed from the axis L direction, the abutment member 71a has a flat, umbrella-shaped shape. In this embodiment, the abutment member 71a is preferably made of a resin-based material such as polyphenylene sulfide (PPS) containing fluorine. The abutment member 71a in this embodiment has a flat, umbrella-shaped shape, but it is not limited to this, as long as the shape is suitable for the mounting hole 75a with the stepped portion.

[0078] <Assembly of Radial Movement Suppression Components>

[0079] like Figure 1As shown in (c), when the abutting member 71a is housed in the mounting hole 75a, the protrusion amount B of the abutting member 71a protruding into the circumferential mounting groove 76a is set to be relatively large relative to the gap A1 between the guide portion 32 and the bearing hole 24 (e.g., approximately 0.03 to 0.10 mm on one side). Therefore, with the abutting member 71a housed in the mounting hole 75a, by assembling the force-applying member 72a into the circumferential mounting groove 76a, a force F1 is generated in the orthogonal direction of the axis L on the guide portion 32 via the abutting member 71a, which can move the gap A between the drive shaft 30 and the guide portion 32 by an amount. Since this force F1 is set to be greater than the magnetic attraction of the stepper motor 60, the drive shaft 30 will not rotate or swing due to the magnetic attraction. Furthermore, the thread loosening C of the threaded feed mechanism (see reference) Figure 1 (d) C1+C2) is the gap A between guide part 32 and bearing hole 24 (refer to) Figure 1 (c) is greater than 2×A1). Therefore, as Figure 1 As shown in (d), when the radial movement suppression member 70a applies force to the external thread portion 31a in the orthogonal direction of the axis L via the guide portion 32, the external thread portion 31a will not rotate or oscillate relative to the internal thread portion 23a, thereby maintaining a small gap C1 in the radial direction. At this time, the tooth flanks of the thread feed mechanism contact each other in such a way that the contact area does not change. Therefore, in addition to the centrifugal force with stability as the radial component, a stable axial component force also acts on the thread feed mechanism, thereby suppressing the collision between the tooth flanks of the thread feed mechanism. Thus, the complex helical motion of the drive shaft 30 rotating and oscillating in a way that offsets the axis from one side of the prior art while moving along the axis L is corrected into a rotational axis motion that rotates while moving along the axis L. Furthermore, when viewed from the axis L direction, the abutting member 71a in this embodiment has a planar contact portion, making the contact state between the abutting member 71a and the guide portion 32 a line contact. However, this is not a limitation; for example, it may also have a semi-cylindrical contact portion, making the contact state between the abutting member 71a and the guide portion 32 a line contact. Thus, in this embodiment, by setting the contact state between the abutting member 71a and the guide portion 32 to a line contact, the guide portion 32 can be pressed horizontally and stably using the full height of the abutting member 71a through this line contact extending along the axis L direction.

[0080] The electric valve 100a of this embodiment maintains a small gap C1 in the radial direction within the threaded feed mechanism by means of the radial movement suppression member 70a, eliminating the existing problem of collisions in the threaded feed mechanism. Therefore, low operating noise can be achieved even in a dry (oil-depleted) state. Furthermore, in the radial movement suppression member 70a of this embodiment, force is always applied to the external thread 31a in the radial direction relative to the internal thread 23a, regardless of the lifting position of the drive shaft 30. Moreover, since the radial movement suppression member 70a of this embodiment is located between the bearing hole 24 and the guide portion 32, the abutment member 71a and the external thread 31a do not overlap, thus not affecting the movement of the drive shaft 30 along the axis L. Furthermore, since the radial movement suppression member 70a of this embodiment applies force to the external thread 31a in the orthogonal direction of the axis L via the abutment member 71a that contacts the drive shaft 30, space is saved and the structure is simple. Furthermore, in the radial movement suppression member 70a of this embodiment, the abutting member 71a is arranged facing the outer peripheral surface of the guide portion 32, and the force is applied to the abutting member 71a by the force-applying member 72a. Therefore, compared with conventional electric valves, it can be introduced without significant changes. In addition, in this embodiment, the abutting member 71a and the force-applying member 72a have a long contact area in the circumferential direction, so the force of the force-applying member 72a can be reliably transmitted to the abutting member 71a.

[0081] (Modification 1 of the first embodiment)

[0082] Here, use Figure 2 and Figure 3 The radial movement suppression members 70a1 to 70a7 of the first embodiment's variation 1 will be described. In this variation 1 of the first embodiment, the radial movement suppression members 70a1 to 70a7 are respectively configured to prevent rotation of the force-applying members 72a1 to 72a7, which differs from the radial movement suppression member 70a in the first embodiment, but other basic structures are the same as in the first embodiment. Here, the same symbols are used for the same components, and repeated descriptions are omitted. Furthermore, in the support portion 21 of this embodiment, in order to stabilize shrinkage during resin molding and obtain the desired shape and size, a radial groove 21a is formed on the side opposite to the mounting hole 75a relative to the axis L.

[0083] like Figure 1 As shown in (b), in the radial movement suppression member 70a of the first embodiment, with the abutment member 71a housed in the mounting hole 75a, a circumferential mounting groove 76a (see reference) is continuously formed on the outer peripheral surface of the bracket portion 21. Figure 1(c) The force-applying component 72a is assembled from a C-shaped ring. Therefore, the force-applying component 72a is held in the circumferential mounting groove 76a in a state where its movement in the circumferential direction is unrestricted. Therefore, there is a concern that the force-applying component 72a may rotate in the circumferential direction due to vibrations or the like generated when the electric valve 100a is driven.

[0084] Here, regarding the force exerted by the force-applying member 72a, which is composed of a C-ring, on the abutting member 71a, when the cut portion of the C-ring is located opposite to the abutting member 71a across the axis L (see reference...), Figure 1 The force applied by the force member 72a becomes maximum when (a) is in the position opposite to the abutting member 71a, and minimum when the cut of the C-ring is in the position opposite to the abutting member 71a. Therefore, due to vibrations generated during operation, the force applied by the force member 72a rotates circumferentially relative to the abutting member 71a, that is, the circumferential position of the cut changes, and thus the force applied by the force applied by the force member 72a to the abutting member 71a changes, raising concerns about the instability of the pressing pressure of the guide portion 32 on the bearing hole 24.

[0085] In response to this, the radial movement suppression members 70a1 to 70a7 in Modification 1 of the First Embodiment are respectively configured to prevent the rotation of the force-applying members 72a1 to 72a7. Furthermore, the radial movement suppression members 70a1 to 70a7 in Modification 1 of the First Embodiment are generally divided into radial movement suppression members 70a1 to 70a3 of Modification 1-1 of the First Embodiment (provided on the abutting members 71a1 to 71a3) and radial movement suppression members 70a4 to 70a7 of Modification 1-2 of the First Embodiment (provided on the support portion 21), depending on the method of preventing the rotation of the force-applying members 72a1 to 72a3. These will be described in detail below. Hereinafter, Modification 1 of the First Embodiment will be described in the order of Modification 1-1 of the First Embodiment and Modification 1-2 of the First Embodiment.

[0086] (Modification 1-1 of the first embodiment)

[0087] like Figure 2 As shown in (a) to (c), in the radial movement suppression members 70a1 to 70a3 of the first embodiment, the force-applying members 72a1 to 72a3 are respectively provided with anti-rotation devices on the abutting members 71a1 to 71a3, so that the force-applying members 72a1 to 72a3 are indirectly held on the support portion 21 via the abutting members 71a1 to 71a3, including the three methods of the first embodiment (1) to the second embodiment (3).

[0088] (Variation 1-1(1))

[0089] like Figure 2As shown in (a), the radial movement suppression member 70a1 in the modified example 1-1 (1) of the first embodiment includes, in its central portion on the radially outer side, an abutting member 71a1 having a protrusion (anti-rotation portion) 71a1p protruding in the outer diameter direction; and a force-applying member 72a1 having a pair of circumferentially extending cut ends (anti-rotation engaging portions) (a pair of ends) 72a1n. Regarding the assembly of this radial movement suppression member 70a1, with the abutting member 71a1 housed in the mounting hole 75a, the force-applying member 72a1 is assembled in the circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. At this time, the protrusion 71a1p of the abutting member 71a1 is positioned between the pair of cut ends 72a1n of the force-applying member 72a1. Furthermore, in this embodiment, the pair of cut ends 72a1n and the protrusion 71a1p are engaged such that at least one of them has a plurality of gaps. This is because if the pair of cut ends 72a1n and the protrusion 71a1p are brought together without any gap, the pair of cut ends 72a1n open in the direction of separation from each other, and thus the radial force of the force-applying member 72a1 is weakened.

[0090] In summary, in the radial movement suppression member 70a1 of this embodiment, even if the force-applying member 72a1 attempts to rotate circumferentially within the circumferential mounting groove 76a due to vibrations or other factors generated during operation, the pair of cut ends 72a1n interfere with the protrusion 71a1p, thereby maintaining the circumferential position of the pair of cut ends 72a1n. Thus, by maintaining the force exerted by the force-applying member 72a1 on the abutting member 71a1, the pressing pressure of the guide portion 32 on the bearing hole 24 can be stabilized. Furthermore, in this embodiment, by simply changing the shapes of the abutting member 71a1 and the force-applying member 72a1, the rotation of the force-applying member 72a1 can be stopped relatively easily. Additionally, in this embodiment, since the inner circumferential radius of the force-applying member 72a1 is larger than the outer circumferential radius of the abutting member 71a1, the pair of cut ends 72a1n make point contact with the outer circumferential surface of the abutting member 71a1 at two locations, thus enabling the application of force in a stable state. Furthermore, the outer radius of the contacting member 71a1 and the inner radius of the force-applying member 72a1 can also be set to be the same, in which case there are two circumferential line contacts. In this embodiment, since the force-applying member 72a1 is formed of a circular wire, there are two point contacts, but the force-applying member 72a1 can also be formed of a square wire, in which case there are two line contacts in the axial direction L.

[0091] (Variation 1-1(2))

[0092] like Figure 2As shown in (b), the radial movement suppression member 70a2 in the modified example 1-1(2) of the first embodiment includes, at the center of its outer peripheral surface: an abutting member 71a2 having a recessed portion (anti-rotation portion) 71a2d that is recessed in the inward direction; and a force-applying member 72a2 having a pair of radially folded-back ends (anti-rotation engaging portions) (a pair of ends) 72a2f that are folded back in the inward direction. Regarding the assembly of the radial movement suppression member 70a2, with the abutting member 71a2 housed in the mounting hole 75a, the force-applying member 72a2 is assembled in the circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. At this time, the pair of radially folded-back ends 72a2f of the force-applying member 72a2 are configured to engage with the recessed portion 71a2d of the abutting member 71a1.

[0093] Therefore, in the radial movement suppression member 70a2 of this embodiment, even if the force-applying member 72a2 wants to rotate circumferentially within the circumferential mounting groove 76a due to vibrations or the like generated during operation, the pair of radially folded-back ends 72a2f interfere with the recessed portion 71a2d, thereby maintaining the circumferential position of the pair of radially folded-back ends 72a2f. Thus, by maintaining the force exerted by the force-applying member 72a2 on the abutting member 71a2, the pressing pressure of the guide portion 32 on the bearing hole 24 can be stabilized. Furthermore, in this embodiment, similar to modified example 1-1(1), by simply changing the shape of the abutting member 71a2 and the force-applying member 72a2, the rotation prevention of the force-applying member 72a2 can be performed relatively easily. Furthermore, in this embodiment, since the inner radius of the force-applying member 72a2 is larger than the outer radius of the abutting member 71a2, the force-applying member 72a2 makes point contact with the outer circumferential surface of the abutting member 71a2 at two points, and the pair of radially folded-back ends 72a2f engage with the recessed portion 71a2d, thus enabling force application in a more stable state. Additionally, the outer radius of the abutting member 71a2 and the inner radius of the force-applying member 72a2 can also be set to be the same, in which case there will be two circumferential line contacts. Furthermore, in this embodiment, since the force-applying member 72a2 is formed of a circular wire, there are two point contacts; however, the force-applying member 72a2 can also be formed of a square wire, in which case there will be two line contacts in the axial direction L.

[0094] (Variation 1-1(3))

[0095] like Figure 2As shown in (c), the radial movement suppression member 70a3 in the first embodiment of the modified example 1-1(3) includes on its outer peripheral surface: an abutting member 71a3 having a straight portion (anti-rotation portion) 71a3s; and a force-applying member 72a3 having a pair of straight bent ends (anti-rotation engaging portions) (a pair of ends) 72a3b bent into a straight shape. Regarding the assembly of this radial movement suppression member 70a3, with the abutting member 71a3 housed in the mounting hole 75a, the force-applying member 72a3 is assembled in the circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. At this time, the pair of straight bent ends 72a3b of the force-applying member 72a3 are configured to engage with the straight portion 71a3s of the abutting member 71a3.

[0096] Therefore, in the radial movement suppression member 70a3 of this embodiment, even if the force-applying member 72a3 wants to rotate circumferentially within the circumferential mounting groove 76a due to vibrations generated during operation, the pair of straight bent ends 72a3b interfere with the straight portion 71a3s, thereby maintaining the circumferential position of the pair of straight bent ends 72a3b. Thus, by maintaining the force exerted by the force-applying member 72a3 on the abutting member 71a3, the pressing pressure of the guide portion 32 on the bearing hole 24 can be stabilized. Furthermore, in this embodiment, similar to modified example 1-1(2), by simply changing the shape of the abutting member 71a3 and the force-applying member 72a3, the rotation of the force-applying member 72a2 can be stopped relatively easily. In addition, in the force-applying member 72a3 of this embodiment, since the pair of straight bent ends 72a3b make line contact with the straight portion 71a3s at two points and engage in the same direction toward the axis L, force can be applied in a more stable state. In addition, the abutting member 71a3 of this embodiment can be miniaturized and made lighter compared to the abutting member 71a2 of variant 1-1(2). Furthermore, in this embodiment, since the force-applying member 72a3 is formed of a circular wire, there are two line contacts. However, the force-applying member 72a3 can also be formed of a square wire, in which case there are two surface contacts with width in the axial direction L.

[0097] (Variations 1-2 of the first embodiment)

[0098] like Figure 3 As shown in (a) to (h), for the radial movement suppression members 70a4 to 70a7 in the modifications 1-2 of the first embodiment, by providing the anti-rotation of the force-applying members 72a4 to 72a7 to the support portion 21 respectively, the force-applying members 72a4 to 72a7 are directly held in the support portion 21, including the four methods of modifications 1-2 (1) to modifications 1-2 (4). In addition, the abutting member 71a in the modifications 1-2 of the first embodiment and the abutting member 71a of the first embodiment (refer to Figure 1(b) is the same.

[0099] (Variation 1-2(1))

[0100] like Figure 3 As shown in (a) to (b), the radial movement suppression member 70a4 in the modified examples 1-2 (1) of the first embodiment includes: a protrusion (anti-rotation portion) 21b formed on the outer peripheral surface of the support portion 21; a circumferential mounting groove 76a4 discontinuously formed on the outer peripheral surface of the support portion 21 through the protrusion 21b; and a force-applying member 72a4 having a pair of circumferentially extending cut ends (anti-rotation engaging portions) (a pair of ends) 72a4n. Regarding the assembly of the radial movement suppression member 70a4, with the abutment member 71a housed in the mounting hole 75a, the force-applying member 72a4 is assembled in the circumferential mounting groove 76a4 discontinuously formed on the outer peripheral surface of the support portion 21. At this time, the protrusion 21b of the support portion 21 is positioned between the pair of cut ends 72a4n of the force-applying member 72a4. Furthermore, in this embodiment, for the same reasons as in the modified example 1-1(1) described above, the pair of cut-out ends 72a4n and the protrusion 21b are engaged by providing a plurality of gaps on at least one side. In this embodiment, the protrusion 21b of the bracket portion 21 is provided at a position approximately 90° off in the circumferential direction relative to the mounting hole 75a, but is not limited to this; for example, it can be any circumferential position away from the mounting hole 75a and the radial groove 21a.

[0101] Therefore, in the radial movement suppression member 70a4 of this embodiment, even if the force-applying member 72a4 attempts to rotate circumferentially within the circumferential mounting groove 76a4 due to vibrations or other factors generated during operation, the pair of cut ends 72a4n interfere with the protrusion 21b, thereby maintaining the circumferential position of the pair of cut ends 72a4n. This maintains the force exerted by the force-applying member 72a4 on the abutting member 71a, stabilizing the pressing pressure of the guide portion 32 on the bearing hole 24. Furthermore, in this embodiment, by simply changing the shape of the bracket portion 21 and the force-applying member 72a4, the anti-rotation of the force-applying member 72a4 can be performed relatively easily. Additionally, in the force-applying member 72a4 of this embodiment, since the pair of cut ends 72a4n are not located opposite the abutting member 71a, as explained, a larger force can be applied to the abutting member 71a. Furthermore, in this embodiment, similar to variant 1-1(1), the force-applying member 72a4 makes point contact with the outer periphery top of the abutting member 71a. However, it is not limited to this; the outer periphery radius of the abutting member 71a and the inner periphery radius of the force-applying member 72a4 may be set to be the same, so that the force-applying member 72a4 makes contact with the entire outer periphery of the abutting member 71a. In this way, force can be applied in a stable state.

[0102] (Variation 1-2(2))

[0103] like Figure 3 As shown in (c) to (d), the radial movement suppression member 70a5 in the modified examples 1-2 (2) of the first embodiment includes: a circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21; a pin hole 21c that runs through the circumferential mounting groove 76a in the axial direction L and opens above it; a limiting pin (anti-rotation portion) 21d pressed into the pin hole 21c; and a force-applying member 72a5 having a pair of circumferentially extending cut ends (anti-rotation engaging portions) (a pair of ends) 72a5n. Regarding the assembly of the radial movement suppression member 70a5, with the abutment member 71a housed in the mounting hole 75a, the force-applying member 72a5 is assembled in the circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. At this time, when viewed from the axis L direction, the gaps of the pair of cut ends 72a5n are arranged to overlap with the pin hole 21c. Then, the limiting pin 21d is pressed into the pin hole 21c, thereby positioning the force-applying member 72a5 circumferentially. Through the circumferential positioning of the force-applying member 72a5, the circumferential mounting groove 76a formed on the outer circumferential surface of the bracket portion 21 is discontinuous in the circumferential direction. Furthermore, in this embodiment, for the same reason as in the above-described modified example 1-1(1), the pair of cut ends 72a5n and the limiting pin 21d are engaged by providing a plurality of gaps on at least one side. In this embodiment, the limiting pin 21d is provided at a position approximately 90° off from the mounting hole 75a in the circumferential direction, but it is not limited to this. For example, it can be any circumferential position away from the mounting hole 75a and the radial groove 21a. Furthermore, in this embodiment, the limiting pin 21d is pressed into the pin hole 21c, but it is not limited to this; for example, it can also be inserted into the pin hole 21c.

[0104] Therefore, in the radial movement suppression member 70a5 of this embodiment, even if the force-applying member 72a5 wants to rotate circumferentially within the circumferential mounting groove 76a due to vibrations generated during operation, the pair of cut ends 72a5n interfere with the limiting pin 21d, thereby maintaining the circumferential position of the pair of cut ends 72a5n. As a result, by maintaining the force exerted by the force-applying member 72a5 on the abutting member 71a, the pressing pressure of the guide portion 32 on the bearing hole 24 can be stabilized. Furthermore, in this embodiment, similar to modified examples 1-2 (1), by only changing the shape of the bracket portion 21 and the force-applying member 72a5, the rotation of the force-applying member 72a5 can be stopped relatively easily, and since the pair of cut ends 72a5n of the force-applying member 72a5 are not located opposite the abutting member 71a, a larger force can be applied to the abutting member 71a. Furthermore, in this embodiment, similar to variant 1-1(1), the force-applying member 72a5 makes point contact with the outer periphery top of the abutting member 71a. However, it is not limited to this; the outer periphery radius of the abutting member 71a and the inner periphery radius of the force-applying member 72a5 may be set to be the same, so that the force-applying member 72a5 makes contact with the entire outer periphery of the abutting member 71a. In this way, force can be applied in a stable state.

[0105] (Variations 1-2(3))

[0106] like Figure 3 As shown in (e) to (f), the radial movement suppression member 70a6 in the modified examples 1-2 (3) of the first embodiment includes: a radial groove (anti-rotation portion) 21a formed in the support portion 21; and a force-applying member 72a6 having a pair of radially folded-back ends (anti-rotation engaging portions) (a pair of ends) 72a6f that fold back in the inner diameter direction. The radial groove 21a is continuously connected to the circumferential mounting groove 76a on the radially inner side. Here, regarding the assembly of the radial movement suppression member 70a6, with the abutment member 71a housed in the mounting hole 75a, the force-applying member 72a6 is assembled in the circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. At this time, the pair of radially folded-back ends 72a6f of the force-applying member 72a6 are configured to engage with the radial groove 21a of the support portion 21.

[0107] Therefore, in the radial movement suppression member 70a6 of this embodiment, even if the force-applying member 72a6 wants to rotate circumferentially within the circumferential mounting groove 76a due to vibrations generated during operation, the pair of radially folded-back ends 72a6f interfere with the radial groove 21a, thereby maintaining the circumferential position of the pair of radially folded-back ends 72a6f. As a result, by maintaining the force exerted by the force-applying member 72a6 on the abutting member 71a, the pressing pressure of the guide portion 32 on the bearing hole 24 can be stabilized. Furthermore, in this embodiment, by simply changing the shape of the force-applying member 72a2 and utilizing the radial groove 21a for shrinkage countermeasures, the rotation of the force-applying member 72a6 can be stopped relatively easily. In addition, in the force-applying member 72a6 of this embodiment, similar to the modified examples 1-2 (1), the pair of radially folded-back ends 72a6f are not located opposite the abutting member 71a, so a larger force can be applied to the abutting member 71a. Furthermore, in this embodiment, similar to variant 1-1(1), the force-applying member 72a6 makes point contact with the outer periphery top of the abutting member 71a. However, it is not limited to this; the outer periphery radius of the abutting member 71a and the inner periphery radius of the force-applying member 72a6 may be set to be the same, so that the force-applying member 72a6 makes contact with the entire outer periphery of the abutting member 71a. In this way, force can be applied in a stable state.

[0108] (Variations 1-2(4))

[0109] like Figure 3 As shown in (g) to (h), the radial movement suppression member 70a7 in the modified examples 1-2 (4) of the first embodiment includes: a circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21; an axial direction groove (anti-rotation portion) 21e formed on the outer peripheral surface of the support portion 21 in a manner that traverses the circumferential mounting groove 76a in the axial direction L; and a force-applying member 72a7 having a pair of axial direction bent ends (anti-rotation engaging portions) (a pair of ends) 72a7b that are bent into a straight shape in the axial direction L. The axial direction groove 21e is continuously connected relative to the circumferential mounting groove 76a in the axial direction L. Here, regarding the assembly of the radial movement suppression member 70a7, with the abutment member 71a housed in the mounting hole 75a, the force-applying member 72a7 is assembled in the circumferential mounting groove 76a continuously formed on the outer peripheral surface of the support portion 21. At this time, the pair of axially bent ends 72a7b of the force-applying component 72a7 are configured to engage with the axially bent groove 21e of the support portion 21. Furthermore, in this embodiment, both pairs of axially bent ends 72a7b are configured to be bent downwards (see reference). Figure 3 (the solid line of (h)), but not limited to this, for example, a pair of axially bent ends 72a7b respectively pointing upwards (see reference). Figure 3The bend can be made in either direction (the dashed line of (h)) or below. Furthermore, in this embodiment, the axial direction groove 21e is provided at a position approximately 90° off in the circumferential direction relative to the mounting hole 75a, but it is not limited to this. For example, it can be any circumferential position away from the mounting hole 75a and the radial groove 21a.

[0110] Therefore, in the radial movement suppression member 70a7 of this embodiment, even if the force-applying member 72a7 wants to rotate circumferentially within the circumferential mounting groove 76a due to vibrations generated during operation, the pair of axially bent ends 72a7b interfere with the axially bent groove 21e, thereby maintaining the circumferential position of the pair of axially bent ends 72a7b. As a result, maintaining the force exerted by the force-applying member 72a7 on the abutting member 71a can stabilize the pressing pressure of the guide portion 32 on the bearing hole 24. Furthermore, in this embodiment, similar to modified examples 1-2 (1), by only changing the shape of the bracket portion 21 and the force-applying member 72a7, the rotation of the force-applying member 72a7 can be stopped relatively easily, and since the pair of axially bent ends 72a7b of the force-applying member 72a7 are not located opposite the abutting member 71a, a larger force can be applied to the abutting member 71a. Furthermore, in this embodiment, similar to variant 1-1(1), the force-applying member 72a7 makes point contact with the outer periphery top of the abutting member 71a. However, it is not limited to this; the outer periphery radius of the abutting member 71a may be set to be the same as the inner periphery radius of the force-applying member 72a5, so that the force-applying member 72a7 makes contact with the entire outer periphery of the abutting member 71a. In this way, force can be applied in a stable state.

[0111] (Modification 2 of the first embodiment)

[0112] Here, use Figures 4 to 6 The radial movement suppression members 70a1-1 to 70a1-4 of the first embodiment's variation 2 will be described. In the radial movement suppression members 70a1-1 to 70a1-4 of this first embodiment's variation 2, the shape of the contact portion of the abutting member 71a1-1 to 71a1-4 that contacts the guide portion 32 is changed. This is different from the radial movement suppression member 70a1 in the first embodiment's variation 1-1(1) (see reference 70a1). Figure 2 The variation (a) is different, but the other basic structures are the same as those in variation 1-1(1) of the first embodiment. Here, the same symbols are used to mark the same parts, and repeated descriptions are omitted. For the sake of explanation, this variation 2 of the first embodiment is set as the variation 1-1(1) of the first embodiment (refer to...). Figure 2 The structure used in (a) is not limited to this; for example, it can also be set as other variations 1-1(2), (3) of the first embodiment (see reference). Figure 2(b) and Figure 2 (c) and variations 1-2(1)~(4) ( Figure 3 (a) to Figure 3 The structure used in (h)). Furthermore, the radial movement suppression members 70a1-1 to 70a1-4 of the first embodiment's variation 2 are generally divided into radial movement suppression members 70a1-1 and 70a1-2 (stable support method) of the first embodiment's variation 2-1 and radial movement suppression members 70a1-3 and 70a1-4 (method to reduce sliding resistance) of the first embodiment's variation 2-2, according to the shape of the contact portion in the abutment members 71a1-1 to 71a1-4, which will be described in detail below. Hereinafter, the first embodiment's variation 2 will be described in the order of the first embodiment's variation 2-1 and the first embodiment's variation 2-2.

[0113] (Modification 2-1 of the first embodiment)

[0114] In the radial movement suppression member 70a1 of the first embodiment, as in the variation 1-1(1), Figure 2 As shown in (a), when viewed from the axis L, the contact portion of the abutment member 71a1 opposite the guide portion 32 has a planar shape, thus the contact state between the abutment member 71a1 and the guide portion 32 becomes a line contact extending along the axis L. Therefore, due to vibrations generated during operation, the circumferential position of the abutment member 71a1 relative to the guide portion 32 is prone to deviate, raising concerns about instability in the circumferential position of the line contact. Consequently, the force exerted by the force-applying member 72a1 in a direction not passing through the axis of the guide portion 32 is applied through the circumferentially unstable line contact, raising concerns about instability in the pressing pressure of the guide portion 32 on the bearing hole 24.

[0115] In response to this, in the radial movement suppression members 70a1-1 and 70a1-2 of the first embodiment, the contact portions 71a1c-1 and 71a1c-2 of the abutting members 71a1-1 and 71a1-2 respectively have stable support methods, including the two methods of the modified example 2-1 (1) and the modified example 2-1 (2).

[0116] (Variation Example 2-1(1))

[0117] like Figure 4 As shown in (a), in the radial movement suppression member 70a1-1 of the modified example 2-1 (1) of the first embodiment, when viewed from the axis L direction, the contact portion 71a1c-1 of the abutment member 71a1-1 opposite to the guide portion 32 has a reverse arc shape that is close to the outer peripheral surface of the guide portion 32. Therefore, as Figure 4As shown in (b), the contact state between the abutting member 71a1-1 and the guide portion 32 is a line contact Ca-1 extending along the axis L. In this embodiment, the radius of curvature of the contact portion 71a1c-1 is set to be larger than the radius of curvature of the guide portion 32, but more preferably it is set to be slightly larger than the radius of curvature of the guide portion 32. Furthermore, the radii of curvature of the contact portion 71a1c-1 and the guide portion 32 may also be set to be the same, so that the contact state is a surface contact.

[0118] Therefore, in the radial movement suppression member 70a1-1 of this embodiment, even if the circumferential position of the contact member 71a1-1 is slightly deviated from the guide portion 32 due to vibrations or the like generated during operation, the guide portion 32 can easily return to the top of the reverse arc-shaped contact portion 71a1c-1, thereby making contact with the radial movement suppression member 70a1 in the modified example 1-1(1) of the first embodiment (see reference 70a1). Figure 2 Compared to (a), the movement of the line contact Ca-1 can be suppressed to a smaller extent. Therefore, the force of the force-applying member 72a1 is applied in the direction near the axis of the guide portion 32 via the abutment member 71a1-1, thereby maintaining the pressing pressure of the guide portion 32 on the bearing hole 24 in a more stable state. Furthermore, in this embodiment, similar to the first embodiment, by setting the contact state between the abutment member 71a1-1 and the guide portion 32 as a line contact, the guide portion 32 can be pressed horizontally and stably using the full height of the abutment member 71a1-1 via this line contact extending along the axis L.

[0119] (Variation Example 2-1(2))

[0120] like Figure 4 As shown in (c), in the radial movement suppression member 70a1-2 of the modified example 2-1(2) of the first embodiment, when viewed from the axis L direction, the contact portion 71a1c-2 of the abutment member 71a1-2 opposite to the guide portion 32 has a conical shape that is recessed relative to the outer peripheral surface of the guide portion 32. Therefore, as Figure 4 As shown in (d), the contact state between the abutting member 71a1-2 and the guide portion 32 is two line contacts Ca-2 extending along the axis L direction across the axis L.

[0121] Therefore, in the radial movement suppression member 70a1-2 of this embodiment, even if the circumferential position of the contact member 71a1-2 is slightly deviated from the guide portion 32 due to vibrations or the like generated during operation, it is stably supported by the two line contacts Ca-2. Therefore, it is similar to the radial movement suppression member 70a1 in the modified example 1-1(1) of the first embodiment (see...). Figure 2Compared to (a), the movement of the two line contacts Ca-2 can be minimized. Therefore, the force of the force-applying member 72a1 is applied to the guide portion 32 in approximately the axial direction via the abutment member 71a1-2, thereby further maintaining the pressing pressure of the guide portion 32 on the bearing hole 24 in a stable state. Furthermore, in this embodiment, similar to the first embodiment, by setting the contact state between the abutment member 71a1-2 and the guide portion 32 as a line contact, the guide portion 32 can be pressed horizontally and stably using the full height of the abutment member 71a1-2 via this line contact extending along the axis L.

[0122] Here, use Figure 5 The conditions under which the pair of edge portions E1 and E2 in the contact portion 71a1c-2 do not abut against the guide portion 32 will be explained. First, straight lines are drawn from the linear edge portions E1 and E2 formed on the outer edge of the contact portion 71a1c-2 to the center O of the guide portion 32, and the angle formed by ∠E1OE2 is defined as α. This angle α formed by ∠E1OE2 is obtained by passing through 2×Sin －1 The value is calculated using (Lb / Da). Here, Da represents the diameter of the guide portion 32, and Lb represents the tapered width of the contact portion 71a1c-2. Furthermore, the vertex of the tapered shape of the contact portion 71a1c-2 is set as O1, and the vertex angle formed by ∠E1O1E2 is set as the tapered angle θ.

[0123] Here, for example, when θ = 180 - α, the sum of the angles formed by ∠OE1O1 and ∠OE2O1 is 180 (°), meaning that the angles formed by ∠OE1O1 and ∠OE2O1 are both 90 (°), thus the linear edge portions E1 and E2 become the contact points of the guide portion 32. Therefore, in this embodiment, by satisfying the following (Equation 1), the contact point position of the guide portion 32 relative to the conical contact portion 71a1c-2 can be set on the conical surface excluding the vertex O1 side of the linear edge portions E1 and E2. As a result, it is possible to prevent the linear edge portions E1 and E2 from abutting against the cylindrical guide portion 32.

[0124] θ>180-α (Equation 1)

[0125] Equation 1 is θ>180-2×Sin －1 (Lb / Da). Therefore, by setting the diameter Da of the guide portion 32 and the tapered width Lb of the contact portion 71a1c-2 in such a way that the cone angle θ of the contact portion 71a1c-2 satisfies (Equation 1), it is possible to suppress the deformation or wear of the linear edge portions E1 and E2 due to the contact pressed by the guide portion 32, thereby preventing changes in the pressing force of the guide portion 32 on the bearing hole 24.

[0126] (Modification 2-1 of the first embodiment)

[0127] In the radial movement suppression member 70a1 of the first embodiment, as in the variation 1-1(1), Figure 2 As shown in (a), the contact state between the abutting member 71a1 and the guide portion 32 becomes a line contact extending along the axis L. Therefore, the sliding resistance of the guide portion 32, which rotates relative to the abutting member 71a1, increases, raising concerns that the driving force of the stepper motor 60 cannot be efficiently transmitted to the valve core 42.

[0128] In response to this, in the radial movement suppression members 70a1-3 and 70a1-4 of the first embodiment, the contact portions 71a1c-3 and 71a1c-4 of the abutting members 71a1-3 and 71a1-4 respectively have a way to reduce sliding resistance, including the two ways of variation 2-2 (1) and variation 2-2 (2).

[0129] (Variation Example 2-2(1))

[0130] like Figure 6 As shown in (a), in the radial movement suppression member 70a1-3 of the modified example 2-2(1) of the first embodiment, when viewed from the axis L direction, the contact portion 71a1c-3 of the abutment member 71a1-3 opposite to the guide portion 32 has a spherical shape. Therefore, as Figure 6 As shown in (b), the contact state between the abutting part 71a1-3 and the guide part 32 becomes a point contact Ca-3.

[0131] Therefore, in the radial movement suppression member 70a1-3 of this embodiment, the abutting member 71a1-3 forms a point contact Ca-3 with respect to the guide portion 32. This reduces the sliding resistance of the guide portion 32, which rotates relative to the abutting member 71a1-3, resulting in efficient transmission of the driving force of the stepper motor 60 to the valve core 42. Furthermore, while the spherical contact portion 71a1c-3 in this embodiment is fixed relative to the abutting member 71a1-3, this is not a limitation. For example, by employing a component that is held in a rotatable position, such as a bearing, the sliding resistance can be further reduced.

[0132] (Variation Example 2-2(2))

[0133] Here, as Figure 6As shown in (a), in the radial movement suppression member 70a1-3 of the first embodiment's variant 2-2(1), since the contact state between the abutting member 71a1-3 and the guide portion 32 becomes a point contact Ca-3, there is a concern that the abutting member 71a1-3 is prone to tilting relative to the horizontal direction. As a result, the force exerted by the force-applying member 72a1 is also applied via the abutting member 71a1-3 in a direction that is not perpendicular to the axis L of the guide portion 32, thus raising concerns that the pressing pressure of the guide portion 32 on the bearing hole 24 cannot be stabilized.

[0134] In response to this, such as Figure 6 As shown in (c) and (d), in the radial movement suppression member 70a1-4 of the modified example 2-2 (2) of the first embodiment, when viewed from the axis L direction, the contact portion 71a1c-4 of the abutment member 71a1-4 opposite to the guide portion 32 has two spherical shapes arranged along the axis L direction. Therefore, as Figure 6 As shown in (d), the contact state between the abutting part 71a1-4 and the guide part 32 is two point contacts Ca-4 arranged along the axis L.

[0135] Thus, in the radial movement suppression member 70a1-4 of this embodiment, since the abutting member 71a1-4 forms two point contacts Ca-4 arranged along the axis L relative to the guide portion 32, the abutting member 71a1-4 will not tilt relative to the horizontal direction. Therefore, the force of the force-applying member 72a1 is applied only in the direction perpendicular to the axis L of the guide portion 32 via the abutting member 71a1-4, thereby stabilizing the pressing pressure of the guide portion 32 on the bearing hole 24. Furthermore, in this embodiment, similar to variant 2-2(1), the sliding resistance of the guide portion 32, which rotates relative to the abutting member 71a1-4, can be made relatively small, resulting in the efficient transmission of the driving force of the stepper motor 60 to the valve core 42. In addition, the contact portion 71a1c-4 with a spherical shape in this embodiment is fixed relative to the abutting member 71a1-4, but it is not limited to this. For example, by using a component that is held to rotate, such as a bearing, the sliding resistance can be further reduced.

[0136] (Modification 3 of the first embodiment)

[0137] Here, use Figures 7 to 9 The radial movement suppression members 70a8 and 70a9 of the first embodiment's variation 3 will be described. The radial movement suppression members 70a8 and 70a9 in this first embodiment's variation 3 are mainly provided with structures to suppress the loosening of the abutment members 71a' and 71a" within the mounting holes 75a and 75a". This is similar to the first embodiment's variations 1-2 (1) (see...). Figure 3The radial movement suppression member 70a4 in (a) is different, but the other basic structures are the same as those in variations 1-2 (1) of the first embodiment. Here, the same symbol is used for the same component, and repeated descriptions are omitted. In addition, in the support portion 21 of this embodiment, as Figure 7 and Figure 8 As shown, in order to stabilize the shrinkage during resin molding and obtain the desired shape and size, radial grooves 21a, 21a” are formed on the side opposite to the mounting holes 75a, 75a” relative to the axis L.

[0138] like Figure 3 As shown in (a), in the radial movement suppression member 70a4 of the modified examples 1-2 (1) of the first embodiment, the inner peripheral surface and the outer peripheral top of the abutment member 71a are perpendicular to the axis L in the horizontal plane relative to the guide portion 32 and the force-applying member 72a4. Figure 3 The contact is along a straight line in the left-right direction of (a). That is to say, the force F1 (refer to) Figure 1 (b) is formed along this straight line. Here, in the radial movement suppression member 70a4, in order to facilitate smooth assembly, a small gap is provided between the abutment member 71a and the mounting hole 75a in the circumferential and axial directions, so that the abutment member 71a is housed in the mounting hole 75a. Due to this assembly gap, whenever the guide portion 32 rotates and moves along the axial direction L, the abutment member 71a moves in conjunction with the guide portion 32, tilting relative to the orthogonal direction of the axial direction L and the axial direction L. As a result, the direction of the force F1 is not constant, and there is a concern that the abutment member 71a may not be able to press the guide portion 32 in a stable state.

[0139] In response to this, the radial movement suppression members 70a8 and 70a9 in the first embodiment of the modified example 3 are provided with a structure to suppress the loosening of the abutment members 71a' and 71a” in the mounting holes 75a and 75a”, including two methods: modified example 3-1 (structure to suppress circumferential loosening) and modified example 3-2 (structure to suppress loosening in the axial direction L).

[0140] (Variation 3-1)

[0141] First, the radial movement suppression member 70a8 in the first embodiment, variation 3-1, has a structure that suppresses circumferential loosening. Specifically, the radial movement suppression member 70a8 includes an abutment member 71a', which is generally L-shaped, having an abutment portion 71a'1 that abuts against the guide portion 32, and a force-applying portion 71a'2 that extends circumferentially along the outer peripheral surface of the support portion 21 away from the axis L71a' of the abutment portion 71a'1 and abuts against the force-applying member 72a4. Regarding the assembly of the radial movement suppression member 70a8, with the abutment member 71a' housed in the mounting hole 75a, the force-applying member 72a4 is assembled in the circumferential mounting groove 76a4 discontinuously formed on the outer peripheral surface of the support portion 21, and the protrusion 21b of the support portion 21 is positioned between a pair of cut-out ends 72a4n of the force-applying member 72a4. At this time, the force-applying component 72a4, through contact with the force-applying portion 71a'2 of the abutment component 71a', always applies a torque M1 to the abutment component 71a' within the mounting hole 75a. Through this torque M1, the axis L71a' of the abutment portion 71a'1 is tilted relative to the axis of the mounting hole 75a. As a result, the abutment component 71a' is firmly supported by two abutment portions (see the × mark in the figure) separated circumferentially in the mounting hole 75a, thus restricting circumferential rotation.

[0142] Furthermore, for the purpose of explanation, the modified example 3-1 of this embodiment is based on the modified example 1-2 (1), wherein the anti-rotation part and the anti-rotation engagement part of the force-applying member 72a4 adopt a protrusion 21b and a pair of cut-out ends 72a4n (see reference). Figure 3 (a)). However, not limited thereto, the anti-rotation part and the anti-rotation engagement part of the force-applying component may, for example, adopt a limit pin and a pair of cut-out ends (see (a)). Figure 3 (c)), radial grooves and a pair of radially folded-back ends (see reference) Figure 3 (e)), axial groove and a pair of axially bent ends (refer to) Figure 3 (g) any one of them.

[0143] Therefore, in the radial movement suppression member 70a8 of this embodiment, the abutting member 71a' is inclined in the orthogonal direction relative to the axis L and interferes with the mounting hole 75a, thus suppressing circumferential loosening of the abutting member 71a' within the mounting hole 75a. Consequently, the abutting member 71a' can press the guide portion 32 in a stable state without being linked to the rotation of the guide portion 32. Furthermore, in the radial movement suppression member 70a8 of this embodiment, since the torque M1 is set larger than the torque generated in the abutting member 71a' that is linked to the rotation of the guide portion 32, even if the guide portion 32 not only moves towards the guide portion 32, the radial movement suppression member 70a8 can still suppress circumferential loosening of the guide portion 32. Figure 7Even when rotating from the clockwise direction to the counterclockwise direction, that is, even if a torque is generated in the direction of the counteracting torque M1, the abutment member 71a' can be firmly supported in the mounting hole 75a.

[0144] (Variation 3-2)

[0145] In the radial movement suppression member 70a8 of the first embodiment variation 3-1, since the diameter of the force-applying member 72a4 is set to be relatively small, during the assembly of the radial movement suppression member 70a8, the force-applying member 72a4, the internal thread limiter (not shown), and the guide rail 26 (see reference) are included. Figure 1 There are concerns about interference. Furthermore, in the radial movement suppression member 70a8, when assembled with the diameter of the force-applying member 72a4 set to a relatively large value, there is a connection between the force-applying member 72a4 and the protrusion 67 of the magnetic rotor 62 (see reference). Figure 1 Concerns about interference.

[0146] In response to this, the radial movement suppression member 70a9 in the modified example 3-2 of the first embodiment has the following structure: it suppresses loosening in the direction of the axis L, and during assembly, it suppresses interference between the force-applying member 72a9 and other members. Specifically, as Figure 8 and Figure 9 As shown, the radial movement suppression member 70a9 includes an abutment member 71a”, which is generally L-shaped and has an abutment portion 71a”1 that abuts against the guide portion 32, and an axis L71a (see reference) extending from the abutment portion 71a”1. Figure 8The force-applying part 71a”2 extends along the axis L of the outer peripheral surface of the support part 21 and abuts against the force-applying member 72a9 in the manner of (b) leaving. Furthermore, the radial movement suppression member 70a9 includes: a protrusion (anti-rotation part) 21b” formed on the outer peripheral surface of the support part 21; a circumferential mounting groove 76a” formed discontinuously on the outer peripheral surface of the support part 21 through the protrusion 21b”; a plurality of anti-detachment claw parts 21f formed on the upper part of the circumferential mounting groove 76a” on the outer peripheral surface of the support part 21; and a force-applying member 72a9 having a pair of cut-out ends (anti-rotation engaging parts) (a pair of ends) 72a9n extending in the circumferential direction. Regarding the assembly of the radial movement suppression member 70a9, with the abutment member 71a” housed in the mounting hole 75a”, the force-applying member 72a9 is assembled between the circumferential mounting groove 76a” discontinuously formed on the outer peripheral surface of the support portion 21 and the circumferential mounting groove 71a” 21 of the abutment member 71a” and the multiple anti-disengagement claw portions 21f. Furthermore, the force-applying member 72a9 has a protrusion 21b” of the support portion 21 disposed between a pair of cut ends 72a9n, and is configured such that the center position Oa of the force-applying member 72a9 is offset from the axis L towards the abutment member 71a” side. Here, since the diameter of the force-applying member 72a9 is set to be relatively large, it will not interfere with the internal thread limiter (not shown) or the guide rail 26. In addition, since the force-applying member 72a9 is mounted below the protrusion 67 of the magnetic rotor 62 in the direction of the axis L, it will not interfere with the protrusion 67. At this time, as... Figure 8 As shown in (b), the force-applying member 72a9 always applies a torque M2 to the abutment member 71a" within the mounting hole 75a" by contacting the force-applying portion 71a"2 of the abutment member 71a". Through this torque M2, the axis L71a" of the abutment portion 71a"1 is tilted relative to the axis of the mounting hole 75a". As a result, the abutment member 71a" is firmly supported by two abutment portions (see × in the diagram) separated in the direction of the axis L of the mounting hole 75a", thus restricting rotation along the axis L.

[0147] Furthermore, in variation 3-2 of this embodiment, the anti-rotation portion and anti-rotation engaging portion of the force-applying member 72a9 adopt a protrusion 21b” and a pair of cut-out ends 72a9n. However, it is not limited to this; for example, the anti-rotation portion and anti-rotation engaging portion of the force-applying member may also adopt a limiting pin and a pair of cut-out ends (see reference). Figure 3 (c)), radial grooves and a pair of radially folded-back ends (see reference) Figure 3 (e)), axial groove and a pair of axially bent ends (refer to) Figure 3 Any of (g)).

[0148] Therefore, in the radial movement suppression member 70a9 of this embodiment, since the diameter of the force-applying member 72a9 is set to be relatively large, it will not interfere with the support member 20”, the magnetic rotor 62, etc., thus improving the freedom of the force-applying height position and the assemblability of the force-applying member 72a9. Furthermore, in the radial movement suppression member 70a9 of this embodiment, the abutting member 71a” is inclined relative to the axis L direction and interferes with the mounting hole 75a”, thus suppressing the loosening of the abutting member 71a” in the axis L direction within the mounting hole 75a”. As a result, the abutting member 71a’ can press the guide portion 32 in a stable state without being linked to the movement of the guide portion 32 in the axis L direction. Furthermore, in the radial movement suppression member 70a9 of this embodiment, since the torque M2 is set to be larger than the torque generated in the abutting member 71a” that is linked to the movement of the guide portion 32 in the axis L direction, even if the guide portion 32 not only moves towards the guide portion 32, the torque M2 is also suppressed. Figure 8 Even when the axis L shown in (b) moves downwards, that is, even when a torque is generated in the direction of the counteracting torque M2, the abutment member 71a is firmly supported in the mounting hole 75a”.

[0149] Furthermore, for illustrative purposes, Modification 3 of the first embodiment shows a structure for suppressing circumferential loosening in Modification 3-1 and a structure for suppressing loosening in the axial direction L in Modification 3-2. However, it is not limited to this. For example, as a structure for suppressing loosening in both the circumferential and axial directions L, the force-applying portion 71a”2 of the abutment member 71a” in Modification 3-2 is provided at an angle relative to the axial direction L, thereby the axis L71a” of the abutment portion 71a”1 is configured in a torsional relationship relative to the axis of the mounting hole 75a”. As a result, the abutment member 71a” is firmly supported by two abutment portions that are separated in both the axial direction L and the circumferential direction of the mounting hole 75a”, thus simultaneously restricting rotation in both the axial direction L and the circumferential direction.

[0150] (Second Implementation)

[0151] use Figure 10 The electric valve 100b of the second embodiment will be described. The shapes of the abutment member 71b and the mounting hole 75b of the electric valve 100b of the second embodiment differ from those of the electric valve 100a of the first embodiment, but other basic structures are the same as those of the first embodiment. Here, the same symbols are used to denote the same structure, and repeated descriptions are omitted. Furthermore, the structures of the force-applying member 72b and the circumferential mounting groove 76b are the same as those of the force-applying member 72a and the circumferential mounting groove 76a, but different symbols are used for ease of explanation.

[0152] The radial movement suppression member 70b of the second embodiment includes: an abutment member 71b made of a resin-based material with high sliding properties; a force-applying member 72b made of a C-ring; a mounting hole 75b that connects the inner and outer peripheral surfaces of the support portion 21 with the same diameter in the orthogonal direction of the axis L; and a circumferential mounting groove 76b continuously formed on the outer peripheral surface of the support portion 21. The abutment member 71b has an elongated elliptical shape. In this embodiment, the abutment member 71b is preferably made of a resin-based material such as polyphenylene sulfide (PPS) containing fluorine. The abutment member 71b in this embodiment has an elongated elliptical shape, but it is not limited to this, as long as the shape is suitable for the mounting hole 75b with the same diameter.

[0153] <Assembly of Radial Movement Suppression Components>

[0154] like Figure 10 As shown, with the abutting member 71b housed in the mounting hole 75b, a force F2 is generated in the guide portion 32 via the abutting member 71b in the orthogonal direction of the axis L by mounting the force-applying member 72b in the circumferential mounting groove 76b. Similar to the force F1 in the first embodiment, this force F2 is set to be greater than the magnetic attraction force of the stepper motor 60. Furthermore, similar to the radial movement suppression member 70a in the first embodiment, the radial movement suppression member 70b ensures that the external thread portion 31a always maintains a small gap relative to the internal thread portion 23a in the radial direction.

[0155] Thus, in the electric valve 100b of the second embodiment, by using a radial movement suppression member 70b instead of a radial movement suppression member 70a, in addition to achieving the same effect as the first embodiment (low operating noise), the shape of the abutment member 71b and the mounting hole 75b can be simplified, thereby reducing costs.

[0156] (Third Implementation)

[0157] use Figure 11 The electric valve 100c of the third embodiment will be described. The structure of the radial movement suppression member 70c of the electric valve 100c of the third embodiment differs from that of the electric valve 100a of the first embodiment, but other basic structures are the same as those of the first embodiment. Here, the same symbols are used to denote the same structure, and repeated descriptions are omitted. Furthermore, the structure of the mounting hole 75c is the same as that of the mounting hole 75b, but different symbols are used for ease of explanation.

[0158] The radial movement suppression member 70c of the third embodiment includes: an abutment member 71c made of a resin-based material with high sliding properties; a force-applying member 72c made of a compression coil spring; a retaining member 73c that clamps the force-applying member 72c between itself and the abutment member 71c; a mounting hole 75c that connects the inner and outer peripheral surfaces of the support portion 21 with the same diameter in the orthogonal direction of the axis L; and an axially outward mounting groove 77c formed with a stepped portion on the outer peripheral surface of the support portion 21. The abutment member 71c has an expanded-diameter cylindrical shape. In this embodiment, the abutment member 71c is preferably made of a resin-based material such as polyphenylene sulfide (PPS) containing fluorine. The abutment member 71c in this embodiment has an expanded-diameter cylindrical shape, but it is not limited to this, as long as the shape is suitable for the mounting hole 75c with the same diameter.

[0159] <Assembly of Radial Movement Suppression Components>

[0160] like Figure 11 As shown in (a) and (b), with the abutting member 71c housed in the mounting hole 75c, a force F3 in the orthogonal direction of the axis L is generated in the guide portion 32 via the abutting member 71c by assembling the retaining member 73c, which holds the force-applying member 72c between the abutting member 71c and the guide member 75c, into the mounting groove 77c on the outer side of the axis. Similar to the force F1 in the first embodiment, this force F3 is set to be greater than the magnetic attraction force of the stepper motor 60. Furthermore, similar to the radial movement suppression member 70a in the first embodiment, the radial movement suppression member 70c ensures that the external thread portion 31a always maintains a small gap relative to the internal thread portion 23a in the radial direction.

[0161] Thus, in the electric valve 100c of the third embodiment, by using a radial movement suppression member 70c instead of a radial movement suppression member 70a, in addition to obtaining the same effect as the first embodiment (low operating noise), by preparing a force-applying member 72c with various spring constants, the force F3 can be adjusted without changing the abutment member 71c.

[0162] (Fourth Implementation)

[0163] use Figure 12 The electric valve 100d according to the fourth embodiment will be described. The structure of the radial movement suppression member 70d of the electric valve 100d in the fourth embodiment differs from that of the electric valve 100a in the first embodiment, but the other basic structures are the same as those in the first embodiment. Here, the same symbols are used to denote the same structures, and repeated descriptions are omitted.

[0164] The radial movement suppression member 70d of the fourth embodiment includes: an abutting member 71d made of an elastic member in the shape of a ring (such as an O-ring); a retaining member 73d that clamps the abutting member 71d between itself and the guide portion 32; an anti-detachment ring 74d that fixes and supports the retaining member 73d from below; and an axially inward mounting groove 78d formed in such a way that it has a stepped portion on the inner circumferential surface of the bracket portion 21.

[0165] The retaining component 73d is an annular sleeve made of a resin-based material with high sliding properties, such as... Figure 12 As shown in (a), it has a sliding portion 73du that is slidably positioned close to the guide portion 32, and a receiving portion 73dd located below the sliding portion 73du and slidably housing the abutment member 71d. Figure 12 As shown in (b), the receiving portion 73dd has an outer peripheral surface 73do formed concentrically with respect to the axis L and an inner peripheral surface 73di eccentrically with respect to the axis L. In this embodiment, the retaining member 73d is preferably a resin-based material such as polyphenylene sulfide (PPS) or polytetrafluoroethylene (PTFE) containing fluorine.

[0166] <Assembly of Radial Movement Suppression Components>

[0167] First, the retaining member 73d is embedded and fixed in the mounting groove 78d on the inner side of the bracket portion 21 in the axial direction. Then, the abutting member 71d is housed in the receiving portion 73dd of the retaining member 73d, and the drive shaft 30 is inserted from below the bracket portion 21 upward along the axial direction L via the bearing hole 24 while being threaded into the threaded feed mechanism. Furthermore, the retaining member 73d and the abutting member 71d are supported from below by an anti-detachment ring 74d, and the anti-detachment ring 74d is fixed to the bracket portion 21 by welding or the like. As a result, the abutting member 71d can be clamped between the guide portion 32 and the inner circumferential surface 73di of the retaining member 73d.

[0168] Here, the mounting groove 78d on the inner side of the bracket portion 21 in the axial direction and the outer peripheral surface 73do of the retaining member 73d are both formed concentrically with the axis L. On the other hand, the inner peripheral surface 73di of the retaining member 73d is formed to have a center point Od that is eccentric relative to the axis L. Furthermore, the annular width in the radial direction of the abutting member 71d in the uncompressed state, as viewed from the axis L direction, is set to be greater than the maximum annular width in the radial direction between the guide portion 32 and the inner peripheral surface 73di of the retaining member 73d (see reference). Figure 12 (b) is larger on the left. In addition, the diameter of the annular opening of the abutment member 71d, as viewed from the axis L direction, is set to be smaller than the diameter of the guide portion 32, so the inner circumferential surface of the abutment member 71d is held to contract toward the guide portion 32 by its own elastic force.

[0169] Thus, by clamping the abutting member 71d between the guide portion 32 and the inner circumferential surface 73di of the retaining member 73d, the abutting member 71d deforms in the orthogonal direction of the axis L, and a force F4 in the orthogonal direction of the axis L is generated in the guide portion 32. Furthermore, since the retaining member 73d is embedded and fixed in the mounting groove 78d inside the axial direction of the bracket portion 21, the inner circumferential surface 73di of the retaining member 73d slides relative to the abutting member 71d. Similar to the force F1 in the first embodiment, this force F4 is set to be greater than the magnetic attraction force of the stepper motor 60. Also, similar to the radial movement suppression member 70a in the first embodiment, the radial movement suppression member 70d enables the external thread portion 31a to always maintain a small gap relative to the internal thread portion 23a in the radial direction.

[0170] Thus, in the electric valve 100d of the fourth embodiment, by using a radial movement suppression member 70d instead of a radial movement suppression member 70a, in addition to obtaining the same effect as the first embodiment (low operating noise), by preparing a holding member 73d with a center point Od having various eccentricities, the force F4 can be adjusted without changing the abutting member 71d.

[0171] Furthermore, in the electric valves 100a to 100c of the first to third embodiments, since abutment members 71a, 71b, and 71c are provided in the mounting holes 75a, 75b, and 75c that extend in the orthogonal direction along the axis L, there is a concern that fluid movement through the mounting holes 75a, 75b, and 75c may affect the movement of the abutment members 71a, 71b, and 71c in the direction in which force is applied. To address this, in the electric valve 100d of the fourth embodiment, by arranging all the structures of the radial movement suppression member 70d inside the support portion 21, the influence of fluid movement in the direction in which force is applied to the abutment member 71d can be suppressed, thereby enabling it to function more reliably.

[0172] (Fifth Implementation)

[0173] use Figure 13 The electric valve 100e of the fifth embodiment will be described. The electric valve 100e of the fifth embodiment omits the retaining member 73d, the anti-detachment ring 74d, and the inner mounting groove 78d in the axial direction, which differs from the electric valve 100d of the fourth embodiment, but the other basic structures are the same as those of the fourth embodiment. Here, the same symbols are used to refer to the same structures, and repeated descriptions are omitted.

[0174] The radial movement suppression member 70e of the fifth embodiment includes an abutment member 71e made of an annular elastic member (such as an O-ring) and a circumferential groove 79e of a guide portion 32 formed eccentrically relative to the axis L.

[0175] <Assembly of Radial Movement Suppression Components>

[0176] First, the abutment member 71e is received in the circumferential groove 79e of the guide portion 32, and the drive shaft 30 is inserted from below the bracket portion 21 upward along the axis L direction via the bearing hole 24 while being threadedly connected to the threaded feed mechanism portion. As a result, the abutment member 71e can be clamped between the guide portion 32 and the bearing hole 24.

[0177] Here, the bearing hole 24 is formed concentrically with the axis L, while the circumferential groove 79e of the guide portion 32 is formed with a center point Oe that is eccentric relative to the axis L. Furthermore, the annular width in the radial direction of the abutment member 71e in its uncompressed state, as viewed from the axis L direction, is set to be greater than the maximum annular width in the radial direction of the circumferential groove 79e of the guide portion 32 (see reference). Figure 13 (b) is larger on the left. In addition, the diameter of the annular opening of the abutment member 71e, as viewed from the axis L direction, is set to be smaller than the diameter of the non-circumferential groove of the guide portion 32. Therefore, the inner circumferential surface of the abutment member 71e is held to contract toward the guide portion 32 by its own elastic force.

[0178] Thus, by clamping the abutment member 71e between the guide portion 32 and the bearing hole 24, the abutment member 71e deforms in the orthogonal direction of the axis L, and a force F5 in the orthogonal direction of the axis L is generated in the guide portion 32. Furthermore, since the abutment member 71e is held within the circumferential groove 79e of the guide portion 32 by its own elastic force, the outer circumferential surface of the abutment member 71e slides relative to the bearing hole 24. Similar to the force F1 in the first embodiment, this force F5 is set to be greater than the magnetic attraction force of the stepper motor 60. Also, similar to the radial movement suppression member 70a in the first embodiment, the radial movement suppression member 70e ensures that the external thread portion 31a always maintains a small gap relative to the internal thread portion 23a in the radial direction. Furthermore, since the radial movement suppression member 70e in this embodiment is provided between the bearing hole 24 and the guide portion 32, the abutment member 71e does not overlap with the internal thread portion 23a, and does not affect the movement of the drive shaft 30 in the direction of the axis L.

[0179] Thus, in the electric valve 100e of the fifth embodiment, by employing a radial movement suppression member 70e in addition to the radial movement suppression member 70d, the same effect as that of the fourth embodiment (low operating noise and suppression of fluid movement) can be achieved.

[0180] Furthermore, in the electric valves 100a-100d of the first to fourth embodiments, when viewed from the axis L direction, the directions of the forces F1-F4 of the radial movement suppression members 70a-70d are fixed in one direction regardless of the rotation of the drive shaft 30. Therefore, there is a concern about excessive one-sided wear in the thread feed mechanism. To address this, in the electric valve 100e of the fifth embodiment, the inner circumferential surface of the abutment member 71e is held in place by its own elastic force in the guide portion 32, while the outer circumferential surface of the abutment member 71e slides relative to the bearing hole 24. As a result, the direction of the force F5, viewed from the axis L direction, rotates together with the drive shaft 30, thus suppressing one-sided wear in the thread feed mechanism.

[0181] Furthermore, in this embodiment, the use of a radial movement suppression member in electric valves 100a to 100d is described. In these electric valves 100a to 100d, an external thread portion 31a is provided on the drive shaft 30 connected to the magnetic rotor 62, and an internal thread portion 23a is fixed to the valve body 10, allowing the external thread portion 31a to move relative to the internal thread portion 23a along the axis L. However, this is not a limitation. For example, an electric valve may have an internal thread portion on the inner circumferential surface of the magnetic rotor, and an external thread portion fixed to the valve body, allowing the internal thread portion to move relative to the external thread portion along the axis L. In such an electric valve, a radial movement suppression member can be used to apply force to the drive shaft connected to the magnetic rotor in the orthogonal direction of the axis L.

[0182] <About the Refrigeration Cycle System>

[0183] use Figure 14 The refrigeration cycle system of the present invention will be described. The refrigeration cycle system includes: an expansion valve 100 using electric valves 100a-100e of the first to fifth embodiments; an outdoor heat exchanger 200 mounted in the outdoor unit; an indoor heat exchanger 300 mounted in the indoor unit; a flow path switching valve 400 constituting a four-way valve; and a compressor 500. Here, the expansion valve 100, outdoor heat exchanger 200, indoor heat exchanger 300, flow path switching valve 400, and compressor 500 are connected by conduits to form a heat pump type refrigeration cycle. Furthermore, illustrations of the energy storage unit, pressure sensor, temperature sensor, etc., are omitted.

[0184] The flow path of the refrigeration cycle is switched between two paths: the flow path during cooling operation and the flow path during heating operation, via the flow path switching valve 400. During cooling operation (refer to the solid arrow in the figure), the refrigerant compressed by the compressor 500 flows from the flow path switching valve 400 into the outdoor heat exchanger 200, which functions as a condenser. The liquid refrigerant flowing out of the outdoor heat exchanger 200 flows into the indoor heat exchanger 300 via the expansion valve 100, which functions as an evaporator.

[0185] On the other hand, during heating operation (refer to the dotted arrow in the diagram), the refrigerant compressed by the compressor 500 circulates from the flow path switching valve 400 in the following sequence: indoor heat exchanger 300, expansion valve 100, outdoor heat exchanger 200, flow path switching valve 400, and compressor 500. The indoor heat exchanger 300 functions as a condenser, and the outdoor heat exchanger 200 functions as an evaporator. Therefore, the expansion valve 100 causes the liquid refrigerant flowing into the outdoor heat exchanger 200 during cooling operation, or the liquid refrigerant flowing into the indoor heat exchanger 300 during heating operation, to depressurize and expand, and can control the flow rate of the refrigerant.

[0186] Furthermore, the present invention is not limited to the first to fifth embodiments, and includes other structures that can achieve the purpose of the present invention. The present invention also includes the modifications shown below. For example, in the first to fifth embodiments, electric valves 100a to 100e used in air conditioners such as household air conditioners are shown as examples, but the electric valves of the present invention are not limited to household air conditioners, but can also be used in commercial air conditioners, and are not limited to air conditioners, but can also be applied to various refrigeration units, etc.

[0187] <Other>

[0188] Of course, the electric valves 100a to 100e of this embodiment can be applied not only to the illustrated refrigeration cycle, but also to all fluid devices and fluid circuits. Furthermore, the present invention is not limited to the various methods, embodiments, and variations described above, and appropriate changes and modifications can be made without departing from the technical concept of the present invention.

Claims

1. An electric valve, characterized in that, have: The drive shaft moves along the axial direction through a threaded feed mechanism that converts rotary motion into linear motion by threading an external threaded part and an internal threaded part. The support component has a bearing portion that engages with a cylindrical guide portion of the drive shaft and can slide along the axial direction to guide the guide portion. The valve core, connected to the guide portion of the aforementioned drive shaft, adjusts the opening degree between the valve port and the valve seat; and A radial movement suppression member applies force to one of the external threaded portion and the internal threaded portion in a direction orthogonal to the axis, thereby suppressing the relative radial movement of the external threaded portion and the internal threaded portion. The aforementioned radial movement suppression member is located only between the aforementioned bearing portion and the aforementioned guide portion, and applies force to the aforementioned guide portion.

2. The electric valve according to claim 1, characterized in that, The radial movement suppression member has an abutting member that contacts the drive shaft, and forces are applied to one of the external thread portion and the internal thread portion in the orthogonal direction of the axis via the abutting member.

3. The electric valve according to claim 2, characterized in that, The contact state between the drive shaft of the radial movement suppression member and the abutting member is at least one line contact extending along the axial direction of the drive shaft.

4. The electric valve according to claim 2, characterized in that, The contact state between the drive shaft of the radial movement suppression member and the abutting member is at least one point contact.

5. The electric valve according to claim 2, characterized in that, The aforementioned abutting component is disposed facing the outer peripheral surface of the aforementioned drive shaft. The aforementioned radial movement suppression member also has a force-applying member that applies force to the aforementioned abutting member.

6. The electric valve according to claim 5, characterized in that, The aforementioned abutting member is generally L-shaped, having an abutting portion that abuts against the aforementioned drive shaft, and a force-applying portion that extends along the outer peripheral surface of the aforementioned support member and abuts against the aforementioned force-applying member in a manner that departs from the axis of the aforementioned abutting portion.

7. The electric valve according to claim 6, characterized in that, The force-applying part extends along the axial direction of the outer peripheral surface of the support component.

8. The electric valve according to claim 5, characterized in that, The force-applying component is C-shaped with a slit, and anti-rotation engaging portions are provided at a pair of ends of the force-applying component, which are directly or indirectly held in place by the support component.

9. The electric valve according to claim 8, characterized in that, An anti-rotation portion is provided on the radially outer side of the abutting member. By engaging the anti-rotation engagement portion of the force-applying member with the anti-rotation engagement portion of the force-applying member, the force-applying member is held in the support member via the abutting member.

10. The electric valve according to claim 8, characterized in that, A circumferential mounting groove is formed on the outer peripheral surface of the aforementioned support member. An anti-rotation part is provided on the aforementioned support member in such a discontinuous manner as the circumferential mounting groove. The anti-rotation part engages with the anti-rotation engagement part of the aforementioned force-applying member, thereby holding the aforementioned force-applying member on the aforementioned support member.

11. The electric valve according to claim 8, characterized in that, A continuous circumferential mounting groove is formed on the outer peripheral surface of the support member, and an anti-rotation part is provided that is continuously connected to the circumferential mounting groove in the radially inner direction or in the axial direction. The anti-rotation part engages with the anti-rotation engagement part of the force-applying member, thereby holding the force-applying member on the support member.

12. The electric valve according to claim 5, characterized in that, The radial movement suppression member further includes a retaining member that clamps the force-applying member between itself and the abutting member.

13. The electric valve according to claim 2, characterized in that, The aforementioned abutting member is composed of a ring-shaped elastic member and also has a retaining member that clamps the abutting member between itself and the aforementioned drive shaft when it is deformed in the orthogonal direction of the axis.

14. The electric valve according to claim 2, characterized in that, The aforementioned abutting member is composed of a ring-shaped elastic component, which is arranged in the circumferential groove of the aforementioned drive shaft in a state of deformation along the orthogonal direction of the axis.

15. The electric valve according to claim 1, characterized in that, The valve core is connected to the drive shaft in a manner that allows for radial relative displacement. The aforementioned radial movement suppression member applies force to the aforementioned drive shaft.

16. A refrigeration cycle system comprising a compressor, a condenser, an expansion valve, and an evaporator, characterized in that, The electric valve described in any one of claims 1 to 15 is used as the aforementioned expansion valve.

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