JP2014114765A - Ejector device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To compactify a system such as a fuel cell system by integrally assembling a flow rate regulation valve to an ejector device.SOLUTION: A nozzle 30 is accommodated in a suction chamber 10a, and a second fluid is taken into the suction chamber 10a from a second fluid introduction port 10c by suction force due to a negative pressure generated when a first fluid is jetted from the nozzle 30. The first fluid jetted from a nozzle port 30b of the nozzle 30 and the second fluid in the suction chamber 10a are mixed, and the it is supplied to a circulation passage 10b at a downstream side of the nozzle. A housing 20 is formed with a valve accommodation chamber 20a formed at an upstream side of the nozzle 30 on an axis line L of the nozzle 30. A flow rate regulation valve 40 is accommodated in the valve accommodation chamber 20a, and a needle 28 to be displaced in conjunction with a first valving element 26 of the flow rate regulation valve 40, is disposed on an axis L between the flow rate regulation valve 40 and the nozzle 30. An opening area between a nozzle port 30b and a tip of the needle is changed by displacing the needle 28 in accompany with flow rate control by the flow rate regulation valve 40.

Description

  The present invention is a negative pressure generated by flowing the first fluid from the gas supply path in the pipe, sucking the second fluid (stack double flow) into the pipe and mixing the first fluid and the second fluid, The present invention relates to an ejector device for supplying a fluid to a secondary side.

  Conventionally, as this type of ejector device, for example, there are those disclosed in Japanese Patent Application Laid-Open No. 2009-301951 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2010-242508 (Patent Document 2). These ejector devices mix and recirculate fuel off-gas (hydrogen off-gas) discharged from the fuel cell in a fuel cell system with newly supplied fuel gas (hydrogen gas).

  In Patent Document 1, a needle disposed in a nozzle is configured to be driven by an electromagnetic actuator, and the needle is inserted into a nozzle hole of the nozzle in a non-excited state of the solenoid of the electromagnetic actuator. Is not inserted. In the non-excited state, the hydrogen gas supplied to the nozzle is throttled by the needle and the nozzle hole to accelerate the hydrogen gas, and the hydrogen off-gas is generated by the negative pressure generated by the jet pump effect of the hydrogen gas ejected from the nozzle. Is sucked into the outer periphery of the nozzle, the sucked hydrogen off gas is mixed with the accelerated hydrogen gas, and supplied from the outlet port to the hydrogen supply passage leading to the fuel cell via the diffuser. Further, in the solenoid excited state, the needle is not inserted into the nozzle hole, thereby increasing the effective area of the nozzle hole and supplying a relatively large flow of hydrogen to the fuel cell.

  Patent Document 2 discloses a fuel cell system using an ejector device as shown in FIG. The first fluid (hydrogen gas) in the hydrogen tank is adjusted to a predetermined flow rate by the flow rate adjusting valve and flows into the ejector device (variable ejector), and this first fluid is supplied into the fuel cell stack. In the ejector device, the second fluid (hydrogen offgas) discharged from the fuel cell is sucked by the negative pressure generated when the first fluid is ejected from the nozzle portion, and this is mixed with the first fluid and again the fuel cell. To supply. The ejector device disclosed in Patent Document 2 displaces the needle by the expansion and contraction action of the urging member of the pressure sensing chamber, and closes the opening of the nozzle portion with the needle when the first fluid (hydrogen gas) is not pressurized (system stopped). Moreover, the opening adjustment part which changes the opening amount of a nozzle part is comprised.

JP 2009-301951 A JP 2010-242508 A

  In the fuel cell system disclosed in Patent Document 2, as shown in FIG. 6, a flow rate adjusting valve is used to adjust the flow rate of the first fluid supplied to the ejector device. In this conventional system, Since the flow rate adjusting valve is arranged on the upstream side of the ejector device, the entire system becomes large and expensive.

  In view of the conventional problems, an object of the present invention is to provide an ejector device in which a flow rate adjusting valve and an ejector are integrated.

  The ejector device according to claim 1, wherein when the nozzle is accommodated in the suction chamber and the first fluid is ejected from the nozzle, the second fluid is taken into the suction chamber by a suction force generated by the negative pressure generated in the suction chamber. An ejector device that mixes the first fluid ejected from the nozzle port of the nozzle and the second fluid in the suction chamber and supplies the fluid to the flow passage on the downstream side of the nozzle, the housing including the suction chamber A second fluid introduction port communicating with the flow passage, the suction chamber, a valve accommodating chamber located on the upstream side of the nozzle on the axis of the nozzle, and a valve accommodating chamber for supplying the first fluid from the supply source An inlet port that flows into the valve, a flow rate adjusting valve is accommodated in the valve accommodating chamber, and a needle that is displaced in conjunction with the valve body of the flow rate adjusting valve on the axis between the flow rate adjusting valve and the nozzle Is disposed on the flow rate adjusting valve. The flow rate control and the needle are displaced to change the opening area between the nozzle port and the needle tip, and the opening area of the nozzle port and the needle tip is determined by the valve opening degree of the flow control valve. It is characterized by being large when it is large and small when the valve opening degree of the flow rate adjusting valve is small.

  An ejector device according to a second aspect is the ejector device according to the first aspect, wherein the valve body and the needle of the flow rate adjusting valve have a ratio between a displacement amount of the valve body and a displacement amount of the needle. It is connected via a setting spring to be set and a main spring.

  An ejector device according to a third aspect is the ejector device according to the first or second aspect, wherein the nozzle port is fully closed by the needle when the flow rate adjusting valve is closed.

  An ejector device according to a fourth aspect is the ejector device according to any one of the first to third aspects, wherein the flow rate adjusting valve is a double seat type control valve.

  An ejector device according to a fifth aspect is the ejector device according to any one of the first to third aspects, wherein the flow rate adjusting valve is a single-seat control valve.

  According to the ejector device of the first aspect, since the flow rate adjusting valve is integrally assembled in the valve accommodating chamber of the housing, the piping member that causes pressure loss between the secondary side port of the flow rate adjusting valve and the ejector device. Therefore, the flow rate of the first fluid at the nozzle can be increased. Therefore, the suction force with respect to the 2nd fluid of an ejector apparatus can be raised. Further, the ejector device is made compact and inexpensive.

  According to the ejector device of the second aspect, in addition to the effect of the first aspect, the displacement amount of the needle can be increased with respect to the displacement amount of the valve body by the relationship between the setting spring and the main spring. Here, when the object is sandwiched between springs having different spring constants, the output of the displacement of the object can be set to a predetermined ratio with respect to the displacement input to one spring due to the difference in the spring constant. By making the spring constant of the setting spring smaller than the spring constant of the main spring, the displacement amount of the needle becomes larger than the displacement amount of the valve body. Thus, since the displacement amount of the needle can be increased with respect to the displacement amount of the valve body, the stroke of the valve body of the flow rate adjustment valve can be reduced, and the flow rate adjustment valve can be reduced in size.

  According to the ejector device of the third aspect, in addition to the effect of the first or second aspect, for example, when the fuel cell system is stopped, the flow rate adjustment valve is closed. At this time, the nozzle port is fully closed at the needle tip. Therefore, the second fluid (hydrogen off-gas), which is a humidifying fluid, can be prevented from flowing into the flow rate adjustment valve side, and operation at a low temperature (freezing) is not hindered.

  According to the ejector device of the fourth aspect, in addition to the effect of any one of the first to third aspects, since the flow rate adjusting valve is a double seat type control valve, the first fluid flowing through the flow rate adjusting valve is a large flow rate. Even at this time, the flow control valve can be miniaturized by the provision of a plurality of valve ports.

  According to the ejector device of the fifth aspect, in addition to the effect of any one of the first to third aspects, since the flow rate adjusting valve is a single seat type control valve, the first fluid flowing through the flow rate adjusting valve has a small flow rate. As an ejector apparatus suitable for the system, it is further downsized and inexpensive.

It is sectional drawing when the valve opening degree of the ejector apparatus of 1st Embodiment of this invention is small. It is sectional drawing when the valve opening degree of the ejector apparatus of 1st Embodiment of this invention is large. It is a partial sectional view of a flow control valve and a needle of an ejector device of a 1st embodiment of the present invention. It is sectional drawing when the valve opening degree of the ejector apparatus of 2nd Embodiment of this invention is small. It is sectional drawing when the valve opening degree of the ejector apparatus of 3rd Embodiment of this invention is small. It is a block diagram of the conventional fuel cell system.

  Next, an embodiment of the present invention will be described. 1 is a cross-sectional view of the ejector device of the first embodiment when the valve opening is small, FIG. 2 is a cross-sectional view of the ejector device of the first embodiment when the valve opening is large, and FIG. 3 is a diagram of the ejector device of the first embodiment. It is a partial cross section figure of a flow control valve and a needle. The ejector device according to this embodiment includes a first housing 10 and a second housing 20.

  The housing 10 is formed with a suction chamber 10a, a flow passage 10b communicating from the suction chamber 10a to the outside, and a second fluid introduction port 10c communicating with a side portion of the suction chamber 10a. The housing 20 includes a valve accommodating chamber 20a located on the upstream side of the nozzle 30 on the axis L of the nozzle 30 to be described later, and a secondary port 20b that communicates the bottom of the valve accommodating chamber 20a with the hollow portion 30a of the nozzle 30. And an inlet port 20c through which a first fluid (hydrogen gas) from a supply source such as a hydrogen tank (not shown) flows into the center of the side of the valve storage chamber 20a, and one end side and the other end side of the valve storage chamber 20a communicate with each other. The outlet ports 20d and 20e and the connecting path 20f that connects the outlet ports 20d and 20e and is sealed by the lid member 20A are formed.

  A nozzle 30 is attached to the secondary port 20 b side of the housing 20. The nozzle 30 protrudes into the suction chamber 10a of the housing 10, and the nozzle port 30b on the tip side is opposed to the flow passage 10b.

  A flow rate adjusting valve 40 is accommodated in the valve accommodating chamber 20 a of the housing 20. In FIG. 1 and FIG. As shown in FIG. 3, the flow rate adjustment valve 40 is a double seat type control valve and has a valve housing 1. The flow rate adjusting valve 40 is arranged with the axis L in the horizontal direction, but in the description of FIG.

  The valve housing 1 includes a second secondary port 1a that communicates with the outlet port 20d, a primary port 1b that communicates with the inlet port 20c, and a cylindrical sub-second that communicates with the second secondary port 1a. Two valve chambers 11, a first valve chamber 12 communicating with the primary side port 1b, a second valve port 13 communicating with the sub-second valve chamber 11 and the first valve chamber 12, and a lower portion of the first valve chamber 12. A substantially cylindrical main second valve chamber 14 is formed. The horizontal cross-sectional shape of the second valve port 13 is circular, and a second valve seat 13a is disposed on the side of the secondary second valve chamber 11.

  A valve seat member 17b and a valve guide 16 are fitted into the main second valve chamber 14, and the valve seat member 17b and the valve guide 16 are fixed by caulking the end of the valve housing 1. The valve seat member 17b is formed with a first valve port 17 that conducts the first valve chamber 12 and the main second valve chamber 14, and the first valve port 17 has a first valve chamber 12 side opening around the first valve chamber 12 side. A valve seat 17a is provided. A slide hole 16a is formed at the center of the valve guide 16, and a first secondary port 16b is formed around the slide hole 16a. The second secondary port 1a is electrically connected to the main second valve chamber 14 and the first secondary port 16b by the outlet ports 20d and 20e of the housing.

  An inner diameter of a seal surface 26a of the first valve body 26 described later and an inner diameter of a seal surface 21a of the second valve body 21 are set to be substantially the same diameter. These inner diameters are set smaller than the inner diameter of the sub second valve chamber 11, the inner diameter of the first valve chamber 12, and the inner diameter of the main second valve chamber 14. Further, in the valve housing 1, an opening portion 11a at the upper end of the sub second valve chamber 11 (a portion to which a plunger case 3 described later is fixed) opens to one side of the valve housing 1, and the inner diameter of the opening portion 11a. Is substantially the same diameter as the inner diameter of the sub second valve chamber 11. In the valve housing 1, the opening portion 14 a at the lower end of the main second valve chamber 14 opens to the other side of the valve housing 1, and the inner diameter of the opening portion 14 a is substantially the same as the inner diameter of the main second valve chamber 14. It is a diameter. The first valve chamber 12 is located between the sub-second valve chamber 11 and the main second valve chamber 14, and the first valve chamber 12 and the main second valve chamber 14 are cup-shaped first described later. The insertion is made through the insertion hole 12 a having an inner diameter larger than that of the valve body 26. The inner diameter of the seal surface 26a of the first valve body 26 and the inner diameter of the seal surface 21a of the second valve body 21 may be the same diameter.

  In the sub second valve chamber 11, the first valve chamber 12, the second valve port 13, the first valve port 17, and the main second valve chamber 14, a double valve member 2 that can be displaced in the direction along the axis L is provided. Has been extended. The double valve member 2 includes a second valve member 2B and a first valve member 2A. The 2nd valve member 2B is located in the sub 2nd valve chamber 11, the 2nd valve body 21 which can be contacted / separated with respect to the 2nd valve seat 13a, and the elongate circle extended below from the 2nd valve body 21 It has a columnar valve rod 22, a columnar guide portion 23 extending upward from the second valve body 21, and a connecting rod portion 24 extending further upward from the guide portion 23. An annular end surface perpendicular to the axis L on the second valve seat 13 a side of the second valve body 21 is a seal surface 21 a for the second valve port 13. In addition, the annular rectifying plate 23 a disposed above the sub second valve chamber 11 does not allow the fluid that has passed through the second valve port 13 to flow into the plunger 5 side. The flow is rectified so as to be easily discharged to the secondary port 1a.

  The first valve member 2 </ b> A is disposed in the first valve chamber 12 and the main second valve chamber 14, and is formed in a cylindrical shape with a cylindrical portion 25 centering on the axis L and on the first valve chamber 12 side from the cylindrical portion 25. A cup-shaped first valve body 26 that can be brought into and out of contact with the first valve seat 17a, a spherical portion 27 formed below the cylindrical portion 25, and a needle 28 extending downward from the spherical portion 27. ing. The cylindrical portion 25, the first valve body 26, the spherical portion 27, and the needle 28 are integrally formed. An annular end surface perpendicular to the axis L on the first valve seat 17 a side of the first valve body 26 is a seal surface 26 a for the first valve port 17. The cylindrical portion 25 is formed with an insertion hole 25a centered on the axis L. The needle 28 is inserted into the slide hole 16a of the valve guide 16, and the spherical portion 27 is fitted in the slide hole 16a.

  The second valve member 2B and the first valve member 2A are assembled as follows. After the cylindrical portion 25 of the first valve member 2A is inserted into the valve rod 22 of the second valve member 2B through the insertion hole 25a, the valve seat member 17b and the valve guide 16 are incorporated into the lower portion of the valve housing 1, and the second In a state where the second valve port 13 is closed by the valve member 2B and the first valve port 17 is closed by the first valve member 2A, the locking agent 29 is placed in the cup-shaped first valve body 26 of the first valve member 2A. The second valve member 2B and the first valve member 2A are integrally fixed by being injected and solidifying the locking agent 29. Thereby, the dimension between the seal parts of the 2nd valve body 21 and the 1st valve body 26 becomes the same dimension as the dimension between the seal parts of the 2nd valve seat 13a and the 1st valve seat 17a. Note that, at the location of the locking agent 29, a fixed groove including a plurality of grooves that form a circumference around the axis L is formed on the inner surface of the first valve body 26 and the outer peripheral surface of the valve rod 22. As a result, the relative displacement (displacement) of the second valve member 2B and the first valve member 2A in the direction of the axis L after the locking agent 29 is solidified is prevented.

  A cylindrical plunger case 3 is airtightly fixed to the upper opening end of the sub second valve chamber 11, and a suction element 4 is airtightly fixed to the upper portion of the plunger case 3 by welding. The plunger 5 is disposed inside the plunger case 3, and the plunger spring 6 is disposed in a compressed state between the plunger 5 and the step portion 23 a of the guide portion 23 and the connecting rod portion 24. ing. The plunger spring 6 has one end abutted against the inner bottom surface 52 of the plunger 5 and the other end locked to the step portion 23a. Thereby, the plunger 5 is made to contact | abut to the below-mentioned retaining member 24a. Note that the attractor 4 and the plunger 5 are made of a magnetic material, and each has a rotationally symmetric shape with the axis L as an axis except for the vent hole 5a of the plunger 5.

  The suction element 4 and the plunger 5 are formed with insertion holes 41 and 51 coaxial with the axis L, respectively. Then, the connecting rod portion 24 of the second valve member 2B is inserted into the insertion hole 51 of the plunger 5, and a cylindrical retaining member 24a is provided at the end of the connecting rod portion 24 in the insertion hole 41 of the suction element 4. It is inserted. The retaining member 24a and the end of the connecting rod portion 24 are fixed by welding.

  The suction element 4 is formed with an adjustment portion hole 42 having a diameter larger than that of the insertion hole 41, and a setting adjustment portion 43 is disposed in the adjustment portion hole 42. The setting adjustment unit 43 includes an adjustment screw 43a, a ball receiver 43b, an adjustment spring 43c, and a ball 43d. The adjustment spring 43c is disposed in a compressed state between the adjustment screw 43a and the ball receiver 43b, and the ball 43d is disposed in the insertion hole 41 of the suction element 4 while being in contact with the ball receiver 43b. . The adjustment spring 43c urges the ball 43d to come into contact with the upper end of the retaining member 24a via the ball receiver 43b. The adjustment screw 43 a is attached to the suction element 4 by screwing the male screw part 43 a 1 on the outer periphery thereof with a female screw part 4 a formed on the upper inner peripheral surface of the suction element 4.

  An electromagnetic coil 7 wound around a bobbin 71 is provided on the outer periphery of the plunger case 3 and the attractor 4, and a magnetic circuit is formed by excitation of the electromagnetic coil 7, so that the attractor 4 and the plunger 5 A magnetic attraction force is generated between them.

  With the above configuration, the flow rate adjustment valve 40 operates as follows. The setting adjustment unit 43 urges the double valve member 2 toward the second valve seat 13a and the first valve seat 17a via the ball receiver 43b, the ball 43d, and the retaining member 24a by the adjustment spring 43c. By exciting the electromagnetic coil 7, the plunger 5 is attracted by the attractor 4, the double valve member 2 is displaced against the biasing force of the adjusting spring 43c, and the second valve body 21 and the first valve body 26 are They are separated from the second valve seat 13a and the first valve seat 17a, respectively. Thereby, the valve is closed and the valve is opened, and the opening degree of the second valve port 13 and the first valve port 17 is controlled by the current value applied to the electromagnetic coil 7.

  Further, by eliminating the excitation of the electromagnetic coil 7, the second valve body 21 and the first valve body 26 are seated on the second valve seat 13a and the first valve seat 17a, respectively, and the valve is closed. As described above, the dimensions between the seal portions of the second valve body 21 and the first valve body 26 are the same as the dimensions between the seal portions of the second valve seat 13a and the first valve seat 17a. Therefore, the second valve body 21 and the first valve body 26 are seated simultaneously.

  The double valve member 2 has a valve closing which acts on the first valve body 26 at the first valve port 17 due to the pressure difference between the pressure in the first valve chamber 12 and the pressure in the sub second valve chamber 11 and the main second valve chamber 14. Direction force and the valve opening direction force acting on the second valve body 21 at the second valve port 13 work, the inner diameter of the seal surface 26a of the first valve body 26 and the seal surface 21a of the second valve body 21 Therefore, the force acting on the double-valve member 2 is canceled by the differential pressure, and control that is not affected by the differential pressure is possible.

  Note that, by changing the inner diameter of the first secondary port 16b of the valve guide 16, the differential pressure (P1-P2 ') acting on the first valve body 26 at the first valve port 17 in the valve open state is increased. The change characteristic of the valve opening with respect to the change of the pressure of the primary port 1b can be changed arbitrarily.

  The needle 28 has a conical portion 28 a at the tip, and the conical portion 28 a is inserted into the nozzle port 30 b of the nozzle 30. By controlling the energization amount to the electromagnetic coil 7 of the flow regulating valve 40, the valve opening degree of the second valve body 21 and the first valve body 26 is controlled, and the needle 28 is connected to the second valve body 21 and the first valve body 21. Since it is connected to the valve body 26, the needle 28 is also displaced according to the valve opening degree. The displacement of the needle 28 changes the gap amount (opening area) between the nozzle port 30b and the conical portion 28a of the needle 28, and the speed of the hydrogen gas ejected from the nozzle 30 is adjusted.

  When the second valve body 21 and the first valve body 26 are opened by the flow rate adjustment valve 40, the hydrogen gas (first fluid) flowing in from the inlet port 20 c passes through the first valve port 17 and the first two It flows to the secondary port 16b and flows to the secondary port 20b. Further, also through the second valve port 13, it flows to the second secondary port 1 a and the outlet ports 20 d and 20 e and flows to the secondary port 20 b. The hydrogen gas that has passed through the secondary side port 20b is supplied to the hollow portion 30a of the nozzle 30 and is jetted into the flow passage 10b from the gap between the conical portion 28a of the needle 28 and the nozzle port 30b of the nozzle 30. Then, the hydrogen off-gas as the second fluid is taken into the suction chamber 10a from the second fluid introduction port 10c and ejected from the nozzle port 30b by the suction force due to the negative pressure generated by the jet pump effect of the jetted hydrogen gas. Hydrogen gas and hydrogen off-gas are mixed and supplied to the flow passage 10 b on the downstream side of the nozzle 10. As described above, since the first valve port 17 of the flow rate adjusting valve 40 and the nozzle port 30b of the nozzle 30 are opposed to each other on the axis L or in a direction parallel to the axis L, the first valve port 17 and the nozzle The pressure loss between 30 and the hydrogen gas flow rate does not decrease.

  When the electromagnetic coil 7 is excited and the secondary flow rate of the flow rate adjusting valve 40 increases, the needle 28 is displaced to the left together with the second valve body 21 and the first valve body 26 as shown in FIG. At this time, since the secondary side flow rate from the flow rate adjustment valve 40 increases, the flow rate ejected from the nozzle 30 increases normally, but the gap amount between the nozzle port 30b and the conical portion 28a increases. For this reason, the flow rate of the hydrogen gas ejected from the nozzle 30 decreases. Therefore, the suction force generated when the hydrogen gas is ejected from the nozzle 30 is also reduced, and an increase in the flow rate of the hydrogen off gas (second fluid) taken into the suction chamber 10a is suppressed.

  When the secondary flow rate from the flow regulating valve 40 is small, that is, when the valve opening degree of the flow regulating valve 40 is small, a small current is energized to the electromagnetic coil 7. At this time, the needle is located on the right side together with the valve body as shown in FIG. At this time, since the secondary flow rate of the flow rate adjusting valve 40 is reduced, the flow velocity ejected from the nozzle 30 is reduced, but the gap amount between the nozzle port 30b and the conical portion 28a is reduced, and the nozzle The flow rate of the hydrogen gas ejected from 30 increases. Therefore, the suction force due to the negative pressure generated by the jet pump effect of the hydrogen gas ejected from the nozzle portion 30 into the flow passage 10b does not decrease, and the flow rate of the hydrogen off-gas (second fluid) taken into the suction chamber 10a does not decrease. Suppresses the decline.

  In this way, the suction force generated by flowing through the ejector pipe from the low flow rate to the large flow rate from the flow rate adjustment valve 40 is properly maintained, and the hydrogen off-gas (second fluid) is taken into the suction chamber 10a. The fluid can be sufficiently circulated in the system together with the hydrogen gas (first fluid) of the supply source.

  When the system is stopped (the flow rate adjustment valve 40 is closed), the conical portion 28a of the needle 28 comes into contact with the nozzle port 28b, and the hydrogen off-gas (second fluid) that is a humidified fluid flows into the flow rate adjustment valve 40 side. Therefore, it does not interfere with operation at low temperatures (freezing).

  As described above, since the flow regulating valve and the ejector device are integrated, there is no piping member that causes pressure loss between the secondary port of the flow regulating valve and the ejector device, so the first fluid at the nozzle The flow rate of can be increased. Therefore, the suction force with respect to the 2nd fluid of an ejector apparatus can be raised. Further, the ejector device is made compact and inexpensive.

  FIG. 4 is a cross-sectional view of the ejector device according to the second embodiment when the valve opening is small. Elements similar to those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. The second embodiment is an example in which the first valve member 2A of the flow rate adjustment valve 40 and the needle are separated. As shown in the enlarged view of FIG. 4, the first valve member 2A is composed of a cylindrical portion 25 'that abuts on the ball 8a and a first valve body 26', and a lock within the first valve body 26 '. The agent 29 is fixed to the valve stem 22 (second valve member 2B).

  A ball receiver 8b is in contact with the ball 8a. The needle 28 'has a flange portion 28b' at the end in the valve accommodating chamber 20a, and the main spring 8c is disposed in a compressed state between the flange portion 28b 'and the ball receiver 8b. A setting spring 8d is disposed between the flange portion 28b 'and the housing 20 in a compressed state. That is, the main spring 8c and the setting spring 8d are arranged in series on the axis L with the flange portion 28b 'interposed therebetween.

  The plunger case 3, the connecting structure of the connecting rod portion 24 and the plunger 5, the attractor 4, the electromagnetic coil 7, the setting adjusting portion 43 and the like are the same as in the first embodiment.

With the above configuration, when the first valve body 26 ′ (and the second valve body 21) of the flow rate adjusting valve 40 is displaced, the needle 28 ′ is set with the spring constant of the main spring 8 c according to the displacement amount of the valve body. The spring 8d is displaced by an amount corresponding to the spring constant. This spring constant relationship is
The relationship of the spring constant of the setting spring 8d <the spring constant of the main spring 8c is preferable.

  Thus, in the second embodiment, the displacement amount of the needle 28 'is larger than the displacement amount of the first valve body 26' (and the second valve body 21) due to the relationship between the setting spring 8d and the main spring 8c. Therefore, the stroke of the first valve body 26 '(and the second valve body 21) can be reduced, and the flow control valve 40' can be reduced in size.

  FIG. 5 is a cross-sectional view of the ejector device according to the third embodiment when the valve opening is small. Although the sizes are different, the same elements as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. The flow rate adjustment valve 40 of the first embodiment and the second embodiment is a double seat type control valve, but the flow rate adjustment valve 40 ′ of this third embodiment is a single seat type control valve. The ejector device of this embodiment has a first housing 10 and a second housing 20 '.

  In the housing 10, a suction chamber 10a, a flow passage 10b, and a second fluid introduction port 10c are formed as in the above embodiment. The housing 20 ′ includes a valve accommodating chamber 20 a ′ located on the upstream side of the nozzle 30 on the axis L of the nozzle 30, and a secondary port communicating the bottom of the valve accommodating chamber 20 a ′ with the hollow portion 30 a of the nozzle 30. 20b 'and a supply source such as a hydrogen tank (not shown) are formed. The nozzle 30 is attached to the secondary port 20b ′ side of the housing 20 ′, as in the above embodiment. A flow rate adjusting valve 40 'is accommodated in the valve accommodating chamber 20a'.

  The flow regulating valve 40 'has a valve housing 1'. A primary side port 1b 'communicating with the inlet port 20c' and a valve chamber 12 'communicating with the primary side port 1b' are formed in the valve housing 1 '. A valve seat member 17b and a valve guide 16 are fixed to the end of the valve housing 1 '. A valve port 17 is formed in the valve seat member 17b. A slide hole 16a is formed at the center of the valve guide 16, and a secondary port 16b is formed around the slide hole 16a.

  A valve member 2 ″ that can be displaced in the direction along the axis L extends in the valve chamber 12 ′, the valve port 17, and the valve guide 16. The valve member 2 ″ is disposed in the valve chamber 12 ′. A cylindrical valve body 26 ″ that can be brought into and out of contact with the valve seat member 17b, a connecting rod portion 24 extending from the valve body 26 ″, a spherical portion 27 similar to the first embodiment, and a spherical portion 27. And a needle 28 extending downward. The valve body 26 ″, the connecting rod portion 24, the spherical portion 27, and the needle 28 are integrally formed.

  The plunger case 3, the connecting structure of the connecting rod portion 24 and the plunger 5, the attractor 4, the electromagnetic coil 7, the setting adjusting portion 43, and the like are the same as in the above embodiment.

  With the above configuration, when the electromagnetic coil 7 is excited, the valve member 2 "is displaced to the left side in FIG. 5, and the valve body 26" is separated from the valve seat member 17b to be in the valve open state. The opening degree of the valve port 17 is controlled by the current value applied to the electromagnetic coil 7. Further, by eliminating the excitation of the electromagnetic coil 7, the valve body 26 ″ is seated on the valve seat member 17b and the valve is closed.

  Further, when the energization amount to the electromagnetic coil 7 is controlled, the valve opening of the valve body 26 ″ is adjusted, and the needle 28 is connected to the valve body 26 ″. Displace. As a result, the gap amount (opening area) between the nozzle port 30b and the conical portion 28a of the needle 28 changes, and the velocity of the hydrogen gas ejected from the nozzle 30 is the same as in the first and second embodiments. Is adjusted.

  In the third embodiment, the flow rate adjustment valve 40 'is a single seat control valve, and the hydrogen gas (first fluid) flowing through the flow rate adjustment valve 40' is suitable for a system with a small flow rate, and is compact as an ejector device. ing.

  In the single seat type control valve of the third embodiment, a main spring and a setting spring similar to those of the second embodiment may be provided between the valve body 26 ″ and the needle 28.

DESCRIPTION OF SYMBOLS 10 1st housing 10a Suction chamber 10b Flow path 10c 2nd fluid introduction port 20 2nd housing 20a Valve accommodation chamber 20b Secondary side port 20c Inlet port 20d Outlet port 20e Outlet port 30 Nozzle 30a Hollow part 30b Nozzle port 40 Flow rate Regulating valve L Axis 1 Valve housing 1a Second secondary port 1b Primary port 11 Sub second valve chamber 12 First valve chamber 13 Second valve port 13a Second valve seat 14 Main second valve chamber 16 Valve guide 16a Slide hole 16b First secondary port 17 First valve port 17a First valve seat 17b Valve seat member 2 Double valve member 2A First valve member 2B Second valve member 21 Second valve body 22 Valve rod 24 Connecting rod portion 25 cylindrical portion 25a insertion hole 26 first valve body 27 spherical portion 28 needle 28a conical portion 29 locking agent 4 attractor 5 plunger 7 electromagnetic coil 8 Ball 25 'Cylindrical portion 8b Ball receiver 28' Needle 28a 'Conical portion 28b' Flange portion 8c Main spring 8d Setting spring 20 'Housing 20a' Valve accommodating chamber 40 'Flow regulating valve 12' Valve chamber 2 "Valve member 26" Valve body

Claims (5)

When the nozzle is accommodated in the suction chamber and the first fluid is ejected from the nozzle, the second fluid is taken into the suction chamber by the negative pressure generated in the suction chamber and ejected from the nozzle port of the nozzle. An ejector device that mixes the first fluid and the second fluid in the suction chamber and supplies the fluid to the flow passage on the downstream side of the nozzle,
A housing, the suction chamber, the flow passage, a second fluid introduction port communicating with the suction chamber, a valve storage chamber located upstream of the nozzle on the axis of the nozzle, and a first from a supply source An inlet port for allowing one fluid to flow into the valve storage chamber;
A flow rate adjusting valve is accommodated in the valve accommodating chamber, and a needle that is displaced in conjunction with the valve body of the flow rate adjusting valve is disposed on the axis between the flow rate adjusting valve and the nozzle,
Along with the flow control in the flow control valve, the needle is displaced, and the opening area between the nozzle port and the needle tip is changed,
An ejector device characterized in that the opening area of the nozzle port and the tip of the needle is large when the valve opening degree of the flow rate adjusting valve is large and small when the valve opening degree of the flow rate adjusting valve is small.   The valve body and the needle of the flow rate adjusting valve are connected via a setting spring and a main spring that set a ratio of a displacement amount of the valve body and a displacement amount of the needle. Item 2. The ejector device according to Item 1.   The ejector device according to claim 1 or 2, wherein when the flow rate adjustment valve is closed, the nozzle port is fully closed by the needle.   The ejector device according to any one of claims 1 to 3, wherein the flow rate adjusting valve is a double seat type control valve.   The ejector device according to any one of claims 1 to 3, wherein the flow rate adjusting valve is a single seat control valve.

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