JP5944884B2 - On-off valve - Google Patents

Description

  The present invention relates to an on-off valve that is used in, for example, a refrigerant circulation circuit of an air conditioner such as an air conditioner or a refrigerator, and controls the flow of fluid by operation of a valve body.

  2. Description of the Related Art Conventionally, a pilot-type electromagnetic valve provided with an on-off valve, for example, a pilot valve is configured as disclosed in Patent Document 1 (Japanese Utility Model Publication No. 61-41015).

  FIG. 11 is a longitudinal sectional view of a conventional pilot-type solenoid valve 100 showing a state in which fluid flows from the primary-side flow path to the secondary-side flow path in the conventional pilot-type solenoid valve 100 of Patent Document 1. 12 is a longitudinal sectional view of a conventional pilot-type solenoid valve 100 showing a state in which fluid flows from the secondary-side flow path to the primary-side flow path in the conventional pilot-type solenoid valve 100, and FIG. FIG. 3 is a longitudinal sectional view of a conventional pilot-type solenoid valve 100 in a closed state.

  That is, as shown in FIGS. 11 to 13, the conventional pilot-type electromagnetic valve 100 includes a valve body 102. The valve body 102 is formed with a substantially cylindrical cylinder chamber 104 formed in the vertical direction, that is, in the axis Y direction in FIGS.

  In the cylinder chamber 104, a piston valve 106 constituting a piston-shaped valve body that is slidable in the vertical direction, that is, in the axis Y direction in FIGS.

  Further, the piston valve 106 includes a large diameter portion 112 that slides on the inner peripheral wall 110 of the side peripheral wall 108 of the cylinder chamber 104, and has a smaller diameter than the large diameter portion 112 below the large diameter portion 112. A valve body 114 constituting the body is formed.

  Further, a primary port 116 is formed on the right side in FIGS. 11 to 13 on the side peripheral wall 108 of the cylinder chamber 104, and a joint-shaped primary flow path 118 is attached to the primary port 116. Yes.

  A secondary port 120 is formed below the cylinder chamber 104, and a joint-shaped secondary flow path 122 is attached to the secondary port 120. A valve seat 124 is formed above the secondary port 120, and a valve port 124 a is formed in the valve seat 124.

  On the other hand, the cylinder chamber 104 of the valve body 102 has a valve chamber a formed on the valve seat 124 side of the piston valve 106 and a side opposite to the valve seat 124 side of the piston valve 106 across the piston valve 106. A formed valve chamber b is formed.

  Further, the large-diameter portion 112 of the piston valve 106 is formed with a recess 130 that forms a part of the space of the valve chamber b on the inner peripheral side thereof. The recess 130 has a stepped portion having a reduced diameter. 132 is formed.

  The valve body portion 114 of the piston valve 106 is connected to a valve body communicating with a recess 130 forming a part of the valve chamber b and a valve chamber a formed on the valve seat side of the piston valve 106. A passage 134 is formed.

  That is, as shown in FIGS. 11 to 13, the valve body communication path 134 includes an axial communication path 136 formed in the axial direction of the piston valve 106 in the center of the bottom of the recess 130 of the piston valve 106, and this shaft. Two radial communication paths 138 extending from the lower end of the direction communication path 136 to the radially outer side of the valve body 114 of the piston valve 106 are formed.

  Further, the openings 140 of these radial communication passages 138 open to the vertical side wall 142 of the valve body 114 of the piston valve 106, and as shown in FIGS. In the valve open state, it is formed at a position facing the primary side port 116 of the primary side flow path 118.

  Further, as shown in FIG. 13, the valve body 114 of the valve body 114 of the piston valve 106 is seated on the valve seat 124 and closes the valve port 124a in the closed state, as shown in FIG. A tapered inclined surface 144 whose diameter decreases toward the port 124a is formed.

A ball-shaped check valve 146 is mounted in the axial communication path 136 of the piston valve 106, and a ring-shaped check valve seat 148 mounted at the center of the bottom of the recess 130 of the piston valve 106. In addition, it is configured to act as a check valve by contacting and separating. Reference numeral 141 indicates a biasing coil spring 141 that biases the check valve 146 toward the check valve seat 148 .

  The check valve seat 148 is fixed by caulking 150 the peripheral wall of the opening of the axial communication path 136 formed at the center of the bottom of the recess 130 of the piston valve 106.

  Further, an opening 152 is formed in the upper part of the cylinder chamber 104 of the valve body 102. After the piston valve 106 is mounted on the cylinder chamber 104 through the opening 152, the opening 152 is covered with a lid member. 154 is configured to be closed.

  The lid member 154 is fixed by caulking 156 on the side peripheral wall 108 of the opening 152 at the top of the cylinder chamber 104.

  Further, a spring 158 is interposed in a compressed state between the step portion 132 of the concave portion 130 of the large diameter portion 112 of the piston valve 106 and the lid member 154, whereby the piston valve 106 is inserted into the valve seat 124. It is comprised so that it may urge in the direction of.

  On the other hand, as shown in FIGS. 11 to 13, the valve main body 102 has a left and right direction, that is, an axis X direction orthogonal to the axis Y direction in FIGS. A pilot valve chamber 160 is formed on the left side in FIG.

  A pilot valve seat 162 is formed on the lower side wall of the valve body 102, and a pilot port 164 is formed in the pilot valve seat 162. A pilot passage 166 that communicates the pilot valve chamber 160 and the secondary port 120 is also formed.

  Further, a communication passage 168 that connects the valve chamber b of the cylinder chamber 104 and the pilot valve chamber 160 in the axis Y direction in FIGS. 11 to 13 is formed in the side peripheral wall 108 of the cylinder chamber 104 of the valve body 102. Has been.

  A cylindrical plunger case 172 is fixed to the side peripheral wall 170 of the pilot valve chamber 160. The plunger case 172 includes a plunger 174 that can move left and right in the direction of the axis X of the plunger case 172.

  A suction element 176 is fixed to the end of the plunger case 172 in the opposite direction to the pilot valve chamber 160. Between the suction element 176 and the plunger 174, the plunger 174 is moved in the right direction, that is, the pilot. A coil spring 178 that biases the plunger 174 in the direction of the valve seat 162 is interposed.

  That is, the coil spring 178 is interposed between the spring mounting hole 180 formed on the plunger 174 on the side of the suction element 176 and the suction element 176.

  Further, a spherical pilot valve 182 spaced from the pilot valve seat 162 is provided at the tip of the plunger 174.

  That is, the pilot valve 182 is attached in a state of protruding from the tip 174 a of the plunger 174 toward the pilot valve seat 162 by crimping the tip 174 a of the plunger 174.

  A control unit 186 including an electromagnetic coil 184 is provided on the outer periphery of the plunger 174. Note that the control unit 186 is illustrated in a simplified manner, and although not illustrated, the control unit 186 includes a magnetic frame that forms a magnetic path.

  An annular sub-channel 188 is formed by a clearance between the large diameter portion 112 formed at the upper portion of the piston valve 106 and the inner peripheral wall 110 of the side peripheral wall 108 of the cylinder chamber 104.

  The conventional pilot type solenoid valve 100 configured as described above is operated as follows.

  For example, when the solenoid valve 100 is used in a refrigerant circulation circuit of an air conditioner such as an air conditioner / refrigerator, the flow direction from the primary side flow path 118 to the secondary side flow path 122 (arrow K in FIG. 11). When the heating operation is performed, the electromagnetic coil 184 of the control unit 186 is energized from the state of FIG. 13 so that the plunger 174 is attracted against the urging force of the coil spring 178 as shown in FIG. It moves in the direction of the child 176 (to the left in FIG. 11).

  As a result, as shown in FIG. 11, the pilot valve 182 attached to the tip 174a of the plunger 174 moves away from the pilot valve seat 162 formed in the valve body 102, and the pilot passage 166 is opened. Will be.

  Immediately after the electromagnetic coil 184 of the control unit 186 is energized, the high-pressure fluid remaining in the valve chamber b formed in the cylinder chamber 104 is transferred to the cylinder chamber 104 of the valve body 102 as indicated by an arrow J in FIG. It flows into the pilot valve chamber 160 through a communication passage 168 formed in the side peripheral wall 108.

  Furthermore, the high-pressure fluid that has flowed into the pilot valve chamber 160 passes through the secondary port 120 through the pilot port 164 and the pilot passage 166 formed in the pilot valve seat 162, and then through the secondary channel 122. Discharged. For this reason, the valve chamber b is in a low pressure state.

  As a result, the valve chamber a becomes high pressure and the valve chamber b becomes low pressure. Due to this pressure difference, the piston valve 106 moves away from the valve seat 124 against the biasing force of the spring 158, The valve port 124a formed in the seat 124 is opened.

  As a result, as indicated by an arrow K in FIG. 11, the primary side channel 116 passes through the valve port a, the valve port 124a formed in the valve seat 124, the secondary side port 120, and the secondary side port 118. A fluid flow reaching the secondary flow path 122 is formed.

  In the state where the electromagnetic coil 184 of the control unit 186 is energized, the valve chamber b is connected from the primary port 116 of the primary channel 118 and the valve chamber a of the cylinder chamber 104 to the inside of the side peripheral wall 108 of the cylinder chamber 104. Some high-pressure fluid flows in through the secondary flow path 188 between the peripheral wall 110 and is discharged through the pilot passage 166 and the secondary side flow path 122. For this reason, the low pressure state of the valve chamber b is maintained, and the open state of the piston valve 106 is maintained.

  Conversely, for example, during cooling operation, the electromagnetic coil 184 of the control unit 186 is not energized, and the plunger 174 is positioned away from the attractor 176 (on the right side in FIG. 11) by the biasing force of the coil spring 178. To do. As a result, the pilot valve 182 attached to the tip 174 a of the plunger 174 abuts on the pilot valve seat 162 formed in the valve body 102 and closes the pilot passage 166.

  The high-pressure fluid that flows into the valve chamber a from the secondary-side flow path 122, which is the high-pressure side, through the secondary port 120 and the valve port 124a formed in the valve seat 124, resists the biasing force of the spring 158. Thus, the piston valve 106 moves away from the valve seat 124. As a result, the valve port 124a formed in the valve seat 124 is opened and discharged from the primary side port 116 to the primary side flow path 118 as indicated by an arrow L in FIG.

  At this time, if the pressure of the high pressure fluid flowing into the pilot passage 166 from the secondary side flow path 122 which is the high pressure side is larger than the biasing force of the coil spring 178 of the plunger 174, the plunger 174 becomes the biasing force of the coil spring 178. On the contrary, it moves in the direction of the suction element 176 (to the left in FIG. 12).

  Accordingly, as indicated by an arrow Q in FIG. 12, the pilot valve 182 attached to the tip 174a of the plunger 174 moves away from the pilot valve seat 162 formed in the valve body 102, and the pilot passage 166 Will be released.

  As a result, the high-pressure fluid that has flowed into the pilot passage 166 from the secondary side flow path 122 flows into the pilot valve chamber 160 as indicated by the arrow P in FIG. 12, and the side peripheral wall of the cylinder chamber 104 of the valve body 102 It flows into the valve chamber b through the communication passage 168 formed in 108.

  However, the high-pressure fluid that has flowed into the valve chamber b is formed in the valve body 114 of the piston valve 106 with the check valve 146 being separated from the check valve seat 148 as indicated by the arrow O in FIG. From the axial direction communication path 136, it returns to the valve chamber a through the radial direction communication path 138, and is discharged from the primary side port 116 to the primary side flow path 118.

  As a result, as indicated by an arrow L in FIG. 12, the primary side flow path 118 passes from the secondary side port 120 of the secondary side flow path 122 through the valve port 124 a formed in the valve chamber a and the valve seat 124. A fluid flow to the primary side port 116 is formed.

  As indicated by an arrow L in FIG. 12, when the secondary side flow path 122 has a high pressure and the fluid flow direction flows from the secondary side flow path 122 to the primary side flow path 118 on the low pressure side, the spring If a pressure difference that causes the piston valve 106 to move away from the valve seat 124 against the urging force of 158 is generated, the opening / closing control of the piston valve 106 by the electromagnetic coil 184 of the control unit 186 cannot be performed. The valve open state is maintained only by the difference.

Japanese Utility Model Publication No. 61-41015

  However, in such a conventional pilot-type solenoid valve 100, as shown by an arrow K in FIG. 11, for example, in a heating operation, the piston valve 106, which is a valve body, is in an open state in which it is separated from the valve seat 124. The high-pressure fluid flowing into the valve chamber a of the cylinder chamber 104 of the valve body 102 abuts against the vertical side wall 142 of the valve body portion 114 via the primary port 116 of the primary channel 118. The direction of the 90 ° flow is changed, and a fluid flow is formed through the valve port 124 a and the secondary side port 120 formed in the valve seat 124 to the secondary side flow path 122.

  For this reason, a turbulent flow is generated by such a flow, the flow rate is reduced due to pressure loss, and a large flow rate cannot be controlled.

  In view of the present situation, an object of the present invention is to provide an on-off valve that is less likely to generate turbulence by devising an internal structure, can reduce pressure loss, and can control a large flow rate.

The present invention has been invented in order to achieve the problems and objects in the prior art as described above.
An on-off valve configured to move in a direction away from a valve seat formed in a valve body, and to open a valve port provided in the valve seat;
When the piston valve is open from the valve seat, the main valve portion of the piston valve facing the primary port of the primary flow path is configured with a tapered inclined surface whose diameter decreases toward the valve port. and,
The valve body is formed with a valve chamber a formed on the valve seat side in the piston valve and a valve chamber b formed on the opposite side to the valve seat side in the piston valve,
The piston valve is formed with a valve body communication passage that communicates the valve chamber b and the valve chamber a.
The valve body communication path includes a radial communication path including an opening that extends radially outward of the valve body portion of the piston valve and communicates with the valve chamber a.
In the open state in which the piston valve is separated from the valve seat, the opening of the radial communication path communicating with the valve chamber a is in the valve opening direction with respect to the primary side port of the primary side flow path, and the primary side It is provided at a position not facing the port .

  Thus, for example, during heating operation, in a valve-open state in which the piston valve is separated from the valve seat, the high-pressure side fluid that flows in through the primary port of the primary channel flows along the tapered inclined surface. You will be guided smoothly towards the port. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a large flow rate can be controlled.

  Further, for example, during cooling operation, when the piston valve is open from the valve seat, the high-pressure fluid flowing through the secondary port and the valve port of the secondary channel flows into the tapered inclined surface. Along the way, it is smoothly guided from the valve port toward the primary port. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a large flow rate can be controlled.

Further, with this configuration, in the open state in which the piston valve is separated from the valve seat, the opening of the valve body communication passage communicating with the valve chamber a is the primary side primary port primary side flow passage. Since the primary side port is provided in a position that does not face the primary side port in the valve opening direction, the amount of high-pressure fluid from the primary side port of the primary side flow path into the valve body communication passage is small. Become.

  Further, in the open state in which the piston valve is separated from the valve seat, the high-pressure fluid that has flowed into the valve chamber b due to the negative pressure of the high-pressure fluid that flows in through the secondary-side port of the secondary-side flow path, It becomes easy to be smoothly discharged from the valve chamber b to the valve chamber a through the valve body communication passage.

  Thereby, in a valve open state in which the piston valve is separated from the valve seat, the high-pressure fluid flowing into the valve chamber b is smoothly discharged from the valve chamber b to the valve chamber a via the valve body communication passage. Therefore, since the inside of the valve chamber b becomes a low pressure, the piston valve does not contact the valve seat to close the valve port, and the fluid can flow smoothly and without a decrease in the flow rate.

In the on-off valve of the present invention, the valve main body includes a valve chamber a formed on the valve seat side of the piston valve and a valve chamber b formed on the side opposite to the valve seat side of the piston valve. Formed,
The piston valve is formed with a valve body communication passage that communicates the valve chamber b and the valve chamber a.
When the piston valve is opened from the valve seat, an opening of the valve body communication passage communicating with the valve chamber a is provided on the tapered inclined surface.

  With this configuration, since the opening of the valve body communication passage communicating with the valve chamber a is provided on the tapered inclined surface in the open state in which the piston valve is separated from the valve seat, the primary-side flow path is provided. The high-pressure fluid from the primary side port is guided along the tapered inclined surface and guided toward the valve port, and the amount flowing into the valve body communication path is reduced.

  Thereby, in a valve open state in which the piston valve is separated from the valve seat, the high-pressure fluid flowing into the valve chamber b is smoothly discharged from the valve chamber b to the valve chamber a via the valve body communication passage. Therefore, since the inside of the valve chamber b becomes a low pressure, the piston valve does not contact the valve seat to close the valve port, and the fluid can flow smoothly and without a decrease in the flow rate.

  The on-off valve of the present invention is characterized in that a plurality of openings of the valve body communication passage communicating with the valve chamber a are formed in the circumferential direction of the piston valve.

  With this configuration, a plurality of high-pressure fluids that flow into the valve chamber b are formed from the valve chamber b in the circumferential direction of the piston valve when the piston valve is open from the valve seat. Since the valve chamber a is smoothly discharged through the opening of the valve body communication passage communicating with the valve body and the valve body communication passage, the inside of the valve chamber b becomes low pressure, so that the piston valve contacts the valve seat. Thus, the valve port is not closed, and the fluid can flow smoothly and without decreasing the flow rate.

  The on-off valve of the present invention is characterized in that the tapered inclined surface is formed of a plurality of tapered inclined surfaces having different inclination angles α.

  With this configuration, in a valve-opened state where the piston valve is separated from the valve seat, the high-pressure side fluid flowing in through the primary port of the primary channel has a plurality of stages of taper inclinations with different inclination angles α. It will be guided more smoothly along the surface towards the valve port. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  In addition, when the piston valve is open from the valve seat, the high pressure fluid flowing in through the secondary port and the valve port of the secondary flow passage has a plurality of stages of taper inclinations with different inclination angles α. It will be smoothly guided along the surface from the valve port toward the primary port. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  Further, in the on-off valve of the present invention, the tapered inclined surfaces of the plurality of stages are formed such that the tapered inclined surface on the proximal end side of the main valve portion of the piston valve has a larger inclination angle α than the tapered inclined surface on the distal end side. It is characterized by being.

  With this configuration, when the piston valve is in the open state separated from the valve seat, the high-pressure side fluid flowing in through the primary port of the primary flow path is the base end side of the main valve portion of the piston valve. The taper inclined surface is more smoothly guided toward the valve port along a plurality of steps of the taper inclined surface having a larger inclination angle α than that of the tip side taper inclined surface. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  Further, in the open state where the piston valve is separated from the valve seat, the high-pressure side fluid flowing in via the secondary side port and the valve port of the secondary side flow passage is on the base end side of the main valve portion of the piston valve. The tapered inclined surface is smoothly guided from the valve port toward the primary side port along a plurality of tapered inclined surfaces formed with a larger inclination angle α than the tapered inclined surface on the distal end side. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  In the on-off valve of the present invention, the taper inclined surface of the plurality of stages is formed such that the taper inclined surface on the proximal end side of the main valve portion of the piston valve has a smaller inclination angle α than the taper inclined surface on the distal end side. It is characterized by being.

  With this configuration, when the piston valve is in the open state separated from the valve seat, the high-pressure side fluid flowing in through the primary port of the primary flow path is the base end side of the main valve portion of the piston valve. The tapered inclined surface is more smoothly guided toward the valve port along the plurality of tapered inclined surfaces formed with a smaller inclination angle α than the tapered inclined surface on the distal end side. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  Further, in the open state where the piston valve is separated from the valve seat, the high-pressure side fluid flowing in via the secondary side port and the valve port of the secondary side flow passage is on the base end side of the main valve portion of the piston valve. The tapered inclined surface is smoothly guided from the valve port toward the primary port along a plurality of tapered inclined surfaces formed with a smaller inclination angle α than the tapered inclined surface on the distal end side. Therefore, turbulent flow does not occur, pressure loss is reduced, and the flow rate can be improved.

  The on-off valve of the present invention is a pilot-type on-off that includes a main valve portion that opens and closes a valve port formed on the valve seat, and a pilot valve that opens and closes a pilot passage communicating with the flow path. It is a valve.

  According to the present invention, in a valve-opened state where the piston valve is separated from the valve seat, the main valve portion of the piston valve facing the primary port of the primary flow path has a tapered inclined surface whose diameter decreases toward the valve port. It consists of

  Thus, for example, during heating operation, in a valve-open state in which the piston valve is separated from the valve seat, the high-pressure side fluid that flows in through the primary port of the primary channel flows along the tapered inclined surface. You will be guided smoothly towards the port. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a large flow rate can be controlled.

  Further, for example, during cooling operation, when the piston valve is open from the valve seat, the high-pressure fluid flowing through the secondary port and the valve port of the secondary channel flows into the tapered inclined surface. Along the way, it is smoothly guided from the valve port toward the primary port. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a large flow rate can be controlled.

FIG. 1 is a longitudinal sectional view of an on-off valve 10 of the present invention showing a state in which fluid flows from a primary side flow path to a secondary side flow path in the on-off valve 10 of the present invention. FIG. 2 is a vertical cross-sectional view of the on-off valve 10 of the present invention showing a state in which fluid flows from the secondary side flow path to the primary side flow path in the on-off valve 10 of the present invention. FIG. 3 is a longitudinal sectional view of the on-off valve 10 of the present invention in a closed state. 4A is a partially enlarged cross-sectional view of the piston valve 16 of the on-off valve 10 of the present invention, and FIG. 4B is a cross-sectional view taken along line II of the piston valve 16 of FIG. 4A. . FIG. 5A is a partially enlarged cross-sectional view of the piston valve 16 of the on-off valve 10 of the present invention, and FIG. 5B is a cross-sectional view of the piston valve 16 of FIG. . FIG. 6 is a schematic diagram for explaining a necessary lift amount of the piston valve 16 of the on-off valve 10 of the present invention. FIG. 7 is a longitudinal sectional view similar to FIG. 1 showing a comparative example of the structure in which the piston valve 16 is removed from the on-off valve 10 of the present invention. FIG. 8 is a longitudinal sectional view showing only the piston valve 16 showing another embodiment of the on-off valve 10 of the present invention. FIG. 9 is an external side view showing only the piston valve 16 similar to FIG. 8 showing another embodiment of the on-off valve 10 of the present invention. FIG. 10 is an external side view showing only the piston valve 16 similar to FIG. 8 showing another embodiment of the on-off valve 10 of the present invention. FIG. 11 is a longitudinal sectional view of a conventional pilot type solenoid valve 100 showing a state in which fluid flows from the primary side flow path to the secondary side flow path in the conventional pilot type solenoid valve 100. FIG. 12 is a longitudinal sectional view of a conventional pilot-type electromagnetic valve 100 showing a state in which fluid flows from the secondary-side flow path to the primary-side flow path in the conventional pilot-type electromagnetic valve 100. FIG. 13 is a longitudinal sectional view of a conventional pilot-type solenoid valve 100 in a closed state.

Hereinafter, embodiments (examples) of the present invention will be described in more detail with reference to the drawings.
Example 1

  FIG. 1 is a longitudinal sectional view of an on-off valve 10 of the present invention showing a state in which fluid flows from a primary side flow path to a secondary side flow path in the on-off valve 10 of the present invention, and FIG. In the valve 10, it is a longitudinal cross-sectional view of the on-off valve 10 of this invention which shows the state in the case of flowing a fluid from a secondary side flow path to a primary side flow path.

  1-2, the code | symbol 10 has shown the on-off valve 10 of this invention as a whole.

  1 to 2 show an embodiment in which the on-off valve 10 of the present invention is applied to a pilot-type electromagnetic valve provided with a pilot valve.

  As shown in FIGS. 1 to 2, the on-off valve 10 of the present invention includes a valve body 12. The valve body 12 is formed with a substantially cylindrical cylinder chamber 14 formed in the vertical direction, that is, in the axis Y direction in FIGS.

The cylinder chamber 14 is provided with a piston valve 16 that constitutes a piston-shaped valve body that can slide in the vertical direction, that is, in the direction of the axis Y in FIGS.
Reference numeral 11 denotes a sliding ring 11 that is attached to the outer periphery of the large-diameter portion 22 and slides the piston valve 16 straight in the axis Y direction in the cylinder chamber 14.

  The piston valve 16 includes a large-diameter portion 22 that slides on the inner peripheral wall 20 of the side peripheral wall 18 of the cylinder chamber 14, and has a smaller diameter than the large-diameter portion 22 below the large-diameter portion 22. A small-diameter valve body 24 constituting the body is formed.

  Further, a primary port 26 is formed on the right side in FIGS. 1 to 2 in the side peripheral wall 18 of the cylinder chamber 14, and a joint-shaped primary flow path 28 is attached to the primary port 26. Yes.

  A secondary port 30 is formed below the cylinder chamber 14, and a joint-shaped secondary flow path 32 is attached to the secondary port 30. A valve seat 34 is formed above the secondary port 30, and a valve port 34 a is formed in the valve seat 34.

  On the other hand, the cylinder chamber 14 of the valve body 12 has a valve chamber a formed on the valve seat 34 side of the piston valve 16 and a side opposite to the valve seat 34 side of the piston valve 16 across the piston valve 16. A formed valve chamber b is formed.

  Further, the large-diameter portion 22 of the piston valve 16 is formed with a recess 40 that forms a part of the space of the valve chamber b on the inner peripheral side, and the recess 40 has a stepped portion having a reduced diameter. 42 is formed.

  The valve body 24 of the piston valve 16 is connected to a valve body communicating with a recess 40 forming a part of the valve chamber b and a valve chamber a formed on the valve seat side of the piston valve 16. A passage 44 is formed.

  That is, as shown in FIGS. 1 to 2, the valve body communication passage 44 is formed with an axial communication passage 46 formed in the axial direction of the piston valve 16 in the center of the bottom of the recess 40 of the piston valve 16, and this shaft. The directional communication passage 46 is formed from a lower end portion of the directional communication passage 46 and a radial communication passage 48 extending outward in the radial direction of the valve body portion 24 of the piston valve 16.

In addition, the openings 50 of these radial communication passages 48 are open in the vertical side wall 52 of the valve body 24 of the piston valve 16, and in a valve open state where the piston valve 16 is separated from the valve seat 34, The opening 50 of the radial communication passage 48 communicating with the valve chamber a is in the valve opening direction relative to the primary port 26 of the primary flow path 28 (that is, the opening 50 of the radial communication path 48 is connected to the primary flow path. 28 ( position not facing the primary side port 26) (in FIGS. 1 to 2, it is provided at a position in the valve opening direction from the position of the Z line).

With this configuration, in the open state in which the piston valve 16 is separated from the valve seat 34, the opening 50 of the radial communication path 48 that communicates with the valve chamber a serves as the primary port 26 of the primary flow path 28. Since the opening 50 of the radial direction communication path 48 is provided in the valve opening direction (that is, the position where the opening 50 of the radial communication path 48 does not face the primary side port 26) , the primary side port 28 of the primary side flow path 28 is provided. The amount of the high-pressure fluid from 26 flows into the valve body communication passage 44 (the axial communication passage 46 and the radial communication passage 48) is reduced.

  Further, when the piston valve 16 is opened from the valve seat 34, the negative pressure of the high-pressure fluid flowing into the valve chamber a through the secondary port 30 and the valve port 34a of the secondary channel 32 is obtained. The high-pressure fluid that has flowed into the valve chamber b is likely to be smoothly discharged from the valve chamber b into the valve chamber a via the valve body communication passage 44 (the axial communication passage 46 and the radial communication passage 48).

  As a result, in the open state where the piston valve 16 is separated from the valve seat 34, the high-pressure fluid that has flowed into the valve chamber b passes from the valve chamber b to the valve body communication passage 44 (the axial communication passage 46, the radial communication passage 48). ) Is smoothly discharged to the valve chamber a, the pressure in the valve chamber b becomes low, the piston valve 16 does not contact the valve seat 34 and the valve port 34a is not closed, and the fluid is discharged. It can flow smoothly and without a decrease in flow rate.

  In this case, it is desirable that a plurality of opening positions (openings 50 of the radial communication passage 48) that open to the valve chamber a of the radial communication passage 48 are formed in the circumferential direction of the piston valve 16 that is a valve body. . For example, as shown in FIG. 4, two radial communication passages 48 may be formed at a central angle of 180 ° in the circumferential direction of the piston valve 16, and as shown in FIG. Four radial communication paths 48 may be formed 90 ° apart from each other, and the number, position, etc. thereof can be changed as appropriate.

  With this configuration, a plurality of high-pressure fluids flowing into the valve chamber b are formed in the circumferential direction of the piston valve 16 from the valve chamber b when the piston valve 16 is opened from the valve seat 34. The air is smoothly discharged to the valve chamber a through the radial communication passage 48. Since the pressure in the valve chamber b is low, the piston valve 16 does not come into contact with the valve seat 34 to close the valve port 34a, so that the fluid can flow smoothly and without decreasing the flow rate.

  Further, on the distal end side of the side wall 52 in the vertical direction of the valve body 24 of the piston valve 16, the piston valve 16 faces the primary side port 26 of the primary side flow path 28 in a valve-opened state separated from the valve seat 34. A tapered inclined surface 54 which is a main valve portion of the piston valve 16 and whose diameter decreases toward the valve port 34a is formed.

  That is, in a valve open state in which the piston valve 16 is separated from the valve seat 34, the main valve portion of the piston valve 16 facing the primary side port 26 of the primary side flow path 28 is all this tapered inclined surface 54, and the piston The portion of the side wall 52 in the vertical direction of the valve body portion 24 of the valve 16 is formed at a position that does not face the primary side port 26 of the primary side flow path 28.

  The tapered inclined surface 54 is seated on the valve seat 34 in the valve closing position to close the valve port 34a.

  In this case, the inclination angle α of the tapered inclined surface 54 is not particularly limited, and is preferably about 60 °.

  With this configuration, for example, in a valve opening state in which the piston valve 16 that is a valve element is separated from the valve seat 34 during the heating operation, the valve chamber a The fluid on the high-pressure side flowing into the gas is smoothly guided toward the valve port 34a along the tapered inclined surface 54. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a large flow rate can be controlled.

  Further, for example, during the cooling operation, in a valve open state in which the piston valve 16 that is the valve body is separated from the valve seat 34, the valve chamber a is connected via the secondary port 30 and the valve port 34a of the secondary channel 32. The fluid on the high pressure side flowing into the gas is smoothly guided from the valve port 34 a toward the primary port 26 along the tapered inclined surface 54. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a large flow rate can be controlled.

  A ball-shaped check valve 56 is mounted in the axial communication passage 46 of the piston valve 16, and a ring-shaped check valve seat 58 mounted at the center of the bottom of the recess 40 of the piston valve 16. In addition, it is configured to act as a check valve by contacting and separating. Reference numeral 51 indicates a biasing coil spring 51 that biases the check valve 56 toward the check valve seat 58.

  The check valve seat 58 is fixed by caulking 60 the peripheral wall of the opening of the axial communication passage 46 formed at the center of the bottom of the recess 40 of the piston valve 16.

  Furthermore, an opening 62 is formed in the upper part of the cylinder chamber 14 of the valve body 12. After the piston valve 16 is mounted on the cylinder chamber 14 through the opening 62, the opening 62 is covered with a lid member. 64 is configured to be closed.

  The lid member 64 is fixed by caulking 66 the side peripheral wall 18 of the opening 62 at the top of the cylinder chamber 14.

  On the other hand, as shown in FIGS. 1 and 2, the valve body 12 is shown in the left-right direction, that is, in the axis X direction, which is a direction orthogonal to the axis Y direction in FIGS. A pilot valve chamber 70 is formed on the left side in FIG.

  A pilot valve seat 72 is formed on the lower side wall of the valve body 12, and a pilot port 74 is formed in the pilot valve seat 72. A pilot passage 76 that communicates the pilot valve chamber 70 and the secondary port 30 is also formed.

  Further, a communication passage 78 that connects the valve chamber b of the cylinder chamber 14 and the pilot valve chamber 70 is formed in the side peripheral wall 18 of the cylinder chamber 14 of the valve body 12 in the axis Y direction in FIGS. Has been.

  A cylindrical plunger case 82 is fixed to the side peripheral wall 80 of the pilot valve chamber 70. In this plunger case 82, a plunger 84 is provided that can move left and right in the direction of the axis X of the plunger case 82.

  A suction element 86 is fixed to the end of the plunger case 82 in the direction opposite to the pilot valve chamber 70, and the plunger 84 is moved in the right direction, that is, the pilot between the suction element 86 and the plunger 84. A coil spring 88 for biasing the plunger 84 in the direction of the valve seat 72 is interposed.

  In other words, the coil spring 88 is interposed between the spring mounting hole 90 formed on the plunger 84 side of the plunger 84 and the suction element 86.

  Furthermore, a spherical pilot valve 92 that is spaced apart from the pilot valve seat 72 is provided at the tip of the plunger 84.

  That is, the pilot valve 92 is attached so as to protrude from the tip 84 a of the plunger 84 toward the pilot valve seat 72 by caulking the tip 84 a of the plunger 84.

  Further, a controller 96 including an electromagnetic coil 94 is provided on the outer periphery of the plunger 84. Note that the control unit 96 is shown in a simplified manner, and although not shown, the control unit 96 includes a magnetic frame that forms a magnetic path.

  An annular sub-channel 98 is formed by a clearance between the large-diameter portion 22 formed in the upper part of the piston valve 16 and the inner peripheral wall 20 of the side peripheral wall 18 of the cylinder chamber 14.

  The on-off valve 10 of the present invention configured as described above is operated as follows.

  For example, when the on-off valve 10 is used in a refrigerant circulation circuit of an air conditioner such as an air conditioner / refrigerator, the flow direction from the primary flow path 28 to the secondary flow path 32 (arrow C in FIG. 1). When the heating operation is set to the heating operation, the plunger 84 is attracted against the biasing force of the coil spring 88 as shown in FIG. It moves in the direction of the child 86 (to the left in FIG. 1).

  As a result, as shown in FIG. 1, the pilot valve 92 attached to the tip 84a of the plunger 84 moves in a direction away from the pilot valve seat 72 formed in the valve body 12, and the pilot passage 76 is opened. Will be.

  Then, immediately after the electromagnetic coil 94 of the control unit 96 is energized, the high-pressure fluid remaining in the valve chamber b formed in the cylinder chamber 14 flows into the cylinder chamber 14 of the valve body 12 as shown by the arrow B in FIG. It flows into the pilot valve chamber 70 through a communication passage 78 formed in the side peripheral wall 18.

  Further, the high-pressure fluid that has flowed into the pilot valve chamber 70 is discharged through the secondary flow path 32 through the pilot port 74 and the pilot passage 76 formed in the pilot valve seat 72. For this reason, the valve chamber b is in a low pressure state.

  As a result, the valve chamber a has a high pressure and the valve chamber b has a low pressure. Due to this pressure difference, the piston valve 16 moves away from the valve seat 34, and the valve port 34a formed in the valve seat 34 is Opened.

  As a result, as indicated by an arrow C in FIG. 1, the primary side flow path 28 passes from the primary side port 26 to the valve chamber a, the valve port 34 a formed in the valve seat 34, and the secondary side port 30. A fluid flow reaching the secondary flow path 32 is formed.

  In the state where the electromagnetic coil 94 of the control unit 96 is energized, the valve chamber b is connected from the primary port 26 of the primary channel 28 and the valve chamber a of the cylinder chamber 14 to the inside of the side peripheral wall 18 of the cylinder chamber 14. Some high-pressure fluid flows in through the auxiliary flow path 98 between the peripheral wall 20 and is discharged through the pilot passage 76 and the secondary flow path 32. For this reason, the low pressure state of the valve chamber b is maintained, and the open state of the piston valve 16 is maintained.

Conversely, for example, during cooling operation, the electromagnetic coil 94 of the control unit 96 is not energized, and the plunger 84 is positioned away from the attractor 86 (on the right side in FIG. 1) by the biasing force of the coil spring 88. To do. As a result, the pilot valve 92 attached to the tip 84 a of the plunger 84 abuts on the pilot valve seat 72 formed in the valve body 12 and closes the pilot passage 76.

  The piston valve 16 is moved to the valve seat 34 by the action of the high-pressure fluid that flows into the valve chamber a through the valve port 34a formed in the secondary port 30 and the valve seat 34 from the secondary flow path 32 that is the high pressure side. Move away from the direction. As a result, the valve port 34a formed in the valve seat 34 is opened and discharged from the primary side port 26 to the primary side flow path 28 as indicated by the arrow D in FIG.

  At this time, if the pressure of the high-pressure fluid flowing into the secondary-side port 30 from the secondary-side flow path 32 that is the high-pressure side is greater than the biasing force of the coil spring 88 of the plunger 84, the plunger 84 is attached to the coil spring 88. It moves in the direction of the suction element 86 (to the left in FIG. 1) against the force.

  Accordingly, as indicated by an arrow F in FIG. 2, the pilot valve 92 attached to the tip 84 a of the plunger 84 moves in a direction away from the pilot valve seat 72 formed in the valve body 12, and the pilot passage 76. Will be released.

  As a result, the high-pressure fluid flowing from the secondary side flow path 32 into the pilot passage 76 flows into the pilot valve chamber 70 as shown by the arrow G in FIG. 2, and the side peripheral wall of the cylinder chamber 14 of the valve body 12. 18 flows into the valve chamber b through the communication passage 78 formed in the valve 18.

  However, the high-pressure fluid that has flowed into the valve chamber b is formed in the valve body 24 of the piston valve 16 with the check valve 56 being separated from the check valve seat 58 as indicated by arrow E in FIG. From the axial direction communication path 46, it returns to the valve chamber a through the radial direction communication path 48 and is discharged from the primary side port 26 to the primary side flow path 28.

  In this case, the opening 50 of the radial communication passage 48 opens to the vertical side wall 52 of the valve body 24 of the piston valve 16, and the primary valve is opened in a state where the piston valve 16 is separated from the valve seat 34. The side passage 28 is provided in the valve opening direction with respect to the primary port 26.

At this time, when the piston valve 16 is open from the valve seat 34, the negative pressure of the high-pressure fluid flowing into the valve chamber a through the secondary port 30 and the valve port 34a of the secondary flow path 32 is obtained. 2, the high-pressure fluid flowing into the valve chamber b passes through the valve chamber communication passage 44 (the axial communication passage 46, the radial communication passage 48) through the valve chamber b. It becomes easy to be smoothly discharged into the chamber a.

  As a result, the main valve 14 is moved in the direction of the valve seat 34 due to the pressure of the high-pressure fluid flowing into the valve chamber b, and the valve port 34a is effectively prevented from being closed by the piston valve 16. ing.

As a result , as indicated by an arrow D in FIG. 2, the primary side flow path 28 passes from the secondary side port 30 of the secondary side flow path 32 through the valve chamber a and the valve port 34 a formed in the valve seat 34. A fluid flow to the primary side port 26 is formed.

As indicated by an arrow D in FIG. 2, when the secondary flow path 32 is at a high pressure and flows from the secondary flow path 32 to the primary flow path 28 on the low pressure side , the piston valve 16 When the pressure difference that moves the valve in the direction away from the valve seat 34 is generated, the opening / closing control of the piston valve 16 by the electromagnetic coil 94 of the control unit 96 cannot be performed, and the valve open state is maintained.

  In this case, as shown in FIG. 6, the required lift amount e of the piston valve 16 may be determined as follows when the piston valve 16, which is a valve body, is opened from the valve seat 34.

That is, as shown in FIGS. 6A and 6B, the opening area includes the radius r of the bottom surface 55 of the piston valve 16, the radius R of the valve port 34a of the valve seat 34, and the bottom surface 55 of the piston valve 16. The side area of the cone is the side length L of the cone formed with the valve seat 34.
In the following formula, D represents the diameter of the secondary port 30.

Therefore, the conical side area A1 = π · L (r + R).
On the other hand, the relationship between the valve lift e of the piston valve 16 and the opening area A1 is determined as follows.

When the relationship between the valve lift e of the piston valve 16 and the side length L of the cone is L = f (e), the relationship of the opening area A1 with respect to the valve lift e is as follows.
A1 = π · (r + R) × f (e)

Further, the valve lift e required by the piston valve 16 desirably has an opening area A1 larger than the aperture area of the valve port 34a.
In this case, the diameter area A2 = πD ^2/4

Therefore,
A1> A2
Therefore, π · (r + R) × f (e)> πD 2/4

Therefore, f (e)> (πD 2/4) / (π × (r + R))
Therefore, the valve lift e of the piston valve 16 that satisfies this relational expression is required.

The on-off valve 10 of the present invention configured as described above has a structure in which the piston valve 16 is removed from the conventional pilot-type electromagnetic valve 100 shown in FIG. 11 and the on-off valve 10 of the present invention shown in FIG. The same constituent members as those in the embodiment of FIGS. 1 to 3 are given the same reference numerals, and the flow rate is improved by 10%.
The flow rate of the comparative example and the flow rate of the conventional pilot type solenoid valve 100 are substantially the same.
(Example 2)

  FIG. 8 is a longitudinal sectional view showing only the piston valve 16 showing another embodiment of the on-off valve 10 of the present invention.

  The on-off valve 10 of this embodiment has basically the same configuration as that of the on-off valve 10 of the first embodiment shown in FIGS. 1 to 5, and the same reference numerals are given to the same components. Detailed description thereof will be omitted.

  In the on-off valve 10 of this embodiment, when the piston valve 16 that is the valve body is in the open state separated from the valve seat 34, the opening position that opens to the valve chamber a of the radial communication passage 48 (the opening of the radial communication passage 48). Part 50) is provided on the tapered inclined surface 54.

  That is, as shown in FIG. 8, the radial communication path 48 is formed to be inclined downward and configured to open to the tapered inclined surface 54.

  With this configuration, in the open state in which the piston valve 16 is spaced from the valve seat 34, the opening position (the opening 50 of the radial communication path 48) that opens to the valve chamber a of the radial communication path 48 is Since it is provided on the tapered inclined surface 54, the high-pressure fluid from the primary port 26 of the primary side flow path 28 is guided along the tapered inclined surface 54 and guided toward the valve port 34a. The amount flowing into the valve body communication passage 44 (the axial communication passage 46 and the radial communication passage 48) is reduced.

As a result, in the open state where the piston valve 16 is separated from the valve seat 34, the high-pressure fluid that has flowed into the valve chamber b passes from the valve chamber b to the valve body communication passage 44 (the axial communication passage 46, the radial communication passage 48). ) Is smoothly discharged to the valve chamber a, so that the pressure in the valve chamber b is low, so that the piston valve 16 does not abut against the valve seat 34 and closes the valve port 34a. Can flow smoothly and without a decrease in flow rate.
(Example 3)

  FIG. 9 is an external side view showing only the piston valve 16 similar to FIG. 8 showing another embodiment of the on-off valve 10 of the present invention.

  The on-off valve 10 of this embodiment has basically the same configuration as that of the on-off valve 10 of the first embodiment shown in FIGS. 1 to 5, and the same reference numerals are given to the same components. Detailed description thereof will be omitted.

  In the on-off valve 10 of this embodiment, the tapered inclined surface 54 is formed of a plurality of tapered inclined surfaces having different inclination angles α.

  That is, in the on-off valve 10 of this embodiment, the taper inclined surface of the plurality of stages is such that the taper inclined surface 54a on the proximal end side of the valve body 24 of the piston valve 16 is inclined more than the taper inclined surface 54b on the distal end side. α (α1> α2) is formed large. In addition, in this Example, it comprised from the two taper inclined surfaces 54a and the taper inclined surface 54b, However, The number will not be specifically limited if it is plurality.

  With this configuration, when the piston valve 16 is open from the valve seat 34, the high-pressure fluid flowing into the valve chamber a via the primary port 26 of the primary flow path 28 is The taper inclined surface 54a on the proximal end side of the sixteen valve body portions 24 is formed along a plurality of tapered inclined surfaces (54a, 54b) having a larger inclination angle α than the tapered inclined surface 54b on the distal end side. It is guided more smoothly toward the valve port 34a. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

Further, when the piston valve 16 is opened from the valve seat 34, the high-pressure side fluid flowing into the valve chamber a through the secondary port 30 and the valve port 34a of the secondary flow path 32 is replaced with the piston valve. The taper inclined surface 54a on the proximal end side of the sixteen valve body portions 24 is formed along a plurality of tapered inclined surfaces (54a, 54b) having a larger inclination angle α than the tapered inclined surface 54b on the distal end side. Smooth guidance is provided from the valve port 34a toward the primary port 26. It is difficult to generate turbulent flow, it is possible to reduce pressure loss and control a larger flow rate.
Example 4

  FIG. 10 is an external side view showing only the piston valve 16 similar to FIG. 8 showing another embodiment of the on-off valve 10 of the present invention.

  The on-off valve 10 of this embodiment has basically the same configuration as that of the on-off valve 10 of the first embodiment shown in FIGS. 1 to 5, and the same reference numerals are given to the same components. Detailed description thereof will be omitted.

  In the on-off valve 10 of this embodiment, the tapered inclined surface 54 is formed of a plurality of tapered inclined surfaces having different inclination angles α.

  That is, in the on-off valve 10 of this embodiment, the taper inclined surface of the plurality of stages is such that the taper inclined surface 54a on the proximal end side of the valve body 24 of the piston valve 16 is inclined more than the taper inclined surface 54b on the distal end side. α (α1 <α2) is formed small. In addition, in this Example, it comprised from the two taper inclined surfaces 54a and the taper inclined surface 54b, However, The number will not be specifically limited if it is plurality.

  With this configuration, when the piston valve 16 is open from the valve seat 34, the high-pressure fluid flowing into the valve chamber a via the primary port 26 of the primary flow path 28 is The taper inclined surface 54a on the proximal end side of the sixteen valve bodies 24 is formed with a smaller inclination angle α than the tapered inclined surface 54b on the distal end side, and along the plurality of tapered inclined surfaces (54a, 54b), It is guided more smoothly toward the port 34a. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  Further, when the piston valve 16 is opened from the valve seat 34, the high-pressure side fluid flowing into the valve chamber a through the secondary port 30 and the valve port 34a of the secondary flow path 32 is replaced with the piston valve. The taper inclined surface 54a on the proximal end side of the sixteen valve bodies 24 is formed with a smaller inclination angle α than the tapered inclined surface 54b on the distal end side, and along the plurality of tapered inclined surfaces (54a, 54b), It is smoothly guided from the port 34a toward the primary port 26. Therefore, turbulent flow hardly occurs, pressure loss can be reduced, and a larger flow rate can be controlled.

  The preferred embodiment of the present invention has been described above. However, the present invention is not limited to this. For example, the cylinder chamber 14 is formed in the direction of the axis Y of the above embodiment, and the axis is in the cylinder chamber 14. The present invention can be applied to an on-off valve having a configuration in which a piston valve 16 that can slide in the Y direction is mounted and a pilot valve chamber 70 is formed in the axis Y direction.

  Further, in the above embodiment, the ball-shaped check valve 56 is mounted in the axial communication passage 46 of the piston valve 16, but the check valve 56 may be omitted.

  Further, the present invention can be applied to an open / close valve in which a throttle channel (groove) is formed in a valve closed state in addition to a valve whose flow rate is completely shut off in the valve closed state.

  Furthermore, the on-off valve of the present invention shows an embodiment applied to a pilot-type electromagnetic valve provided with a pilot valve in the above-mentioned embodiment, but although not shown, it is also applied to a so-called “direct-acting on-off valve”. It is possible to apply.

  That is, the cylinder chamber 14 is composed of a plunger case 82, the piston valve 16 is composed of a plunger 84, and the valve body 24 is also applied to a direct acting on-off valve composed of a needle valve provided at the tip of the plunger 84. Various modifications are possible without departing from the object of the present invention.

  The present invention can be applied to, for example, an open / close valve for opening and closing a flow path used in a refrigerant circulation circuit of an air conditioner such as an air conditioner or a refrigerator.

DESCRIPTION OF SYMBOLS 10 On-off valve 11 Sliding ring 12 Valve body 14 Cylinder chamber 16 Piston valve 18 Side peripheral wall 20 Inner peripheral wall 22 Large diameter part 24 Valve body part 26 Primary side port 28 Primary side flow path 30 Secondary side port 32 Secondary side flow path 34 Valve seat 34a Valve port 40 Recess 42 Step part 44 Valve body communication path 46 Axial communication path 48 Radial direction communication path 50 Opening 51 Energizing coil spring 52 Side wall 54 Tapered inclined surface 54a Tapered inclined surface 54b Tapered inclined surface 55 Bottom surface 56 Check valve 58 Check valve seat 60 Crimping 62 Opening 64 Lid member 66 Caulking 70 Pilot valve chamber 72 Pilot valve seat 74 Pilot port 76 Pilot passage 78 Communication passage 80 Side peripheral wall 82 Plunger case 84 Plunger 84a Tip 86 Suction element 88 Coil spring 90 Spring mounting hole 92 Pilot valve 94 Electromagnetic coil 96 Control unit 8 Sub flow path 100 Solenoid valve 102 Valve body 104 Cylinder chamber 106 Piston valve 108 Side peripheral wall 110 Inner peripheral wall 112 Large diameter section 114 Valve body section 116 Primary side port 118 Primary side flow path 120 Secondary side port 122 Secondary side flow path 124 Valve seat 124a Valve port 130 Recess 132 Step part 134 Valve body communication path 136 Axial direction communication path 138 Radial direction communication path 140 Opening part 141 Energizing coil spring 142 Side wall 144 Tapered inclined surface 145 Bottom surface 146 Check valve 148 Check valve seat 150 Caulking 152 Opening 154 Lid member 156 Caulking 158 Spring 160 Pilot valve chamber 162 Pilot valve seat 164 Pilot port 166 Pilot passage 168 Side passage 170 Side peripheral wall 172 Plunger case 174 Plunger 174a Tip 176 Suction element 178 Coil spring 80 spring attachment hole 182 pilot valve 184 solenoid coil 186 controller 188 sub-passage
a, b Valve chamber

Claims (6)

An on-off valve configured to move in a direction away from a valve seat formed in a valve body, and to open a valve port provided in the valve seat;
When the piston valve is open from the valve seat, the main valve portion of the piston valve facing the primary port of the primary flow path is configured with a tapered inclined surface whose diameter decreases toward the valve port. and,
The valve body is formed with a valve chamber a formed on the valve seat side in the piston valve and a valve chamber b formed on the opposite side to the valve seat side in the piston valve,
The piston valve is formed with a valve body communication passage that communicates the valve chamber b and the valve chamber a.
The valve body communication path includes a radial communication path including an opening that extends radially outward of the valve body portion of the piston valve and communicates with the valve chamber a.
In the open state in which the piston valve is separated from the valve seat, the opening of the radial communication path communicating with the valve chamber a is in the valve opening direction with respect to the primary side port of the primary side flow path, and the primary side An on-off valve characterized by being provided at a position not facing the port . 2. The on-off valve according to claim 1 , wherein a plurality of openings of the valve body communication passage communicating with the valve chamber a are formed in a circumferential direction of the piston valve. The on-off valve according to claim 1 , wherein the tapered inclined surface is formed of a plurality of tapered inclined surfaces having different inclination angles α. Claims the tapered inclined surface of the plurality of stages, a tapered inclined surface of the proximal end side of the main valve portion of the piston valve, characterized in that the inclination angle α than the taper inclined surface of the front end side is larger Item 5. The on-off valve according to Item 3 . Claims the tapered inclined surface of the plurality of stages, a tapered inclined surface of the proximal end side of the main valve portion of the piston valve, characterized in that the inclination angle α than the taper inclined surface of the distal end side is formed smaller Item 5. The on-off valve according to Item 3 . Wherein the piston valve, characterized in that the main valve part for opening and closing a valve port formed in said valve seat, a pilot on-off valve and a pilot valve for opening and closing a pilot passage communicating with the flow path Item 6. The on-off valve according to any one of Items 1 to 5 .

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