Centrifugal pump

Abstract

A centrifugal pump includes: a rotating blade member including an impeller member and a rotor magnet associated with the impeller member, a main body casing in which the rotating blade member is accommodated, a coil portion that rotates the rotating blade member, wherein the coil portion is located on a periphery of the rotor magnet, and an axial member which is associated with the main body casing, wherein the rotating blade member pivots around the axial member. A clearance, in which the rotor magnet is allowed to move, is provided between the blade member and the rotor magnet.

Claims

1. A centrifugal pump comprising: a rotating blade member including an impeller member and a rotor magnet associated with the impeller member, wherein the impeller member includes a blade; a main body casing in which the rotating blade member is accommodated; a coil portion that rotates the rotating blade member, wherein the coil portion is located on a periphery of the rotor magnet; and an axial member which is associated with the main body casing, wherein the rotating blade member pivots around the axial member, wherein a clearance, in which the rotor magnet is allowed to move, is provided between the blade and the rotor magnet, and wherein the clearance between the blade and the rotor magnet includes a radial clearance r between the blade and the rotor magnet and an axial clearance h between the blade and the rotor magnet, and r is smaller than h.

2. The centrifugal pump of claim 1, further comprising: a dropout preventing means to prevent the impeller member and the rotor magnet from dropping out.

3. The centrifugal pump of claim 1, wherein the main body casing has a first end and a second end in an axial direction of the axial member, and the axial member is fixed at the first end and the second end.

4. The centrifugal pump of claim 1, wherein the main body casing has a third end at a side of the rotor magnet, and the axial member is fixed at the third end.

5. The centrifugal pump of claim 1, wherein the blade includes a first blade part, a second blade part, and a third blade part, the second blade part is placed between the first blade part and the third blade part, a first length of the first blade part in a radial direction perpendicular to the axial member is shorter than a second length of the second blade part in the radial direction, and a second length of the second blade part in the radial direction is shorter than a third length of the third blade part in the radial direction.

6. The centrifugal pump of claim 5, wherein the rotor magnet is associated the first blade part and the second blade part.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a vertical cross sectional view of the centrifugal pump.

(2) FIG. 2 is a partially enlarged cross sectional view of FIG. 1.

(3) FIG. 3 is a partially enlarged cross sectional view, similar to FIG. 2, in which Embodiment 2 of the centrifugal pump is shown.

(4) FIG. 4 is a partially enlarged cross sectional view, similar to FIG. 2, in which Embodiment 3 of the centrifugal pump.

(5) FIG. 5 is a vertical cross sectional view that shows Embodiment 4 of the centrifugal pump.

(6) FIG. 6 is a vertical cross sectional view that shows Embodiment 5 of the centrifugal pump.

(7) FIG. 7 is a vertical cross sectional view of the conventional centrifugal pump.

(8) FIG. 8 is a vertical cross sectional view that shows the mechanism of the generation of the abnormal sound of the conventional centrifugal pump.

DESCRIPTION OF EMBODIMENTS

(9) Hereafter, embodiments are described in the detail or more on the basis of the drawing.

Embodiment 1

(10) FIG. 1 is a vertical cross sectional view of the centrifugal pump.

(11) FIG. 2 is a partially enlarged sectional view of FIG. 1.

(12) In FIG. 1, reference numeral 10 indicates a centrifugal pump as a whole.

(13) In the centrifugal pump 10 of FIG. 1, for convenience sake of clarification, a composition member such as the coil portion 204, which is located on the periphery of the rotor magnet 122, as described in the conventional centrifugal pump 100 shown in FIG. 7, and is disposed on the outer periphery of the rotor magnet accommodating portion 146 of the lower main body casing 138, and rotates the rotating blade member 102, is omitted and shown in the drawing.

(14) As shown in FIG. 1, the centrifugal pump 10 comprises a rotating blade member 12.

(15) This rotating blade member 12 comprises a plurality of impeller members 16, which are radially extended toward the outer periphery at an upper part of a circular tube bearing portion 14.

(16) In addition, the number of impeller members 16 may be elected according to the usage of centrifugal pump 10 and the pump ability that is required, and is not limited particularly.

(17) As shown in FIG. 1, the impeller member 16 includes a base end portion 18 which is extended toward the outer periphery of the bearing portion 14, an enlarged diameter portion 20, which is enlarged upwardly toward the outer periphery from this base end portion 18, and an outside blade portion 22, which is extended from this enlarged diameter portion 20 toward the outer periphery.

(18) By forming the shape of the impeller member 16 like this shape, the discharge ability can be improved by the outside blade portion 22's function caused by rotation of the impeller member 16.

(19) Moreover, on the rotating blade member 12, a rotor magnet accommodating portion 24, which is extended toward the outer periphery, is formed under the bearing portion 14.

(20) In addition, a rotor magnet 32, which includes an annular permanent magnet, is fitted to the rotor magnet accommodating portion 24.

(21) In addition, this rotor magnet 32 includes a component described below as a dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out.

(22) That is, as shown in the enlarged view of FIG. 2, a groove 13, which is formed at the rotor magnet accommodating portion 24 of the impeller member 16, is provided, and a snap ring 11 is provided at this groove 13 and it is engaged.

(23) As a result, the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(24) Consequently, the impeller member 16 is rotated around an axial member 64 together with the rotor magnet 32.

(25) By the configuration like this, since the dropout preventing means (in this Embodiment, the groove 13 and the snap ring 11) is provided, the impeller member 16 and the rotor magnet 32 are prevented from dropping out.

(26) As a result, the abnormal sound is not generated, and the rotation of the rotor magnet 32 can surely be transmitted to the impeller member 16.

(27) Moreover, a moderate clearance (backlash) can be formed between the impeller member 16 and the rotor magnet 32.

(28) As a result, the load, by which the rotor magnet 32 is drawn to the coil 210, is not transmitted to the impeller member 16.

(29) Consequently, the impeller member 16 itself is not inclined, and the impeller member 16 is not contacted to the axial member 64 and the main body casing 34, and the durability and quietness is superior, and eccentricity of the impeller member 16 is not caused, and the predetermined objective pump performance can be retained.

(30) In this case, as snap ring 11, for instance, the snap ring 11 having the ring C shape can be used.

(31) Moreover, the material of the snap ring 11 is not particularly limited, and the metal and made of the plastic, etc. can be used.

(32) Furthermore, as shown in FIG. 1, the centrifugal pump 10 includes a main body casing 34 in which the rotating blade member 12 is accommodated.

(33) The main body casing 34 includes an upper main body casing 36.

(34) The upper main body casing 36 includes a top wall 38 and a side peripheral wall 40 which is downwardly extended from an outer periphery of the top wall 38.

(35) Moreover, as shown in FIG. 1, on the side peripheral wall 40 of the upper main body casing 36, an opening portion to fix a suction side coupling member 42 is formed.

(36) As shown in FIG. 1, the suction side coupling member 42 is fixed to the opening portion in a sealed state with, for instance, the welding, the soldering and the adhesion, etc.

(37) As a result, the suction side coupling member 42 is connected to the main body casing 34.

(38) On the side peripheral wall 40 of the upper main body casing 36, an opening portion to fix a discharge side coupling member 46 is formed.

(39) As shown in FIG. 1, on this opening portion, the discharge side coupling member 46 is fixed in a sealed state with, for instance, the welding, the brazing and the adhesion, etc.

(40) As a result, the discharge side coupling member 46 is connected to the main body casing 34.

(41) Moreover, as shown in FIG. 1, the main body casing 34 is provided with a lower main body casing 48.

(42) Moreover, on an inner wall of a lower end part 51 of the side peripheral wall 40 of the upper main body casing 36, an outer periphery flange 52 of the lower main body casing 48 is fixed in a sealed state with, for instance, the welding, the brazing and the adhesion, etc.

(43) As a result, in the main body casing 34, an interior space S1, which is surrounded with the upper main body casing 36 and the lower main body casing 48, is formed.

(44) As shown in FIG. 1, this lower main body casing 48 includes a blade accommodating portion 54, which is extended horizontally from an outer periphery flange 52 of the lower main body casing 48 toward inner periphery side, and a rotor magnet accommodating portion 56, which is extended downwardly from this blade accommodating portion 54.

(45) In addition, under this rotor magnet accommodating portion 56, a lower bearing member accommodating portion 58, which is of a cylindrical shape having a bottom, is formed.

(46) Moreover, in the lower bearing member accommodating portion 58, a lower bearing member 60 is fitted by, for instance, press fit, etc.

(47) In a shaft hole 62 formed in this lower bearing member 60, a lower end portion 66 of an axial member 64 is fixed as pivoted by, for instance, press fit, etc.

(48) Moreover, in the bearing portion 14 of this rotating blade member 12, the axial member 64 passes through so that the rotating blade member 12 can be rotated around the axial member 64.

(49) In addition, as shown in FIG. 1, the main body casing 34 is provided with a blade casing 68.

(50) An outer periphery flange 70 of this blade casing 68 is fixed in a sealed state with, for instance, the welding, the brazing and the adhesion, as sandwiched between a lower end part 51 of the upper main body casing 36 and an outer periphery flange 52 of the lower main body casing 48.

(51) Moreover, the blade casing 68 includes a side peripheral wall 72, which is upwardly extended from the outer periphery flange 70, and an extending portion 74, which is extended inwardly in the horizontal direction from the side peripheral wall 72 along the outside blade portion 22 of the impeller member 16.

(52) By having such a shape, between the blade accommodating portions 54 of the blade casing 68 and the lower main body casing 48, the impeller member 16 can be accommodated.

(53) Moreover, to a protruding portion 38a, which is projected downwardly to a central portion of the top wall 38 of the upper main body casing 36, an upper bearing member 78 is fixed by a fixing holder 71, so that it is protruded downwardly in an inner periphery side opening portion 76 of an extending portion 74 of the blade casing 68.

(54) On a shaft hole 80 formed in the upper bearing member 78, a top portion 82 of the axial member 64, which passes through an inside of the bearing portion 14 of the rotating blade member 12, for instance, by pressing fit, is fixed as pivoted.

(55) Moreover, as shown in FIG. 1, the diameter of the side peripheral wall 72 of the blade casing 68 is formed smaller than the diameter of the side peripheral wall 40 of the upper main body casing 36.

(56) In addition, the height of the side peripheral wall 72 of the blade casing 68 is formed smaller than the height of the side peripheral wall 40 of the upper main body casing 36.

(57) As a result, by the blade casing 68, the interior space S1, which is formed by the upper main body casing 36 and the lower main body casing 48, is partitioned.

(58) Consequently, a fluid introducing passage 84 is formed on the upper part.

(59) Moreover, a rotating accommodating space S2, in which the rotating blade member 12 is accommodated, is formed on the lower part.

(60) The centrifugal pump 10 configured like this is operated as follows.

(61) First of all, the electric current is flowed through the coil 210 of the coil portion 204, so that the coil 210 is excited.

(62) As a result, it effects on the rotor magnet 32 of the rotating blade member 12.

(63) Consequently, the rotating blade member 12 can be rotated around the axial member 64, which passes through the bearing portion 14.

(64) As a result, the rotating blade member 12 is rotated.

(65) Consequently, as shown by arrow A of FIG. 1, the fluid sucked from the suction side coupling member 42 passes from the fluid introducing passage 84, which is formed by the blade casing 68 and the upper main body casing 36, to the inner periphery side opening portion 76 of the extending portion 74 of the blade casing 68.

(66) Moreover, the fluid that passes through the inner periphery side opening portion 76 is introduced into the rotating accommodating space S2, which is formed by the blade casing 68 and the lower main body casing 48.

(67) In addition, by the turning force of the impeller member 16 of the rotating blade member 12, as shown by arrow B of FIG. 1, the fluid introduced into the rotating accommodating space S2 is discharged through the discharge side coupling member 46 from the rotating accommodating space S2 of the main body casing 34.

(68) By the way, in the conventional centrifugal pump 100, as shown in FIG. 8, the rotating blade member 102 including the rotor magnet 122 and the impeller member 106 swings and rotates, as shown by the chain line in FIG. 8, in the contacting state by two points (T1 and T2).

(69) As a result, the abnormal sound (resonance sound) is generated.

(70) In order to prevent such swinging, in the centrifugal pump 10 of this Embodiment, as shown in FIG. 2, at the portion C and D enclosed with the circle of FIG. 2, a clearance, in which the rotor magnet 32 can be moved, is formed between the impeller member 16 and the rotor magnet 32.

(71) That is, at the portion C enclosed with the circle of FIG. 2, between a lower end 18a of the base end portion 18 of the impeller member 16 and an upper surface 33 of the rotor magnet 32, an axial clearance V1 is formed.

(72) Moreover, at the portion D enclosed with the circle of FIG. 2, between an inside diameter side 31a of an outer periphery cylindrical portion 31 which extends in an axial direction of the rotor magnet 32 and an outside diameter side 18b of the base end portion 18 of the impeller member 16, a radial clearance V2 between the impeller member 16 and the rotor magnet 32 is formed.

(73) By configuring like this, between the impeller member 16 and the rotor magnet 32, the axial clearance V1 and the radial clearance V2 are formed, so that the clearance in which in the rotor magnet can be moved is formed.

(74) Therefore, swinging of the rotor magnet 32 can be absorbed by the clearance, which includes the axial clearance V1 and the radial clearance V2.

(75) That is, a little clearance (i.e. backlash) V1, V2 are provided between the rotor magnet 32 and the impeller member 16.

(76) As a result, the load, by which the rotor magnet 32 is drawn to the coil, is not transmitted to the impeller member 16. Consequently, the impeller member 16 itself is not inclined.

(77) Therefore, the impeller member 16 is not contacted to the axial member 64 and the main body casing 34 (the lower main body casing 48).

(78) As a result, the durability and quietness are superior, and eccentricity of the impeller member 16 is not caused, and the predetermined objective pump performance can be retained.

(79) Moreover, it has the configuration in which the rotor magnet 32 can be moved.

(80) As a result, even if there is the state that the foreign matter is invaded and bitten between the rotor magnet 32 and the main body casing 34 (the lower main body casing 48), the rotor magnet 32 can be moved along with the rotation of the rotating blade member 12.

(81) Consequently, this bite state can be released instantaneously.

(82) Therefore, the lock state, in which the rotating blade member 12 cannot be rotated by the bite with the foreign matter, can be prevented.

(83) Moreover, in this case, as shown by the enlarged view of FIG. 2, it is desirable that, the relation between a radial clearance r between the impeller member 16 and the rotor magnet 32; and an axial clearance h between the impeller member 16 and the rotor magnet 32 is set to the relation of r<h.

(84) Thus, the relation between a radial clearance r between the impeller member 16 and the rotor magnet 32; and an axial clearance h between the impeller member 16 and the rotor magnet 32 is set to the relation of r<h.

(85) As a result, the movement of the rotor magnet 32 (i.e. inclination) is absorbed by the axial clearance h.

(86) Consequently, the movement of the rotor magnet 32 (inclination) is not transmitted to the impeller member 16.

(87) As a result, the impeller member 16 itself is not inclined following to the movement of the rotor magnet 32.

(88) Therefore, the impeller member 16 is not contacted to the axial member 64 and the main body casing 34 (the lower main body casing 48), and the durability and quietness is superior, and eccentricity of the impeller member 16 is not caused, and the predetermined objective pump performance can be retained.

(89) Moreover, in this case, as shown by the enlarged view of FIG. 2, it is desirable that, the relation between a clearance R between the impeller member 16 and the axial member 64; the radial clearance r between the impeller member 16 and the rotor magnet 32; and a clearance W between the outer periphery and main body casing 34 (lower main body casing 48) of the rotor magnet 32 is set to the relation of W>R+r.

(90) As a result, the effect of preventing the lock state, in which the rotating blade member 12 cannot be rotated by the bite with the foreign matter is superior.

(91) Moreover, as shown by the enlarged view of FIG. 2, it is desirable that, the relation between the clearance R between the impeller member 16 and the axial member 64 and the radial clearance r between the impeller member 16 and the rotor magnet 32 is set to the relation of R<r.

(92) Thus, the relation between the clearance R between the impeller member 16 and the axial member 64 and the radial clearance r between the impeller member 16 and the rotor magnet 32 is set to the relation of R<r.

(93) As a result, the impeller member 16 is not contacted to the axial member 64, and swinging of the rotor magnet 32 can be absorbed by this radial clearance r.

(94) That is, if the clearance R between the impeller member 16 and the axial member 64 is narrow, the inclination of the impeller member 16 is small.

(95) However, the dimension control of the clearance is, for instance, management of about 0.01-0.03 mm.

(96) As a result, the demanded accuracy of parts is extremely high, high cost is required. Actually, it is difficult to achieve such a dimension control.

(97) Therefore, the radial clearance r between the impeller member 16 and the rotor magnet 32 is enlarged to the extent that the clearance R between the impeller member 16 and the axial member 64 cannot be narrowed.

(98) As a result, inclination (Swinging) of the rotating blade member 12 is prevented, and contact of the impeller member 16 with the axial member 64 is controlled and the generation of the abnormal sound is prevented.

Embodiment 2

(99) FIG. 3 is a partially enlarged cross sectional view similar to FIG. 2, in which Embodiment 2 of the centrifugal pump is shown.

(100) The centrifugal pump 10 of this Embodiment includes basically similar composition of the Embodiment shown in FIG. 1-FIG. 2.

(101) The same reference numerals refer to the same composition members, and the detailed explanation is omitted.

(102) In the centrifugal pump 10 of Embodiment 1, between the impeller member 16 and the rotor magnet 32, the axial clearance V1 and the radial clearance V2 are formed.

(103) However, in the centrifugal pump 10 of this Embodiment 2, the rotor magnet 32 is of a cylindrical shape.

(104) Moreover, between the outside diameter side 18b of the base end portion 18 of the impeller member 16 and an inside diameter side 32a of the rotor magnet 32, only a radial clearance V3 is formed.

(105) Thus, only the radial clearance V3 may be formed as a clearance, in which the rotor magnet 32 can be moved between the impeller member 16 and the rotor magnet 32.

(106) As a result, swinging of the rotor magnet 32 can be absorbed by the clearance, which includes this radial clearance V3.

(107) In the centrifugal pump 10 of Embodiment 1, as shown in FIG. 1, as for the rotor magnet 32, as the dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the groove 13, which is formed at the rotor magnet accommodating portion 24 of the impeller member 16, is provided, and the snap ring 11 is provided at this groove 13 and it is engaged.

(108) As a result, the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(109) On the contrary, in the centrifugal pump 10 of this Embodiment, as shown in FIG. 3, as a dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the rotor magnet 32 having the cylindrical shape is fitted to the groove 13, which is formed on the outside diameter side 18b of the base end portion 18 of the impeller member 16 to correspond to the shape of the rotor magnet 32.

(110) As a result, the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

Embodiment 3

(111) FIG. 4 is a partially enlarged cross sectional view similar to FIG. 2 in which Embodiment 3 of the centrifugal pump is shown.

(112) The centrifugal pump 10 of this Embodiment includes basically similar composition of the Embodiment 1 shown in FIG. 1-FIG. 2.

(113) The same reference numerals refer to the same composition members, and the detailed explanation is omitted.

(114) In the centrifugal pump 10 of Embodiment 1, as shown in FIG. 1, as for the rotor magnet 32, as the dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the groove 13, which is formed at the rotor magnet accommodating portion 24 of the impeller member 16, is provided, and the snap ring 11 is provided at this groove 13 and it is engaged.

(115) As a result, the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(116) On the contrary, in the centrifugal pump 10 of this Embodiment, as shown in FIG. 4, as a dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the groove 13, which is formed at the rotor magnet accommodating portion 24 of the impeller member 16, is provided, and the snap ring 11 is provided at the groove 13 and it is engaged.

(117) Furthermore, an engagement hole 17 is formed at the lower end of the base end portion 18 of the impeller member 16, and a protruding portion 19, which is formed on the top of the rotor magnet 32, is fitted to this engagement hole 17.

(118) As a result, the rotation transmission portion is configured and the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(119) In addition, in case of this Embodiment, as shown in FIG. 4, as the snap ring 11, for instance, the snap ring 11 having the O-ring shape and including the elastic member such as rubber is used.

(120) Moreover, as the snap ring 11, for instance, the snap ring 11 including a retaining ring, which has the spring and elasticity, and which is molded by metallic linear member in a ring C shape, may be used.

(121) Like this, by including the snap ring 11 formed of the elastic member, even if the rotor magnet 32 is a fragile material, when the rotor magnet 32 is provided, the crack is not caused in the rotor magnet 32 due to the elasticity of the snap ring 11.

(122) In addition, when the impeller member 16 and the rotor magnet 32 are rotated, the stress does not concentrate on this fixing portion, and the dropout can surely be prevented.

(123) Moreover, in the centrifugal pump 10 of this Embodiment 3, as well as the centrifugal pump 10 of Embodiment 2, the rotor magnet 32 is of a cylindrical shape.

(124) Moreover, between an outside diameter side 15a of a lower side 15 of the bearing portion 14 of the impeller member 16 and an inside diameter side 32a of the rotor magnet 32, only radial clearance V4 is formed.

(125) As a result, swinging of the rotor magnet 32 can be absorbed by the clearance, which includes the radial clearance V4.

Embodiment 4

(126) FIG. 5 is a vertical sectional view that shows Embodiment 4 of the centrifugal pump.

(127) The centrifugal pump 10 of this Embodiment includes basically similar composition of the Embodiment 1 shown in FIG. 1-FIG. 2.

(128) The same reference numerals refer to the same composition members, and the detailed explanation is omitted.

(129) In the centrifugal pump 10 of Embodiment 1, as shown in FIG. 1, as for the rotor magnet 32, as the dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the groove 13, which is formed at the rotor magnet accommodating portion 24 of the impeller member 16, is provided, and the snap ring 11 is provided at this groove 13 and it is engaged.

(130) As a result, the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(131) On the contrary, in the centrifugal pump 10 of this Embodiment, as a dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the following configuration is provided.

(132) That is, as shown in FIG. 5, rotor magnet accommodating portion 24 is provided with a protruding portion 26, which is extended downwardly from the lower side of the base end portion 18, and a holding flange portion 28, which includes an enlarged tip of the protruding portion 26.

(133) In addition, an installation portion 30 includes these protruding portion 26 and holding flange portion 28.

(134) Moreover, the protruding portion 26 of the installation portion 30 is inserted in a setting 32b of the rotor magnet 32 including the annular permanent magnet.

(135) As a result, by the enlarged holding flange portion 28, the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(136) In this case, as for the enlarged holding flange portion 28, after inserting the protruding portion 26 of the installation portion 30 into the setting 32b of the rotor magnet 32, for instance, by welding the tip of protruding portion 26 of installation portion 30, the enlarged holding flange portion 28 may be formed.

(137) Moreover, in this welding, it is desirable that, between the rotor magnet 32 and the enlarged holding flange portion 28, the axial clearance is formed, in order to attain the above-mentioned abnormal sound prevention.

(138) Moreover, in the centrifugal pump 10 of this Embodiment 4, the rotor magnet 32 is of a cylindrical shape as well as the centrifugal pump 10 of Embodiment 2.

(139) In addition, between an outside diameter side 15a of a lower side 15 of the bearing portion 14 of the impeller member 16 and an inside diameter side 32a of the rotor magnet 32, only radial clearance V5 is formed.

(140) As a result, swinging of the rotor magnet 32 can be absorbed by the clearance, which includes the radial clearance V5.

(141) In addition, in the centrifugal pump 10 of Embodiment 1, to the protruding portion 38a, which is projected downwardly to the central portion of the top wall 38 of the upper main body casing 36, the upper bearing member 78 is fixed by the fixing holder 71, so that it is protruded downwardly in the inner periphery side opening portion 76 of the extending portion 74 of the blade casing 68.

(142) On the shaft hole 80 formed in the upper bearing member 78, the top portion of the axial member 64, which passes through an inside of the bearing portion 14 of the rotating blade member 12, is fixed as pivoted.

(143) On the contrary, in the centrifugal pump 10 of this Embodiment 4, such upper bearing member 78 is not formed, and the top portion of the axial member 64 is not pivoted, and it is of so-called cantilever form.

(144) Moreover, in the centrifugal pump 10 of this Embodiment, an end portion portion 14a of the bearing portion 14 is protruded upwardly from the inner periphery side opening portion 76 of the extending portion 74 of the blade casing 68 such that it is exposed to the fluid introducing passage 84.

(145) By the configuration like this, according to the rotational movement of the impeller member 16, the fluid easily enters into the interior space S1 and the rotating accommodating space S2 through inner periphery side opening portion 76 that is the flowing-in hole.

(146) As a result, the fluid loss can be reduced.

Embodiment 5

(147) FIG. 6 is a vertical cross sectional view that shows Embodiment 5 of the centrifugal pump.

(148) The centrifugal pump 10 of this Embodiment includes basically similar composition of the Embodiment shown in FIG. 1-FIG. 2.

(149) The same reference numerals refer to the same composition members, and the detailed explanation is omitted.

(150) In the centrifugal pump 10 of Embodiment 1, to the protruding portion 38a, which is projected downwardly to the central portion of the top wall 38 of the upper main body casing 36, the upper bearing member 78 is fixed by the fixing holder 71, so that it is protruded downwardly in the inner periphery side opening portion 76 of the extending portion 74 of the blade casing 68.

(151) On the shaft hole 80 formed in the upper bearing member 78, the top portion 82 of the axial member 64, which passes through the bearing portion 14 of the rotating blade member 12, is fixed as pivoted.

(152) On the contrary, in the centrifugal pump 10 of this Embodiment 5, such upper bearing member 78 is not formed, and the top portion of the axial member 64 is not pivoted, and it is of so-called cantilever form.

(153) Moreover, in the centrifugal pump 10 of this Embodiment, as well as the centrifugal pump 10 of Embodiment of FIG. 4, as the dropout preventing means to prevent the impeller member 16 and the rotor magnet 32 from dropping out, the groove 13, which is formed at the rotor magnet accommodating portion 24 of the impeller member 16, is provided, and the snap ring 11 is provided at the groove 13 and it is engaged.

(154) Furthermore, the engagement hole 17 is formed at the lower end of the base end portion 18 of the impeller member 16, and the protruding portion 19, which is formed on the top of the rotor magnet 32, is fitted to this engagement hole 17.

(155) As a result, the rotation transmission portion is configured and the turn stop of the rotor magnet 32 and the fall of the rotor magnet 32 are prevented against the impeller member 16.

(156) Furthermore, in the centrifugal pump 10 of this Embodiment 4, as well as the centrifugal pump 10 of Embodiment 2, the rotor magnet 32 is of a cylindrical shape.

(157) Moreover, between an outside diameter side 15a of a lower side 15 of the bearing portion 14 of the impeller member 16 and an inside diameter side 32a of the rotor magnet 32, only radial clearance V6 is formed.

(158) As a result, swinging of the rotor magnet 32 can be absorbed by the clearance, which includes the radial clearance V6.

(159) Although preferable embodiment is described above, embodiments are not limited to that embodiment.

(160) For instance, in the above-mentioned Embodiments, materials of the main body casing 34, the upper main body casing 36, the lower main body casing 48, and the blade casing 68, etc. may be made of metallic, or may be made of plastic, and it may be selected appropriately according to the usage, and it is not limited particularly.

(161) In addition, in the Embodiment, the number of the suction side coupling member 42 and the number of the discharge side coupling member 46 are assumed to be one, respectively.

(162) However, the number of suction side coupling members 42 and the number of discharge side coupling members 46 can be plural.

(163) Therefore, various changes are possible in the scope.

INDUSTRIAL APPLICABILITY

(164) Embodiments can be applied to a centrifugal pump and a method of producing of the centrifugal pump to circulate the fluid in the closed circuit, for instance, refrigerant used for refrigerant circulation circuits such as air conditioners and freezers, and cooling water, etc. used for cooling circulation circuits for parts and apparatuses that generate heat, etc.

EXPLANATION OF LETTERS OR NUMERALS

(165) 10 Centrifugal pump 11 Snap ring 12 Rotating blade member 13 Groove 14 Bearing portion 14a End portion 15 Lower side 15a Outside diameter side 16 Impeller member 17 Engagement hole 18 Base end portion 18a Lower end 18b Outside diameter side 19 Protruding portion 20 Enlarged diameter portion 22 Outside blade portion 24 Rotor magnet accommodating portion 26 Protruding portion 28 Holding flange portion 30 Installation portion 31 Outer periphery cylindrical portion 31a Inside diameter side 32 Rotor magnet 32a Inside diameter side 32b Setting hole 33 Upper surface 34 Main body casing 36 Upper main body casing 38 Top wall 38a Protruding portion 40 Side peripheral wall 42 Suction side coupling member 46 Discharge side coupling member 48 Lower main body casing 51 Lower end part 52 Outer periphery flange 54 Blade accommodating portion 56 Rotor magnet accommodating portion 58 Lower bearing member accommodating portion 60 Lower bearing member 62 Shaft hole 64 Axial member 66 Lower end portion 68 Blade casing 70 Outer periphery flange 71 Fixing holder 72 Side peripheral wall 74 Extending portion 76 Inner periphery side opening portion 78 Upper bearing member 80 Shaft hole 82 Top portion 84 Fluid introducing passage 100 Centrifugal pump 102 Rotating blade member 104 Bearing portion 106 Impeller member 106a Inside diameter side 108 Base end portion 110 Enlarged diameter portion 112 Outside blade portion 122 Rotor magnet 124 Main body casing 126 Upper main body casing 128 Top wall 128a Protruding portion 130 Side peripheral wall 132 Suction side coupling member 136 Discharge side coupling member 138 Lower main body casing 141 Lower end part 142 Outer periphery flange 144 Blade accommodating portion 146 Rotor magnet accommodating portion 148 Lower bearing member accommodating portion 150 Lower bearing member 152 Shaft hole 154 Axial member 156 Lower end portion 158 Blade casing 160 Outer periphery flange 161 Fixing holder 162 Side peripheral wall 164 Extending portion 164a Inner periphery side opening portion 168 Upper bearing member 170 Shaft hole 172 Top portion 174 Fluid introducing passage 186 Main body casing side fixing bracket 204 Coil portion 206 Bobbin casing 208 Winding wire 210 Coil 214 Coil cover main body 216 Coil side fixing protruded portion 226 Connector 228 Lead line 230 Magnetic pole sensor 240 Screw member O Rotation central axis S1 Interior space S2 Rotating accommodating space V1V6 Clearance