JPH10205482A - Magneto drive pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a magneto drive pump to have fast structure, reduce the diameter of a pump shaft as much as possible, improve durability by preventing breakage of a bearing during racing operation and air entrainment operation as much as possible, and besides be assembled in a multistage easily and at a low cost. SOLUTION: A magneto drive pump is constituted such that a drive magnet body 8 attached on the inner peripheral surface of a cylinder case 7 coupled to a motor shaft 6 and a driven magnet body 11 fixed at a rotor 10 arranged around a pump shaft 9 are positioned facing each other with a shell 5 nipped therebetween, and an impeller 14 rotated along with a rotor 10 is rotatably contained in a pump casing 40 having a suction nozzle part 41a. In this case, a rotary bearing 60 is fitted in the inner peripheral surface of the rotor 10, and the end face of the boss part of the impeller 14 is coupled to the end face of the rotary shaft 60 such that the rotary bearing 60 and the impeller 14 are integrally rotated.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a magnet-driven pump which is one of the most suitable sealless pumps used for pumping a handling liquid while preventing leakage, for example, for sending a highly toxic chemical solution. .

[0002]

2. Description of the Related Art FIG. 21 shows a conventional general structure of a pump shaft fixed type frequently used for a plastic magnet drive pump. A drive motor 1 is provided with a substantially cylindrical pump bracket 2. Pump casing 3 through
The pump casing 3 is provided with a suction nozzle 3a and a discharge nozzle 3b extending in directions orthogonal to each other.

[0003] A shell 5 forming a pump chamber 4 between the pump bracket 2 and the pump casing 3 with a peripheral portion hermetically sandwiched and fixed between the pump bracket 2 and the pump casing 3 is provided inside the pump bracket 2. , So that even if the pump chamber 4 is filled with the liquid, the liquid does not leak outside the shell 5.

A cylindrical case 7 surrounding the periphery of the shell 5 is provided on the motor shaft 6 of the drive motor 1.
The drive magnet body 8 is connected to the inner peripheral surface of the cylindrical case 7 in a non-contact manner outside the shell 5.
Is fixed.

On the other hand, a pump shaft 9 is arranged inside the pump chamber 4, and a driven magnet body 11 is integrally fixed to a rotor 10 rotating around the pump shaft 9 by a resin mold. The driven magnet body 11 and the drive magnet body 8 are arranged so as to face each other with the shell 5 interposed therebetween.

Here, the pump shaft 9 has one end supported by a plurality of ribs 12 provided in a boss 5a at the bottom of the shell 5 and the other end provided in a suction nozzle 3a of the pump casing 3. The suction nozzle portion 3a is fitted and fitted in the boss member 13 so that its axis coincides with the center of the flow path of the suction nozzle 3a.

The pump shaft 9 has an impeller 14
Are rotatably supported, and the impeller 14
And the rotor 10 are connected to each other, whereby the rotation of the driving magnet body 8 accompanying the rotation of the driving motor 1
The rotor 10 and the impeller 14 connected thereto are rotated via the driven magnet 11.

The rotor 10 is rotatably supported by a pump shaft 9 via a radial bearing 15. Further, in the vicinity of a suction mouth 14 a of the impeller 14, a rotating thrust bearing 16 a is provided on the pump casing 3. A fixed-side thrust bearing 16b opposed to the rotating-side thrust bearing 16a is provided on an inner peripheral surface facing the rotating-side thrust bearing 16a.

FIG. 22 shows a general configuration of a conventional magnet drive pump of a pump shaft rotation type. The difference from the conventional example shown in FIG. 21 is as follows.

That is, a casing cover 20 is interposed between the pump bracket 2 and the pump casing 3, a peripheral portion of the shell 5 is sandwiched and fixed between the casing cover 20 and the pump bracket 2, and the pump The shaft 9 and the rotor 10 are connected via a key 21a to the pump shaft 9
And the impeller 14 are configured to rotate integrally with each other via a key 21b.

A fixed bearing 22a is provided on the inner peripheral surface of the casing cover 20, and a rotary bearing 22b opposed to the fixed bearing 22a is provided on an end surface of the rotor 10, respectively.

With the rotation of the drive magnet body 8 accompanying the rotation of the drive motor 1, the rotor 10 and the impeller 14 fixed thereto are integrated with the pump shaft 9 via the driven magnet body 11. Rotate, and this rotation is applied to the rotor 1
The casing is supported by a rotary bearing 22b that rotates integrally with the casing cover 20 and a fixed bearing 22a that is fixed to the casing cover 20.

FIG. 23 shows a conventional general pump shaft rotating type multi-stage magnet drive pump (two stages in this example). The differences from the conventional example shown in FIG. 22 are as follows. .

That is, a pump casing 30 is constituted by a suction casing 31 having a suction nozzle portion 31a and a discharge casing 32 having a discharge nozzle portion 32a, and a first stage impeller is provided in the suction casing 31. The second stage (final stage) impeller 14 is housed in the discharge casing 32, and further between the first stage impeller 14 and the pump shaft 9, and the second stage impeller. Keys 21c and 21d between the car 14 and the pump shaft 9, respectively.
Is mounted so that the rotating shaft 9 and the first and second stage impellers 14 and 14 rotate integrally.

The first stage impeller 14 and the second stage impeller 14
A partition plate 33 is arranged between the stage impeller 14 and
Furthermore, the suction mouth portion 14a of the second stage impeller 14
Is in sliding contact with the inner peripheral surface of a partition wall 34 extending to the suction mouth portion 14a of the discharge casing 32.

In the above-mentioned magnet-driven pump of the pump shaft rotation type, the transmission of power to the impeller is performed by the pump shaft, and the impeller serving as a liquid contact part is made to have excellent corrosion resistance. It has been widely practiced that the pump shaft is made of ceramic, which has excellent corrosion resistance and is more rigid than plastic. Also, in order to further increase the rigidity, insert metal into the boss of the impeller,
It has been widely practiced to form a pump shaft by molding metal with plastic.

[0017]

However, in each of the above conventional examples, the pump shaft made of plastic or ceramics generally has a lower strength than metal or the like.
Especially in the case of a magnet-driven pump of the pump shaft rotation type, it is necessary to reduce the surface pressure applied to the power transmission part.
It is necessary to increase the diameter, and accordingly, the bearing parts also increase in size, resulting in a problem that the parts are expensive.

If a pump shaft is formed by inserting metal into the boss of the impeller and molding the metal with plastic, a seal such as an O-ring is required as a countermeasure against metal corrosion. The metal may be corroded.

Moreover, in the conventional example shown in FIG.
The ribs provided at the suction part of the casing or the boss members supported by the ribs may be damaged by the sliding heat generated between the pump shaft and the radial bearing during the idle operation or air entrainment operation. was there.

In both cases, since the center of pump suction and the center of rotation of the impeller and rotor are on the same line, in a piping system having no suction foot valve or discharge check valve, backflow of pumped liquid during idling operation or the like may occur. As a result, the water inside the pump escapes to the position below the mouthpiece of the impeller, causing the underwater bearing to operate in a dry mode, causing the damage.

Further, in the case of the magnet-driven pump of the fixed pump shaft type, the connection (connection) between the impellers is generally difficult, and the impeller cannot be assembled in multiple stages. Inevitably, the pump shaft rotation type must be adopted.However, when the pump shaft is multi-staged in this way, the length of the pump shaft becomes longer, and when this is made of ceramics, the longer the pump shaft becomes, The more grooves such as key grooves, the more bending occurs during sintering, the more time is required for machining after sintering, and the more expensive it is in terms of processing accuracy. That was the current situation.

The present invention has been made in view of the above circumstances, and has a rugged structure capable of reducing the diameter of the pump shaft as much as possible. It is an object of the present invention to provide a magnet-driven pump that can be assembled in multiple stages easily and inexpensively while improving the performance.

[0023]

According to the first aspect of the present invention, a driving magnet body attached to an inner peripheral surface of a cylindrical case connected to a motor shaft is fixed to a rotor disposed around the pump shaft. And a driven magnet body opposed to each other across a shell, and an impeller that rotates with the rotation of the rotor is rotatably housed inside a pump casing having a suction nozzle. A rotating bearing is fitted to the inner peripheral surface of the magnet, and an end face of a boss portion of the impeller is connected to an end face of the rotating bearing so that the rotating bearing and the impeller rotate integrally. Drive pump.

According to the present invention, the rotary bearing fitted to the inner peripheral surface of the rotor and the impeller rotating integrally with the rotary bearing are arranged on the outer peripheral portion of the pump shaft. Without increasing the diameter of the shaft, the diameter of the power transmission unit with the impeller can be increased to reduce the surface pressure of the transmission unit.

According to a second aspect of the present invention, a casing cover is interposed between the pump casing and a pump bracket accommodating the rotor, and the casing cover is fixed to an inner peripheral surface of the casing cover so as to face the rotary bearing. The magnet-driven pump according to claim 1, wherein a bearing is fixed. Thus, the corresponding rotary bearing and the pump shaft can be rotatably supported via the fixed bearing fixed to the inner peripheral surface of the casing cover.

According to a third aspect of the present invention, the end face of the boss portion of the impeller located at the front stage and the end face of the boss portion of the impeller located at the rear stage are connected so as to rotate integrally with each other. 3. The magnet-driven pump according to claim 2, wherein are connected in multiple stages. Thus, the impellers can be connected in multiple stages via the boss portion of the impeller having a diameter larger than that of the pump shaft, thereby forming a multi-stage pump in which the plurality of impellers rotate integrally with the pump shaft.

According to a fourth aspect of the present invention, the pump shaft is formed by integrally molding plastic on the outer periphery of a cylindrical portion extending integrally from a metal portion of the rotor. It is a magnet driven pump.
Thereby, the strength of the pump shaft can be further increased while maintaining the corrosion resistance.

According to a fifth aspect of the present invention, there is provided the magnet drive pump according to the third aspect, wherein the pump shaft is formed by integrally molding plastic on the outer peripheral surface of a metal rod. . Thereby, the strength of the pump shaft can be further increased while maintaining the corrosion resistance.

According to a sixth aspect of the present invention, the suction nozzle portion of the pump casing is disposed so that the center of the flow path of the suction nozzle portion and the axis of the pump shaft extend in parallel with a predetermined space therebetween. A rotation bearing is provided on a suction side boss portion of the impeller, and a fixed bearing facing the rotation bearing is provided on an inner peripheral surface of the pump casing facing a suction mouth portion of the impeller. 1 to 5
A magnet driven pump according to any one of the above.

Thus, the center of the flow path of the suction nozzle portion of the pump casing is shifted from the axis of the pump, and a fixed bearing for supporting the pump shaft is provided on the inner peripheral surface of the highly rigid pump casing, whereby the strength is unstable. It is possible to have a robust structure excluding any ribs or the like.

According to a seventh aspect of the present invention, the pump casing is disposed horizontally so that the center of the flow path of the suction nozzle portion of the pump casing is located directly above the pump shaft, and the center of the flow path of the suction nozzle portion is located at the same position. The distance between the pump shaft and the shaft center is such that when the flow path bottom of the suction nozzle portion is above the upper end of the suction mouth portion of the impeller, and when the liquid flows out of the suction nozzle portion due to backflow, the sliding of each of the bearings is performed. 7. The magnet-driven pump according to claim 6, wherein the section is set so as to secure residual water that can be submerged.

Thus, the sliding portion of each bearing (submersible bearing) disposed around the pump shaft is always submerged, so that it can be used in a piping system without a suction foot valve or a discharge check valve. In addition, it is possible to prevent the bearing from being in a dry operation during an idle operation or the like.

According to an eighth aspect of the present invention, a communication hole is provided in a partition that divides the interior of the pump casing into a suction chamber and a pump chamber and extends to a suction mouth portion of the impeller, and that allows the suction chamber and the pump chamber to communicate with each other. The magnet-driven pump according to claim 6, wherein: Thereby, the liquid in the discharge pipe can be returned to the impeller suction mouth portion from the communication hole during the idle operation.

According to a ninth aspect of the present invention, a pressure water introduction flow path is formed inside the pump shaft, and a bearing mounted between the pump casing and the impeller has a thrust load balancing function. 7. The method according to claim 6, wherein
A magnet drive pump according to any one of claims 1 to 8.

According to a tenth aspect of the present invention, a protection plate for preventing abrasion is provided on a side wall facing one or both of an inlet and an outlet of the pressure water introduction flow channel provided on the pump shaft. A magnet drive pump according to claim 9.

The invention according to claim 11 is the first invention.
Or the connection described in 3 is a clutch connection by fitting unevenness,
A magnet-driven pump using one of connection by fitting using chamfering, screw connection, pin connection, and key connection.

[0037]

FIG. 1 is a block diagram showing an embodiment of the present invention.
This will be described with reference to FIGS. The same members as those in the conventional example shown in FIGS. 21 to 23 are denoted by the same reference numerals and described.

FIGS. 1 to 4 show a first embodiment of a magnet drive pump according to the present invention applied to a pump shaft fixed type. A drive motor 1 is provided via a substantially cylindrical pump bracket 2. The pump casing 40 is connected.

The pump casing 40 is constituted by joining together two members, a suction casing 41 having a suction nozzle portion 41a and a discharge casing 42 having a discharge nozzle portion 42a.
The discharge casing 42 is provided with a partition 43 extending to the suction mouth portion 14 a of the impeller 14.
3, the inside of the pump casing 40 becomes the suction chamber 4
4 and a pump chamber 45.

The shell 5 forming the pump chamber 45 between the pump bracket 2 and the discharge casing 42 with the peripheral edge thereof being hermetically sealed between the pump bracket 2 and the discharge casing 42 is fixed to the pump bracket 2. , So that even if the inside of the pump chamber 45 is filled with the liquid, the liquid does not leak outside the shell 5.

A cylindrical case 7 surrounding the periphery of the shell 5 is provided on the motor shaft 6 of the drive motor 1.
And a driving magnet body 8 located on the inner peripheral surface of the cylindrical case 7 and outside the shell 5.
Is fixed.

On the other hand, from the suction chamber 44 to the pump chamber 45
A driven magnet body 11 is integrally fixed to a rotor 10 that rotates around the pump shaft 9 by resin molding, and the driven magnet body 11 and the driving magnet The body 8 is disposed so as to face each other with the shell 5 interposed therebetween.

[0043] The pump shaft 9 is disposed to extend in parallel with the axis O ₁ is at a channel center O ₂ and the interval L of the suction nozzle portion 41a flow path center O _2. That is, the axis O ₁ of the pump shaft 9 and the center O ₂ of the flow path of the suction nozzle portion 41a are not aligned on the same line, but have an interval L therebetween.

The pump shaft 9 is fixed at one end to a boss 5a at the bottom of the shell 5,
The other end is loosely fitted in the rotary bearing 46. A fixed bearing 47 that forms a pair with the rotary bearing 46 is a suction mouth portion 14 a of the impeller 14 on the inner peripheral surface of the suction casing 41.
Is fixed at a position facing the.

As described above, the center O ₂ of the flow passage of the suction nozzle 41 a of the pump casing 40 is connected to the axis O of the pump shaft 9.
_By providing the fixed bearing 47 for supporting the pump shaft 9 on the inner peripheral surface of the pump casing 40 having high rigidity, it is possible to obtain a robust structure excluding ribs and the like which are unstable in strength.

[0046] Here, the distance L between the channel center O ₂ of the axis O ₁ and the suction nozzle portion 41a of the pump shaft 9, channel center O ₂ of the suction nozzle portion 41a directly above the pump shaft 9 When installed horizontally to be located, the suction nozzle 4
1a is the suction mouth portion 14 of the impeller 14
When the liquid flows out from the suction nozzle 41a due to the backflow above the upper end 49 of a, the sliding portion of the bearings 46 and 47 is set to be able to secure residual water that can be submerged.

Thus, the bearing 4 for supporting the pump shaft 9
Even if the sliding portions 6 and 47 are always submerged and used in a piping system without a suction foot valve or a discharge check valve, the bearings 46 and 47 are in a dry operation during an idle operation or the like. Can be prevented.

Then, the back-flowed liquid is pressurized again and returned to the discharge pipe, and thereafter, these phenomena are repeated, and the bearings 46 and 47 are constantly wetted.

The center of the pump shaft 9 is provided with a pressure water introduction passage 5 extending over the entire length thereof in the axial direction.
0, and the outer diameter d ₁ of the bearings 46 and 47 on the impeller suction side is changed to the outer diameter d of the suction mouth portion 14 a of the impeller 14.
_By setting the same as ( ₂ ) (d ₁ = d ₂ ), the bearings 46 and 47 have a thrust load balance function.

As described above, when the flow path 50 for introducing pressure water is formed in the pump shaft 9, the flow velocity becomes high near the inlet and the outlet of the flow path 50 for introducing pressure water. For this reason, the suction casing 4 facing the inlet and outlet of the pressure water introduction flow path 50
Wear protection plates 51 and 52 are provided on the shell 1 and the shell 5, respectively, to prevent wear.

Further, the partition wall 43 is provided with a communication hole 53 for communicating the suction chamber 44 and the pump chamber 45, so that the siphon effect at the time of backflow is cut off and the liquid is reliably collected inside the pump. And sucks the liquid in the discharge pipe directly into the suction mouth portion 14a of the impeller 14.
And the bearings 46 and 47 installed on the impeller suction side can be wetted.

Here, inside the rotor 10, a rotary bearing 60 is integrated with the rotor 10 to form the pump shaft 9.
, And one end of a boss of the impeller 14 is attached to an end of the rotary bearing 60, and the rotary bearing 46 on the suction side of the impeller is attached to the other end of the boss of the impeller 14. They are connected so as to rotate together.

Thus, the rotor 10, the rotor 1
The rotation bearing 60 fitted in the inside 0, the impeller 14, and the rotation bearing 46 installed on the impeller suction side are integrally rotated around the pump shaft 9 arranged in a fixed state.

That is, as shown in detail in FIG. 2, on the end face of the rotary bearing 46 on the impeller 14 side, two concave portions 46a and two convex portions 46b are provided alternately. And
A concave portion 14b and a convex portion 14c are provided at a position complementary to the concave portion 46a and the convex portion 46b on the end face of the boss portion of the impeller 14 on the side of the rotary bearing 46, as shown in detail in FIG. The convex portion 14c of the impeller 14 is provided in the concave portion 46a of the rotary bearing 46, and the rotary bearing 46 is provided in the concave portion 14b of the impeller 14.
Are fitted to each other.

Further, as shown in detail in FIG. 3, a concave portion 14d is also provided on the end face of the boss portion of the impeller 14 on the side of the rotary bearing 60.
And the convex portion 14e are provided.
The concave portion 14d and the convex portion 1 on the end face of the boss portion on the side of the impeller 14
4e, a concave portion 60a and a convex portion 60b are provided, as shown in detail in FIG. 4, so that the convex portion 60b of the rotary bearing 60 is disposed within the concave portion 14c of the impeller 14. The protrusions 14d of the impeller 14 are fitted in the recesses 60b.

Thus, the rotation of the rotor 10 is transmitted from the rotary bearing 60 to the impeller 14. Since the rotary bearing 60 and the impeller 14 are arranged on the outer peripheral portion of the pump shaft 9, the pump shaft It is possible to increase the diameter of the power transmission unit with the impeller 14 without increasing the diameter of 9 and reduce the surface pressure of the transmission unit.

If the power transmission portion is made of plastic, the power transmission portion may be damaged by inching operation or the like. However, the rotating bearing 60 is made of a material having hardness, strength, and corrosion resistance such as ceramics. This can be dealt with by using a material having hardness, strength and corrosion resistance such as ceramics for the whole or this boss portion.

Here, the rotary bearing 4 on the impeller suction side is used.
6 and the impeller 14, and each of the joint end faces of the impeller 14 and the rotary bearing 60, as shown in detail in FIGS. 3 and 4, have a concave portion 61a and a convex portion 61b shaped along this shape.
For example, a cushioning material 61 made of a flexible material such as rubber or plastic is interposed.

By providing the cushioning material 61 with a sealing property, it is possible to take measures to prevent slurry from being mixed into the connection portion.

In the above example, the power from the rotor 10 is transmitted to the impeller 14 via the rotary bearing 60 and further from the impeller 14 to the rotary bearing 46 by the so-called uneven clutch connection.
, But it is a matter of course that the present invention is not limited to this.

For example, as shown in FIGS. 5 to 8, chamfers 6 are formed on both sides of the outer peripheral surface of the end of the rotary bearing 60 on the impeller 14 side.
0c, and a concave groove 14f having a shape matching the end of the rotary bearing 60 is provided in the boss of the impeller 14,
The impeller 14 and the rotary bearing 60 may be connected so that they rotate integrally with each other by using a cushioning material having a shape along the concave groove 14f.

As shown in FIGS. 9 and 10, a male screw portion 14g is provided on the outer peripheral surface of the boss portion on the suction side of the impeller 14.
Although not shown, a female screw portion to be screwed with the male screw portion 14g is provided on the inner peripheral surface of the boss portion of the rotary bearing 46 on the impeller suction side, and the female screw portion 14h is further rotated on the inner peripheral surface of the other boss portion of the impeller 14. A so-called screw connection in which a male screw portion 60d screwed to the female screw portion 14h is provided on the outer peripheral surface of the impeller-side end portion of the bearing 60, and a so-called hollow disk-shaped buffer material 63 is used. May be.

Further, as shown in FIGS. 11 and 12, pin holes 14i are provided at both end surfaces of the boss portion of the impeller 14, and pin holes are also provided at positions corresponding to the pin holes 14i on the end surface of the boss portion of the rotary bearing 60. Although not shown, a pin hole is similarly provided in the rotary bearing 46 on the impeller suction side (not shown), and a pin 64 is inserted into each of the pin holes 14i and 60e.
A so-called pin connection may be employed, and the cushioning material 65 may be a hollow disk having a pin insertion hole 65a.

As shown in FIGS. 13 and 14, a key groove 14j is provided on the outer peripheral surface of the suction side boss portion of the impeller 14, and not shown, but also on the inner peripheral surface of the boss portion of the rotary bearing 46 on the impeller suction side. A key groove is provided, and a key groove 14k is further provided on the inner peripheral surface of the other boss portion of the impeller 14, and a key groove 60f is provided on an outer peripheral surface of an end portion of the rotary bearing 60 on the impeller side. A so-called key connection in which a key 66 is mounted in each of 14k and 60f may be employed, and a hollow disk-shaped material may be used as the cushioning material 67.

It should be noted that various connection (connection) structures between the impeller 14 and the rotary bearing 60 as described above can be adopted in the following embodiments.

FIG. 15 shows a second embodiment of the present invention applied to a magnet shaft driven pump of a pump shaft rotation type. The difference of the second embodiment from the first embodiment is as follows. It is as follows.

That is, the casing cover 20 is interposed between the pump bracket 2 and the discharge casing 42 of the pump casing 40, and the casing cover 2
The outer peripheral portion of the shell 5 is clamped and fixed between the pump bracket 2 and the pump bracket 2, and a fixed bearing 70 facing the rotary bearing 60 is fixed to the inner peripheral surface of the casing cover 20.

Here, the pump shaft 9, which extends from the suction chamber 44 to the pump chamber 45, is held by the rotor 10 at the end on the rotor 10 side. As a result, the pump shaft 9 and the rotary bearing 60 rotate, and this rotation is supported by a fixed bearing 70 fixed to the inner peripheral surface of the casing cover 20.

The rotation of the rotary bearing 60 is transmitted to the impeller 14 and further transmitted to the rotary bearing 46 on the suction side of the impeller, and the fixed bearing 47 opposed to the rotary bearing 46.
Is the same as described above.

Here, the rotating bearing 60 and the fixed bearing 70
Like the sliding part between the rotary bearing 46 and the fixed bearing 47 on the suction side of the impeller, the sliding part is always submerged and used for a piping system without a suction foot valve or a discharge check valve. Also, the bearings 60 and 70 are configured so as not to be in the dry operation during the idle operation or the like.

FIG. 16 shows a third embodiment of the present invention applied to a pump shaft rotating type multistage magnet drive pump (two stages in this example), which is different from the conventional example shown in FIG. Is as follows.

That is, the first stage impeller 14 is provided in the suction casing 31 and the second stage impeller 14 is provided in the discharge casing 32, respectively. The impeller 14 and the second-stage impeller 14 are connected by a so-called concave / convex clutch connection.

That is, the projection 14c provided on the end surface of the boss portion of the second stage impeller 14 is inserted into the concave portion 14d provided on the end surface of the boss portion of the first stage impeller 14, The first-stage impeller 1 is provided in a concave portion 14 b provided on the end face of the boss portion of the vehicle 14.
The protrusions 14e provided on the end faces of the bosses 4 are fitted into the respective bosses so that the two 14 and 14 rotate integrally.

A rotary bearing 60 is fitted on the inner peripheral surface of the rotor 10 so as to rotate integrally therewith. The rotary bearing 60 and the second stage impeller 14 are similarly They are connected by a so-called uneven clutch connection.

That is, the projection 60b provided on the end face of the boss of the rotary bearing 60 is provided in the recess 14d provided on the end face of the boss of the second stage impeller 14, and the recess provided on the end face of the boss of the rotary bearing 60. The protrusions 14e provided on the end face of the boss of the second stage impeller 14 are fitted into the inner surfaces 60a, respectively.
Are designed to rotate together.

Further, near the suction mouth portion 14a of the first stage impeller 14, a rotary thrust bearing 16a is provided.
Is the rotation side thrust bearing 16 of the suction casing 31.
a on the inner peripheral surface facing the rotating thrust bearing 16.
The fixed thrust bearings 16b opposed to a are provided in the same manner as the conventional example shown in FIG.

In this embodiment, the rotation of the rotor 10 is transmitted to the second (final) impeller 14 via the rotary bearing 60 and further from the second impeller 14 to the first impeller. Of the power transmission unit with the impeller 14, so that the diameter of the power transmission unit with respect to the impeller 14 is larger than that of the pump shaft 9 without increasing the diameter of the pump shaft 9. Can be lowered.

FIG. 17 shows a fourth embodiment of the present invention applied to a pump shaft rotating type multi-stage magnet drive pump. This embodiment is different from the one shown in FIG. Is added.

That is, a connecting casing 71 is interposed between the suction casing 41 and the discharge casing 42, and the first-stage impeller 14 is discharged into the connecting casing 71 by discharging the first-stage impeller 14. The impeller 14 is housed so as to be located between the second-stage impeller 14 located in the rotor 42 and the rotary bearing 46 on the impeller suction side. Are connected so as to rotate integrally with the rotary bearing 60 fitted to the shaft.

That is, the two impellers 14 and 14 are formed in the same shape, and the boss end face of the second stage impeller 14 is provided in the recess 14 d provided in the end face of the boss portion of the first stage impeller 14. The protrusions 14c provided on the boss end face of the first-stage impeller 14 fit into the recesses 14b provided on the boss end face of the second-stage impeller 14, respectively. The two members 14 are configured to rotate integrally.

The first stage impeller 14 and the rotary bearing 4
6 and the second stage impeller 14 and rotary bearing 60
Is similar to that shown in FIG.

Here, the first stage impeller 14 and the second stage impeller 1 are located in the connection casing 71.
A partition plate 33 is disposed between the first stage impeller 14 and the partition plate 33.
This fixed bearing 7 is located at a position facing the fixed bearing 72.
The rotating bearings 73 opposed to 2 are respectively fixed.

In this embodiment, the impeller 1
By unitizing the unit 4 and the connecting casing 71 and simply connecting them, the pump can be assembled easily and inexpensively in multiple stages.

For example, although not shown, when assembling into three stages, a pump shaft suitable for the length is used,
Two connecting casings are interposed between the suction casing and the discharge casing, and three impellers of the same shape are further incorporated between the two rotary bearings located at both ends of the pump shaft. Can be assembled in three stages.

FIG. 18 shows a fifth embodiment of the present invention applied to a pump shaft rotating type multi-stage magnet drive pump. This embodiment is different from the fourth embodiment in that: The pump shaft 9 is constituted by a plurality of (three in the figure) divided pump shafts 9a to 9c.

That is, the first split pump shaft 9a which straddles the rotary bearing 46 on the impeller suction side and the first stage impeller 14.
A second split pump shaft 9b extending over the first-stage impeller 14 and the second-stage impeller 14, and a second-stage impeller 14
The pump shaft 9 is constituted by the third divided pump shaft 9c extending over the rotary bearing 60 fitted on the inner peripheral surface of the rotor 10.

Since the pump shaft 9 does not transmit power as described above, it can be divided into a plurality of parts as described above.
The cost of the pump shaft 9 can be reduced.

FIG. 19 shows a sixth embodiment of the present invention applied to a pump shaft rotation type multi-stage magnet drive pump. This embodiment is different from the fourth embodiment in that The difference is that a plastic shaft 82 is integrally molded with the outer periphery of a metal cylindrical portion 81 extending from the metal portion 80 inside the rotor 10 to form a pump shaft 9d which rotates integrally with the rotor 10.

With this configuration, the rigidity of the pump shaft can be increased while maintaining the corrosion resistance.

FIG. 20 shows a seventh embodiment of the present invention applied to a pump shaft rotating type multi-stage magnet drive pump. This embodiment is different from the fourth embodiment in that: A plastic shaft 82 is molded integrally with the outer periphery of a metal rod 83 extending by screwing one end to a metal portion 80 inside the rotor 10 to form a pump shaft 9e that rotates integrally with the rotor 10. is there.

With this configuration, the rigidity of the pump shaft can be increased while maintaining the corrosion resistance.

[0092]

As described above, according to the present invention, the end face of the boss portion of the impeller is attached to the end face of the rotary bearing fitted to the inner peripheral surface of the rotor, and the rotary bearing and the impeller are integrally formed. By rotatingly connecting the pump shaft, a larger-diameter rotary bearing disposed on the outer peripheral portion of the pump shaft can be used as a power transmission unit with the impeller, thereby increasing the diameter of the pump shaft. Without increasing the diameter of the power transmission unit with the impeller, the surface pressure of the transmission unit can be reduced.

In particular, in a pump shaft rotating type multistage pump, a ceramic pump shaft is very expensive. However, according to the present invention, the cost of the pump shaft is reduced, and It can be assembled easily and inexpensively in multiple stages.

Further, the suction nozzle portion of the pump casing is disposed so that the center of the flow path of the suction nozzle portion and the axis of the pump shaft extend in parallel with a predetermined space therebetween.
By providing a rotary bearing on the suction side boss portion of the impeller and a fixed bearing facing the rotary bearing on the inner peripheral surface of the pump casing facing the suction mouth portion of the impeller, the flow of the suction nozzle portion of the pump casing is provided. The center of the path is displaced from the axis of the pump, and a fixed bearing for supporting the pump shaft is provided on the inner peripheral surface of the pump casing having high rigidity, so that a rigid structure in which ribs and the like which are unstable in strength are eliminated can be obtained.

Further, the pump is installed horizontally so that the center of the flow path of the suction nozzle portion of the pump casing is located directly above the pump shaft, and the distance between the center of the flow passage of the suction nozzle portion and the axis of the pump shaft is set. When the flow path bottom of the suction nozzle is above the upper end of the suction mouth of the impeller, and when the liquid flows out of the suction nozzle due to the backflow, it is possible to secure residual water in which the sliding part of each bearing can be submerged. By setting so that the sliding part of each bearing (underwater bearing) arranged around the pump shaft is always submerged, it can be used for piping systems without suction foot valve or discharge check valve. In addition, it is possible to prevent the bearing from being in the dry operation during the idle operation or the like, and to improve the durability.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a first embodiment of the present invention.

2A and 2B show a rotary bearing on an impeller suction side in FIG. 1, wherein FIG.
(B) is a right side view.

FIG. 3 shows a cushioning material and an impeller in FIG. 1, and (a)
Is a perspective view of the cushioning material, (b) is a left side view of the impeller, (c)
Is a cross-sectional view (a cross-sectional view taken along line BB of FIG. 2B), and FIG.

4A and 4B show a cushioning material and a rotary bearing on the rotor side in FIG. 1, wherein FIG. 4A is a perspective view of the cushioning material, FIG. 4B is a left side view of the rotary bearing, and FIG. It is CC sectional drawing.

FIG. 5 shows a first example of a connection portion between the impeller and the rotary bearing on the rotor side.
It is sectional drawing at the time of connection which shows the modification of.

FIG. 6 is a sectional view of the impeller in FIG.

FIG. 7 is a perspective view of the cushioning member in FIG.

8 shows a rotary bearing on the rotor side in FIG. 5,
(A) is a left side view, and (b) is a cross-sectional view (a cross-sectional view taken along line DD in (a)).

FIG. 9 shows a second connection portion between the impeller and the rotary bearing on the rotor side.
It is sectional drawing at the time of connection which shows the modification of.

FIG. 10 is an exploded view of FIG. 9;

FIG. 11 is a cross-sectional view at the time of connection showing a third modification of the connection portion between the impeller and the rotary bearing on the rotor side.

FIG. 12 is an exploded view of FIG.

FIG. 13 is a cross-sectional view showing a fourth modified example of the connection portion between the impeller and the rotary bearing on the rotor side at the time of connection.

FIG. 14 is an exploded view of FIG.

FIG. 15 is a sectional view showing a second embodiment of the present invention.

FIG. 16 is a sectional view showing a third embodiment of the present invention.

FIG. 17 is a sectional view showing a fourth embodiment of the present invention.

FIG. 18 is a sectional view showing a fifth embodiment of the present invention.

FIG. 19 is a sectional view showing a sixth embodiment of the present invention.

FIG. 20 is a sectional view showing a seventh embodiment of the present invention.

FIG. 21 is a sectional view showing a conventional example.

FIG. 22 is a sectional view showing another conventional example.

FIG. 23 is a sectional view showing still another conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Drive motor 2 Pump bracket 5 Shell 6 Motor shaft 7 Cylindrical case 8 Drive magnet body 9, 9a, 9b, 9c, 9d, 9e Pump shaft 10 Rotor 11 Drive magnet body 14 Impeller 14a Same suction mouth part 14b, 14d Same recess 14c, 14e Convex part 20 Casing cover 30, 40 Pump casing 31, 41 Suction casing 31a, 41a Suction nozzle part 32, 43 Discharge casing 33, 43 Partition wall 44 Suction chamber 45 Pump chamber 46 Rotating bearing 47 Fixed bearing 50 Pressure Water introduction flow passages 51, 52 Protective plate for wear protection 53 Communication hole 60 Rotary bearing 60a Same concave portion 60b Same convex portion 61, 62, 63, 65, 67 Buffer material 70 Fixed bearing 71 Connection casing 82 Plastic

Claims (11)

[Claims] 1. A drive magnet body attached to an inner peripheral surface of a cylindrical case connected to a motor shaft and a driven magnet body fixed to a rotor arranged around a pump shaft are opposed to each other across a shell. And a magnet drive pump in which an impeller that rotates with the rotation of the rotor is rotatably housed inside a pump casing having a suction nozzle portion, wherein a rotary bearing is fitted to the inner peripheral surface of the rotor, A magnet-driven pump, wherein an end face of a boss portion of the impeller is connected to an end face of the rotary bearing so that the rotary bearing and the impeller rotate integrally. 2. A casing cover is interposed between the pump casing and a pump bracket accommodating the rotor, and a fixed bearing facing the rotary bearing is fixed to an inner peripheral surface of the casing cover. The magnet-driven pump according to claim 1, wherein 3. An end face of a boss portion of an impeller located at a preceding stage and an end face of a boss portion of an impeller located at a later stage are connected so as to rotate integrally, and the impeller is connected in multiple stages. The magnet-driven pump according to claim 2, wherein: 4. The magnet driven pump according to claim 3, wherein said pump shaft is formed by integrally molding plastic on an outer periphery of a cylindrical portion extending integrally from a metal portion of said rotor. 5. The magnet driven pump according to claim 3, wherein said pump shaft is formed by integrally molding plastic on the outer peripheral surface of a metal rod. 6. A suction nozzle portion of the pump casing is disposed so that a center of a flow path of the suction nozzle portion and an axis of the pump shaft extend in parallel with a predetermined distance therebetween, and suction of the impeller is performed. 6. A rotary bearing is provided on a side boss portion, and a fixed bearing facing the rotary bearing is provided on an inner peripheral surface of the pump casing facing a suction mouth portion of the impeller, respectively. The described magnet-driven pump. 7. The pump casing is disposed horizontally so that the center of the flow path of the suction nozzle portion of the pump casing is located directly above the pump shaft, and the center of the flow channel of the suction nozzle portion and the axis of the pump shaft When the flow path bottom of the suction nozzle part is above the upper end of the suction mouth part of the impeller, and when the liquid flows out of the suction nozzle part by the backflow, the remaining water that can slide the sliding part of each bearing is submerged. 7. The magnet driven pump according to claim 6, wherein the pump is set so as to be able to be secured. 8. A communication hole for connecting the suction chamber and the pump chamber to each other, wherein a partition partitioning the inside of the pump casing into a suction chamber and a pump chamber and extending to a suction mouth portion of the impeller is provided. The magnet-driven pump according to claim 6 or 7, wherein: 9. A pressure water introduction flow path is formed inside the pump shaft, and a bearing mounted between the pump casing and the impeller has a thrust load balancing function. Item 9. A magnet-driven pump according to any one of Items 6 to 8. 10. The magnet drive according to claim 9, wherein a protection plate for preventing abrasion is provided on a side wall facing one or both of an inlet and an outlet of the pressure water introduction channel provided on the pump shaft. pump. 11. The connection according to claim 1, wherein any one of clutch connection by fitting of unevenness, connection by fitting using chamfering, screw connection, pin connection, and key connection is used. A magnet-driven pump, comprising: