Valve

Abstract

Provided is a valve capable of accurately controlling the pressure discharged from the valve. A valve (1) is provided with a valve body (51) and a valve seat (15a) that are provided between one pressure chamber (13) and the other pressure chamber (14) and that control the flow rate of a fluid passing through the one pressure chamber (13) and the other pressure chamber (14) by opening and closing, in which the valve body (51) and the valve seat (15a) are provided in a part of the other pressure chamber (14), and the valve body (51) and the valve seat (15a) are provided in the other pressure chamber (14). A pressure-sensitive body (61) into which the pressure of one pressure chamber (13) is introduced is disposed so as to be capable of being brought into contact with or separated from the valve body (51).

Description

Technical Field

[0001] The present invention relates to a valve, such as a valve for controlling flow. Background Art

[0002] In various fields, there is known a valve which is provided in the middle of a flow path through which a fluid flows and is used to control a flow rate according to an opening degree of the valve.

[0003] For example, the valve in Patent Document 1 is a solenoid expansion valve, which is mainly composed of a valve seat, a valve core, a spring, and a solenoid. The valve seat is provided between a primary pressure chamber connected to the primary pressure side of the flow path and a secondary pressure chamber connected to the secondary pressure side of the flow path. The valve core is pressed toward the valve seat by the spring. In addition, the valve core can move from the valve seat in a separation direction in response to the electromagnetic force of the solenoid.

[0004] Thus, the valve in Patent Document 1 is in a non-energized state and maintains a closed state in contact with a valve seat until the electromagnetic force exceeds the spring force and the valve is separated from the valve seat and opened.

[0005] Prior art literature

[0006] Patent Literature

[0007] Patent Document 1: Japanese Patent Application Publication No. 2013-145090 (pp. 5, 6, Figure 2 ) Summary of the invention

[0008] Problems to be solved by the invention

[0009] In the valve disclosed in Patent Document 1, the electromagnetic force changes according to the amount of current flowing, and the opening between the valve core and the valve seat can be adjusted to control the flow rate of the fluid and adjust the secondary pressure. However, in the valve disclosed in Patent Document 1, for example, when the primary pressure increases and the differential pressure with the secondary pressure increases in the closed valve state, the opening may sometimes differ even with the same amount of current flowing. As a result, there is a problem of uneven secondary pressure.

[0010] The present invention has been made in view of such problems, and an object of the present invention is to provide a valve capable of accurately controlling the pressure discharged from the valve.

[0011] Means for solving problems

[0012] In order to solve the above problems, the valve of the present invention comprises:

[0013] A valve core and a valve seat, wherein the valve core and the valve seat are arranged between one pressure chamber and another pressure chamber, and the flow rate of the fluid passing through the one pressure chamber and the other pressure chamber is controlled by opening and closing, wherein:

[0014] A pressure sensitive body for introducing the pressure of the one pressure chamber into the interior is arranged in a part of the other pressure chamber so as to be contactable with or separable from the valve body.

[0015] This reduces the influence of the pressure on the valve body and allows accurate control of the pressure discharged from the valve.

[0016] The valve may be switchable between a first state in which the valve opening is in an open state and a second state in which the valve element is throttled at a position closer to the valve seat than in the open state.

[0017] Thus, the valve has the function of an on-off valve and the function of a pressure reducing valve, thereby contributing to reducing the number of valve parts and simplifying control.

[0018] The valve element may be separated from the pressure sensitive body in the first state, and may be in contact with the pressure sensitive body in the second state.

[0019] Thus, the valve can be quickly switched from the first state to the second state, and the pressure discharged from the valve can be accurately controlled in the second state.

[0020] Alternatively, the pressure sensitive body may include a connector.

[0021] The valve core has an abutment portion at the front end.

[0022] At least one of the adapter and the contact portion has a tapered surface, and the tapered surface can contact the other.

[0023] Thus, when the valve is shifted from the first state to the second state, the tapered surface provided on one side is guided to the other side. Thus, the valve core can be aligned. Therefore, the accuracy of the valve in controlling the pressure discharged from the valve is improved.

[0024] The valve body may be formed with a communication passage that communicates with a space formed by the contact portion and the adapter and the one pressure chamber in the second embodiment.

[0025] As a result, a fluid can pass between the space and one of the pressure chambers, so that the valve element can instantly come into contact with and be separated from the pressure sensitive body.

[0026] The effective opening area of ​​the valve may be the same as the effective area of ​​the pressure sensitive body.

[0027] Thereby, the valve body can be operated without being affected by the pressure. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 is a schematic diagram showing a heat pump cycle to which a valve according to an embodiment of the present invention is applied;

[0029] Figure 2 is a cross-sectional view showing the valve in an open state;

[0030] Figure 3 is a diagram for explaining a shaft holder;

[0031] Figure 4 It is a graph for explaining the state transition of the valve with respect to the amount of current flowing;

[0032] Figure 5 is a cross-sectional view showing the valve just after operation;

[0033] Figure 6 is a cross-sectional view showing the valve in a throttling control state;

[0034] Figure 7 is a cross-sectional view showing the valve in a closed state. DETAILED DESCRIPTION

[0035] Hereinafter, a mode for implementing the valve of the present invention will be described based on examples.

[0036] Example

[0037] Reference Figures 1 to 7 As a valve of the embodiment, a solenoid valve that functions as an expansion valve during heating will be described. Figure 2 Specifically, the right side of the paper where the valve housing 10 is arranged is the right side of the solenoid valve, and the left side of the paper where the solenoid 80 is arranged is the left side of the solenoid valve.

[0038] like Figure 1 As shown, the solenoid valve 1 of the present invention, together with the compressor C, heat exchangers H1, H2, H3, the on-off valve V, the expansion valve E, etc., constitutes a heat pump cycle S used in an air conditioning system of an automobile or the like.

[0039] In the heat pump cycle S during cooling, the on-off valve V is closed and the expansion valve E is throttled. Figure 1 As indicated by the solid arrows, the compressor C, the heat exchanger H1, the solenoid valve 1, the heat exchanger H2, the expansion valve E, and the heat exchanger H3 circulate in the heat pump cycle S in this order. At this time, the solenoid valve 1 is in an open state.

[0040] The heat exchangers H1 and H3 are arranged in a duct D that introduces air from outside or inside the vehicle depending on the position of the damper d1 on the upstream side. During cooling, air sent by the blower B arranged in the duct D passes through the heat exchanger H3.

[0041] The cooled air is directed to Figure 1The baffle d2 on the downstream side is shown by the solid line, so that Figure 1 In other words, the air that has passed through the heat exchanger H3 is prevented from passing through the heat exchanger H1 and exchanging heat with the heat medium by the baffle d2.

[0042] In the heat pump cycle S during heating, the on-off valve V is opened and the expansion valve E is closed. Figure 1 As indicated by the dotted arrow, the compressor C, the heat exchanger H1, the solenoid valve 1, the heat exchanger H2, and the on-off valve V circulate in the heat pump cycle S in this order. At this time, the solenoid valve 1 is in a throttle control state.

[0043] During heating, the air delivered by the blower B passes through the heat exchanger H3 and is then Figure 1 The air is guided by the baffle d2 at the position indicated by the double-dashed line and passes through the heat exchanger H1. Figure 1 The liquid is supplied into the vehicle as indicated by the hollow arrow.

[0044] As described above, the solenoid valve 1 can be switched so that the pressure of the heat medium during cooling is approximately equal to the primary pressure (i.e., the pressure of one pressure chamber) P 1 The state of passing through the open state, and the pressure of the heat medium during heating is changed from the primary pressure P 1 To the secondary pressure (i.e. the pressure of another pressure chamber) P 2 The throttling control state of the reduced pressure. In contrast, when an expansion valve such as that in Patent Document 1 is applied, an additional on-off valve needs to be provided. Thus, the solenoid valve 1 of this embodiment can reduce the number of components used in the heat pump cycle S. The solenoid valve 1 is described in detail below.

[0045] like Figure 2 As shown, the solenoid valve 1 is mainly composed of a valve housing 10 , a valve core 51 , a pressure sensitive body 61 and a solenoid 80 , and the valve seat 15 a in the valve housing 10 and the valve core 51 constitute the valve 50 .

[0046] The valve housing 10 is formed of a metal material or a resin material into a stepped cylindrical shape. Two inlet ports 11 and two outlet ports 12 are formed on the peripheral wall of the valve housing 10 .

[0047] The inlet port 11 and the outlet port 12 are formed by penetrating the peripheral wall of the valve housing 10 in the radial direction. In addition, the inlet port 11 is arranged on the solenoid 80 side, and the outlet port 12 is arranged on the pressure sensitive body 61 side. In addition, the number and arrangement of the inlet port 11 and the outlet port 12 can also be changed appropriately.

[0048] A primary pressure chamber 13 as one pressure chamber and a secondary pressure chamber 14 as the other pressure chamber are formed on the inner diameter side of the valve housing 10 .

[0049] The primary pressure chamber 13 communicates with each inlet port 11 and is defined by the peripheral wall of the valve housing 10 , the annular convex portion 15 of the valve housing 10 , the small diameter end portion 16 of the valve housing 10 , and the center column 82 of the solenoid 80 .

[0050] The annular projection 15 projects radially inward from slightly to the left of the axial center of the peripheral wall of the valve housing 10. The annular projection 15 defines a communication flow path 10a communicating with the primary pressure chamber 13 and the secondary pressure chamber 14. The inner diameter side end of the annular projection 15 serves as a valve seat 15a.

[0051] The small diameter end portion 16 is an annular portion bent from the left end of the peripheral wall of the valve housing 10 toward the inner diameter side.

[0052] The secondary pressure chamber 14 communicates with each outlet port 12. The secondary pressure chamber 14 is defined by the peripheral wall of the valve housing 10, the annular convex portion 15, and the base 64 of the pressure sensitive body 61.

[0053] The valve element 51 has a base material 52 , a shaft holder 53 , and an abutment 54 as an abutment portion.

[0054] The base material 52 is formed in a substantially cylindrical shape, and has a curved surface 52 a protruding toward the right side and the inner diameter side at the axial right end portion.

[0055] In addition, in this embodiment, the curved surface 52a is formed as a plane extending linearly toward the inner diameter side toward the axial right side, but is not limited to this. It can also be a curved surface that is bent in a manner that protrudes toward the outer diameter side or the inner diameter side, or it can be a shape that tapers in a step-like manner, and its shape can also be changed appropriately.

[0056] The through hole that axially passes through the radial center of the substrate 52 is composed of a small diameter hole portion 52b and a large diameter hole portion 52c. The small diameter hole portion 52b opens to the axial left side. The large diameter hole portion 52c opens to the axial right side and communicates with the small diameter hole portion 52b.

[0057] The shaft holder 53 is press-fitted and fixed in the small diameter hole portion 52b of the base material 52. The shaft holder 53 may be fixed to the base material 52 by shrink fitting or by welding, and the fixing method may be changed as appropriate.

[0058] like Figure 3 As shown, the shaft holder 53 is formed to have three through grooves 53a (see FIG. Figure 3 (b)) is a cylindrical shape with steps in the circumferential direction.

[0059] The through groove 53a is composed of side surfaces on both sides of the circumferential direction extending linearly from the outer peripheral surface of the shaft retainer 53 toward the substantially inner diameter direction and a bottom surface extending linearly across the inner diameter end of these side surfaces, and is open toward the outer diameter side. In addition, the through groove 53a extends linearly in the axial direction and is open on both sides of the axial direction. In addition, the configuration, shape and number of the through grooves 53a can also be appropriately changed. In addition, it can also be a hole instead of a groove.

[0060] In addition, the through hole that axially penetrates the radial center of the shaft retainer 53 is composed of a small diameter hole portion 53b and a large diameter hole portion 53c. The small diameter hole portion 53b opens to the axial left side. The large diameter hole portion 53c opens to the axial right side and communicates with the small diameter hole portion 53b. In addition, the large diameter hole portion 53c communicates with the axial right end portion of each through groove 53a.

[0061] Reference Figure 2 The right end of the shaft 83 is press-fitted and fixed to the small-diameter hole 53b of the shaft holder 53. In addition, similarly to the base material 52 and the shaft holder 53, the fixing method can also be appropriately changed.

[0062] Three communication paths 51a are evenly arranged inside the valve core 51. The communication paths 51a are formed by the inner peripheral surface of the small-diameter hole portion 52b of the base material 52 and the through grooves 53a of the shaft holder 53 embedded in the small-diameter hole portion 52b (see Figure 3 ) is divided into.

[0063] Each communication passage 51a is connected to the large diameter hole portion 53c of the shaft holder 53 (see Figure 3 ) connected.

[0064] The left end portion of the contact member 54 is press-fitted and fixed to the large-diameter hole portion 52c of the base member 52. In addition, similarly to the base member 52 and the shaft holder 53, the fixing method thereof may be changed as appropriate.

[0065] The abutment member 54 is formed into a cylindrical shape with a flange extending toward the outer diameter side at the axial right end. The outer periphery and the right end of the flange become a curved surface 54a protruding toward the right side and the inner diameter side. In addition, similarly to the curved surface 52a, the shape of the curved surface 54a can also be appropriately changed, and can also be a tapered surface that gradually decreases in diameter toward the right side.

[0066] In addition, a through hole 54b is formed in the radial center of the contact member 54 so as to penetrate in the axial direction. The through hole 54b and the large diameter hole portion 53c (see Figure 3 ) connected.

[0067] The pressure sensitive body 61 is mainly composed of a bellows core 62 , an adapter 63 , a base 64 , and a coil spring 65 .

[0068] The axial left end of the bellows core 62 is fixed to the adapter 63 in a sealed state. The axial right end of the bellows core 62 is fixed to the base 64 in a sealed state. In addition, a coil spring 65 is arranged inside the bellows core 62.

[0069] In addition, the coil spring may be provided outside the bellows core 62. In addition, the bellows core itself may have elastic force, and in such a bellows core, the coil spring may be omitted.

[0070] The adapter 63 is formed into a cylindrical shape with a flange extending to the outer diameter side at the axial left end, and is in a leftward T-shape when viewed from a cross section. A recessed portion 63a is formed in the radial center of the flange, which is recessed toward the axial right side and opened toward the axial left side. More specifically, the recessed portion 63a is divided by a flat bottom 63b and a cylindrical portion 63c extending from its outer diameter end to the axial left.

[0071] The left end of the cylindrical portion 63c of the adapter 63 is formed into a tapered surface 63d which gradually decreases in diameter toward the axial right side. The shape of the tapered surface 63d may be appropriately changed, and the contact portion may have a tapered surface, the adapter may have a curved surface, or both may have tapered surfaces.

[0072] The base 64 is formed in a disk shape. A through hole 64 a penetrating in the axial direction is formed in the radial center of the base 64. The through hole 64 a communicates with an internal space 66 defined by the bellows core 62, the adapter 63, and the base 64.

[0073] Here, the flow path communicating with the downstream side of the heat exchanger H1 is connected in parallel with the inlet port 11 of the solenoid valve 1 and the through hole 64a (see Figure 1 ). Thus, the heat medium of the primary pressure that has passed through the heat exchanger H1 is introduced into the internal space 66 of the primary pressure chamber 13 and the pressure sensitive body 61 .

[0074] When the pressure of the internal space 66 of the pressure sensitive body 61 becomes relatively higher than the primary pressure of the heat medium having passed through the heat exchanger H1 , a portion of the heat medium in the internal space 66 is discharged from the through hole 64 a and introduced into the inlet port 11 .

[0075] Thus, the primary pressure chamber 13 and the internal space 66 of the pressure sensitive body 61 are maintained at substantially the same primary pressure.

[0076] The outlet port 12 of the solenoid valve 1 is connected to a flow path communicating with the upstream side of the heat exchanger H2 (see Figure 1 ).

[0077] The solenoid 80 is connected to the valve housing 10 and applies a driving force to the valve element 51. The solenoid 80 is mainly composed of a housing 81, a center column 82, a shaft 83, a movable iron core 84, a coil spring 85, a coil 86, and a sleeve 87.

[0078] The housing 81 is formed in a stepped cylindrical shape.

[0079] The center column 82 is formed of a rigid body of a magnetic material such as iron or silicon steel into a cylindrical shape that is T-shaped to the right when viewed from a cross section. The center column 82 is inserted from the opening on the axial right side of the housing 81 toward the axial left side. In addition, the right end of the center column 82 is embedded and fixed to the small diameter end 16 of the valve housing 10. In addition, the small diameter end 16 is embedded and fixed to the opening on the axial right side of the housing 81.

[0080] The shaft 83 is inserted through the center column 82 and is arranged to be reciprocatable in the axial direction.

[0081] The axial left end portion of the shaft 83 is inserted and fixed to the movable iron core 84 .

[0082] The coil spring 85 is disposed between the center column 82 and the movable iron core 84 , and urges the movable iron core 84 toward the opening direction of the valve 50 , that is, toward the axial left side.

[0083] The coil 86 is for excitation, and is wound around the center column 82 and the outer side of the sleeve 87 via a bobbin.

[0084] The sleeve 87 is formed in a bottomed cylindrical shape. A part of the center column 82 , the movable iron core 84 , and the coil spring 85 are accommodated inside the sleeve 87 .

[0085] Next, the working form of the solenoid valve 1 is described. In addition, in this description, the force acting on the valve core 51 axially to the right, that is, the closing direction of the valve 50 is sometimes recorded as a positive force, and the force acting on the valve core 51 axially to the left, that is, the opening direction of the valve 50 is sometimes recorded as a negative force.

[0086] like Figure 4 As shown, the solenoid valve 1 can be switched to an open state of the valve 50 according to the amount of power supplied including the non-powered power zero state (see Figure 2 ) and the valve 50 is in the throttle control state in the second state A2 (refer to Figure 6 , Figure 7 ). Hereinafter, the states of the solenoid valve 1 will be described in detail in the order in which the amount of energization increases from the non-energized state.

[0087] like Figure 2 As shown, in the non-energized state of the solenoid valve 1, the movable iron core 84 is moved by the force (F sp1) is pressed axially to the left. As a result, the valve core 51 is pressed against the center column 82 via the shaft 83.

[0088] At this time, the valve 50 is in the open state with the maximum opening degree. Therefore, the heat medium introduced into the primary pressure chamber 13 from the inlet port 11 is at a substantially primary pressure P 1 After flowing into the secondary pressure chamber 14 through the communication flow path 10a, the heat medium flows into the secondary pressure side, that is, the heat exchanger H2 from the outlet port 12. Therefore, the pressure of the heat medium in the primary pressure chamber 13 is substantially the same as the pressure of the heat medium in the secondary pressure chamber 14.

[0089] In addition, the valve body 51 is pressed against the center post 82. As a result, the primary pressure P in the primary pressure chamber 13 is increased. 1 The heat medium is difficult to flow into the communication passage 51a of the valve core 51 and the large diameter hole portion 53c (see Figure 3 ) and inside the through hole 54b.

[0090] On the other hand, the communication passage 51a, the large diameter hole portion 53c and the through hole 54b of the valve body 51 communicate with the secondary pressure chamber 14 through the through hole 54b. 2 The heat medium flows into the communication passage 51 a of the valve element 51 , the large-diameter hole portion 53 c , and the through hole 54 b .

[0091] Reference Figure 2 , Figure 4 When the electromagnetic valve 1 is powered (i.e., in normal control, so-called duty cycle control), if the current applied to the solenoid 80 is less than a1 ampere, the electromagnetic force (F sol ) is the force of the coil spring 85 (F sp1 ) or less (F sol ≤F sp ). Therefore, the valve 50 is maintained in the open state (first state A1).

[0092] In addition, refer to Figures 4 to 6 When the current applied to the solenoid 80 exceeds a1 ampere, the electromagnetic force (F sol ) exceeds the force of the coil spring 85 (F sp1 )(F sol >F sp1 As a result, the movable iron core 84 overcomes the force (F sp1 ) and is pulled toward the center column 82 side, that is, toward the right side in the axial direction. The valve element 51 driven by the movable iron core 84 together with the shaft 83 abuts against the pressure sensitive body 61, and the electromagnetic valve 1 switches from the first state A1 to the second state A2.

[0093] The switching from the first state A1 to the second state A2 will be described in detail. Figure 5As shown, when the movable iron core 84 is pulled to the right in the axial direction and starts to move, the valve body 51 is driven by the movable iron core 84 and the shaft 83 and slightly separates from the center column 82. At this time, the contact member 54 separates from the adapter 63.

[0094] The valve body 51 is separated from the center column 82, whereby the communication passage 51a, the large diameter hole 53c and the through hole 54b communicate with the primary pressure chamber 13 and the secondary pressure chamber 14. Therefore, the heat medium can pass through the communication passage 51a, the large diameter hole 53c and the through hole 54b.

[0095] Furthermore, the effective area of ​​the valve body 51 is reduced by each communication passage 51a compared to the effective area of ​​a solid valve body. Therefore, the resistance generated when the valve body 51 moves is smaller than the resistance generated when the solid valve body moves.

[0096] As a result, the valve element 51 can be brought into instantaneous contact with the pressure sensitive body 61 (see Figure 6 ). Thus, the solenoid valve 1 can be instantly switched from the first state A1 to the second state A2.

[0097] When the valve element 51 contacts the pressure sensitive body 61, the curved surface 54a of the contact member 54 of the valve element 51 contacts the tapered surface 63d of the adapter 63 of the pressure sensitive body 61 (see Figure 6 ). At this time, the curved surface 54a of the abutment 54 is guided by the conical surface 63d of the adapter 63 so that its axis is roughly consistent with the axis of the pressure sensitive body 61. As a result, the valve core 51 can be aligned with the pressure sensitive body 61. In addition, the axis of the pressure sensitive body 61 is previously aligned with the axis of the valve seat 15a.

[0098] In addition, the axial right end of the contact member 54 including the curved surface 54a is fitted in and contacts the axial left end of the adapter 63 (see Figure 6 ). As a result, the valve element 51 is supported by the pressure sensitive body 61. Therefore, even if an external force such as vibration acts on the valve element 51, the valve element 51 can be suppressed from tilting.

[0099] The curved surface 54a of the contact member 54 contacts the tapered surface 63d of the adapter 63, thereby defining a space R (see FIG. 1 ) inside the contact member 54 and the adapter 63. Figure 6 The space R is formed by the large diameter hole portion 53c of the valve core 51, the through hole 54b of the valve core 51, and the recessed portion 63a of the adapter 63. On the other hand, the space R communicates with the primary pressure chamber 13 through the communication path 51a of the valve core 51.

[0100] Thus, in the space R, the heat medium corresponds to the primary pressure P of the heat medium in the primary pressure chamber 13. 1 Therefore, the pressure of the heat medium in the space R is maintained at the same level as the primary pressure P of the heat medium in the primary pressure chamber 13. 1About the same.

[0101] In addition, the space R is sealed by the contact between the curved surface 54a and the tapered surface 63d. 1 The heat medium accidentally flows out from the space R into the secondary pressure chamber 14.

[0102] Reference Figure 6 In the second state A2, the primary pressure P of the heat medium in the primary pressure chamber 13, the sleeve 87 and the space R acts on the valve body 51. 1 , the secondary pressure P of the heat medium in the secondary pressure chamber 14 2 , the primary pressure P of the heat medium in the pressure sensitive body 61 1 , electromagnetic force (F sol ), the force of the coil spring 85 (F sp1 ) and the force of the coil spring 65 (F sp2 ).

[0103] The primary pressure P of the heat medium in the primary pressure chamber 13, the sleeve 87 and the space R 1 It can be considered that the pressure acts on an effective area that is substantially the same as the effective opening area S1 of the valve 50, that is, the flow path cross-sectional area S1 of the communication flow path 10a. 11 =P 1 ×S1) Press the shaft to the right.

[0104] The secondary pressure P of the heat medium in the secondary pressure chamber 14 2 It can be regarded as the pressure acting on the effective opening area S1 of the valve 50 and the effective area S2 of the pressure sensitive body 61. As a result, the valve core 51 is subjected to the force (-F 21 =-P 2 ×S1) is pressed toward the left side of the axis and is driven by force (F 22 =P 2 ×S2) Press toward the right side of the axis.

[0105] The primary pressure P of the heat medium in the pressure sensitive body 61 1 It can be regarded as the pressure acting on the effective area S2 of the pressure sensitive body 61. As a result, the valve core 51 is 12 =-P 1 ×S2) Press toward the left side of the axis.

[0106] The solenoid valve 1 is configured such that an effective opening area S1 of the valve 50 is equal to an effective area S2 of the pressure sensitive body 61 ( S1 = S2 ).

[0107] As a result, the valve element 51 is adjusted from the primary pressure P 1 The force (F P1 =F 11 -F 12=P 1 ×S1-P 1 × S2) becomes zero. In addition, the valve core 51 is adjusted from the secondary pressure P 2 The force (F P2 =-F 21 +F 22 =-P 2 ×S1+P 2 × S2) becomes zero. That is, the valve core 51 changes from the primary pressure P 1 , secondary pressure P 2 The force (F P1P2 =F P1 -F P2 ) becomes zero.

[0108] Thus, in the second state A2, the valve element 51 is moved according to the force (F=F P1P2 +F sol -(F sp1 +F sp2 )=F sol -(F sp1 +F sp2 )) and move.

[0109] Thus, the solenoid valve 1 can be operated according to the electromagnetic force (F sol ) and the sum of the forces of the coil springs 65 and 85 (F sp1 +F sp2 ) to operate the valve core 51. That is, the solenoid valve 1 can control the opening of the valve 50 corresponding to the signal with a good response to the input signal output from the control unit not shown.

[0110] Specifically, if the electromagnetic force (F sol ) exceeds the sum of the forces of coil springs 65 and 85 (F sp1 +F sp2 ), the valve core 51 overcomes the sum of the forces of the coil springs 65 and 85 (F sp1 +F sp2 ) and moves axially to the right, the opening of valve 50 becomes narrower. sol ) is lower than the sum of the forces of coil springs 65 and 85 (F sp1 +F sp2 ), the valve core 51 is acted upon by the sum of the forces of the coil springs 65 and 85 (F sp1 +F sp2 ) is pressed and moves axially to the left, and the opening of the valve 50 is enlarged.

[0111] Furthermore, if Figure 4 As shown, when the current applied to the solenoid 80 reaches a2 amperes, as shown in Figure 7As shown in FIG. 1 , the curved surface 52a of the valve body 51 is seated on the valve seat 15a. As a result, the valve 50 is in a closed state.

[0112] In this closed state, the curved surface 52a of the valve body 51 is guided and seated on the valve seat 15a. Therefore, the valve 50 is stably in the closed state.

[0113] like Figure 4 As shown in FIG. 1 , in the electromagnetic valve 1 , the change in the opening of the valve 50 relative to the current applied to the solenoid 80 is very gentle relative to the change in the opening when switching from the first state A1 to the second state A2. In addition, in the second state A2, the valve core 51 reduces the primary pressure P of the heat medium as described above. 1 and secondary pressure P 2 Therefore, the secondary pressure P can be accurately controlled. 2 .

[0114] In addition, as described above, in the solenoid valve 1, the valve core 51 can be centered by the pressure sensitive body 61. Therefore, the solenoid valve 1 is sensitive to the secondary pressure P 2 For example, when the axis of the valve core tilts relative to the axis of the valve seat, the opening of the valve core and the valve seat will vary at various points on the circumference of the valve core, which may result in a secondary pressure P different from the desired one. 2 difference.

[0115] On the other hand, when the current applied to the solenoid 80 is less than a1 ampere, the electromagnetic force (F sol ) is lower than the force of the coil spring 85 (F sp1 )(F sol <F sp1 As a result, the movable iron core 84 is biased by the force (F sp1 ) is pressed to the opposite side of the center column 82, that is, to the axial left side. The valve core 51 driven by the movable iron core 84 together with the shaft 83 is separated from the pressure sensitive body 61 (refer to Figure 2 and Figure 5 ), the solenoid valve 1 switches to the first state A1.

[0116] The switching from the second state A2 to the first state A1 will be described in detail. As described above, in the second state A2, the pressure of the heat medium in the space R is maintained at the same pressure as the primary pressure P of the heat medium in the primary pressure chamber 13. 1 This prevents the movement of the valve element 51 from being hindered.

[0117] In addition, as described above, in the space R, the heat medium corresponds to the primary pressure P of the heat medium in the primary pressure chamber 13. 1Therefore, the solenoid valve 1 prevents the valve core 51 from being separated from the pressure sensitive body 61, thereby preventing the pressure in the space R from decreasing and becoming difficult to separate.

[0118] As described above, the valve element 51 connects the primary pressure chamber 13 and the secondary pressure chamber 14 via the communication passage 51 a , the large diameter hole 53 c , and the through hole 54 b , thereby reducing the resistance during movement.

[0119] Thereby, the solenoid valve 1 can be instantly switched from the second state A2 to the first state A1.

[0120] According to the above content, if Figure 4 As shown, in the electromagnetic valve 1 , the change in the opening degree of the valve 50 between the open state and the closed state, that is, the movement amount of the valve element 51 changes intermittently with respect to the current applied to the solenoid 80 .

[0121] Thus, when switching from cooling to heating, the solenoid valve 1 can quickly enter the throttling control state and reduce the primary pressure P 1 Reduce to the desired secondary pressure P 2 In addition, when switching from heating to cooling, the solenoid valve 1 can be quickly opened to maintain the primary pressure P 1 The state allows the heat medium to pass through.

[0122] For example, in the process from the position of the valve core in the non-powered state to the seat on the valve seat, the solenoid valve whose opening changes in the form of a proportional function or a quadratic function needs time to become a throttling control state or an open state when switching from cooling to heating or from heating to cooling. During this period, heat medium with unexpected pressure is easily supplied to the secondary pressure side.

[0123] The solenoid valve 1 can switch between the on-off valve function and the pressure reducing valve function simply by controlling the current applied to the solenoid 80. Therefore, the solenoid valve 1 can help simplify control compared to a structure that requires separate control of an on-off valve and a pressure reducing valve.

[0124] As mentioned above, although the embodiment of the present invention is described based on the drawings, the specific structure is not limited to these embodiments, and even if there are changes and additions within the scope that does not depart from the gist of the present invention, they are also included in the present invention.

[0125] For example, in the above-mentioned embodiment, the valve is described as being applied to a heat pump cycle, but the invention is not limited thereto and may be applied to a hydraulic circuit or may be modified as appropriate.

[0126] In addition, in the above embodiment, the case where the fluid passing through the valve is a heat medium is described, but it is not limited to this. The type of fluid such as water and air can be appropriately changed, the state of fluid such as air, liquid, and mist can be appropriately changed, and the type and state of fluid can be mixed.

[0127] In the above embodiments, the valve is described as being used as an on-off valve and as a pressure reducing valve, but the present invention is not limited thereto. For example, the valve may be used only as a pressure reducing valve or only as an on-off valve.

[0128] In the above-described embodiment, an expansion valve is exemplified as the function of the valve as a pressure reducing valve, but the present invention is not limited to this, and a pressure reducing valve other than an expansion valve may be used.

[0129] In the above-mentioned embodiment, the case where the valve is a solenoid-type electromagnetic valve is described, but the present invention is not limited thereto, and the driving source may be the rotation of a motor, or may be manual, or may be modified as appropriate.

[0130] In the above-described embodiment, the valve is a normally open type that is opened in a non-energized state, but the present invention is not limited thereto and may be a normally closed type that is closed in a non-energized state.

[0131] In addition, in the above-mentioned embodiment, the case where the effective opening area of ​​the valve is the same as the effective area of ​​the pressure-sensitive body is described, but it is not limited to this and may be different. Even with such a structure, the force acting on the valve core can be reduced accordingly according to the amount of overlap between the effective opening area of ​​the valve and the effective area of ​​the pressure-sensitive body.

[0132] In the above embodiment, the open state is described as the maximum opening of the valve, but the present invention is not limited thereto and the valve may not be the maximum opening as long as the opening allows the heat medium to pass at a constant pressure or at substantially the same pressure.

[0133] In the above embodiment, the structure in which the valve opening in the first state is kept substantially constant is described, but the present invention is not limited thereto and may be appropriately changed as long as the change in the valve opening is smaller than when switching from the first state to the second state.

[0134] In addition, in the above-mentioned embodiment, the case where the valve opening when transferring from the first form to the second form changes rapidly when it is approximately orthogonal to the change in the valve opening in the first form is described, but it is not limited to this. As long as the change in the valve opening is more rapid than the change in the valve opening in the second state, it can be appropriately changed.

[0135] Furthermore, in the above-described embodiment, the configuration in which the valve opening degree in the second mode changes in the form of a proportional function has been described, but the present invention is not limited thereto and may change in the form of a quadratic function.

[0136] In the above embodiment, the valve element is described as being composed of a base material, a shaft holder, and a contact member, but the present invention is not limited thereto and may be a single component. For example, the contact portion may be a part of the base material.

[0137] In addition, in the above-mentioned embodiment, the valve core is described as a component separate from the shaft, but the present invention is not limited thereto and the valve core may be integrated with the shaft. For example, the shaft and the shaft holder may be a single component.

[0138] In addition, in the above embodiment, the structure in which the space divided by the valve core and the pressure sensitive body in the second form is connected to the primary pressure chamber is described, but it is not limited to this. The primary pressure chamber side may be closed and connected to the secondary pressure chamber. For example, a through hole connected to the secondary pressure chamber may be formed in the adapter. Even with such a structure, the valve core and the pressure sensitive body can be smoothly abutted, and the valve core and the pressure sensitive body can be smoothly separated.

[0139] In addition, in the above-mentioned embodiment, the structure in which the valve core and the pressure sensitive body define a space in the second form is described, but it is not limited to this, and the valve core and the pressure sensitive body may be configured so that no space is formed. Even in such a structure, from the viewpoint of contact or separation between the valve core and the pressure sensitive body, it is also preferable to configure so that no heat medium remains between the valve core and the pressure sensitive body that are concavely and convexly fitted.

[0140] In addition, in the above-mentioned embodiment, the three communication passages 51a having openings in the effective opening area S1 of the valve 50 in the valve core 51 are described as the communication passages of the valve core, but the present invention is not limited thereto, and the communication passages may be any structure as long as they are connected to the primary pressure chamber 13 and the space R. For example, the structure may be a structure that does not open to the axial right end of the valve core but opens in the outer diameter direction, and the structure may be appropriately changed.

[0141] In the above embodiment, the case where the heat medium flows from the primary pressure chamber 13 to the secondary pressure chamber 14 is described, but the present invention is not limited to this. Figure 2 , it is also possible to have a structure in which the heat medium flows from the other pressure chamber 14 to the one pressure chamber 13. That is, in the throttling control state of the valve, the other pressure chamber may be the primary pressure side, and the one pressure chamber may be the secondary pressure side.

[0142] Explanation of symbols

[0143] 1: Solenoid valve (valve);

[0144] 13: primary pressure chamber (one pressure chamber);

[0145] 14: Secondary pressure chamber (another pressure chamber);

[0146] 15a: valve seat;

[0147] 50: valve;

[0148] 51: valve core;

[0149] 51a: connecting road;

[0150] 54: abutment member (abutment portion);

[0151] 54a: curved surface;

[0152] 61: pressure sensitive body;

[0153] 63: adapter;

[0154] 63d: cone surface;

[0155] 66: Internal space;

[0156] 80: Solenoid;

[0157] A1: First form;

[0158] A2: Second form;

[0159] P1: one-time pressing;

[0160] P2: secondary pressure;

[0161] R: Space;

[0162] S1: effective opening area;

[0163] S2: effective area.

Claims

1. A valve having a valve element and a valve seat, the valve element and the valve seat being disposed between a pressure chamber and another pressure chamber, and controlling the flow rate of fluid passing through the pressure chamber and the other pressure chamber by opening and closing. Wherein, On a part of the other pressure chamber, a pressure-sensitive body that internally introduces the pressure of the one pressure chamber is disposed so as to be able to contact or separate from the valve element.

2. The valve according to claim 1, Wherein, The valve can be switched to a first form in which the opening degree of the valve is in an open state and a second form in which the valve element performs throttling control at a position closer to the valve seat than the open state.

3. The valve according to claim 2, Wherein, The valve element is separated from the pressure-sensitive body in the first form and abuts against the pressure-sensitive body in the second form.

4. The valve according to claim 3, Wherein, The pressure-sensitive body has an adapter, The valve element has an abutting portion at the front end, At least one of the adapter and the abutting portion has a tapered surface that can abut against the other.

5. The valve according to claim 4, Wherein, A communication path is formed in the valve element, and the communication path communicates with the space formed by the abutting portion and the adapter and the one pressure chamber in the second form.

6. The valve according to any one of claims 1 to 5, Wherein, The effective opening area of the valve is the same as the effective area of the pressure-sensitive body.

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