Rotary switching valve

Abstract

To provide a rotary type selector valve capable of stabilizing switching operation by preventing the positional deviation of a main valve.SOLUTION: A rotary type selector valve 1 includes a valve body 10 including a valve chest 11, a valve seat part 20, a main valve 30, a sub valve 40, and driving means 50, the main valve 30 being provided with a low pressure flow path 31a, and a pressure equalization hole 31b, the valve body 10 or the valve seat part 20 being provided with a main valve stopper 29 which abuts on the main valve 30 at a predetermined switching position to stop the rotation of the main valve 30 rotated in the rotating direction of a rotary shaft 53. Between the valve body 10 and the main valve 30, rotation restricting means 60 is provided for restricting the rotation of the main valve 30 from the switching position in the direction opposite to the rotating direction. The rotation restricting means 60 has a holding part 62 provided on one of the valve body 10 and the main valve 30 for holding the other, and a held part 61 provided on the other and held by the holding part 62.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a rotary switching valve.

Background Art

[0002] A rotary switching valve including a valve housing having a valve chamber, a valve seat member disposed within the valve housing, a main valve that slidably contacts the valve seat member and rotates about a central axis intersecting the upper surface of the valve seat member, a sub-valve housed within the main valve, and a drive unit that rotationally drives the sub-valve is known (see, for example, Patent Documents 1 and 2). In this type of rotary switching valve, a valve passage formed in the main valve communicates a plurality of ports among the ports formed in the valve seat member. The main valve is formed with a pressure equalizing hole that communicates inside and outside. When the pressure equalizing hole is closed, the main valve is pressed against the valve seat member by the differential pressure inside and outside the main valve. On the other hand, when the pressure equalizing hole is open, the force pressing the main valve against the valve seat member is reduced by canceling the differential pressure. The main valve rotates as the sub-valve is rotationally driven with the pressure equalizing hole open, and switches the ports to be communicated.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the rotary switching valve described in Patent Document 1, the main valve and the sub-valve can be rotationally transmitted through a plurality of convex portions that mesh with each other (in this specification, these plurality of convex portions are also collectively referred to as a clutch). The clutch meshes with each other with the pressure equalizing holes of the main valve open, and in this state, the rotation of the sub-valve is transmitted to the main valve. The main valve that has rotated together with the sub-valve abuts against a stopper at a predetermined switching position and stops. Thereafter, only the sub-valve rotates with respect to the main valve, and the convex portion of the sub-valve rides on the convex portion of the main valve to close the pressure equalizing hole. However, according to such a configuration, if the rotational resistance of the main valve becomes larger than expected, the meshing of the clutch may be disengaged before the main valve rotates to the predetermined switching position, and the rotation may not be transmitted to the main valve. Further, even when the main valve is normally rotated to the predetermined switching position, the state where the convex portion of the sub-valve rides on the convex portion of the main valve as described above is a state where the clutch is disengaged, and since the reverse rotation of the main valve is not restricted, there is a possibility that the main valve may deviate from the switching position due to the fluid force.

[0005] In the rotary switching valve described in Patent Document 2, the rotation of the sub-valve is transmitted to the main valve by locking the main valve and the sub-valve with each other's locking portions, and after the main valve that has rotated with the pressure equalizing hole open abuts against a stopper at a predetermined switching position and stops, the sub-valve rotates in the reverse direction to close the pressure equalizing hole. However, there is a possibility that the main valve may also rotate in the reverse direction along with the reverse rotation of the sub-valve, the pressure equalizing hole may not be normally closed, and the main valve may deviate from the switching position.

[0006] An object of the present invention is to obtain a rotary switching valve capable of stabilizing the switching operation by preventing displacement of the main valve.

Means for Solving the Problems

[0007] In order to solve the above problems and achieve the object, the rotary switching valve of the present invention includes a valve body having a valve chamber, a valve seat portion having a plurality of ports opening into the valve chamber, a main valve rotatably provided in the valve chamber around the axis of a rotating shaft that intersects the upper surface of the valve seat portion on the valve seat portion, a sub-valve rotatably provided with respect to the main valve, and a driving means for rotationally driving the sub-valve. The rotary switching valve is characterized in that the main valve is provided with a valve passage communicating with the port and an equalizing hole communicating the valve passage and the valve chamber. The sub-valve opens and closes the equalizing hole. The valve body or the valve seat portion is provided with a main valve stopper that abuts against the main valve at a predetermined switching position to stop the rotation of the main valve rotating in the rotational direction around the axis of the rotating shaft. Between the valve body and the main valve, a rotation restricting means for restricting the rotation of the main valve in the reverse rotation direction, which is the direction opposite to the rotational direction, from the switching position is provided. The rotation restricting means has a holding portion provided on one of the valve body and the main valve and capable of holding the other, and a held portion provided on the other and held by the holding portion. The main valve has a main valve seat surface with which the sub-valve makes sliding contact, a sub-valve stopper that abuts against the sub-valve to stop relative rotation therebetween, and a low-pressure flow path that communicates two of the plurality of ports. The pressure equalizing hole is formed from the low-pressure flow path across the main valve seat surface. The sub-valve has a sub-valve seat surface that makes sliding contact with the main valve seat surface, a contact portion that abuts against the sub-valve stopper, and a sub-valve flow path that is formed by notching the sub-valve seat surface and can communicate with the pressure equalizing hole. It is characterized by the above.

[0008] According to the present invention as described above, the main valve that abuts against the main valve stopper at a predetermined switching position and stops rotating in the rotational direction is restricted from rotating in the reverse rotation direction by the rotation restricting means. For this reason, it is possible to suppress valve leakage and the like caused by the unintentional displacement of the main valve from the predetermined switching position, and to maintain well the state in which the switching of the port is normally performed. Therefore, it is possible to obtain a rotary switching valve capable of stabilizing the switching operation by preventing the displacement of the main valve.

[0009] Also, at this time , before The sub-valve is rotationally driven by the valve driving means, and when the contact portion abuts against the sub-valve stopper, the sub-valve passage communicates with the pressure equalizing hole. Along with the rotation of the sub-valve, the main valve is rotated. After the main valve abuts against the main valve stopper and the rotation of the main valve stops at the switching position, the sub-valve is driven in the reverse rotation direction by the driving means, so that the sub-valve passage no longer communicates with the pressure equalizing hole and the pressure equalizing hole is closed by the sub-valve seat surface, which is preferable. According to such a configuration, it is not necessary to connect the main valve and the sub-valve via a clutch as in a conventional rotary switching valve, so that the possibility that the clutch inadvertently disengages and the main valve deviates from the switching position can be eliminated. Further, when the sub-valve is driven in the reverse rotation direction while the main valve is stopped at the switching position, the rotation of the main valve in the reverse rotation direction is restricted by the rotation restricting means, so that it is possible to suppress the main valve from rotating together with the sub-valve as the sub-valve rotates in the reverse direction. Thereby, the pressure equalizing hole can be normally closed, and it is possible to suppress the main valve from deviating from the switching position.

[0010] Further, the rotation restricting means preferably has an elastic member provided in the vicinity of the main valve stopper. The elastic member has an elastically deformable elastic arm portion and a convex portion as the holding portion provided at the tip of the elastic arm portion. The held portion has a concave portion provided in the main valve, and it is preferable that the state in which the rotation of the main valve is restricted is maintained by the convex portion locking the concave portion. According to such a configuration, the rotation restricting means can be configured by a simple configuration in which the concave portion provided in the main valve is locked by the convex portion provided at the tip of the elastic arm portion.

[0011] Further, the elastic member may be constituted by a leaf spring.

[0012] Further, the elastic member preferably has a tapered guide portion that slidably contacts the main valve on the tip side of the convex portion, and the convex portion is preferably formed in a hemispherical convex shape. According to such a configuration, by bringing the tapered guide portion formed on the tip side of the convex portion into sliding contact with the main valve, the main valve can be guided toward the main valve stopper. Therefore, with the main valve being guided, locking of the concave portion by the convex portion can be achieved. Accordingly, the locking of the concave portion by the convex portion can be surely performed, and the rotation restriction of the main valve in the reverse rotation direction by the rotation restricting means can be more surely performed.

[0013] Further, the rotation restricting means has an elastic member provided on the main valve. The elastic member has an elastically deformable elastic arm portion and a convex portion as the held portion provided at the tip of the elastic arm portion. The main valve stopper may maintain a state in which the rotation of the main valve is restricted by locking the convex portion as the holding portion. According to such a configuration, since the main valve stopper also functions as a holding portion, there is no need to newly prepare a holding portion, and the configuration of the rotation restricting means can be simplified.

[0014] Further, at least one of the holding portion and the held portion of the rotation restricting means is a magnet, and the other is composed of a magnet or a magnetic body, and the rotation of the main valve may be restricted by magnetic adhesion to each other. According to such a configuration, the rotation restricting means can be configured without forming a concave portion as the held portion or a convex portion as the holding portion, so that the configuration of the rotation restricting means can be simplified. Thereby, the molding of the main valve and the valve body (particularly, the vicinity of the main valve stopper) can be facilitated.

Advantages of the Invention

[0015] According to the present invention, a rotary switching valve capable of stabilizing the switching operation by preventing displacement of the main valve can be obtained.

Brief Description of the Drawings

[0016]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Embodiment for Carrying Out the Invention

[0017] Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 10. In the drawings, the central axis direction of the valve body 10 to be described later is denoted as "axial direction L", one side of the axial direction L is denoted as "upper side L1", and the other side is denoted as "lower side L2". The direction orthogonal to the axial direction L is denoted as "radial direction X". Further, as shown in FIG. 5 etc., the side closer to the rotation shaft 53 in the radial direction X may be denoted as "inner side X1", and the opposite side of the inner side X1 (the side farther from the rotation shaft 53) may be denoted as "outer side X2". This is only for convenience of explanation and does not necessarily coincide with the directions in the actual use state of the rotary switching valve 1, and does not limit the respective directions in the actual use state of the rotary switching valve 1.

[0018] The rotary switching valve 1 according to an embodiment of the present invention is used, for example, in a heat pump type refrigeration cycle system S to switch the flow path of the refrigerant. As shown in FIG. 1, the rotary switching valve 1 includes a valve body 10, a valve seat portion 20, a main valve 30, a sub-valve 40, a driving means 50, and a rotation restricting means 60. The valve body 10 is composed of a bottomed cylindrical case member having a bottom at the upper side L1 and opening toward the lower side L2, and has a valve chamber 11 inside. The valve chamber 11 includes an upper valve chamber 11a above the piston ring 32a to be described later on the upper side L1 and a lower valve chamber 11b below the piston ring 32a on the lower side L2. The valve seat portion 20 includes a valve seat body 21 that fits into the opening of the valve body 10 and joins to the lower side L2 portion of the valve body 10, and a flange portion 22 that extends outward X2 in the radial direction X from the end of the valve seat body 21 on the lower side L2. The valve seat body 21 is formed in a substantially cylindrical shape, and its outer peripheral surface is a male thread, which is screwed with the female thread on the inner peripheral surface of the valve body 10, and the lower end surface of the valve body 10 and the upper surface of the flange portion 22 are hermetically fixed by welding. A shaft support portion 23 that is recessed in the axial direction L is formed at the center of the valve seat body 21, and the lower end portion of the rotation shaft 53 to be described later is inserted into the shaft support portion 23.

[0019] Around the shaft support portion 23, a plurality of ports penetrating in the axial direction L are formed at equal intervals around the central axis of the rotary shaft 53. That is, the valve seat portion 20 has a plurality of ports opening into the valve chamber 11. As shown in FIG. 2, the plurality of ports are composed of a D port 24, an S port 25, a C switching port 26, and an E switching port 27. As shown in FIG. 10, the D port 24 communicates with the discharge side of the compressor P in the refrigeration cycle system S. The S port 25 communicates with the suction side of the compressor P. The C switching port 26 communicates with the outdoor heat exchanger B. The E switching port 27 communicates with the indoor heat exchanger A. In the vicinity of the opening edge of the D port 24 on the upper surface L1 of the valve seat body 21, as shown in FIG. 2, a leaf spring positioning pin 28 protruding upward on L1 and a main valve stopper 29 are formed. That is, the leaf spring positioning pin 28 and the main valve stopper 29 are arranged in the valve chamber 11. In the present embodiment, the configuration in which the leaf spring positioning pin 28 and the main valve stopper 29 are provided on the valve seat portion 20 is illustrated, but the leaf spring positioning pin 28 and the main valve stopper 29 may be provided on the valve body 10. That is, the leaf spring positioning pin 28 and the main valve stopper 29 may be provided on either the valve body 10 or the valve seat portion 20.

[0020] As shown in FIG. 2(B), the leaf spring positioning pin 28 determines the position of the holding portion 62 on the valve seat body 21 by being inserted into the first through hole 65 of the holding portion 62 of the rotation restricting means 60 described later. The main valve stopper 29 is a member with which the protruding end portion 34a of the latch portion 34 formed in the skirt portion 31 of the main valve 30 described later abuts, and is formed in a columnar shape. The main valve stopper 29 fixes the holding portion 62 to the valve seat body 21 in a state of being inserted into the second through hole 66 of the holding portion 62.

[0021] The main valve 30 is a valve member rotatably provided around the axis of a rotating shaft 53, which will be described later, on a valve seat portion 20 in a valve chamber 11. The main valve 30 is formed of resin so that its outer periphery is circular, and includes a bowl-shaped skirt portion 31 that opens to the valve seat portion 20 side, a cylindrical piston portion 32 provided coaxially with the skirt portion 31 and extending upward to L1, and a bearing portion 33 that extends in the axial direction L through the centers of the skirt portion 31 and the piston portion 32. The skirt portion 31 is formed with a low-pressure flow path 31a (see Fig. 3(B)) as a valve passage, a pressure equalizing hole 31b (see Figs. 1 and 3(A)) that communicates the low-pressure flow path 31a with the upper valve chamber 11a (valve chamber 11) described above, and a high-pressure flow path 31c (see Fig. 3(B)) arranged in the radial direction X in parallel with the low-pressure flow path 31a. The low-pressure flow path 31a is formed by drilling one side in the radial direction X of a bearing hole 33a, which will be described later, in a dome shape. In the present embodiment, the low-pressure flow path 31a covers and communicates with two of the above-described S port 25, C switching port 26, and E switching port 27, and isolates them from the valve chamber 11.

[0022] A seal rib 35 that slidably contacts the upper surface of the valve seat body 21 at L1 is formed at the opening edge of the low-pressure flow path 31a. As shown in Fig. 3(B), the seal rib 35 is adjusted to be located on the same plane as a pair of sliding ribs 36 formed on the lower surface of the skirt portion 31 at L2. Thereby, the inclination of the main valve 30 with respect to the valve seat body 21 is suppressed. Inside the low-pressure flow path 31a, a reinforcing member 37 is installed that extends from the outer wall surface in the outer direction X2 in the radial direction X to the inner wall surface in the inner direction X1 in the radial direction X. Although the inside of the low-pressure flow path 31a may be at a lower pressure than the valve chamber 11, the installation of the reinforcing member 37 prevents deformation of the low-pressure flow path 31a due to the pressure difference. The pressure equalizing hole 31b is a hole that cancels the differential pressure inside and outside the low-pressure flow path 31a by communicating the low-pressure flow path 31a with the upper valve chamber 11a. As shown in Fig. 1, the pressure equalizing hole 31b is formed through the skirt portion 31 from the ceiling portion of the low-pressure flow path 31a to a main valve seat surface 39c, which will be described later.

[0023] The high-pressure flow path 31c has a shape substantially the same as that of the low-pressure flow path 31a and is formed on the other side in the radial direction X of the bearing hole 33a. As shown in FIG. 3(B), a notch 38 is formed in a portion on the outer side X2 of the high-pressure flow path 31c, which cuts out the lower L2 portion of the skirt portion 31 in a range of approximately 90°. As a result, the high-pressure flow path 31c is also open in the radial direction X and is always open to the inside and outside, constantly communicating the valve chamber 11 and the D port 24. A pair of latch portions 34 that protrude toward each other in the circumferential direction are formed at both ends of the notch 38. The latch portion 34 is the held portion 61 in the present embodiment and is locked to a holding portion 62 described later. The held portion 61 and the holding portion 62 together constitute the rotation restricting means 60 of the present invention. The protruding end portion 34a of the latch portion 34 is provided so as to contact the main valve stopper 29 described above. When the latch portion 34 contacts the main valve stopper 29, the rotation of the main valve 30 around the rotation shaft 53 is restricted.

[0024] In addition, in the present embodiment, as shown in FIGS. 6(A) and 8, the ports communicating with the low-pressure flow path 31a are switched between the position where one latch portion 34 contacts the main valve stopper 29 and the position where the other latch portion 34 contacts the main valve stopper 29. Specifically, in the state shown in FIG. 6(A) where one latch portion 34 contacts the main valve stopper 29, the S port 25 and the E switching port 27 communicate with each other. On the other hand, in the state shown in FIG. 8 where the other latch portion 34 contacts the main valve stopper 29, the S port 25 and the C switching port 26 communicate with each other. Therefore, in the present embodiment, the position where the latch portion 34 contacts the main valve stopper 29 is called a predetermined switching position in the main valve 30. The switching position is composed of a first predetermined position where one latch portion 34 contacts the main valve stopper 29 as shown in FIG. 6(A) and a second predetermined position where the other latch portion 34 contacts the main valve stopper 29 as shown in FIG. 8. Also, the direction in which the main valve 30 rotates around the axis of the rotation shaft 53 toward each switching position is called the rotation direction, and the direction in which it rotates in the opposite direction to the rotation direction is called the reverse rotation direction.

[0025] On the outer surface of the latch portion 34, as shown in FIG. 3(B), there is a recess 34b that is recessed inward X1 in the radial direction X and has a V-shaped cross-sectional shape in a direction orthogonal to the axial direction L. That is, the latch portion 34 as the held portion 61 has a recess 34b provided in the main valve 30. The recess 34b is configured to be locked by a convex portion 68a of an elastic portion 64 (elastic member) described later, whereby the state in which the rotation of the main valve 30 is restricted is maintained. Note that the cross-sectional shape of the recess 34b in the direction orthogonal to the axial direction L is not limited to a V shape, and may be various shapes such as a hemispherical shape or a rectangular shape. The piston portion 32 is disposed in the upper L1 portion of the skirt portion 31 and is formed in a bottomed cylindrical shape that opens upward L1. A piston ring 32a is attached to the outer periphery of the piston portion 32. Also, an inner ring 32b formed of a metal leaf spring material is installed inside the piston ring 32a, and the piston ring 32a is pushed outward in the radial direction X by the tension load acting on the outside of the inner ring 32b. As shown in FIG. 1, the piston ring 32a is slidably in contact with the inner wall surface of the valve body 10 in the valve chamber 11, whereby the main valve 30 is movable in the axial direction L while being guided by the inner wall surface of the valve body 10.

[0026] The inside of the piston portion 32 constitutes a substantially cylindrical sub-valve accommodation chamber 39 for accommodating the sub-valve 40. On the bottom wall of the sub-valve accommodation chamber 39, there is formed a pedestal 39a that protrudes upward L1 and extends around the rotation shaft 53. On the pedestal 39a, three substantially fan-shaped sub-valve support portions 39b that protrude upward L1 are formed at equal intervals in the circumferential direction of the rotation shaft 53. The upper L1 surfaces of the sub-valve support portions 39b respectively constitute main valve seat surfaces 39c with which the sub-valve 40 is in sliding contact. Among the three main valve seat surfaces 39c, the above-described pressure equalizing hole 31b opens in one of them. The inside of the pedestal 39a constitutes the upper L1 end portion of the bearing portion 33, and a bearing hole 33a that penetrates in the axial direction L is formed at the center of the bearing portion 33. The rotation shaft 53 of the driving means 50 is inserted into the bearing hole 33a, whereby the main valve 30 is rotatable about the axis of the rotation shaft 53. That is, the main valve 30 is rotatably provided in the valve chamber 11 about the axis of the rotation shaft 53 that intersects the upper surface of the valve seat portion 20 on the valve seat portion 20.

[0027] On the side wall of the pilot valve housing chamber 39, a pair of pilot valve stoppers 39d that project inward X1 in the radial direction X and extend in the axial direction L are formed at intervals in the circumferential direction. The pilot valve stopper 39d has a substantially trapezoidal cross-sectional shape in the circumferential direction. The pilot valve stopper 39d has a function of stopping the relative rotation around the rotation axis 53 of the main valve 30 and the pilot valve 40 by contacting the pilot valve 40. The pilot valve 40 is a member disposed in the pilot valve housing chamber 39 and provided rotatably with respect to the main valve 30. As shown in FIGS. 4(A) and 4(B), the pilot valve 40 includes a cylindrical boss portion 41 that extends in the axial direction L, and a semi-disk-shaped flange 42 formed on the outer surface of the lower L2 portion of the boss portion 41. At the center of the boss portion 41, a square hole 43 that opens upward L1 and a bearing hole 44 that communicates with the square hole 43 and opens downward L2 are formed. The cam portion 54 of the driving means 50 described later is fitted into the square hole 43, whereby the pilot valve 40 and the driving means 50 are integrated. The bearing hole 44 is formed coaxially with the bearing hole 33a of the main valve 30 described above, and the rotation axis 53 of the driving means 50 is inserted therethrough.

[0028] The wall surface of the lower L2 of the boss portion 41 constitutes a pilot valve seat surface 45 that slidably contacts the main valve seat surface 39c. The pilot valve seat surface 45 opens and closes the equalizing hole 31b described above when the pilot valve 40 rotates. In the boss portion 41, a pair of pilot valve flow paths 46 that are cut out from the pilot valve seat surface 45 to the outer surface of the boss portion 41 are formed at intervals around the rotation axis 53. As shown in FIGS. 4(A) and 4(B), the flange 42 is formed so as to avoid the pair of pilot valve flow paths 46 and cover the boss portion 41 by approximately 180° around the axis. Both circumferential ends of the flange 42 serve as contact portions 47 that contact the pilot valve stopper 39d of the main valve 30 described above, and when the contact portion 47 contacts the pilot valve stopper 39d, the rotation of the pilot valve 40 with respect to the main valve 30 stops.

[0029] The driving means 50 is configured to rotationally drive the sub-valve 40. As shown in FIG. 1, it has a worm gear 51 fixed to the drive shaft of a motor (not shown), a worm wheel 52 meshing with the worm gear 51, and a rotating shaft 53 passing through the center of the worm wheel 52 and extending in the axial direction L. The worm gear 51 rotates around the axis of the drive shaft extending in the front-rear direction in FIG. 1. The worm wheel 52 rotates around the axis of the rotating shaft 53 in accordance with the rotation of the worm gear 51. A cam portion 54 protruding downward to the lower side L2 is formed at the center of the wall surface on the lower side L2 of the worm wheel 52. The cam portion 54 is fitted into the square hole 43 of the sub-valve 40. Thereby, the sub-valve 40 is integrated with the worm wheel 52 in a state where its rotation around the rotating shaft 53 is restricted with respect to the worm wheel 52, and is slidable only in the axial direction L.

[0030] Therefore, when the worm gear 51 rotates, the worm wheel 52 and the sub-valve 40 rotate around the axis of the rotating shaft 53 in cooperation. A coil spring 55 extending from the wall surface on the lower side L2 of the worm wheel 52 to the wall surface on the upper side L1 of the flange 42 of the sub-valve 40 is installed around the cam portion 54. The coil spring 55 biases the sub-valve 40 toward the main valve 30 side. The rotating shaft 53 passes through the worm wheel 52, passes through the bearing hole 44 of the sub-valve 40 and the bearing hole 33a of the main valve 30, and extends to the valve seat portion 20. The end portion on the upper side L1 of the rotating shaft 53 is inserted into the shaft support portion 12 formed on the ceiling surface of the valve body 10. The end portion on the lower side L2 of the rotating shaft 53 is inserted into the shaft support portion 23 of the valve seat portion 20 as described above.

[0031] The rotation restricting means 60 is provided between the valve body 10 and the main valve 30, and is configured to restrict the main valve 30 from rotating in the reverse rotation direction from the switching position described above. As shown in FIG. 1, the rotation restricting means 60 includes a held portion 61 (in this embodiment, the latch portion 34) and a holding portion 62. As described above, the held portion 61 is formed in the skirt portion 31 of the main valve 30 and is constituted by the latch portion 34 having the concave portion 34b. In this embodiment, as shown in FIG. 2(B), the holding portion 62 is constituted by a metal member provided in the vicinity of the main valve stopper 29. The holding portion 62 includes a ring portion 63 that covers the outer periphery of the D port 24, and an elastic portion 64 (elastic member) that rises from the end portion of the outer side X2 of the ring portion 63 and extends around the rotation axis 53 of the shaft.

[0032] The ring portion 63 is formed of a frame-shaped plate member placed on the upper surface L1 of the valve seat body 21. As shown in FIGS. 5(A) and 5(B), a first through hole 65 penetrating in the plate thickness direction is formed at the inner end portion X1 side of the ring portion 63, and a second through hole 66 penetrating in the plate thickness direction is formed at the outer end portion X2 of the ring portion 63. As shown in FIGS. 2(A) and 2(B), the above-described leaf spring positioning pin 28 is inserted into the first through hole 65. A lower portion (not shown) having a smaller diameter than the portion where the main valve 30 of the main valve stopper 29 described above abuts is inserted into the second through hole 66. Then, by inserting the lower portion of the main valve stopper 29 into the second through hole 66, the ring portion 63 is fixed to the valve seat body 21. Specifically, by fixing the lower portion with a smaller diameter of the main valve stopper 29 to the second insertion hole 66 by press-fitting or the like, the ring portion 63 is sandwiched between the stepped surface between the upper portion with a larger diameter of the main valve stopper 29 and the lower portion with a smaller diameter of the main valve stopper 29 and the valve seat body 21, whereby the ring portion 63 is fixed to the valve seat portion 20.

[0033] Regarding the fixation to the second insertion hole 66 at the lower part of the small diameter of the main valve stopper 29, various fixation methods may be used in addition to press-fitting. For example, a male thread may be formed on the outer peripheral surface of the lower part of the small diameter of the main valve stopper 29, a female thread may be formed on the inner peripheral surface of the second insertion hole 66, and they may be screwed together for screw fixation. Also, an adhesive or the like may be used to bond the outer peripheral surface of the lower part of the small diameter of the main valve stopper 29 and the inner peripheral surface of the second insertion hole 66, or a heating means may be used to weld the outer peripheral surface of the lower part of the small diameter of the main valve stopper 29 and the inner peripheral surface of the second insertion hole 66. The elastic portion 64 is composed of a metal leaf spring and includes a connecting portion 67 rising from the ring portion 63 and a pair of elastic arm portions 68 extending in a direction away from each other from the connecting portion 67. The connecting portion 67 is formed in a substantially rectangular shape as shown in FIG. 5(B). The elastic arm portions 68 extend from both ends in the long side direction of the connecting portion 67, inclined toward the ring portion 63 with respect to the plate surface of the connecting portion 67, and are provided so as to be elastically deformable in the radial direction X.

[0034] A convex portion 68a protruding inward X1 is formed at the tip of the elastic arm portion 68. The convex portion 68a is formed in a hemispherical convex shape as shown in FIG. 5(C). The convex portion 68a locks the latch portion 34 by fitting into the concave portion 34b of the latch portion 34. In the elastic arm portion, a tapered guide portion 68b inclined outward X2 in the radial direction X is formed on the tip side of the convex portion 68a. The tapered guide portion 68b is the portion where the protruding end portion 34a of the latch portion 34 of the main valve 30 rotating toward a predetermined position first comes into sliding contact, and has a function of guiding the latch portion 34 of the main valve 30 toward the main valve stopper 29.

[0035] In addition, in this embodiment, the convex portion 68a has a hemispherical convex shape, but the shape of the convex portion 68a is not limited to this. FIGS. 5(D) and (E) are enlarged views showing variations of the convex portion 68a. As shown in FIG. 5(D), after the tip of the elastic arm portion 68 is bent inward X1 in the radial direction X at an acute angle, the tip is further bent toward the base end side of the elastic arm portion 68 to form a polygon convex in plan view, and this convex can be used as a convex portion 68c corresponding to the convex portion 68a. Also, as shown in FIG. 5(E), after the tip of the elastic arm portion 68 is bent inward X1 in the radial direction X at an obtuse angle, the tip is further bent outward X2 in the radial direction X to form a polygon convex in plan view, and this convex can be used as a convex portion 68d corresponding to the convex portion 68a. Note that in the modification examples of FIGS. 5(D) and (E) as well, there is a tapered guide portion 68b as in FIG. 5(C), and similar to the above, it has a function of guiding the latch portion 34 of the main valve 30 toward the main valve stopper 29. In this embodiment, the elastic portion 64 is formed of a metal leaf spring, but the material of the elastic portion 64 is not limited to metal, and various materials such as rubber and soft plastic may be used. Also, the elastic portion 64 may be formed of a coil spring (a coil spring provided with a convex portion) other than a leaf spring.

[0036] Next, the operation of the rotary switching valve 1 will be described with reference to FIGS. 6(A) to 8. FIGS. 6(A) to 8 are diagrams showing the state in which the main valve 30 rotates around the rotation axis 53. From the initial state of FIG. 6(A) in which the main valve 30 is positioned at the above-described first switching position and the pressure equalizing hole 31b is closed, to the completion state of FIG. 8 in which the main valve 30 is positioned at the second switching position and the pressure equalizing hole 31b is closed, the state in which the main valve 30 rotates is shown step by step. Specifically, FIG. 6(A) shows the main valve 30 and the sub-valve 40 in the initial state. FIG. 6(B) shows the state in which the sub-valve 40 abuts against the sub-valve stopper 39d. FIG. 7(A) shows the state in which the main valve 30 and the sub-valve 40 rotate in cooperation. FIG. 7(B) shows the state in which the main valve 30 is locked to the holding portion 62. FIG. 8 shows the main valve 30 and the sub-valve 40 in the completion state.

[0037] And, the upper, middle, and lower parts of FIGS. 6(A) to 8 show the main valve 30 and the sub-valve 40 at the same stage. The upper part is a cross-sectional view obtained by horizontally cutting the main valve 30 and the sub-valve 40 portions of the rotary switching valve 1, the middle part is a side view when looking at the upper part from the A direction, and the lower part shows a plan view of the skirt portion 31 and the valve seat portion 20. Note that since each component of the rotary switching valve 1 has already been described with reference numerals, here, to prevent the drawing from becoming complicated, only the reference numerals necessary for the description may be attached, and other reference numerals may be omitted.

[0038] In the initial state shown in FIG. 6(A), as shown in the upper and middle parts of FIG. 6(A), the sub-valve seat surface 45 of the sub-valve 40 (the hatched part in the upper part of FIG. 6(A)) abuts against the main-valve seat surface 39c of the main valve 30, closing the pressure equalizing hole 31b. In this state, as shown in the lower part of FIG. 6(A), the low-pressure flow path 31a covers and communicates the S port 25 and the E switching port 27. Also, the C switching port 26 and the D port 24 are released and communicate with each other through the valve chamber 11 by the high-pressure flow path 31c. Further, in this state, as shown in the middle part of FIG. 6(A), since the sub-valve flow path 46 does not communicate with the pressure equalizing hole 31b, the inside of the low-pressure flow path 31a is at a low pressure with respect to the high-pressure sub-valve housing chamber 39 and the upper valve chamber 11a. Due to the differential pressure and the biasing force of the coil spring 55, the sub-valve 40 is pressed against the main valve 30, and due to this biasing force and the differential pressure above and below the main valve 30, the main valve 30 is pressed against the valve seat portion 20. Also, in this state, as shown in the lower part of FIG. 6(A) and FIG. 9, the convex portion 68a of the holding portion 62 fits into the concave portion 34b of one of the latch portions 34, and the convex portion 68a locks the latch portion 34.

[0039] Thereafter, the position of the main valve 30 remains unchanged, and only the sub-valve 40 is rotated in the rotational direction (in this case, the clockwise direction about the rotation axis 53) by the driving means 50. As a result, as shown in the middle stage of FIG. 6(B), the sub-valve flow path 46 communicates with the pressure equalizing hole 31b, and the pressure equalizing hole 31b is released from the closed state. Thereby, the differential pressure described above is canceled, and the upper valve chamber 11a and the low-pressure flow path 31a become substantially the same pressure. For this reason, the force for pressing the sub-valve 40 against the main valve 30 and the force for pressing the main valve 30 against the valve seat portion 20, as described above, are relaxed, and the resistance such as friction when the main valve 30 rotates with respect to the valve seat portion 20 is reduced. The sub-valve 40 rotates in the rotational direction until the contact portion 47 contacts the sub-valve stopper 39d, as shown in the upper stage of FIG. 6(B). Then, by contacting the sub-valve stopper 39d, it can no longer rotate, and the relative rotation with the main valve 30 stops.

[0040] Thereafter, when the sub-valve 40 further attempts to rotate in the rotational direction, the force for rotating the sub-valve 40 is transmitted to the main valve 30 via the sub-valve stopper 39d. Therefore, as shown in the upper stage of FIG. 7(A), the sub-valve 40 and the main valve 30 become integrated, and they rotate in the rotational direction in cooperation. At this time, as shown in the lower stage of FIG. 7(A), the convex portion 68a of the holding portion 62 comes out of the concave portion 34b of one of the latch portions 34, and the locking of the concave portion 34b by the convex portion 68a is released. Then, as shown in FIG. 7(B), the main valve 30 and the sub-valve 40 rotate in the rotational direction until the protruding end portion 34a of the other latch portion 34 in the main valve 30 contacts the main valve stopper 29 and the rotation of the main valve 30 in the rotational direction is restricted (that is, until the second switching position is reached).

[0041] When the protruding end portion 34a of the latch portion 34 approaches the main valve stopper 29, first, the protruding end portion 34a comes into sliding contact with the tapered guide portion 68b of the holding portion 62. As a result, while the protruding end portion 34a elastically deforms the elastic arm portion 68 outward in the radial direction X (X2), it is guided toward the main valve stopper 29. On the other hand, the convex portion 68a of the holding portion 62 gets over the protruding end portion 34a in the rotational direction and fits into the concave portion 34b of the other latch portion 34 in the main valve 30 in the rotational direction as shown in the lower part of FIG. 7(B). Thereby, the convex portion 68a locks the latch portion 34. And the state where the rotation of the main valve 30 is restricted is maintained. In this state, as shown in the lower part of FIG. 7(B), the low-pressure flow path 31a covers and communicates the S port 25 and the C switching port 26. Also, the E switching port 27 and the D port 24 are released by the high-pressure flow path 31c and communicate with each other through the valve chamber 11.

[0042] Thereafter, as shown in the upper and middle parts of FIG. 8, with the position of the main valve 30 locked to the holding portion 62 remaining unchanged, only the sub-valve 40 is rotated by the driving means 50 in the reverse rotational direction (in this case, the counterclockwise direction around the rotation shaft 53). As a result, the sub-valve seat surface 45 of the sub-valve 40 comes into contact with the main-valve seat surface 39c of the main valve 30, and the pressure equalizing hole 31b is closed again. Also, in this state, as shown in the middle part of FIG. 8, since the sub-valve flow path 46 is not in communication with the pressure equalizing hole 31b, the inside of the low-pressure flow path 31a is at a low pressure with respect to the high-pressure upper valve chamber 11a. The sub-valve 40 is pressed against the main valve 30 by the differential pressure and the biasing force of the coil spring 55, and the main valve 30 is pressed against the valve seat portion 20 by this biasing force and the differential pressure above and below the main valve 30. Also, in this state, as shown in the lower part of FIG. 8, since the state where the latch portion 34 is locked to the holding portion 62 is maintained, the main valve 30 is prevented from rotating as the sub-valve 40 rotates.

[0043] In this way, when the sub-valve 40 is rotationally driven by the driving means 50 and the sub-valve passage 46 communicates with the pressure equalizing hole 31b at the position where the contact portion 47 contacts the sub-valve stopper 39d, the main valve 30 is rotated as the sub-valve 40 rotates. Then, after the main valve 30 contacts the main valve stopper 29 and the rotation of the main valve 30 stops at the switching position, the sub-valve 40 is driven in the reverse rotation direction by the driving means 50, so that the sub-valve passage 46 no longer communicates with the pressure equalizing hole 31b, and the pressure equalizing hole 31b is closed by the sub-valve seat surface 45.

[0044] Next, a refrigeration cycle system S using the rotary switching valve 1 will be described. FIG. 10 is a schematic diagram of a refrigeration cycle system S according to an embodiment of the present invention. This refrigeration cycle system S is an example of a refrigeration cycle system of an air conditioner. The air conditioner has a compressor P, an outdoor heat exchanger B, an expansion valve V, an indoor heat exchanger A, and the rotary switching valve 1 of the embodiment. These elements are respectively connected as shown by conduits to constitute a heat pump type refrigeration cycle system S. The flow path of the refrigeration cycle system S is switched to two types of flow paths for cooling operation and heating operation by rotating the main valve 30 around the rotation axis 53. In the cooling operation, the state shown in FIG. 10(A) is obtained, and in the heating operation, the state shown in FIG. 10(B) is obtained. Note that the rotary switching valve 1 shown in FIG. 10 shows only the positional relationship of the main parts as viewed from the lower side L2 of the valve seat portion 20, and the hatched portion of a part of the main valve 30 shows the portion in contact with the valve seat portion 20.

[0045] During the cooling operation shown in Fig. 10(A), in the rotary switching valve 1, the S port 25 is communicated with the E switching port 27 through the low-pressure flow path 31a of the main valve 30, and the D port 24 is communicated with the C switching port 26 through the high-pressure flow path 31c. Then, as indicated by the arrows in the figure, the refrigerant as the fluid compressed by the compressor P flows into the D port 24 of the rotary switching valve 1, flows into the outdoor heat exchanger B from the C switching port 26, and the refrigerant flowing out of the outdoor heat exchanger B flows into the expansion valve V. Then, the refrigerant is expanded by the expansion valve V and supplied to the indoor heat exchanger A. The refrigerant flowing out of the indoor heat exchanger A flows from the E switching port 27 to the S port 25 through the rotary switching valve 1 and circulates from the S port 25 to the compressor P.

[0046] During the heating operation shown in Fig. 10(B), in the rotary switching valve 1, the S port 25 is communicated with the C switching port 26 through the low-pressure flow path 31a of the main valve 30, and the D port 24 is communicated with the E switching port 27 through the high-pressure flow path 31c. Then, as indicated by the arrows in the figure, the refrigerant compressed by the compressor P flows into the D port 24 of the rotary switching valve 1, flows into the indoor heat exchanger A from the E switching port 27, and the refrigerant flowing out of the indoor heat exchanger A flows into the expansion valve V. Then, the refrigerant is expanded by the expansion valve V and supplied to the outdoor heat exchanger B. The refrigerant flowing out of the outdoor heat exchanger B flows from the C switching port 26 to the S port 25 through the rotary switching valve 1 and circulates from the S port 25 to the compressor P.

[0047] As described above, according to the above-described embodiment, the main valve 30 that abuts against the main valve stopper 29 at a predetermined switching position and stops rotating in the rotational direction is restricted from rotating in the reverse rotational direction by the rotation restricting means 60. For this reason, it is possible to suppress valve leakage and the like caused by the unintentional displacement of the main valve 30 from the predetermined switching position, and to maintain well the state in which the switching of the D port 24, the S port 25, the E switching port 27, and the C switching port 26 is normally performed. Therefore, it is possible to obtain the rotary switching valve 1 that can stabilize the switching operation by preventing the displacement of the main valve 30.

[0048] Moreover, according to this configuration, it is not necessary to connect the main valve 30 and the sub-valve 40 via a clutch as in a conventional rotary switching valve. Therefore, it is possible to eliminate the possibility that the clutch inadvertently disengages and the main valve 30 deviates from the switching position. Further, when the sub-valve 40 is driven in the reverse rotation direction while the main valve 30 is stopped at the switching position, the rotation of the main valve 30 in the reverse rotation direction is restricted by the rotation restricting means 60. That is, the main valve 30 is restricted from rotating in the reverse rotation direction by the convex portion 68a of the holding portion 62 locking the concave portion 34b of the latch portion 34. For this reason, it is possible to suppress the main valve 30 from rotating together in the reverse rotation direction as the sub-valve 40 rotates in the reverse direction. Thereby, the pressure equalizing hole 31b can be normally closed, and it is possible to suppress the main valve 30 from deviating from the switching position.

[0049] Moreover, according to this configuration, the rotation restricting means 60 can be configured with a simple configuration in which the concave portion 34b provided in the main valve 30 is locked by the convex portion 68a provided at the tip of the elastic arm portion 68. Further, according to this configuration, by bringing the tapered guide portion 68b formed on the tip side of the convex portion 68a into sliding contact with the main valve 30, the main valve 30 can be guided toward the main valve stopper 29. For this reason, with the main valve 30 being guided, the locking of the concave portion 34b by the convex portion 68a can be realized. Therefore, the locking of the concave portion 34b by the convex portion 68a can be reliably performed, and the rotation of the main valve 30 in the reverse rotation direction by the rotation restricting means 60 can be more reliably performed. As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and design changes and the like within the scope not departing from the gist of the present invention are also included in the present invention.

[0050] FIG. 11(A) is a plan view of the rotation restricting means according to the first modification, and FIG. 11(B) is an enlarged view of the main part of FIG. 11(A). In the first modification, the configuration of the rotation restricting means 60 is different from that of the above-described embodiment. Specifically, a leaf spring 70 (an elastic member provided on the main valve 30), which protrudes from the protruding end portion 34a in the circumferential direction of the skirt portion 31 (hereinafter referred to as the circumferential direction), is installed on the latch portion 34 that constitutes the held portion 61. The leaf spring 70 has a plate-shaped elastic arm portion 71 (an elastically deformable elastic arm portion) and a convex portion 72 (a convex portion as the held portion 61) formed at the tip of the elastic arm portion 71 and protruding outward X2 in the radial direction X. As shown on the left side of FIG. 11(B), the convex portion 72 may be formed in a hemispherical convex shape, or as shown on the right side of FIG. 11(B), the tip portion may be bent to form a triangular shape in plan view. A recess 73 is formed between the protruding end portion 34a of the latch portion 34 and the convex portion 72.

[0051] In the first modification, when the main valve 30 rotates in the rotational direction and approaches the main valve stopper 29, the leaf spring 70 elastically deforms inward X1 in the radial direction X. At this time, the convex portion 72 gets over the main valve stopper 29 in the rotational direction. After that, the leaf spring 70 restores to a state substantially the same as the state before the elastic deformation. At this time, the main valve stopper 29 fits into the recess 73 and gets caught by the recess 73. That is, the rotation of the main valve 30 in the rotational direction is restricted by hooking the leaf spring 70 on the main valve stopper 29. In this configuration, the leaf spring 70 corresponds to the held portion 61 described above. And the main valve stopper 29 corresponds to the holding portion 62. That is, the held portion 61 is provided on the main valve 30 side, and the holding portion 62 is provided on the valve body 10 side.

[0052] According to such a configuration, since the main valve stopper 29 also functions as the holding portion 62, it is not necessary to newly prepare a metal member provided with a ring portion 63 or the like as the holding portion 62 as in the case of one embodiment, and the configuration of the holding portion 62 can be simplified. Further, since the main valve stopper 29 also functions as the holding portion 62, the rotation restricting means 60 can be configured without changing the configuration on the valve body 10 side. Further, since it is not necessary to form the concave portion 34b as in the above-described embodiment on the side surface of the latch portion 34, the configuration of the latch portion 34 can be made simpler than in the above-described embodiment. Thus, the configurations of the valve body 10 and the latch portion 34 are simplified, and the manufacturing costs of the valve body 10 and the latch portion 34 can be reduced.

[0053] FIG. 12(A) is a plan view of the rotation restricting means 60 according to the second modification, and FIG. 12(B) is an enlarged view of the main part of FIG. 12(A). FIG. 13(A) is a perspective view of the main valve 30 and the valve seat portion 20 according to the second modification, and FIG. 13(B) is an enlarged view of the main part of FIG. 13(A). FIG. 14 is a perspective view of the rotation restricting portion 80 constituting the holding portion 62 according to the second modification. In the second modification, the configuration of the rotation restricting means 60 is different from that of the above-described embodiment and the first modification. Specifically, as shown in FIGS. 12(A) and 12(B), the latch portion 34 is formed with a first concave portion 34c that opens outward X2 in the radial direction X and a second concave portion 34d that opens inward X1 in the radial direction X. And, at the position where the main valve stopper 29 was arranged in the above-described embodiment and the first modification, as shown in FIG. 13, a rotation restricting portion 80 formed by bending a metal member is fixed using fixing means 81 such as a rivet.

[0054] The rotation restricting portion 80 corresponds to the holding portion 62 of the above-described embodiment. As shown in FIG. 14, the rotation restricting portion 80 includes a bottom plate 82 having a predetermined width in the radial direction X, a pair of vertical plates 83 rising upward L1 from both end portions in the long side direction of the bottom plate 82, and a plate-shaped main valve latch portion 84 that continuously extends in the circumferential direction of the crotch portion 31 (hereinafter referred to as the circumferential direction) from the outer end portion on the X2 side of the vertical plate 83, and a plate-shaped main valve stopper portion 85 that continuously extends in the circumferential direction of the crotch portion 31 from the inner end portion on the X1 side of the vertical plate 83. The main valve latch portion 84 is provided so as to be elastically deformable in the radial direction X starting from the edge portion on the vertical plate 83 side, and its tip portion is bent so as to fit into the first concave portion 34c and protrudes inward in the radial direction X. The main valve stopper portion 85 includes a first plate portion 86 extending in the circumferential direction of the crotch portion 31, and a second plate portion 87 formed by bending the tip portion of the first plate portion 86 so as to extend inward X1 in the radial direction X.

[0055] The surface of the second plate portion 87 facing the outer circumferential direction constitutes a flat surface portion 87a that can contact a stopper surface 34e (shown only in FIG. 12(B)), which is a surface parallel to the radial direction X in the second concave portion 34d of the latch portion 34. A first reinforcing rib 88 is provided at the edge portion of the first plate portion 86 on the vertical plate 83 side starting from the edge portion to prevent the main valve stopper portion 85 from elastically deforming in the radial direction X. Further, a second reinforcing rib 89 is provided at the continuous portion between the first plate portion 86 and the second plate portion 87 to suppress the deformation of the second plate portion 87. As shown in FIG. 12(B), the main valve latch portion 84 and the main valve stopper portion 85 face each other in the radial direction X so as to sandwich the protruding end portion 34a of the latch portion 34.

[0056] In this second modification, when the main valve 30 rotates in the rotation direction and approaches the main valve latch portion 84, the tip portion of the main valve latch portion 84 elastically deforms outward X2 in the radial direction X and gets over the protruding end portion 34a in the rotation direction. Thereafter, the tip portion of the main valve latch portion 84 restores to substantially the same state as before the elastic deformation and fits into the first concave portion 34c. Thereby, the rotation of the main valve 30 in the rotation direction is restricted. At this time, when the tip portion of the main valve latch portion 84 fits into the first concave portion 34c, the flat surface portion 87a of the main valve stopper portion 85 contacts the stopper surface 34e of the second concave portion 34d, and the main valve 30 stops rotating.

[0057] As a result, the state in which the rotation of the main valve 30 is restricted is maintained. Thus, in the second modification example, the rotation restricting portion 80 integrally has the functions of the above-described main valve stopper 29 and the holding portion 62. According to such a configuration, it is not necessary to form the main valve stopper 29 on the valve seat portion 20 or to fix the holding portion 62 to the main valve stopper 29. Therefore, the structure of the valve seat portion 20 can be simplified. In addition, with a simple configuration in which the rotation restricting portion 80 is fixed to the valve seat portion 20, it is possible to achieve both restricting the rotation of the main valve 30 and maintaining the state in which the rotation of the main valve 30 is restricted.

[0058] FIG. 15(A) is a plan view of the rotation restricting means 60 according to the third modification example, and FIG. 15(B) is an enlarged view of the main part of FIG. 15(A). In the third modification example, the configuration of the rotation restricting means 60 is different from that of the above-described embodiment, the first modification example, and the second modification example. Specifically, a magnet M is provided at the protruding end portion 34a of the latch portion 34. And the main valve stopper 29 is made of a magnet or a magnetic material. In this third modification example, when the main valve 30 rotates in the rotational direction and abuts against the main valve stopper 29, the protruding end portion 34a and the main valve stopper 29 are magnetically attracted to each other by the magnetic force of the magnet M, and the main valve stopper 29 is held by the protruding end portion 34a. As a result, the rotation of the main valve 30 in the rotational direction is restricted, and the state in which the rotation of the main valve 30 is restricted is maintained. In the above description, an example in which the magnet M is provided at the protruding end portion 34a of the latch portion 34 has been described. However, what is provided at the protruding end portion 34a of the latch portion 34 is not limited to the magnet M, and for example, a magnetic material may be provided. In this case, the main valve stopper 29 is made of a magnet.

[0059] According to such a configuration, it is not necessary to newly prepare a configuration such as forming a recess 34b in the latch portion 34 or fitting into the recess 34b to lock it, and the structures of the held portion 61 and the holding portion 62 can be made simpler. Thereby, the main valve 30 and the valve body 10 (particularly, the vicinity of the main valve stopper 29) can be easily molded.

[0060] In the above-described embodiments and modified examples, the rotary switching valve 1 of the type that does not have a clutch for engaging the main valve 30 and the sub-valve 40 has been described. However, this is merely an example, and the present invention can also be applied to a rotary switching valve of the type that has a clutch for engaging the main valve 30 and the sub-valve 40 as in the prior art.

Explanation of Reference Numerals

[0061] 1 Rotary switching valve 10 Valve body 11 Valve chamber 20 Valve seat portion 29 Main valve stopper 30 Main valve 31a Low-pressure flow path 31b Equalizing hole 40 Sub-valve 50 Driving means 53 Rotating shaft 60 Rotation restricting means 61 Held portion 62 Holding portion

Claims

1. A rotary switching valve comprising a valve body having a valve chamber, a valve seat portion having a plurality of ports opening into the valve chamber, a main valve rotatably provided in the valve chamber about a rotation axis intersecting the upper surface of the valve seat portion on the upper surface of the valve seat portion, a sub-valve rotatably provided with respect to the main valve, and drive means for rotationally driving the sub-valve, wherein the main valve is provided with a valve passage communicating with the port and a pressure equalizing hole communicating the valve passage and the valve chamber, the sub-valve opens and closes the pressure equalizing hole, the valve body or the valve seat portion is provided with a main valve stopper that abuts against the main valve at a predetermined switching position to stop the rotation of the main valve rotating in the rotational direction about the rotation axis, between the valve body and the main valve, rotational restriction means for restricting the rotation of the main valve in the reverse rotational direction, which is the direction opposite to the rotational direction, from the switching position is provided, the rotational restriction means has a holding portion provided on one of the valve body and the main valve and capable of holding the other, and a held portion provided on the other and held by the holding portion, the main valve has a main valve seat surface in sliding contact with the sub-valve, a sub-valve stopper that abuts against the sub-valve to stop relative rotation with the sub-valve, and a low-pressure flow path that communicates two of the plurality of ports, the pressure equalizing hole is formed from the low-pressure flow path across the main valve seat surface, the sub-valve has a sub-valve seat surface in sliding contact with the main valve seat surface, a contact portion that abuts against the sub-valve stopper, and a sub-valve flow path formed by notching the sub-valve seat surface and capable of communicating with the pressure equalizing hole, and is characterized by a rotary switching valve.

2. When the sub-valve is rotationally driven by the drive means and the sub-valve flow path communicates with the pressure equalizing hole at a position where the contact portion abuts against the sub-valve stopper, and the main valve is rotated as the sub-valve rotates, after the main valve abuts against the main valve stopper and the rotation of the main valve stops at the switching position, the sub-valve is driven in the reverse rotational direction by the drive means, so that the sub-valve flow path no longer communicates with the pressure equalizing hole and the pressure equalizing hole is closed by the sub-valve seat surface. The rotary switching valve according to claim 1, characterized in that

3. The rotation restricting means has an elastic member provided in the vicinity of the main valve stopper. The elastic member has an elastically deformable elastic arm portion and a convex portion as the holding portion provided at the tip of the elastic arm portion. The held portion has a concave portion provided in the main valve, and the state in which the rotation of the main valve is restricted is maintained by the convex portion locking the concave portion. The rotary switching valve according to claim 1 or 2, characterized in that.

4. The rotary switching valve according to claim 3, characterized in that the elastic member is constituted by a leaf spring.

5. The elastic member has a tapered guide portion that slidably contacts the main valve on the tip side of the convex portion. The rotary switching valve according to claim 4, characterized in that the convex portion is formed in a hemispherical convex shape.

6. The rotation restricting means has an elastic member provided in the main valve. The elastic member has an elastically deformable elastic arm portion and a convex portion as the held portion provided at the tip of the elastic arm portion. The rotary switching valve according to claim 1 or 2, characterized in that the state in which the rotation of the main valve is restricted is maintained by the main valve stopper locking the convex portion as the holding portion.

7. The holding portion and the held portion of the rotation restricting means are such that at least one of them is a magnet and the other is constituted by a magnet or a magnetic body, and the rotation of the main valve is restricted by magnetic attraction to each other. The rotary switching valve according to claim 1 or 2, characterized in that.

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