JP4959424B2 - Pump device - Google Patents

Description

  The present invention provides a mechanism for rotating a rotor and an impeller in a non-contact state in an impeller casing by indirectly driving a metal cylindrical rotor fixed to one side of a closed impeller with a rotating magnetic field generator. It is related with the provided pump apparatus.

  Various types of pump devices having a non-seal structure and a mechanism for rotating the impeller in a state where the impeller is floated in the liquid have been filed. Many of the troubles that occur in these pump devices are caused by contact between the rotor and the can (a partition wall separating the rotor and the rotating magnetic field generator). In order to avoid such troubles, an arc-shaped partition parallel to the rotation trajectory of the impeller is provided in the outer peripheral region than the impeller in the impeller casing, and one end of the partition is opened at a part of the impeller casing. A pump device has been proposed in which the other end of the partition wall is disposed at a position facing the discharge port (see, for example, Patent Document 1).

  According to the pump device described in Patent Document 1, the hydraulic pressure at the position facing the discharge port is almost equal to the hydraulic pressure at the opposite position of the discharge, and the phenomenon that the rotating impeller is drawn toward the discharge port is eliminated. Contact and sliding between the rotor and the can and between the impeller and the casing are eliminated, and troubles caused by these contact and sliding can be prevented.

JP 2005-90478 A

  In the pump device described in Patent Document 1, when the rotating impeller moves to one side along the rotational axis for some reason, the gap between one side surface of the impeller and the inner side surface of the impeller casing is reduced, and the impeller Since the gap between the other side surface and the inner side surface of the impeller casing is enlarged, the liquid flow rate in the enlarged gap is increased. As the flow rate increases, the dynamic pressure also increases, so that the expanded gap is further expanded, so that the impeller further moves to one side, and the impeller and the impeller casing contact or slide between the rotor and the can. Sometimes.

  Therefore, the problem to be solved by the present invention is to provide a pump device in which contact and sliding between a rotor and an impeller and a casing surrounding them do not occur.

In the pump device of the present invention, a rotor made by indirectly driving a metal cylindrical rotor fixed on the drive side surface of a closed-type impeller coaxially with its rotational axis by a rotating magnetic field generator arranged with a partition wall therebetween. In the horizontal type pump device of the single suction, the upper discharge and the one side drive system, equipped with a mechanism for holding and rotating the impeller in a non-contact state in the casing,
Protruding ridges projecting in the diameter-expanding direction along the outer circumferences of the two side surfaces of the impeller are provided, and the rim portions on the inner side surfaces of the impeller casing respectively opposed to the side surfaces of the impeller are arranged in the outer peripheral regions. Providing an annular wall surrounding the ridge,
As the impeller moves in the rotational axis direction, when the side surface and the inner surface of the impeller casing approach and separate from each other, a flow rate adjustment surface that is separated from each other and approaches is provided on the projecting portion of the side surface and the opposed portion of the annular wall. Each is provided.

  With such a configuration, when the rotating impeller moves to one side along the rotation axis and the one side surface of the impeller and the inner side surface of the impeller casing approach each other, the protruding portion and the annular wall on the one side surface The flow rate adjusting surfaces respectively provided at the facing portions are spaced apart from each other, and the flow rate adjusting surfaces provided at the facing portions between the protrusions on the other side surface and the annular wall approach each other. For this reason, the flow rate between the one side surface close to each other and the inner side surface of the impeller casing is increased and the dynamic pressure is increased, and the flow rate between the other side surface and the impeller casing inner side surface which are separated from each other is decreased. The dynamic pressure also decreases.

  Therefore, the impeller moved to one side along the rotation axis is located at the position where the dynamic pressures on the two side surfaces of the impeller are equal to each other due to the change in the dynamic pressure on the two side surfaces, that is, the two side surfaces of the impeller and the impeller casing. It returns to a position where the gaps with the inner surface are equal to each other. Such an impeller return function occurs even when the impeller moves in any direction along the rotation axis, so that the rotating impeller can always be held at a predetermined position. For this reason, contact and sliding between the rotor and the impeller and the casing surrounding them do not occur.

  On the other hand, the rotating impeller moves to one side along the rotation axis, the one side surface of the impeller approaches the inner side surface of the impeller casing, and the amount of liquid inflow between the flow rate adjustment surfaces that are separated from each other extremely increases. Then, the impeller may move violently toward the other side surface. Therefore, it is desirable to provide a through hole in the annular wall that communicates the inner peripheral region and the outer peripheral region of the annular wall. With such a configuration, the amount of liquid inflow between the flow rate adjustment surfaces that are separated from each other is reduced, so that the impeller can be moved gently.

  According to the present invention, it is possible to provide a pump device in which contact and sliding between the rotor and the impeller and the casing surrounding them do not occur.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 is a sectional view of a pump device according to an embodiment of the present invention, FIG. 2 is a partially cutaway exploded view of the pump device shown in FIG. 1, FIG. 3 is a sectional view taken along line X1-Y1 in FIG. FIG. 5 is a diagram showing the behavior of the liquid in the casing in the conventional pump device without a partition wall, FIG. 5 is a diagram showing the contact state of the impeller, rotor, casing, and can in the pump device shown in FIG. It is a figure which shows the behavior of the liquid in the casing in the pump apparatus shown in FIG.

  The specifications of the pump device 40 shown in FIG. 1 are as follows. The diameter of the suction pipe from the outside (the diameter of the suction port 26) is 32 mm, and the diameter of the discharge pipe (the diameter of the discharge port 27) is 20 mm. The material of the impeller 20 is PVC, its outer diameter is 80 mm, the diameter of the suction hole 20a is 32 mm, and the number of impeller blades is five. The rotor 30 is formed of an aluminum cylinder having a thickness of 3 mm, and the exposed surface thereof is coated with Teflon (registered trademark) having a thickness of 200 μm. The can 38 has a double cylindrical structure with a thickness of 2 mm, and includes an inner can 31 and an outer can 32. The clearances between the inner can 31 and the outer can 32 and the rotor 30 are 2 mm. The main casing 21 has a double wall structure and a liquid passage width of 10 mm.

  The number of the outer magnets 33 and the inner magnets 34 constituting the rotating magnetic field generator is 4P, and the material thereof is a neodymium magnet. The drive motor 37 is a 3φ, 200V type, and its output is 0.4 kW. A total of eight wedge-shaped inclined surfaces B1 to B8 are formed alternately with the concave grooves 25-3 for taking in the wedge liquid, and the inclination angle θ of each wedge-shaped inclined surface B1 to B8 (see FIG. 8) is 2 degrees. . The pump device has a discharge amount of 50 l / min, a lift of 8 m, and a pump efficiency of 24%.

  As shown in FIGS. 1 and 2, in the pump device 40, the impeller casing 21 holds the partition wall 23-1 and the casing main plate 23 between the suction side casing side plate 21-1 and the can side casing side plate 21-2. These members are fixed by tightening these members with a tightening bolt 28. An impeller 20 is disposed in the impeller casing 21, and an aluminum rotor 30 is fixed to one side (drive side surface) of the impeller 20 coaxially with the rotation axis. If the tightening bolt 28 is loosened and removed, the impeller 20 and the rotor 30 can be easily taken out or placed in their original locations. The rotor 30 is an aluminum hollow cylindrical body that is a non-magnetic good electrical conductor, and the exposed surface thereof is coated with Teflon (registered trademark) resin.

  The impeller 20 and the rotor 30 (hereinafter referred to as “rotating portion”) are arranged so as to freely rotate in the casing 21 and the can 38 (the inner can 31 and the outer can 32). The can 38 (the inner can 31 and the outer can 32) has a double cylindrical structure made of a non-magnetic high electrical resistance material, and the bottom of the inner can 31 (the portion near the impeller 20) is closed and the other portion ( The portion near the drive motor 37 has a closed shape in which the inner can 31 and the outer can 32 are joined together.

  A plurality of sets of outer magnets 33 and inner magnets 34 are arranged on the inner side of the inner can 31 and the outer side of the outer can 32 with a gap therebetween. The outer magnet 33 and the inner magnet 34 are attached to a double cylindrical magnet holder 35 including an outer magnet yoke 33-1 and an inner magnet yoke 34-1 respectively. And the axial center part of this magnet holder 35 is connected with the output shaft (not shown) of the drive motor 37 via the holder connecting shaft 36.

  Here, with reference to FIG. 3, the arrangement | positioning state of the inner magnet 34 and the outer magnet 33 is demonstrated. As shown in FIG. 3, the opposing surfaces of the inner magnet 34 attached to the inner magnet yoke 34-1 and the outer magnet 33 attached to the outer magnet yoke 33-1 are different from each other. The magnets on the adjacent surfaces of the inner magnet 34 and the outer magnet 33 are arranged so as to be different from each other. The inner magnet 34 and the outer magnet 33 are simultaneously rotationally driven by a single drive motor 37 via a holder connecting shaft 36 fixed to the axis of the magnet holder 35.

  Thus, by rotating the inner magnet 34 and the outer magnet 33 together with the magnet holder 35, a rotating magnetic field is generated between the inner magnet 34 and the outer magnet 33, and between the inner magnet 34 and the outer magnet 33. The magnetic flux intersects with the rotor 30 to generate an induced current in the rotor 30 and to generate a rotational force and a repulsive force in the rotor 30. These rotational force and repulsive force become the rotational driving force of the impeller 20.

  Since the rotor 30 is attached only to one side (drive side surface) of the impeller 20, the center of gravity of the rotating portion including the impeller 20 and the rotor 30 is located in a portion near the rotor 30 of the impeller 20, and the impeller 20 is left and right. There is a risk of shaking. In order to prevent this, a cylindrical balance projecting to the opposite side of the rotor 30 on the impeller side plate 20-1 constituting the suction side surface located on the opposite side of the drive surface of the impeller 20 (the surface on which the rotor 30 is attached). A cylinder 20-3 is provided. The balance cylinder 20-3 is provided coaxially with the rotation axis of the impeller 20, and the balance cylinder 20-3 is formed on the inner surface of the suction side casing side plate 21-1 facing the balance cylinder 20-3. A circular concave groove 21a is formed in which the tip side is accommodated.

  By providing such a balancing cylinder 20-3 and the concave groove 21a, the liquid present in the gap between the rotating balancing cylinder 20-3 and the concave groove 21a causes a radial wedge effect. The balance cylinder 20-3 rotates in a state of being stably held in the concave groove 21a without contacting the inner wall of the concave groove 21a. Therefore, the wedge effect generated in the gap between the rotor 30 and the can 38 and the wedge effect generated in the gap 30 between the balance cylinder 20-3 and the concave groove 21a and the gap 30 are combined, and the rotating impeller 20 and the stability of the rotor 30 are further improved. For this reason, the contact and sliding between the impeller 20 and the impeller casing 21 and the rotor 30 and the can 38 are eliminated, and failure due to these contact and sliding can be prevented. In this embodiment, when the inner diameter and the outer diameter of the balancing cylinder 20-3 are equal to the inner diameter and the outer diameter of the rotor 30, the stability of the impeller 20 and the rotor 30 is excellent.

  Further, as shown in FIG. 2 and FIG. 6 to be described later, the impeller 20 is provided with a suction hole 20a penetrating coaxially with the rotational axis thereof, and suction is performed on the inner surface of the casing side plate 21-1 facing the suction side surface of the impeller 20. An auxiliary suction cylinder 21-1-1 (see FIG. 1) that protrudes into the suction hole 20a is provided at the periphery of the fluid suction port 26 that is opened coaxially with the hole 20a. By providing the auxiliary suction cylinder 21-1-1, the movement of the impeller 20 in the thrust direction, which is generated by the fluid sucked into the impeller 20 at the start or during the rotation of the impeller 20, can be reduced. For this reason, it is possible to prevent contact and sliding between the impeller 20 and the impeller casing 21 when the impeller 20 starts to rotate.

  Further, an inflow liquid adjusting boss 31-1 protruding into the suction hole 20a is provided at a central portion of the inner surface of the casing side plate 21 facing the drive side surface of the impeller 20 (bottom of the inner can 31). By providing such an inflowing liquid adjustment boss 31-1, the movement in the thrust direction of the impeller 20 generated by the fluid sucked into the impeller 20 at the start of the rotation of the impeller 20 or during the rotation is reduced as described above. can do. For this reason, it is possible to prevent contact and sliding between the impeller 20 and the impeller casing 21 when the impeller 20 starts to rotate.

  Further, a conical protrusion 31-1a having a vertex portion located on the rotational axis of the impeller 20 and a smoothly extending base portion is provided on the front end surface of the influent adjustment boss 31-1. By providing such a protrusion 31-1a, the liquid flowing into the suction hole 20a along the rotation axis of the impeller 20 is uniformly distributed in the radial direction along the outer peripheral surface of the protrusion 31-1a. It becomes possible to do. For this reason, the movement of the impeller 20 in the thrust direction is alleviated, and the stability of the impeller 20 at the start of rotation and during rotation can be further improved.

Here, FIG. 4 is a sectional view showing a part of a conventional pump device having no partition in the casing, and shows the relationship between the pump impeller 20 and the impeller casing 21 when the discharge port 27 is on the upper side. . In FIG. 4, when the center point of the impeller 20 is φ ₁ , when the impeller 20 rotates and liquid discharge starts from the protruding port 27, the hydraulic pressure P _{1 at the} position facing the discharge port 27 in the impeller casing 21 is It becomes lower than the hydraulic pressure P ₂ at the symmetrical position across the suction port 26. At this time, the impeller 20 that is in a non-contact state in the impeller casing 23 is pushed upward by the pressure difference between the hydraulic pressure P ₁ and the hydraulic pressure P ₂ as shown in FIG. The impeller 20 and the rotor 30 are rotated while being in contact with the outer can 32 and the outer can 32. At this time, the rotor 30 is in contact with the inner can 31 and the outer can 32 at Q ₁ and Q ₂ , and the impeller 20, the suction side casing side plate 21-1 and the can side casing side plate 21-2 are Q ₃ , Q Contact at ₄ part. If the sliding generated by such contact is simply due to insufficient repulsive force, the rotor 30, the inner can 31 and the outer can 32 should slide entirely. However, considering that such contact and sliding occur only partially, it cannot be said that the repulsive force is insufficient.

  Therefore, in order to solve the contact and sliding phenomenon described above, the pump device 40 of the present embodiment employs a structure as shown in FIG. As shown in FIG. 6, an arc-shaped partition wall 23-1 parallel to the rotation trajectory of the impeller 20 is provided in the outer peripheral region of the impeller casing 21 in the outer peripheral region in order to partition the outer peripheral region into the outer peripheral side and the inner peripheral side. And one end portion 23-1a of the partition wall 23-1 is disposed facing the inner opening of the discharge port 27 provided at the upper end portion of the casing 21, and the other end portion 23-1b of the partition wall 23-1 is disposed at the discharge port 27. It is arranged near the position opposite to.

  Thus, an arc-shaped double wall is formed by the partition wall 23-1 and the outer wall 23-2, and an arc-shaped closing wall 23-5 is arranged at a position facing these double walls. And between the one end part 23-1a and the other end part 23-1b of the partition 23-1, and the closing wall 23-5, the discharge holes 23-3 and 23-4 respectively connected with the outer peripheral area | region of the impeller 20 are provided. Established, the area in the circumferential direction is almost the same. The liquid flow that has passed through the lower discharge hole 23-4 flows through the discharge liquid passage 24 between the partition wall 23-1 and the outer wall 23-2, and passes through the upper discharge hole 23-3 at a position facing the discharge port 27. It merges with the liquid flow that has passed.

As described above, the arc-shaped partition wall 23-1 is provided in the outer peripheral region of the impeller 20 in the casing 21, the one end portion 23-1 a is arranged facing the inner opening of the discharge port 27, and the other end portion 23- When placed near the position opposite to the ejection opening 27 to 1b, the fluid pressure P ₄ in the hydraulic pressure P ₃ ≒ discharge holes 23-4 in the discharge hole 23-3. Accordingly, the impeller 20 rotates at a normal position without deviating from the rotation axis, and the rotation portion does not tilt, and the rotor 20 and the inner can 31 that are generated in the conventional pump device shown in FIGS. The contact with the outer can 32, the sliding phenomenon, the contact with the casing 21 due to the inclination of the impeller 20, and the sliding phenomenon could be eliminated. Further, as shown in FIG. 7, the discharge holes 23-3 and 23-4 are respectively opened in pairs so as to be positioned on the outer periphery of the impeller side plates 20-1 and 20-2. The liquid flows separately into a pair of discharge holes 23-3 and 23-4. For this reason, blurring of the impeller 20 during rotation is reduced, and an extremely stable rotation state can be obtained.

  On the other hand, in the pump device 40 of the present embodiment, a thrust force (force in the direction of the rotational axis = force in the axial direction of the holder connecting shaft 36) is generated in the impeller 20, and the magnitude thereof is determined by the pump head and the discharge amount. It depends on. Due to such a thrust force, the impeller 20 tilts to the left and right, and may slide with the casing 21 as it is. In order to prevent this, in the pump device 40, as shown in FIG. 1, wedge surface portions 25-1 and 25-2 are respectively provided on the casing side plates 21-1 and 21-2 facing the impeller side plates 20-1 and 20-2. Is provided. As shown in FIG. 8, which will be described later, the wedge surface portions 25-1 and 25-2 include eight concave grooves 25-3 formed radially around the rotation axis of the impeller 20, and the concave grooves 25-. The wedge-shaped inclined surfaces B <b> 1 to B <b> 8 are formed in the eight regions partitioned by 3 so as to form an upward gradient along the impeller rotation direction R.

  If the wedge surface portions 25-1 and 25-2 are provided, when the impeller 20 approaches the casing side plates 21-1 and 21-2 by the thrust force, the impeller 20 and the wedge surface portions 25-1, Since the wedge effect is generated by the liquid flowing into the gap with 25-2, contact between the two can be prevented.

  Here, the wedge effect will be described in detail with reference to FIGS. 7 is a partially enlarged view of the pump device shown in FIG. 1, FIG. 8 is a view taken along the line X2-Y2 in FIG. 7, and FIG. 9 is a view of the impeller side plate 20-1 (20-2) and the wedge surface portion 25-1. It is a figure which shows the relationship with (25-2).

As shown in FIGS. 7 and 8, the wedge surface portion 25-2 of the casing side plate 21-2 is partitioned by a plurality of wedge-shaped inclined surfaces B1 to B8 by a plurality of concave grooves 25-3. In FIG. 8, an arcuate arrow line 39 with a plurality of branch lines represents the upward gradient of the wedge-shaped inclined surfaces B1 to B8, R represents the rotational direction of the impeller 20, and W enters the wedge-shaped inclined surfaces B1 to B8. This represents the flow direction of the liquid. In FIG. 9, θ represents the inclination angle of the wedge-shaped inclined surfaces B1 to B8, and g ₁ and g ₂ represent the wedge surface portion 25-1 (25-2) of the casing side plate 21-2 and the impeller side plate 20-1 (20− 2).

The repulsive force FA generated by the wedge surface portion 25-1 (25-2) is roughly expressed as follows. If the viscosity of the liquid and the inflow speed of the liquid into the wedge surface portion 25-1 (25-2) (in this embodiment, it is assumed to be proportional to the rotational speed of the impeller 20) are constant,
FA∝ (b ² × L × n) / g ₁ ²
(B: width of wedge-shaped inclined surface, L: length of wedge-shaped inclined surface, n: number of wedge-shaped inclined surfaces)
It can be expressed as. Here, g ₂ is a gap on the inlet side to the wedge-shaped inclined surfaces B1 to B8, g ₁ is a gap on the outflow side, and a value of g ₂ / g ₁ = 2 to 4 is normal. , L and θ are determined. From the above, when the outer diameter of the impeller 20 is small, the area (b × L) that can be opposed to the wedge surface portion 25-1 (25-2) is narrowed and the wedge effect is reduced. There is a tendency to greatly decrease as the value becomes narrower.

  As a countermeasure against the reduction of the wedge effect, when the outer diameter of the impeller 20 is small, the blades of the impeller 20 are left as they are, and only the side plates of the impeller 20 are enlarged, and the facing casing side plates 21-1, 21-2 are opposed. It is desirable to expand the wedge surface portions 25-1 and 25-2. That is, as shown in FIG. 8, while providing the extension part 20-1-1 and 20-2-1 in the outer periphery of the impeller side board 20-1 and 20-2 which comprises the impeller 20, the casing side board 21 facing this is provided. The necessary wedge effect can be secured by enlarging the wedge surface portions 25-1 and 25-2 of -1 and 21-2.

  In the pump device 40, only the rotor 30 has to use metal in the liquid. In order to prevent corrosion (electric corrosion), the exposed surface (contact surface with the liquid) needs to be sufficiently coated or lined with resin or the like, but the rotor 30 with coating or the like is applied to the impeller 20. When installing, it should be attached indirectly, not directly with screws or screws. That is, as shown in FIG. 10, it is desirable that the rotor 30 is not directly attached to the impeller 20 with screws 30-2, but is attached via an auxiliary mounting plate 30-1 made of resin. This is because, when a screw hole is made in the rotor 30, it is difficult to completely coat the inside of the screw hole, and if there is a poorly coated part inside the screw hole, this causes electric corrosion. .

  Due to the rotational force, the repulsive force, and the wedge effect that the rotor 30 receives from the rotating magnetic field device (the outer magnet 33, the inner magnet 34, and the magnet holder 35) during the period from the start to the full speed operation of the pump device 40 of the present embodiment. FIG. 11 is a graph showing the characteristics of the repulsive force caused by the liquid flow between the can 38 and the rotor 30. In FIG. 11, the horizontal axis represents the speed of the rotor 30 (slip S), and the vertical axis represents the rotational force T received by the rotor 30, the repulsive force Fm received by the rotor 30 from the magnetic field, and the repulsive force FA caused by the wedge effect. The characteristics are shown.

  In FIG. 11, a curve C1 shows a rotational force T, a curve C2 shows a repulsive force Fm caused by a magnetic field, and a curve C3 shows a repulsive force FA caused by a wedge effect. Here, the slip S is S = (no−n) / no when the rotational speed no of the outer magnet 33 and the inner magnet 34 and the rotational speed n of the rotor 30 are set. The rotational force T received by the rotor 30 by the rotating magnetic field approximates the rotational force-speed characteristic of a general-purpose drive motor having an extremely large gap, and thus is approximately C1. The repulsive force Fm received by the rotor 30 from the rotating magnetic field is a repulsive force when S · Rm> 1, and is attracted when S · Rm <1. Here, Rm is a numerical value determined by a magnetic gap between the magnets 33 and 34 and the rotor 30, a thickness of the rotor 30, a material, and the like, and is called a magnetic Reynolds number.

  As shown in FIG. 11, the point at which S is maximized, that is, S = 1 at the time of activation, the repulsive force is maximum at this time. That is, since the rotor 30 receives the maximum repulsive force at the time of startup, the rotor 30 first floats and then starts to rotate. Thereby, the sliding between the rotor 30 and the can 38 does not occur at the time of starting, which is convenient.

  On the other hand, when the rotational speed of the rotor 30 increases, that is, when the rotational speed of the impeller 20 increases, the repulsive force becomes 0 at S = 0. However, the repulsive force generated by the wedge effect generated between the can 38 and the rotor 30 increases proportionally as the rotational speed of the rotor 30 increases as long as liquid exists. Assuming that the slip S1 is obtained when the rotor 30, that is, the impeller 20 is rotated normally, the repulsive force received by the rotor 30 is FmS1 + FAS1, and the rotor 30 is lifted and stabilized. However, if no liquid is present, FA = 0, the rotational speed of the rotor 30 further increases, Fm becomes extremely small, and the repulsive force is almost eliminated.

  This indicates that the repulsive force becomes extremely small when no liquid is present, and the rotor 30 and the can 38 slide. Therefore, it is necessary to take measures to prevent idling in the pump device, and at least when the casing 21 is empty, it is necessary to prevent the drive motor 37 from starting.

  Therefore, in the pump device 40 of this embodiment, as shown in FIG. 1 described above, a liquid sensor 29 for detecting the presence or absence of liquid is attached in the vicinity of the discharge port 27, and a liquid detection signal from the liquid sensor 29 is sent to the pump device. It is a start condition. That is, when there is no liquid detection signal from the liquid sensor 29, the drive motor 37 is not activated. Thereby, the idle driving | operation of the pump apparatus 40 can be prevented. As a means for preventing idling of the pump device 40, there is a method of filling the pump casing with liquid even when the pump is stopped.

  In the pump device 40 according to the present embodiment, the rotating part (the rotor 30 and the impeller 20) and the peripheral wall (the casing 21 and the can 38) are not only during the start, stop, and operation, but also in the fully opened and fully closed state of the discharge valve. No sliding trace was observed. Inspecting the rotating part with inspection coating, operating, and then checking for sliding according to the presence or absence of peeling of the inspection coating, there is no problem in testing with fine slurry or limestone liquid It was. In addition, it was confirmed that a reactivation can always be performed by attaching a check valve (not shown) to the suction pipe (not shown) connected to the suction port 26.

  As described above, the pump device 40 according to the present embodiment has a non-seal structure, does not have a bearing in the liquid, and the rotating portion (the rotor 30, the impeller 20) floats without contacting the peripheral wall (the casing 21, the can 38). In this state, it can be operated in a very stable state, so there is no contamination caused by sliding. In addition, since all the portions that come into contact with the liquid can be made of a synthetic resin material, a resin coating material, a ceramic material, or the like, it is not necessary to use a metal material for the liquid contact surface. Therefore, elution of metal ions into the liquid fed by the pump device 40 can be eliminated. In addition, the absence of a sliding part during operation realizes a drastic reduction in failure, prolongation of service life, and can be maintenance-free.

  Next, the automatic return function of the impeller 20 will be described with reference to FIGS. 1, 2, 7, and 12 to 14. 1 is a vertical sectional view showing the pump device 40, FIG. 2 is a partially cutaway exploded view of the pump device 40 shown in FIG. 1, FIG. 7 is a partially enlarged view of the pump device 40 shown in FIG. FIG. 13 is a diagram showing the behavior of the impeller 20 shown in FIG. 12, and FIG. 14 is a diagram showing the behavior of the impeller 20 shown in FIG.

  As shown in FIGS. 1, 2, 7, and 12, in the pump device 40, protrusions 20 px and 20 py that protrude in the diameter increasing direction along the outer circumferences of the two side surfaces 20 x and 20 y of the impeller 20. Annular wall 41x, which surrounds the respective protrusions 20px, 20py in the outer peripheral region rather than the protrusions 20px, 20py on the impeller casing inner side surfaces 21x, 21y respectively opposed to the two side surfaces 20x, 20y of the impeller 20. 41y is provided. Then, as shown in FIG. 12, when the impeller 20 moves in the direction of the rotational axis D (see FIG. 7), the flow rate adjusting surface 20xs that separates and approaches when the side surface 20x and the impeller casing inner surface 21x approach and separate from each other. , 41xs are provided at the opposing portions of the protrusion 20px of the side surface 20x and the annular wall 41x, respectively. Similarly, when the impeller 20 moves in the direction of the rotational axis D, when the side surface 20y and the impeller casing inner side surface 21y approach and separate from each other, the flow rate adjusting surfaces 20ys and 41ys that are separated from each other and approach each other, And the annular wall 40y.

  During normal operation, as shown in FIG. 12, the impeller 20 rotates while maintaining an equal interval from the impeller casing inner side surfaces 21x and 20y opposed to the two side surfaces 20x and 20y, respectively. Here, as shown in FIG. 13, when the rotating impeller 20 moves to the left along the rotation axis D (see FIG. 7) and one side surface 20x of the impeller 20 and the impeller casing inner side surface 21x approach each other, The flow rate adjusting surfaces 20xs and 41xs provided at the opposing portions of the protruding portion 20px on one side surface 20x and the annular wall 41x are separated from each other, and the protruding portion 20py on the other side surface 20y and the annular wall 41y are opposed to each other. The flow rate adjusting surfaces 20ys and 41ys provided in the portions approach each other. For this reason, the flow rate between one side surface 20x approaching each other and the impeller casing inner side surface 21x increases to increase the dynamic pressure, and the flow rate between the other side surface 20y and the impeller casing inner side surface 21y that are separated from each other. Decreases and the dynamic pressure decreases.

  Therefore, the impeller 20 that has moved to the left along the rotational axis D (see FIG. 7) has the same dynamic pressure on the side surfaces 20x and 20y of the impeller 20 due to the change in the dynamic pressure on the two side surfaces 20x and 20y described above. As shown in FIG. 12, the positions, that is, the gaps between the two side surfaces 20x and 20y of the impeller 20 and the inner side surfaces 21x and 21y of the impeller casing are automatically returned to the same position.

  On the other hand, as shown in FIG. 14, when the rotating impeller 20 moves to the right along the rotation axis D (see FIG. 7) and one side surface 20 y of the impeller 20 and the impeller casing inner side surface 21 y approach, The flow rate adjusting surfaces 20ys and 41ys provided at the opposing portions of the 20y protruding portion 20py and the annular wall 41y are separated from each other, and provided at the opposing portions of the protruding portion 20px and the annular wall 41x of the side surface 20x. The flow rate adjustment surfaces 20xs and 41xs approach each other. Therefore, the flow rate between the side surface 20y and the impeller casing inner side surface 21y that are close to each other increases and the dynamic pressure increases, and the flow rate between the side surface 20y and the impeller casing inner side surface 21y that are separated from each other decreases. Dynamic pressure decreases.

  Therefore, the impeller 20 that has moved to the left along the rotational axis D (see FIG. 7) has the same dynamic pressure on the side surfaces 20x and 20y of the impeller 20 due to the change in the dynamic pressure on the two side surfaces 20x and 20y described above. As shown in FIG. 12, the positions, that is, the gaps between the two side surfaces 20x and 20y of the impeller 20 and the inner side surfaces 21x and 21y of the impeller casing are automatically returned to the same position.

  Thus, even if the impeller 20 moves in any direction along the rotational axis D, the impeller 20 automatically returns to the state shown in FIG. It can be held in place. Therefore, contact and sliding between the rotor 30 and the impeller 20 and the casing side plates 21-1, 21-2 and the like surrounding them do not occur.

  By the way, the rotating impeller 20 moves to the left side (right side) along the rotation axis D, and as shown in FIG. 13 (FIG. 14), one side surface 20x (20y) of the impeller 20 and the inner side surface 21x of the impeller casing. When (21y) approaches and the liquid inflow amount between the flow rate adjustment surfaces 20xs, 41xs (20ys, 41ys) separated from each other increases extremely, the impeller moves violently toward the other side surface 20y (20x). Sometimes. Therefore, in the pump device 40, as shown in FIG. 12, through-holes 42x and 42y that respectively connect the inner peripheral region and the outer peripheral region of the two annular walls 41x and 41y are provided in the annular walls 41x and 41y. . If such through holes 42x and 42y are provided, the amount of liquid inflow between the flow rate adjusting surfaces 20xs and 41xs (20ys and 41ys) that are separated from each other is relieved. It can be moved to the position. In addition, since the shape of the through holes 42x and 42y is not limited, it can be circular or polygonal.

  The pump device of the present invention can be used for pure liquids and corrosive liquids, and can be widely used in various technical fields for pumping and transferring various liquids such as a fine slurry mixed liquid.

It is a vertical sectional view showing a pump device which is an embodiment of the present invention. It is a partially cutaway exploded view of the pump device shown in FIG. It is the X1-Y1 sectional view taken on the line in FIG. It is a figure which shows the behavior of the liquid in a casing in the pump apparatus without a partition in a casing. It is a figure which shows the contact state of the impeller in the pump apparatus shown in FIG. 4, a rotor, a casing, and a can. It is a figure which shows the behavior of the liquid in the casing in the pump apparatus shown in FIG. FIG. 2 is a partially enlarged view of the pump device shown in FIG. 1. It is the X2-Y2 line arrow directional view in FIG. It is a figure which shows the positional relationship of the wedge surface and impeller which comprise the pump apparatus shown in FIG. It is sectional drawing which shows other embodiment regarding the attachment structure of a rotor. FIG. 2 is an operational characteristic diagram of a rotor constituting the pump device shown in FIG. 1. FIG. 8 is a partially enlarged view of FIG. 7. It is a figure which shows the behavior of the impeller shown in FIG. It is a figure which shows the behavior of the impeller shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Impeller 2 Impeller and rotor connecting shaft 3 Impeller main casing 4 Impeller casing inner plate 5 Can 6 Inner / outer magnet holder 7 Outer magnet 8 Inner magnet 9 Rotor 10 Pump casing 11 Timing pulley 12 Timing belt 13 Drive motor 13a Output shaft 14 Tightening bolt 15 Suction port 16 Discharge port 20 Impeller 20a Suction hole 20c Impeller center 20px, 20py Protrusion 20x, 20y Side surface 20xs, 20ys, 41xs, 41ys Flow rate adjustment surface 20-1, 20-2 Impeller side plate 20-1-1, 20- 2-1 Extension side plate 20-3 Cylindrical body for balancing 21 Impeller casing 21x, 21y Inner side surface of impeller casing 21a, 25-3 Recessed groove 21-1, 21-2 Casing side plate 21-1-1 Auxiliary suction cylinder 22 Drive unit casing Main body 23 Casing main plate 23-1 Partition 23-1a One end 23-1b Other end 23-2 Outer wall 23-3 Upper discharge hole 23-4 Lower discharge hole 23-5 Closed wall 24 Discharge liquid passage 25-1, 25- 2 Wedge surface portion 25-3 Concave groove 26 Suction port 27 Discharge port 28 Tightening bolt 29 Liquid detection sensor 30 Rotor 30-1 Auxiliary plate for mounting 30-2 Screw 31 Inner can 31-1 Inflowing liquid adjustment boss 31-1a Protruding portion 32 Outer can 33 Outer magnet 33-1 Outer magnet yoke 34 Inner magnet 34-1 Inner magnet yoke 35 Magnet holder 36 Holder connecting shaft 37 Drive motor 38 Can 39 Arrow line 40 Pump device 41x, 41y Annular wall 42x, 42y Through hole D rotation axis _{P 1, P 2, P 3} , P 4 hydraulic Q ₁ rotor and the can contact point Q ₂ rotor and the can contact point Q ₃ in the in La and the casing of the contact point Q ₄ impeller and the inflow direction θ wedge inclined surface in the rotational direction W liquid contact point B1~B8 wedge inclined surface R impeller casing inclination angle g _1, and g ₂ wedge inclined surface and the impeller plate Clearance b Wedge-shaped inclined surface width L Wedge-shaped inclined surface length S Slip T Rotational force F Suction force Fm Repulsive force FA Repulsive force due to wedge effect C1 TS characteristic curve C2 Fm-S characteristic curve C3 FA-S characteristic curve S1 Normal operation Slip of time

Claims (2)

A metal cylindrical rotor fixed coaxially with the rotation axis of the closed impeller is indirectly driven by a rotating magnetic field generator arranged with a partition wall therebetween, so that the rotor and impeller are not moved in the casing. In the horizontal type pump device with a single suction, upward discharge and one side drive system, equipped with a mechanism for holding and rotating in a contact state,
Protruding ridges projecting in the diameter-expanding direction along the outer circumferences of the two side surfaces of the impeller are provided, and in the outer peripheral region than the ridges on the inner side surface of the impeller casing facing the two side surfaces of the impeller. Providing an annular wall surrounding each said ridge,
As the impeller moves in the rotational axis direction, when the side surface and the inner surface of the impeller casing approach and separate from each other, a flow rate adjustment surface that is separated from each other and approaches is provided on the projecting portion of the side surface and the opposed portion of the annular wall. Pump devices characterized by being provided respectively.   The pump device according to claim 1, wherein a through hole that communicates an inner peripheral region and an outer peripheral region of the annular wall is provided in the annular wall.

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