JP7404135B2 - How to maintain pump equipment, water supply equipment, and pump equipment - Google Patents

Description

The present invention relates to a pump device, a water supply device, and a maintenance method for a pump device.

A pump device including a pump and a motor is known (see, for example, Patent Document 1).

Japanese Patent Application Publication No. 7-224781

To perform maintenance work on components of the pump system, an operator may pull the motor from the pump. In a typical pump device, an impeller is housed within a cylindrical pump casing. Therefore, when pulling out the motor, the operator pulls out the motor in the axial direction of the pump casing while removing all fasteners that connect the pump casing and the motor. Such a pulling operation is called back pullout. In order to perform back pullout, it is necessary to provide a space behind the motor for back pullout. As a result, the pump device must be installed in a relatively large space.

However, pump equipment cannot be installed in locations where there are nearby obstructing structures (walls in buildings, underground spaces, water tanks, etc.), such as along building walls, underground spaces, or spaces below or next to water tanks. There may also be requests to install one. Therefore, it is desired to provide a pump device that can perform maintenance work even in such an installation environment.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a pump device, a water supply device, and a maintenance method for a pump device that allow easy maintenance work without being restricted by the installation environment.

In one aspect, a pump device is provided that includes an impeller, a rotating shaft to which the impeller is fixed, and a casing assembly that accommodates the impeller. The casing assembly includes a suction flange formed with a suction port connectable to a suction pipe and having an annular shape extending perpendicularly to the axial direction of the rotating shaft, and a pump casing connected to the suction flange. Be prepared.

In one aspect, the suction flange has a casing contact surface that is in contact with the pump casing and extends parallel to an end wall of the pump casing, and the suction flange only contacts the casing contact surface with the pump casing. is connected to the suction casing in contact with the end wall of the suction casing.
In one aspect, the casing assembly includes a flange supporter that supports the suction flange, and the suction flange has a threaded hole into which a fastener can be inserted through a through hole formed in the flange supporter. ing.
In one aspect, the pump device includes a stator and a rotor that rotate the rotating shaft, a motor casing that accommodates the stator and the rotor, and a fastening member that fastens the casing assembly and the motor casing. , wherein the fastening member extends through the casing assembly and is inserted into an insertion hole formed in the motor casing.

In one aspect, the suction flange is made of resin or metal.
In one aspect, the pump casing has a discharge port connectable to a discharge pipe, and the pump device includes a discharge pipe supporter that supports the discharge pipe.

In one aspect, a water supply device is provided that includes the pump device described above and a control panel provided with an operation panel. The operation panel is arranged facing in the same direction as the direction in which the pump casing is pulled out.

In one aspect, a method for maintaining the pump device described above is provided. With the suction pipe connected to the suction flange, the operation of the pump device is stopped, the connection between the pump casing and the suction flange is released, and the pump casing is pulled out to the side of the suction flange. .

In one aspect, the step of pulling out the pump casing to the side of the suction flange is performed while the suction flange is supported by a flange supporter that supports the suction flange.
In one aspect, the step of pulling out the pump casing to the side of the suction flange is performed with the discharge pipe supported by a discharge pipe supporter that supports the discharge pipe connected to the discharge port of the pump casing. be exposed.

The pump device includes a suction flange and a pump casing connected to the suction flange so as to be removable to the side of the suction flange. Therefore, movement of the pump casing in the side pull-out direction is not hindered by the suction flange, and the pump casing can be easily pulled out in the side pull-out direction. As a result, the pump device allows an operator to easily perform maintenance work without being restricted by the installation environment.

FIG. 1 is a diagram showing an embodiment of a pump device. FIG. 3 shows a perspective view of a pump device connected to a suction pipe and a discharge pipe. FIG. 3 shows a suction flange connected to a suction casing. It is a figure which shows the flange supporter which supports a suction flange. FIG. 2 is a perspective view showing a water supply device including the pump device according to the embodiment shown in FIG. 1. FIG. It is a figure which shows the discharge pipe supporter which supports a discharge pipe. FIG. 3 is a diagram showing the pump casing and motor pulled out in the side pull-out direction. FIG. 3 is an enlarged view of the intermediate casing. 9 is a view seen from the direction of line A in FIG. 8. FIG. 9 is a view seen from the direction of line B in FIG. 8. FIG. It is a sectional view showing a fitting structure of a pump casing. It is a figure which shows the comparative example for demonstrating the effect of the intermediate casing based on this embodiment. It is a figure for explaining the effect of the intermediate casing concerning this embodiment. It is a figure showing a partition member. 12 is an enlarged view of the seal structure shown in FIG. 11. FIG. It is a figure showing other embodiments of a seal structure. It is a figure showing other embodiments of a pump device. It is a figure which shows yet another embodiment of a pump device.

Embodiments of the present invention will be described below with reference to the drawings. In the drawings described below, the same or corresponding components are given the same reference numerals and redundant explanations will be omitted. In the plurality of embodiments described below, the configuration of one embodiment that is not particularly described is the same as that of the other embodiments, and thus the redundant explanation will be omitted.

FIG. 1 is a diagram showing one embodiment of a pump device 1. As shown in FIG. As shown in FIG. 1, a pump device 1, which is an example of a mechanical device, includes a pump 2, which is an example of a rotating machine that transfers fluid (liquid in this embodiment), and a motor (electric motor) 3 that operates the pump 2. A mechanical device comprising: In this embodiment, the pump 2 is a horizontal shaft multi-stage pump. The pump 2 includes a rotating shaft 10, a plurality of (in this embodiment, three stages) impellers 6A to 6C fixed to the rotating shaft 10, and a pump casing 7 that accommodates the plurality of impellers 6A to 6C. A suction flange 200 is detachably connected to the pump casing 7. Hereinafter, the pump casing 7 may be simply referred to as a casing.

The rotating shaft 10 is connected to a motor 3 as a drive source. The motor 3 rotates the rotating shaft 10 by driving the motor 3 . The impellers 6A to 6C rotate together with the rotating shaft 10. The motor 3 includes a rotor 11 fixed to a rotating shaft 10, a stator 12 arranged to surround the rotor 11, and a motor casing that houses the rotor 11 and stator 12. It is equipped with 13. The stator 12 is fixed to the inner peripheral surface of the motor casing 13. Rotor 11 and stator 12 are rotating elements.

In one embodiment, the motor 3 may be provided with an inverter (not shown) arranged in series along the axis CL direction of the rotating shaft 10. The combination of motor 3 and inverter is called a motor assembly. In this case, the pump device 1 is a mechanical device including a pump 2 and an electric motor assembly.

The combination of pump casing 7 and suction flange 200 is casing assembly 250. The pump casing 7 includes a suction casing 16 connected to a suction flange 200, a discharge casing 18 having a discharge port 17, and an intermediate casing 20 disposed between the suction casing 16 and the discharge casing 18. .

As shown in FIG. 1, the suction flange 200, the suction casing 16, the intermediate casing 20, and the discharge casing 18 are arranged in series in this order. The suction flange 200 has a suction port 15 that opens in the direction of the axis CL of the rotating shaft 10, and the discharge port 17 of the discharge casing 18 opens in a direction perpendicular to the direction of the axis CL.

In the embodiment shown in FIG. 1, the impeller 6A is housed in the suction casing 16, the impeller 6B is housed in the intermediate casing 20, and the impeller 6C is housed in the discharge casing 18. When the impellers 6A to 6C fixed to the rotating shaft 10 rotate, liquid is introduced into the pump casing 7 through the suction port 15 of the suction flange 200. The liquid introduced into the pump casing 7 is pressurized step by step by the impellers 6A to 6C, and is transferred to the outside of the pump 2 through the discharge port 17. Hereinafter, the impellers 6A to 6C may be simply referred to as an impeller 6 without distinction. The impeller 6 may be made of resin or metal.

FIG. 2 is a diagram showing a perspective view of the pump device 1 connected to the suction pipe P1 and the discharge pipe P2. As shown in FIG. 2, the suction port 15 of the suction flange 200 is connected to the suction pipe P1, and the discharge port 17 of the discharge casing 18 is connected to the discharge pipe P2. Pump device 1 is arranged on base B. More specifically, the motor 3 is supported by a motor supporter 205 fixed to the base B, and the pump casing 7 is supported by a flange supporter 215 via the suction flange 200. Details of the configuration of the flange supporter 215 will be described later.

As shown in FIG. 2, a plurality of reinforcing ribs 201 are formed on the suction flange 200 to improve the rigidity of the suction flange 200. The plurality of reinforcing ribs 201 are arranged at equal intervals along the circumferential direction of the suction flange 200 and extend radially in the radial direction of the suction flange 200. The number of reinforcing ribs 201 is not limited to this embodiment.

FIG. 3 shows a suction flange 200 connected to the suction casing 16. Note that in FIG. 3, illustration of the reinforcing rib 201 is omitted. The suction flange 200 is made of a member (metal (for example, stainless steel) or resin) that has an annular shape and extends perpendicularly to the direction of the axis CL of the rotating shaft 10 . The suction flange 200 has a main body portion 210 in which reinforcing ribs 201 are formed, and a suction port portion 211 that protrudes from the main body portion 210.

The main body portion 210 and the suction port portion 211 are integrally molded members and are arranged concentrically with the rotating shaft 10. The suction flange 200 has a suction port side surface (first surface) 200a on which reinforcing ribs 201 are formed, and a casing contact surface (second surface) 200b on the opposite side to the first surface 200a. . The first surface 200a and the second surface 200b are both end surfaces of the main body portion 210.

As shown in FIGS. 2 and 3, the suction flange 200 is fastened to the pump casing 7 (more specifically, the suction casing 16) by a plurality of fastening members (for example, through bolts) 8. Although four fastening members 8 are depicted in the embodiment shown in FIG. 2, the number of fastening members 8 is not limited to the embodiment shown in FIG.

The fastening member 8 fastens the casing assembly 250 (ie, the pump casing 7 and the suction flange 200) and the motor casing 13. More specifically, as shown in FIG. 1, the fastening member 8 extends through the suction flange 200, the suction casing 16, the intermediate casing 20, and the discharge casing 18, and is inserted into the motor casing 13. . The motor casing 13 is made of a metal member and has an insertion hole 13a into which the fastening member 8 is inserted. A threaded groove (not shown) into which the fastening member 8 can be screwed is formed in the insertion hole 13a.

With such a configuration, an operator places the suction casing 16, intermediate casing 20, and discharge casing 18 in this order between the suction flange 200 and the motor casing 13, and in this state, attaches the fastening member 8 to the motor casing. 13 into the insertion hole 13a. Thereafter, the operator tightens the fastening member 8, so that the suction flange 200, the suction casing 16, the intermediate casing 20, the discharge casing 18, and the motor casing 13 are firmly fastened to each other. In this embodiment, the fastening member 8 is screwed into an insertion hole 13a formed in a metal motor casing 13. With such a configuration, the fastening members 8 can be forcefully tightened, and as a result, the number of fastening members 8 can be reduced.

As shown in FIG. 3, the suction casing 16 has an end wall 19 that closely contacts the suction flange 200. The end wall 19 has a communication hole 19a formed in the center thereof. The communication hole 19a communicates with the suction port 15 of the suction flange 200, and has a diameter larger than the diameter of the suction port 15. A second surface (ie, casing contact surface) 200b of the suction flange 200 is formed with an annular seal groove 203 into which a seal member 202 such as an O-ring is mounted. This seal groove 203 is arranged concentrically with the rotating shaft 10. When the suction flange 200 is fastened to the suction casing 16 by the fastening member 8, the sealing member 202 is compressed by the second surface 200b of the suction flange 200 and the end wall 19 of the suction casing 16. As a result, the seal member 202 can prevent liquid from leaking between the suction flange 200 and the suction casing 16.

By configuring the suction flange 200 to which the suction pipe P1 is connected from metal, the following effects can be achieved. A large load from the suction pipe P1 acts on the suction flange 200, and the suction flange 200 made of metal has a strength capable of withstanding the large load from the suction pipe P1. Therefore, troubles such as separation of the suction pipe P1 from the pump device 1 and deformation or damage of the suction pipe P1 can be prevented, and as a result, the pump device 1 can be operated safely.

FIG. 4 is a diagram showing a flange supporter 215 that supports the suction flange 200. As shown in FIGS. 2 and 4, the pump device 1 (more specifically, the casing assembly 250) may further include a flange supporter 215 that supports the suction flange 200. As shown in FIG. 4, the flange supporter 215 has an L-shaped cross-section.

The flange supporter 215 includes a suction flange side part 215a connected to the suction flange 200, a base side part 215b connected to the base B, and a connection part 215c connecting the suction flange side part 215a and the base side part 215b. have. The suction flange side portion 215a and the suction flange 200 are fastened together by a fastener 216, and the base side portion 215b and the base B are fastened together by a fastener 217. More specifically, the suction flange 200 has a screw hole 219 into which a fastener 216 can be inserted through a through hole 218 formed in the flange supporter 215.

A threaded groove (not shown) into which the fastener 216 can be screwed is formed in the threaded hole 219 . Therefore, the operator inserts the fastener 216 into the screw hole 219 of the suction flange 200 through the through hole 218 of the flange supporter 215 and tightens the fastener 216, thereby fastening the flange supporter 215 and the suction flange 200 to each other. . As a result, flange supporter 215 supports suction flange 200. In this way, the flange supporter 215 can receive the load of the suction pipe P1 via the suction flange 200.

FIG. 5 is a perspective view showing a water supply device 300 including the pump device 1 according to the embodiment shown in FIG. As shown in FIG. 5, the water supply device 300 includes a plurality of (two in FIG. 5) pump devices 1, a base B on which the plurality of pump devices 1 are placed, and controls the operation of the pump devices 1. It includes a control panel 301 and a support member 302 that supports the control panel 301. The control panel 301 is provided with an operation panel 312. In FIG. 5, the operation panel 312 is arranged facing the rear of the motor 3.

Here, as shown in FIG. 5, with the pump device 1 as a reference, the front side of the pump device 1 is defined as the "front", the back side of the pump device 1 is defined as the "rear", and the lateral side of the pump device 1 is defined as the "front". is defined as "lateral". Therefore, behind the motor 3 means a position on the rear side of the motor 3.

The control panel 301 is supported by a support member 302 that extends above the motor 3 and is disposed above the motor 3. The support member 302 includes leg portions 302a that are fixed to the base B and extend upward from the surface of the base B, and a pedestal 302b that is fixed to the leg portions 302a and on which the control panel 301 is placed. There is. The pedestal 302b extends in a direction parallel to the surface of the base B (that is, in the horizontal direction), and has a size on which the control panel 301 can be placed. The pedestal 302b has a wide shape extending parallel to the longitudinal direction of the base B. Here, the longitudinal direction of the base B is defined as the direction perpendicular to the width direction of the base B. The width direction of the base B is defined as a direction parallel to the axis CL direction of the rotating shaft 10.

In the embodiment shown in FIG. 5, the pump casing 7 and the motor 3 can be pulled out in a direction perpendicular to the radial direction of the suction flange 200, that is, to the rear of the motor 3 (back pull-out direction). Furthermore, the pump casing 7 and the motor 3 can also be pulled out in the radial direction of the suction flange 200, that is, to the side of the motor 3 (in the side pull-out direction). The radial direction of the suction flange 200 is a direction perpendicular to the axis CL direction, in other words, a direction parallel to the longitudinal direction of the base B.

When the operator pulls out the pump casing 7 and the motor 3 in the back pull-out direction, the control panel 301 is preferably arranged so that the operation panel 312 faces the rear of the motor 3. In this case, the operator can operate the operation panel 312 from a position behind the motor 3, and can pull out the pump casing 7 and the motor 3 in the back pull-out direction from a position behind the motor 3. .

The pump casing 7 and the motor 3 are pulled out with the suction flange 200 connected to the suction pipe P1. More specifically, the operator stops the operation of the pump device 1, removes the fastening member 8, and separates the pump casing 7 from the suction flange 200 while the suction flange 200 is supported by the flange supporter 215. . Through such work, the operator can pull out the pump casing 7 and the motor 3 in the back pull-out direction while the suction pipe P1 is supported by the flange supporter 215 via the suction flange 200.

According to this embodiment, the pump casing 7 and the motor 3 can be pulled out simply by removing the fastening member 8 without removing the suction flange 200 from the suction pipe P1. 7 and the motor 3 can be easily maintained.

The fastening member 8 extends through the suction flange 200 and the pump casing 7 and is fastened to the motor casing 13, while the fastener 216 extends through the flange supporter 215 and is fastened to the suction flange 200. There is. Therefore, flange supporter 215 can continue to support suction flange 200 unless fastener 216 is removed. Therefore, by removing the fastening member 8 while leaving the fastener 216 in place, the operator can pull out the pump casing 7 and motor 3 while supporting the suction flange 200 with the flange supporter 215.

Even if the pump casing 7 and motor 3 are pulled out, the suction pipe P1 is supported by the flange supporter 215 via the suction flange 200, so the suction pipe P1 will not come off from the suction flange 200, and the suction pipe P1 will not be deformed. , it is possible to prevent problems such as damage.

FIG. 6 is a diagram showing the discharge pipe supporter 100 that supports the discharge pipe P2. In the embodiment shown in FIG. 6, the discharge pipe supporter 100 is a rod member extending upward from the base B, and supports the discharge pipe P2. The discharge pipe supporter 100 is arranged between two pump casings 7 and independently of these pump casings 7. Therefore, even if the pump casing 7 and motor 3 are pulled out, the discharge pipe supporter 100 can continue to support the discharge pipe P2. Although not shown, a pressure tank (not shown) connected to the discharge pipe P2 may be arranged between the two pump devices 1. In this case, the legs 302a of the support member 302 may be arranged to straddle the pressure tank.

FIG. 7 is a diagram showing the pump casing 7 and motor 3 pulled out in the side pull-out direction. As shown in FIG. 7, depending on the installation environment of the water supply device 300, the water supply device 300 may be arranged adjacent to the wall WL. In this case, since the wall WL is arranged near the motor 3 at a position on the rear side of the motor 3, it is difficult to pull out the pump casing 7 and the motor 3 in the back pull-out direction.

In the embodiment shown in FIG. 7, the pump casing 7 is connected to a suction flange 200 that has a disc shape and extends parallel to the axis CL direction of the rotating shaft 10. The casing contact surface 200b of the suction flange 200 and the end wall 19 of the suction casing 16 extend parallel to each other, and the suction flange 200 has only its casing contact surface 200b in contact with the end wall 19 of the suction casing 16. , connected to the suction casing 16. Therefore, movement of the pump casing 7 in the side pull-out direction is not inhibited by the suction flange 200, and the pump casing 7 and motor 3 can be pulled out in the side pull-out direction.

Furthermore, by disposing the discharge pipe supporter 100 between the leg portion 302a of the support member 302 and the pump casing 7, movement of the pump casing 7 in the side pull-out direction is not hindered by the discharge pipe supporter 100, and the discharge pipe Since the supporter 100 can support the discharge pipe P2, it can prevent the discharge pipe P2 from being deformed or damaged.

As shown in FIG. 7, the control panel 301 is placed on a pedestal 302b so that its direction can be changed. Therefore, when the water supply device 300 is arranged adjacent to the wall WL, the control panel 301 is preferably arranged so that the operation panel 312 faces the same direction as the side pull-out direction. With this arrangement, the operator can operate the operation panel 312 at a position on the side of the motor 3, and can pull out the pump casing 7 and the motor 3 in the side pull-out direction.

Hereinafter, the structures of the suction casing 16, the intermediate casing 20, and the discharge casing 18 will be described with reference to the drawings. In this embodiment, the suction casing 16, the intermediate casing 20, and the discharge casing 18 are made of resin. Examples of resins include polyamide (PA), polypropylene (PP), or polyphenylene sulfide (PPS). The resin suction casing 16, intermediate casing 20, and discharge casing 18 are lighter than the metal pump casing, and can reduce the overall material cost and processing cost of the pump casing 7. Since the pump casing 7 is subjected to the high pressure of the liquid moving inside it, the pump casing 7 must have a highly pressure-resistant structure.

In order to increase the pressure resistance of the pump casing 7, a method of increasing the wall thickness of the suction casing 16, intermediate casing 20, and discharge casing 18 can be considered. However, when the thickness of the resin is increased, it takes a long time for the melted resin to completely solidify during the manufacturing process. Furthermore, in this case, there is a possibility that a depression called a "sink mark" may be formed in the resin. In the worst case, cavities may be formed inside the resin. Furthermore, a phenomenon unique to resins called creep deformation may occur in resins. Creep deformation is a phenomenon in which resin is plastically deformed as a result of high pressure continuing to act on the resin for a long period of time. "Sink marks" and/or cavities can promote creep deformation. If creep deformation occurs in the resin, the pump casing may be damaged or liquid may leak from the pump casing.

The pump casing 7 according to this embodiment has a structure to solve the above-mentioned problems. In this embodiment, the suction casing 16, the intermediate casing 20, and the discharge casing 18 all have basically the same structure, so the structure of the intermediate casing 20 of the pump casing 7 will be explained with reference to the drawings below. I will explain.

FIG. 8 is an enlarged view of the intermediate casing 20. As shown in FIG. 8, the intermediate casing 20 made of resin includes an annular inner circumferential wall (inner wall or first circumferential wall) 21 having a size that can accommodate the impeller 6B therein, and An annular outer circumferential wall (outer wall or second circumferential wall) 22 is arranged, and an inner circumferential wall 21 and an outer circumferential wall 22 are arranged between the inner circumferential wall 21 and the outer circumferential wall 22 and reinforce the inner circumferential wall 21. and a reinforcing member 23 fixed to the. These inner circumferential wall 21, outer circumferential wall 22, and reinforcing member 23 are made of resin and are integrally molded members.

The thickness of the inner circumferential wall 21 and the thickness of the outer circumferential wall 22 are determined as necessary based on the strength of the pump casing 7. In one embodiment, the thickness of the inner circumferential wall 21 and the thickness of the outer circumferential wall 22 may be the same. In this case, from the viewpoint of the strength of the pump casing 7, the thickness of the part of the pump casing 7 that should be the thickest is determined, and the thickness of the inner peripheral wall 21 and The thickness of the outer peripheral wall 22 is made uniform. As a result, the pump casing 7 can be easily molded with resin. In other embodiments, the thickness of the inner circumferential wall 21 and the thickness of the outer circumferential wall 22 may be different. In this case, the thickness of the parts of the pump casing 7 that require strength can be made thicker, and the thickness of parts of the pump casing 7 that do not need strength can be made thinner. As a result, the material cost of the pump casing 7 can be reduced.

In one embodiment, at least one of the suction casing 16, the discharge casing 18, and the intermediate casing 20 includes an inner peripheral wall made of resin, an outer peripheral wall made of resin disposed to surround the inner peripheral wall, and an inner peripheral wall. and a resin reinforcing member disposed between the outer peripheral wall and the outer peripheral wall.

FIG. 9 is a diagram seen from the direction of line A in FIG. 8. FIG. 10 is a view seen from the direction of line B in FIG. 8. In FIGS. 9 and 10, illustration of the impeller 6B and the partition member 50 (described later) is omitted. The outer peripheral wall 22 is arranged to surround the inner peripheral wall 21. The inner circumferential wall 21 and the outer circumferential wall 22 are arranged concentrically with the rotating shaft 10 and constitute a double wall.

As shown in FIGS. 9 and 10, the reinforcing member 23 includes radial ribs 23a that extend toward the radially outer side of the inner circumferential wall 21 (that is, the radially inner side of the outer circumferential wall 22), and the inner circumferential wall 21 (and the outer circumferential wall). 22), an axial rib 23b extending in the axial direction. Here, the axial direction of the inner circumferential wall 21 (and the outer circumferential wall 22) means a direction parallel to the axis CL direction of the rotating shaft 10.

In the embodiment shown in FIGS. 9 and 10, the number of radial ribs 23a is 16, but the number of radial ribs 23a is not limited to this embodiment. Although the number of axial ribs 23b is 16, the number of axial ribs 23b is not limited to this embodiment. In one embodiment, the intermediate casing 20 may include only axial ribs 23b, and may optionally include radial ribs 23a.

In this embodiment, each of the four axial ribs 23b has a through hole 20a having a size that allows the aforementioned fastening member 8 (see FIG. 1) to pass therethrough. The through hole 20a extends parallel to the axial rib 23b.

The radial ribs 23a and the axial ribs 23b are alternately arranged at equal intervals along the circumferential direction of the inner peripheral wall 21 (and outer peripheral wall 22). Axial ribs 23b (or radial ribs 23a) are arranged between adjacent radial ribs 23a (or axial ribs 23b). More specifically, as shown in FIG. 8, the radial rib 23a is arranged between both ends 26, 27 of the axial rib 23b. In this embodiment, the radial rib 23a and the axial rib 23b are integrally molded members.

The high pressure of the liquid boosted by the impeller 6B acts on the inner circumferential wall 21 surrounding the impeller 6B, and stress is generated in the inner circumferential wall 21. In this embodiment, the intermediate casing 20 has a double wall structure and includes a reinforcing member 23. Therefore, the intermediate casing 20 can improve its pressure resistance and can withstand the pressure of the liquid acting inside the intermediate casing 20.

According to this embodiment, the intermediate casing 20 can sufficiently withstand the pressure of the liquid without increasing its wall thickness. Therefore, the wall thickness of the components of the intermediate casing 20 can be made relatively thin, and the formation of cavities due to the thickening of the resin wall does not occur. Moreover, in this embodiment, since an outer casing (for example, see Patent Document 2) that covers the components of the pump casing can be omitted, material costs and processing costs can be suppressed.

As shown in FIGS. 9 and 10, the intermediate casing 20 includes a partition wall 24 extending radially inward from the inner circumferential surface 21a of the inner circumferential wall 21 toward the rotating shaft 10. As shown in FIGS. The partition wall 24 is a member that partitions a front-stage pump chamber and a rear-stage pump chamber. The partition wall 24 has an annular shape, and an inner circumferential surface 24a is formed at the center thereof.

The thickness of the partition wall 24 is determined as necessary based on the strength of the pump casing 7. In one embodiment, the thickness of the partition wall 24 may be the same as the thickness of the inner circumferential wall 21 and the thickness of the outer circumferential wall 22. In this case, from the viewpoint of the strength of the pump casing 7, the thickness of the part of the pump casing 7 that should be the thickest is determined, and the thickness of the partition wall 24 is adjusted according to the determined thickness of the part of the pump casing 7. The thickness of the inner circumferential wall 21 and the thickness of the outer circumferential wall 22 are made uniform. As a result, the pump casing 7 can be easily molded with resin. In other embodiments, the thickness of the partition wall 24, the thickness of the inner circumferential wall 21, and the thickness of the outer circumferential wall 22 may be different. In this case, the thickness of the parts of the pump casing 7 that require strength can be made thicker, and the thickness of parts of the pump casing 7 that do not need strength can be made thinner. As a result, the material cost of the pump casing 7 can be reduced.

The intermediate casing 20 shown in FIG. 8 and the suction casing 16 adjacent to the intermediate casing 20 have a structure in which they fit into each other. Similarly, the intermediate casing 20 shown in FIG. 8 and the discharge casing 18 adjacent to the intermediate casing 20 have a structure in which they fit into each other.

The fitting structure of the pump casing 7 will be described below with reference to FIG. 11. FIG. 11 is a sectional view showing the fitting structure of the pump casing 7. The inner peripheral wall 21 has an annular end surface 21b located on the suction casing 16 side and an annular end surface 21c located on the discharge casing 18 side. An annular projection 28 is formed on the end surface 21b on the side of the suction casing 16 and extends in a direction (horizontal direction) away from the end surface 21b, and an annular projection 28 is formed on the end surface 21c on the side of the discharge casing 18 in a direction (horizontal direction) that extends away from the end surface 21c. An annular protrusion 29 extending in the horizontal direction is formed. The annular projection 29 has an annular inclined surface 29a formed inside thereof.

Each of the suction casing 16 and the discharge casing 18 has a double-walled structure similar to the intermediate casing 20. More specifically, the suction casing 16 includes an annular inner circumferential wall 31 having a size that can accommodate the impeller 6 therein, an annular outer circumferential wall 32 disposed outside the inner circumferential wall 31, and an annular outer circumferential wall 32 disposed on the outside of the inner circumferential wall 31. and a reinforcing member 33 fixed to the inner circumferential wall 31 and the outer circumferential wall 32 so as to reinforce the inner circumferential wall 31. The reinforcing member 33 includes an axial rib 33b having the same structure as the axial rib 23b described above. Although not shown, the reinforcing member 33 may include a radial rib having a similar structure to the radial rib 23a described above.

The discharge casing 18 has an annular inner circumferential wall 36 having a size that can accommodate the impeller 6 therein, an annular outer circumferential wall 37 disposed outside the inner circumferential wall 36, and the inner circumferential wall 36 and the outer circumferential wall 37. A reinforcing member 38 is provided between the inner circumferential wall 36 and the outer circumferential wall 37 so as to reinforce the inner circumferential wall 36 . The reinforcing member 38 includes a radial rib 38a (see FIG. 1) having a similar structure to the above-described radial rib 23a, and an axial rib 38b having a similar structure to the above-described axial rib 23b.

As shown in FIG. 11, the inner peripheral wall 31 of the suction casing 16 has an annular end surface 31a located on the intermediate casing 20 side. An annular projection 34 is formed on the end surface 31a and extends in a direction away from the end surface 31a. The annular projection 28 of the intermediate casing 20 and the annular projection 34 of the suction casing 16 fit into each other. Therefore, when the pump casing 7 is assembled, the annular projection 28 is in close contact with the end surface 31a, and the annular projection 34 is in close contact with the end surface 21b.

The annular projection 34 has an annular inclined surface 34a formed on the inside thereof. When the annular projection 34 comes into close contact with the end surface 21b, an annular projection 34a is formed between the annular inclined surface 34a, the end surface 21b, and the annular projection 28. A seal space 35 is formed. An annular seal member (for example, an O-ring) 40 is disposed in the seal space 35, and the seal member 40 seals the gap between the suction casing 16 and the intermediate casing 20.

The inner peripheral wall 36 of the discharge casing 18 has an annular end surface 36a located on the intermediate casing 20 side. An annular projection 39 is formed on the end surface 36a and extends in a direction away from the end surface 36a. The annular projection 29 of the intermediate casing 20 and the annular projection 39 of the discharge casing 18 fit into each other. Therefore, when the pump casing 7 is assembled, the annular projection 39 is in close contact with the end surface 21c, and the annular projection 29 is in close contact with the end surface 36a.

When the annular projection 29 comes into close contact with the end surface 36a, an annular seal space 55 is formed between the annular inclined surface 29a, the end surface 36a, and the annular projection 39. An annular seal member (for example, an O-ring) 56 is arranged in the seal space 55, and the seal member 56 seals the gap between the discharge casing 18 and the intermediate casing 20.

Such a fitting structure of the pump casing 7 may be a structure in which an intermediate casing different from the intermediate casing 20 is arranged between the suction casing 16 (and/or the discharge casing 18) and the intermediate casing 20. The same is true.

As shown in FIG. 11, the partition wall 24 is disposed between one end surface 21b and the other end surface 21c of the inner peripheral wall 21 in the axial direction of the inner peripheral wall 21. As shown in FIG. In one embodiment, the partition wall 24 may be arranged at a central portion of the inner peripheral wall 21 in the direction of the axis CL. The radial rib 23a is arranged between the inner circumferential wall 21 and the outer circumferential wall 22 so as to be aligned with the partition wall 24. This straight line is a line segment extending in a direction perpendicular to the axis CL direction of the rotating shaft 10.

The inner peripheral surface 21a of the inner peripheral wall 21 and the surface 24b of the partition wall 24 on the discharge casing 18 side are provided with a plurality of (in this embodiment, , 7) The guide vanes 45 are fixed. These plurality of guide vanes 45 are made of resin and are integrally formed with the inner circumferential wall 21 and the partition wall 24. The guide vanes 45 are provided not only in the intermediate casing 20 but also in the suction casing 16 and the discharge casing 18.

The plurality of guide vanes 45 are arranged at equal intervals along the circumferential direction of the inner circumferential wall 21 and are located outside the impeller 6 in the radial direction. The plurality of guide vanes 45 extend spirally, and each of the plurality of guide vanes 45 has a curved shape. A guide channel 47 through which liquid passes is formed between the guide vanes 45 adjacent to each other.

The inner circumferential surface 21a of the inner circumferential wall 21 and the surface 24c of the partition wall 24 on the side of the suction casing 16 are provided with a plurality of (in this embodiment, seven) holes for rectifying the liquid introduced into the impeller 6 of the next stage. A return vane 46 is fixed. The return vanes 46 are provided not only on the intermediate casing 20 but also on the discharge casing 18.

These plurality of return vanes 46 are made of resin and are integrally formed with the inner circumferential wall 21 and the partition wall 24. The plurality of return vanes 46 are arranged at equal intervals along the circumferential direction of the inner peripheral wall 21 and extend in a spiral shape. Each of the plurality of return vanes 46 has a curved shape. A return flow path 48 through which liquid passes is formed between the return vanes 46 adjacent to each other. The guide vane 45 and the return vane 46 constitute a guide device.

FIG. 12 is a diagram showing a comparative example for explaining the effects of the intermediate casing 20 according to the present embodiment. FIG. 13 is a diagram for explaining the effect of the intermediate casing 20 according to this embodiment. As shown in FIG. 12, when the impeller 600 rotates, the pressure of the liquid is increased by the impeller 600. The high pressure of the liquid acts radially outward of the impeller 600 and on the wall member 601 surrounding the impeller 600 (see arrows in FIG. 12).

The wall member 601 has an L-shaped cross section, and the rear end of the wall member 601 is a free end. In this way, since the distance from the front end of wall member 601 to the rear end of wall member 601 is long, the rigidity of wall member 601 against the pressure of the liquid is low. Therefore, when the high pressure of the liquid acts on the wall member 601, the amount of deformation of the wall member 601 increases, and a relatively large stress (first stress) is generated in the wall member 601.

As shown in FIG. 13, in this embodiment, the partition wall 24 is arranged between both end surfaces 21b and 21c of the inner peripheral wall 21. As shown in FIG. With this arrangement, the distance from the partition wall 24 to the end surface 21c (and the end surface 21b) becomes relatively short, so that the rigidity of the inner peripheral wall 21 is improved. Therefore, even if the high pressure Pa of the liquid acts on the inner circumferential wall 21, the amount of deformation of the inner circumferential wall 21 is small, and no large stress is generated in the inner circumferential wall 21, which is lower than the first stress explained in FIG. A small stress (second stress) is generated.

Under the condition that the interval between the front-stage impeller 6 and the rear-stage impeller 6 (so-called inter-stage pitch) is the same, as shown in FIGS. 12 and 13, the inner peripheral wall 21 and The length L1 of the pressure receiving portion of the outer peripheral wall 22 is shorter than the length L2 of the pressure receiving portion of the wall member 601. Therefore, the intermediate casing 20 can sufficiently withstand the pressure Pa of the liquid.

The liquid is pressurized in stages in multiple pump chambers and is transferred to the outside. The pressure of the liquid generated in the pump chamber at the rear stage is greater than the pressure of the liquid generated at the pump chamber at the front stage, so there is a pressure difference (so-called difference between stages) between the pump chamber at the front stage and the pump chamber at the rear stage. pressure) is generated. Therefore, as shown in FIG. 13, liquid pressure Pb as an interstage pressure difference acts on the surface 24b of the partition wall 24 on the discharge casing 18 side toward the surface 24c of the partition wall 24 on the suction casing 16 side. According to this embodiment, the guide device (ie, the guide vane 45 and the return vane 46) and the bulkhead 24 are integrally molded members, and the guide device functions as a reinforcing member (rib). Therefore, the intermediate casing 20 can have high rigidity and can withstand the liquid pressure Pb acting on the surface 24b of the partition wall 24 on the discharge casing 18 side.

Since the intermediate casing 20 according to the present embodiment has high rigidity, it can sufficiently withstand the high pressure of the liquid and can suppress the occurrence of creep deformation. Furthermore, since the intermediate casing 20 is made of resin, the entire weight of the pump device 1 can be reduced, and the cost of the entire pump device 1 can be reduced.

FIG. 14 is a diagram showing the partition member 50. As shown in FIGS. 1 and 14, the pump 2 further includes a partition member 50 that partitions the guide vane 45 and the return vane 46. The partition member 50 is an annular plate member and is arranged adjacent to the return vane 46 . The partition member 50 is made of resin and is a separate member from the intermediate casing 20. In one embodiment, partition member 50 may be constructed from metal such as stainless steel.

As shown in FIG. 14, a plurality of liquid inflow portions (fluid inflow portions) 51 are formed on the outer peripheral surface 50a of the partition member 50. The number of liquid inlets 51 corresponds to the number of guide channels 47 (and return channels 48). In this embodiment, the number of guide channels 47 and return channels 48 is seven, so seven liquid inlets 51 are formed. The plurality of liquid inflow portions 51 are arranged at equal intervals along the circumferential direction of the partition member 50.

Each of the plurality of liquid inflow portions 51 is a cutout extending from the outer peripheral surface 50a of the partition member 50 toward the inner peripheral surface 50b of the partition member 50. As long as the liquid can pass through the partition member 50, the shape of the liquid inflow portion 51 is not limited to this embodiment.

The liquid pressurized by the impeller 6 at the front stage passes through the guide channel 47 and the plurality of liquid inlets 51 . Thereafter, the liquid passes through the return flow path 48 and is guided to the impeller 6 at the next stage.

FIG. 15 is an enlarged view of the seal structure shown in FIG. 11. FIG. 16 is a diagram showing another embodiment of the seal structure. In the embodiment shown in FIG. 15, the seal member 40 is arranged in a seal space 35 formed between the annular inclined surface 34a, the end surface 21b, and the annular projection 28. In other words, the pump casing 7 has an annular triangular seal groove formed between the suction casing (first casing) 16 and the intermediate casing (second casing) 20, and the sealing member 40 It is installed in the seal groove.

In one embodiment, as shown in FIG. 16, the annular protrusion 34 does not have an annular sloped surface 34a, and instead, the inner circumferential wall 21 has an annular sealing groove 234 formed in its end surface 21b. You may. In other words, the pump casing 7 has an annular parallel seal groove formed between the suction casing (first casing) 16 and the intermediate casing (second casing) 20, and the sealing member 40 has an annular parallel seal groove. It is installed in the seal groove.

In the embodiment shown in FIG. 16, the annular seal groove 234 faces the annular projection 34, and a seal space 235 is formed between the annular seal groove 234 and the annular projection 34. The seal member 40 is arranged in this seal space 235.

In the embodiment shown in FIG. 15, the seal space 35 has a triangular shape whose size gradually decreases toward the outside in the radial direction of the pump casing 7. In the embodiment shown in FIG. 15, the triangular seal space 35 is formed by the cross section of the inner circumferential wall 31 and the cross section of the inner circumferential wall 21. In the embodiment shown in FIG. Due to this shape, the pressure of the liquid increased by the impeller 6 acts on the inner peripheral wall 21 and the inner peripheral wall 31, and when the inner peripheral wall 21 and the inner peripheral wall 31 deform toward the outside in the radial direction of the pump casing 7, There is a possibility that the size of the seal space 35 may change. As a result, the amount of squeezing of the seal member 40 changes, and the seal member 40 may not be able to properly prevent liquid leakage.

In the embodiment shown in FIG. 16, the seal member 40 disposed in the seal space 235 is compressed between the annular projection 34 (i.e., the end surface of the suction casing 16) and the seal compression surface 234a of the annular seal groove 234. There is. The annular projection 34 and the seal compression surface 234a extend parallel to each other along the radial direction of the pump casing 7.

In this way, the seal space 235 has a rectangular shape whose size does not change toward the outside in the radial direction of the pump casing 7. In the embodiment shown in FIG. 16, the rectangular seal space 235 is formed by the cross section of the inner peripheral wall 31 and the cross section of the inner peripheral wall 21. In the embodiment shown in FIG. Due to this shape, the pressure of the liquid increased by the impeller 6 acts on the inner peripheral wall 21 and the inner peripheral wall 31, and the inner peripheral wall 21 and the inner peripheral wall 31 are deformed toward the outside in the radial direction of the pump casing 7. However, since the size of the seal space 235 does not change, the amount of squeezing of the seal member 40 does not change, and the seal member 40 can appropriately prevent liquid leakage.

By providing the annular parallel seal groove in the pump casing 7 in this way, the seal member 40 can stably exhibit its sealing performance even if the pump casing 7 is deformed. The annular triangular seal groove can have effects such as reducing manufacturing costs. Therefore, based on various conditions for designing the pump device 1, an annular triangular seal groove and/or an annular parallel seal groove can be adopted.

Although not shown, an annular triangular seal groove (see FIG. 15) or an annular parallel seal groove (see FIG. 16) may be formed between the intermediate casing 20 and the discharge casing 18.
In one embodiment, an annular triangular seal groove (or an annular parallel seal groove) may be formed between the suction casing 16 and the intermediate casing 20, and an annular parallel seal groove (or an annular parallel seal groove) may be formed between the intermediate casing 20 and the discharge casing 18. Alternatively, an annular triangular seal groove) may be formed.

In the embodiment described above, the pump 2 is described as a horizontal shaft multistage pump, but the pump 2 may be a horizontal shaft single stage pump. FIG. 17 is a diagram showing another embodiment of the pump device 1. The configuration of this embodiment, which is not particularly described, is the same as the embodiment described above, so the redundant explanation will be omitted.

As shown in FIG. 17, the pump 2 includes a rotating shaft 10, an impeller 6 fixed to the rotating shaft 10, a suction flange 200 having a suction port 15, and a pump casing 7 having a discharge port 17. ing. The combination of suction flange 200 and pump casing 7 is casing assembly 250.

The pump casing 7 includes an inner circumferential wall 91 made of resin and having a size that can accommodate the impeller 6 therein, an outer circumferential wall 92 made of resin arranged to surround the inner circumferential wall 91, and an inner circumferential wall 91 and an outer circumferential wall. 92 and a reinforcing member (radial rib 93a and axial rib 93b) 93 made of resin. The inner circumferential wall 91, the outer circumferential wall 92, and the reinforcing member 93 are integrally molded members.

Also in the embodiment shown in FIG. 17, the fastening member 8 passes through the suction flange 200 and the pump casing 7, and is inserted into the insertion hole 13a formed in the motor casing 13. The pump device 1 is assembled by tightening the fastening member 8.

FIG. 18 is a diagram showing still another embodiment of the pump device. In the embodiment described above, the pump device 1 includes a motor casing 13 connected to a pump casing 7, and a rotating shaft 10 to which an impeller 6 and a rotor 11 are fixed. In the embodiment shown in FIG. 18, the pump device 1 includes a rotating shaft 10 to which the impeller 6 is fixed, and a drive shaft 320 to which the rotor 11 is fixed. These rotating shaft 10 and drive shaft 320 are connected to each other via a coupling (shaft joint) 330.

As shown in FIG. 18, the pump casing 7 and the motor casing 13 are spaced apart from each other and are located on both sides of the coupling 330. With this configuration, the pump casing 7 can be pulled out in the side pull-out direction while the motor 3 is supported by the motor supporter 205 and the suction flange 200 is supported by the flange supporter 215. More specifically, the operator disconnects the rotating shaft 10 and the drive shaft 320 via the coupling 330 and removes the fastening member 8. As a result, the pump casing 7 is separated from the suction flange 200 and the motor 3, so that the operator can pull out the pump casing 7 in the side pull-out direction.

Also in the embodiment shown in FIG. 18, the fastening member 8 may be inserted into an insertion hole 13a formed in the motor casing 13, or an insertion hole (not shown) into which the fastening member 8 is inserted into the pump casing 7. may be provided.

In the embodiment shown in FIG. 18, the pump device 1 includes the pump 2 as a horizontal single-stage pump, but such a pump device 1 may include the pump 2 as a horizontal multi-stage pump.

In the embodiment described above, the pump device 1 is a horizontal shaft pump device in which the rotating shaft 10 (and the drive shaft 320) extends in the horizontal direction, but the configuration of the pump device 1 is not limited to the embodiment described above. In one embodiment, the pump device 1 may be a vertical shaft pump device (a vertical shaft single stage pump device or a vertical shaft multistage pump device) in which the rotating shaft 10 (and the drive shaft 320) extends in the vertical direction.

Although the embodiments of the present invention have been described so far, the present invention is not limited to the above-described embodiments, and it goes without saying that the present invention may be implemented in various different forms within the scope of its technical idea.

1 Pump device (mechanical device)
2 Pump (rotating machine)
3 Motor (electric motor)
6A to 6C Impeller 7 Pump casing 8 Fastening member 10 Rotating shaft 11 Rotor
12 Stator
13 Motor casing 13a Insertion hole 15 Suction port 16 Suction casing 17 Discharge port 18 Discharge casing 19 End wall 19a Communication hole 20 Intermediate casing 20a Through hole 21 Inner peripheral wall 21a Inner peripheral surface 21b End surface 21c End surface 22 Outer peripheral wall 23 Reinforcing member 23a Radial direction Rib 23b Axial rib 24 Partition wall 24a Inner peripheral surface 24b Surface 24c Surfaces 26, 27 Both ends 28 Annular projection 29 Annular projection 31 Inner peripheral wall 31a End surface 32 Outer peripheral wall 33 Reinforcement member 33b Axial rib 34 Annular projection 34a Annular inclined surface 35 Seal Space 36 Inner peripheral wall 36a End face 37 Outer peripheral wall 38 Reinforcement member 38a Radial rib 38b Axial rib 39 Annular protrusion 40 Seal member 45 Guide vane 46 Return vane 47 Guide channel 48 Return channel 50 Partition member 50a Outer peripheral surface 50b Inner peripheral surface 51 Liquid inlet 55 Seal space 56 Seal member 91 Inner peripheral wall 92 Outer peripheral wall 93 Reinforcement member 93a Radial rib 93b Axial rib 100 Discharge pipe supporter 200 Suction flange 200a Suction port side surface (first surface)
200b Casing contact surface (second surface)
201 Reinforcement rib 202 Seal member 203 Seal groove 210 Body portion 211 Suction port portion 215 Flange supporter 215a Suction flange side portion 215b Base side portion 215c Connection portion 216 Fastener 217 Fastener 218 Through hole 219 Threaded hole 234 Annular seal groove 234a Seal compression Surface 235 Seal space 250 Casing assembly 300 Water supply device 301 Control panel 302 Support member 302a Legs 302b Frame 312 Operating panel 320 Drive shaft 330 Coupling B Base CL Axis P1 Suction pipe P2 Discharge pipe WL Wall

Claims (9)

impeller and
a rotating shaft to which the impeller is fixed;
a casing assembly housing the impeller;
The casing assembly includes:
a suction flange formed with a suction port connectable to the suction pipe and having an annular shape extending perpendicularly to the axial direction of the rotating shaft;
a pump casing connected to the suction flange ;
The suction flange is
a casing contact surface that is in contact with the pump casing and extends parallel to an end wall of the pump casing;
an annular seal groove formed on the casing contact surface and into which a seal member is attached;
The suction flange is connected to the pump casing with only the casing contact surface in contact with an end wall of the pump casing . The casing assembly includes a flange supporter that supports the suction flange,
The pump device according to claim 1 , wherein the suction flange has a screw hole into which a fastener can be inserted through a through hole formed in the flange supporter. The pump device includes:
a stator and a rotor that rotate the rotating shaft;
a motor casing that houses the stator and the rotor;
further comprising a fastening member that fastens the casing assembly and the motor casing,
The pump device according to claim 1 or 2 , wherein the fastening member extends through the casing assembly and is inserted into an insertion hole formed in the motor casing. The pump device according to any one of claims 1 to 3 , wherein the suction flange is made of resin or metal. The pump casing has a discharge port connectable to a discharge pipe,
The pump device according to any one of claims 1 to 4 , wherein the pump device includes a discharge pipe supporter that supports the discharge pipe. The pump device according to any one of claims 1 to 5 ,
A control panel equipped with an operation panel,
In the water supply device, the operation panel is arranged to face the same direction as the direction in which the pump casing is pulled out. A method for maintaining a pump device according to any one of claims 1 to 5 , comprising:
Stopping the operation of the pump device with the suction pipe connected to the suction flange,
A method of disconnecting the pump casing from the suction flange and pulling the pump casing to the side of the suction flange. 8. The method according to claim 7 , wherein the step of pulling out the pump casing to the side of the suction flange is performed while the suction flange is supported by a flange supporter that supports the suction flange. The step of pulling out the pump casing to the side of the suction flange is performed while the discharge pipe is supported by a discharge pipe supporter that supports the discharge pipe connected to the discharge port of the pump casing. 7 or the method according to claim 8 .

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