CN111162634A - Drum type permanent magnet governor - Google Patents
Drum type permanent magnet governor Download PDFInfo
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- CN111162634A CN111162634A CN202010118837.1A CN202010118837A CN111162634A CN 111162634 A CN111162634 A CN 111162634A CN 202010118837 A CN202010118837 A CN 202010118837A CN 111162634 A CN111162634 A CN 111162634A
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- permanent magnet
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K9/00—Arrangements for cooling or ventilating
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
- H02K49/10—Dynamo-electric clutches; Dynamo-electric brakes of the permanent-magnet type
- H02K49/102—Magnetic gearings, i.e. assembly of gears, linear or rotary, by which motion is magnetically transferred without physical contact
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
- H02K49/10—Dynamo-electric clutches; Dynamo-electric brakes of the permanent-magnet type
- H02K49/104—Magnetic couplings consisting of only two coaxial rotary elements, i.e. the driving element and the driven element
- H02K49/106—Magnetic couplings consisting of only two coaxial rotary elements, i.e. the driving element and the driven element with a radial air gap
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K9/00—Arrangements for cooling or ventilating
- H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
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- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Motor Or Generator Cooling System (AREA)
Abstract
本发明涉及一种筒式永磁调速器，包括基座、外转子及内转子，基座设有冷却液喷液结构；外转子安装于基座上并可以第一轴线为中心转动，外转子设有容置腔；内转子安装于基座上并可以第一轴线为中心转动，内转子的径向外周面与容置腔的径向内周面间隔配合形成气隙；沿第一轴线方向，内转子具有相对的第一端部和第二端部，第一端部设有与冷却液喷液结构对应的径向导流扩散部；所述径向导流扩散部用于引导冷却液向远离第一轴线的方向扩散流动；如此既能降低冷却液溅离内转子的比例，又能增大冷却液与内转子的接触面积，进而可改善了冷却液以柱状喷向内转子时，冷却液溅离内转子，导致筒式永磁调速器散热效果不佳的问题。
The invention relates to a cylindrical permanent magnet speed governor, comprising a base, an outer rotor and an inner rotor, the base is provided with a cooling liquid spray structure; the outer rotor is mounted on the base and can rotate around a first axis, and the outer rotor The rotor is provided with an accommodating cavity; the inner rotor is installed on the base and can rotate around the first axis, and the radial outer peripheral surface of the inner rotor and the radial inner peripheral surface of the accommodating cavity are spaced to form an air gap; along the first axis The inner rotor has an opposite first end and a second end, and the first end is provided with a radial diversion and diffusion part corresponding to the cooling liquid spray structure; the radial diversion and diffusion part is used to guide the cooling liquid to the Diffusion flow in the direction away from the first axis; this can not only reduce the proportion of the cooling liquid splashing off the inner rotor, but also increase the contact area between the cooling liquid and the inner rotor, thereby improving the cooling effect when the cooling liquid is sprayed to the inner rotor in a columnar shape. The liquid splashes away from the inner rotor, which leads to the problem of poor heat dissipation of the barrel type permanent magnet governor.
Description
Technical Field
The invention relates to the technical field of permanent magnet speed regulation, in particular to a cylindrical permanent magnet speed regulator.
Background
The cylinder type permanent magnet speed regulator is a transmission device for transmitting torque through an air gap, and the existing cylinder type permanent magnet speed regulator mainly comprises an induction rotor and a permanent magnet rotor. The induction rotor is fixed on the driving shaft and connected with the end of the motor; the permanent magnet rotor is fixed on the load shaft and connected with the load. There is a gap between the induction rotor and the permanent magnet rotor. The connection between the motor and the load is thus changed from the original mechanical connection to a magnetic connection. The output torque on the load shaft can be changed by adjusting the distance or the area of the air gap between the permanent magnet rotor and the induction rotor, so that the load rotating speed is adjusted.
The eddy current in the induction rotor can cause the rotor to generate heat, the temperature rises, and when the permanent magnet exceeds a certain temperature, demagnetization can occur, so that the speed regulator fails. The more power the governor delivers, the more eddy currents it generates and the more heat the copper conductor heats up. At present, a speed regulator with larger power is generally in a water-cooled structure, and cooling liquid is sprayed to a working air gap by introducing an external pressure water source to realize cooling.
The water-cooled structure used at present is mainly an injection type temperature reduction. The cooling mode is that the permanent magnet rotor and the induction rotor are arranged on the machine base, the position of the machine base corresponding to the induction rotor is provided with a nozzle, and the induction rotor and the permanent magnet rotor are sprayed by pressurized cooling liquid introduced from the outside.
Under the action of the centrifugal force generated by the high-speed rotation of the induction rotor, the cooling liquid is difficult to be in good contact with the permanent magnet rotor and the induction rotor, so that the heat exchange between the cooling liquid and the permanent magnet rotor and the induction rotor is insufficient, and the cooling effect of the induction rotor and the permanent magnet rotor is poor.
Disclosure of Invention
Based on the above, the present invention provides a cartridge type permanent magnet speed regulator to overcome the defects of the prior art, so as to solve the problem of poor cooling effect of the induction rotor and the permanent magnet rotor.
A cylinder type permanent magnet speed regulator comprises a base, an outer rotor and an inner rotor, wherein the base is provided with a cooling liquid spraying structure; the outer rotor is arranged on the base and can rotate by taking a first axis as a center, and an accommodating cavity is formed in the outer rotor; the inner rotor is arranged on the base and can rotate by taking the first axis as a center, and the radial outer peripheral surface of the inner rotor is in clearance fit with the radial inner peripheral surface of the accommodating cavity to form an air gap; the inner rotor is provided with a first end part and a second end part which are opposite to each other along a first axial direction, and the first end part is provided with a radial flow guide diffusion part corresponding to the cooling liquid spraying structure; the radial flow guiding diffusion part is used for guiding the cooling liquid to diffuse and flow in the direction far away from the first axis.
In the cartridge type permanent magnet speed regulator, the cooling liquid from the cooling liquid spraying structure is sprayed to the radial guide diffusion part; under the action of the radial diversion diffusion part, the cooling liquid flows in a diffusion mode in the direction far away from the first axis. Under the guide action of the radial guide diffusion part, the cooling liquid can better flow along the end surface of the first end part, so that the proportion of the cooling liquid splashing away from the inner rotor is reduced; meanwhile, under the diffusion action of the radial flow guide diffusion part, the cooling liquid can flow to a plurality of directions in the circumferential direction of the first axis, and then the contact area of the cooling liquid and the inner rotor can be increased. Therefore, the problem that the heat dissipation effect of the cylindrical permanent magnet speed regulator is poor due to the fact that the cooling liquid splashes away from the inner rotor when the cooling liquid is sprayed to the inner rotor in a columnar mode can be solved.
In one embodiment, the radial guide diffuser portion is disposed circumferentially around the first axis. When the inner rotor rotates relative to the base, the radial flow guiding diffusion part which surrounds the first axial line in the circumferential direction can continuously keep corresponding relation with the cooling liquid spraying structure, so that the cooling liquid sprayed from the cooling liquid spraying structure to the radial flow guiding diffusion part can be continuously guided and diffused.
In one embodiment, the radial flow guiding diffusion part is provided with a radial flow guiding diffusion surface on one side away from the first axis; the radial flow guiding diffusion surface is in smooth transition connection with the end surface of the first end part. The radial flow guiding diffusion surface is in smooth transition connection with the end face of the first end portion, so that cooling liquid can smoothly flow to the end face of the first end portion, and the proportion of splashing of the cooling liquid from the inner rotor is reduced.
In one embodiment, the first end part is concavely provided with a liquid collecting cavity, the radial flow guide diffusion part is arranged at the bottom of the liquid collecting cavity, and the radial flow guide diffusion part is in spaced fit with the side wall of the liquid collecting cavity; the inner rotor is provided with a radial centrifugal runner, an inlet of the radial centrifugal runner is communicated with the liquid collecting cavity, and an outlet of the radial centrifugal runner is positioned on the radial peripheral surface of the inner rotor. The cooling liquid sprayed out of the cooling liquid spraying structure flows to the radial diversion diffusion part through the inlet of the liquid collecting cavity; the cooling liquid flows to the side wall of the liquid collecting cavity under the action of the radial guide diffusion part; under the action of centrifugal force, the cooling liquid is accumulated on the side wall of the liquid collecting cavity. Because the radial centrifugal flow channel is communicated with the liquid collecting cavity, after a certain amount of cooling liquid is collected in the liquid collecting cavity, the cooling liquid enters the radial centrifugal flow channel under the action of centrifugal force and flows out of the radial outer peripheral surface of the inner rotor to enter the air gap.
In one embodiment, there are at least two of the radial centrifugal flow channels, the outlets of the at least two radial centrifugal flow channels being distributed around the circumference of the first axis. Through the export of the radial centrifugal runner of distributing in first axis circumference, the coolant liquid can follow a plurality of positions on the radial outer peripheral face of inner rotor and get into the air gap, can promote the homogeneity that the coolant liquid distributes at first axis circumference like this, and then can promote the refrigerated homogeneity of coolant liquid to cylinder permanent magnet speed regulator in the circumference of first axis.
In one embodiment, the inner rotor is provided with an axial flow channel, an inlet of the axial flow channel is communicated with the liquid collecting cavity, and an outlet of the liquid collecting cavity is located on the end face of the second end portion. The coolant flow from the axial flow channel may flow to a portion of the outer rotor adjacent the second end, thereby cooling the portion of the outer rotor adjacent the second end.
In one embodiment, there are at least two of the axial flow passages, and the outlets of the at least two axial flow passages are distributed around the circumference of the first axis. Through the export of distributing in two at least axial runners on first axis circumference, the coolant liquid can cool down to two at least positions that are close to the second tip on the outer rotor, so can promote the coolant liquid to the refrigerated homogeneity of cylinder permanent magnet speed regulation ware.
In one embodiment, the outer rotor is provided with a mounting port communicated with the accommodating cavity, and the mounting port can be used for the inner rotor to enter and exit the accommodating cavity along the first axis.
In one embodiment, the outer rotor is provided with a liquid outlet communicated with the accommodating cavity, and the liquid outlet corresponds to the second end part. Therefore, the cooling liquid in the accommodating cavity can flow out, and the liquid collection in the accommodating cavity is reduced.
In one embodiment, a cooling cavity is arranged in the base, the inner rotor and the outer rotor are installed in the cooling cavity, and the cooling liquid spraying structure is arranged on the inner wall of the cooling cavity. The cooling cavity is utilized to facilitate the recycling of the cooling liquid; and simultaneously, the influence of the cooling liquid environment can be reduced.
Drawings
FIG. 1 is a schematic structural diagram of a cartridge type permanent magnet governor according to an embodiment;
FIG. 2 is a schematic structural view of an inner rotor and an outer rotor according to an embodiment;
fig. 3 is a partially enlarged view of a portion a in fig. 2.
Description of reference numerals: 10. the device comprises a base, 11, a cooling cavity, 100, a lower shell, 101, a lower cavity, 20, an outer rotor, 200, an accommodating cavity, 210, a mounting port, 220, a liquid outlet, 30, an inner rotor, 31, a first end portion, 32, a second end portion, 300, a radial flow guide diffusion portion, 301, a radial flow guide diffusion surface, 310, a liquid collecting cavity, 320, a radial centrifugal flow channel, 330, an axial flow channel, 340, a liquid guide cavity, 400, a first axis, 500 and an air gap.
Detailed Description
To facilitate an understanding of the invention, the invention will now be described more fully with reference to the accompanying drawings. Preferred embodiments of the present invention are shown in the drawings. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.
It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. In contrast, when an element is referred to as being "directly on" another element, there are no intervening elements present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only and do not represent the only embodiments.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
Referring to fig. 1, an embodiment provides a cartridge type permanent magnet speed regulator, including a base 10, an outer rotor 20 and an inner rotor 30, where the base 10 is provided with a cooling liquid spraying structure (not shown in the figure); the outer rotor 20 is mounted on the base 10 and can rotate around a first axis 400, and the outer rotor 20 is provided with a containing cavity 200 (not marked in the figure); the inner rotor 30 is mounted on the base 10 and can rotate around the first axis 400, and the radial outer peripheral surface of the inner rotor 30 and the radial inner peripheral surface of the accommodating cavity 200 are in spaced fit to form an air gap 500; the inner rotor 30 has a first end 31 and a second end 32 (not labeled in the figure) opposite to each other along the first axis 400, and the first end 31 is provided with a radial flow guide diffusion part 300 corresponding to the cooling liquid spraying structure; the radial guide diffuser portion 300 is used to guide the coolant to diffuse and flow in a direction away from the first axis 400.
In the cartridge type permanent magnet speed controller, the cooling liquid discharged from the cooling liquid discharge structure is discharged toward the radial flow diffusion portion 300; the coolant is diffused and flows in a direction away from the first axis 400 by the radial guide diffuser 300. Under the guide action of the radial guide diffusion part 300, the cooling liquid can better flow along the end surface of the first end part 31, so that the proportion of the cooling liquid splashing away from the inner rotor 30 is reduced; meanwhile, the coolant can flow in a plurality of directions in the circumferential direction of the first axis 400 by the diffusion action of the radial flow guide diffuser 300, and thus the contact area between the coolant and the inner rotor 30 can be increased. Therefore, the problem that the heat dissipation effect of the cylindrical permanent magnet speed regulator is poor due to the fact that the cooling liquid splashes away from the inner rotor 30 when the cooling liquid is sprayed to the inner rotor 30 in a cylindrical shape can be solved.
It should be noted that the above-described cooling liquid ejecting structure may be an ejecting port provided in the base 10, or may be a nozzle provided in the base 10.
When the cylindrical permanent magnet speed regulator is cooled, the cooling liquid spraying structure is connected with a cooling liquid supply device to cool the inner rotor 30 and the outer rotor 20.
Referring to fig. 1 and 2, in an embodiment, the radial flow guiding diffuser 300 is disposed around the first axis 400. The radial flow guiding diffuser 300 circumferentially disposed around the first axis 400 may be continuously maintained in correspondence with the coolant spray structure when the inner rotor 30 rotates relative to the base 10, so that the coolant sprayed from the coolant spray structure to the radial flow guiding diffuser 300 may be continuously guided and diffused.
Specifically, as shown in fig. 1 and 2, the radial flow guiding diffuser 300 is annular and surrounds the first axis 400 in the circumferential direction. The radial flow guide diffuser portion 300 is provided on the end surface of the first end portion 31 on the side in the first axis 400 direction.
Of course, in other embodiments, instead of the "radial flow guide diffuser portion 300 provided around the first axis 400", a plurality of radial flow guide diffuser portions 300 provided around the first axis 400 in the circumferential direction may be used. The difference between the two is that in the former, the plurality of radial guide diffusers 300 are not connected end to end.
In an embodiment, as shown in fig. 3, a side of the radial flow guiding diffuser portion 300 away from the first axis 400 has a radial flow guiding diffuser surface 301; the radial flow guiding diffusion surface 301 is connected with the end surface of the first end portion 31 in a smooth transition manner. The radial flow guiding diffusion surface 301 is connected with the end surface of the first end portion 31 in a smooth transition manner, so that the cooling liquid can smoothly flow to the end surface of the first end portion 31, and the proportion of the cooling liquid splashing away from the inner rotor 30 is further reduced.
In an embodiment, as shown in fig. 2 and 3, the first end portion 31 is concavely provided with a liquid collecting cavity 310, the radial flow guiding diffusion portion 300 is arranged at the bottom of the liquid collecting cavity 310, and the radial flow guiding diffusion portion 300 is in spaced fit with the side wall of the liquid collecting cavity 310; the inner rotor 30 is provided with a radial centrifugal runner 320, an inlet of the radial centrifugal runner 320 is communicated with the liquid collecting cavity 310, and an outlet of the radial centrifugal runner 320 is positioned on the radial outer peripheral surface of the inner rotor 30. The cooling liquid sprayed from the cooling liquid spraying structure flows to the radial flow guiding diffusion part 300 through the inlet of the liquid collecting cavity 310; the cooling liquid flows to the side wall of the liquid collecting cavity 310 by the radial guide diffusion part 300; under the centrifugal force, the coolant accumulates at the sidewall of the liquid collection chamber 310. Since the radial centrifugal flow channel 320 communicates with the liquid collection chamber 310, when a certain amount of the coolant is collected in the liquid collection chamber 310, the coolant enters the radial centrifugal flow channel 320 by a centrifugal force and flows out from an outlet of the radial centrifugal flow channel 320 located on the radial outer circumferential surface of the inner rotor 30 to enter the air gap 500.
Note that, the aforementioned "radial flow guide diffuser portion 300 is provided on the end surface of the first end portion 31"; in the embodiment in which "the radial guide diffuser portion 300 is provided at the bottom of the liquid collection chamber 310", the bottom wall of the liquid collection chamber 310 may be understood as the end surface of the first end portion 31.
Referring to fig. 2 and 3, in an embodiment, at least two liquid guiding cavities 340 communicating with the liquid collecting cavity 310 are disposed in the inner rotor 30, the liquid guiding cavities 340 are spaced apart from each other and are disposed on the circumferential direction of the first axis 400, the liquid guiding cavities 340 extend in the inner rotor 30 along the direction of the first axis 400, and the liquid guiding cavities 340 are in one-to-one communication with the radial centrifugal runners 320; the inlet of the radial centrifugal flow channel 320 is communicated with the liquid collecting cavity 310 through the liquid guide cavity 340.
Specifically, the communication port of the liquid guide chamber 340 communicating with the liquid collection chamber 310 is located on the side wall of the liquid collection chamber 310 away from the first axis 400. This allows cooling to be delivered into the drainage lumen 340 by the centrifugal force experienced by the cooling fluid. Meanwhile, liquid collection in the liquid guide cavity 340 can be avoided, so that the flowing speed of the cooling liquid can be improved.
In the first axial direction, the inner wall of the inlet of the liquid collecting cavity 310 covers the communication port for communicating the liquid guide cavity 340 and the liquid cavity 310.
Further, as shown in fig. 3, the radial centrifugal flow channel 320 includes at least two openings 321 spaced along the first axis 400, outlets of the openings 321 are located on the radial outer peripheral surface of the inner rotor 30, and inlets of the openings 321 are communicated with the liquid collecting cavity 310. Through the at least two orifices 321 distributed at intervals along the direction of the first axis 400, the cooling liquid can enter the air gap 500 from a plurality of positions along the direction of the first axis 400, so as to be beneficial to improving the uniformity of the cooling liquid for cooling the cartridge type permanent magnet speed regulator along the direction of the first axis 400.
Specifically, the inlet of the duct 321 is located on the inner wall of the drainage chamber 340.
It should be noted that in the previous embodiment, the radial centrifugal flow channel 320 includes at least two openings 321 spaced along the first axis 400. Of course, in other embodiments, the opening of the radial centrifugal flow channel 320 is slit-shaped, and the length direction of the opening is arranged along the first axis 400.
In one embodiment, as shown in fig. 2 and 3, there are at least two radial centrifugal flow channels 320, and outlets of the at least two radial centrifugal flow channels 320 are distributed around the circumference of the first axis 400. Through the outlets of the radial centrifugal runners 320 distributed on the circumferential direction of the first axis 400, the cooling liquid can enter the air gaps 500 from a plurality of positions on the radial outer circumferential surface of the inner rotor 30, so that the uniformity of the cooling liquid distributed on the circumferential direction of the first axis 400 can be improved, and further, the uniformity of the cooling liquid for the cylindrical permanent magnet speed regulator can be improved on the circumferential direction of the first axis 400.
In one embodiment, as shown in fig. 3, the inner rotor 30 is provided with an axial flow passage 330, an inlet of the axial flow passage 330 is communicated with the liquid collecting cavity 310, and an outlet of the liquid collecting cavity 310 is located on the end surface of the second end 32. The flow of the coolant flowing out of the axial flow passage 330 may flow to a portion of the outer rotor 20 near the second end 32, so that the portion of the outer rotor 20 near the second end 32 may be cooled.
In one embodiment, there are at least two axial channels 330, and the outlets of the at least two axial channels 330 are distributed around the circumference of the first axis 400. Through the outlets of the at least two axial runners 330 distributed along the circumferential direction of the first axis 400, the cooling liquid can cool at least two positions on the outer rotor 20 close to the second end portion 32, so that the uniformity of cooling the cartridge type permanent magnet speed regulator by the cooling liquid can be improved.
Specifically, the inlet of the axial flow channel 330 is located on the inner wall of the drainage chamber 340.
Referring to fig. 2, in an embodiment, the outer rotor 20 is provided with a mounting opening 210 communicating with the accommodating cavity 200, and the mounting opening 210 allows the inner rotor 30 to enter and exit the accommodating cavity 200 along a first axis 400.
When the inner rotor 30 and the outer rotor 20 are assembled, the inner rotor 30 is inserted into the receiving cavity 200 of the outer rotor 20 through the mounting opening 210.
In adjusting the cartridge permanent magnet governor, the inner and outer rotors 30 and 20 are relatively moved along the first axis 400 to adjust the strength of the magnetic coupling of the inner and outer rotors 30 and 20. It should be noted that the adjustment may be achieved by adjusting the coupling area of the magnetic coupling or the coupling distance (i.e., the size of the air gap) of the magnetic coupling when moving along the first axis 400.
There are three ways to achieve relative movement of the inner rotor 30 and the outer rotor 20 along the first axis 400, which are specifically as follows:
first, relative movement of the inner rotor 30 and the outer rotor 20 may be achieved by moving the outer rotor 20 along the first axis 400 while the axial position of the inner rotor 30 with respect to the first axis 400 is unchanged.
In the second mode, when the axial position of the outer rotor 20 with respect to the first axis 400 is not changed, the relative movement of the inner rotor 30 and the outer rotor 20 can be achieved by moving the inner rotor 30 along the first axis 400.
Third, the inner rotor 20 and the outer rotor 30 are moved simultaneously along the first axis 400 to achieve relative movement of the inner rotor 30 and the outer rotor 20.
In addition, when the inner rotor 30 and the outer rotor 20 relatively move along the first axis 400, the inner rotor 30 may be always located in the accommodating cavity 200; of course, the inner rotor 30 may also partially protrude out of the accommodating cavity 200 through the mounting opening 210.
While the inner rotor 30 is always in the receiving cavity 200. At this time, the cooling liquid spraying structure corresponds to the radial guide diffuser 300 through the mounting opening 210, so that the cooling liquid flowing out of the cooling liquid spraying structure can be sprayed toward the radial guide diffuser 300.
When the inner rotor 30 may partially protrude out of the receiving cavity 200, the coolant spray structure may spray the coolant directly toward the radial guide diffuser 300.
In one embodiment, the outer rotor 20 is provided with a liquid outlet 220 communicating with the accommodating cavity 200, and the liquid outlet 220 corresponds to the second end 32. Therefore, the cooling liquid in the accommodating cavity 200 can flow out, and the liquid collection in the accommodating cavity 200 is reduced.
Referring to fig. 1, in an embodiment, a cooling cavity 11 is formed in the base 10, the inner rotor 30 and the outer rotor 20 are installed in the cooling cavity 11, and the coolant spray structure is disposed on an inner wall of the cooling cavity 11. The cooling cavity 11 is utilized to facilitate the recycling of the cooling liquid; and simultaneously, the influence of the cooling liquid environment can be reduced.
The base 10 includes an upper housing and a lower housing 100 that are snap-coupled to each other. The lower housing 100 is shown.
Specifically, the lower case 100 is provided with a lower cavity 101 opened upward, and the upper case is provided with a lower cavity 101 opened downward. When the upper and lower housings 100 are snap-fit connected, the lower housing 101 communicates with the upper housing to form the cooling chamber 11.
The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.
The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (10)
1. A drum-type permanent magnet speed regulator is characterized by comprising
The base is provided with a cooling liquid spraying structure;
the outer rotor is arranged on the base and can rotate by taking a first axis as a center, and an accommodating cavity is formed in the outer rotor; and
the inner rotor is arranged on the base and can rotate by taking the first axis as a center, and the radial outer peripheral surface of the inner rotor is in clearance fit with the radial inner peripheral surface of the accommodating cavity to form an air gap;
in a first axial direction, the inner rotor has opposite first and second ends; the first end part is provided with a radial flow guide diffusion part corresponding to the cooling liquid spraying structure; the radial flow guiding diffusion part is used for guiding the cooling liquid to diffuse and flow in the direction far away from the first axis.
2. The cartridge type permanent magnet speed regulator according to claim 1, wherein the radial flow guide diffuser portion is annularly arranged on the circumference of the first axis.
3. The cartridge type permanent magnet speed regulator according to claim 1, wherein the radial flow guiding diffusion part is provided with a radial flow guiding diffusion surface on one side far away from the first axis; the radial flow guiding diffusion surface is in smooth transition connection with the end surface of the first end part.
4. The cartridge type permanent magnet speed regulator according to any one of claims 1 to 3, wherein the first end is concavely provided with a liquid collecting cavity, the radial flow guide diffusion part is arranged at the bottom of the liquid collecting cavity, and the radial flow guide diffusion part is in spaced fit with the side wall of the liquid collecting cavity;
the inner rotor is provided with a radial centrifugal runner, an inlet of the radial centrifugal runner is communicated with the liquid collecting cavity, and an outlet of the radial centrifugal runner is positioned on the radial peripheral surface of the inner rotor.
5. The cartridge permanent magnet governor of claim 4, wherein there are at least two of the radial centrifugal flow passages, the outlets of the at least two radial centrifugal flow passages being distributed about the circumference of the first axis.
6. The cartridge type permanent magnet governor according to claim 4, wherein the inner rotor is provided with an axial flow passage, an inlet of the axial flow passage communicates with a liquid collection chamber, and an outlet of the liquid collection chamber is located on an end surface of the second end portion.
7. The cartridge permanent magnet governor of claim 6, wherein there are at least two of the axial flow passages, the outlets of the at least two axial flow passages being distributed about the circumference of the first axis.
8. The cartridge type permanent magnet speed regulator according to claim 6, wherein the outer rotor is provided with a mounting port communicating with the receiving cavity, the mounting port allowing the inner rotor to enter and exit the receiving cavity along the first axis.
9. The cartridge type permanent magnet speed regulator according to claim 6, wherein the outer rotor is provided with a liquid outlet communicated with the accommodating cavity, and the liquid outlet corresponds to the second end portion.
10. The cartridge type permanent magnet speed regulator according to claim 1, wherein a cooling cavity is provided in the base, the inner rotor and the outer rotor are mounted in the cooling cavity, and the cooling liquid spraying structure is provided on an inner wall of the cooling cavity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010118837.1A CN111162634A (en) | 2020-02-25 | 2020-02-25 | Drum type permanent magnet governor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010118837.1A CN111162634A (en) | 2020-02-25 | 2020-02-25 | Drum type permanent magnet governor |
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| CN111162634A true CN111162634A (en) | 2020-05-15 |
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| CN202010118837.1A Pending CN111162634A (en) | 2020-02-25 | 2020-02-25 | Drum type permanent magnet governor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115395693A (en) * | 2022-06-27 | 2022-11-25 | 重庆大学 | Cooling mechanism of permanent magnet speed regulator |
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