CN109787387B

CN109787387B - Wind generating set, electric automobile, motor, rotor, heat sink type permanent magnet magnetic pole fastening structure, processing, heat dissipation and torsional vibration reduction method

Info

Publication number: CN109787387B
Application number: CN201910086760.1A
Authority: CN
Inventors: 马盛骏
Original assignee: Beijing Goldwind Science and Creation Windpower Equipment Co Ltd
Current assignee: Beijing Goldwind Science and Creation Windpower Equipment Co Ltd
Priority date: 2019-01-29
Filing date: 2019-01-29
Publication date: 2020-09-15
Anticipated expiration: 2039-01-29
Also published as: CN109787387A

Abstract

The invention discloses a wind generating set, an electric automobile, a motor, a rotor, a heat sink type permanent magnetic pole fastening structure, a processing and heat dissipation method and a method for reducing torsional vibration of a shaft system of the wind generating set. When the temperature around the permanent magnetic pole rises, the heat sink type permanent magnetic pole fastening structure can absorb heat to perform phase change, and the heat absorption rate of the permanent magnetic pole and a motor heat source can be improved by one order of magnitude by means of the heat exchange rate during the phase change. In addition, the phase change medium can flow in the cavity in the process of rotating along with the heat sink type permanent magnetic pole fastening structure, and the effects of repeatedly refreshing a boundary layer formed by liquid-solid contact and enhancing heat transfer are generated.

Description

Wind generating set, electric automobile, motor, rotor, heat sink type permanent magnet magnetic pole fastening structure, processing, heat dissipation and torsional vibration reduction method

Technical Field

The invention relates to the technical field of electromagnetic devices, in particular to a wind generating set, an electric automobile, a motor, a heat sink type permanent magnet magnetic pole fastening structure, a machining method and a method for reducing torsional vibration of a shaft system of the wind generating set.

Background

Referring to fig. 1-3, fig. 1 is an axial view of a motor; FIG. 2 is a partial heat transfer heat flow view of FIG. 1; fig. 3 is a view showing the fastening of the hold-down bar and the yoke, magnetic pole.

The motor comprises a rotor and a stator, wherein the rotor comprises a magnetic yoke 01 which is positioned at the outermost side and is shown in figure 1, a plurality of magnetic poles 04 which are distributed along the circumferential direction are arranged on the inner side of the magnetic yoke 01, adjacent magnetic poles 04 are fastened through pressing strips 05, specifically, bolts 06 are inserted into the pressing strips 05 and connected with the magnetic yoke 01, and inclined surfaces at two sides of each pressing strip 05 respectively press the outer surfaces, contacted with the adjacent magnetic poles 04, of the two magnetic poles 04, so that the magnetic poles 04 are fastened to be close to the magnetic yoke 01. The gaps between the batten 05 and the outer surface of the magnetic pole 04 are refilled with protective resin, and a fiber reinforced resin protective coating is laid on the radial outer surface. The stator includes a core formed by laminating a plurality of laminations 02 in an axial direction, and a plurality of teeth 021 are formed on an outer edge of the laminations 02, and slots 022 are formed between the teeth 021 to accommodate windings.

As shown in fig. 2, the heat source (based on copper loss and iron loss) of the stator generates heat, and when radiating radially outward, the heat reaches the protective coating layer of the protective magnetic pole first, and then is transmitted to the magnetic pole 04 and the bead 05. The pressing strip 05 is usually made of a resin laminated plate, the heat conductivity coefficient is small, when heat is transferred along the radial direction of the motor through the pressing strip 05, heat conduction is blocked, thermal resistance is large, meanwhile, due to the fact that the thermal resistance of the pressing strip 05 is large, shunting in the circumferential direction is blocked, heat flow reaching the magnetic pole 04 is difficult to transfer to the pressing strip 05 along the circumferential direction of the magnetic pole 04, and actually, most of radiation heat flow of the stator is transferred to the magnetic yoke 01 through the magnetic pole 04. When the radiant heat flow is transmitted to the yoke 01 in a heat conduction manner, the heat flow at two sides of the magnetic pole 04 flows to the region with lower temperature of the yoke 01, namely to the region of the yoke 01 opposite to the batten 05, and the region is also the region of the yoke 01 of the batten 05 along the back region of the rotor in the radial direction, so that a transmission path for the heat flow which is symmetrical and inclined in the radial direction of the rotor of the motor is formed, such as a region B shown in figure 2, and thus, the heat transmission path is lengthened, and the radial temperature gradient of the region of the yoke 01 is reduced (due to the fact that the thermal resistance of the batten 05 is larger). The heat flow transferred to the yoke 01 is further radially diffused to the outside, and is convectively transferred with the air flow on the outer wall of the yoke 01. The region a shown in fig. 2 belongs to a region where the temperature of the yoke 01 is relatively high. It can be seen that the outward transfer of the stator radiant heat flow is somewhat impeded (about one quarter of the rotor inner surface radial heat transfer) by the presence of the batten 05.

With continued reference to fig. 4 and 5, fig. 4 is a schematic view illustrating the magnetic pole 04 being fixed by the magnetic pole protection box 07; fig. 5 is a schematic view of the magnetic pole guard box 07.

As shown in fig. 4, the magnetic pole shield box 07 is clamped on the magnetic poles 04, the magnetic pole shield box 07 is fixed with the magnetic yoke 01, edges 07a are provided on both sides of the magnetic pole shield box 07, and the adjacent magnetic poles 04 are covered by the edges 07 a. In this scheme, the cover plate of the magnetic pole protection box 07 often has a surface with high spectral reflectivity and low absorptivity, so that the rotor and the stator are almost thermally isolated, and the heat radiated out from the stator in the radial direction is more difficult to radiate outwards through the rotor.

Disclosure of Invention

The invention also provides a heat sink type permanent magnetic pole fastening structure which is provided with a cavity, wherein the cavity is filled with a phase change medium, the phase change medium can absorb heat, and the phase change medium absorbs heat and generates phase change after the temperature rises to a certain temperature.

Optionally, the heat sink type permanent magnet pole fastening structure is a heat sink type pressing bar between adjacent permanent magnet poles, or the heat sink type permanent magnet pole fastening structure is a permanent magnet pole protection box for clamping and covering the permanent magnet poles.

Optionally, a reinforcing part is arranged in the cavity of the heat sink type pressing strip, and two ends of the reinforcing part are respectively connected with two sides of the heat sink type permanent magnetic pole fastening structure.

Optionally, the reinforcing part is a reinforcing support beam, and a plurality of reinforcing support beams arranged along the length direction of the heat sink type batten are arranged in the heat sink type batten;

or, the reinforcing part is a screening plate provided with a plurality of screen holes, the screening plate divides the cavity into an inner cavity and an outer cavity, and when the rotor provided with the permanent magnetic pole rotates, the phase change medium flows between the inner cavity and the outer cavity through the screen holes and can be separated from gas and liquid.

Optionally, the screening plate comprises a screening pipe, the screening pipe penetrates through the screening plate, and two ends of the screening pipe protrude out of the surface of the screening plate; the screening pipe is inserted into the screening holes, or the screening pipe is integrally formed on the screening plate, and the tube cavity of the screening pipe forms the screening holes.

Optionally, one end of the heat sink type permanent magnet magnetic pole fastening structure is a condensation section, the condensation section is made of a material with high thermal conductivity and thermal diffusivity, and the outer surface of the condensation section has high infrared radiation emissivity, and/or the outer surface of the condensation section is coated with a coating with high thermal conductivity.

Optionally, the heat sink permanent magnet pole fastening structure is provided with a suction hole to evacuate the inner cavity.

Optionally, the heat sink permanent magnet pole fastening structure is provided with a sealing portion to seal the suction hole.

Optionally, the phase change medium is a gas-liquid phase change medium, or a solid-liquid phase change medium.

Optionally, the phase change medium is any one of water, deionized water, a mixed solution of ionized water and ethylene glycol, a hydrated salt, a polyol, a polymer resin, and an ester acid.

The invention also provides a rotor, which comprises a magnetic yoke and a permanent magnetic pole, wherein the permanent magnetic pole is fixed on the magnetic yoke through a heat sink type permanent magnetic pole fastening structure, and the heat sink type permanent magnetic pole fastening structure is any one of the heat sink type permanent magnetic pole fastening structures.

The invention also provides a motor which comprises a rotor and a stator, wherein the rotor is the rotor.

Optionally, the motor is further provided with a cold source capable of providing a cooling medium; the shafting of the motor is provided with an elevation angle, the heat sink type permanent magnetic pole fastening structure is correspondingly provided with a high position end and a low position end in a gravity field, and the cooling medium can cool the high position end of the heat sink type permanent magnetic pole fastening structure.

Optionally, the heat sink is a vortex separator.

Optionally, the electric machine includes an iron core, and a fastening member penetrating through the iron core along an axial direction of the electric machine to tighten the iron core, the fastening member is provided with an airflow channel extending along an axial direction of the fastening member, and the airflow channel penetrates through a high end of a position in a gravity field of the fastening member, and a cooling airflow generated by an output of the eddy current separator device can enter the airflow channel and flow out from the high end of the position, and then flows to the high end of the position of the heat sink type permanent magnet pole fastening structure.

Optionally, the motor is of an outer rotor structure; the motor comprises an iron core bracket, and the eddy current separator is arranged at the iron core bracket; the motor is also provided with an inlet channel which penetrates through the peripheral walls of the iron core and the iron core bracket so as to communicate the airflow channel with the vortex separator.

Optionally, the vortex separator is provided with a plurality of cooling air flow outlet lines corresponding to the air flow passages for delivery to the plurality of fasteners.

Optionally, the fastening member is provided with a recovery passage penetrating through the lower end of the fastening member and an outlet passage penetrating through the peripheral walls of the core and the core support, and the cooling air flows back to the vortex separator from the recovery passage and the outlet passage after flowing out of the air flow passage.

Optionally, the fastener is provided with a channel which penetrates along the axial direction and is separated to form the airflow channel and the recovery channel; and a side wall channel penetrating through the iron core and the peripheral wall of the iron core bracket is further arranged, and the side wall channel is separated to form the inlet channel and the outlet channel.

Optionally, the gas flow channels are isolated to form a first channel and a second channel which can be respectively introduced with a cooling medium and a heating medium.

The invention also provides a wind generating set which comprises a generator, a cabin and a wind turbine, wherein the generator is the motor.

Optionally, the cold source is provided at the nacelle; the cold source is an eddy current separator, or an open cooling system formed by a ventilator communicated with the natural environment, or a closed cooling system comprising a ventilator and a surface heat exchanger which are connected in series, and the generated cooling medium or cold airflow from the natural environment is conveyed to the generator through an airflow conveying pipeline and flows to the high end of the position of the heat sink type permanent magnetic pole fastening structure.

The invention further provides an electric automobile which comprises the motor, wherein the motor is any one of the motors.

The invention also provides a processing method of the heat sink type permanent magnetic pole fastening structure, the heat sink type permanent magnetic pole fastening structure with the cavity is processed and formed, under the condition that the temperature is higher than the normal temperature or is close to the working temperature, the phase change medium is injected into the cavity and can absorb heat, and the phase change medium absorbs heat and generates phase change after the temperature rises to a certain temperature.

The invention also provides a heat dissipation method of the motor, the motor comprises a rotor and a stator, the rotor comprises a magnet yoke and a permanent magnetic pole, and the heat dissipation method comprises the following steps:

fixing the permanent magnetic pole to the magnetic yoke through a heat sink type permanent magnetic pole fastening structure;

the heat sink type permanent magnet magnetic pole fastening structure is provided with a cavity, and a phase change medium is injected into the cavity, when the motor is warmed, the phase change medium can absorb heat, and the phase change medium can generate phase change after the heat absorption temperature rises to a certain temperature, so that the motor can dissipate heat.

The invention also provides a method for reducing torsional vibration of a shafting of a wind generating set, wherein the motor comprises a rotor and a stator, the rotor comprises a magnet yoke and a permanent magnetic pole, and the method for reducing torsional vibration of the shafting of the wind generating set comprises the following steps:

the heat sink type permanent magnetic pole fastening structure is provided with a cavity, and a phase change medium is injected into the cavity; regulating and controlling the phase change temperature of the phase change medium so as to keep the magnetic field temperature of the motor within a working temperature range;

the motor is cooled through phase change, so that the magnetic field temperature of the motor is kept in a working temperature range, and the torsional vibration of a shafting of the wind generating set is reduced.

Optionally, regulating the phase change temperature of the phase change medium comprises:

adding a mixture into the phase change medium, and regulating and controlling the phase change temperature of the phase change medium; and/or adjusting the vacuum degree in the cavity and adjusting and controlling the phase change temperature of the phase change medium.

The heat sink type permanent magnet pole fastening structure provided in the above scheme, namely the corresponding rotor, motor, wind generating set and electric automobile with the permanent magnet pole fastening structure, all produce the following technical effects:

when the temperature rises around the permanent magnetic pole, the heat sink type permanent magnetic pole fastening structure can absorb heat, phase change is carried out after the temperature rises to a certain temperature, and the heat transfer rate is remarkably improved by means of the heat exchange rate during the phase change, so that the heat absorption rate of the permanent magnetic pole and a motor heat source is improved. In addition, the phase change medium can flow in the cavity in the rotating process, so that a boundary layer formed by repeatedly refreshing liquid-solid contact is generated, heat transfer is enhanced, and the heat exchange effect is further improved. Therefore, the scheme creatively utilizes the heat sinking type permanent magnetic pole fastening structure as a container of the phase change medium, and converts the phase change medium into a carrier with high-efficiency heat transfer capacity, so that the heat dissipation performance of the permanent magnetic pole is improved. Therefore, in the scheme, the heat sink type permanent magnetic pole fastening structure is not used as a barrier of heat transfer any more, the function of heat sink is exerted while the function of fastening the permanent magnetic pole is exerted, the radiant heat received by the permanent magnetic pole is transferred and shunted, the radiant heat of a stator heat source is absorbed and shunted in a large capacity, the thermal effect generated by induced current on the surface of the shunt permanent magnetic pole is achieved, and the uniformity of temperature rise control, the uniformity of temperature distribution and the controllability of temperature rise speed are considered. Correspondingly, the heat sink type permanent magnet magnetic pole fastening structure can reduce the heat flux share transferred from the permanent magnet magnetic pole to the magnetic yoke in the radial direction, and the function of protecting the permanent magnet magnetic pole is also achieved.

In addition, the heat sink type permanent magnetic pole fastening structure in the scheme is adopted, the temperature control effect and the constant temperature fact of liquid gasification at full load are generated on the permanent magnetic pole, and the constant temperature control on the permanent magnetic pole can be realized. In addition, because the control of the converter rectification part at the downstream of the energy transfer power flow to the stator current can indirectly brake the rotation of the rotor permanent magnetic pole, the resistance and the inductance value of the motor stator armature, and the temperature change of the rotor permanent magnetic pole can enable the rotor and a prime motor (namely a wind turbine) thereof to be in dynamic regulation all the time. The phase change medium plays roles of peak clipping, valley filling and change inhibition in the process of great change of the radial heat flux density of the motor air gap, stabilizes the temperature of a magnetic field and stabilizes the electrical parameters in the phase change process, is favorable for realizing the control of the armature current of the permanent magnet motor stator to balance the rotating torque of the motor rotor, and is favorable for the dynamic balance adjustment of the rotating torque and the braking torque of a motor shaft system.

Drawings

FIG. 1 is an axial view of an electric machine;

FIG. 2 is a partial heat transfer heat flow view of FIG. 1;

FIG. 3 is a fastening view showing the heat sink bar and the yoke, permanent magnet pole;

FIG. 4 is a schematic view of a PMT magnetic pole encapsulated and fixed by a PMT protective box retaining cap;

FIG. 5 is a schematic view of a permanent magnet pole guard box;

FIG. 6 is a schematic distribution diagram of an embodiment of a rotor-heatsink type batten in a typical physical clock position according to the present invention;

FIG. 7 is a state diagram of the heat-sink molding of FIG. 6 at the position corresponding to the clock 12 point;

FIG. 8 is a state diagram of the heat-sink molding of FIG. 6 at the position corresponding to the clock 3 point;

FIG. 9 is a state diagram of the heat-sink molding of FIG. 6 at the position corresponding to the clock 6 point;

FIG. 10 is a state diagram of the heat-sink molding of FIG. 6 at the position corresponding to clock 9;

fig. 11 is a sectional view taken along line a-a of fig. 7. (ii) a

FIG. 12 is a schematic view of a heat sink type bead with a screening plate circumferentially distributed along an inner wall surface of a rotor;

FIG. 13 is a schematic view of the heat sink molding of FIG. 12 in the clock 12 position;

FIG. 14 is a schematic view of the screening deck of FIG. 13;

FIG. 15 is a schematic view of a generator shafting facing in the elevation of the windward direction;

FIG. 16 is a schematic view of an embodiment of a motor provided in the present invention;

FIG. 17 is a sectional view taken along line B-B of FIG. 16;

FIG. 18 is a schematic diagram of the basic structure of the vortex separator of FIG. 16 and the overall temperature separation of the gas flow;

FIG. 19 is a flow-through cross-sectional view of the nozzle flow passage of FIG. 18;

FIG. 20 is a schematic view of the internal flow field, thermal energy transfer within the vortex separator element of the core of FIG. 18;

FIG. 21 is a schematic diagram comparing free and forced vortices;

FIG. 22 is a schematic representation of the overall temperature separation operation within the vortex separator of FIG. 18 based on a thermodynamic temperature-entropy (T-S) diagram;

FIG. 23 is a cross-sectional view of the fastener of FIG. 16;

FIG. 24 is a simplified schematic illustration of a plurality of stator cores with axial fasteners spatially parallel and circumferentially distributed;

FIG. 25 is a schematic view of a vortex separator delivering cooling air flow in multiple directions;

fig. 26 is a schematic view of a wind turbine generator system according to an embodiment of the present invention.

The reference numerals in fig. 1-5 are illustrated as follows:

01 magnet yoke, 02 lamination, 021 tooth part, 022 tooth groove, 03 protective layer, 04 permanent magnet pole, 05 layering, 06 bolt, 07 permanent magnet pole protective box, 07a edge.

The reference numerals in fig. 6-26 are illustrated as follows:

10 magnetic yokes;

20 heat sink beads, 201 outer cavity, 202 inner cavity, 203 bolt, 204 radial support, 205 suction hole, 206 seal, 207 reinforcing support beam, 208 screening plate, 208a screening tube, 20a outer side, 20b inner side, 20c first side, 20d second side, 20e bead position high end, 20f bead position low end; 20' a phase change medium;

311 vortex separator, 3111 vortex separator tube, 3112 nozzle, 3111a vortex chamber, 3111b warm end tube section, 3111c cold end tube section, 3111d cold end, 3111e warm end, 3111a1 end plate, 3113 throttle; 312 compressor, 313 recovery unit;

40 permanent magnet poles, 50 windings, 60 iron core brackets, 70 iron cores, 701 fasteners, 701a first channel, 701c second channel, 701b recycling channel, 601 inlet channel, 602 outlet channel and 702 nuts;

100 generators, 200 hubs, 300 wind turbines, 400 air filters, 500 drive motors, 600 ventilators, 700 towers, 800 nacelles, 900 airflow transport ducts.

Detailed Description

In order to make the technical solutions of the present invention better understood by those skilled in the art, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.

The permanent magnetic pole fastening structure provided by the invention is provided with the cavity, the phase change medium is injected in the cavity, and when the temperature rises outside the permanent magnetic pole fastening structure, the phase change medium can absorb heat and rise to a certain temperature to generate phase change. The permanent magnetic pole fastening structure at the moment is used as a heat sink to form a heat sink type permanent magnetic pole fastening structure. The following embodiments are mainly explained by taking a heat sink type permanent magnet magnetic pole fastening structure as a heat sink type pressing bar, as follows:

referring to fig. 6-10, fig. 6 is a schematic distribution diagram of an embodiment of a rotor heat sink type batten 20 at a typical physical clock position, showing a cross section of the heat sink type batten 20, showing a state of the heat sink type batten 20 distributed at different circumferential positions of the magnetic yoke 10; FIG. 7 is a state diagram of the heat-sink molding 20 of FIG. 6 in a position corresponding to the clock 12 point; FIG. 8 is a state diagram of the heat-sink molding 20 of FIG. 6 in the position corresponding to the clock 3 point; FIG. 9 is a state diagram of the heat-sink molding 20 of FIG. 6 in the position corresponding to the clock 6 point; fig. 10 is a state diagram of the heat-sink type molding 20 in fig. 6 at the position corresponding to the clock 9 point.

The heat sink type pressing strip 20 is specifically disposed between the two permanent magnet poles 40, and is used for pressing the permanent magnet poles 40 against the magnetic yoke 10, and for this purpose, the cross section of the heat sink type pressing strip 20 may be trapezoidal or a cross section shape shown in fig. 3 in the background art, so as to cooperate with the permanent magnet poles 40 to generate radial pressure, thereby achieving a pressing and fastening effect along the radial direction of the motor rotor. The initial force of the pressing and fastening is finally from the bolt 203, the bolt 203 is inserted into the heat sink type pressing strip 20 and the magnetic yoke 10 to lock the heat sink type pressing strip 20 to the magnetic yoke 10, and the permanent magnet pole 40 is correspondingly fixed, of course, the form of locking the heat sink type pressing strip 20 to the magnetic yoke 10 is not limited to the bolt 203, and the bonding or the clamping groove and the like are feasible to realize the fixing of the heat sink type pressing strip 20 to the surface of the magnetic yoke 10. The specific working principle of the heat sink bead 20 can be understood with reference to the background art. In fig. 6, only the state views of the heat sink type depression bar 20 at the positions of 12 o 'clock, 3 o' clock, 6 o 'clock and 9 o' clock are shown to facilitate understanding of the internal fluid state change of the heat sink type depression bar 20 when rotating to different orientations, and the heat sink type depression bar 20 in other orientations and the structures of the permanent magnet pole 40, the magnetic yoke 10 and the like are not shown in fig. 6.

It should be emphasized that the heat sink depression bar 20 in this embodiment is not a solid structure, but a hollow structure, and has a cavity, and the cavity is filled with a phase change medium 20', which, as the name suggests, is a medium capable of absorbing heat and increasing temperature and then performing phase change, and does not increase temperature in the phase change process, such as a medium performing liquid-gas phase change, solid-liquid phase change, and solid-solid phase change, because the temperature of the medium does not increase in the phase change process, the temperature increase rate of the permanent magnet pole 40 is suppressed and becomes slow.

Specifically, when the phase change medium 20' is a gas-liquid phase change medium, the liquid and gas phase transformation can be accomplished by using water, deionized water, a mixed solution of ionized water and ethylene glycol, and the like. Phase change media 20' may also be supplemented with solid-liquid phase change media, which may be classified according to their chemical composition into inorganic phase change materials, organic phase change materials, and composite phase change materials, such as: paraffin and a mixture thereof (the mixture contains an additive material, the phase transition temperature can be regulated and controlled, for example, stearic acid is added into the paraffin to form a composite phase transition material, the phase transition temperature is regulated and controlled at 60-70 ℃, the paraffin share is increased, the phase transition temperature is reduced, but the heat conductivity coefficient of the composite phase transition material is improved), hydrated salt, fatty acid, polyol and high molecular resin, and the prior art can be corresponding to any phase transition temperature, namely, the phase transition temperature of the phase transition medium 20 'can be regulated and controlled by a method of adding the mixture into the phase transition medium 20'. Both solid-liquid phase change media and gas-liquid phase change media are suitable for use in this embodiment, and the solid-liquid phase change media also have better stability.

Therefore, when the temperature around the permanent magnet pole 40 rises, the heat sink type pressing strip 20 can absorb heat, phase change is carried out after the temperature rises to a certain temperature, and the heat transfer rate is remarkably improved by means of the heat exchange rate during the phase change, so that the heat absorption rate of the permanent magnet pole 40 and a motor heat source is further improved. For example, the heat conduction capability of the heat sink type molding 20 can be improved by several times or more as compared with the molding made of resin in the background art. Moreover, the phase change medium 20' can flow in the cavity during the rotation process, so that a boundary layer formed by repeatedly refreshing liquid-solid contact and enhancing heat transfer are generated, and the heat exchange effect is further improved. Therefore, the scheme creatively utilizes the heat sink type permanent magnet pole fastening structure as a container of the phase change medium 20' to convert the phase change medium into a carrier with high-efficiency heat transfer capacity, thereby improving the heat dissipation performance of the permanent magnet pole 40. When the heat sink type pressing bar is applied to an outer rotor motor, the heat radiation of the stator positioned at the inner side of the permanent magnetic pole 40 can be obviously more effectively transmitted from the heat sink type pressing bar 20 and the permanent magnetic pole 40 to the magnetic yoke 10, and finally the heat exchange with the outside air is realized to realize the cooling and heat dissipation functions. Therefore, in the scheme, the pressing strip is no longer used as a barrier of heat transfer, the fastening function of the permanent magnetic pole 40 is exerted, the heat sink function is also exerted, the radiant heat received by the permanent magnetic pole 40 is transferred and shunted, the radiant heat of a stator heat source is absorbed and shunted in a large capacity, the heat effect generated by induced current on the surface of the shunt permanent magnetic pole 40 is considered, and the uniformity of temperature rise control, the homogenization of temperature distribution and the controllability of temperature rise rate are considered. Accordingly, the heat sink type permanent magnet pole fastening structure can reduce the heat flux portion transferred from the permanent magnet pole 40 to the yoke 10 in the radial direction, and thus, the permanent magnet pole 40 can be protected.

By adopting the heat sink type pressing strip 20 in the scheme, the temperature control effect and the constant temperature fact of liquid gasification at full load are generated on the permanent magnetic pole 40, and the constant temperature control of the permanent magnetic pole can be realized. In addition, because the control of the converter rectifying part at the downstream of the energy transfer power flow to the stator current can indirectly brake the rotation of the rotor permanent magnetic pole 40, the resistance and inductance value of the motor stator armature, and the temperature change of the rotor permanent magnetic pole 40 can enable the rotor and a prime mover (namely a wind turbine) thereof to be in dynamic regulation all the time, after the heat sink type pressing strip 20 in the scheme is adopted, the parameter of the permanent magnetic pole 40 becomes relatively stable, the dynamic balance between the converter and the rotor is easy to realize, the requirement of the converter for realizing the torque balance by controlling the stator current is indirectly reduced, and when the motor is applied to a wind generating set, the damage caused by the shafting torsional vibration of the wind generating set can. Namely, the phase change medium 20' plays roles of peak clipping, valley filling and change inhibition in the process of great change of the radial heat flux density of the motor air gap, stabilizes the temperature of a magnetic field and stabilizes the electrical parameters in the phase change process, is favorable for realizing the balance of the rotating torque of a motor rotor through the control of the armature current of a permanent magnet motor stator, and is favorable for the adjustment of the dynamic balance of the rotating torque and the braking torque of a motor shafting.

Therefore, the embodiment actually provides a method for reducing the torsional vibration of the shafting of the wind generating set, specifically:

the permanent magnet pole 40 is fixed to the yoke 10 by a heat sink type permanent magnet pole fastening structure;

the heat sink type permanent magnetic pole fastening structure is provided with a cavity, and a phase change medium 20' is injected into the cavity; regulating and controlling the phase change temperature of the phase change medium 20' so as to keep the magnetic field temperature of the motor within the working temperature range;

the motor is cooled through phase change, so that the temperature of a magnetic field of the motor is kept in a working temperature range, and the torsional vibration of a shafting of the wind generating set is reduced.

It should be noted that, when the phase change medium 20 ' absorbs heat and changes phase, the volume will increase, so in order to realize that the phase change medium 20 ' can change phase when absorbing heat, when the phase change medium 20 ' is injected in a liquid state, the cavity of the heat sink type permanent magnet pole fastening structure is not filled with the liquid state, so as to reserve a space when the phase changes into a gaseous state. Or liquid filling can be performed at a higher temperature (higher than the normal temperature or close to the working temperature), the heat source is removed after the liquid in the heat sink type pressing strip 20 is encapsulated, the external surface of the heat sink type pressing strip 20 is restored to the normal temperature, and vacuum and space are formed inside the heat sink type pressing strip. The liquid filling is carried out when the temperature is higher than the normal temperature or is close to the working temperature, the pressure in the cavity is close to the pressure in the working process during the filling process, the reserved space can be controlled more accurately, and the required phase change temperature of the phase change medium 20' is obtained. The operating temperature here is, for example, about 60 degrees celsius around the heat-sink permanent magnet pole fastening structure during operation.

As will be understood with continued reference to fig. 6-10, the heat sink type batten 20 shown in this embodiment is disposed in the outer rotor motor, where a side of the heat sink type batten 20 facing the stator is defined as an inner side 20b, a side facing the magnetic yoke 10 is defined as an outer side 20a, and two sides facing the permanent magnet pole 40 are respectively defined as a first side 20c and a second side 20 d. Since the phase change medium 20 'is not filled in the whole cavity of the heat sink type depression bar 20 when being in a liquid state, when the heat sink type depression bar 20 rotates along with the rotor, the phase change medium 20' flows and takes different forms in the heat sink type depression bar 20. Fig. 6 shows the heat sink type pressure bar 20 in four typical positions, when the heat sink type pressure bar 20 is at the clock 12 point position, the phase change medium 20' sinks, the inner side 20b is used as the bottom, and the liquid level is at a certain distance from the outer side 20 a; when the clock is at the position of 3 points, the first side 20c is used as the bottom, and the liquid level is at a certain distance from the second side 20 d; at the position of the clock 6 point, the outer side 20a is used as the bottom, and the liquid level has a certain distance with the inner side 20 b; at the clock 9 point, the second side 20d acts as the bottom and the liquid level is spaced from the first side 20 c.

As shown in fig. 11, fig. 11 is a sectional view taken along a-a of fig. 7.

The heat sink type permanent magnet pole fastening structure may be provided with a suction hole 205, specifically, as shown in fig. 11, the heat sink type pressing strip 20 is provided with a suction hole 205, and a cavity of the heat sink type pressing strip 20 may be evacuated from the suction hole 205. The temperature of the phase change is related to the type and pressure of the phase change medium 20', for example, the temperature of boiling phase change to gas state of water in high altitude and low pressure environment may be lower than 100 ℃. The suction holes 205 are arranged for suction to adjust the vacuum degree in the cavity, namely, pressure adjustment is realized, and the phase change temperature is adjusted and controlled through the method. The pressure regulation can be carried out according to the specific requirements of liquid phase-change temperature regulation. When heat is radiated to the position of the permanent magnetic pole 40 and the requirement of heat radiation to the natural environment by the permanent magnetic pole 40 is high, the phase change temperature can be correspondingly high, such as 90 ℃, and the vacuum degree can be properly reduced; when the permanent magnetic pole 40 has a low operating temperature level and requires a general heat dissipation requirement to the natural environment by means of the permanent magnetic pole 40, the liquid phase transition temperature may be set to be lower, for example, 60 ℃, and the vacuum degree may be set to be higher. In addition, the motor is generally provided with a cooling system, and the requirement on the cooling capacity of the motor cooling system can be reduced by adjusting the vacuum degree, for example, the flow rate of gas injected into cooling equipment is reduced, the diameter and the rotating speed of ventilation equipment are reduced, and then the noise is reduced, and the power consumption is reduced.

The two sides of the heat sink type depression bar 20 are matched with the permanent magnet poles 40, so the suction hole 205 can be arranged at one end of the heat sink type depression bar 20, as shown in fig. 11, a sealing part 206 can also be arranged, and after the suction is finished, the suction hole 205 is sealed by the sealing part 206. Bolt holes may be provided inside the heat sink molding 20, peripheral walls of the bolt holes forming the radial supports 204, and bolts 203 are inserted into the bolt holes to fasten the heat sink molding 20 and the yoke 10.

With continued reference to fig. 6, the cavity of the heat sink type pressing strip 20 is further provided with a reinforcing portion, and two ends of the reinforcing portion are respectively connected to two sides of the heat sink type pressing strip 20, that is, the first side 20c and the second side 20d of the heat sink type pressing strip 20. As mentioned above, the first side 20c and the second side 20d of the heat sink type batten 20 are pressed on the permanent magnetic pole 40, during the rotation of the rotor, the heat sink type batten 20 bears the pressure from the permanent magnetic pole 40, and the reinforcing part is arranged to enhance the pressure bearing capacity of the heat sink type batten 20, so as to ensure the fastening effect and the safety performance.

Specifically, the reinforcing portion may be a reinforcing support beam 207 as shown in fig. 7-10, and one or more reinforcing support beams 207 may be disposed within the cavity of the heat-sink molding 20, the plurality of reinforcing support beams 207 being disposed along the length of the heat-sink molding 20. The provision of the reinforcing support beam 207 preferably does not affect the flow of the phase change medium 20' during rotation to ensure a higher heat exchange effect. The reinforcing support beam 207 can have certain elasticity, and in the process of expansion with heat and contraction with cold of the permanent magnet pole 40, the heat sink type pressing strip 20 provided with the reinforcing support beam 207 can make up the possible looseness in the circumferential direction, so that the mounting stability of the permanent magnet pole 40 is ensured.

The reinforcement may also be a screening plate provided with a plurality of screening holes.

As can be understood with reference to fig. 12, fig. 12 is a schematic view of the heat sink beads 20 provided with screening plates circumferentially distributed along the inner wall surface of the rotor, again showing only the heat sink beads 20 at eight typical locations.

The screening plate serves as a reinforcement, and both ends are connected to the first side 20c and the second side 20d of the heat sink type batten 20, respectively. In addition, unlike the reinforcing support beams 207 described above, the screening plate may separate the chamber into an inner chamber 202, i.e., the chamber near the inner side 20b, and an outer chamber 201, i.e., the chamber near the outer side 20 a. Therefore, when the rotor rotates, the heat sink type pressing strip 20 rotates along with the rotor, and the phase change medium 20' flows between the inner cavity 202 and the outer cavity 201 through the sieve holes, so that a throttling effect is generated, and the throttling is more beneficial to realizing gas-liquid separation of the phase change medium. As mentioned above, the phase change medium 20 ' absorbs a certain amount of heat and undergoes phase change (the phase change process or the temperature in the phase change stage is almost unchanged) after the temperature rise stage is completed, still taking fig. 12 as an example, the phase change medium 20 ' absorbs heat to form a gas-liquid two-phase, and when rotating, the phase change medium 20 ' flows from the inner cavity 202 to the outer cavity 201 through the sieve holes, and due to the gas-liquid separation, the gaseous medium is favorably separated from the liquid medium, so that more liquid medium is favorably retained in the inner cavity 202, the heat absorption and phase change are continuously performed, and the heat dissipation efficiency is improved.

In addition, referring to fig. 13 and 14, fig. 13 is a schematic view of the heat sink type batten 20 at the position of the clock 12 point in fig. 12; fig. 14 is a schematic view of the screening deck of fig. 13.

As shown in fig. 13 and 14, the sieve plate has sieve holes, and sieve tubes are inserted into the sieve holes, and both ends of the sieve tubes protrude from the outer surface of the sieve plate. Thus, when the screening plates rotate with the heat sink beads 20, the phase change medium 20' does not flow too much, nor quickly, to the physical low level due to the obstruction of the screening tubes. Taking fig. 12 as an example, when the heat sink type pressing bar 20 rotates from the clock 3 point position to the clock 4 point half position, due to the arrangement of the sieving pipe, the liquid levels of the inner cavity 202 and the outer cavity 201 are not flush, and the liquid medium of the inner cavity 202 does not flow to the outer cavity 201 more, so that the residence time of the liquid medium of the inner cavity 202 is increased, the chances of receiving the stator radiation heat flow with the inner side 20b, contacting the inner surface of the inner side 20b with the liquid and absorbing the inner surface heat flow are increased, and the heat exchange rate is improved; meanwhile, the sieve pores have the functions of throttling and hanging-down backflow, the inner surface of the cavity is poured in the hanging-down backflow process, the convection heat transfer coefficient is higher when the liquid hanging-down process pours the solid surface, the solid surface of the inner cavity is repeatedly refreshed, the refreshing means that the boundary layer is contacted again and is reestablished in liquid-solid contact, and the heat exchange is enhanced while the boundary layer is beneficial to gas separation, buoyancy lift and upward movement.

The screening pipe can be directly formed on the screening plate, namely, the screening pipe and the screening plate are integrated components, the screen holes are the pipe cavities of the screening plate, the screening pipe and the screening plate can also be the separated components and are inserted into the screen holes of the screening plate, and the screening pipe is not limited by the scheme.

The permanent magnet pole 40 and the magnetic yoke 10 mentioned above belong to a part of a rotor of a motor, and when the motor is specifically applied as the wind driven generator 100, a shaft system of the motor has a certain elevation angle.

Referring to fig. 15, fig. 15 is a schematic diagram of the generator 100 with the shaft facing the windward elevation. As shown in fig. 15, the elevation angle α of the motor shaft system of the wind power generator 100 is typically in the range of 5 ° to 6 °.

Because the motor shaft system is facing upward and the wind comes and has an elevation angle, a plurality of components (such as the permanent magnet pole 40, the heat sink type batten 20 and the like) in the motor parallel to the shaft system also have an elevation angle, so that a higher physical position end and a lower physical position end in a gravity field are formed, and the positions are defined as a high position end and a low position end as follows, for example, the heat sink type batten 20 serving as a heat sink type permanent magnet pole fastening structure has a batten position high end 20e and a batten position low end 20 f. At this time, when part of the phase change medium 20' in the cavity of the heat sink type pressing bar 20 changes into a gas state, the gas medium will gather toward the high end 20e of the pressing bar position, as shown in fig. 15, the gas flow will converge upward and flow toward the high end 20e of the pressing bar position on the left side, and after condensation (see the following detailed description), the gas flow will flow from the bottom end of the heat sink type pressing bar 20 in a liquid state from the left side to the right side, and the flow path is indicated by an arrow in fig. 15.

Therefore, the cooling source capable of providing the cooling medium is further arranged in the embodiment, the cooling medium output by the cooling source can cool the high end 20e of the position of the pressing bar, the gaseous medium gathered inside the high end 20e of the position of the pressing bar can be condensed and returns to the liquid state again, and flows from the high end 20e of the position of the pressing bar to the low end 20f of the position of the pressing bar under the action of gravity, so that the function of absorbing and storing larger heat energy to ensure that the temperature of the heat sink type pressing bar 20 is hardly increased any more in the phase change heat absorption process is continuously exerted. The cooling medium may be in a liquid state (e.g., a liquid medium having an insulating function), a gas state, or the like. It can be seen that after the cold source is arranged for cooling, not only the temperature rise rate of the permanent magnetic pole 40 is inhibited and becomes slow, but also the heat sink type pressing strip 20 is used as a main force and a main channel for radial heat flow transmission of the rotor, and the combined action of the force of the liquid gasification buoyancy and the centrifugal force and the capillary force generated by rotation in the heat sink type pressing strip 20 can be used, the gas generated by gasification carries a small amount of liquid to move to the high end 20e of the position of the heat sink type pressing strip, at the high end 20e of the position of the heat sink type pressing strip, the external surface is cooled by an external cold source medium, the gas is condensed into liquid and flows back to the low end 20f of the position of the heat sink type pressing strip under the. The arrangement of the cold source capable of providing the cooling medium enables the gasification rate of the phase change medium of the heat sink type pressing strip 20 to be obviously improved, the temperature of the permanent magnetic pole 40 and the temperature of the winding 50 to be effectively reduced, the permanent magnetic pole 40 and the winding 50 can be kept in a normal working temperature range, and the electric energy of the motor can be increased.

Referring to fig. 16 and 17, fig. 16 is a schematic diagram of an embodiment of a motor according to the present invention, which is a lower half of an axial cross-sectional view of the motor, and an elevation angle of a shaft system of the motor also exists; fig. 17 is a sectional view taken along line B-B of fig. 16.

The motor in the embodiment is an outer rotor motor, the rotor is located on the outermost side of the shafting in the radial direction, and the stator is located on the inner side of the rotor in the radial direction. Specifically, the rotor of the motor includes a yoke 10 and a permanent magnet pole 40, and the heat sink type pressing bar 20 is not shown, and the permanent magnet pole 40 is fixed to the yoke 10 by the heat sink type permanent magnet pole fastening structure in any of the above embodiments, and presses the permanent magnet pole 40 toward the inner wall surface of the yoke 10.

As further shown in fig. 16, the stator of the motor includes a core 70, and a fastener 701 axially penetrating the core 70 and tightening the core 70, where the fastener 701 may be a bolt, and both ends are fastened by nuts 702. The core 70 may be formed by stacking a plurality of axially stacked laminations, and the fasteners 701 may extend axially through the core 70, i.e., through all of the laminations, thereby axially compressing the plurality of laminations to ensure the continuity of the solid medium of the core 70 as a whole.

In this embodiment, the fastener 701 is provided with an air flow passage extending in the axial direction thereof, and the air flow passage extends through at least the high end, i.e., the left end in fig. 16, of the fastener 701. Cooling air can enter the air flow channel and flow out from the high end of the fastener 701, as shown in fig. 16, the flowing cooling air can flow to the high end of the heat-sink type permanent magnet pole fastening structure (specifically, the heat-sink type batten 20) and can flow out from the gap between the permanent magnet pole 40 and the iron core 70. As shown in fig. 11, a condensing section 20-1 can be arranged at the high end 20e of the pressing bar position, the material of the condensing section 20-1 has high thermal conductivity and thermal diffusivity, the outer surface has high infrared radiation emissivity, and a coating with high thermal conductivity can be coated on the condensing section, so that the gaseous medium can be rapidly condensed at the high end 20e of the pressing bar position, and the purposes of efficient cooling and gas-liquid reciprocating circulation are achieved.

Of course, no matter whether the motor shaft system has an elevation angle, cooling air flow can be conveyed to the heat sink type pressing strip 20, so that medium cooling, reciprocating heat absorption and cyclic utilization can be better completed. It is understood that a heat sink may not be provided, so that the heat absorbing and dissipating capacity of the heat sink beads 20 is limited.

The cooling source for providing the cooling air flow according to the present embodiment may adopt a vortex separator 311, the vortex separator 311 is capable of providing the cooling air flow, and the following will describe the principle of the vortex separator 311 in detail:

as shown in fig. 18 and 19, fig. 18 is a basic structure of the vortex separator 311 in fig. 16 and a schematic diagram of the total temperature separation operation of the air flow; fig. 19 is a flow-through cross-sectional view of the flow passage of the nozzle 3112 of fig. 18.

In the figure, the vortex separator 311, which can be used as a heat sink and a heat source, includes a spray pipe 3112 and a vortex separation pipe 3111, the spray pipe 3112 is connected to a side wall of the vortex separation pipe 3111, a portion of an inner cavity of the vortex separation pipe 3111 facing the spray pipe 3112 forms a vortex chamber 3111a, one end (left end in fig. 18) of the vortex chamber 3111a is a cold end pipe 3111c, the other end (right end in fig. 18) is a hot end pipe 3111b, an outlet of the cold end pipe 3111c is a cold end 3111d for outputting a cold air flow, an outlet of the hot end pipe 3111b is a hot end 3111e for outputting a hot air flow, an end plate 3111a1 at one end of the vortex chamber 3111a is provided with a through hole, which is defined as a cold end orifice plate, and the cold end pipe 3111c is connected to the through hole, as shown in fig. 18, the cold end pipe 3111c is a thin. The vortex chamber 3111a and the hot end pipe section 3111b are equal diameter pipe sections, and they can be integrated or separated, so that the integrated arrangement is simpler.

The nozzle 3112 of the vortex separator 311, which carries a heat source and a cold source, is an energy conversion member for converting pressure energy of the compressed gas into kinetic energy carried by the high-speed gas flow, and the nozzle 3112 may include an inlet section, a main body section, and an outlet section, and the outlet section is provided with a nozzle for spraying the gas flow. The air flow can form a spiral air flow after passing through the spray pipe 3112, as shown in fig. 19, a swirl plate is arranged inside the spray pipe 3112, that is, the outlet section of the spray pipe 3112 is a volute, the air flow can form a spiral air flow output after entering the spray pipe 3112, the spray pipe 3112 requires a tangential communication with the vortex chamber 3111a, that is, the spiral air flow sprayed from the nozzle is screwed into the vortex separation pipe 3111 along the tangential direction of the vortex separation pipe 3111. The volute can distribute the airflow uniformly to the nozzle of the outlet section of the nozzle 3112, and energy loss is reduced as much as possible, and the airflow flow on the inner circle of the volute is guaranteed to be axisymmetric.

Because of the smaller cross-sectional area of the cold end segment 3111c, the resistance to the helical flow entering the vortex chamber 3111a is greater at the orifice of the cold end 3111d and the flow tangentially swirling into the vortex separator 3111 flows toward the opposite hot end segment 3111 b. Here, the sectional area of the hot end pipe segment 3111b may be equal to or greater than that of the vortex chamber 3111a to ensure that the helical flow will flow in the direction of the hot end pipe segment 3111 b.

A valve with a conical surface is further arranged in the hot end pipe section 3111b, specifically, as shown in fig. 18, a conical throttle 3113 is arranged, the conical end of the throttle 3113 is oriented in the direction opposite to the flow direction of the spiral airflow, in fig. 18, the spiral airflow enters the vortex separation pipe 3111 from the nozzle 3112 and then flows spirally from left to right, when flowing to the throttle 3113, the external airflow of the spiral airflow can flow out of the valve, namely, flows out along the annular gap between the throttle 3113 and the vortex separation pipe 3111 and is heated to be hot airflow, as shown in fig. 18, the hot airflow flows out of the hot end 3111e of the hot end pipe section 3111 b.

The middle air flow of the spiral air flow contacts the throttle 3113, and flows in a reverse swirling manner after colliding with and guiding the conical surface of the throttle 3113 to form a backflow air flow, and the backflow air flow is gradually cooled in the flowing process, so that the temperature of the cooling air flow can be greatly reduced, and can be reduced to-50-DEG C. The outer airflow and the middle airflow are relative to the center line of the spiral airflow, the spiral airflow close to the center line is the middle airflow, and the airflow far away from the center line and close to the outermost side in the radial direction of the spiral airflow is the outer airflow. To ensure the spiral flow of air to the hot end section 3111b and the back flow to form hot and cold air flows, a throttle 3113 may be provided at the end of the hot end section 3111 b.

Since the spiral air flow is required to form a spiral air flow flowing in the opposite direction after passing through the valve, the conical throttle 3113 is provided, and the valve may have a conical surface within a certain range from the formation of the spiral air flow, for example, the valve may have a circular truncated cone shape (i.e., a section of the valve having no conical tip but a conical shape), or a half cone cut open in the axial direction. It will be appreciated that in order to better create the choking effect and to better direct the back-streaming helical flow, it is preferred to provide the valve with a full cone shape as shown in figure 18. In addition, the axis of the conical throttle 3113 coincides with the axis of the cold-end segment 3111c, so that the spiral airflow flowing back spirals towards the cold-end segment 3111c, which facilitates the precession of the airflow and reduces energy loss.

It can be seen that the iron core 70 of the electromagnetic device carries the vortex separator 311 of the cold source, which can generate the separation effect of separating the temperature of the same air flow to obtain two air flows, i.e. cold air flow and hot air flow, and the two air flows have very different temperature levels. The vortex separator 311 is developed based on the inspired phenomenon of tornado.

Tornado is a strong cyclone phenomenon which is generated in nature under specific atmospheric conditions, and ocean vortexes which vertically propagate from the water surface to the sea bottom are also generated in oceans under specific conditions. The airflow structure of a typical tornado shows that the center of the tornado is a funnel-shaped or trumpet-shaped pointed cone. The cone is a cyclone convergence area, the rotating direction of the cone is the same as that of the rising hot airflow filled with dust at the periphery, but the axial flowing direction of the airflow in the central cone is opposite to that of the rising airflow at the periphery, and the downward airflow is presented. The actual tracking measurement in natural environment can reach 17 m/s of the descending flow velocity of the cold air flow of a central cone of the tornado. When the cone tip of the central cone is touched and diffused, the tornado is rapidly strengthened, and the cone tip disappears to become a truncated cone. When the peripheral hot air flow rises while rotating and reaches the bottom surface of the upper cold cloud layer or the stratosphere, the hot air flow can immediately present bell mouth type horizontal rotation emission and divergence, change the rotation direction and reversely rotate and throw out. The air rotates around the axis of the tornado rapidly, and is attracted by the extremely reduced air pressure in the center of the tornado, in the thin layer of air which is tens of meters thick near the ground, the air flow is sucked into the bottom of the vortex from all directions, and then becomes the vortex which rotates upwards at high speed around the axis, so the wind in the tornado is always cyclone, the air pressure in the center is ten percent lower than the ambient air pressure, generally can be as low as 400hPa, and can be as low as 200 hPa. The tornado has a great sucking function, can suck seawater or lake water away from the sea surface or the lake surface to form a water column, and then is connected with the cloud, commonly called as 'dragon water taking'.

Energy sources of tornado: one is the heat energy of the peripheral airflow of the tornado, and the other is the vacuum energy of the low-pressure area of the vortex core. The interaction between the high-temperature gas of the peripheral airflow of the tornado and the tornado leads the heat energy to be converted into the rotational kinetic energy, and the mechanism is explained by the Crocco theorem. The Crocco theorem is derived in the fluid vortical field based on the first law of thermodynamics of conservation of energy. The theorem quantitatively expresses the relation between the gradient of thermodynamic enthalpy and the gradient of entropy in the vortex field and the vortex rotation strength. The temperature difference and the up-down convection in the atmosphere are the precondition for the formation of the tornado vortex, and the energy for enhancing the tornado vortex comes from the ambient heat energy. The gradient of thermodynamic enthalpy formed by the ascending hot air flow at the periphery of the tornado and the descending cold air flow at the center of the vortex becomes a key factor for converting atmospheric heat energy into vortex kinetic energy. After the tornado reaches a certain intensity by means of heat energy, further strengthening needs to rely on vacuum energy in the low-pressure area of the vortex core. The lower cone in the center of the tornado rotates in the same direction with the peripheral airflow. The air flow in the cone descends in a rotating way and gathers towards the center. When the centripetal acceleration exceeds a certain critical value, the radial aggregation process generates an accelerating rotation effect on the radial peripheral airflow through viscous diffusion under the action of the Coriolis force.

That is, the total temperature of the tornado is separated, the vortex separator 311 provided in this embodiment is similar to the tornado, and the nozzle 3112 is arranged to form the incoming compressed air into a spiral air flow, which can be regarded as the spiral flow of the small-scale tornado, so that the total temperature separation of the tornado can be simulated in the vortex separation tube 3111, and then the required hot air flow and the cold air flow are formed.

The above is a mechanism of this embodiment that is pursued from the natural world, and the following description is made on the principle of the temperature separation effect of the vortex separator 311.

Referring to fig. 20-21, fig. 20 is a schematic view of the internal flow field and thermal energy transfer within the components of the vortex separator 311 of fig. 18; FIG. 21 is a schematic diagram comparing free and forced vortices.

According to the law of conservation of energy, the sum of the energy of the cold and hot gas flows out of the vortex separator 3111 should be equal to the energy of the compressed gas entering the nozzle 3112 of the vortex separator 311 (provided that the vortex separator 311 is well insulated). Thus, there must be a process of energy redistribution in the vortex separator 311, with a portion of the energy being transferred from the cooling gas stream to the hot gas stream.

First, compressed gas, hereinafter referred to as high-pressure gas, is supplied to the nozzle 3112, a compressor 312 may be provided, the compressed gas supplied from the compressor 312, and an air filter may be provided at an inlet of the compressor 312 in order to prevent the supplied cooling gas flow from affecting the internal environment of the core 70.

The flow of compressed gas expands and accelerates in the nozzle 3112 of the vortex separator 311, and the velocity may approach sonic velocity when entering the vortex chamber 3111a of the vortex separator 3111, and may exceed sonic velocity if a convergent-divergent nozzle 3112 is used. Since the air stream rapidly expands through the nozzle 3112, which can be considered approximately as an adiabatic process, the flow velocity of the air stream at the outlet nozzle of the nozzle 3112 is very high, and its corresponding thermodynamic temperature will be much lower than the temperature at the inlet of the nozzle 3112, i.e., a controlled temperature reduction.

When the air flow enters the vortex chamber 3111a of the vortex separation tube 3111 tangentially, it continues to make spiral motion along the inner wall of the vortex chamber 3111a to form a high-speed rotating air flow, and when the air flow just exits the nozzle 3112, V ═ const or ω · r ═ const exists, where V is the tangential velocity of the air flow and ω is the angular velocity, and such rotation is also called free vortex, as shown in fig. 21, which shows the difference between the tangential velocity and the angular velocity of the free vortex and the forced vortex. The movement of the gas flow in the vortex chamber can be regarded as moving along the Archimedes spiral. The cooling air flow and hot air flow formation process are analyzed below.

Formation of a hot gas flow: since the flow of the air flow just exiting the nozzle 3112 is free vortex, the angular velocity has a gradient along the radial direction, which causes friction between radial layers of the air flow, so that the angular velocity of the outer air flow of the spiral air flow gradually increases, while the angular velocity of the middle air flow of the spiral air flow gradually decreases, but since the flow is fast and the path is short, the spiral air flow does not reach a complete forced vortex and develops toward the central portion thereof, the outer air flow of the spiral air flow moves along a spiral in the hot end pipe section 3111b, and has both rotational motion and axial motion, and during the movement, the outer air flow rubs against the inner wall of the hot end pipe section 3111b, the velocity of the outer air flow becomes lower and lower, the temperature gradually increases, and finally flows out from the annular gap between the throttle 3113 and the hot end pipe section 3111 b. By adjusting the gap between the orifice 3113 and the hot end section 3111b, the ratio of cold to hot gas flow can be adjusted.

Formation of cold air flow: the gas flow just exiting the nozzle 3112 is free vortex, and is blocked by the orifice of the cold end 3111d of the cold end section 3111c, and flows close to the inner wall of the hot end section 3111b to the throttle 3113 under the action of centrifugal force. During the flow, the axial velocity of the swirling flow moving to a certain position in the axial direction is already close to zero due to the gradual dissipation of the axial velocity, which can be defined as a stagnation point. At this time, due to the accumulation of the middle air flow at the stagnation point, the pressure is constantly increased, the pressure at the stagnation point is higher than the pressure at the cold end 3111d at the outlet of the cold end pipe section 3111c, and a reverse axial motion is generated in the central area of the hot end pipe section 3111b, that is, a backflow air flow appears from the stagnation point, and the temperature is gradually reduced to form a cold air flow, that is, the temperature is reduced for the second time. At the stagnation point, the total temperature of the outer airflow is higher than the total temperature of the middle airflow. During the movement of the backward flow toward the cold end 3111c, the spiral gas flow continuously having the outer layer is diverted and converged, so that the flow is gradually increased, and the backward flow reaches the maximum when reaching the cold end 3111d orifice plate.

As shown in fig. 20, in the same flow passage section of the vortex separation tube 3111, the outermost static flow pressure of the outer stream is the largest and the centermost static flow pressure of the middle stream on the central axis is the smallest, and in the section near the nozzle of the nozzle 3112, the ratio of the largest static pressure to the smallest static pressure is the largest, which may reach 1.5-2, and the static temperature is the highest at the wall surface of the vortex separation tube 3111 and the lowest on the central axis.

The tangential velocity of the gas flow at any point is dominant in any flow channel cross section. Near the nozzle of the nozzle 3112, both the radial velocity and the axial velocity of the gas flow reach a maximum and gradually decrease in the respective directions.

As mentioned above, the air flow leaving the nozzle enters the vortex separation pipe 3111 tangentially, and is divided into two regions, and the external air flow rotates tangentially along the inner wall of the vortex separation pipe 3111 and tends to the outlet of the hot end 3111e of the hot end pipe section 3111b, i.e. the external air flow in the outer region forms a free vortex. The middle air flow flows back from the position where the throttle 3113 is provided, is driven by the surrounding free vortex, and then, by friction, the inner region (middle air flow) where the air flow rotates like a rigid body is converted into or close to the forced vortex.

The boundary between the outer and middle regions, i.e. the outer and middle portions, depends on the cooling flow rate, and the boundary between the hot and cold flows can be seen in fig. 20. The boundary interface is generally located within a range of 0.65-0.75R from the central axis, i.e., the flow range of the central gas flow in the radial direction, R being the radius of the vortex separation tube 3111, throughout the length of the vortex separation tube 3111. The axial flow of the external air flow from the nozzle of the nozzle 3112 to the throttle 3113 is in the range between the radii 0.65-1R, i.e., the flow range of the external air flow in the radial direction. In the inner region, the middle stream flows in the opposite direction, beginning at throttle 3113.

The central stream temperature of the middle stream is highest at throttle 3113, and the reverse stream is gradually cooled and lowest at the cold end 3111d orifice. The greatest temperature differential occurs in the direction of the central axis, with the highest temperature at the central axis corresponding to the throttle 3113 and the lowest temperature at the centerline axis corresponding to the cold end 3111d orifice plate. For the middle stream of the inner layer, i.e. the cold stream, its static temperature is lowest at the central axis and highest at the interface with the outer stream.

In any cross section of the flow passage of the vortex separation tube 3111, the total temperature is highest near the inner wall surface of the vortex separation tube 3111 and is lowest on the central axis. The difference between the wall temperature and the center axis temperature of the vortex separation pipe 3111 reaches the maximum value at the flow passage section at the nozzle.

With respect to the total temperature separation effect of the vortex separator 311, reference may be made to fig. 22, and fig. 22 is a schematic diagram of the thermodynamic temperature-entropy (T-S) based total temperature separation operation process inside the vortex separator 311 in fig. 18. As can be seen in fig. 22, the vortex separator 311 does provide temperature separation of the compressed gas stream entering the nozzle 3112.

In fig. 22, point 4 is a state before gas compression, i.e., before entering the compressor 312. Points 4-5 are the isentropic compression of the gas stream. Point 5-1 is the isobaric cooling process of the compressed gas. Point 1 shows the compressed gas before it enters the nozzle 3112 of the vortex separator 311, which has been expanded adiabatically to p under ideal conditions₂Pressure, with consequent temperature reduction to T_sI.e., the point 2a state. Point 2 is the cold gas flow state from the vortex tube, the temperature of which is T_c. Point 3 is the separated hot gas flow regime, the temperature of which is T_h. Points 1-2 and 1-3 are the separation process of the cold and hot air flows. 3-3' is the throttling process of hot air flow through the throttling piece 3113, and the front-to-back ratio enthalpy value of throttling is unchanged.

Because of the entire operation, isentropic expansion of the gas stream in the nozzle 3112 is not possible. There is some loss of kinetic energy exchange between the inner and outer gases in the vortex chamber 3111a and the heat transfer to the center in the vortex chamber 3111a causes the flow to deviate from adiabatic expansion in point 1-2 processes, resulting in a temperature T of the cold flow exiting the vortex separation tube 3111_cTotal higher than the cold gas flow temperature T under adiabatic expansion_s。

Turning again to the cooling and heating effects of the vortex separator 311 in the embodiments described above.

The vortex separation pipe 3111 is set to a temperature T during operation₁Is separated into a gas with a temperature T_cCold air flow and temperature T_hThe hot gas flow of (2). Therefore, Δ T_c＝T₁-T_cCooling effect, Δ T, called vortex separator 3111_h＝T_h-T₁Known as the heating effect of vortex tubes. Will be Delta T_s＝T₁-T_sDefined as the isentropic expansion effect, to mark the theoretical cooling effect of the vortex separation tube 3111 accordingly, the effectiveness of the refrigeration in the vortex separation tube 3111 is indicated by cooling efficiency η_cRepresents, i.e.:

wherein p is₁-vortex separator 311 inlet gas flow pressure; p is a radical of₂The pressure of the gas stream after expansion into the vortex chamber 3111a in the nozzle 3112; k-the adiabatic index of a gas such as air.

In addition, during the operation of the vortex separator 311, there is a balance between the flow rate and the heat, as follows:

if with q_m1、q_mc、q_mhQ represents the flow rates of the high-velocity gas flow entering the vortex separation tube 3111, the cold gas flow at the cold end 3111d and the hot gas flow at the hot end 3111e, respectively_m1＝q_mc+q_mh。

If with h₁、h_cAnd h_h(KJ/Kg) represents their specific enthalpies, respectively, and q is the kinetic energy of the gas when it is discharged, neglecting_m1h₁＝q_mch_c+q_mhh_h。

Flow ratio of cold air

The corresponding relation h ═ C between gas enthalpy and temperature_pT

Obtaining: t is₁＝μ_cT_c+(1-μ_c)T_hT

The cooling capacity of the vortex separator 3111 can also be obtained as follows:

refrigerating capacity Q of vortex separation pipe 3111₀(kW) is Q₀＝q_mcc_p(T₁-T_c)＝μ_cq_m1c_pΔT_c

The refrigerating capacity per kilogram of cold air flow is

If the specific refrigerating capacity q 'is specified for each kilogram of high-pressure gas'₀Can be expressed as:

please see the heating quantity Q of the vortex separation pipe 3111_h(kW)：

Q_h＝q_mhc_p(T_h-T₁)＝(1-μ_c)q_m1c_pΔT_h

The heat production per kilogram of hot gas flow is

If for each kilogram of high pressure gas, the specific heat production can be expressed as:

cooling effect Δ T of vortex separator 3111_c＝T₁-T_cAnd unit refrigerating capacity q₀Is related to the cold gas flow component mu_cInlet working pressure p of nozzle 3112₁Moisture content in the gas stream.

Component μ of cold air flow_cWhen the component value of the cold airflow changes, Δ T_cAnd q is_oAll vary accordingly and are in mu_cThe maximum value exists in the range of 0 to 1. When mu is_cWhen 0.3 to 0.35, Δ T_cHas a maximum value; when mu is_cWhen q is 0.6 to 0.7, q is_oA maximum value is reached. At the same time, the heating effect is also dependent on μ_cChange when μ changes_cAt time of increase Δ T_hAre continuously increasing and have no limit.

Inlet working pressure p of nozzle 3112₁When p is₁At increasing time,. DELTA.T_cAnd q is_oAre all increasing. But at an increase of Δ T_cMaximum value of (d) to μ_cReduced directional movement, q_oMaximum value of (d) is to mu_cThe increasing direction.

When the gas is wet, the water vapor in the cold air flow is condensed to release heat, so that the refrigeration temperature is increased, and the cooling efficiency is reduced; the temperature rise of hot air flow is reduced, and the heating effect is reduced.

Having described the principle of the vortex separator 311 in detail above, the vortex separator 311 may separate a hot air stream and a cold air stream, and the cold air stream may be used as a cooling air stream for an input air stream channel to be delivered to the high end of the position of the sunken permanent magnet pole fastening structure, thereby condensing the phase change medium 20' after the gaseous state.

From the above principle analysis, it can be seen that the vortex separator 311 has a simple structure, can generate a cooling airflow by its own structure, and has a simple and compact structure, and does not occupy too much space, thereby facilitating arrangement in a motor. In fig. 16, the eddy current separator 311 is mounted in the cavity of the core 70, specifically, on the core holder 60 in the cavity, and the core holder 60 is used to support the core 70.

At this time, a side wall passage may be further provided on the core 70, the side wall passage penetrating through peripheral walls of the core 70 and the core holder 60 to communicate an air flow passage of the fastener 701 with the vortex separator 311 at the core holder 60. As can be seen in fig. 16, 17, the sidewall channels may extend radially.

Referring back to fig. 16, and as will be appreciated in conjunction with fig. 23, fig. 23 is a cross-sectional view of the fastener 701 of fig. 16, further illustrating a portion of the passageway provided in the core holder 60.

The fastener 701 is further provided with a recovery passage 701b penetrating the lower end of the position of the fastener 701, and a feed passage penetrating the peripheral walls of the core 70 and the core holder 60. After the cooling airflow flows out of the airflow channel, the cooling airflow can flow from the gap between the permanent magnet pole 40 and the core 70 to the space at the other end (the lower end), and then can enter the recovery channel 701b at the other end, and flow back to the vortex separator 311 through the delivery channel, and specifically can flow back to the compressor 312 of the vortex separator 311 again for recycling, as shown in fig. 16, a recovery device 313 is further provided to pretreat the recovered airflow, and deliver the airflow to the compressor.

As shown in fig. 16, the fastening member 701 is provided with a passage penetrating in the axial direction, and the passage separates the air flow passage and the recovery passage 701 b; there are also provided side wall passages extending through the peripheral wall of the core 70 and the peripheral wall of the core support 60, the side wall passages separating an inlet passage 601 for forming a cooling air flow and an outlet passage 602 for recovering the air flow. This form facilitates processing. Of course, it is also possible that the air flow passage and recovery passage 701b, the inlet passage 601 and the outlet passage 602 are separately opened. Further, the outlet passage 602 and the recovery passage 701b may not be provided, and the cooling air flow may be discharged to the outside from the gap of the motor after cooling and heat exchange, or may be sucked and discharged by a device inside or outside the motor.

In addition, for the air flow channel, a first channel 701a and a second channel 701c may be separately provided to introduce the cooling air flow and the hot air flow, which is equivalent to that in fig. 23, an L-shaped tube is inserted into the inlet channel 601 of the air flow channel and the side wall channel, the lumen of the transverse section of the L-shaped tube forms the first channel 701a, and the gap between the transverse section and the inner wall of the air flow channel forms the second channel 701 c. The vertical pipe section of the L-shaped pipe is used for cooling airflow to enter in the inlet channel 601 of the side wall channel, and the gap between the vertical pipe section and the inlet channel 601 is used for heating airflow to enter, so that the drying effect can be achieved when hot airflow is introduced. Of course, it is also possible that the first passage 701a is introduced with hot air, and the second passage 701c is introduced with cooling air, and it is possible to separately provide the first passage 701a and the second passage 701c by other methods, or to form two passages by using a partition plate for separation.

With this arrangement, after the air flow is ejected from one end of the air flow passage, the heat exchange function is completed near the one end, and after the cooling and/or drying function is realized, the air flow is accumulated to some extent, and flows into the other end of the fastening member 701 from the gap between the core 70 and the permanent magnet pole 40, and the air flow can continue to perform heat exchange at the other end, and then flows into the recovery passage 701b at the other end of the fastening member 701 of the core 70, and then flows out from the side wall passage. The discharged air flow can be recycled, for example, the cooled air flow can be used for drying after heat exchange and temperature rise, and can be conveyed to the compressor 312 again, or can be conveyed to other positions needing drying. At this time, the eddy current separator 311 is not only a device for generating cooling airflow, but also forms a transportation channel (a channel is formed on the fastening member 701) extending into the core 70, thereby forming a novel motor structure having a cold source.

As can be appreciated with continued reference to fig. 24 and 25, fig. 24 is a simplified schematic illustration of a plurality of stator cores with axial fasteners 701 spatially parallel and circumferentially distributed; FIG. 25 is a schematic view of vortex separator 311 delivering cooling airflow in multiple directions.

As shown in fig. 24, the core 70 is tightened in the axial direction by the plurality of fastening members 701, and correspondingly, in order to more uniformly deliver the cooling air flow, so that the cooling air flow can be obtained at the high ends 20e of the bead positions in the vicinity of all the fastening members 701, as shown in fig. 25, the vortex separator 311 may be provided with a plurality of output ducts for the cooling air flow corresponding to the air flow passages delivered to the plurality of fastening members 701.

The embodiment of the present scheme further provides a wind generating set, including generator 100, a cabin and wind turbine 300, where generator 100 is the motor described in any of the above embodiments, and beneficial effects are the same and are not described again.

Referring to fig. 26, fig. 26 is a schematic view of a wind turbine generator set according to an embodiment of the present invention. The wind generating set comprises a generator 100, a wind turbine 300, a hub 200 and a nacelle 800, wherein the nacelle 800 is arranged at the top end of a tower 700.

In the above embodiment, a cold source may be provided to cool the high end of the position of the heat sink type permanent magnet magnetic pole fastening structure, so that the gaseous medium after phase change is condensed, thereby performing a circulating cooling process. The heat sink may be disposed within a nacelle of the wind turbine 100. In fig. 26, a ventilator 600 is shown, an air filter 400 is connected to an inlet of the ventilator 600 to filter the air flow to meet the air flow requirement inside the generator 100, and the ventilator 600 is further provided with a power source driving motor 500. The outlet of the ventilator 600 is connected to the airflow transportation pipeline 900 to convey the relatively cooled airflow inside the nacelle 800 or outside the nacelle 800 to the inside of the generator 100 and to align with the upper end 20e of the bead position of the heat sink bead 20, so as to perform the cooling function. That is, the cooling source may be an open cooling system formed by a ventilator 600 communicated with the natural environment.

It is to be understood that the ventilator shown in fig. 26 may be a surface heat exchanger, and the cooling airflow generated by the surface heat exchanger may be sent to the generator 100, or may be sent through the airflow transport line. The surface heat exchanger may be, for example, a dividing wall type heat exchanger, and may extract a hot air flow inside the generator 100, and a cooling air flow obtained after heat exchange by the dividing wall type heat exchanger is conveyed to the inside of the generator 100 to cool the high end 20e of the heat sink type bead position. The surface heat exchanger is also used for exchanging heat between air flow of natural environment and internal hot air flow to form cooling air flow, a ventilator needs to be configured to form circulation, and a cold source at the moment is a closed cooling system comprising the ventilator and the surface heat exchanger which are connected in series.

Of course, when the cooling source is the vortex separator 311, it may be disposed in the nacelle, and the cooling airflow is directly conveyed to the inside of the generator 100, or through the airflow transportation pipeline 900 described above is also possible.

In the above embodiments, the description is mainly given of the outer rotor motor as an example, and it is understood that the present invention is also applicable to the inner rotor motor. When the heat sink type permanent magnet magnetic pole fastening structure is the heat sink type pressing strip 20, the definitions of the inner side and the outer side of the heat sink type pressing strip 20 are just opposite, and other working principles are the same and are not described in detail.

In addition, the heat sink type pressing bar 20 is taken as an example of the heat sink type permanent magnet pole fastening structure in the above embodiment, and it can be known that other types of heat sink type permanent magnet pole fastening structures can achieve the purpose of improving the heat dissipation effect by injecting the phase change medium 20'. For example, a heat sink type permanent magnet pole fastening structure mentioned in the background art is a permanent magnet pole protection box for clamping and covering a permanent magnet pole to fix the permanent magnet pole, according to the principle of the present invention, the permanent magnet pole protection box can also be set to have a cavity structure, and phase change media are injected into the interior of the cavity structure, so as to achieve the purpose of the present invention.

It can be understood that the sinkers pm magnetic pole fastening structure enables the motor with the structure to have the above beneficial effects, and all products including the motor also have the same technical effects. Except that the wind driven generator set can adopt the motor, other products can also use the motor, for example, a permanent magnet motor can be arranged on an electric automobile, and the permanent magnet motor can be the motor with the heat sink type permanent magnet pole fastening structure in any embodiment.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that it is obvious to those skilled in the art that various modifications and improvements can be made without departing from the principle of the present invention, and these modifications and improvements should also be considered as the protection scope of the present invention.

Claims

1. The heat sink type permanent magnetic pole fastening structure is characterized by comprising a cavity, wherein a phase change medium (20 ') is injected into the cavity, the phase change medium (20 ') can absorb heat, and the phase change medium (20 ') absorbs heat and generates phase change after the temperature rises to a certain temperature; the heat sink type permanent magnetic pole fastening structure is a heat sink type pressing strip (20) positioned between adjacent permanent magnetic poles (40), or the heat sink type permanent magnetic pole fastening structure is a permanent magnetic pole protection box which clamps and covers the permanent magnetic poles (40); a reinforcing part is arranged in a cavity of the heat sink type pressing bar (20), and two ends of the reinforcing part are respectively connected with two sides of the heat sink type permanent magnetic pole fastening structure;

the reinforcing part is a reinforcing support beam (207), and a plurality of reinforcing support beams (207) arranged along the length direction of the heat sink type pressing strip (20) are arranged in the heat sink type pressing strip (20);

or the reinforcing part is a screening plate (208) provided with a plurality of screen holes, the screening plate (208) divides the cavity into an inner cavity (202) and an outer cavity (201), and when the rotor provided with the permanent magnet magnetic pole (40) rotates, the phase change medium (20') flows between the inner cavity (202) and the outer cavity (201) through the screen holes and can be separated from gas and liquid.

2. The structure of claim 1, wherein the screening plate (208) comprises a screening tube (208a), the screening tube (208a) extending through the screening plate (208) and having two ends protruding beyond the surface of the screening plate (208); the screening tube (208a) is inserted into the screening holes, or the screening tube (208a) is integrally formed on the screening plate (208), and the tube cavities of the screening tube (208a) form the screening holes.

3. The structure of claim 1, wherein the heat sink permanent magnet pole fastening structure has a condensation section (20-1) at one end, the condensation section (20-1) is made of a material with high thermal conductivity, high thermal diffusivity, high emissivity of infrared radiation on its outer surface, and/or the condensation section (20-1) has a coating with high thermal conductivity on its outer surface.

4. A heat sink permanent magnet pole fastening structure as claimed in any of claims 1-3 wherein the heat sink permanent magnet pole fastening structure is provided with suction holes (205) to evacuate the internal cavity.

5. A heat sink permanent magnet pole fastening structure according to claim 4 wherein the heat sink permanent magnet pole fastening structure is provided with a seal (206) to seal the suction hole (205).

6. A heat-sink permanent magnet pole fastening structure according to any of claims 1-3 wherein the phase change medium (20') is a gas-liquid phase change medium, or a solid-liquid phase change medium.

7. The structure of claim 6, wherein the phase change medium (20') is any one of water, deionized water, a mixture of ionized water and ethylene glycol, a hydrated salt, a polyol, a polymer resin, and an ester acid.

8. Rotor, the rotor includes yoke (10) and permanent-magnet pole (40), permanent-magnet pole (40) pass through heat sink permanent-magnet pole fastening structure and fix in yoke (10), characterized by, the heat sink permanent-magnet pole fastening structure is the heat sink permanent-magnet pole fastening structure of any claim 1-7.

9. An electrical machine comprising a rotor and a stator, wherein the rotor is the rotor of claim 8.

10. The electric machine of claim 9, wherein the electric machine is further provided with a cold source capable of providing a cooling medium; the shafting of the motor is provided with an elevation angle, the heat sink type permanent magnetic pole fastening structure is correspondingly provided with a high position end and a low position end in a gravity field, and the cooling medium can cool the high position end of the heat sink type permanent magnetic pole fastening structure.

11. An electric machine as claimed in claim 10, characterized in that the heat sink is an eddy current separator (311).

12. An electric machine according to claim 11, characterized in that the electric machine comprises a core (70) and a fastening member (701) extending through the core (70) in the axial direction of the electric machine for tightening the core (70), the fastening member (701) is provided with an air flow channel extending in the axial direction thereof, and the air flow channel extends through a high end of the fastening member in the gravitational field, and the output of the eddy current separator (311) device generates a cooling air flow which can enter the air flow channel and flow out of the high end thereof to the high end of the sinkers pm pole fastening structure.

13. The electric machine of claim 12, wherein the electric machine is an outer rotor configuration; the motor comprises a core support (60), and the eddy current separator (311) is arranged at the core support (60); the motor is further provided with an inlet channel (601), and the inlet channel (601) penetrates through peripheral walls of the iron core (70) and the iron core bracket (60) to communicate the air flow channel with the vortex separator (311).

14. An electric machine as claimed in claim 13, characterized in that the vortex separator (311) is provided with a plurality of outlet ducts for the cooling air flow, corresponding to the air flow channels for feeding a plurality of the fasteners (701).

15. An electric machine according to claim 14, characterized in that the fastening member (701) is provided with a recovery passage (701b) extending through the lower end thereof and an outlet passage (602) extending through the peripheral walls of the core (70) and the core support (60), and that the cooling air flows out of the air flow passage and then flows back from the recovery passage (701b) and the outlet passage (602) to the vortex separator (311).

16. An electric machine as claimed in claim 15, characterized in that said fastening member (701) is provided with a passage passing through in an axial direction, said passage separating said air flow passage and said recovery passage (701 b); and a side wall channel penetrating through the peripheral walls of the iron core (70) and the iron core bracket (60) is further arranged, and the side wall channel is separated to form the inlet channel (601) and the outlet channel (602).

17. The machine according to claim 16, characterised in that the air flow channels are separated to form a first channel (701a) and a second channel (701c) into which a cooling medium and a heating medium can be fed, respectively.

18. Wind park comprising a generator (100), a nacelle (800) and a wind turbine (300), wherein the generator is an electrical machine according to any of claims 10-17.

19. Wind park according to claim 18, wherein said cold source is provided at said nacelle (800); the cold source is an eddy current separator (311), or an open cooling system formed by a ventilator (600) communicated with the natural environment, or a closed cooling system comprising a ventilator and a surface heat exchanger which are connected in series, and the generated cooling medium or cold airflow from the natural environment is conveyed to the generator (100) through an airflow conveying pipeline (900) and flows to the high end of the heat sink type permanent magnetic pole fastening structure.

20. An electric vehicle comprising an electric machine, characterized in that the electric machine is an electric machine according to any of claims 9-17.

21. A method of manufacturing a heat sink permanent magnet pole fastening structure, wherein the heat sink permanent magnet pole fastening structure is according to any one of claims 1 to 8, the method comprising: processing to form a heat sink type permanent magnetic pole fastening structure with a cavity, wherein the heat sink type permanent magnetic pole fastening structure is a heat sink type pressing strip (20) positioned between adjacent permanent magnetic poles (40), or the heat sink type permanent magnetic pole fastening structure is a permanent magnetic pole protection box for clamping and covering the permanent magnetic poles (40); under the condition that the temperature is higher than the normal temperature or close to the working temperature, the phase change medium (20 ') is injected into the cavity, the phase change medium (20 ') can absorb heat, and the phase change medium (20 ') absorbs heat and generates phase change after the temperature rises to a certain temperature.

22. Method for dissipating heat of an electric machine comprising a rotor and a stator, said rotor comprising a yoke (10) and permanent-magnet poles (40), characterized in that said method comprises:

-fixing the permanent magnet pole (40) to the magnet yoke (10) by means of a heat-sink permanent magnet pole fastening structure according to any of claims 1-8; the heat sink type permanent magnetic pole fastening structure is a heat sink type pressing strip (20) positioned between adjacent permanent magnetic poles (40), or the heat sink type permanent magnetic pole fastening structure is a permanent magnetic pole protection box which clamps and covers the permanent magnetic poles (40);

the heat sink type permanent magnet magnetic pole fastening structure is provided with a cavity, a phase change medium (20 ') is injected into the cavity, when the motor is heated, the phase change medium (20 ') can absorb heat, and the phase change medium (20 ') absorbs heat and generates phase change after the temperature rises to a certain temperature so as to dissipate heat of the motor.

23. The method for reducing the torsional vibration of the shafting of the wind generating set comprises a rotor and a stator, wherein the rotor comprises a magnet yoke (10) and a permanent magnet pole (40), and is characterized in that the method for reducing the torsional vibration of the shafting of the wind generating set comprises the following steps:

the heat sink type permanent magnetic pole fastening structure is provided with a cavity, and a phase change medium (20') is injected into the cavity; regulating the phase change temperature of the phase change medium (20') so as to keep the magnetic field temperature of the motor within the working temperature range;

24. The method for reducing torsional vibration of a shafting of a wind turbine generator system according to claim 23, wherein the step of regulating the phase change temperature of the phase change medium (20') comprises:

adding a mixture into the phase change medium (20 ') to regulate the phase change temperature of the phase change medium (20'); and/or adjusting the vacuum degree in the cavity and regulating and controlling the phase change temperature of the phase change medium (20').