JP2004251286A - In-line type pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve an output and efficiency of a pump. <P>SOLUTION: On the inner side of a cylindrical stator 102, a rotor 103 having an axial flow vane 108 to feed a fluid sucked from a suction port 117 axially toward a discharge port 119 is rotatably provided. A pressure chamber 122 is provided to convert the rotational motion energy of the fluid fed by the axial flow vane 108 toward the discharge port 119 into static energy. A second pressure chamber 123 is provided between the pressure chamber 122 and the discharge port 119 parted by a partition wall 121 from the pressure chamber 122. A guide hole 124 is formed at the outer circumferential part of the partition wall 121 to connect the pressure chamber 122 and the second pressure chamber 123 to each other. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

  The present invention relates to an in-line pump in which a flow path is formed inside a motor having a stator and a rotor as main components.

  As this type of in-line type pump, for example, as described in Patent Document 1 or Patent Document 2, a rotor provided inside a stator has an axial flow by forming a projection and a recess on the outer periphery. It has a function of a blade, and has a structure in which a fluid sucked from a suction port on one end side of the rotor is discharged from a discharge port on the other end side of the rotor by rotating the rotor.

JP-A-10-246193 Japanese Patent Application Laid-Open No. 230088/1990

  In the above-described in-line type pump, rotational kinetic energy is imparted to the fluid by the axial flow blade, and the kinetic energy is not converted to static pressure energy. Since it is sent after being lost as a vortex loss, the efficiency as a pump is poor.

  Further, since the fluid always flows only in one axial direction of the rotor, the reaction pressure of the fluid acts on the rotor as a thrust load, and there is a problem that the life of the bearing is shortened.

  SUMMARY OF THE INVENTION An object of the present invention is to provide an in-line pump capable of improving the supply efficiency of a fluid while satisfying the miniaturization of the structure.

  The invention according to claim 1 is an inline-type pump in which a rotor having an axial flow blade for axially sending fluid sucked from an inlet toward an outlet is rotatably provided inside a cylindrical stator, A pressure chamber that converts rotational kinetic energy of the fluid sent to the outlet by the axial flow blade of the rotor into static pressure energy, and a pressure chamber disposed between the pressure chamber and the outlet. Has a second pressure chamber defined by a partition wall, and a guide hole disposed on an outer peripheral portion of the partition wall and connecting between the pressure chamber and the second pressure chamber.

  Therefore, when the rotor is rotated, the fluid sucked from the suction port is sent to the pressure chamber by the axial flow blade, and the rotational kinetic energy is converted into static pressure energy in the pressure chamber. It is discharged from the outlet via.

  According to a second aspect of the present invention, in the in-line pump according to the first aspect, a sliding bearing that rotatably supports a rotating shaft of the rotor with a predetermined clearance is provided at a center of the partition wall, and the partition wall has a sliding bearing. Has a leak flow path communicating between the second pressure chamber and the inner peripheral surface of the slide bearing.

  Therefore, since the fluid in the second pressure chamber is interposed between the rotating shaft of the rotor and the sliding bearing with a uniform pressure distribution, the lubrication of the rotating shaft can be favorably maintained for a long time.

  According to a third aspect of the present invention, in the in-line type pump according to the first or second aspect, the second pressure chamber is provided with a second axial blade that rotates integrally with the rotor.

  Therefore, the fluid can be sent by dispersing the pressure by the axial flow blade provided inside the stator and the second axial flow blade provided in the second pressure chamber.

  According to a fourth aspect of the present invention, in the in-line type pump according to any one of the first to third aspects, the rotor has a plurality of magnetic poles on an outer diameter and a helical groove formed in an outer periphery and communicating in an axial direction. This constitutes the axial flow blade.

  According to a fifth aspect of the present invention, in the in-line type pump according to the fourth aspect, the diameter of the concave portion of the spiral groove in which the radius centered on the axis of the rotor is minimum is formed on the partition wall to support the sliding bearing. The diameter is set to be larger than the diameter of the formed support portion.

  Therefore, it is possible to reduce the vortex loss due to the collision between the fluid sent by the axial flow blade and the supporting portion that supports the sliding bearing, and it is possible to prevent cavitation.

  According to a sixth aspect of the present invention, in the in-line pump according to the fourth or fifth aspect, the width and the depth of the spiral groove are set to substantially equal values.

  Therefore, by appropriately setting the relationship between the width and the depth of the spiral groove, it is possible to reduce the flow path resistance and suppress the generation of a vortex. Thereby, the fluid can be sent more efficiently.

  The invention according to claim 7 is an inline-type pump in which a rotor having an axial flow blade for axially sending fluid sucked from an inlet toward an outlet is rotatably provided inside a cylindrical stator, A pressure chamber that converts rotational kinetic energy of the fluid sent to the outlet by the axial flow blade of the rotor into static pressure energy, and a centrifugal blade that is disposed in the pressure chamber and rotates integrally with the rotor, A suction path in which the fluid sucked from the suction port is guided to the pressure chamber via the outer peripheral portion of the stator, and is sent toward a surface of the centrifugal blade opposite to the axial flow blade. A flow path; and a guide flow path that guides fluid in the pressure chamber from an outer peripheral portion of the pressure chamber to a discharge port by rotation of the centrifugal blade.

  Therefore, when the rotor is rotated, the fluid sucked from the suction port is sent to the pressure chamber by the axial flow blade, where the rotational kinetic energy is converted into static pressure energy by the pressure chamber, and the suction flow path of another system is formed. Through the pressure chamber. The fluid guided to the pressure chamber through the two paths is discharged from the discharge port through the guide flow path by the rotation of the centrifugal blade. Thereby, the fluid can be sent efficiently. In this case, the centrifugal blade rotating integrally with the axial flow blade receives the pressure of the fluid sent by the axial flow blade and the pressure of the fluid sucked from the suction flow path, but in a direction in which the bidirectional pressures cancel each other. Since it acts, the thrust load given to the rotor by the fluid can be reduced, and the loss can be reduced.

  According to an eighth aspect of the present invention, in the invention of the seventh aspect, the connection portion of the guide channel with the pressure chamber is such that the energy of the flowing fluid is substantially equal at a symmetric position about the axis of the rotor. Stipulated in

  Therefore, the radial load on the rotor can be reduced. The fluid energy is energy that can be represented by a product of a fluid flow velocity and a pressure.

  According to the first aspect of the present invention, the rotational kinetic energy of the fluid sent toward the discharge port by the axial flow blade is converted into static pressure energy by the pressure chamber and then discharged from the discharge port via the second pressure chamber. As a result, the fluid can be sent efficiently, and the pump efficiency can be improved.

  According to the second aspect of the present invention, in the in-line pump according to the first aspect, the rotation shaft of the rotor is rotatably supported with a predetermined clearance at the center of the partition wall that partitions the first and second pressure chambers. Is provided, and the partition wall is formed with a leak flow path communicating the second pressure chamber and the inner peripheral surface of the slide bearing for supporting the rotary shaft. The fluid in the second pressure chamber can be interposed with a uniform pressure distribution between the sliding bearing and the sliding bearing, so that the lubrication of the rotating shaft can be favorably maintained for a long time.

  According to the third aspect of the present invention, in the in-line pump according to the first or second aspect, the second pressure chamber is provided with the second axial flow blade that rotates integrally with the rotor. The pressure can be dispersed and the fluid can be sent by the axial flow blade provided inside and the second axial flow blade provided in the second pressure chamber. Therefore, when the rotor is downsized, the decrease in the fluid feeding performance of the axial flow blade can be compensated for by the second axial flow blade. Thereby, the fluid can be efficiently sent while satisfying further miniaturization.

  According to a fifth aspect of the present invention, in the in-line pump according to the fourth aspect, the diameter of the concave portion of the axial flow vane having a minimum radius around the axis of the rotor supports the sliding bearing that supports the rotating shaft of the rotor. Therefore, the diameter of the support portion formed on the partition wall is set larger than the diameter of the support portion, so that the loss caused by the collision between the fluid sent by the axial flow blade and the support portion supporting the slide bearing can be reduced.

  According to the sixth aspect of the present invention, in the inline pump according to the fourth or fifth aspect, the axial flow blade has a spiral groove formed on the outer periphery of the cylindrical body, and the width and the depth of the spiral groove are substantially equal. Since the value is set to the value, the flow path resistance can be reduced and the generation of vortices can be suppressed. Thereby, the fluid can be sent more efficiently.

  According to the invention as set forth in claim 7, the rotational kinetic energy of the fluid sent toward the discharge port by the axial flow blade is guided to the pressure chamber to be converted into static pressure energy, and via a separate suction passage. Guided to the pressure chamber, and the fluid guided to the pressure chamber via these two routes is discharged from the outlet through the guide channel by the rotation of the centrifugal blade, so that the fluid can be sent efficiently Therefore, the pump efficiency can be improved. Further, since the pressure acting on the centrifugal vanes from the fluid sent by the axial flow vanes and the pressure acting on the centrifugal vanes from the fluid passing through the suction flow path are offset, the thrust load given to the rotor by the fluid is reduced. Can be reduced.

  According to the eighth aspect of the present invention, in the in-line pump according to the seventh aspect, in the connection portion of the guide flow path with the pressure chamber, the energy of the flowing fluid is substantially equal at a symmetrical position about the axis of the rotor. Therefore, the load on the rotor in the radial direction can be reduced.

(First Reference Example)
First, a first reference example will be described.

  As shown in FIGS. 1 to 5, the in-line type pump 1 includes a stator 3 constituting a main part of a motor 2, frames 5 and 6 for rotatably supporting a rotor 4 on an inner diameter of the stator 3, and a pressure chamber 7. It is composed of

  The stator 3 includes a stator core 9 having six poles of the same shape arranged at an inner circumference at a pitch of 60 °, and a coil 10 and the like for each magnetic pole 8 of the stator core 9. Stator core 9 is cylindrical and is formed by stacking a plurality of silicon steel plates in the axial direction. The coil 10 is wound around the magnetic poles 8 of the stator core 9 in the order of A-phase, B-phase, C-phase, A-phase, B-phase and C-phase in the counterclockwise direction. Then, each phase is wired in a Y-connection or a Δ-connection, three lead wires are drawn out, and a three-phase alternating current having a phase of 120 ° is applied to each lead wire, and the frequency is changed. The rotation speed can be changed.

  The entire inner peripheral surface of the stator core 9 of the stator 3 and the inside including the coil 10 are waterproofed by molding with an insulating resin 11 such as polyester.

  As shown in FIG. 3, the rotor 4 includes a rotor core 12, a rotating shaft 13 for holding the rotor core 12, and the like. The rotating shaft 13 is rotatably supported by bearing supports 15, 15 of the frames 5, 6 via bearings 14, 14.

  The rotor core 12 is formed by molding four salient poles 16 magnetized so as to have different polarities alternately in the circumferential direction into a cylindrical shape by molding, and has a spiral concave portion 17 formed in the outer peripheral portion thereof. The inner diameter of the stator 3 and the concave portion 17 form an axial fluid flow path. This spiral concave portion 17 functions as an axial blade. The width, depth, inclination angle, spiral pitch and the like of the concave portion 17 are selected according to the desired performance of the pump. That is, the helical pitch can be selected from 1 to N depending on the performance. The shape of the concave portion can correspond to any shape such as a V-groove and a U-groove.

  On the other hand, the frame 5 has a suction port 19 formed between one end 18 of the rotor 4 for sucking fluid, and the other frame 6 discharges fluid between the other end 20 of the rotor 4 via the pressure chamber 7. The discharge port 21 is formed. The suction port 19 is divided into four by fixed guide vanes 22 that bridge the frame 5 and the bearing support 15. The pressure chamber 7 has a function of smoothing and reducing the flow velocity of the rotating fluid. This pressure chamber 7 is arranged on the other end side of the rotor 4. The bearing supports 15 are provided on the inner periphery of the bottom diameter of the concave portion 17 of the rotor 4.

  Next, the operating principle of the in-line pump will be described with reference to FIGS. First, when the A-phase coil of the stator core 9 is excited, the A-phase magnetic pole 8 becomes the S-pole, and as shown in FIG. 4A, the N-pole salient pole of the rotor core 12 comes to the position of the A-magnetic pole. Stabilize. Next, when the B-phase coil is excited, the B-phase magnetic pole 8 becomes the S-pole, and as shown in FIG. 4 (b), the rotor core 12 has the N-pole salient pole located at the position of the B-phase magnetic pole 8. And stable. Next, when the C-phase coil is excited, the C-phase magnetic pole 8 becomes the S-pole, and the N-pole salient pole of the rotor core 12 comes to the position of the C-phase magnetic pole 8 as shown in FIG. Stabilize.

  Next, when the A-phase coil is excited again, the A-phase magnetic pole 8 becomes the S-pole, and as shown in FIG. 5 (a), the rotor core 12 moves the N-pole salient pole to the position of the A-phase magnetic pole 8. Come and be stable. Next, when the B-phase coil is excited, the B-phase magnetic pole 8 becomes an S-pole, and as shown in FIG. 5 (b), the rotor core 12 has the N-pole salient pole at the position of the B-phase magnetic pole 8. And stable. Next, when the C-phase coil is excited, the C-phase magnetic pole 8 becomes the S-pole, and as shown in FIG. 5 (c), the rotor core 12 has the N-pole salient pole located at the position of the C-phase magnetic pole 8. And stable. Then, when the A-phase coil is excited again, the magnetic pole 8 of the A-phase becomes the S-pole, and the rotor returns to the state shown in FIG. The rotor core 12 rotates by sequentially switching the excitation phases in this manner, and the speed of the motor changes by changing the switching speed.

  In the configuration of FIG. 1, when the rotor 4 rotates, the axial flow blade formed of a spiral concave portion on the outer peripheral portion of the rotor 4 rotates, and the fluid flows in from the suction portion as indicated by an arrow in the drawing. The fluid flows out of the outlet 21 through the spiral recess 17 of the stator 3 and the rotor 4 and further through the pressure chamber 7.

  As described above, since the spiral concave portion 17 communicating with the rotating shaft 13 in the axial direction is formed in the outer peripheral portion of the rotor 4 to form the axial flow blade, the shaft formed by the spiral concave portion 17 of the rotor 4 is formed. The fluid accelerated by the flow vanes is swirled. A pressure chamber 7 for converting the kinetic energy into pressure is provided on the discharge side of the rotor 4. The fluid discharged from the axial flow blades of the rotor 4 turns in the pressure chamber 7 and is diffused to the outer periphery. In the discharge flow, the flow velocity decreases toward the outer periphery, and the pressure increases. Although the load on the axial flow blade due to the provision of the pressure chamber 7 can be almost ignored, the inclination angle of the blade with respect to the axial direction is set to 45 to 70 °. As a result, in each of the axial flow blades, the discharge pressure and the flow rate were improved by about 50% as compared with those without the pressure chamber 7.

  Further, since the stator 3 is molded with the insulating resin 11 to perform waterproofing, the inline pump can be used underwater. As a result, the cooling effect can be enhanced, and sufficient heat radiation can be achieved even if the size is reduced.

(Second reference example)
Next, a second reference example will be described. The same parts as those in the first embodiment are denoted by the same reference numerals, and different parts will be described.

  As shown in FIG. 6, the other end 20 of the rotor 4 is arranged to extend to the inside of the pressure chamber 7. The bottom of the spiral concave portion 17 of the rotor 4 is gradually made shallow, so that the axial flow component is directed to the outer peripheral direction. Further, by providing the pressure chamber 7 facing the rotor 4 with the inclined section 23 as a rectifying section, it is possible to prevent the discharge flow from the axial flow blade from generating a turbulent flow due to a collision at right angles to the bottom surface of the pressure chamber 7. The pressure in the direction can be increased.

(Third reference example)
Next, a third reference example will be described. Note that the same reference numerals are given to the same portions as those in each of the above-described reference examples, and different portions will be described.

  As shown in FIGS. 7 and 8, the centrifugal blade 24 has a blade 25 inclined in the rotation direction. The centrifugal blade 24 is mounted on the rotating shaft 13 so as to face the blade 25 side and the other end 20 of the rotor 4, and is disposed in the pressure chamber 7. Since the swirling speed of the fluid is improved in the same size pump, it is effective in increasing the pump output and improving the maximum discharge pressure.

  In each of the reference examples, a rotor using a four-pole salient pole structure is described. However, it is needless to say that the present invention is not necessarily limited to this.

(First Embodiment)
A first embodiment of the present invention will be described with reference to FIGS. 9 is a vertical sectional side view of the in-line pump P1, FIG. 10 is a sectional view taken along line AA of FIG. 9, and FIG. 11 is a vertical sectional side view showing a part of the rotor.

  In FIG. 9, reference numeral 101 denotes a motor. The motor 101 includes a cylindrical stator 102 and a rotor 103. The stator 102 has a stator core 104 formed by laminating an annular iron core, a coil 105 wound around the stator core 104, and a resin layer 106 that covers the coil 105 together with the end face of the stator core 104.

  The rotor 103 has an axial flow blade 108 fixedly provided with a rotation shaft 107 at the center, and a magnetic pole 109 provided on a part of the outer periphery of the axial flow blade 108. The axial flow blade 108 in the present embodiment has a spiral groove 111 formed on the outer periphery of a cylindrical body 110, and the width w and the depth h of the spiral groove 111 are set to substantially equal values, as shown in FIG. Have been.

  A flange 112 is fixed to one end of the stator 102. The flange 112 has a dome-shaped support portion 114 for supporting a bearing 113 and an opening 115 opening around the support portion 114, and a plurality of rectifying plates 116 are radially formed in the opening 115. ing.

  A suction port body 118 having a suction port 117 for suctioning a fluid is fixed to the surface of the flange 112. A peripheral edge of a cup-shaped discharge port body 120 having a discharge port 119 is fixedly joined to a peripheral edge of the other end of the stator 102, and a partition wall 121 is provided inside the discharge port body 120. Although this partition wall 121 is formed integrally with the discharge port body 120, it may be formed by a separate member and fixed to the discharge port body 120. A pressure chamber 122 is formed between the partition wall 121 and the ends of the stator 102 and the rotor 103, and a second pressure chamber 123 is formed between the partition wall 121 and the discharge port 119. The chambers 122 and 123 are connected by a plurality of guide holes 124 formed on the outer periphery of the partition wall 121. As shown in FIG. 10, a rib 125 connecting the inner peripheral surface of the discharge port body 120 and the outer peripheral edge of the partition wall 121 is provided at the center of the guide holes 124. The inclination angles of the axial flow blades 108 with respect to the rotation shaft 107 are determined so that the ribs 125 can correct the flow of the fluid in the swirling direction in the axial flow direction.

  Further, as shown in FIG. 9, a support portion 127 supporting the outer periphery of the slide bearing 126 is provided at a central portion of the partition wall 121, and a leak flow communicating the second pressure chamber 123 and the inner peripheral surface of the slide bearing 126. A passage 128 is formed.

  The rotating shaft 107 of the rotor 103 is rotatably supported by a bearing 113 and a sliding bearing 126. Further, the diameter of the concave portion (the bottom of the spiral groove 111 in this example) of the axial flow blade 108 having the minimum radius centered on the axis (rotation center) of the rotor 103 is determined to be larger than the diameter of the support portion 127. I have.

  In such a configuration, when the suction port 117 is connected to the fluid supply source, the discharge port 119 is connected to the fluid supply destination, and a current flows through the coil 105, the motor 101 is driven. That is, the rotor 103 having the axial blades 108 rotates. As a result, the fluid is sucked in from the suction port 117, is rectified by the rectifying plate 116 formed in the opening 115 of the flange 112, is sent to the pressure chamber 122 by the axial flow vanes 108, and is further supplied to the second pressure from the guide hole 124. It is discharged from the discharge port 119 via the chamber 123. In this case, the fluid is sent while rotating while the axial flow blade 108 rotates, but the rotational kinetic energy is converted into static pressure energy in the pressure chamber 122, so that the fluid can be efficiently sent out from the discharge port 119.

  That is, the rotational speed of the fluid discharged from the spiral groove 111 becomes lower as the radius of the rotation becomes closer to the outer circumference, and the difference in the speed of the kinetic energy is converted into pressure.

  In the present embodiment, a sliding bearing 126 that rotatably supports the rotating shaft 107 of the rotor 103 with a predetermined clearance is provided at the center of the partition wall 121, and the partition wall 121 has a second pressure chamber 123 and a sliding bearing 126. Since the leak flow path 128 communicating with the inner peripheral surface of the slide bearing 126 is formed, the fluid in the second pressure chamber 123 has a uniform pressure between the rotation shaft 107 of the rotor 103 and the slide bearing 126. Intervene with distribution. Therefore, the lubrication of the rotating shaft 107 can be favorably maintained for a long time.

  Further, in the present embodiment, the diameter of the concave portion of the axial flow blade 108 (the bottom of the spiral groove 111 in this example) having the minimum radius centered on the axis of the rotor 103 is set to be larger than the diameter of the support portion 127. Therefore, the fluid can be easily guided toward the outside of the pressure chamber 122 in which the guide hole 124 is formed, and the fluid sent by the axial flow blade 108 and the supporting portion 127 that supports the sliding bearing 126 can be provided. Loss due to collision of the vehicle.

  Note that the concave portion of the axial flow blade that is larger than the diameter of the support portion 127 is not limited to the above example. For example, as described in Patent Literature 1, a plurality of core pieces are stacked to include a concave portion in an axial flow blade having salient poles and a concave portion. In the case where an axial flow blade called a screw or an impeller having a plurality of inclined blades is used, the root of the blade with respect to the rotating shaft is a concave portion.

  That is, to make the diameter of the concave portion of the axial flow blade larger than the diameter of the support portion 127, in other words, to change the dimension and shape of the axial flow blade so that the fluid can easily flow toward the outside in the radial direction of the support portion 127. It is to determine. The axial flow blade 108 satisfies this condition. By using the axial flow blade 108, it is possible to reduce the loss due to collision between the sent fluid and the support portion 127 supporting the sliding bearing 126.

  As shown in FIG. 10, the axial flow blade 108 is formed by forming a spiral groove 111 on the outer periphery of a cylindrical body 110. In this case, as w and h are made as large as possible, the flow path resistance is reduced and the efficiency is improved. However, when h is constant, the larger the value of w is such that w> h, the more the laminar flow normal state is disturbed, and a turbulent flow is generated, which is returned to the suction side behind the spiral groove 111 in the rotational direction, Efficiency decreases. When w <h, the above-mentioned turbulence does not occur, but the flow path resistance increases and the efficiency decreases. However, in the present embodiment, since the width w and the depth h of the spiral groove 111 are set to substantially the same value, the fluid can be sent more efficiently.

(Second embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted. FIG. 12 is a vertical sectional side view of the in-line pump P2.

  In the in-line pump P2 in the present embodiment, the rotating shaft 107 of the rotor 103 extends to the second pressure chamber 123, and a second axial flow blade 129 is fixedly provided at the extending portion. The second axial blade 129 uses an axial impeller having a plurality of blades.

  In such a configuration, the fluid can be sent by dispersing the pressure by the axial blade 108 provided inside the stator 102 and the second axial blade 129 provided in the second pressure chamber 123. . Further, the power of the motor 101 can be dispersed. By doing so, when the rotor 103 is downsized, the second axial blade 129 can compensate for the decrease in the fluid feeding performance of the axial blade 108. Thereby, the fluid can be efficiently sent while satisfying the miniaturization of the motor 101.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. The same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted. FIG. 13 is a longitudinal side view of the inline pump P3, and FIG. 14 is a longitudinal side view of the inline pump P3 shown in FIG.

  The motor 101 according to the present embodiment includes a cylinder 130 that covers the outer periphery of the stator 102. A connection port 131 is fixed to one end (the lower end in FIGS. 13 and 14) of the motor 101. The connection port body 131 is separated from a pressure chamber 132 that converts the rotational kinetic energy of the fluid sucked by the axial flow blade 108 of the rotor 103 into static pressure energy, and is spaced 180 degrees from the outer periphery of the pressure chamber 132. And two pipe-shaped guide passages 133 projecting downward from the inclined position. These guide channels 133 are merged on an extension of the center of the rotor 103, and a discharge port 134 is formed at the junction. The pressure chamber 132 is provided with a centrifugal blade 135 fixed to the lower end of the rotating shaft 107 of the rotor 103. One end of the rotating shaft 107 penetrating through the centrifugal blade 135 is rotatably supported by a bearing 137 supported by a support 136 provided at the center of the connection port 131.

  138 is a suction case formed in a container shape. The opening surface of the suction case 138 is covered by a suction port body 140 having a suction port 139 formed at the center. The motor 101 and a part of the connection port 131 are accommodated in a suction case 138.

  FIG. 15 is a bottom view of the in-line pump P3 viewed from the direction of arrow B in FIG. In the drawing, reference numeral 132a denotes a bottom surface of the pressure chamber 132, and the bottom surface 132a is formed in a disk shape in conformity with the bottom surface of the cylindrical motor 101, but only the guide channel 133 is exposed below the suction case 138. It is formed in such a dimensional shape.

  A suction passage 141 for sucking fluid is formed between the outer periphery of the motor 101 and the outer periphery of the connection port 131 and the inner surface of the suction case 138. As shown by arrows in FIGS. 13 and 14, the suction flow path 141 guides the fluid sucked from the suction port 139 to the pressure chamber 132 via the outer peripheral portion of the stator 102, and the axial flow blade of the centrifugal blade 135. The path is set so as to be fed toward the surface opposite to 108. That is, as shown in FIG. 13, the suction passage 141 is connected to two connection holes 142 formed at symmetrical positions on the bottom of the pressure chamber 132 of the connection port 131 with the center of the rotation shaft 107 therebetween. Connection portion 141a. As is apparent from FIG. 13, the connection portion 141 a is disposed so as to pass through between the bottom surface 132 a of the pressure chamber 132 of the connection port body 131 and the guide channel 133.

  In such a configuration, when the rotor 103 is rotated, the fluid sucked from the suction port 139 is rectified by the rectifying plate 116 formed in the opening 115 of the flange 112, and is sent to the pressure chamber 132 by the axial flow blade 108. Then, the rotational kinetic energy is converted into static pressure energy in the pressure chamber 132, and is guided to the pressure chamber 132 via the suction passage 141 of another system. The fluid guided to the pressure chamber 132 via the two paths is discharged from the discharge port 134 via the guide channel 133 by the rotation of the centrifugal blade 135. Thereby, the fluid can be sent efficiently.

  In this case, the centrifugal blade 135 that rotates integrally with the axial flow blade 108 receives the pressure of the fluid sent by the axial flow blade 108 on the upper surface in FIGS. 13 and 14, and the fluid that is sent through the connection portion 141 a of the suction flow path 141. Is received on the lower surface. That is, since the bidirectional pressures act in directions that cancel each other, the thrust load applied to the rotor 103 by the fluid can be reduced.

  Further, most of the suction flow path 141 formed between the motor 101 and the outer periphery of the pressure chamber 132 has an annular shape, has a uniform flow path cross-sectional area, and further forms a part of the suction flow path 141. The connection portion 141a and the guide channel 133 of the connection port 131 are formed at symmetrical positions and with symmetrical shapes and sizes around the axis of the rotating shaft 107 of the rotor 103. That is, the suction flow path 141 and the guide flow path 133 are determined so that the energy of the flowing fluid is substantially equal at a symmetric position about the axis of the rotor 103. Therefore, the radial load on the rotor 103 can be reduced. Thus, the life of the bearing 113, the bearing 137, and the rotating shaft 107 can be increased, and the motor 101 can be smoothly rotated for a long time.

  It is apparent that the present invention is not limited to the embodiments, and that various modifications can be made without departing from the spirit of the invention.

It is sectional drawing of the whole in-line type pump which shows a 1st reference example. It is a top view of the reference example. It is a front view of the rotor of the reference example. It is a schematic diagram for explaining the rotation operation of the rotor of the reference example. It is a schematic diagram for explaining the rotation operation of the rotor of the reference example. FIG. 4 is an overall cross-sectional view of an in-line pump showing a second reference example. It is a front view of the whole in-line type pump which shows a 3rd reference example. It is a partial sectional view of the centrifugal blade of the reference example. It is a longitudinal side view of an in-line type pump in a 1st embodiment of the present invention. FIG. 10 is a sectional view taken along line AA of FIG. 9. It is a vertical side view which shows a part of rotor. It is a longitudinal side view of the in-line type pump in a 2nd embodiment of the present invention. It is a longitudinal side view of the in-line type pump in a 3rd embodiment of the present invention. FIG. 14 is a vertical sectional side view of the in-line pump shown in FIG. 13 viewed from a direction different by 90 degrees. FIG. 14 is a bottom view of the in-line pump as viewed from the direction of arrow B in FIG. 13.

Explanation of reference numerals

102 Stator 103 Rotor 122, 132 Pressure chamber 117, 139 Suction port 119, 134 Discharge port 135 Centrifugal blade 108 Axial flow blade 110 Cylindrical body 111 Spiral groove 121 Partition wall 123 Second pressure chamber 124 Guide hole 126 Slide bearing 127 Support portion 128 Leak flow path 129 Second axial flow blade 133 Guide flow path 141 Suction flow path

Claims (8)

An in-line pump in which a rotor having axial flow blades for axially sending fluid sucked from a suction port toward a discharge port inside a cylindrical stator is rotatably provided.
A pressure chamber for converting rotational kinetic energy of the fluid sent toward the outlet by the axial flow blade of the rotor into static pressure energy;
A second pressure chamber disposed between the pressure chamber and the discharge port, wherein the pressure chamber is partitioned by a partition wall,
A guide hole arranged on the outer peripheral portion of the partition wall and connecting between the pressure chamber and the second pressure chamber;
An in-line pump comprising:   A sliding bearing is provided at the center of the partition wall to rotatably support the rotating shaft of the rotor with a predetermined clearance, and the partition wall communicates the second pressure chamber with the inner peripheral surface of the sliding bearing. The in-line pump according to claim 1, wherein a leak flow path is formed.   The in-line pump according to claim 1, wherein a second axial flow blade that rotates integrally with the rotor is provided in the second pressure chamber.   The rotor according to any one of claims 1 to 3, wherein the rotor has a plurality of magnetic poles on an outer diameter, and has a spiral groove formed in an outer periphery thereof and communicating with the axial direction. Inline pump as described.   The diameter of the concave portion of the spiral groove where the radius centered on the axis of the rotor is minimum is set to a diameter larger than the diameter of the support portion formed on the partition wall to support the slide bearing. The in-line pump according to claim 4, wherein   6. The in-line pump according to claim 4, wherein a width and a depth of the spiral groove are set to substantially equal values. An in-line pump in which a rotor having axial flow blades for axially sending fluid sucked from an inlet toward an outlet is rotatably provided inside a cylindrical stator,
A pressure chamber for converting the rotational kinetic energy of the fluid sent toward the outlet by the axial flow vanes of the rotor into static pressure energy;
A centrifugal blade arranged in the pressure chamber and rotating integrally with the rotor,
A suction path in which the fluid sucked from the suction port is guided to the pressure chamber via the outer peripheral portion of the stator and is sent toward a surface of the centrifugal blade opposite to the axial flow blade. A flow path;
A guide channel that guides fluid in the pressure chamber from the outer peripheral portion of the pressure chamber to a discharge port by rotation of the centrifugal blade,
An in-line pump comprising: The in-line according to claim 7, wherein a connection portion of the guide passage with the pressure chamber is set such that energy of a flowing fluid is substantially equal at a symmetric position about an axis of the rotor. Type pump.

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