JP6621669B2 - Centrifugal pump and cooling system using centrifugal pump - Google Patents

Description

  The present invention is, for example, a centrifugal pump for circulating a fluid in a closed circuit, such as a refrigerant used in a refrigerant circuit such as an air conditioner or a refrigerator, or a cooling water used in a cooling circuit such as a component or device that generates heat, The present invention also relates to a cooling system using a centrifugal pump.

  FIG. 9 is a longitudinal sectional view of a conventional centrifugal pump, and FIG. 10 is a longitudinal sectional view similar to FIG. 9 showing a state where a plurality of thrust washers 230 are mistakenly inserted in the conventional centrifugal pump. FIG. 11, FIG. 11 is a partially enlarged cross-sectional view of a portion G in FIG. 10, and FIG. 12 is a diagram showing a state in the case of forgetting to install the thrust washer 230 in the conventional centrifugal pump. A similar longitudinal sectional view, FIG. 13, is a partially enlarged sectional view of a portion I in FIG.

  As shown in FIG. 9, the conventional centrifugal pump 100 includes a rotary blade member 102. The rotary blade member 102 includes a plurality of impeller members 106 that extend radially in the outer circumferential direction at the upper portion of a cylindrical bearing portion 104.

  In the present specification, terms indicating the vertical direction such as “upper”, “upper”, “upper”, “lower”, “lower”, “lower” and the like indicate the vertical direction in each drawing. Yes, it indicates the relative positional relationship of each member, and does not indicate an absolute positional relationship.

  The impeller member 106 includes a base end portion 108 that extends in the lower outer peripheral direction of the bearing portion 104, a diameter-expanding portion 110 that expands upward from the base end portion 108 in the outer peripheral direction, and the diameter-expanding portion 110. It is comprised from the outer blade | wing part 112 extended in the outer peripheral direction.

  The rotating blade member 102 is provided with a rotor magnet 122 made of an annular permanent magnet on the outer periphery of the base end portion 108.

  The rotor magnet 122 and the impeller member 106 are structured to prevent the rotor magnet 122 from rotating and falling off the impeller member 106, and the impeller member 106 together with the rotor magnet 122. The shaft member 154 is configured to rotate.

  Furthermore, the conventional centrifugal pump 100 includes a main body case 124 that houses the rotary blade member 102, as shown in FIG. The main body case 124 includes an upper main body case 126, and the upper main body case 126 includes a top wall 128 and a side peripheral wall 130 that extends downward from the outer periphery of the top wall 128.

  A suction side joint member (suction side conduit) 132 is fixed to the side peripheral wall 130 of the upper body case 126 in a sealed state. Thus, the suction side joint member 132 is configured to communicate with the main body case 124.

  Further, a discharge side joint member 136 is fixed to the side peripheral wall 130 of the upper body case 126 in a sealed state so as to face the suction side joint member 132. Thus, the discharge side joint member 136 is configured to communicate with the main body case 124.

  Also, as shown in FIG. 9, the main body case 124 includes a lower main body case (rotor case) 138. The outer peripheral flange 142 of the lower main body case 138 is fixed to the inner wall of the lower end 141 of the side peripheral wall 130 of the upper main body case 126 in a sealed state. Thus, an internal space S1 surrounded by the upper body case 126 and the lower body case 138 is formed in the body case 124.

  As shown in FIG. 9, the lower main body case 138 includes a blade accommodating portion 144 that extends from the outer peripheral flange 142 of the lower main body case 138 to the inner peripheral side, and a rotor that extends downward from the blade accommodating portion 144. And a magnet housing portion 146. Further, a bottomed cylindrical shaft fixing member accommodating portion 148 is formed below the rotor magnet accommodating portion 146.

  The shaft fixing member 150 is fitted into the shaft fixing member accommodating portion 148 by, for example, press fitting. The lower end portion 156 of the shaft member 154 is fixed to the shaft hole 152 formed in the shaft fixing member 150 so as to be pivotally supported.

  A shaft member 154 is inserted into the bearing portion 104 of the rotary blade member 102 so that the rotary blade member 102 can rotate.

  Further, the main body case 124 includes a blade case 158. In the blade case 158, the outer peripheral flange 160 of the blade case 158 is fixed to the lower side of the side peripheral wall 130 of the upper body case 126 in a sealed state on the suction side joint member 132 side.

  That is, the outer peripheral flange 160 of the blade case 158 is fixed in a sealed state so as to be sandwiched between the inner wall of the lower end 141 of the side peripheral wall 130 of the upper body case 126 and the outer peripheral flange 142 of the lower body case 138. Has been.

  On the other hand, the blade case 158 has an opening formed in the side peripheral wall 162 on the discharge side joint member 136 side, and the periphery of the opening of the side peripheral wall 162 is connected to the side peripheral wall 130 of the main body case 124 on the discharge side joint member. Together with 136, it is fixed in a sealed state.

  Further, the blade case 158 includes a side peripheral wall 162 extending upward from the outer peripheral flange 160, and an extending portion 164 extending from the side peripheral wall 162 inward in the horizontal direction along the outer blade portion 112 of the impeller member 106. It has.

  With such a shape, the impeller member 106 can be accommodated between the vane case 158 and the vane accommodating portion 144 of the lower main body case 138.

  In addition, the blade case 158 partitions the internal space S1 formed by the upper body case 126 and the lower body case 138 to form a fluid introduction flow path 174 on the upper side, and the rotary blade member 102 on the lower side. A rotating part accommodating space S2 for accommodating is formed.

  Further, as shown in FIG. 9, the conventional centrifugal pump 100 is disposed on the outer periphery of the rotor magnet accommodating portion 146 of the lower body case 138 so as to be positioned around the rotor magnet 122, and the rotary blade member 102 is disposed on the outer periphery of the rotor magnet 122. A coil unit 204 to be rotated is provided. The coil unit 204 is provided with a plurality of coils 210 composed of windings 208 wound around a bobbin case 206 and spaced apart at regular intervals in the circumferential direction.

  These coils 210 are mounted so as to be fitted to the outer periphery of the rotor magnet housing portion 146 of the lower body case 138 of the main body case 124 inside the substantially cylindrical coil cover main body 214.

  As shown in FIG. 9, the coil cover main body 214 containing the coil portion 204 is moved below the main body case 124 by engaging the main body case side fixing bracket 186 and the coil side fixing protrusion 216. It is configured so that it can be detachably attached.

  In FIG. 9, reference numeral 226 denotes a connector, and 228 denotes a lead wire.

  In the conventional centrifugal pump 100 configured as above, the coil 210 is excited by passing a current through the coil 210 of the coil unit 204, thereby acting on the rotor magnet 122 of the rotating blade member 102, thereby rotating the rotating blade. The member 102 can be rotated around a shaft member 154 inserted through the bearing portion 104.

  As a result, the fluid sucked from the suction side joint member 132 passes through the inner peripheral side opening 164a of the extending portion 164 of the blade case 158 from the fluid introduction channel 174 formed by the blade case 158 and the upper body case 126. pass. Then, the fluid that has passed through the inner peripheral side opening 164a is introduced into the rotating portion accommodating space S2 formed by the blade case 158 and the lower body case 138.

  Further, the fluid introduced into the rotating part accommodating space S2 by the rotational force of the impeller member 106 of the rotating blade member 102 is discharged from the rotating part accommodating space S2 of the main body case 124 via the discharge side joint member 136. It is like that.

Japanese Patent Laid-Open No. 10-9185 JP 2014-141913 A

  By the way, in such a conventional centrifugal pump 100, in order to prevent wear and contact noise due to rotational sliding between the rotary blade member 102 and the shaft member 154, as shown in FIG. A thrust washer 230 is interposed around the shaft member 154 between the portion 102 a and the upper end portion 150 a of the shaft fixing member 150.

  That is, by interposing the thrust washer 230, the dynamic friction between the two members of the rotary blade member 102 (bearing portion 104) and the shaft member 154 is reduced. By reducing the dynamic friction in this manner, the generation of foreign matter and contact noise due to wear between the rotary blade member 102 (bearing portion 104) and the shaft member 154 are prevented.

  Further, the thrust washer 230 also has an effect of reducing the force in the thrust direction (that is, the direction toward the shaft member (shaft) 154 that is the rotation shaft) generated in the rotary blade member 102, and the rotary blade member 102 (bearing portion) 104) and the shaft member 154, which is a rotating shaft, has an effect of preventing wear.

  By the way, such a conventional centrifugal pump 100 is used, for example, in a system that assists cooling of heat-generating parts, equipment, etc. by utilizing the circulation of fluid, and depending on the use of the incorporated system, It may also be used for household equipment (home appliances).

  In recent years, household appliances have become smaller and quieter, and in order to achieve this, similar specifications are required for pumps that perform fluid circulation.

  Further, a pump intended for circulating a high-purity fluid is required to have high airtightness, corrosion resistance, etc., and intrusion of internal residues and foreign matters is not permitted during manufacture and use.

  Incidentally, as shown in FIG. 9, in the conventional centrifugal pump 100, due to the structure of the centrifugal pump 100, the rotary blade member 102 is configured to rotate and slide on the thrust washer 230.

  However, as shown in FIGS. 10 and 11, a plurality of thrust washers 230 are erroneously disposed around the shaft member 154 between the lower end portion 102 a of the rotary blade member 102 and the upper end portion 150 a of the shaft fixing member 150. There is a possibility of interposing.

  In this case, foreign matters are generated due to wear (wear powder) by sliding between the thrust washers 230.

  On the other hand, as shown in FIGS. 12 and 13, the thrust washer 230 is erroneously interposed around the shaft member 154 between the lower end portion 102 a of the rotary blade member 102 and the upper end portion 150 a of the shaft fixing member 150. You might forget to do it.

  In this case, the sliding resistance between the rotary blade member 102 (bearing portion 104) and the shaft member 154 increases, and foreign matter and contact noise are generated due to wear, resulting in a decrease in durability. become.

  However, since the inside cannot be confirmed after the centrifugal pump 100 is assembled, a plurality of sheets are erroneously disposed around the shaft member 154 between the lower end portion 102a of the rotary blade member 102 and the upper end portion 150a of the shaft fixing member 150. It is impossible to confirm whether the thrust washer 230 has been inserted or whether the thrust washer 230 has been forgotten by mistake.

  In view of such a current situation, the present invention erroneously places a plurality of components around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member without using a complicated structure or an inspection mechanism. It is possible to check whether a thrust washer has been inserted, or forgetting to install a thrust washer by mistake, preventing the durability from being lowered due to an error in the manufacturing process. It is an object of the present invention to provide a centrifugal pump capable of performing the above.

  In addition, the present invention can suppress the generation of wear powder, wear powder does not enter the sliding portion between the rotary blade member and the shaft member (shaft), excellent in durability and operability, An object of the present invention is to provide a centrifugal pump that does not generate abnormal noise, is excellent in quietness, and can maintain the intended pump performance.

The present invention was invented in order to achieve the problems and objects in the prior art as described above.
A rotating blade member composed of an impeller member and a rotor magnet provided on the impeller member;
A body case that houses the rotating blade member;
A coil portion arranged to be located around the rotor magnet and rotating the rotary blade member;
A shaft member provided in the main body case and pivotally supported so that the rotary blade member rotates around the periphery;
A shaft fixing member disposed at an end portion of the shaft member in the axial direction and fixing the end portion of the shaft member;
A thrust washer interposed between the rotary blade member and the shaft fixing member;
A centrifugal pump comprising:
The relation between the thickness t of the thrust washer interposed between the rotary blade member and the shaft fixing member, the gap H between the axial end of the rotary blade member and the main body case,
H <t
It is set so that it becomes.

With this configuration, the thickness t of the thrust washer interposed between the rotating blade member and the shaft fixing member, the gap H between the axial end of the rotating blade member and the main body case Relationship with
H <t
It is set to become.

  Therefore, if a plurality of thrust washers are accidentally inserted around the shaft member between the lower end portion of the rotating blade member and the upper end portion of the shaft fixing member, the axial direction of the rotating blade member The end portion and the main body case come into contact with each other.

  Also, if you forget to install a thrust washer around the shaft member between the lower end of the rotating blade member and the upper end of the shaft fixing member, the shaft is fixed to the rotating blade member. While directly contacting with the member, the axial end of the rotary blade member and the main body case are in contact with each other.

  As described above, the axial end of the rotating blade member and the main body case come into contact with each other, so that rotational resistance is generated with respect to the rotation of the rotating blade member, and the current value increases or the rotational speed of the rotating blade member increases. Will be reduced.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, a plurality of thrust washers are erroneously interposed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the thrust washer has been accidentally inserted, and it is possible to prevent the durability from being lowered due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

  In the centrifugal pump of the present invention, the gap H between the axial end of the rotary blade member and the main body case has an axial end portion on the axial fixing member side of the rotary vane member, and the main body case. It is the gap H between these.

  With this configuration, if you forget to accidentally insert a thrust washer around the shaft member between the lower end of the rotating blade member and the upper end of the shaft fixing member, The end of the blade member in the axial direction on the shaft fixing member side comes into contact with the main body case.

  As a result, the end of the rotating blade member on the shaft fixing member side in the axial direction and the main body case come into contact with each other, thereby causing rotational resistance against the rotation of the rotating blade member, increasing the current value, or rotating blade member. The number of rotations will decrease.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, forgetting to install a thrust washer by mistake around the shaft member between the lower end of the rotary blade member and the upper end of the shaft fixing member without using a complicated structure or inspection mechanism. It is possible to confirm whether or not the failure has occurred, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

The centrifugal pump of the present invention is
A gap H between the axial end of the rotary blade member and the main body case is a gap H1 between the axial end of the rotor magnet of the rotary blade member and the main body case.
H1 <t
It is set so that it becomes.

  With this configuration, since H1 <t is set, a thrust washer is accidentally placed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member. When forgetting to interpose, the axial end of the rotor magnet of the rotating blade member and the main body case come into contact with each other.

  As a result, the axial end of the rotor magnet of the rotating blade member and the main body case come into contact with each other, thereby causing rotational resistance against rotation of the rotating blade member, increasing the current value, and rotating the rotating blade member. The number will decrease.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, forgetting to install a thrust washer by mistake around the shaft member between the lower end of the rotary blade member and the upper end of the shaft fixing member without using a complicated structure or inspection mechanism. It is possible to confirm whether or not the failure has occurred, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

  Further, in the centrifugal pump of the present invention, the gap H between the axial end of the rotary blade member and the main body case has an end opposite to the axial fixed member side in the axial direction of the impeller member, It is a gap H between the main body case and the main body case.

  By configuring in this way, when a plurality of thrust washers are accidentally interposed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member, the blade The end of the vehicle member in the axial direction opposite to the shaft fixing member side comes into contact with the main body case.

  Thereby, the end of the impeller member in the axial direction opposite to the shaft fixing member side and the main body case come into contact with each other, thereby causing rotational resistance to the rotation of the rotating blade member, increasing the current value, The number of rotations of the rotary blade member will decrease.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, a plurality of thrust washers are erroneously interposed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the failure has occurred, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

The centrifugal pump of the present invention is
A gap H between the axial end of the rotary blade member and the main body case is a gap H2 between the axial end of the outer blade portion of the impeller member of the rotary blade member and the main body case. Yes,
H2 <t
It is set so that it becomes.

  With this configuration, since H2 <t is set, a plurality of sheets are mistakenly around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member. When the thrust washer is interposed, the axial end of the outer blade portion of the impeller member of the rotating blade member and the main body case come into contact with each other.

  Thereby, the axial end of the outer blade part of the impeller member of the impeller member of the rotating blade member and the main body case come into contact with each other, resulting in rotational resistance against the rotation of the rotating blade member, and the current value increases. The number of rotations of the rotary blade member will decrease.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, a plurality of thrust washers are erroneously interposed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the failure has occurred, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

The centrifugal pump of the present invention is
A gap H between the axial end of the rotary blade member and the main body case is a gap H3 between the axial end of the bearing portion of the impeller member of the rotary blade member and the main body case. ,
H3 <t
It is set so that it becomes.

  With this configuration, since H3 <t is set, a plurality of sheets are erroneously formed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member. When the thrust washer is interposed, the axial end of the bearing portion of the impeller member of the rotary blade member and the main body case come into contact with each other.

  As a result, the axial end of the bearing portion of the impeller member of the rotating blade member and the main body case come into contact with each other, thereby causing rotational resistance against rotation of the rotating blade member, increasing the current value, The number of rotations of the blade member will decrease.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, a plurality of thrust washers are erroneously interposed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the failure has occurred, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

In addition, the cooling system using the centrifugal pump of the present invention,
A cooling system using the centrifugal pump according to any one of the above,
A cooling system including a heat medium circulation path for cooling an object to be cooled is characterized in that a centrifugal pump is disposed in the heat medium circulation path.

  By configuring in this way, for example, when used in a system that assists cooling of heat-generating parts, equipment, etc. using circulation of fluid, it is excellent in durability and operability, and no abnormal noise is generated. In addition, it is possible to provide a cooling system with excellent silence.

According to the present invention, the thickness t of the thrust washer interposed between the rotary blade member and the shaft fixing member, and the gap H between the axial end of the rotary blade member and the main body case. Relationship
H <t
It is set to become.

  Therefore, if you accidentally forget to install the thrust washer around the shaft member between the lower end of the rotating blade member and the upper end of the shaft fixing member, the rotating blade member and the shaft fixing member And the end of the rotary blade member in the axial direction come into contact with the main body case.

  Further, when a plurality of thrust washers are mistakenly inserted around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member, the axial direction of the rotary blade member The end portion and the main body case come into contact with each other.

  As described above, the axial end of the rotating blade member and the main body case come into contact with each other, so that rotational resistance is generated with respect to the rotation of the rotating blade member, and the current value increases or the rotational speed of the rotating blade member increases. Will be reduced.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Therefore, a plurality of thrust washers are erroneously interposed around the shaft member between the lower end portion of the rotary blade member and the upper end portion of the shaft fixing member without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the thrust washer has been accidentally inserted, and it is possible to prevent the durability from being lowered due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

FIG. 1 is a longitudinal sectional view of a centrifugal pump according to the present invention. FIG. 2 is a partially enlarged cross-sectional view of a portion C of the centrifugal pump shown in FIG. FIG. 3 is a partially enlarged cross-sectional view of a portion D of the centrifugal pump of FIG. FIG. 4 is a longitudinal sectional view similar to FIG. 1 showing a state in the case of forgetting to install the thrust washer 50 by mistake in the centrifugal pump of the present invention. FIG. 5 is a partial enlarged cross-sectional view of a portion E in FIG. FIG. 6 is a longitudinal sectional view similar to FIG. 1 showing a state where a plurality of thrust washers 50 are mistakenly inserted in the centrifugal pump of the present invention. FIG. 7 is a partial enlarged cross-sectional view of a portion F in FIG. FIG. 8 is a schematic view showing an embodiment of a cooling system 300 using the centrifugal pump of the present invention. FIG. 9 is a longitudinal sectional view of a conventional centrifugal pump. FIG. 10 is a longitudinal sectional view similar to FIG. 9 showing a state where a plurality of thrust washers 230 are mistakenly inserted in a conventional centrifugal pump. FIG. 11 is a partial enlarged cross-sectional view of a portion G in FIG. FIG. 12 is a longitudinal sectional view similar to FIG. 9 showing a state in the case where the conventional centrifugal pump forgets to install the thrust washer 230 by mistake. 13 is a partially enlarged cross-sectional view of a portion I in FIG.

Hereinafter, embodiments (examples) of the present invention will be described in more detail with reference to the drawings.
(Example 1)

  1 is a longitudinal sectional view of a centrifugal pump of the present invention, FIG. 2 is a partially enlarged sectional view of a portion C of the centrifugal pump of FIG. 1, and FIG. 3 is a partially enlarged sectional view of a portion D of the centrifugal pump of FIG. FIG. 4 is a longitudinal sectional view similar to FIG. 1 showing a state where the thrust washer 50 is forgotten by mistake in the centrifugal pump of the present invention, and FIG. FIG. 6 is a partially enlarged sectional view, FIG. 6 is a longitudinal sectional view similar to FIG. 1 showing a state where a plurality of thrust washers 50 are mistakenly inserted in the centrifugal pump of the present invention, and FIG. It is a partial expanded sectional view of F part of 6. FIG.

  In FIG. 1, the code | symbol 10 has shown the centrifugal pump of this invention whole.

  As shown in FIG. 1, the centrifugal pump 10 of the present invention includes a rotary blade member 12. The rotary blade member 12 includes a plurality of impeller members 16 that extend radially in the outer circumferential direction on the upper part of a cylindrical bearing portion 14.

  The number of impeller members 16 may be selected according to the application of the centrifugal pump 10 and the required pump capacity, and is not particularly limited.

  As shown in FIG. 1, the impeller member 16 includes a base end portion 18 that extends in the lower outer peripheral direction of the bearing portion 14, and a diameter increasing portion 20 that increases in diameter from the base end portion 18 in the outer peripheral direction. And an outer blade portion 22 extending in the outer peripheral direction from the enlarged diameter portion 20.

  By setting the shape of the impeller member 16 to such a shape, the discharge capability can be improved by the action of the outer blade portion 22 due to the rotation of the impeller member 16.

  Further, the rotary blade member 12 is provided with a rotor magnet 32 made of an annular permanent magnet on the outer periphery of the base end portion 18.

  The rotor magnet 32 and the impeller member 16 are structured to prevent the rotor magnet 32 from rotating and falling off the impeller member 16, and the impeller member 16 together with the rotor magnet 32. The shaft member 64 is configured to rotate.

  Moreover, the centrifugal pump 10 of the present invention includes a main body case 34 that accommodates the rotary blade member 12 as shown in FIG. The main body case 34 includes an upper main body case 36, and the upper main body case 36 includes a top wall 38 and a side peripheral wall 40 that extends downward from the outer periphery of the top wall 38.

  As shown in FIG. 1, the side peripheral wall 40 of the upper body case 36 is formed with an opening for fixing the suction side joint member 42. As shown in FIG. 1, the suction side coupling member 42 is fixed to the opening in a sealed state by, for example, welding, brazing, welding, or the like. Thus, the suction side joint member 42 is configured to communicate with the main body case 34.

  An opening for fixing the discharge side joint member 46 is formed in the side peripheral wall 40 of the upper body case 36.

  As shown in FIG. 1, the discharge-side joint member 46 is fixed to the opening in a sealed state by, for example, welding, brazing, welding, or the like. Accordingly, the discharge side joint member 46 is configured to communicate with the main body case 34.

  As shown in FIG. 1, the main body case 34 includes a lower main body case 48. The outer peripheral flange 52 of the lower main body case 48 is fixed to the inner wall of the lower end 51 of the side peripheral wall 40 of the upper main body case 36 in a sealed state, for example, by welding, brazing, welding, or the like. Thus, an internal space S <b> 1 surrounded by the upper body case 36 and the lower body case 48 is formed in the body case 34.

  As shown in FIG. 1, the lower main body case 48 includes, from the outer peripheral flange 52 of the lower main body case 48, a blade accommodating portion 54 that extends horizontally to the inner peripheral side, and extends downward from the blade accommodating portion 54. And a rotor magnet housing portion 56. Further, a bottomed cylindrical shaft fixing member accommodating portion 58 is formed below the rotor magnet accommodating portion 56.

  The shaft fixing member 60 is fitted into the shaft fixing member accommodating portion 58 by, for example, press fitting. The lower end portion 66 of the shaft member 64 is fixed to the shaft hole 62 formed in the shaft fixing member 60 so as to be supported by, for example, press fitting.

  That is, as shown in FIG. 1, in the centrifugal pump 10 of this embodiment, the upper end portion of the shaft member 64 is not pivotally supported, and the shaft member 64 is fixed to the shaft fixing member accommodating portion 58 of the main body case 34. It is fixed via the member 60. That is, the shaft member 64 is a so-called “cantilever type” in which the shaft member 64 is fixed at the end of the shaft member 64 on the rotor magnet 32 side in the axial direction.

  Therefore, since the shaft member 64 is not fixed while being tilted, the operation efficiency of the pump is not lowered, the utmost care is not required for assembly, and the precision is not required.

  In the centrifugal pump 10 of this embodiment, the end of the bearing portion 14 of the impeller member 16 on the side of the fluid introduction flow path 84 in the axial direction, that is, the upper end portion 14 a of the bearing portion 14 extends from the blade case 68. A protruding portion is provided above the inner peripheral side opening 76 of the portion 74 so as to be exposed to the fluid introduction channel 84.

  Therefore, since it is a so-called “cantilever type”, there is no shaft fixing portion at the inner peripheral side opening of the blade case as in the conventional so-called “both-end type”.

  As a result, there is no pressure loss in the flow of the fluid due to the collision of the fluid with the shaft fixed part, the pump efficiency is not lowered, and no noise such as abnormal noise is generated. It is excellent in silence and can maintain the desired pump performance.

  Further, by configuring in this way, the rotary blade member 12 rotates, and the fluid sucked from the suction side joint member 42 flows from the fluid introduction flow path 84 formed by the blade case 68 and the upper body case 36. It passes through the inner peripheral side opening 76 of the extending portion 74 of the blade case 68.

  At this time, the fluid is rotated (rectified) by this rotation along the rotational movement of the upper end portion 14 a of the impeller member 16.

  As a result, it is easy to smoothly flow into the internal space S1 and the rotating portion accommodating space S2 through the inner peripheral opening 76 that is an inflow hole, and as a result, the pressure loss can be reduced. Yes.

  Therefore, pressure loss does not occur in the flow of fluid, pump efficiency does not decrease, noise such as abnormal noise does not occur, durability and silence are excellent, and the intended pump It is possible to maintain performance.

  A shaft member 64 is inserted into the bearing portion 14 of the rotary blade member 12 so that the rotary blade member 12 can rotate.

  Furthermore, as shown in FIG. 1, the main body case 34 includes a blade case 68. In the blade case 68, the outer peripheral flange 70 of the blade case 68 is fixed to the lower side of the side peripheral wall 40 of the upper body case 36 in a sealed state on the suction side joint member 42 side.

  That is, for example, welding, so that the outer peripheral flange 70 of the blade case 68 is sandwiched between the inner wall of the lower end 51 of the side peripheral wall 40 of the upper main body case 36 and the outer peripheral flange 52 of the lower main body case 48. It is fixed in a sealed state by brazing or welding.

  On the other hand, the blade case 68 has an opening formed in the side peripheral wall 72 on the discharge side joint member 46 side, and the periphery of the opening of the side peripheral wall 72 is connected to the side peripheral wall 40 of the main body case 34 on the discharge side joint member. Together with 46, it is fixed in a sealed state.

  The blade case 68 has a side peripheral wall 72 extending upward from the outer peripheral flange 70, and an extension extending from the side peripheral wall 72 inward in the horizontal direction in a shape along the outer blade portion 22 of the impeller member 16. A portion 74 is provided.

  With such a shape, the impeller member 16 can be accommodated between the vane case 68 and the vane accommodating portion 54 of the lower main body case 48.

  As shown in FIG. 1, the diameter of the side peripheral wall 72 of the blade case 68 is smaller than the diameter of the side peripheral wall 40 of the upper body case 36, and the height of the side peripheral wall 72 of the blade case 68 is The upper body case 36 is formed to be smaller than the height of the side peripheral wall 40.

  Thereby, the blade case 68 divides the internal space S1 formed by the upper body case 36 and the lower body case 48 to form the fluid introduction flow path 84 on the upper side and the rotary blade member 12 on the lower side. Rotation part accommodation space S2 which accommodates is formed.

  As shown in FIG. 1, the centrifugal pump 10 of the present invention is disposed on the outer periphery of the rotor magnet housing portion 56 of the lower body case 48 so as to be positioned around the rotor magnet 32, and the rotary blade member 12. The coil part 24 which rotates is provided. The coil portion 24 is provided with a plurality of coils 30 composed of windings 28 wound around a bobbin case 26 so as to be spaced apart at regular intervals in the circumferential direction.

  These coils 30 are mounted inside the substantially cylindrical coil cover main body 33 so as to be fitted to the outer periphery of the rotor magnet housing portion 56 of the lower main body case 48 of the main body case 34.

  As shown in FIG. 1, the coil cover main body 33 accommodating the coil portion 24 is moved below the main body case 34 by engaging the main body case side fixing bracket 96 and the coil side fixing protrusion 31. It is configured so that it can be detachably attached.

  In FIG. 1, reference numeral 35 denotes a connector, and 37 denotes a lead wire.

  The centrifugal pump 10 of the present invention configured as described above is operated as follows.

  First, the coil 30 is excited by passing a current through the coil 30 of the coil portion 24, thereby acting on the rotor magnet 32 of the rotating blade member 12, and the shaft through which the rotating blade member 12 is inserted into the bearing portion 14. It can be rotated around the member 64.

  As a result, the rotating blade member 12 rotates, and the fluid sucked from the suction side joint member 42 is formed by the blade case 68 and the upper body case 36 as shown by the arrow A in FIG. The passage 84 passes through the inner peripheral side opening 76 of the extending portion 74 of the blade case 68.

  Then, the fluid that has passed through the inner peripheral side opening 76 is introduced into the rotating portion accommodating space S <b> 2 formed by the blade case 68 and the lower main body case 48.

  In addition, the fluid introduced into the rotating part accommodating space S2 by the rotational force of the impeller member 16 of the rotating blade member 12 flows from the rotating part accommodating space S2 of the main body case 34 as shown by the arrow B in FIG. It is discharged via the discharge side joint member 46.

  By the way, in such a centrifugal pump 10 of the present invention, in order to prevent wear and contact noise due to rotational sliding between the rotary blade member 12 and the shaft member 64, as shown in FIGS. A thrust washer 50 is interposed around the shaft member 64 between the lower end portion 12 a of the member 12 and the upper end portion 60 a of the shaft fixing member 60.

  That is, by interposing the thrust washer 50, the dynamic friction between the two members of the rotary blade member 12 (bearing portion 14) and the shaft member 64 is reduced. By reducing the dynamic friction in this way, the generation of foreign matter and contact noise due to wear between the rotary blade member 12 (bearing portion 14) and the shaft member 64 is prevented.

  Further, the thrust washer 50 also has an effect of reducing the force in the thrust direction (that is, the direction toward the shaft member (shaft) 64 that is the rotation shaft) generated in the rotary blade member 12, and the rotary blade member 12 (bearing portion). 14) and the shaft member 64, which is the rotating shaft, has an effect of preventing wear.

  Incidentally, as shown in FIG. 9, in the conventional centrifugal pump 100, due to the structure of the centrifugal pump 100, the rotary blade member 102 is configured to rotate and slide on the thrust washer 230.

  However, as shown in FIGS. 10 and 11, a plurality of thrust washers 230 are erroneously disposed around the shaft member 154 between the lower end portion 102 a of the rotary blade member 102 and the upper end portion 150 a of the shaft fixing member 150. There is a possibility of interposing.

  In this case, foreign matters are generated due to wear (wear powder) by sliding between the thrust washers 230.

  On the other hand, as shown in FIGS. 12 and 13, the thrust washer 230 is erroneously interposed around the shaft member 154 between the lower end portion 102 a of the rotary blade member 102 and the upper end portion 150 a of the shaft fixing member 150. You might forget to do it.

  In this case, the sliding resistance between the rotary blade member 102 (bearing portion 104) and the shaft member 154 increases, and foreign matter and contact noise are generated due to wear, resulting in a decrease in durability. become.

  However, since the inside cannot be confirmed after the centrifugal pump 100 is assembled, a plurality of sheets are erroneously disposed around the shaft member 154 between the lower end portion 102a of the rotary blade member 102 and the upper end portion 150a of the shaft fixing member 150. It is impossible to confirm whether the thrust washer 230 has been inserted or whether the thrust washer 230 has been forgotten by mistake.

For this reason, in the centrifugal pump 10 of the present invention, as shown in FIGS. 1 to 3, the thickness t of the thrust washer 50 interposed between the rotary blade member 12 and the shaft fixing member 60 has a rotary blade. An end portion in the axial direction of the member 12 (that is, an end portion 32a in the axial direction of a rotor magnet 32 of the rotating blade member 12 described later, and an end portion 22a in the axial direction of the outer blade portion 22 of the impeller member 16 of the rotating blade member 12 The relationship between the upper end portion 14a in the axial direction of the bearing portion 14 of the impeller member 16 of the rotary blade member 12 and a gap H (H1, H2, H3, which will be described later) between the main body case 34,
H <t
It is set to become.

With this configuration, the thickness t of the thrust washer 50 interposed between the rotary blade member 12 and the shaft fixing member 60, the axial end of the rotary blade member 12, the main body case 34, The relationship with the gap H between
H <t
It is set to become.

  Therefore, when a plurality of thrust washers 50 are accidentally interposed around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60, the rotary blade member 12 end portions in the axial direction and the main body case 34 come into contact with each other.

  In addition, even if the thrust washer 50 is forgotten to be accidentally disposed around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60, the rotary blade The member 12 and the shaft fixing member 60 are in direct contact with each other, and the axial end portion of the rotary blade member 12 is in contact with the main body case 34.

  As described above, the axial end of the rotary blade member 12 and the main body case 34 come into contact with each other, so that rotational resistance is generated with respect to the rotation of the rotary blade member 12, and the current value increases or the rotary blade member 12. The number of rotations will decrease.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Accordingly, a plurality of thrust washers 50 are erroneously inserted around the shaft member between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60 without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the thrust washer 50 has been accidentally installed, and it is possible to prevent the durability from being lowered due to an error in the manufacturing process. .

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between a rotary blade member and a shaft member (shaft), it is excellent in durability and operability, and abnormal noise is generated. It does not occur, is excellent in quietness, and can maintain the intended pump performance.

  That is, the gap H between the axial end of the rotary blade member 12 and the main body case 34 is the gap H between the end of the rotary vane member 12 on the axis fixing member side in the axial direction and the main body case. It is.

Specifically, as shown in FIGS. 1 and 2, in the centrifugal pump 10 of the present invention, the gap H between the axial end of the rotary blade member 12 and the main body case 34 has a rotary blade member. 12 is a gap H1 between the axial end portion 32a of the 12 rotor magnets 32 and the horizontal portion 48a of the lower body case 48 of the body case 34;
H1 <t
It is set to become.

  With this configuration, since H1 <t is set, a thrust is accidentally caused around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60. 4 and FIG. 5, when the forgetting to place the washer 50, the axial end 32 a of the rotor magnet 32 of the rotary blade member 12 and the lower main body of the main body case 34 are provided. The horizontal portion 48a of the case 48 comes into contact (contact) as shown by a portion J in FIGS.

  As a result, the axial end 32a of the rotor magnet 32 of the rotary blade member 12 and the horizontal portion 48a of the lower main body case 48 of the main body case 34 come into contact with each other, thereby rotating with respect to the rotation of the rotary blade member 12. It becomes resistance, and the current value increases or the rotational speed of the rotary blade member 12 decreases.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Accordingly, a thrust washer is erroneously interposed around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60 without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not the user has forgotten, and it is possible to prevent the durability from being lowered due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between the rotary blade member 12 and the shaft member (shaft) 64, and is excellent in durability and operability. No noise is generated, the sound is excellent, and the desired pump performance can be maintained.

  Next, a gap H between the axial end of the rotary blade member 12 and the main body case 34 is such that the end of the impeller member 16 opposite to the axial fixing member side in the axial direction, A portion that is the gap H between the two will be described.

As shown in FIGS. 1 and 3, in this part, in the centrifugal pump 10 of the present invention, the gap H between the axial end portion of the rotary blade member 12 and the main body case 34 has a rotary blade member. A gap H2 between the axial end 22a of the outer blade portion 22 of the twelve impeller members 16 and the blade case 68 of the main body case 34;
H2 <t
It is set to become.

  In such a case, since H2 <t is set, a plurality of sheets are mistakenly around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60. When the thrust washer 50 is interposed, as shown in FIGS. 6 and 7, the axial end 22 a of the outer blade portion 22 of the impeller member 16 of the rotary blade member 12, and the main body case 34. The blade case 68 comes into contact (contact) as shown by a portion K in FIGS.

  Accordingly, the axial end 22a of the outer blade portion 22 of the impeller member 16 of the rotary blade member 12 and the blade case 68 of the main body case 34 come into contact with each other to rotate with respect to the rotation of the rotary blade member 12. It becomes resistance, and the current value increases or the rotational speed of the rotary blade member 12 decreases.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Accordingly, a plurality of thrust washers 50 are mistakenly disposed around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60 without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not it has been interposed, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between the rotary blade member 12 and the shaft member (shaft) 64, and is excellent in durability and operability. No sound is generated, the sound is excellent, and the desired pump performance can be maintained.

Finally, as shown in FIGS. 1 and 3, in the centrifugal pump 10 of the present invention, the gap H between the axial end portion of the rotary blade member 12 and the main body case 34 is set so that the rotary blade member 12 has a gap H. A gap H3 between the axial upper end portion 14a of the bearing portion 14 of the impeller member 16 and the top wall 38 of the main body case 34;
H3 <t
The site | part set so that it may become is demonstrated.

  Since this portion is set to satisfy H3 <t, a plurality of sheets are erroneously formed around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60. When the thrust washer 50 is interposed, as shown in FIGS. 6 and 7, the axial upper end portion 14 a of the bearing portion 14 of the impeller member 16 of the rotary blade member 12 and the body case 34 The top wall 38 comes into contact (contact) as shown by the L portion in FIGS. 6 and 7.

  As a result, the axially upper end portion 14 a of the bearing portion 14 of the impeller member 16 of the rotating blade member 12 and the top wall 38 of the main body case 34 come into contact with each other, so that rotation resistance against rotation of the rotating blade member 12 is achieved. Thus, the current value increases or the rotational speed of the rotary blade member 12 decreases.

  As a result, the performance value of the centrifugal pump, such as the current value and the rotational speed, is affected. For example, a conventional measuring device such as an ammeter or a rotational speed detector can be used, and the detection becomes easy.

  Accordingly, a plurality of thrust washers 50 are mistakenly disposed around the shaft member 64 between the lower end portion of the rotary blade member 12 and the upper end portion of the shaft fixing member 60 without using a complicated structure or an inspection mechanism. It is possible to confirm whether or not it has been interposed, and it is possible to prevent a decrease in durability due to an error in the manufacturing process.

  For this reason, generation | occurrence | production of abrasion powder can be suppressed, and abrasion powder does not enter into the sliding part between the rotary blade member 12 and the shaft member (shaft) 64, and is excellent in durability and operability. No sound is generated, the sound is excellent, and the desired pump performance can be maintained.

In the above embodiment, the gap H between the axial end of the rotary blade member 12 and the main body case 34 is such that the end of the impeller member 16 opposite to the axial fixing member side, The gap H between the case 34 is the smallest gap H,
H <t
It is only necessary to be set so that.

That is, in the centrifugal pump 10 of this embodiment, the gap H2 between the axial end 22a of the outer blade portion 22 of the impeller member 16 of the rotary blade member 12 and the blade case 68 of the main body case 34, the rotary blade Regarding the gap H3 between the axial upper end 14a of the bearing portion 14 of the impeller member 16 of the member 12 and the top wall 38 of the main body case 34, at least the smaller one of the gap H2 and the gap H3. For gap H
The relationship between the thickness t of the thrust washer interposed between the rotary blade member and the shaft fixing member, the gap H between the axial end of the rotary blade member and the main body case is as follows:
H <t
It is only necessary to be set so that.
(Example 2)

  FIG. 8 is a schematic view showing an embodiment of a cooling system 300 using the centrifugal pump of the present invention.

  The centrifugal pump 10 used in the cooling system 300 of this embodiment has basically the same configuration as the centrifugal pump 10 of the embodiment shown in FIGS.

  In the cooling system 300 of this embodiment, as shown in FIG. 8, in the cooling system 300 including the heat medium circulation path 302 for cooling the object to be cooled, the centrifugal pump 10 is disposed in the heat medium circulation path 302. This is the configuration.

  That is, the cooling system 300 of this embodiment includes the centrifugal pump 10 in the heat medium circulation path 302, and the heat medium causes the heat medium such as water to pass through the heat medium circulation path 302 a by the centrifugal pump 10. Via the radiator 304.

  In the radiator 304, although not shown, the heat medium is cooled by, for example, air cooling or water cooling using a fan or the like.

  The heat medium cooled by passing through the radiator 304 is sent to the heat exchanger 306 via the heat medium circulation paths 302b and 302c. The object to be cooled 308 to be cooled is attached to the heat exchanger 306. The heat of the object to be cooled 308 is exchanged with the heat medium to cool the object to be cooled 308. It can be warmed.

  Then, the heat medium warmed by passing through the heat exchanger 306 is circulated again to the centrifugal pump 10 through the heat medium circulation paths 302a and 302b.

  And it is comprised so that such a circulation cooling cycle may be performed repeatedly.

  By configuring in this way, for example, when used in a system that assists cooling of heat-generating parts, equipment, etc. using circulation of fluid, it is excellent in durability and operability, and no abnormal noise is generated. In addition, it is possible to provide a cooling system with excellent silence.

  The preferred embodiment of the present invention has been described above, but the present invention is not limited to this. For example, in the above embodiment, the main body case 34, the upper main body case 36, the lower main body case 48, the blades The material of the case 68, the rotary blade member 12, the thrust washer 50, the shaft member 64 and the like may be made of metal or resin, and may be appropriately selected depending on the application, and is not particularly limited. Absent.

  Moreover, in the said Example, although the number of the suction side coupling members 42 and the discharge side joint members 46 was each one, it is also possible to provide two or more numbers of the suction side joint members 42 and the discharge side joint members 46. Various modifications can be made without departing from the scope of the present invention.

  The present invention is, for example, a centrifugal pump for circulating a fluid in a closed circuit, such as a refrigerant used in a refrigerant circuit such as an air conditioner or a refrigerator, or a cooling water used in a cooling circuit such as a component or device that generates heat, And it can apply to the cooling system using a centrifugal pump.

DESCRIPTION OF SYMBOLS 10 Centrifugal pump 12 Rotating blade member 12a Lower end part 14 Bearing part 14a Upper end part 16 Impeller member 18 Base end part 20 Expanded part 22 Outer blade part 22a End part 24 Coil part 26 Bobbin case 28 Winding 30 Coil 31 Coil side fixing Projection 32 Rotor magnet 32a End 33 Coil cover main body 34 Main body case 35 Connector 36 Upper main body case 37 Lead wire 38 Top wall 40 Side peripheral wall 42 Suction side joint member 46 Discharge side joint member 48 Lower main body case 48a Horizontal portion 50 Thrust Washer 51 Lower end 52 Outer peripheral flange 54 Blade housing portion 56 Rotor magnet housing portion 58 Shaft fixing member housing portion 60 Shaft fixing member 60a Upper end portion 62 Shaft hole 64 Shaft member 66 Lower end portion 68 Blade case 70 Outer flange 72 Side peripheral wall 74 Extension portion 76 Inner peripheral side opening 84 Fluid introduction flow path 96 Suction side fixing metal fitting 100 Centrifugal pump 102 Rotary blade member 102a Lower end portion 104 Bearing portion 106 Impeller member 108 Base end portion 110 Expanded portion 112 Outer blade portion 122 Rotor magnet 124 Body case 126 Upper body case 128 Top wall 130 Side wall 132 Suction side joint member 136 Discharge side joint member 138 Lower main body case 141 Lower end 142 Outer flange 144 Blade accommodating part 146 Rotor magnet accommodating part 148 Shaft fixing member accommodating part 150 Shaft fixing member 150a Upper end part 152 Shaft hole 154 Shaft member 156 Lower end 158 Blade case 160 Outer peripheral flange 162 Side peripheral wall 164 Extension part 164a Inner peripheral side opening 174 Fluid introduction flow path 186 Main body case side fixing bracket 204 Coil part 206 Bobbin case 208 Winding 210 Coil 214 Coil cover main body 216 Side fixed protrusion 226 Connector 228 Lead wire 230 Thrust washer 300 Cooling system 302 Heat medium circulation path 302a Heat medium circulation path 302b Heat medium circulation path 304 Radiator 306 Heat exchanger 308 Cooled object H Gap H1 Gap H2 Gap H3 Gap S1 Inside Space S2 Rotating part accommodation space

Claims (7)

A rotating blade member composed of an impeller member and a rotor magnet provided on the impeller member;
A body case that houses the rotating blade member;
A coil portion arranged to be located around the rotor magnet and rotating the rotary blade member;
A shaft member provided in the main body case and pivotally supported so that the rotary blade member rotates around the periphery;
A shaft fixing member disposed at an end portion of the shaft member in the axial direction and fixing the end portion of the shaft member;
A thrust washer interposed between the rotary blade member and the shaft fixing member;
A centrifugal pump comprising:
The relation between the thickness t of the thrust washer interposed between the rotary blade member and the shaft fixing member, the gap H between the axial end of the rotary blade member and the main body case,
H <t
Centrifugal pump characterized by being set to be   The gap H between the axial end of the rotary blade member and the main body case is the gap H between the axial fixed member side end of the rotary vane member and the main body case. The centrifugal pump according to claim 1, characterized in that: A gap H between the axial end of the rotary blade member and the main body case is a gap H1 between the axial end of the rotor magnet of the rotary blade member and the main body case.
H1 <t
The centrifugal pump according to claim 2, wherein the centrifugal pump is set to be   A gap H between the axial end of the rotary blade member and the main body case is a gap H between the end of the impeller member opposite to the axial fixing member side in the axial direction and the main body case. The centrifugal pump according to claim 1, wherein the centrifugal pump is provided. A gap H between the axial end of the rotary blade member and the main body case is a gap H2 between the axial end of the outer blade portion of the impeller member of the rotary blade member and the main body case. Yes,
H2 <t
The centrifugal pump according to claim 4, wherein the centrifugal pump is set to be A gap H between the axial end of the rotary blade member and the main body case is a gap H3 between the axial end of the bearing portion of the impeller member of the rotary blade member and the main body case. ,
H3 <t
The centrifugal pump according to claim 4, wherein the centrifugal pump is set to be A cooling system using the centrifugal pump according to any one of claims 1 to 6,
A cooling system using a centrifugal pump, wherein a centrifugal pump is disposed in the heat medium circulation path in a cooling system having a heat medium circulation path for cooling an object to be cooled.

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