US20040234395A1 - Magnetic coupling pump - Google Patents
Magnetic coupling pump Download PDFInfo
- Publication number
- US20040234395A1 US20040234395A1 US10/838,197 US83819704A US2004234395A1 US 20040234395 A1 US20040234395 A1 US 20040234395A1 US 83819704 A US83819704 A US 83819704A US 2004234395 A1 US2004234395 A1 US 2004234395A1
- Authority
- US
- United States
- Prior art keywords
- main body
- rotor
- cavity
- magnetic coupling
- stator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 230000008878 coupling Effects 0.000 title claims abstract description 30
- 238000010168 coupling process Methods 0.000 title claims abstract description 30
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 30
- 239000012530 fluid Substances 0.000 claims abstract description 30
- 238000003756 stirring Methods 0.000 claims description 11
- 239000002826 coolant Substances 0.000 abstract description 28
- 230000005611 electricity Effects 0.000 description 6
- 238000001816 cooling Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 229920003002 synthetic resin Polymers 0.000 description 2
- 239000000057 synthetic resin Substances 0.000 description 2
- 239000004952 Polyamide Substances 0.000 description 1
- 239000006247 magnetic powder Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 229920002647 polyamide Polymers 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
- F04D13/064—Details of the magnetic circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0673—Units comprising pumps and their driving means the pump being electrically driven the motor being of the inside-out type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/5806—Cooling the drive system
Definitions
- the present invention relates to a magnetic coupling pump for pumping fluids such as engine coolant for vehicles, and more particularly, relates to an outer-rotor type magnetic coupling pump in which a stator is located toward a rotation center of a rotor having impellers for feeding fluids, and a substantially cylindrical magnet section of the rotor is located around the stator.
- the housing includes a pump chamber having inlet port and outlet port of coolant, and a motor chamber.
- the rotor includes impellers which are projected from top face of a disc-shaped body of the rotor to be located in the pump chamber, and a substantially cylindrical magnet section which is projected from back face of the rotor body to be located in the motor chamber.
- This rotor is located in the coolant, and is driven to rotate by rotating magnetic field generated by a stator located inward of the magnet section in the motor chamber to suck the coolant from the inlet port and exhaust it from the outlet port.
- the present invention contemplates to solve the above mentioned problem, and therefore, has an object to provide a magnetic coupling pump capable of preventing heat-up of an inner circumferential part of the stator.
- a magnetic coupling pump is to suck fluid from an inlet port and exhaust the fluid from an outlet port, and includes a housing and a rotor.
- the housing includes a pump chamber having the inlet and outlet ports of fluid and a motor chamber.
- the rotor includes: a plurality of impellers projected from top face of a substantially disc-shaped main body of the rotor to be located in the pump chamber; and a magnet section projected from back face of the main body to be located in the motor chamber and having a substantially cylindrical shape.
- the rotor is located in the fluid and driven by a rotating magnetic field generated by a stator located inward of the magnet section in the motor chamber.
- a cavity is located along an inner circumference of the stator so as to communicate with passages of fluid along an inner circumference of the magnet section and the back face of the main body of the magnet section.
- fluid flows into the cavity located inward of the stator from fluid passages along the inner circumference of the magnet section and the back face of the main body of the rotor, and the inner circumferential part of the stator is cooled down by this fluid.
- the magnetic coupling pump of the present invention is able to prevent heat -up of the inner circumferential part of the stator and burnout of coils of the stator, whereby becomes durable even under high-load driving which consumes a lot of electricity.
- the fluid in the cavity is able to flow into the pump chamber via the through holes of the rotor main body. That is, the fluid forms a cooling stream for cooling the stator that flows from the outer circumferential side to the inner circumferential side of the stator, and further flows from the inner circumferential side of the stator to the pump chamber. Therefore, heat-up of the inner circumferential part of the stator is further prevented, and in addition, heat-up of the outer circumferential side of the stator is properly prevented, too. Consequently, burnout of the coils of the stator and heat deformation of the housing are properly prevented, which further elongates a life span of the pump even under high-load driving which consumes a lot of electricity.
- the shaft section is desirably provided in its outer circumference with a plurality of impellers for stirring the fluid.
- the impellers are able to stir the fluid in the cavity when the rotor is driving, and therefore, entire area of the inner part of the stator is cooled down quickly and properly.
- the shaft section internally includes a passage with apertures opening in the cavity and in a top face side of the main body, such that the fluid in the cavity circulates to the top face side of the main body through the passage.
- the fluid in the cavity is able to flows out toward the top face side of the rotor main body or into the pump chamber via the passage of the shaft section.
- the fluid in a bottom part of the cavity is also able to circulate to the pump chamber via the passage. Therefore, cooling-down effect of the inner circumferential part of the stator is enhanced.
- FIG. 1 is a vertical section of an embodiment of the magnetic coupling pump according to the present invention.
- FIG. 2 is a vertical section of the rotor of the pump of FIG. 1;
- FIG. 3 is a transverse section of the rotor of FIG. 2 taken along line III-III of FIG. 2;
- FIG. 4 is a vertical section of another embodiment of the magnetic coupling pump according to the present invention.
- FIGS. 1 to 3 illustrate an embodiment P 1 of the magnetic coupling pump according to the present invention for feeding engine coolant W for vehicles.
- the pump P 1 includes a housing 1 which is made from synthetic resin and has therein a rotor 15 with a plurality of impellers 17 for feeding the coolant W.
- the housing 1 includes a pump chamber 2 in which the impellers 17 of the rotor 15 are located, and a motor chamber 6 located below the pump chamber 2 .
- the pump chamber 2 has a ceiling wall 2 a and has a substantially cylindrical shape.
- An inlet pipe 3 for introducing the coolant W projects upward from the ceiling wall 2 a
- an outlet pipe 4 for exhausting the coolant W projects outwardly from a circumferential wall 2 b.
- the motor chamber 6 includes a circumferential wall 7 having a substantially cylindrical shape, a bottom wall 8 extending from a lower inner part of the circumferential wall 7 , and a stator section 9 protruding upward from the bottom wall 8 .
- the stator section 9 is provided along its inner circumference with a cavity 11 to which the coolant W is admissible, and has a substantially cylindrical shape as a whole.
- the stator section 9 includes therein a stator 10 wound by coils 10 a for generating a rotating magnetic field when electrified.
- a member designated by a reference numeral 12 is a circuit board for rotating the rotor 15 on which power transistors for driving the stator 10 , and a Hall element for detecting rotation angle of the stator 10 , and so on are located.
- a member designated by a reference numeral 13 is a terminal for supplying electricity to the circuit board 12 .
- the rotor 15 includes a main body 16 having a substantially disc shape and a magnet section 18 .
- the main body 16 has impellers 17 projected upward from its top face 16 a .
- the magnet section 18 has a substantially cylindrical shape, and extends downward from the vicinity of the outer edge of the main body 16 , or from a back face 16 a of the main body 16 to be located between an outer circumference of the stator 10 and an inner circumference of the circumferential wall 7 .
- the magnet section 18 is driven and rotates by the rotating magnetic field generated by the stator 10 .
- the magnet section 18 is made from a material made by mixing magnetic powder into synthetic resin material such as polyamide that forms the rotor 15 except later-described shaft 20 and bearings 25 .
- the main body 16 is provided near the inner circumference of the stator 10 with a plurality of through holes 16 c through from the top to the back.
- a shaft section 19 Located vertically in the center of the main body 16 is a shaft section 19 , which includes a shaft 20 and a sliding boss section 26 .
- the shaft 20 is made of metal pipe, and penetrates the base 16 .
- a lower end 20 b of the shaft 20 is fixed to the center of the bottom wall 8 of the motor chamber 6 in the housing 1 .
- This pipe-shaped shaft 20 is open at its upper end, and is provided in a part submerged in the coolant W near the lower end 20 b , or in a part near a bottom 11 a of the cavity 11 with a plurality of holes 22 communicating in and outsides of the shaft 20 .
- These holes 22 serve as inlet ports for inletting the coolant W such that the coolant W flows through an inner passage 21 of the shaft 20 and flows out of the upper end of the shaft 20 serving as an outlet port 23 .
- the sliding boss section 26 has a cylindrical shape, and is integrally formed with the main body 16 in the center of the main body 16 .
- Bearings 25 are fixed to upper and lower parts of an inner circumference of the sliding boss section 26 such that the shaft 20 rotatably supports the sliding boss section 26 .
- the bearings 25 are made of resin or metal capable of reducing friction force.
- An E-ring 24 is located proximate to the top end 20 a of the shaft 20 to prevent the sliding boss section 26 from coming off from the shaft 20 .
- the E-ring 24 is required since the rotor 15 is prone to float up when rotating because of negative pressure generated near the inlet pipe 3 .
- the rotor 15 rotates at 3000 to 3800 rpm.
- the rotor 15 is submerged in the coolant W except the lower end 20 b of the shaft 20 fixed to the housing 1 .
- the sliding boss section 26 which is located in the cavity 11 or inward of the stator section 9 , is provided on the outer circumference in its lower part with a plurality of stirring impellers 27 for stirring the coolant W in the cavity 11 .
- the coolant W flows into the cavity 11 positioned inward of the stator 10 from fluid passages along the inner circumference 18 a of the magnet section 18 and the back face 16 b of the main body 16 of the rotor 15 , whereby the inner side of the stator 10 is cooled down.
- the magnetic coupling pump P 1 is able to prevent heat-up of an inner circumferential part of the stator 10 and burnout of the coils 10 a of the stator 10 , where by becomes durable even under high-load driving which consumes a lot of electricity.
- the through holes 16 c pierced through vertically are located near the inner circumference of the stator 10 of the main body 16 .
- the coolant W in the cavity 11 flows toward the pump chamber 2 via the through holes 16 c of the main body 16 .
- the coolant W forms a cooling stream F 0 for the stator 10 that flows from the outer circumferential side to the inner circumferential side of the stator 10 , and further flows from the inner circumferential side of the stator 10 to the pump chamber 2 .
- the rotor 15 includes the shaft section 19 projecting into the cavity 11 , and the sliding boss section 26 of the shaft section 19 is provided on its outer circumference with the stirring impellers 27 for stirring the coolant W. Accordingly, the impellers 27 are able to stir the coolant W in the cavity 11 when the rotor 15 is driving, and therefore, entire area of the inner part of the stator 10 is cooled down quickly and properly.
- the rotor 15 includes the shaft section 19 projecting into the cavity 11 , and the shaft 20 of the shaft section 19 internally has the passage 21 provided with apertures open into the bottom part 11 a of the cavity 11 and in the surface 16 a of the main body 16 such that the coolant W in the bottom part 11 a of the cavity 11 circulates to the pump chamber 2 above the rotor main body 16 .
- the coolant W in the bottom part 11 a of the cavity 11 flows into the passage 21 of the shaft 20 from the inlet ports 22 , and then flows out of the outlet port 23 or the top end 20 a of the shaft 20 into the pump chamber 2 above the main body 16 , via the passage 21 . That is, the coolant W forms a cooling stream F 1 for the stator 10 that flows from the outer circumferential side to the inner circumferential side of the stator 10 , and flows from a bottom part of the inner circumferential side of the stator 10 to the pump chamber 2 via the passage 21 .
- cooling-down effect of the inner part of the stator 10 is enhanced.
- the rotor 15 when rotating, is supported by two bearings 25 which are located near the upper and lower end of the rotor 15 , i.e., at a position near the main body 16 and a position in the cavity 11 . Therefore, the rotation of the rotor 15 is stabilized, which reduces the loss of the rotation moment of the rotor 15 .
- the shaft section 19 of the rotor 15 having the sliding boss section 26 with the stirring impellers 27
- the shaft section does not necessarily have to be provided with the impellers 27 .
- the magnetic coupling pump may include a shaft section 19 A which has a sliding boss section 26 with the stirring impellers 27 and a shaft 20 A without the passage 21 , as in a magnetic coupling pump P 2 shown in FIG. 4.
- the rotor 15 may include no through holes 16 c.
Abstract
A magnetic coupling pump according to the present invention has a housing including a pump chamber a motor chamber. The rotor includes a plurality of impellers projected from top face of a substantially disc-shaped main body of the rotor to be located in the pump chamber, and a substantially cylindrical magnet section projected from back face of the main body to be located in the motor chamber. The rotor is located in engine coolant, and is driven by a stator located inward of the magnet section in the motor chamber for sucking coolant from an inlet port and exhausting it from an outlet port. The pump is provided along an inner circumference of the stator with a cavity communicating with passages of fluid along an inner circumference of the magnet section and the back face of the main body of the magnet section. The cavity admits the coolant. The pump according to the present invention is able to prevent heat-up in the inner circumferential part of the stator.
Description
- The present application claims priority from Japanese Patent Application No. 2003-142389 of Hatano, filed on May 20, 2003, the entirety of which is hereby incorporated into the present application by reference.
- 1. Field of the Invention
- The present invention relates to a magnetic coupling pump for pumping fluids such as engine coolant for vehicles, and more particularly, relates to an outer-rotor type magnetic coupling pump in which a stator is located toward a rotation center of a rotor having impellers for feeding fluids, and a substantially cylindrical magnet section of the rotor is located around the stator.
- 2. Description of the Related Art
- In conventional outer-rotor type magnetic coupling pumps for engine coolant for vehicles, a rotor having impellers for feeding coolant is located in a housing, as disclosed in Japanese Laid Open Patent Application No. JP10-311290.
- In this magnetic coupling pump, the housing includes a pump chamber having inlet port and outlet port of coolant, and a motor chamber. The rotor includes impellers which are projected from top face of a disc-shaped body of the rotor to be located in the pump chamber, and a substantially cylindrical magnet section which is projected from back face of the rotor body to be located in the motor chamber. This rotor is located in the coolant, and is driven to rotate by rotating magnetic field generated by a stator located inward of the magnet section in the motor chamber to suck the coolant from the inlet port and exhaust it from the outlet port.
- In the conventional outer-rotor type magnetic coupling pump, however, there is no means of cooling down a part inward of the stator though the outer circumference of the stator can be cooled down by coolant interposed between the stator and the magnet section. Accordingly, heat-up of the stator and burnout of coils of the stator caused by the former has been a concern in a high-load driving condition using a lot of electricity.
- The present invention contemplates to solve the above mentioned problem, and therefore, has an object to provide a magnetic coupling pump capable of preventing heat-up of an inner circumferential part of the stator.
- A magnetic coupling pump according to the present invention is to suck fluid from an inlet port and exhaust the fluid from an outlet port, and includes a housing and a rotor. The housing includes a pump chamber having the inlet and outlet ports of fluid and a motor chamber. The rotor includes: a plurality of impellers projected from top face of a substantially disc-shaped main body of the rotor to be located in the pump chamber; and a magnet section projected from back face of the main body to be located in the motor chamber and having a substantially cylindrical shape. The rotor is located in the fluid and driven by a rotating magnetic field generated by a stator located inward of the magnet section in the motor chamber. A cavity is located along an inner circumference of the stator so as to communicate with passages of fluid along an inner circumference of the magnet section and the back face of the main body of the magnet section.
- In the magnetic coupling pump according to the present invention, fluid flows into the cavity located inward of the stator from fluid passages along the inner circumference of the magnet section and the back face of the main body of the rotor, and the inner circumferential part of the stator is cooled down by this fluid.
- Therefore, the magnetic coupling pump of the present invention is able to prevent heat -up of the inner circumferential part of the stator and burnout of coils of the stator, whereby becomes durable even under high-load driving which consumes a lot of electricity.
- If the main body of the rotor is provided in the vicinity of an inner circumferential part of the stator with a plurality of through holes, the fluid in the cavity is able to flow into the pump chamber via the through holes of the rotor main body. That is, the fluid forms a cooling stream for cooling the stator that flows from the outer circumferential side to the inner circumferential side of the stator, and further flows from the inner circumferential side of the stator to the pump chamber. Therefore, heat-up of the inner circumferential part of the stator is further prevented, and in addition, heat-up of the outer circumferential side of the stator is properly prevented, too. Consequently, burnout of the coils of the stator and heat deformation of the housing are properly prevented, which further elongates a life span of the pump even under high-load driving which consumes a lot of electricity.
- When the rotor includes a shaft section projecting into the cavity, the shaft section is desirably provided in its outer circumference with a plurality of impellers for stirring the fluid. With this arrangement, the impellers are able to stir the fluid in the cavity when the rotor is driving, and therefore, entire area of the inner part of the stator is cooled down quickly and properly.
- When the rotor includes a shaft section projecting into the cavity, moreover, it will also be appreciated that the shaft section internally includes a passage with apertures opening in the cavity and in a top face side of the main body, such that the fluid in the cavity circulates to the top face side of the main body through the passage. With this arrangement, the fluid in the cavity is able to flows out toward the top face side of the rotor main body or into the pump chamber via the passage of the shaft section. Especially, the fluid in a bottom part of the cavity is also able to circulate to the pump chamber via the passage. Therefore, cooling-down effect of the inner circumferential part of the stator is enhanced.
- Furthermore, if the rotor is rotatably supported at two positions of a position proximate to the main body and at a position in the cavity, the rotation of the rotor is stabilized, which reduces the loss of rotation moment of the rotor.
- FIG. 1 is a vertical section of an embodiment of the magnetic coupling pump according to the present invention;
- FIG. 2 is a vertical section of the rotor of the pump of FIG. 1;
- FIG. 3 is a transverse section of the rotor of FIG. 2 taken along line III-III of FIG. 2; and
- FIG. 4 is a vertical section of another embodiment of the magnetic coupling pump according to the present invention.
- Preferred embodiments of the present invention are now described below with reference to the accompanying drawings. However, the invention is not limited to the embodiments disclosed herein. All modifications within the appended claims and equivalents relative thereto are intended to be encompassed in the scope of the claims.
- FIGS.1 to 3 illustrate an embodiment P1 of the magnetic coupling pump according to the present invention for feeding engine coolant W for vehicles. The pump P1 includes a
housing 1 which is made from synthetic resin and has therein arotor 15 with a plurality ofimpellers 17 for feeding the coolant W. - The
housing 1 includes apump chamber 2 in which theimpellers 17 of therotor 15 are located, and amotor chamber 6 located below thepump chamber 2. Thepump chamber 2 has aceiling wall 2 a and has a substantially cylindrical shape. Aninlet pipe 3 for introducing the coolant W projects upward from theceiling wall 2 a, and anoutlet pipe 4 for exhausting the coolant W projects outwardly from acircumferential wall 2 b. - The
motor chamber 6 includes acircumferential wall 7 having a substantially cylindrical shape, abottom wall 8 extending from a lower inner part of thecircumferential wall 7, and astator section 9 protruding upward from thebottom wall 8. - The
stator section 9 is provided along its inner circumference with acavity 11 to which the coolant W is admissible, and has a substantially cylindrical shape as a whole. Thestator section 9 includes therein astator 10 wound bycoils 10 a for generating a rotating magnetic field when electrified. A member designated by areference numeral 12 is a circuit board for rotating therotor 15 on which power transistors for driving thestator 10, and a Hall element for detecting rotation angle of thestator 10, and so on are located. A member designated by areference numeral 13 is a terminal for supplying electricity to thecircuit board 12. - The
rotor 15 includes amain body 16 having a substantially disc shape and amagnet section 18. Themain body 16 hasimpellers 17 projected upward from itstop face 16 a. Themagnet section 18 has a substantially cylindrical shape, and extends downward from the vicinity of the outer edge of themain body 16, or from aback face 16 a of themain body 16 to be located between an outer circumference of thestator 10 and an inner circumference of thecircumferential wall 7. Themagnet section 18 is driven and rotates by the rotating magnetic field generated by thestator 10. In the foregoing embodiment, themagnet section 18 is made from a material made by mixing magnetic powder into synthetic resin material such as polyamide that forms therotor 15 except later-describedshaft 20 andbearings 25. - The
main body 16 is provided near the inner circumference of thestator 10 with a plurality of throughholes 16 c through from the top to the back. Located vertically in the center of themain body 16 is ashaft section 19, which includes ashaft 20 and asliding boss section 26. Theshaft 20 is made of metal pipe, and penetrates thebase 16. Alower end 20 b of theshaft 20 is fixed to the center of thebottom wall 8 of themotor chamber 6 in thehousing 1. This pipe-shaped shaft 20 is open at its upper end, and is provided in a part submerged in the coolant W near thelower end 20 b, or in a part near abottom 11 a of thecavity 11 with a plurality ofholes 22 communicating in and outsides of theshaft 20. Theseholes 22 serve as inlet ports for inletting the coolant W such that the coolant W flows through aninner passage 21 of theshaft 20 and flows out of the upper end of theshaft 20 serving as anoutlet port 23. - The
sliding boss section 26 has a cylindrical shape, and is integrally formed with themain body 16 in the center of themain body 16.Bearings 25 are fixed to upper and lower parts of an inner circumference of the slidingboss section 26 such that theshaft 20 rotatably supports the slidingboss section 26. Thebearings 25 are made of resin or metal capable of reducing friction force. An E-ring 24 is located proximate to thetop end 20 a of theshaft 20 to prevent the slidingboss section 26 from coming off from theshaft 20. - The E-ring24 is required since the
rotor 15 is prone to float up when rotating because of negative pressure generated near theinlet pipe 3. When the pump P1 is in service, therotor 15 rotates at 3000 to 3800 rpm. - The
rotor 15 is submerged in the coolant W except thelower end 20 b of theshaft 20 fixed to thehousing 1. The slidingboss section 26, which is located in thecavity 11 or inward of thestator section 9, is provided on the outer circumference in its lower part with a plurality of stirringimpellers 27 for stirring the coolant W in thecavity 11. - In the magnetic coupling pump P1, the coolant W flows into the
cavity 11 positioned inward of thestator 10 from fluid passages along theinner circumference 18 a of themagnet section 18 and theback face 16 b of themain body 16 of therotor 15, whereby the inner side of thestator 10 is cooled down. - Therefore, the magnetic coupling pump P1 is able to prevent heat-up of an inner circumferential part of the
stator 10 and burnout of thecoils 10 a of thestator 10, where by becomes durable even under high-load driving which consumes a lot of electricity. - In the preferred embodiment, the through
holes 16 c pierced through vertically are located near the inner circumference of thestator 10 of themain body 16. When therotor 15 is driven and rotates, negative pressure occurs toward theinlet pipe 3, and the coolant W in thecavity 11 flows toward thepump chamber 2 via the throughholes 16 c of themain body 16. In other words, the coolant W forms a cooling stream F0 for thestator 10 that flows from the outer circumferential side to the inner circumferential side of thestator 10, and further flows from the inner circumferential side of thestator 10 to thepump chamber 2. Therefore, heat-up of the inner circumferential part of thestator 10 is further prevented, and in addition, heat-up of the outer circumferential side of thestator 10 is properly prevented. Consequently, burnout of thecoils 10 a of thestator 10 and heat deformation of thestator section 9 in thehousing 1 are properly prevented, which further elongates a life span of the pump P1 even under high-load driving which consumes a lot of electricity. - In the preferred embodiment, moreover, the
rotor 15 includes theshaft section 19 projecting into thecavity 11, and the slidingboss section 26 of theshaft section 19 is provided on its outer circumference with the stirringimpellers 27 for stirring the coolant W. Accordingly, theimpellers 27 are able to stir the coolant W in thecavity 11 when therotor 15 is driving, and therefore, entire area of the inner part of thestator 10 is cooled down quickly and properly. - Furthermore, the
rotor 15 includes theshaft section 19 projecting into thecavity 11, and theshaft 20 of theshaft section 19 internally has thepassage 21 provided with apertures open into thebottom part 11 a of thecavity 11 and in thesurface 16 a of themain body 16 such that the coolant W in thebottom part 11 a of thecavity 11 circulates to thepump chamber 2 above the rotormain body 16. When therotor 15 is driven and rotates, negative pressure occurs toward theinlet pipe 3, and the coolant W in thebottom part 11 a of thecavity 11 flows into thepassage 21 of theshaft 20 from theinlet ports 22, and then flows out of theoutlet port 23 or thetop end 20 a of theshaft 20 into thepump chamber 2 above themain body 16, via thepassage 21. That is, the coolant W forms a cooling stream F1 for thestator 10 that flows from the outer circumferential side to the inner circumferential side of thestator 10, and flows from a bottom part of the inner circumferential side of thestator 10 to thepump chamber 2 via thepassage 21. Thus, cooling-down effect of the inner part of thestator 10 is enhanced. - In addition, in the magnetic coupling pump P1, the
rotor 15, when rotating, is supported by twobearings 25 which are located near the upper and lower end of therotor 15, i.e., at a position near themain body 16 and a position in thecavity 11. Therefore, the rotation of therotor 15 is stabilized, which reduces the loss of the rotation moment of therotor 15. - Although the preferred embodiment shows the
shaft section 19 of therotor 15 having the slidingboss section 26 with the stirringimpellers 27, the shaft section does not necessarily have to be provided with theimpellers 27. - Although preferred embodiment shows the
shaft section 19 of therotor 15 having the pipe-shapedshaft 20 which serves as thefluid passage 21, the magnetic coupling pump may include ashaft section 19A which has a slidingboss section 26 with the stirringimpellers 27 and ashaft 20A without thepassage 21, as in a magnetic coupling pump P2 shown in FIG. 4. - Although the preferred embodiment shows the
main body 16 of therotor 15 with a plurality of thoughholes 16 c through from top to bottom, therotor 15 may include no throughholes 16 c.
Claims (11)
1. A magnetic coupling pump for sucking fluid from an inlet port and exhausting the fluid from an outlet port, the pump comprising a housing and a rotor,
the housing including a pump chamber having the inlet and outlet ports of fluid and a motor chamber,
the rotor including:
a plurality of impellers projected from top face of a substantially disc-shaped main body of the rotor to be located in the pump chamber; and
a magnet section projected from back face of the main body to be located in the motor chamber, the magnet section having a substantially cylindrical shape,
the rotor being located in the fluid and driven by a rotating magnetic field generated by a stator located inward of the magnet section in the motor chamber, wherein
a cavity is located along an inner circumference of the stator, the cavity communicating with passages of fluid along an inner circumference of the magnet section and the back face of the main body of the magnet section.
2. The magnetic coupling pump according to claim 1 , wherein:
the main body of the rotor includes a plurality of through holes in the vicinity of an inner circumferential part of the stator, the through holes being through from the top face to the back of the main body.
3. The magnetic coupling pump according to claim 1 , wherein:
the rotor includes a shaft section projecting into the cavity; and
the shaft section is provided in the outer circumference thereof with a plurality of impellers for stirring the fluid.
4. The magnetic coupling pump according to claim 2 , wherein:
the rotor includes a shaft section projecting into the cavity; and
the shaft section is provided in the outer circumference thereof with a plurality of impellers for stirring the fluid.
5. The magnetic coupling pump according to claim 1 , wherein:
the rotor includes a shaft section projecting into the cavity; and
the shaft section internally includes a passage with apertures opening in the cavity and in a top face of the main body,
whereby the fluid in the cavity circulates to the top face side of the main body through the passage.
6. The magnetic coupling pump according to claim 2 , wherein:
the rotor includes a shaft section projecting into the cavity; and
the shaft section internally includes a passage with apertures opening in the cavity and in a top face of the main body,
whereby the fluid in the cavity circulates to the top face side of the main body through the passage.
7. The magnetic coupling pump according to claim 3 , wherein:
the shaft section internally includes a passage with apertures opening in the cavity and in a top face of the main body,
whereby the fluid in the cavity circulates to the top face side of the main body through the passage.
8. The magnetic coupling pump according to claim 1 , wherein the rotor is rotatably supported at two positions of a position proximate to the main body and at a position in the cavity.
9. The magnetic coupling pump according to claim 2 , wherein the rotor is rotatably supported at two positions of a position proximate to the main body and at a position in the cavity.
10. The magnetic coupling pump according to claim 3 , wherein the rotor is rotatably supported at two positions of a position proximate to the main body and at a position in the cavity.
11. The magnetic coupling pump according to claim 4 , wherein the rotor is rotatably supported at two positions of a position proximate to the main body and at a position in the cavity.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003142389A JP2004346774A (en) | 2003-05-20 | 2003-05-20 | Magnetic coupling pump |
JP2003-142389 | 2003-05-20 |
Publications (1)
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US20040234395A1 true US20040234395A1 (en) | 2004-11-25 |
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US10/838,197 Abandoned US20040234395A1 (en) | 2003-05-20 | 2004-05-05 | Magnetic coupling pump |
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JP (1) | JP2004346774A (en) |
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US20070159020A1 (en) * | 2006-01-11 | 2007-07-12 | Delta Electronics, Inc. | Water pump and bearing thereof |
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US20080073990A1 (en) * | 2006-09-26 | 2008-03-27 | Chi-Der Chen | Bi-directional reversible submersible motor |
US20080112824A1 (en) * | 2006-11-09 | 2008-05-15 | Nidec Shibaura Corporation | Pump |
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US20100158714A1 (en) * | 2008-12-19 | 2010-06-24 | Michael John Werson | Rotary pump with a fixed shaft |
US20100158703A1 (en) * | 2008-12-22 | 2010-06-24 | Aisin Seiki Kabushiki Kaisha | Electric fluid pump and mold for insert-molding casing of electric fluid pump |
US20110052432A1 (en) * | 2008-05-06 | 2011-03-03 | Cunningham Christopher E | Pump with magnetic bearings |
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US8905729B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with electro-magnet coupling inside the impeller |
US8905728B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with permanent magnet coupling inside the impeller |
AU2014240249B1 (en) * | 2014-10-02 | 2015-04-23 | Zenin, Vladimir Mr | Magnet engine |
CN105090096A (en) * | 2014-05-21 | 2015-11-25 | 上海佰诺泵阀有限公司 | Magnetic force peripheral pump |
WO2016008407A1 (en) * | 2014-07-16 | 2016-01-21 | 苏州泰格动力机器有限公司 | Magnetic drive pump |
CN105370584A (en) * | 2014-08-15 | 2016-03-02 | 广东德昌电机有限公司 | Electric pump |
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US20160146219A1 (en) * | 2014-10-27 | 2016-05-26 | Coolit Systems, Inc. | Fluid heat exchange systems |
CN105782063A (en) * | 2014-12-22 | 2016-07-20 | 杭州三花研究院有限公司 | Electrically-driven pump |
US20160290364A1 (en) * | 2015-04-02 | 2016-10-06 | Hyundai Motor Company | Electric water pump |
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US20180229825A1 (en) * | 2014-05-01 | 2018-08-16 | Blue Robotics Inc. | Submersible electric thruster |
IT201700018662A1 (en) * | 2017-02-20 | 2018-08-20 | Baruffaldi Spa | RECIRCULATION PUMP OF A THERMAL MOTOR FLUID WITH ELECTRIC MOTOR CONTROL |
IT201900000615A1 (en) * | 2019-01-15 | 2020-07-15 | Baruffaldi Spa | RECIRCULATION PUMP OF A COOLING FLUID OF THERMAL ENGINES WITH ELECTRIC MOTOR CONTROL |
IT201900001481A1 (en) | 2019-02-01 | 2020-08-01 | Baruffaldi Spa | RECIRCULATION PUMP OF A COOLING FLUID OF THERMAL ENGINES WITH ELECTRIC MOTOR CONTROL |
IT201900002313A1 (en) | 2019-02-18 | 2020-08-18 | Baruffaldi Spa | RECIRCULATION PUMP OF A COOLING FLUID OF THERMAL ENGINES WITH ELECTRIC MOTOR CONTROL |
CN112534141A (en) * | 2018-10-10 | 2021-03-19 | 海拉有限双合股份公司 | Pump, in particular for a liquid circuit in a vehicle |
US11092159B2 (en) * | 2017-11-22 | 2021-08-17 | Nidec Gpm Gmbh | Coolant pump having a use-optimised structure and improved thermal efficiency |
US11125244B2 (en) * | 2017-08-31 | 2021-09-21 | Nidec Gpm Gmbh | Coolant pump with application-optimised design |
CN113494464A (en) * | 2021-08-13 | 2021-10-12 | 宁德时代电机科技有限公司 | High-efficiency water-cooling axial magnetic field permanent magnet intelligent water pump with integrated control device |
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US3220350A (en) * | 1964-09-03 | 1965-11-30 | Crane Co | Motor driven pump |
US4013384A (en) * | 1974-07-18 | 1977-03-22 | Iwaki Co., Ltd. | Magnetically driven centrifugal pump and means providing cooling fluid flow |
US4047847A (en) * | 1975-03-26 | 1977-09-13 | Iwaki Co., Ltd. | Magnetically driven centrifugal pump |
US20010033800A1 (en) * | 2000-04-25 | 2001-10-25 | Aisan Kogyo Kabushiki Kaisha | Magnetic coupling pump |
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US20070159020A1 (en) * | 2006-01-11 | 2007-07-12 | Delta Electronics, Inc. | Water pump and bearing thereof |
US20070177993A1 (en) * | 2006-01-31 | 2007-08-02 | Asian Kogyo Kabushiki Kaisha | Electric pump |
US20070188029A1 (en) * | 2006-02-16 | 2007-08-16 | Nidec Sankyo Corporation | Pump and pumping system |
US20070252458A1 (en) * | 2006-04-27 | 2007-11-01 | Chi-Der Chen | Reversible submerged motor |
US7535138B2 (en) * | 2006-04-27 | 2009-05-19 | Chi-Der Chin | Reversible submerged motor |
WO2008014556A1 (en) * | 2006-08-03 | 2008-02-07 | Richard David Davies | Electric pump-motor design |
US20080073990A1 (en) * | 2006-09-26 | 2008-03-27 | Chi-Der Chen | Bi-directional reversible submersible motor |
US7535139B2 (en) * | 2006-09-26 | 2009-05-19 | Chi-Der Chen | Bi-directional reversible submersible motor |
US20080112824A1 (en) * | 2006-11-09 | 2008-05-15 | Nidec Shibaura Corporation | Pump |
EP2072825A3 (en) * | 2007-12-21 | 2012-03-28 | Geräte- und Pumpenbau GmbH Merbelsrod | Coolant pump |
US20110058966A1 (en) * | 2008-05-05 | 2011-03-10 | Cunningham Christopher E | Flushing system |
US8696331B2 (en) | 2008-05-06 | 2014-04-15 | Fmc Technologies, Inc. | Pump with magnetic bearings |
US20110044831A1 (en) * | 2008-05-06 | 2011-02-24 | Christopher E Cunningham | Motor with high pressure rated can |
US9601964B2 (en) | 2008-05-06 | 2017-03-21 | Fmc Technologies, Inc. | In-line flow mixer |
US20110058965A1 (en) * | 2008-05-06 | 2011-03-10 | Cunningham Christopher E | In-line flow mixer |
AU2009244519B2 (en) * | 2008-05-06 | 2014-04-03 | Fmc Technologies, Inc. | Flushing system |
US20110052432A1 (en) * | 2008-05-06 | 2011-03-03 | Cunningham Christopher E | Pump with magnetic bearings |
WO2009137323A1 (en) * | 2008-05-06 | 2009-11-12 | Fmc Technologies, Inc. | Flushing system |
US8777596B2 (en) | 2008-05-06 | 2014-07-15 | Fmc Technologies, Inc. | Flushing system |
US20100158714A1 (en) * | 2008-12-19 | 2010-06-24 | Michael John Werson | Rotary pump with a fixed shaft |
US8353687B2 (en) * | 2008-12-19 | 2013-01-15 | Dohler Motor GmbH | Rotary pump with a fixed shaft |
US20100158703A1 (en) * | 2008-12-22 | 2010-06-24 | Aisin Seiki Kabushiki Kaisha | Electric fluid pump and mold for insert-molding casing of electric fluid pump |
US8911220B2 (en) * | 2008-12-22 | 2014-12-16 | Aisin Seiki Kabushiki Kaisha | Electric fluid pump and mold for insert-molding casing of electric fluid pump |
US8905728B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with permanent magnet coupling inside the impeller |
US8905729B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with electro-magnet coupling inside the impeller |
WO2014139520A1 (en) * | 2013-03-13 | 2014-09-18 | Bühler Motor GmbH | Centrifugal pump |
CN103790835A (en) * | 2014-01-14 | 2014-05-14 | 苏州泰格动力机器有限公司 | Integrated water-jacketed permanent magnet motor water pump |
US11440633B2 (en) | 2014-05-01 | 2022-09-13 | Blue Robotics Inc. | Electrically-powered unmanned marine vehicle and method of making same |
US20180229825A1 (en) * | 2014-05-01 | 2018-08-16 | Blue Robotics Inc. | Submersible electric thruster |
CN105090096A (en) * | 2014-05-21 | 2015-11-25 | 上海佰诺泵阀有限公司 | Magnetic force peripheral pump |
WO2016008407A1 (en) * | 2014-07-16 | 2016-01-21 | 苏州泰格动力机器有限公司 | Magnetic drive pump |
CN105370584A (en) * | 2014-08-15 | 2016-03-02 | 广东德昌电机有限公司 | Electric pump |
AU2014240249B1 (en) * | 2014-10-02 | 2015-04-23 | Zenin, Vladimir Mr | Magnet engine |
EP3012457A1 (en) * | 2014-10-21 | 2016-04-27 | Pierburg Pump Technology GmbH | Electric motor vehicle coolant pump |
US20160146219A1 (en) * | 2014-10-27 | 2016-05-26 | Coolit Systems, Inc. | Fluid heat exchange systems |
US10415597B2 (en) * | 2014-10-27 | 2019-09-17 | Coolit Systems, Inc. | Fluid heat exchange systems |
CN105782063A (en) * | 2014-12-22 | 2016-07-20 | 杭州三花研究院有限公司 | Electrically-driven pump |
CN106151055A (en) * | 2015-03-26 | 2016-11-23 | 杭州三花研究院有限公司 | Electric drive pump |
US20160290364A1 (en) * | 2015-04-02 | 2016-10-06 | Hyundai Motor Company | Electric water pump |
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CN110325742A (en) * | 2017-02-20 | 2019-10-11 | 巴鲁法蒂股份公司 | It is with electric notor control device, for so that the pump that the cooling fluid of combustion engine recycles |
US11125244B2 (en) * | 2017-08-31 | 2021-09-21 | Nidec Gpm Gmbh | Coolant pump with application-optimised design |
US11092159B2 (en) * | 2017-11-22 | 2021-08-17 | Nidec Gpm Gmbh | Coolant pump having a use-optimised structure and improved thermal efficiency |
CN112534141A (en) * | 2018-10-10 | 2021-03-19 | 海拉有限双合股份公司 | Pump, in particular for a liquid circuit in a vehicle |
US11767858B2 (en) * | 2018-10-10 | 2023-09-26 | HELLA GmbH & Co. KGaA | Pump, in particular for a fluid circuit in a vehicle |
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Legal Events
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AS | Assignment |
Owner name: AISAN KOGYO KABUSHIKI KAISHA S, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HATANO, MAKOTO;REEL/FRAME:015297/0845 Effective date: 20040420 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |