JP7333963B2 - Exhaust valve structure of liquid pumping device - Google Patents

Description

TECHNICAL FIELD The present invention relates to an exhaust valve structure for a liquid pressure-feeding device that pressurizes a liquid stored in a container with a driving fluid that has flowed into the container and discharges the liquid to the outside of the container.

2. Description of the Related Art There is a liquid pumping device that pressurizes a liquid stored in a container using steam or compressed air as a driving fluid and discharges the liquid out of the container (for example, Patent Document 1). A pumping device such as that disclosed in Patent Document 1 is called a pumping trap, and is a mechanical pump that does not require electricity. Pumping traps do not require electricity, so they have the advantage of being applicable, for example, to areas where power supply is difficult.

Japanese Patent No. 5897988

In the conventional liquid pumping device, the opening area of the exhaust valve opening that can be opened by the exhaust valve body is small. Therefore, the discharge capacity of the driving fluid is low, and the opening of the check valve on the inflow side is delayed, which may delay the inflow of the liquid into the container. However, increasing the opening area of the exhaust valve port requires a valve opening force greater than the valve opening force required to open the exhaust valve port with a small opening area.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an exhaust valve structure for a liquid pressure-feeding device capable of increasing the liquid pressure-feeding capacity per unit time by increasing the exhaust capacity and rapidly opening the check valve on the inflow side. there is

In order to achieve the above object, the exhaust valve structure for a liquid pressure-feeding device according to the present invention is a liquid pressure-feeding device for pressurizing a liquid stored in a container with a driving fluid flowed into the container and discharging the liquid outside the container. The exhaust valve structure includes a main exhaust passage that discharges the driving fluid in the container, and a pilot exhaust passage that communicates the space in the container with the main exhaust passage and has a passage area smaller than that of the main exhaust passage. a main exhaust valve for opening and closing the main exhaust passage; a pilot exhaust valve connected to a drive source for opening and closing the pilot exhaust passage; and a second spring member that applies force to the pilot exhaust valve in a direction away from the pilot valve seat and applies force to the main exhaust valve in a direction to be seated on the main valve seat. ing.

According to this configuration, when the valve is opened, the pilot exhaust valve having a small passage area is opened first by the driving force from the driving source and the spring force of the second spring member. When the pilot exhaust valve opens, the spring force of the second spring member becomes zero. In other words, the second spring member eliminates the force acting in the direction of seating the main exhaust valve on the main valve seat. As a result, the main exhaust valve having a large passage area is opened by the driving force from the driving source and the spring force of the first spring member. In this way, since the main exhaust valve is opened by the spring force of the first spring member, the force required to open the pilot exhaust valve with a small passage area opens the main exhaust valve with a large passage area. As a result, the drive fluid can be discharged more efficiently, the check valve on the side of the liquid flowing into the container can be opened quickly, and the liquid can be pressure-fed per unit time.

In the present invention, the spring force of the first spring member is equal to or greater than the valve opening force required to open the main exhaust valve without the first spring member, and It may be set smaller than the sum of the spring force of the second spring member. With this configuration, a large valve opening force can be obtained, so that the operation of the main exhaust valve is stabilized.

In the present invention, the main exhaust valve includes a cylindrical main valve body in which the pilot exhaust passage is formed and which is seated on the main valve seat at one end in the axial direction, and from the other end of the main valve body. It has a disk-shaped bottom plate extending in the radial direction and a cylindrical portion extending from the bottom plate to the other end side in the axial direction, and a first spring member is interposed between the main valve seat and one end surface of the bottom plate. and the pilot valve seat may be formed on the other end face of the bottom plate.

In this case, the pilot exhaust valve has a rod-shaped pilot valve element that moves axially inside the cylindrical portion, and a flange portion that extends like a flange from the pilot valve element. A second spring member may be interposed between the one end surface of the flange portion.

According to the exhaust valve structure of the liquid pressure-feeding device of the present invention, the liquid pressure-feeding capacity per unit time can be increased by increasing the exhaust capacity and rapidly opening the check valve on the inflow side.

1 is a schematic configuration diagram showing a liquid pumping device having an exhaust valve structure according to a first embodiment of the present invention; FIG. 1. It is a schematic block diagram which shows the state different from FIG. 1 of the same liquid pumping apparatus. It is a longitudinal cross-sectional view which shows the same liquid pumping apparatus. It is a longitudinal cross-sectional view showing the first state in which the discharge valve of the liquid pumping device is closed. It is a longitudinal cross-sectional view showing a second state in which the discharge valve of the liquid pumping device is closed. It is a longitudinal cross-sectional view showing a state in which a discharge valve of the same liquid pumping device is open. (A) and (B) are vertical cross-sectional views showing a discharge valve of a conventional liquid pumping device.

Preferred embodiments of the present invention will be described below with reference to the drawings. 1 and 2 are schematic configuration diagrams showing a liquid pumping device having an exhaust valve structure according to a first embodiment of the present invention. The pumping device 1 pressurizes the liquid W stored in the container 2 with the driving fluid F introduced into the container 2 and discharges it to the outside of the container 2 . 1 shows the state in which the liquid W is flowing in, and FIG. 2 shows the state in which the liquid W is discharged. The liquid W in this embodiment is water, in particular condensate from steam pipes, steam equipment and the like. Further, the driving fluid F in this embodiment is steam.

The container 2 is provided with a liquid inlet 4 through which the liquid W flows and a liquid outlet 6 through which the liquid W flows out. A liquid inflow passage 8 is connected to the liquid inflow port 4 , and a liquid outflow passage 10 is connected to the liquid outflow port 6 . An inflow side check valve 12 is connected between the liquid inflow port 4 and the liquid inflow passage 8 , and an outflow side check valve 14 is connected between the liquid outflow port 6 and the liquid outflow passage 10 .

At the top of the container 2 , a driving fluid inlet 16 for allowing the driving fluid F to flow into the container 2 and a driving fluid outlet 18 for discharging the driving fluid F in the container 2 to the outside of the container 2 are provided. A driving fluid inflow passage 17 is connected to the driving fluid inflow port 16 , and a driving fluid outflow passage 19 is connected to the driving fluid outflow port 18 . The pumping device 1 has a driving valve (intake valve) 20 that opens and closes the driving fluid inlet 16 and a discharge valve (exhaust valve) 22 that opens and closes the driving fluid outlet 18 .

A float 24 for detecting the liquid level WL of the liquid W stored in the container 2 is accommodated inside the container 2 . Drive valve 20 and discharge valve 22 are connected to float 24 via actuation member 26 . The actuating member 26 has a known structure, and consists of a plurality of link members 26a and a single spring member 26b that are rotatably connected to each other. The operating member 26 operates the drive valve 20 and the discharge valve 22 based on the liquid level WL detected at the float 24 . In other words, the float 24 and operating member 26 constitute the drive source for the drive valve 20 and the discharge valve 22 .

When the liquid level WL shown in FIG. 1 is low, the float 24 floating on the liquid W is also at a low position. At this time, the operation of the operating member 26 causes the drive valve 20 to close and the discharge valve 22 to open. That is, the inflow of the driving fluid F into the container 2 is blocked, and the internal space of the container 2 is open to the atmosphere. When the liquid level WL is low, the pressure inside the container 2 is low. On the other hand, since the pressure inside the container 2 is low, the outflow side check valve 14 is closed.

When the liquid W flows into the container 2, the liquid level WL rises, and the float 24 also rises accordingly. When the liquid level WL exceeds a specified value, as shown in FIG. 2, the actuation member 26 operates to open the drive valve 20 and close the discharge valve 22 . That is, the driving fluid F flows into the container 2, and the discharge of the driving fluid F from the container 2 to the outside is prevented. As a result, the pressure inside the container 2 increases, so that the liquid W in the container 2 opens the outflow side check valve 14 and is discharged from the liquid outflow port 6 through the liquid outflow passage 10 to the outside of the container 2. . On the other hand, since the pressure inside the container 2 is high, the inflow side check valve 12 is closed.

When the liquid W is discharged out of the container 2, the liquid level WL drops. Along with this, the float 24 also descends and returns to the state shown in FIG. Thereafter, the state of FIG. 1 and the state of FIG. 2 are repeated, and the liquid W is pressure-fed.

Next, details of the structure of the discharge valve 22 will be described with reference to FIGS. Since the structure of the drive valve 20 (FIG. 1) is the same as a known one, its explanation is omitted. As shown in FIG. 3, an operating member 26 is detachably attached to the container 2 with a bolt B. As shown in FIG. An actuating member 26 is arranged inside the container 2 and has a float 24 attached to one end thereof. That is, the float 24 is supported by the container 2 via the actuation member 26 . On the other hand, a power transmission member 28 is connected to the other end of the operating member 26 . The power transmission member 28 transmits the drive force of the drive sources 24 and 26 to the discharge valve 22 .

As shown in FIG. 4 , the discharge valve 22 of this embodiment has a main exhaust passage 30 for discharging the driving fluid F in the container 2 . Specifically, a cylindrical valve seat member 32 is attached to the drive fluid outlet 18 , and a hollow hole of the valve seat member 32 constitutes the main exhaust passage 30 . That is, the main exhaust passage 30 communicates the internal space of the container 2 and the driving fluid outflow passage 19 .

The exhaust valve 22 has a main exhaust valve 34 that opens and closes the main exhaust passage 30 . The main exhaust valve 34 has a cylindrical main valve body 36 . The main valve body 36 closes the main exhaust passage 30 at one axial end (upper end in FIG. 4). That is, the edge of the other axial end surface (lower end surface in FIG. 4) of the valve seat member 32 constitutes the main valve seat 35 on which the main valve body 36 is seated. A pilot exhaust passage 42 is formed inside (hollow hole) of the main valve body 36 . The pilot exhaust passage 42 communicates the space inside the container 2 with the main exhaust passage 30 . The pilot exhaust passage 42 is set to have a passage area smaller than that of the main exhaust passage 30 . Details of the pilot exhaust passage 42 will be described later.

The main exhaust valve 34 further includes a disk-shaped bottom plate 38 extending radially from the other end of the main valve body 36 (lower end in FIG. 4), and a bottom plate 38 extending radially from the bottom plate 38 to the other end in the axial direction (lower end in FIG. 4). ). In the main exhaust valve 34 of this embodiment, a main valve body 36, a bottom plate 38, and a cylindrical portion 40 are integrally formed.

A first spring member 44 is interposed between the main valve seat 35 and one end face 38a of the bottom plate 38 (upper end face in FIG. 4). The first spring member 44 applies a spring force to the main exhaust valve 34 in a direction away from the main valve seat 35 (downward in FIG. 4). The first spring member 44 is, for example, a compression coil spring.

The exhaust valve 22 further has a pilot exhaust valve 46 that opens and closes the pilot exhaust passage 42 . The pilot exhaust valve 46 has a rod-shaped pilot valve body 48 . The pilot valve body 48 closes the pilot exhaust passage 42 at one axial end (upper end in FIG. 4). That is, the edge of the other axial end surface 38b (lower end surface in FIG. 4) of the bottom plate 38 constitutes the pilot valve seat 50 on which the pilot valve element 48 is seated. A power transmission member 28 (FIG. 3) is connected to the other end of the pilot exhaust valve 46 (lower end in FIG. 4). That is, the pilot exhaust valve 46 is connected via the power transmission member 28 to the float 24 (FIG. 3) that is part of the drive source.

The pilot exhaust valve 46 further has a flange portion 52 extending like a flange from the pilot valve body 48 . The outer diameter of the flange portion 52 is set slightly smaller than the inner diameter of the tubular portion 40 . A second spring member 54 is interposed between the other end surface 38b of the bottom plate 38 and one end surface 52a of the flange portion 52 (upper end surface in FIG. 4). The second spring member 54 applies a spring force to the pilot exhaust valve 46 in the direction away from the pilot valve seat 50 (downward in FIG. 4) and in the direction of seating on the main valve seat 35 (upward in FIG. 4). A spring force is applied to the main exhaust valve 34 . The second spring member 54 is, for example, a compression coil spring.

The valve opening force required to open the main exhaust valve 34 without the first spring member 44 is f, the spring force of the first spring member 44 is K1, and the spring force of the second spring member 54 is K2. In this embodiment, the spring force K1 of the first spring member 44 is set equal to or greater than the valve opening force f and smaller than the sum of the valve opening force f and the spring force K2 of the second spring member 54. (f≦K1<(f+K2)).

Next, the operation of the discharge valve 22 of this embodiment will be described with reference to FIGS. 4 to 6. FIG. Prior to this, the operation of the conventional discharge valve 100 will be described with reference to FIGS. 7(A) and (B). In FIG. 7A, when the pressure difference (pressure difference) between the container interior 102 and the driving fluid outflow passage 104 is P, and the cross-sectional area of the exhaust valve port 106 is A1, the exhaust valve 100 is opened (closed). is P×A1 (F10=P×A1).

FIG. 7B shows an example in which the cross-sectional area A2 of the exhaust valve port 106 is larger than that in FIG. 7A (A2>A1). Therefore, in FIG. 7B, the force F20 required to open (close) the discharge valve 100 is P×A2 (F20=(P×A2)>F10).

In the conventional liquid pumping device shown in FIG. 7A, the opening area of the exhaust valve port 106 is small, so the exhaust capacity is low, and the inflow side check valve (the inflow side check valve 12 in FIG. 1) does not open. was delayed, slowing the flow of liquid into the container. However, if the opening area A2 is increased as shown in FIG. 7B, a valve opening force F2 larger than the valve opening force F1 required to open the exhaust valve port with a small opening area is required.

4, the passage area of the main exhaust passage 30 is A2, and the passage area of the pilot exhaust passage 42 is A1. That is, the passage area of the pilot exhaust passage 42 is the same as the opening area A1 in FIG. 7(A), and the passage area of the main exhaust passage 30 is the same as the opening area A2 in FIG. 7(B). Therefore, the valve opening force f required to open the main exhaust valve 34 without the first spring member 44 is the force F20 in FIG. 7B (f=F20).

At this time, assuming that the force required to open (close) the main exhaust valve 34 is the first force F1, and the force required to open the pilot exhaust valve 46 is the second force F2, the main The first force F1 required to open (close) the exhaust valve 34 is F20+K2-K1 (F1=F20+K2-K1=f+K2-K1). On the other hand, the second force F2 required to open (close) the pilot exhaust valve 46 is F10-K2 (F2=F10-K2).

When the liquid level WL drops from the state in which the discharge valve 22 is closed (the state in which the liquid W is pumped) in FIG. do. When this force reaches the second F2, the pilot exhaust valve 46 opens to the state shown in FIG. At this time, the force F2 required to open (close) the pilot exhaust valve 46 is F10-K2. (F2<F10).

In the state of FIG. 5, the second spring member 54 expands and the amount of contraction is almost zero, that is, the spring force K2 of the second spring member 54 is almost zero (K2≈0). Therefore, the first force F1 required to open the main exhaust valve 34 is F20-K1 (F1=F20-K1=f-K1). As described above, the spring force K1 of the first spring member 44 is set to be greater than or equal to the valve opening force f required to open the main exhaust valve 34 without the first spring member 44 (f≦K1). Therefore, the first force F1 becomes zero (F1=0), and the pressure of the driving fluid F in the driving fluid outflow passage 19 opens the main exhaust valve 34, resulting in the state shown in FIG. 6 (inflow state). Become. In this way, the main exhaust valve 34 with a large passage area is opened with the force required to open the pilot exhaust valve 46 with a small passage area.

When the liquid level WL rises from the state in which the discharge valve 22 is open (inflow state) in FIG. Here, since the contraction amount of the second spring member 54 is almost zero, that is, the spring force K2 of the second spring member 54 is almost zero (K2≈0), the main exhaust valve 34 is closed. The first force F1 required for is F20-K1 (F1=F20-K1=f-K1). As described above, since the spring force K1 of the first spring member 44 is set to f≦K1, the first force F1 becomes zero (F1=0) and the main exhaust valve 34 closes.

When the float 24 (FIG. 3) rises further from the state of FIG. 5 and this force reaches F2, the pilot exhaust valve 46 closes and enters the state of FIG. 4 (pumping state). After that, the operations of FIGS. 4 to 6 are repeated.

According to the above configuration, when the valve is opened, the pilot exhaust valve 46 having a small passage area is opened first by the driving force from the driving sources 24 and 26 in FIG. 1 and the spring force k2 of the second spring member 54 in FIG. . When the pilot exhaust valve 46 opens, the spring force of the second spring member 54 becomes substantially zero. In other words, the force exerted by the second spring member 54 in the direction of seating the main exhaust valve 34 on the main valve seat 35 disappears. As a result, the driving force from the driving source 24 and the spring force K1 of the first spring member 44 open the main exhaust valve 34 having a large passage area. Thus, since the main exhaust valve 34 is opened by the spring force K1 of the first spring member 44, the second force F2 required to open the pilot exhaust valve 46 with a small passage area is enough to open the main exhaust valve with a large passage area. Valve 34 opens. As a result, the exhaust capacity increases, the inflow side check valve 12 (FIG. 1) opens quickly, and the liquid pumping capacity per unit time can be increased.

The spring force K1 of the first spring member 44 is greater than or equal to the valve opening force f required to open the main exhaust valve 34 without the first spring member 44, and the valve opening force f and the second spring Since it is set to be smaller than the sum of the spring force K2 of the member 54 (f≦K1<(f+K2)), a large force can be obtained, and the operation of the main exhaust valve 34 is stabilized.

The main exhaust valve 34 has a cylindrical main valve body 36 which has a pilot exhaust passage 42 formed therein and is seated on a main valve seat 35 at one end in the axial direction. It has an extending disc-shaped bottom plate 38 and a cylindrical portion 40 extending from the bottom plate 38 to the other end side in the axial direction. A pilot valve seat 50 is formed on the other end surface 38 b of the bottom plate 38 . The pilot exhaust valve 46 has a rod-shaped pilot valve body 48 that moves axially inside the cylindrical portion 40 , and a flange portion 52 that extends like a flange from the pilot valve body 48 . and one end surface 52a of the flange portion 52, a second spring member 54 is interposed. According to this configuration, the exhaust valve structure of this embodiment can also be applied to a conventional liquid pumping device.

The present invention is not limited to the above embodiments, and various additions, changes, or deletions are possible without departing from the scope of the present invention. Accordingly, such are also included within the scope of this invention.

1 liquid pumping device 2 container 24 float (driving source)
26 actuating member (driving source)
30 main exhaust passage 34 main exhaust valve 35 main valve seat 36 main valve body 38 bottom plate 40 cylindrical portion 42 pilot exhaust passage 44 first spring member 46 pilot exhaust valve 48 pilot valve body 50 pilot valve seat 52 flange portion 54 second Spring member f Valve opening force K1 Spring force of first spring member K2 Spring force of second spring member F Driving fluid W Liquid

Claims (4)

An exhaust valve structure for a liquid pumping device that pressurizes a liquid stored in a container by a driving fluid that has flowed into the container and discharges the liquid to the outside of the container,
a main exhaust passage for discharging the driving fluid in the container;
a pilot exhaust passage communicating between the space in the container and the main exhaust passage and having a passage area smaller than that of the main exhaust passage;
a main exhaust valve that opens and closes the main exhaust passage;
a pilot exhaust valve that is connected to a drive source and opens and closes the pilot exhaust passage;
a first spring member that applies force to the main exhaust valve in a direction away from the main valve seat;
a second spring member that applies force to the pilot exhaust valve in a direction away from the pilot valve seat and applies force to the main exhaust valve in a direction to be seated on the main valve seat;
An exhaust valve structure for a liquid pumping device. 2. The exhaust valve structure for a liquid pressure-feeding device according to claim 1, wherein a spring force of said first spring member at the time of valve opening is sufficient to open said main exhaust valve without said first spring member. An exhaust valve structure for a liquid pumping device, wherein the exhaust valve structure is set to be greater than a required valve opening force and less than the sum of the valve opening force and the spring force of the second spring member when the valve is opened . 3. The exhaust valve structure for a liquid pumping apparatus according to claim 1, wherein the main exhaust valve is
a cylindrical main valve body having the pilot exhaust passage formed therein and seated on the main valve seat at one end in the axial direction;
a disc-shaped bottom plate extending radially from the other end of the main valve body;
a cylindrical portion extending from the bottom plate to the other end side in the axial direction,
A first spring member is interposed between the main valve seat and one end surface of the bottom plate,
An exhaust valve structure for a liquid pumping device, in which the pilot valve seat is formed on the other end surface of the bottom plate. 4. In the exhaust valve structure of the liquid pumping device according to claim 3, the pilot exhaust valve
a rod-shaped pilot valve element that moves axially inside the cylindrical portion;
a flange portion extending in a flange shape from the pilot valve body,
An exhaust valve structure for a liquid pumping device, in which a second spring member is interposed between the other end surface of the bottom plate and one end surface of the flange portion.

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