KR100190807B1 - Magnet pumps - Google Patents

Abstract

The present invention includes a sealed impeller having magnetic means and rotatably driven from the outside of the impeller, a pump casing in which the impeller is rotatably embedded in the pump chamber of the casing, and the suction side of the impeller. Provided with a fixed part fixed to the casing and a moving part fixed to the impeller, a bearing shaped to support radial and thrust forces acting on the impeller, and a magnetic force on the magnetic means of the impeller to rotatably drive the impeller A driving magnet mechanism mounted on the non-contacting part of the casing on the suction side of the impeller and opposed by the impeller to the direction of the axis of rotation of the impeller, and a bearing defined by the center of the driving magnet mechanism and the axis of rotation of the impeller It is formed through the center of the fluid inflow path between the intake port and the pump chamber A magnetic pump comprising: a magnetic means is formed by a permanent magnet embedded in an impeller, the permanent magnet is disc-shaped and oriented perpendicular to the axis of rotation of the impeller, and the outer diameter of the bearing is the inside of the permanent magnet embedded in the impeller It is characterized by smaller than the diameter.

Description

Magnet pump

1 is a longitudinal sectional view showing an embodiment of the present invention,

Figure 1a is a schematic diagram showing the main part of Figure 1,

1b is a plan view of the main portion of FIG.

2 is a longitudinal sectional view showing another embodiment of the present invention;

Figure 2a is a schematic diagram showing the state of the magnet of Figure 2,

2b is a longitudinal sectional view of FIG. 2a,

Figure 3 is a longitudinal cross-sectional view showing another embodiment of the present invention,

Figure 4 (a) (b) (c) is a schematic diagram showing another embodiment of the bearing of the present invention, (a) is a plan view, (b) is a sectional view,

5 is a longitudinal sectional view showing main parts of an embodiment of the impeller of the present invention;

6 is a longitudinal sectional view showing a conventional magnet pump,

6 is a pressure-flow performance curve of a conventional magnet pump,

7 is a longitudinal sectional view showing another conventional magnet pump.

* Explanation of symbols for main parts of the drawings

1: Casing 1a: Suction Cover

1b: rear cover 1c: pump chamber

1d: suction port 1e: discharge port

1f: fixed side bearing 1g: rotary side bearing

1k: inflow path 2: impeller

2b, 23, 34: magnet yoke

2c, 12, 22, 32, M1 ~ M8: permanent magnet

2g, 63: wings 2h, 64: abacus

5: stator 5b: iron core

5c Coil 7 Motor Cover

7b: connector 7c: air inlet

10 ball bearing 11a suction casing cover

11b: rear casing cover 11c: reinforcement plate

20: axis of rotation 35: screw

50: perturbation surface (spherical) 51: groove

52: arrow (rotation direction) 54: screw portion

55: sliding surface (circumferential surface) 56: sliding surface (plane)

57: sliding surface (cylindrical surface) 60b: upstream cover

60c: downstream cover 60d: junction

61d: junction 61b, 61c: container

62b: upstream impeller 62c: downstream impeller

62d: joint surface F1: magnetic attraction force

F2: Drust S, S1-S6: Projection

K1 to K6: Coil B: Bearing

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a so-called magnet pump for rotatably driving an impeller embedded with a magnet by an external magnetic force, and more particularly, a permanent magnet or stator in which a magnet embedded in an impeller is located away from the direction of the axis of rotation of the impeller. The present invention relates to a magnet pump employing an axial gap-type magnetic force transmission mechanism which is rotatably driven by magnetic force from the present invention, and is suitable for the transport and circulation of various chemical liquids due to the simple structure of the liquid contact portion.

Representative examples of the magnet pump described above are shown in FIGS. 6 and 7. The magnet pump shown in FIG. 6 is configured to rotatably drive the impeller of the pump by using the principle of magnet coupling between permanent magnets. The casing 1 of the pump includes a suction cover 1a and a rear cover 1b. And a pump chamber (1c) for accommodating the impeller (2), a suction port (1d) for suctioning the conveying fluid, and a pump chamber (1c) for accommodating the impeller (2), a suction port (1d) for sucking the fluid to be conveyed. ) And a discharge port 1e for discharging the fluid boosted by the impeller 2, and the non-contacting part of the rear cover 1b is rotatably driven by a drive source such as a motor not shown in the main shaft 3. A fixed magnet yoke 3a and a permanent magnet 3b fixed in a ring shape are provided on a surface of the magnet yoke 3a opposite to the back cover 1b and rotatably housed inside the pump chamber 1c. The inside of the impeller 2 is like a ring The permanent magnet (2c) of the ring-shaped net yoke (2b) is embedded are fixed to the impeller (2) by the rotation of the main shaft 3 is rotatably driven the fluid is conveyed. The ring-shaped permanent magnet 2c and the permanent magnet 3b may be one permanent magnet each formed in a ring shape, or a plurality of permanent magnets may be arranged in a ring shape. In any case, on the surface where the permanent magnets 2c and 3b face each other, the N poles and the S poles are alternately arranged in a ring shape. Since the force acting on the impeller 2 in the state where the impeller 2 is at rest is mainly the magnetic attraction force F1 of the permanent magnets 2c and 3b, the impeller 2 is directed to the back cover 1b. Since the pump is started from the abnormal state, the fixed bearing 1f is provided on the side of the rear cover 1b, and the rotating bearing 1g is installed on the rear surface of the impeller 2. It supports load and radial load.

Regarding the bearing which supports the rotation of this impeller 2, in this specification, the rotational coarse member (bearing 1g) and the fixed side coordinating member (bearing 1f) are respectively called a bearing as needed, These will be referred to as a pair of bearings.

In FIG. 6, the arrow of the magnetic attraction force F1 acting on the impeller 2 does not strictly indicate the position at which the force acts, but merely represents the component force in the direction of the rotational axis of the magnetic attraction force. .

When the impeller 2 rotates, the fluid is boosted, and the fluid pressure acts as a thrust force F2 for pressing the impeller 2 to the suction side. Accordingly, the suction force cover 1a is provided with a bearing 1h on the fixed side, and the bearing 2j on the rotation side is provided on a portion of the impeller 2 that faces the bearing 1h. The magnitude of the magnetic attraction force F1 of the permanent magnets 2c and 3b changes with the force of the fluid applied to the impeller 2, and the magnitude of the thrust force F2 also changes with the fluid pressure. Now, with reference to the pressure-flow performance curve of FIG. 6A, the case where the rotation speed of the impeller of the pump is rotated at a constant speed will be described. The vertical axis H indicates the discharge pressure of the pump, and the horizontal axis Q indicates the Since the centrifugal pump shown in FIG. 6 generally starts the pump with the valve on the discharge side closed, the operating point of the pump is at point A. When the opening of the discharge valve is gradually opened, the operating point of the pump is solid. Move right along (a) to reach point B. Among the ABs, the impeller 2 of the pump receives the thrust force F2 greater than the magnetic suction force F1 and is pressed against the suction cover 1a side and rotates. However, at the point B, the magnetic suction force F1 is applied. When the thrust force F2 becomes equal and the flow rate is increased again by increasing the valve opening degree, the magnetic attraction force F1 becomes larger than the thrust force F2, so that the impeller 2 is placed on the rear cover 1b side. Pressed and rotated (point C.) At point C, the impeller 2 rotates at a position away from the suction cover 1a, so that the bearing clearance between the high pressure portion and the low pressure portion increases, and the pressurized fluid circulates to the suction portion. Since the amount increases, the discharge pressure of the pump is lower than the point B. If the valve is opened again, the operating point of the pump reaches point D along the solid line. Then, while the valve opening degree is gradually closed from the point D, the pump operating point reaches the point E after passing through the point C because the magnetic attraction force F1 is larger than the thrust force F2. At the point E, the magnetic attraction force F1 and the thrust force F2 become equal, and when the strength of the valve decreases, the impeller 2 has the same thrust force F2, and when the strength of the valve decreases, the impeller ( 2) is pressed against the suction cover 1a side by the thrust force F2 to rotate, and the operation point reaches the F point. As described above, in the magnet pump of FIG. 6, the pressure-flow performance curve of the pump draws a hysteresis curve. Thus, as described above, the impeller 2 may be driven by the suction cover 1a and the rear cover 1b according to the operating state. Rotate to one side.

The magnet pump of the conventional example shown in FIG. 7 is a magnet pump which drives the magnet embedded in the impeller to be rotatable directly by the electromagnetic force generated in the stator. The basic configuration of the casing 1 and the impeller 2 is shown in FIG. The same as in the conventional example shown, except that the driving magnetic force mechanism, which is a means for rotatably driving the impeller 2, is the stator 5. That is, the stator 5 for driving the magnet embedded in the impeller wraps the coil 5a around the iron core 5b arranged in a ring shape, and the rear cover 1b of the position opposite to the magnet of the impeller 2 is formed. The impeller 2 is rotatably driven in accordance with the operation principle of the so-called DC brushless motor by being provided in the non-contacting part and appropriately energizing these coils 5a from a power supply control circuit not shown. The magnet pump of FIG. 7 also exhibits the same performance curve as that of the pump of FIG. 6 shown in FIG. 6A. The impeller 2 has the suction cover 1a side or the rear cover 1b side depending on the pump operating conditions. It is rotated by being biased to either side of.

In the above-described conventional magnet pump, when the pump is operated, the impeller 2 moves in the direction of the axis of rotation 20 of the impeller in accordance with the driving condition. That is, the permanent magnet 2c embedded in the impeller 2 with respect to the force in the direction of the rotation axis 20 acting on the impeller 2 and the permanent magnet 3b or stator on the driving side for rotatably driving the impeller 2 5) The operating area in which the direction of the combined force between the magnetic attraction force F1 acting between the hydrodynamic pressure force F2 acting on the impeller and the hydraulic force acting on the impeller is directed toward the suction cover 1a (in the performance curve of FIG. A → B, F → A), on the contrary, the driving region (C → D, D → E in the same performance curve) toward the rear cover 1b, and the unstable region (transition region) In the performance curve of the figure, there are B → C, E → F), and the position of the impeller moves in various ways depending on the operation state of the pump. When the impeller 2 is moved in the axial direction, an impact load is applied to the bearings. At this time, the impeller rotates eccentrically with its own rotational speed, and therefore, a sliding contact phenomenon occurs on the sliding surface of the bearing, thereby There was a problem of breaking.

The above phenomenon is particularly problematic when bubbles are included in the conveying fluid. When the fluid containing bubbles is boosted in accordance with the centrifugal action of the impeller 2, the discharge pressure changes drastically, As a result, the thrust force F2 changes due to the fluid pressure, and as a result, the impeller 2 vibrates in the direction of the axis of rotation, but only the discharge pressure of the pump fluctuates, causing the pump to generate other strange sounds. In addition to vibration, bearings may be momentarily broken. In the above-described conventional example, the bearings are provided at the positions of the suction cover 1a side and the rear cover 1b side of the impeller, respectively, and they must be assembled so that they are all parallel or perpendicular to each other. There was a problem in processing of each part, and a problem in their assembly.

In addition, the fact that the bearings are easily damaged means that the fragments of the bearings are mixed in the fluid when transported without contaminating extremely high-purity fluids. In the case of carrying out, the surface treatment layer may be peeled off, even if the function of the pump is maintained.

It is an object of the present invention to provide a magnet pump in which forces in various rotational axis directions acting on the impeller of the pump are in one direction so as to prevent unstable movement of the impeller, and without contaminating a fluid having high purity. It is an object to provide a magnet pump suitable for conveying.

In order to achieve the above object, the present invention provides a magnet pump for rotatably driving an impeller embedded with a permanent magnet by a magnetic force from the outside of the impeller, the pump having a suction port, a discharge port and a pump chamber in which the impeller is accommodated. The magnetic force is applied to the casing, an impeller rotatably housed in the pump chamber of the casing and embedded with permanent magnets, one side of which is fixed to the casing, and one side of which is fixed to the impeller, and a permanent magnet in the impeller. Means for actuating and driving the impeller rotatably, comprising a drive magnetic mechanism provided in the non-contact portion of the casing at a position opposed to the impeller with respect to the direction of the axis of rotation of the impeller, and communicating the suction port with the pump chamber. The inflow path of the fluid is formed through the central portion of the drive magnetic mechanism And.

The second invention of the present invention is particularly suitable for a magnet pump of a type in which an impeller is rotated using the principle of permanent magnet coupling, wherein the impeller embedded with permanent magnet is rotated by a magnetic force from the outside of the impeller. A magnet pump configured to be capable of driving, comprising: a casing of a pump having a pump chamber in which an inlet port, a discharge port, and an impeller are housed; an impeller rotatably housed in a pump chamber of the casing; A means fixed to the casing, the other of which is fixed to the impeller, and a means for applying the magnetic force to the permanent magnet in the impeller to rotatably drive the impeller against the impeller with respect to the direction of the axis of rotation of the impeller; With a driving magnetic force mechanism having a permanent magnet rotatably installed in the non-contact portion of the casing in position The inflow path of the fluid communicating with the suction port and the pump chamber is formed through the central portion of the driving magnetic force mechanism.

The third invention of the present invention is also suitable for a magnet pump in which the impeller is rotated by the action of an electromagnetic force, and the impeller in which the permanent magnet is embedded is rotatably driven by the magnetic force from the outside of the impeller. A magnet pump comprising: a casing of a pump having a pump chamber for accommodating an inlet, an outlet port, and an impeller; an impeller and one end rotatably housed in the pump chamber of the casing; A bearing whose side is fixed to the impeller and a means for applying the magnetic force to the permanent magnet in the impeller so as to rotatably drive the impeller, the ratio of the casing at a position opposite the impeller with respect to the direction of the axis of rotation of the impeller. It is provided with a driving magnetic force mechanism by a stator fixed to the liquid contact portion, the suction port and the pump An inflow path for fluid communicating with the seal is formed through the central portion of the drive magnetic force mechanism.

The fourth invention of the present invention is a configuration suitable for a magnet pump of a type in which the impeller is rotated using the principle of permanent magnet coupling, similarly to the second invention, and an impeller having permanent magnets embedded therein In a magnet pump that is rotatably driven by an external magnetic force, a casing of a pump having a pump chamber in which an inlet port, an outlet port, and an impeller are accommodated, a pump chamber of the casing is rotatably housed, and a permanent magnet is embedded An impeller formed, a bearing fixed to the casing at one end thereof, a bearing fixed at the impeller at the other side, and a means for applying the magnetic force to the permanent magnet in the impeller so as to rotatably drive the impeller. Permanently installed freely on the non-contact part of the casing at a position opposite to that impeller And a stator fixed to a non-contact part on the semi-impeller side of the drive magnet mechanism, as a means for transmitting a rotation to the drive magnet mechanism, wherein the fluid communicates with the suction port and the pump chamber. The suction passage is formed to penetrate the center portion of the drive magnetic mechanism and the center portion of the stator, respectively.

The permanent magnet embedded in the impeller is housed in an inorganic container, and the inflow passage penetrates the center portion of the bearing fixed to the casing side.

In addition, the bearing is made of ceramic, and one side thereof has a groove for generating dynamic pressure on the sliding surface, and the ceramic has a silicon carbide sintered body as a base material, and the surface of the base material is formed of silicon carbide by thermal CVD. It is composed by coating a thin film. Spiral group bearings in which 100 to 200 microns of silicon carbide are formed by thermal CVD on the surface of the silicon carbide sintered body and the spiral grooves are formed on the surface of the CVD layer are not only excellent in corrosion resistance but also excellent in abrasion resistance and a base material. Because of the similar physical properties between the silicon carbide sintered compact and the silicon carbide thin film formed on the surface by thermal CVD, the adhesion strength between them is large, and it is also resistant to thermal changes and impacts, resulting in highly reliable bearings.

Since the present invention is constituted as described above, the magnetic force for rotatably driving the impeller embedded with the permanent magnet is applied from the driving magnetic mechanism external to the impeller, and the driving magnetic mechanism is located at the suction port side of the pump casing. Therefore, the component force in the direction of the axis of rotation of the impeller of the magnetic force acting between the impeller and the driving magnetic mechanism always becomes a force that pushes the impeller in the direction of the driving magnetic mechanism, and again the fluid boosted by the rotation of the impeller Since the force in the rotational axis direction acting on the impeller also becomes the force for pressing the impeller toward the suction inlet side, i.e., the direction of the driving magnetic force mechanism, the force in the rotational axis direction acting on the impeller is constant in any case, even if the pump is operated. In other words, there is no unstable area as a force for pressing the impeller in the direction of the driving magnetic force mechanism.

In addition, even when bubbles are included in the fluid to be conveyed and the discharge pressure of the pump varies, the direction of the magnetic attraction force and the thrust force acting on the impeller 2 is the direction in which the impeller is pressed against the driving magnet mechanism side. Because of this, it does not displace greatly in the direction of the impeller rotation axis.

Next, an embodiment of the present invention will be described with reference to the drawings. 1 is a longitudinal cross-sectional view of the first embodiment of the present invention, and also a third embodiment.

In the figure, the pump casing 1 is composed of a suction cover 1a having a suction port 1d of a fluid and a rear cover 1b having a discharge port 1e of a pressurized fluid. A pump chamber 1c for accommodating the impeller 2 is formed by the rear cover 1b, and the bearing 1g on the rotating side and the bearing 1f on the fixed side are respectively formed on the impeller 2 and the suction cover 1a. It is fixed and the pump chamber 1c and the suction port 1d are communicated by the inflow path 1k. The material of these parts constituting the casing 1 should have corrosion resistance to the fluid to be transported according to the purpose of the pump, but at least the suction cover 1a placed in the magnetic field of high magnetic flux density is preferably a nonmagnetic material. Do.

The impeller 2 rotatably housed in the pump chamber 1c is a ring-shaped permanent magnet 2c attached to the surface of the suction cover 1a side of the magnet yoke 2b formed in a ring shape, and is usually embedded. Nonmagnetic materials such as nylon and fluororesin are used for sealing by known means such as welding or welding, and invasion of the fluid into metal parts is prevented. Moreover, the impeller 2 is provided with the blade | wing 2g so that predetermined | prescribed pump performance may be exhibited. In FIG., In order to improve pump efficiency, the main plate 2h is provided and it is set as the closed blade | wing. The inner surface of the suction cover 1a, that is, the part facing the pump chamber 1c, is fitted with a bearing 1f on the fixed side with the concave surface facing the impeller 2 side, and this and the axis of rotation of the impeller 2 ( In the part of the impeller 2 which opposes the direction 20), the bearing 1g on the rotation side which faces the convex surface corresponding to the concave surface of the bearing 1f on the fixed side to the concave surface is inserted, The friction between the bearing 1f and the bearing 1g supports the thrust load in the direction of the rotation axis 20 and the radial load in the direction perpendicular to the rotation axis.

In addition, a stator 5 serving as a driving magnetic force mechanism, which is a means for rotatably driving the impeller by applying a magnetic force to the permanent magnet 2c embedded in the impeller 2, has a ratio of the suction cover 1a. It is arranged in the liquid contact portion, the magnetic force is generated by energization from a power supply (not shown) so as to rotatably drive the impeller 2, the suction port according to the direction of the rotation axis 20 of the impeller 2 in the center An inflow passage 1k for fluid that communicates between 1d and the pump chamber 1c is formed. Therefore, the fluid flowing into the pump penetrates through the central portion of the driving magnet mechanism in the direction of the rotation axis 20 of the impeller 2, and is boosted by the action of the impeller 2 rotating in the pump chamber 1c to pump the pump chamber ( Via 1c, it is led from the discharge port 1e to the outside of the pump.

1A and 1B are schematic diagrams showing the outline of the power transmission of the magnet pump of the embodiment of FIG. 1, FIG. 1A is a longitudinal cross-sectional view, and FIG. 1B is a side view seen from the right side of FIG. 1A, showing the magnet yoke 2b. Omitted.

In the drawing, six projections S1 to S6 are radially formed on the side facing the permanent magnet 2c in a ring-shaped iron core 5b made of ferromagnetic material, and coils k1 to k6 are respectively formed on each projection S1 to S6. It is wound. In this embodiment, the permanent magnets 2c are arranged in a ring shape by using eight fan-shaped permanent magnets M1 to M8. In this case, the permanent magnets M1 to M8 are magnetized in advance and stator ( On the surface opposite to 5), the S pole and the N pole are arranged alternately. In addition, although the permanent magnet 2c is divided like the fan-shaped magnets M1 to M8 to form one ring-shaped magnet, if necessary, one permanent magnet is formed into a ring shape to form an S pole and an N pole. The magnets may be magnetized so as to be alternately arranged, and the same applies to the later permanent magnets (12, 22, 32). The stator 5 is formed by laminating silicon steel sheets or by sintering iron powder and integrally molding the protrusions S1 to S6, and the number of the protrusions S1 to S6 is generally equal to that of the impeller 2. In order to ensure the start and smooth rotation, the number of poles different from the number of poles (8 poles in the embodiment) of the permanent magnet 2c is selected, and the number of poles is six in the embodiment.

The rotation of the permanent magnets 2c is performed by appropriately switching the energization of direct currents to the coils k1 to k6 based on signals from magnetic pole detection means such as hall elements (not shown).

As described above, in the magnet pump of FIG. 1, the impeller 2 is rotated by the supply of electricity to the stator 5 to boost and transport the fluid. At this time, if the rotational speed of the impeller 2 is the rated rotational speed, the pressure of the fluid acting on the impeller 2 generates a thrust force that presses the impeller 2 to the left in FIG. . On the other hand, since the force acting on the impeller 2 by the stator 5 is the force of the impeller 2 toward the axis of rotation 20 at all times, it is the force that pushes the impeller 2 to the left as well. Even at an operation point such as the above, operation can be continued at a stable position without changing the position.

In addition to the magnetic force by the stator 5 and the force of the fluid boosted by the pump, the impeller 2 acts on the gravity or the fluid pressure of the bearings 1f and 1g, but the magnet pump of FIG. Depends on whether it is installed vertically or horizontally, but the direction of gravity is different, but since it does not affect practically, the explanation is omitted. Again, the fluid pressure in the bearing is normal and the bearing functions as a sliding surface. If the fluid film is formed, reaction force is generated uniformly in the load applied to the bearing, and therefore, the size thereof will not be described in detail here.

2 is an embodiment corresponding to the second invention and an embodiment of the fourth invention in the later stage, and the configuration of the drive magnetic mechanism is different from the above embodiment. That is, in the second aspect of the invention, the permanent magnet is used as a drive magnet mechanism as a means for rotatably driving the impeller 2 embedded with the permanent magnet by an external magnetic force. The magnetic force of the magnet ring is directly used to install the permanent magnet embedded inside the impeller 2, and the permanent magnet is freely installed on the non-contacting part of the casing, and the impeller 2 is rotated. It is made to be possible to drive. Therefore, the detailed description about the part which is common in FIG. 1 is abbreviate | omitted, and the outline is demonstrated.

In the drawing, the casing 1 having the suction port 1d, the discharge port 1e, and the pump chamber 1c comprises a suction cover 1a and a rear cover 1b, and an impeller 2 inside the pump chamber 1c. ) Is accommodated. The outer side of the casing 1 is reinforced by the back casing cover 11b, the suction casing cover 11a, and the reinforcement board 11c fixed to the suction casing cover 1, respectively. A ball bearing 10 is fixed to the inner circumference of the suction casing cover 11a located at the non-contacting part of the casing 1, and a ring-shaped permanent magnet 12 is fixed to the inner ring thereof. Therefore, the ring-shaped permanent magnet 12, which is a driving magnetic force mechanism for rotatably driving the impeller 2, is rotatably installed in the non-contact portion of the casing 1 with little influence of the fluid inside.

The permanent magnet 12 is basically attracted to each other by the permanent magnet 2c embedded in the impeller 2 and the magnetic force, but the permanent magnet 12 on the driving magnet mechanism side is also an impeller 2. As shown in FIG. 2, the magnetic poles are alternately arranged in the same manner as the permanent magnet on the) side. When the permanent magnet 12 on the driving magnet mechanism side rotates, the impeller 2 also rotates in synchronization with this. In addition, the permanent magnet 12 on the side of the drive magnet mechanism is not only a drive magnet mechanism for directly rotating the impeller 2 but also receives the action of the magnetic force for itself to rotate from the stator 5. . As shown in Figs. 2A and 2B, the magnetized state of the permanent magnet 12 is magnetized opposite to each other on the surface opposite to the impeller 2 of the ring-shaped permanent magnet 12. It is. In this way, the permanent magnet 12 has a function as a driving source for the impeller 2, and has a function as a follower for the stator 5. Although the permanent magnet 12 is an integral ring-shaped permanent magnet in the drawing, a plurality of permanent magnets may be divided and arranged in a ring shape to alternately arrange the N pole and the S pole.

In this second embodiment, the inflow path 1k communicating with the pump chamber 1c and the inlet 1d is a permanent magnet 12 which is a driving magnetic force mechanism in accordance with the rotation shaft center 20 of the impeller 2; Although each penetrates through the central portion of the stator 5, in the second invention, the permanent magnet 12 may be rotated by a turbine or a motor, for example, via a gear as a means for rotating the driving magnetic force mechanism. It is preferable that these turbines and motors are not necessarily located on the same axis as the drive magnetic mechanism.

In this embodiment, both the magnetic attraction force F1 acting on the impeller 2 and the thrust force F2 due to the fluid become a force for pressing the impeller 2 toward the driving magnetic force mechanism, and the load is The bearing 1g on the rotating side fixed to the impeller 2 and the bearing 1g on the rotating side fixed to the suction cover 1a opposite to this and the fixed side fixed to the suction cover 1a opposite to this It is supported by the main raceway between the bearing 1f, and the impeller 2 rotates in a stable position similarly to the embodiment of FIG. In addition, in the figure, 7 is a motor cover for accommodating the stator 5, 7b is a connector for supplying electricity from a power supply not shown, and 7c is an air supply for supplying cooling air to the stator 5 portion. It is.

3 is an embodiment corresponding to the fourth invention, and the configuration of the driving magnetic mechanism is different from that of the first embodiment. Therefore, the differences will be described based on these differences.

In the figure, a casing 1 having a suction port 1d, a discharge port 1e, and a pump chamber 1c comprises a suction cover 1a and a rear cover 1b, and an impeller 2 inside the pump chamber 1c. ) Is rotatablely demanded. The outer side of the casing 1 is reinforced by the back casing cover 11b, the suction casing cover 11a, and the reinforcement board 11c fixed to the suction casing cover 11a, respectively. The ball bearing 10 is fixed to the inner circumference of the suction casing cover 11a located at the non-contacting part of the casing 1, and the magnet yoke is provided with a permanent magnet 22 of the driving magnet mechanism on the inner ring thereof. The magnet yoke 34 having the permanent magnet 32 on the driven side which receives the magnetic force of the stator 5 is fixed to the half impeller 2 side again by the screw 35 to fix the driving force. The permanent magnet 22 on the mechanism side and the permanent magnet 32 on the driven side are integrated to rotate.

The stator 5 for rotating the driven permanent magnet 32 is fixed inside the motor cover 7 which is integrally connected with the suction casing cover 11a which contacts the non-contacting part of the casing 1. It is accommodated, and the projection S of the iron core 5b is disposed opposite to the permanent magnet 32 on the driven side. When electricity from a power supply (not shown) is supplied to the coil 5a via the connector 7b, a magnetic field is generated in the projection S of the iron core 5b, and the projection S is in the direction of the rotation axis 20. The permanent magnet 32 on the driven side, which is spaced apart from each other, rotates by this magnetic field, and is again integrated with the magnet yoke 34 on the driven side, and the magnet yoke 23 on the driving magnetic force mechanism side rotatably supported. Is rotated with the magnet yoke 34 on the driven side, and thus the permanent magnet 22 of the driving magnet mechanism rotates to generate a driving magnetic force for rotating the impeller 2. In the third embodiment, the same number of magnetic poles are magnetized to the permanent magnets 2c embedded in the impeller 2 and the permanent magnets 22 of the driving magnet mechanism, and the permanent magnets on the driven side ( For 32), it is preferable that the magnetic poles alternately magnetize by the number of poles in which the most suitable power transmission is achieved in relation to the stator 5.

Thus, in the embodiment of FIG. 3, the permanent magnet 22 is used for the drive magnet mechanism for directly rotatable driving the permanent magnet 2c embedded in the impeller 2, and the drive magnet mechanism is The stator 5 is used as a means for rotating, and the suction path 1k which communicates with the suction port 1d and the pump chamber 1c is formed in accordance with each center part, ie, the center of rotation of the impeller 2.

Also in this case, both the thrust force (2) of the fluid acting on the impeller (2) and the component force (F1) in the direction of the rotational axis of the magnetic attraction force applied by the impeller (2) of the driving magnetic force mechanism of the impeller (2) It acts in the side pressing direction, and the load is between the bearing 1g of the rotating side fixed to the impeller 2, and the bearing 1f of the fixed side fixed to the suction cover 1a opposite to this. It is supported on the sliding surface of the impeller 2, similarly to the embodiment of the present invention shown in Figs. 1 and 2, to rotate in a stable position.

In the present invention, the power transmission between the impeller 2 and the driving magnetic force mechanism uses the principle of permanent magnet coupling as in the second embodiment (figure 2). The loss of power in the transmission process of the magnetic force can be completely ignored as long as the materials of the suction cover 1a and the reinforcing plate 11c are properly selected, and the stator functions as a means for rotating the driving magnetic mechanism. Both (5) and the driving magnetic mechanism are in the non-contact part. The energy conversion from electricity to the rotational torque in the stator 5 is a process involving a considerable loss, and in general, the magnetic gap is a large factor. However, as is apparent from the implementation of FIG. 3, since the configuration that generates the rotational torque in the stator 5 is in the non-contacting portion, the magnetic gap can be made small, which makes it possible to construct an efficient magnet pump. have.

In addition, in the drawing, 7 is a motor cover for accommodating the stator 5, 7b is a connector for supplying electricity from a power supply not shown, and 7c is an air supply for supplying cooling air to the stator 5 portion. 9d is an exhaust port of the cooling air.

4 and 5 are for explaining the preferred embodiment of the magnet pump of the present invention by element, and FIG. 4 is a summary of the bearing, and FIG. 5 is related to the impeller.

(A), (b), (c) are the top view (a) and sectional drawing (b) which showed the outline of the bearing which showed the other Example suitable for the magnet pump of this invention. In the magnet pump according to the present invention, the bearing is preferably a self-lubricating lubricating type bearing in which the fluid inside the pump chamber 1c is used as a lubricating liquid. Particularly, since the load capacity is large, a groove of about 10 microns is formed in one main surface. Spiral group bearings are most preferred. As a bearing material, a ceramic, which is a brittle material which is not easily deformed, is suitable, and in general, a ceramic sintered body such as a silicon carbide sintered body, a silicon nitride sintered body, and an aluminum oxide sintered body may be used. It is preferable to form a high purity ceramic thin film on the entire surface of the ceramic sintered body. Above all, a spiral group bearing having 100 to 200 micron silicon carbide formed on the surface of a silicon carbide sintered body by forming a spiral groove on the surface of the CVD layer is not only excellent in corrosion resistance but also excellent in wear resistance, In addition, since the physical properties of the silicon carbide sintered body of the base material and the silicon carbide thin film formed on the surface thereof by thermal CVD are similar, the adhesion strength between them is large, and they are also resistant to thermal changes and impacts, resulting in highly reliable bearings. The above-described bearings can also be applied to the above-described bearings, and basically all of them are self-lubricating dynamic pressure bearings, and among them, they are called spiral group bearings.

The same figure (a) shows the spherical dynamic pressure bearing shown in the above-mentioned embodiment, and shows only the rotating side bearing, and since the main surface 50 is spherical in shape, the spherical pearl 50 is spherical in the spherical surface 50. The groove 51 of the shape is formed. On the other hand, the surface of the fixed side bearing which is not shown in figure is made into the concave spherical surface as opposed to the said spherical surface 50. The arrow 52 indicates the rotational direction of the bearing B. As the bearing rotates in this direction, the sliding surface 50 is provided with a fluid film having a rigidity which is properly balanced according to the load. Since the sliding surface 50 is spherical in shape, the load of both a thrust force and a radial force can be supported.

Figure (b) shows a conical spiral group bearing, and shows the rotating shaft bearing. In this case, the sliding surface of the fixed side bearing (not shown) has a shape exactly opposite to the sliding surface 55 on the rotating side. It is concave. This rotation side bearing can support the load of both thrust and radial force by rotating the direction of the arrow 52, and especially the position of the impeller 2 is specifically ascertained in this bearing.

Figure (c) is a specific example of a quill-type spiral group bearing illustrated in the prior art and shows the rotary shaft bearing, the spiral group bearing portion 56 and the radial force of the plate supporting the thrust force In the sliding surface of the cylindrical side bearing portion 57 for supporting the bearing, and likewise not shown, it is necessary to have a sliding surface coincident with the sliding surfaces 56 and 57 on the rotation side. .

In the spiral group bearing, the sliding surface forming the groove may be the rotating side or the fixed side, and the rotating side bearings of the above-described drawings (a), (b) and (c) are provided on the fixed side. It may be.

5 is a sectional view of the main portion of the impeller 5, and any material between the iron magnet yoke 2b and the permanent magnet 2c fixed thereto is likely to be corroded. Therefore, it is not only sealed with organic polymer materials (nylon, PTFE, PFA, etc.), but also coated with an inorganic material having high airtightness, and the corrosion resistance of the metal material is increased, and the upstream cover is made of a resin excellent in corrosion resistance such as PFA. 60b), the downstream cover 60c is made, and the magnet yoke 2b and the permanent magnet 2c are accommodated in the upstream cover 60b and the downstream cover 60c, and the upstream cover 60b and the downstream cover 60c The fitting surface 60d is welded to embed the metal parts, and these are again accommodated in the ceramic containers 61b and 61c, and the outermost circumference is covered with the upstream impeller 62b and the downstream impeller 62c made of PTEF, and the joining thereof. The rotor part is sealed by welding the surface 62d. The vane 63 for boosting the fluid is previously formed integrally with the downstream impeller 62, and the main plate 64 is welded to the vane 63. In this way, even if the fluid penetrates the upstream and downstream impellers 62b and 62c of the outer circumferential PTFE in a gaseous state or a liquid form, penetration is prevented by the containers 61b and 61c made of an inorganic material. The magnet 2c and the magnet yoke 2b are kept healthy. In addition, since the containers 61b and 61c shown in FIG. 5 are comprised from the silicon carbide thin film formed by thermal CVD, the junction part 61d is sealed through the thin film of PFA.

In this way, even when transporting a highly permeable and highly corrosive fluid such as hydrofluoric acid, the metal parts embedded in the impeller 2 hardly corrode or corrode for a long time. .

If the fluid to be handled does not corrode quartz, such as sulfuric acid, nitric acid, or hydrochloric acid, the containers 61b and 61c in FIG. 5 are made of quartz, and the joint surface 61d is formed by a known means such as a laser. Complete welding is achieved by welding.

Further, by interposing the upstream cover 60b and the downstream cover 60c made of an elastic material between the metal member such as the permanent magnet 2c or the magnet yoke 2b and the weak containers 61b and 61c as described above. It is also possible to prevent damage to the container.

As described above, if the container is made of a glassy material such as quartz, and the joining surface can be completely sealed by means such as welding or welding, the upstream cover 60b and the downstream cover 60c and Similarly, it is not necessary to seal the metal material, but only to have a cushioning property so that the metal member and the container (inorganic material) do not come into point contact.

What was described about FIG. 4 and FIG. 5 mentioned above is applicable also to all the magnet pumps of this invention.

As described above, according to the present invention, a magnet pump includes a casing of a pump having a pump chamber in which an inlet port, a discharge port, and an impeller are accommodated, and an impeller in which the casing is rotatably housed in the pump chamber and embedded with a permanent magnet. And a means in which one side is fixed to the casing and the other is fixed to the impeller, and a means for rotatably driving the magnetic force on the permanent magnet in the impeller, the impeller with respect to the direction of the axis of rotation of the impeller. And a driving magnetic force mechanism provided in the non-contacting portion of the casing at a position opposite to the first and the inflow path of the fluid communicating with the suction port and the pump chamber to be formed through the central portion of the driving magnetic force mechanism in the direction of the rotation axis of the impeller. It has the following effect.

(1) The direction in which the component force in the direction of the rotational axis of the magnetic attraction force acting between the permanent magnet embedded in the impeller and the drive magnetic mechanism which is a means for directly driving the impeller rotatably acts on the impeller is always Since the direction in which the force of the fluid generated by the rotation of the impeller acts on the impeller is also the direction in which the impeller is always pushed toward the driving magnet mechanism, the driving point of the pump Even if the impeller rotates at a stable position with respect to the axial direction, no impact load is applied to the bearing, and the bearing is also prevented from being broken.

In addition, like the conventional magnet pump, the hysteresis phenomenon does not occur in the pump pressure-flow performance curve.

(2) Even if the handling fluid contains bubbles and there is no fluctuation in the discharge pressure of the pump, there is no hysteresis in the pump pressure-flow performance curve, so that the impeller can always rotate in a stable position, thus making it strange. Vibration is suppressed.

(3) Since the impeller is pressed against the driving magnetic force mechanism and rotates, the magnetic gap between the driving magnetic force mechanism and the impeller is as small as possible. Therefore, since the force for rotating the impeller always has the maximum value, the pump performance can be maximized.

(4) Since the impeller always rotates on the driving magnetic mechanism side, it is economical to install a pair of bearings for supporting the load between the impeller and the casing on the driving magnetic mechanism side.

(5) As described above, since the hysteresis phenomenon does not occur in the pump pressure-flow performance curve, there is no bias contact on the sliding surface of the bearing, so that damage to the bearing is remarkably reduced.

Especially in the 2nd and 4th invention of this invention,

(6) Since the driving magnet mechanism for rotatably driving the impeller is a permanent magnet, the magnetic attraction force acting on the impeller also has a centripetal action of maintaining the position of the impeller at a constant position relative to the direction perpendicular to the axis of rotation axis, Even if there is no axis which keeps a special impeller at a predetermined position in the radial direction, the impeller can be held at a suitable position by centripetal action based on this magnetic force.

On the other hand, in the third invention of the present invention,

(7) Since the stator is used as the driving magnet mechanism, in this magnet pump, the part that rotates is composed only of the impeller of the pump, and the other part is stopped, so that even in a clean environment such as a clean room, particles (particles) It is suitable for use in places where it is not reluctant to release it to the outside and there is no part to lubricate.

(8) It can be made into extremely small magnet pump.

Moreover, in the 4th invention of this invention,

(9) Since the driving magnet mechanism for applying the magnetic force for rotation to the impeller has a permanent magnet, regardless of the magnitude of the output of the magnet pump or the magnitude of the magnetic gap, the transmission of power between the impeller and the driving magnet mechanism is necessary. As for the material of the casing and its reinforcing member interposed between the impeller and the driving magnetic mechanism, there is little power loss if selected properly. Therefore, this power transmission process does not involve heat generation, and the driving magnetic mechanism and Since the stator for rotating the drive magnetic mechanism is located at the non-contacting part, efficient power transmission (energy-conversion) is performed, which can solve the problem of heat generation resulting from power loss, and also provides an efficient magnet pump. Can be configured.

Moreover, in the 5th invention of this invention,

(10) Since metal materials such as magnets and magnet yokes housed inside the impeller are housed in the inorganic container, the penetration of corrosion components in the fluid can be properly prevented or reduced, and the life of the pump is further extended. In addition, it is possible to significantly reduce the probability of releasing corrosion products derived from the metal member in the fluid.

Moreover, in the 6th invention of this invention,

(11) Since the inflow path penetrates the center portion of the bearing fixed to the casing side, the bearing is approximately between the impeller and the driving magnetic force mechanism in the rotational axis direction, and supports the impeller at that position. Various forces acting on the impeller such as magnetic attraction force (F1), impeller thrust force (F2) radial force, and gravity acting on the impeller support the load in the vicinity or center of its working point, You can do it.

Moreover, in the 7th invention of this invention,

(12) Since the bearing is made of ceramic and a groove for generating dynamic pressure is formed on the sliding surface thereof, the bearing not only has excellent corrosion resistance but also excellent wear resistance.

Moreover, in the 8th invention of this invention,

(13) As a bearing, a thin film of silicon carbide is coated on the surface of a silicon carbide sintered body by thermal CVD, and a spiral group bearing hardly elutes its constituents with respect to liquid in a temperature range of 200 ° C or lower. It is suitable for handling extremely high purity chemicals.

Claims (11)

A sealed impeller 2 having a magnetic means 2c and rotatably driven from the outside of the impeller; A pump casing (1) including a suction port (1d), a discharge port (1e), and a pump chamber (1c) such that the impeller (2) is rotatably embedded in the pump chamber (1c) of the casing (1); It is provided on the suction side of the impeller 2 and has a fixed portion 1f fixed to the casing 1 and a moving portion fixed to the impeller to provide radial and thrust forces acting on the impeller 2. Bearings 1f and 1g shaped to support; Means for providing a magnetic force on the magnetic means 2c of the impeller 2 so as to rotatably drive the impeller 2 so that the non-contacting of the casing 1 on the suction side of the impeller 2. A drive magnetic mechanism mounted on the liquid portion and facing the impeller 2 with respect to the direction of the rotation axis 20 of the impeller 2; And It is formed through the center of the drive magnetic mechanism and the center of the control ring (1g, 1f) defined by the rotary shaft core 20 of the impeller (2), between the suction port (1d) and the pump chamber (1c) In a magnet pump comprising a fluid inlet (1k) in communication, The magnetic means is formed by a permanent magnet (2c) embedded in the impeller (2), the permanent magnet (2c) is disc-shaped and oriented perpendicular to the axis of rotation 20 of the impeller (2), A magnet pump, characterized in that the outer diameter of the bearings (1f, 1g) is smaller than the inner diameter of the permanent magnet (2c) embedded in the impeller (2). The method of claim 1, The drive magnet mechanism comprises a permanent magnet (12, 32) rotatably mounted on a non-contact portion of the casing (1). The method of claim 1, The drive magnetic mechanism includes a stator (5) fixed to the non-contact portion of the casing (1). The method of claim 1, The drive magnet mechanism is fixed to the permanent magnet 22 rotatably mounted on the non-contact portion of the casing 1 and the non-contact portion of the casing 1 to provide means for transmitting rotation to the drive magnet mechanism. Magnet pump comprising a stator (5) constituting. The method according to any one of claims 1 to 4, The permanent magnet (2c) embedded in the impeller (2) is a magnet pump, characterized in that built in a container made of inorganic. The method according to any one of claims 1 to 4, The fluid inlet (1k) is a magnet pump, characterized in that penetrates through the center of the fixing portion (1f) of the bearing (1f, 1g) fixed to the casing (1). The method according to any one of claims 1 to 4, The bearing part (1f, 1g) is made of a ceramic material, and one of the bearing parts has a dynamic pressure generating groove (51) formed on its sliding surface. The method of claim 7, wherein The ceramic pump is based on a silicon carbide sintered body, the magnet pump comprising a thin film of silicon carbide coated on the surface of the base material by a thermal CVD process. The method of claim 5, The fluid inlet (1k) is a magnet pump, characterized in that penetrates through the center of the fixing portion (1f) of the bearing (1f, 1g) fixed to the casing (1). The method of claim 5, The bearing part (1f, 1g) is made of a ceramic material, and one of the bearing parts has a dynamic pressure generating groove (51) formed on its sliding surface. The method of claim 6, The bearing part (1f, 1g) is made of a ceramic material, and one of the bearing parts has a dynamic pressure generating groove (51) formed on its sliding surface.

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