JP2005076576A - Marine spool valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a marine spool that can be easily processed.
SOLUTION: A spool port 10 formed in a valve body 2 has a pump port 18 connected to a pump, a fuel supply actuator port 14, an exhaust actuator port 22, and a tank port 25a communicating with the tank. 25b communicate with each other. The pilot portion 28 presses the spool 26 inserted through the spool hole 10 from one end side thereof. The urging means comprising the piston hole 68 and the piston 70 presses the spool 26 from the other end side. By controlling the position of the spool 26 by the pilot unit 28 provided with the electromagnetic drive unit 66, the pressure oil between the pump port 22 and the tank ports 25a and 25b, the fuel supply actuator port 18 and the exhaust actuator port 22 is obtained. The supply and discharge of is controlled.
[Selection] Figure 1

Description

  The present invention relates to a marine spool valve that controls a fluid device used in a marine vessel, for example.

  The marine spool valve as described above may be used, for example, to control a fuel supply pump to the marine internal combustion engine or to control an exhaust valve of the marine internal combustion engine. An example of such a marine spool valve is disclosed in Patent Document 1.

  In the spool valve disclosed in Patent Document 1, a spool hole is formed in the valve body. The spool hole is provided with an actuator port for supplying and discharging the pressure fluid into the chamber of the pressure fluid cylinder. A pump port connected to the fluid pressure source and a tank port connected to the tank are also provided. A spool is inserted into the spool hole. The spool is switched between a state in which the actuator port is connected to the pump port and a state in which the spool is connected to the tank port. A pilot portion is provided inside one end of the spool. In this pilot portion, a piston is fixed in a pressure chamber formed along the axial direction inside one end of the spool. The pressure fluid is supplied to and discharged from the pressure chamber by a pilot spool formed inside one end of the spool. The pilot spool is moved along the length of the spool by the positioning means to supply pressure fluid into the pressure chamber or to discharge pressure fluid from the hole. The other end of the spool is provided with an urging means that presses the spool toward the other end with the pressure fluid.

  In this spool valve, for example, when the pilot spool is moved to the other end side of the spool, the pressure fluid is supplied into the pressure chamber, the pressure in the pressure chamber is increased, and the spool moves to the other end side. The spool stops in a state balanced with the pressing force from the biasing means. Similarly, when the pilot spool is moved to one end side of the spool, the pressure fluid is discharged from the pressure chamber, the pressure in the pressure chamber is lowered, the spool moves to one end side, and the pressure from the urging means is reduced. The spool stops in balance with the pressing force.

Japanese National Patent Publication No. 8-511107

  In the spool valve configured as described above, it is necessary to form a pressure chamber or a pilot spool inside one end portion of the spool, which is troublesome to manufacture.

  An object of the present invention is to provide a marine spool valve that is easy to manufacture.

  The marine spool valve according to the present invention has a first spool hole formed in the valve body. A pump port communicating with the first spool hole is connected to a pressure source. A fuel port communicating with the first spool hole is connected to a fuel supply actuator. An exhaust port communicating with the first spool hole is connected to an actuator of the exhaust valve. A tank port that communicates with the first spool hole communicates with the tank. Each of these ports can be formed in a valve body, such as a tubular section. A spool is inserted through the first spool hole. For example, the spool is preferably slidable along a line connecting the openings of the tubular portion. The pump port, tank port, fuel port and exhaust port are preferably arranged along the sliding direction of the spool. The pilot portion presses the spool from one end side thereof. The urging means presses the spool from the other end side thereof. By controlling the spool to a desired position by the pilot unit, for example, by moving forward and backward, supply of the pressure fluid from the pump port to the fuel or exhaust valve port or from the fuel or exhaust valve port to the tank port The discharge of the pressure fluid is controlled. In the pilot portion, the first piston hole is formed in the valve body, not in the spool, and the first piston is slidably inserted into the first piston hole. For example, the first piston hole is preferably formed in the cover of the valve main body on one end side of the spool in parallel with the sliding direction (axial direction) of the spool. The first piston is preferably slidable along the length direction of the first piston hole, and is preferably in contact with one end of the spool. It is desirable to provide a plurality of these first piston holes and first pistons. This pilot spool is also preferably installed on the valve body, for example, a cover on one end side of the spool, and is preferably slidable in the axial direction of the spool. A first pressure chamber is defined by the first piston and the valve body. A pilot spool for supplying and discharging the pressure fluid from the pressure source is provided in the first pressure chamber. An electromagnetic drive unit for moving the pilot spool is provided. This electromagnetic drive unit can be provided separately from the valve body. A spool return means that opposes the thrust of the electromagnetic drive unit and a detection means that detects the spool position are provided. As the spool return means, for example, an elastic body can be used, and it is desirable that this elastic body can be expanded and contracted along the sliding direction of the spool. The electromagnetic drive unit is controlled based on the signal of the detection means and the control signal. A fuel supply position for supplying the pressure fluid from the pump port to the fuel port by controlling the spool to a desired position by the pilot unit, and the pressure from the fuel port to the tank port A fuel discharge position for discharging the fluid, an exhaust supply position for supplying the pressure fluid from the exhaust port to the tank port, and an exhaust for discharging the pressure fluid from the exhaust port to the tank port The spool position is switched to the discharge position.

  In this marine spool valve, when the pilot spool is moved by the electromagnetic drive unit, the pressure fluid is supplied to and discharged from the first pressure chamber of the pilot unit, and accordingly, the first piston of the pilot unit advances and retreats. The spool is moved to a position where the pressure in the first pressure chamber and the pressing force of the urging means are balanced, and the pressure fluid is supplied to and discharged from the fuel port or the exhaust port. At this time, the spool return means can transmit the movement of the spool to the pilot spool by pressure. By balancing the thrust of the electromagnetic drive unit and the pressure for pushing the spool by the spool return means, Since the supply and discharge of the pressure fluid are controlled, highly accurate control can be performed. In this marine spool valve, the pilot portion is formed not in the spool but in the valve main body separately from the spool. Therefore, the processing can be performed more easily than forming the pilot portion in the spool. Further, the moving range of the electromagnetic drive unit is smaller than the moving range of the spool. Due to this, an electromagnetic drive unit having a small movement range can be used. Furthermore, the processing can be easily performed by reducing the pilot portion.

  A sleeve can be arranged closer to the center side of the valve body than the first piston. The sleeve is preferably provided on the cover of the valve body, and its length direction is preferably parallel to the sliding direction of the spool. A first passage communicating with the first pressure chamber, a second passage communicating with the pressure source, and a third passage communicating with the tank are formed in the sleeve. The pilot spool is slidably inserted into the sleeve. The pilot spool is driven by the electromagnetic drive unit. The pilot spool blocks the first passage from communicating with the second passage or the third passage, thereby controlling supply and discharge of the pressure fluid to and from the first pressure chamber.

  If comprised in this way, the sleeve in which the pilot spool is penetrated will be arrange | positioned close to the 1st pressure chamber. Therefore, the distance between the pilot spool and the first pressure chamber can be shortened, and the spool moves without greatly delaying the movement of the pilot spool valve, and the response delay of the pressure fluid can be reduced. Further, since the sleeve can be formed separately from the valve body and installed on the valve body, the spool valve can be easily manufactured.

  The biasing means may have a second spool hole formed in the spool from the other end of the spool. The second spool hole is preferably formed along the sliding direction of the spool. A second piston is slidably inserted into the second spool hole and is in contact with the valve body. A second pressure chamber is defined in the spool by the second piston. A fourth passage communicates the second pressure chamber and the pressure source.

  If comprised in this way, the urging | biasing means will generate | occur | produce the pressing force with respect to a spool with the pressure of a pressure fluid. Therefore, for example, compared with the case where the pressing force is generated by a spring or the like, a large pressing force can be generated in the same space, so that the spool can be moved at a relatively high speed.

  A feedback spring can be arranged as a spool return means between the spool and the pilot spool. With this configuration, the movement of the spool can be transmitted to the pilot spool with pressure by the feedback spring. By balancing the thrust of the electromagnetic drive unit and the pressure with which the spool is pressed by the feedback spring, the pressure chamber is transferred to the pressure chamber. Since the pressure fluid supply and discharge are controlled, highly accurate control can be performed. In addition, since an electromagnetic drive unit having a small moving range can be used, a proportional solenoid can be used as the electromagnetic drive unit. This makes it possible to use an oil-immersed type in which oil enters the solenoid part, eliminates the need to provide a seal that contacts the plunger of the electromagnetic drive unit, reduces sliding resistance and hysteresis, and increases speed. Can be driven.

  Furthermore, the spring force of the feedback spring can be selected to be greater than the flow force between the pilot spool and the sleeve (thrust due to the flow of pressure fluid). With this configuration, since the pilot spool is always pressed against the electromagnetic drive unit by the spring force of the feedback spring, there is no need to connect the pilot spool and the output shaft of the electromagnetic drive unit, and the pilot spool is attached to the output shaft. The coupling between the output shaft and the pilot spool can be omitted, and manufacturing is facilitated.

  Further, the first passage can be formed by a notch and a square hole. If comprised in this way, the processing distance which is a distance which needs to process the square hole which processing is complicated can be shortened, and processing will become easy.

  Further, as the detecting means, a stroke sensor can be provided on the spool. In this case, the electromagnetic drive unit is controlled based on a signal from the stroke sensor, for example, a stroke signal indicating the spool stroke, and a control signal, for example, a stroke stroke instruction signal indicating the spool stroke by the electromagnetic drive unit. If comprised in this way, an electromagnetic drive part can be controlled so that the stroke of an actual spool may become the stroke instruct | indicated by the stroke instruction | indication signal, and the stroke of a spool can be controlled with high precision.

  As described above, according to the present invention, since the pilot portion is not incorporated in the spool but is provided in the valve body that is separate from the spool, the manufacture thereof is facilitated.

  The marine spool valve according to the first embodiment of the present invention includes, for example, an actuator that supplies fuel to an internal combustion engine of a marine vessel, such as a pump (not shown), and an actuator that exhausts air from the internal combustion engine of the marine vessel, such as an exhaust valve. It is for driving, and has a valve body 2 as shown in FIG. The valve body 2 has a tubular portion 4. The tubular portion 4 is open at both ends, and both ends are closed by covers 6 and 8, respectively.

  A spool hole 10 is formed in the tubular portion 4 along the length direction thereof, for example, on the axis of the tubular portion 4 along the length direction thereof. The spool hole 10 is formed in a circular hole, for example. An annular groove 12 whose diameter is increased outward is formed at a position slightly closer to the cover 8 side than the center in the length direction of the spool hole 10. The annular groove 12 is connected to a fuel supply pump via a fuel supply actuator port 14 formed in the tubular portion 4. An annular groove 16 is formed at a position somewhat away from the annular groove 12 on the cover 6 side. The annular groove 16 is connected to a pressure source, for example, a pressure oil pump, through a pump port 18 formed in the tubular portion 4. An annular groove 20 is formed at a position somewhat away from the annular groove 16 on the cover 8 side. The annular groove 20 is connected to an exhaust actuator via an exhaust actuator port 22 formed in the tubular portion 4. That is, the annular grooves 12 and 20 are formed on both sides of the annular groove 16. Annular grooves 24a and 24b are formed at positions closer to the cover 6 from the annular groove 20 and at positions closer to the cover 8 than the annular groove 12, respectively. These annular grooves 24 a and 24 b are connected to a tank (not shown) via tank ports 25 a and 25 b formed in the tubular portion 4. Although two tank ports 25a and 25b are provided, it is also possible to form a fluid path connecting the annular grooves 24a and 24b in the tubular portion 4 and form only one of the tank ports 25a and 25b.

  A spool 26 is inserted into the spool hole 10. The spool 26 is arranged so that its axis coincides with the axis of the spool hole 10 and is slidable along the axial direction of the spool hole 10. Valve bodies 26a, 26b, and 26c are formed at both ends and the center of the spool 26 at intervals along the length direction of the spool 26. These valve bodies 26a, 26b, and 26c are formed in enormous portions that are enlarged so that the diameters thereof substantially coincide with the diameters of the spool holes 10 so that the annular grooves 12, 16, 20, 24a, and 24b can be closed. The diameter of the part between these valve bodies 26 a, 26 b, 26 c is made smaller than the diameter of the spool hole 10.

  In FIG. 1, the valve body 26 a communicates the annular groove 24 b and the annular groove 12, and the valve body 26 b closes the annular groove 12 and the annular groove 16. A state in which the body 26c closes the annular groove 24a is shown. In this state, pressure fluid, for example, pressure oil, is discharged from the fuel supply pump to the tank, but pressure oil is supplied to the exhaust valve. By changing the position of the spool 26 along the length direction of the spool 26 and changing the opening state of the annular groove 16, the amount of pressure oil supplied to the exhaust valve can be adjusted. The amount of pressure oil discharged from the fuel supply pump can be adjusted by changing the opening state of the groove 24b.

  FIG. 2 shows a state where the spool 26 has moved to the cover 6 side from the state of FIG. In this state, the annular groove 16 is completely closed by the valve body 26b, and the supply of pressure oil to the annular grooves 12 and 20 is stopped. Accordingly, the pressure oil is not supplied to the fuel supply pump and the exhaust valve. Furthermore, although the opening state is narrower than that in FIG. 1, the valve body 26a communicates the annular groove 12 and the annular groove 24b, and the discharge of the pressure oil from the fuel supply pump to the tank is continued. Yes. Further, the valve body 26c releases the blockage of the annular groove 24b and allows the annular groove 20 and the annular groove 24a to communicate with each other. Therefore, the pressure oil is discharged from the exhaust valve to the tank.

  FIG. 3 shows a state in which the spool 26 is further slid toward the cover 6 from the state shown in FIG. In this state, the annular groove 24b is completely closed by the valve body 26a. Accordingly, the discharge of the pressure oil from the fuel supply pump is stopped. Further, the closing by the annular groove 16 by the valve body 26b is continued. Accordingly, the pressure oil is not supplied to the fuel supply pump and the exhaust valve. Moreover, since the opening degree of the annular groove 24a is wider than the state shown in FIG. 2, the discharge amount of the pressure oil from the exhaust valve is larger than the state shown in FIG. In this state, by changing the position of the spool 26, the opening state of the tank port 24a can be changed, and the amount of pressure oil discharged from the exhaust valve to the tank can be adjusted.

  FIG. 4 shows a state where the spool 26 is further moved to the cover 6 side. In this state, the valve body 26a completely closes the annular groove 24b, and the valve body 26b allows the annular grooves 12 and 16 to communicate with each other. Accordingly, the pressure oil is supplied to the fuel supply actuator. At this time, the valve body 26b makes the annular groove 16 and the annular groove 20 in a non-communication state, and the valve body 26c communicates the annular grooves 20 and 24a. The opening degree of the annular groove 24a at this time is larger than that in FIG. Therefore, more pressure oil is discharged from the exhaust valve to the tank than in the state of FIG.

  A pilot portion 28 is formed on the cover 6 which is a part of the valve body 2. As shown in an enlarged view in FIG. 5, the pilot portion 28 has first piston holes 30, 30 formed in the cover 6. These piston holes 30, 30 are formed at positions equidistant from this axis with the axis of the spool hole 10 in between. These piston holes 30, 30 are formed in parallel to the axis of the spool 26, and the side of the spool 26 facing the valve body 26c is opened. The first pistons 32 and 32 are slidably disposed in the piston holes 30 and 30 along the length direction of the piston holes 30 and 30. The tip portions of the pistons 32, 32 protrude from the opening of the piston holes 30, 30 to the spool 26 side and abut on the end face of the valve body 26 c of the spool 26.

  The insides of these pistons 32 and 32 are formed hollow from the inner back side of the piston hole 30 toward the front end side. An elastic body, for example, coil springs 34, 34 are provided between the tip of these hollow portions and the inner back portion of the piston hole 30, and the contact state of the pistons 32, 32 with the spool 26 is maintained. As the pistons 32 and 32 move back and forth, the volume of the first pressure chamber formed by the hollow interior of the pistons 32 and 32 and the piston hole 30 changes.

  A sleeve 36 is provided inside the pistons 32, 32, for example, on the axis of the spool hole 10. The sleeve 36 is arranged so that both ends thereof are opened and the center axis thereof coincides with the axis of the spool hole 10. A first passage 37 is formed substantially in the center of the sleeve 36 in the axial direction. As shown in FIG. 6, the first passage 37 includes a square hole 38 formed outward from the inner peripheral surface of the sleeve 36 by a short distance, a notch 40 communicating with the square hole 38, It consists of an annular groove 42 formed on the outer peripheral surface of the sleeve 36 outside the notch 40. The first passage 37 communicates with the piston holes 30 and 30 through a passage 44 formed in the cover 6.

  A second passage 46 is formed at a position closer to the spool hole 10 than the first passage 37. The second passage 46 includes a square hole 48 that extends outward from the inner peripheral surface of the sleeve 36 and an annular groove 50 that is formed on the outer peripheral surface of the sleeve 36. Although not illustrated, the annular groove 50 is connected to the annular groove 16 connected to the pump via a passage formed in the cover 6 and the tubular portion 4. A third passage 52 is formed on the opposite side of the first passage 37 from the second passage 46. The third passage 52 includes a square hole 54 that extends outward from the inner peripheral surface of the sleeve 36, and an annular groove 56 that is formed in the entire outer peripheral surface of the sleeve 36. Although not shown, the annular groove 56 is connected to the annular groove 24a connected to the tank via a passage formed in the cover 6 and the tubular portion 4.

  A pilot spool 58 is provided in the inner hole of the sleeve 36 so that the center axis thereof coincides with the axis of the spool hole 10. The pilot spool 58 has a valve body 58a at the center thereof. As the pilot spool 58 advances and retreats along the axial direction, the valve body 58a also moves. When the valve body 58a closes the first passage 37, the first pressure chamber composed of the piston 32 and the piston hole 30 is completely cut off from the tank and the pump.

  When the pilot spool 58 moves to the side opposite to the spool hole 10, that is, to the cover 6 side, the valve body 58a also moves to the side opposite to the spool hole 10, and the first passage 37 and the second passage 46 is connected, and pressure oil is supplied into the piston hole 30 which is a part of the first pressure chamber. As a result, the pistons 32 move to the spool hole 10 side, that is, the cover 8 side.

  When the pilot spool 58 moves to the spool hole 10 side, that is, to the cover 8 side, the valve body 58a also moves to the cover 8 side, and the first passage 37 and the third passage 52 are connected, The pressure oil in the piston hole 30 is discharged to the tank. Accordingly, the pistons 32 and 32 move to the cover 6 side.

  According to the movement amount of the pilot spool 58, the supply state of the pressure oil into the first pressure chamber composed of the piston hole 30 and the piston 32 and the discharge state of the pressure oil change.

  A recess 60 is formed at the end of the valve body 26a of the spool 26, and there is a return means between the inner back of the recess 60 and the end of the pilot spool 58 on the spool hole 10 side. For example, a feedback spring 62 is disposed. The feedback spring 62 can be expanded and contracted. When the spool 26 moves to the cover 8 side, the feedback spring 62 expands and moves the pilot spool 58 to the cover 8 side. When the spool 26 moves to the cover 6 side, the feedback spring 62 contracts and moves the pilot spool 58 to the cover 6 side. The feedback spring 62 is constituted by, for example, a coil spring, and the spring force is set to be larger than the flow force between the pilot spool 58 and the sleeve 36.

  The end of the pilot spool 58 opposite to the spool hole 10 is coupled to an electromagnetic drive, for example, a plunger 66a of a proportional solenoid 66, via a coupling 64, as shown in FIGS. The proportional solenoid 66 can arbitrarily control the position of the plunger 66a in proportion to the magnitude of the current supplied thereto. Accordingly, the position of the pilot spool 58 can be arbitrarily controlled as the proportional solenoid 66 is driven.

  On the other end of the spool 26, that is, on the valve body 26a side, an urging means is provided. This biasing means has a plurality of, for example, two second spool holes 68. The second spool hole 68 is formed on both sides of the axis of the spool 26 so as to be symmetrical with respect to the axis of the spool 26 and parallel to the axis of the spool 26. The ends of the spool holes 68 on the cover 8 side are opened, and the inner and inner ends of the spool holes 68 are formed in the annular groove 16 connected to the pump port 18 via a fourth passage 70 formed in the spool 26. Are combined. The formation position of the fourth passage 70 is selected so that pressure oil can be supplied to the second spool hole 68 no matter where the spool 26 moves.

  The second pistons 72 and 72 are inserted into the spool holes 68, respectively. One end of these pistons 72, 72 is in contact with the cover 8. The pistons 72 and 72 are formed so as not to move, and a second pressure chamber is formed between the inner back end portion of the piston 72 and the inner back end portion of the spool hole 68. Since the pistons 72 and 72 are immovable and pressure oil is supplied from the fourth passage 70, the spool 26 is always pressed toward the cover 6 by the reaction force of the pressure oil.

  In the center of the cover 8, position detecting means, for example, a stroke sensor 74 is provided to detect the stroke of the spool 26. A stroke signal representing the detected stroke is supplied to control means of a proportional solenoid 66 (not shown). A stroke instruction signal representing a value for moving the spool 26 is input to the control means in advance, and the proportional solenoid 66 is controlled so that the stroke signal matches the stroke instruction signal.

  In the marine spool valve configured as described above, for example, as shown in FIG. 3, the valve bodies 26 a and 26 b of the spool 26 close the annular grooves 16 and 24 b, whereby the fuel supply actuator port 14 is connected to the pump port 18. And the valve body 26c is blocked from a part of the annular groove 24a connected to the tank port 25a, the exhaust actuator port 22 is communicated with the tank port 25a, and the valve body of the pilot spool 58 is disconnected. It is assumed that 58a is closing the first passage 37. At this time, it is assumed that a predetermined amount of pressurized oil exists in the piston hole 30. This state is referred to as a neutral state.

  In this neutral state, it is assumed that the plunger 66a of the proportional solenoid 66 is moved to the cover 8 side by a predetermined amount by the control means. At this time, the valve body 58a of the pilot spool 58 is also moved to the cover 8 side by a predetermined amount, and the first passage 37 and the third passage 52 are connected while maintaining a predetermined opening degree. Pressure oil is discharged from 30 to the tank. Along with this, the piston 32 moves backward toward the proportional solenoid 66 by an amount corresponding to the opening degree, the pressing force against the spool 26 decreases, and the spool 26 moves toward the proportional solenoid 66 side. At this time, the feedback spring 62 is compressed. Although the pressure oil is supplied to the piston 72 via the fourth passage 70, the volume of the second pressure chamber increases due to the movement of the spool 26 toward the cover 6, and the reaction force based on the pressure oil is Get smaller. The spool 26 stops at a position where the reaction force and the pressing force of the piston 32 are balanced.

  At this time, as shown in FIG. 4, the annular groove 16 connected to the pump port 18 and the annular groove 12 connected to the fuel supply actuator port 14 communicate with each other with a predetermined opening degree. Pressure oil is supplied from the pump port 18. Further, at this time, the block by the valve body 26c to the annular groove 24a is reduced, and a larger amount of pressurized oil is discharged from the exhaust actuator port 22 to the tank port 25a than in the state of FIG. At the same time, the compressed feedback spring 62 expands to return to the original state, so that the pilot spool 58 is pressed toward the proportional solenoid 66 and the valve body 58a closes the first passage 37. As a result, the pressing force of the piston 32 remains constant without changing. Therefore, the state shown in FIG. 4, that is, the state in which the pressure oil is supplied to the fuel actuator port 14 and the pressure oil is discharged in a large amount from the exhaust actuator port is maintained.

  Assume that the plunger 66a of the proportional solenoid 66 is moved to the cover 6 side by a predetermined amount from the state of FIG. At this time, the valve body 58a of the pilot spool 58 also moves to the cover 6 side by a predetermined amount, and the first passage 37 and the second passage 46 are connected to each other while maintaining a predetermined opening degree. Pressure oil is supplied into 30. Along with this, the piston 32 moves to the spool hole 10 side. At this time, the feedback spring 62 is extended. Although the pressure oil is supplied to the piston 72 through the fourth passage, the volume of the second pressure chamber is reduced due to the movement of the spool 26 toward the cover 8, and the reaction force based on the pressure oil is increased. Become. The spool 26 stops at a position where the reaction force and the pressure of the piston 32 are balanced. At this time, the valve body 26a closes the annular groove 24b, the valve body 26b closes the annular groove 16, and the valve body 26c narrows the opening degree of the annular groove 24a, resulting in the state of FIG. At this time, since the extended feedback spring 62 is contracted to return to the original state, the pilot spool 58 is pressed toward the cover 8 and the valve body 58a closes the first passage. As a result, the pressing force of the piston 32 remains constant without changing. Therefore, the state of FIG. 3 is maintained. That is, the supply of the pressure oil to the fuel actuator port is stopped, and the pressure oil is discharged from the exhaust actuator port 22 in a small amount.

  In this state, it is assumed that the plunger 66a of the proportional solenoid 66 is further moved to the cover 8 side by a predetermined amount by the control means. At this time, in the same manner as described above, the spool 26 moves to the cover 8 side as shown in FIG. 2, the valve body 26a opens a part of the annular groove 24b, and the valve body 26b closes the annular groove 16. The valve body 26c is in a state where the opening degree of the annular groove 24a is narrower than the state of FIG. As a result, the pressure oil is discharged from the fuel supply actuator port 14 to the tank port 24b, and the pressure oil is discharged from the exhaust actuator port 22 in a smaller amount than in FIG. Since the operation of the piston 32 and the like of the pilot portion 28 at this time is the same as described above, detailed description thereof is omitted.

  In the state of FIG. 2, when the plunger 66a of the proportional solenoid 66 is moved to the cover 8 side by a predetermined amount by the control means, the spool 26 is moved to the cover 8 side in the same manner as described above. As shown in FIG. 1, the degree of closing of the annular groove 24b by the valve body 26a is narrowed, that is, the degree of opening of the annular groove 24b is widened, and the valve body 26b closes the annular groove 12 and the annular groove 16. And the annular groove 20 are communicated, and the valve body 26a closes the annular groove 24a. As a result, the discharge amount of the pressure oil from the fuel supply actuator port 14 to the fuel tack port 24b becomes larger than that in the state of FIG. 2, and the supply of the pressure oil from the pump port 18 to the exhaust actuator 22 is started. . Since the operation of the piston 32 and the like of the pilot portion 28 at this time is the same as described above, detailed description thereof is omitted.

  In the state of FIG. 1, when the plunger 66a of the proportional solenoid 66 is moved to the cover 6 side by a predetermined amount by the control means, the spool 26 is moved to the cover 6 side in the same manner as described above. As shown in FIG. 2, the valve body 26a enlarges the closed state of the annular groove 24b, the valve body 26b closes the annular groove 16, and the valve body 26c releases the blockage of the annular groove 24a. As a result, the amount of pressure oil discharged from the fuel supply actuator port 14 to the tank port 24b is reduced, and the discharge from the exhaust actuator port 22 to the tank port 25a is started. Since the operations of the piston 32 and the like of the pilot portion 28 at this time are the same as those described above, detailed description thereof is omitted.

  In the state of FIG. 2, when the plunger 66a of the proportional solenoid 66 is moved to the cover 6 side by a predetermined amount by the control means, the spool 26 is moved to the cover 6 side in the same manner as described above. Returning to the state shown in FIG. Thereafter, the same operation is repeated.

  In this marine spool valve, the pilot portion 28 is provided not on the inside of the spool valve 26 but on the cover 6 that forms a part of the valve body 2. Therefore, the manufacture can be performed easily. In particular, the pilot spool 58 is inserted into the sleeve 36, and since the sleeve 36 is formed separately from the cover 8, its manufacture is easy. Further, the portion of the first passage 37 formed in the sleeve 36 is not formed entirely by a square hole, but is formed by the square hole 38 and the notch 40, and the square hole 38 that is relatively difficult to manufacture is formed. Since the distance is shortened, the manufacturing becomes easy. Further, since the sleeve 36 and the pilot spool 58 are disposed in the vicinity of the piston 32 and the piston hole 30, the pressure oil can be quickly supplied to and discharged from the piston hole 30, and the movement of the pilot spool 58 can be prevented. The responsiveness of the piston 30 can be improved. In Patent Document 1, the pilot spool is provided in the spool, and it is necessary to align the pilot spool and the spool. In this embodiment, the feedback spring 62 is used to return the pilot spool 58 to the neutral position. Therefore, alignment between the spool 26 and the pilot spool 58 is not necessary.

  In the marine spool valve of the second embodiment, as shown in FIG. 7, the pilot spool 58 is brought into contact with the plunger 66 a of the proportional solenoid 66 without using the coupling 64. Since other configurations are the same as those of the first embodiment, the same parts are denoted by the same reference numerals, and the description thereof is omitted.

  As described in the first embodiment, since the spring force of the feedback spring 62 is set to be larger than the flow force between the pilot spool 58 and the sleeve 36, the plunger 66a of the pilot spool 58 and the proportional solenoid 66 is used. Even if they are not connected to each other, they only need to be brought into contact with each other, the coupling 64 can be omitted, and the manufacture is facilitated.

  In the marine spool valve of the third embodiment, as shown in FIG. 8, a part of the end of the valve body 26c of the spool 26 is removed, and the cover 6 covers the end of the sleeve 36 on the valve body 26c side. The bag-like portion 100 is provided close to the sleeve 36, and a feedback spring 62 a is provided between the inside of the bag-like portion 100 and the end portion of the sleeve 36. If comprised in this way, the short thing can be used for the feedback spring 62a, and the installation space of the feedback spring 62a can be reduced.

  In each of the above embodiments, the pressure oil is used as the pressure fluid. However, the present invention is not limited to this. For example, compressed air can be used as the pressure fluid. In each of the above embodiments, the spool hole 68 and the piston 70 are used as the biasing means. However, the present invention is not limited to this. For example, an elastic body that presses the spool 26 toward the cover 6 may be used. it can. In each of the above-described embodiments, the proportional solenoid is used as the electromagnetic drive unit. However, the present invention is not limited to this, and for example, a linear motor can be used.

It is a longitudinal cross-sectional front view which shows the state by which the actuator port for fuel supply and the tank port were connected in the marine spool of the 1st Embodiment of this invention, and the actuator port for exhaust_gas | exhaustion and the pump port were connected. FIG. 2 is a longitudinal sectional front view showing a state in which a fuel actuator port and a tank port are connected and an exhaust actuator port and a pump port are connected in the marine spool valve of FIG. 1. FIG. 2 is a longitudinal sectional front view showing a state where a fuel actuator port is in a neutral state and is connected to an exhaust actuator port tank port in the marine spool valve of FIG. 1. FIG. 2 is a longitudinal sectional view showing a state in which a fuel actuator port and a tank port are connected and an exhaust actuator port and a tank port are connected in the marine spool valve of FIG. 1. FIG. 2 is an enlarged longitudinal sectional front view of the vicinity of a pilot portion of the marine spool valve of FIG. 1. FIG. 2 is a longitudinal side view of the vicinity of a pilot portion of the marine spool valve of FIG. 1. It is a vertical front view which shows the pilot part vicinity of the ship spool of the 2nd Embodiment of this invention. It is a vertical front view of the marine spool of the 3rd Embodiment of this invention.

Explanation of symbols

2 Valve body 4 Tubular part 6 8 Cover 10 Spool hole 16 Actuator port 20 Pump port 24 Tank port 28 Pilot part 30 Piston hole 32 Piston 68 Spool hole (biasing means)
70 piston (biasing means)

Claims (7)

A first spool hole formed in the valve body;
A pump port communicating with the first spool hole and connected to a pressure source;
A fuel port communicating with the first spool hole and connected to a fuel supply actuator;
An exhaust port communicating with the first spool hole and connected to an actuator of the exhaust valve;
A tank port communicating with the first spool hole and communicating with the tank;
A spool inserted through the first spool hole;
A pilot portion that presses this spool from one end side thereof; and
A biasing means for pressing the spool against the other side from the end side;
In the marine spool valve provided,
In the pilot portion, a first piston is slidably inserted into a first piston hole formed in the valve main body, and a first pressure chamber is defined by the first piston and the valve main body. A pilot spool that supplies and discharges the pressure fluid from the pressure source is provided in the chamber, an electromagnetic drive unit that moves the pilot spool is provided, spool return means that counteracts the thrust of the electromagnetic drive unit is provided, and the spool position is adjusted. Detecting means for detecting, controlling the electromagnetic drive unit based on a signal and a control signal of the detecting means;
A fuel supply position for supplying the pressure fluid from the pump port to the fuel port by controlling the spool to a desired position by the pilot unit, and the pressure from the fuel port to the tank port A fuel discharge position for discharging the fluid, an exhaust supply position for supplying the pressure fluid from the exhaust port to the tank port, and an exhaust for discharging the pressure fluid from the exhaust port to the tank port Marine spool valve that switches to the discharge position.   2. The marine spool valve according to claim 1, wherein a sleeve is disposed closer to the center of the valve body than the first piston, and the sleeve communicates with the first pressure chamber, and communicates with the pressure source. A second passage that communicates with the tank, and the pilot spool is slidably inserted into the sleeve, and the first passage is moved to the second passage or the second passage by sliding of the pilot spool. A marine spool valve that controls supply and discharge of the pressure fluid to and from the pressure chamber by shutting off communication with the three passages.   3. The marine spool valve according to claim 1, wherein the urging means is inserted into the second spool hole formed in the spool from the other end of the spool, and inserted into the second spool hole. A marine spool valve comprising: a second piston that abuts; a second pressure chamber defined in the spool by the second piston; and a fourth passage communicating the second pressure chamber and the pressure source.   4. The marine spool valve according to claim 1, wherein a feedback spring is disposed between the spool and the pilot spool as the return means, and the electromagnetic drive unit is a proportional solenoid.   5. The marine spool valve according to claim 4, wherein a spring force of the feedback spring is larger than a flow force between the pilot spool and the sleeve.   The marine spool valve according to claim 2, wherein the first passage is formed by a notch and a square hole.   The marine spool valve according to any one of claims 1 to 6, wherein a stroke sensor is provided in the spool as the detection means, and the electromagnetic drive unit is controlled based on a signal from the stroke sensor and a control signal. Spool valve.

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