WO2016184406A1

WO2016184406A1 - Ultra-high speed motor

Info

Publication number: WO2016184406A1
Application number: PCT/CN2016/082702
Authority: WO
Inventors: 罗立峰
Original assignee: 罗立峰
Priority date: 2015-05-19
Filing date: 2016-05-19
Publication date: 2016-11-24
Also published as: CN205858947U; CN205858948U; CN106026517B; CN105889313A; CN205858479U; WO2016184412A1; TWI694210B; WO2016184404A1; TWI704751B; TW201706516A; CN105889313B; CN205864143U; CN106014641A; CN106014641B; CN205864174U; CN105889314A; CN105888818A; CN105889314B; WO2016184414A1; CN105889097A

Abstract

An ultra-high speed motor, comprising a motor housing (1), a rotor (2), a stator (3), two radial bearings (4), a thrust bearing (5), an inner shaft (6) and an outer shaft (7), the radial bearings being groove-type dynamic pressure gas radial bearings, the thrust bearing being a mixed-type dynamic pressure gas thrust bearing, the rotor being sleeved at a central portion of the inner shaft, the two radial bearings being respectively sleeved on the outer shaft located at left and right ends of the rotor, the thrust bearing being sleeved on the outer shaft at the right end, and being located on an outer end side of a right end radial bearing (4b). The present structure implements an ultra-high speed stable operation in an air state, and with regard to identical power requirements, enables the size of the motor to be significantly reduced for miniaturisation.

Description

Ultra high speed motor

Technical field

The invention relates to an ultra-high speed motor and belongs to the technical field of high precision machinery.

Background technique

High-speed motors usually refer to motors with a speed exceeding 10,000 r/min. They have the following advantages: First, because of the high speed, the motor has a high power density, and the volume is much smaller than that of a normal motor, which can effectively save materials; The motives are connected, the traditional speed reduction mechanism is eliminated, the transmission efficiency is high, and the noise is small; the third is because the high-speed motor has a small moment of inertia, so the dynamic response is fast. However, with the continuous improvement of the power level and speed requirements of high-speed motors, ordinary mechanical ball bearings can no longer meet the requirements of high-power high-speed motors. Air-floating bearings have become a hot spot in industry and academia because of their small friction loss, high temperature stability, high reliability, low vibration, no need for lubricating oil, and no limitation on the size of the shaft. Used in aviation and aerospace.

At present, the existing air-floating bearings used in high-speed motors mainly include: tilting type, slot type and foil type. Although the tilting type air bearing has self-adjusting performance, it can be within a smaller air gap. Safe work, insensitive to thermal deformation, elastic deformation, etc., and the processing accuracy is easy to be guaranteed, but its bearing structure is more complicated, the installation process is complex, never suitable for industrial applications; although the foil type dynamic pressure gas radial bearing has The elastic support can make the bearing obtain a certain bearing capacity and the ability to mitigate the impact vibration. However, since the foil bearing is generally made of metal foil, not only the material manufacturing technology and the processing technology still have some problems, but also the damping of the bearing. The value can not be greatly improved, resulting in insufficient rigidity of the bearing, the critical speed of the bearing is low, and it is easy to be unstable or even stuck during high-speed operation; although the slot type dynamic pressure gas radial bearing has good stability, at high speed, Its static bearing capacity is larger than other types of bearings, but the current slotted dynamic gas radial bearing has high rigidity and is not good enough for impact resistance. Bearing capacity is not large enough to realize high-speed operation under a large load. Due to the above-mentioned various problems of the current air bearing technology, the existing high-speed motor still has the following problems: 1. The speed is still limited, and currently only up to 50,000 rpm can be achieved; 2. It cannot be operated for a long time: due to high speed operation The generated heat can not be effectively exported, so that the continuous working time can not be very long; 3, the stability of high-speed operation is not good, so the actual operating efficiency can not reach the ideal goal; 4, the structure is still more complex, larger, can not meet the current miniature Development requirements.

Summary of the invention

In view of the above problems in the prior art, it is an object of the present invention to provide an ultra-high speed motor that can operate stably.

In order to achieve the above object, the technical solution adopted by the present invention is as follows:

An ultra-high speed motor comprising a motor housing, a rotor, a stator, two radial bearings, a thrust bearing, and an inner shaft and an outer shaft; wherein the radial bearing is a slot type dynamic pressure gas path a bearing, comprising a bearing sleeve and a bearing inner sleeve; the thrust bearing is a hybrid dynamic pressure gas thrust bearing comprising two side discs and a middle disc sandwiched between the two side discs, at each side disc A foil-type elastic member is disposed between the middle plate and the middle plate; the rotor is sleeved in the middle of the inner shaft, and two radial bearings are respectively sleeved on the outer shafts at the left and right ends of the rotor, and the thrust bearing sleeve is sleeved On the outer shaft on the right end and on the outer end side of the right-hand radial bearing.

In one embodiment, the ultra high speed motor further includes a left radial bearing sleeve and a left bearing chamber end cover, the left bearing chamber end cover being coupled to the left radial bearing sleeve, the left radial bearing sleeve and The motor housings are connected.

As an embodiment, the ultra-high speed motor further includes a right radial bearing sleeve, a right bearing chamber end cover, a cooling fan and a fan housing, and the fan housing is connected to the right bearing chamber end cover, the right The bearing chamber end cover is connected to the right radial bearing sleeve, the right radial bearing sleeve is connected to the motor housing, and the cooling fan is sleeved on the inner shaft between the right bearing chamber end cover and the fan housing on.

Preferably, a plurality of open slots are defined in a peripheral side of the inner wall of the motor housing, and a plurality of vent holes are formed in an end surface of the motor housing, and the open slots communicate with the vent holes to facilitate gas introduction and derivation. On the one hand, it realizes rapid heat dissipation and exhaust, and on the other hand, it realizes air supply to the bearing chamber.

Preferably, a plurality of exhaust holes are formed on a circumferential side of the left bearing chamber end cover, and a plurality of air inlet holes are formed in an outer end surface of the fan housing.

Preferably, the outer circumferential surface and the both end surfaces of the bearing inner sleeve have a regular pattern of grooves.

In a further preferred embodiment, the groove pattern of one end surface of the bearing inner sleeve is mirror-symmetrical with the groove pattern of the other end surface, and the axial contour line of the groove pattern of the outer circumferential surface and the groove pattern of the both end surfaces The radial contour lines form a one-to-one correspondence and intersect each other.

In a further preferred embodiment, the axial high line in the groove pattern of the outer circumferential surface of the bearing inner sleeve corresponds to the radial high line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered. The axial median line in the groove pattern of the outer circumferential surface corresponds to the radial median line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered; the groove pattern of the outer circumferential surface The axial lower line in the middle corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.

Preferably, the matching gap between the bearing inner sleeve and the bearing outer sleeve is 0.003 to 0.008 mm.

Preferably, a stop ring is provided at both ends of the bearing housing.

Preferably, both end faces of the middle plate are provided with a regular pattern of groove patterns, and the groove pattern of one end face is mirror-symmetrical with the groove pattern of the other end face.

Preferably, the outer circumferential surface of the intermediate disk is also provided with a groove pattern, and the shape of the groove pattern of the outer circumferential surface is the same as the shape of the groove pattern on both end faces, and the groove pattern of the outer circumferential surface The axial contour line forms a one-to-one correspondence with the radial contour lines of the groove patterns on both end faces and intersects each other.

As a further preferred embodiment, the axial high line in the groove pattern of the outer circumferential surface of the middle disk corresponds to the radial high line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered; the outer circumference The axial median line in the groove pattern corresponds to the radial median line in the groove pattern on both end faces, and crosses each other before the end face is chamfered; the axis in the groove pattern of the outer circumferential surface The low-order line corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.

As a further preferred embodiment, a wear-resistant coating is provided on the mating surface of the foil-type elastic member that is fitted to the intermediate disk.

As a further preferred solution, the fitting gap between the foil-type elastic member and the middle plate is 0.003 to 0.008 mm.

As a further preferred aspect, at least one end of the foil-type elastic member is fixed to an inner end surface of the corresponding side disk.

As a further preferred embodiment, the foil-type elastic members on each of the side plates are plural and evenly distributed along the inner end faces of the side plates.

As a further preferred embodiment, the foil-type elastic member fixed to one side disk is mirror-symmetrical to the foil-shaped elastic member fixed to the other side disk.

As a further preferred aspect, a card slot for fixing the foil-type elastic member is provided on the inner end surface of the side disk.

As an embodiment, the foil-type elastic member is composed of a wave foil and a flat foil, and the curved convex top end of the wave foil is attached to the flat foil.

In another embodiment, the foil-type elastic member is composed of a wave foil and a flat foil, and the inter-wave arch transition bottom edge of the wave foil is in contact with the flat foil.

As a further embodiment, the foil-type elastic member is composed of two flat foils.

The above-mentioned groove patterns are all impeller shapes.

The above-mentioned foil-type elastic member is preferably subjected to surface heat treatment.

Preferably, the rotor comprises a rotor base, a magnetic steel and a magnetic steel protective sleeve, the rotor base is sleeved on the inner shaft, the magnetic steel sleeve is disposed at a central portion of the rotor base, and the magnetic steel protective sleeve is sleeved On the magnetic steel.

Preferably, the stator comprises a core and a winding, the core being fixed on an inner wall of a motor housing located above the rotor, the winding being disposed on the core.

Preferably, the core comprises a stator lamination formed by stacking a plurality of punching sheets and an end platen fixed to both sides of the stator lamination.

In a further preferred embodiment, the punching piece has a circular shape, and a plurality of cup-shaped perforations are arranged at intervals in the annular portion, the mouth of the perforated cup is closed, and the bottom of the cup is open.

Preferably, the winding is a three-phase star connection, the center line is not led out, and only three ends of A, B, and C are drawn.

As a further preferred solution, each phase winding is 2 coils, and each coil is continuously wound from an enamelled copper wire.

Compared with the prior art, the present invention has the following beneficial effects:

The motor provided by the invention is a lubricant of a bearing, so that it has not only pollution-free, low friction loss, long service time, wide application range, energy saving and environmental protection, but also has the advantages of good heat dissipation. It can guarantee stable operation for a long time; in particular, because the air bearing of the structure can achieve ultra-high-speed stable operation under air-floating state (tested, the limit speed can reach 100,000-450,000 rpm), so the same power requirement The invention can significantly reduce the volume of the motor to achieve miniaturization, has the advantages of small occupied space and convenient use, and has important value for promoting the development of miniaturization high-tech, and has significant progress compared with the prior art.

DRAWINGS

1 is a schematic cross-sectional structural view of an ultra-high speed motor provided in Embodiment 1;

2 is a partially divided left perspective structural view of a trough type dynamic pressure gas radial bearing provided in Embodiment 1;

Figure 3 is a partial enlarged view of A in Figure 2;

4 is a schematic partial right side perspective view showing the slot type dynamic pressure gas radial bearing provided in Embodiment 1;

Figure 5 is a partial enlarged view of B in Figure 4;

6 is a schematic cross-sectional structural view of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 1;

Figure 7a is a left side view of the center disk described in Embodiment 1;

Figure 7b is a right side view of the center disk described in Embodiment 1;

Figure 8a is a right side view of the left side disk to which the foil-type elastic member is fixed as described in Embodiment 1;

Figure 8b is a left side view of the right side disk with the foil-type elastic member fixed in Embodiment 1;

9 is a schematic cross-sectional structural view of a foil-type elastic member provided in Embodiment 1;

Figure 10 is a perspective view showing the structure of the foil-type elastic member provided in Embodiment 1;

Figure 11a is a left side perspective structural view of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 2;

Figure 11b is a right perspective view showing the hybrid dynamic pressure gas thrust bearing of the second embodiment;

Figure 12 is a partially sectional perspective structural view of the hybrid dynamic pressure gas thrust bearing provided in the second embodiment;

Figure 13 is a left perspective view showing the middle plate of the second embodiment;

Figure 14 is a partial enlarged view of C in Figure 13;

Figure 15 is a right perspective view showing the center disk of the second embodiment;

Figure 16 is a partial enlarged view of D in Figure 15;

Figure 17 is a schematic view showing the structure of a rotor provided in Embodiment 3;

18 is a schematic structural view of a core provided in Embodiment 4;

Figure 19 is a schematic structural view of a punching piece according to Embodiment 4;

20 is a schematic structural view of a winding provided in Embodiment 4;

21 is a perspective structural view of a motor housing provided in Embodiment 5;

Figure 22 is a partial enlarged view of E in Figure 21;

23 is a right perspective view showing the structure of a super high speed motor provided in Embodiment 5.

The figures in the figure are as follows:

1, motor housing; 11, open slot; 12, venting hole; 2, rotor; 21, rotor base; 22, magnetic steel; 23, magnetic steel protective sleeve; 3, stator; 31, iron core; Sheet; 3111, cup-shaped perforation; 3111a, cup mouth; 3111b, cup foot; 312, stator lamination; 313, end plate; 32, winding; 4, trough dynamic gas radial bearing; 4a, left end radial Bearing; 4b, right-end radial bearing; 41, bearing casing; 42, bearing inner sleeve; 43, groove pattern; 431, groove pattern on the outer circumferential surface; 4311, axial high line; 4312, axial center line ;4313, axial low position line; 432, groove pattern on the left end face; 4321, radial high position line; 4322, radial center line; 4323, radial low position line; 433, groove pattern on the right end face; Radial high position line; 4332, radial middle position line; 4333, radial low position line; 44, stop ring; 5, hybrid dynamic pressure gas thrust bearing; 51, side disc; 511, left side disc; 512, right Side plate; 513, card slot; 52, middle plate; 521, groove pattern on the left end face; 5211, radial high position line; 5212, radial center line; 5213, radial low line; Groove pattern on the right end face; 5221, radial high position line; 5222, radial center line; 5223, radial low line; 523, groove pattern on the outer circumferential surface; 5231, axial high line; 5132, axial Medium line; 5233, axial low line; 53, foil-type elastic member; 53a, foil-type elastic member fixed on the left side disk; 53b, foil-type elastic member fixed on the right side plate; 531, wave foil ;5311, curved protrusion; 5122, transition bottom edge between waves; 532, flat foil; 6, inner shaft; 7, outer shaft; 8a, left radial bearing sleeve; 8b, right radial bearing sleeve; Left bearing chamber end cover; 9a1, venting hole; 9b, right bearing chamber end cover; 10, cooling fan; 101, fan housing; 102, air inlet.

detailed description

The technical solution of the present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

Example 1

As shown in FIG. 1 , an ultra-high speed motor provided by the embodiment includes a motor housing 1 , a rotor 2 , a stator 3 , two radial bearings 4 , a thrust bearing 5 , an inner shaft 6 and an outer shaft . 7; the radial bearing 4 is a slot type dynamic pressure gas radial bearing, comprising a bearing outer casing 41 and a bearing inner sleeve 42; the thrust bearing 5 is a hybrid dynamic pressure gas thrust bearing, including two a side disc 51 and a middle disc 52 interposed between the two side discs, and a foil-type elastic member 53 is disposed between each of the side discs 51 and the middle disc 52; the rotor 2 is sleeved on the inner shaft 6 In the middle portion, two radial bearings 4 are respectively sleeved on the outer shaft 7 located at the left and right ends of the rotor 2. The thrust bearing 5 is sleeved on the outer shaft 7 at the right end and outside the right end radial bearing 4b. End side.

The ultra-high speed motor further includes a left radial bearing sleeve 8a, a left bearing chamber end cover 9a, a right radial bearing sleeve 8b, a right bearing chamber end cover 9b, a cooling fan 10 and a fan housing 101, and the left bearing chamber The end cap 9a is connected to the left radial bearing sleeve 8a, the left radial bearing sleeve 8a is connected to the motor housing 1, and the fan housing 101 is connected to the right bearing chamber end cover 9b, the right bearing The chamber end cover 9b is connected to the right radial bearing sleeve 8b, the right radial bearing sleeve 8b is connected to the motor housing 1, and the cooling fan 10 is sleeved on the right bearing chamber end cover 9b and the fan housing. On the inner shaft 6 between 101.

2 to 5, the outer circumferential surface and the left and right end surfaces of the bearing inner sleeve 42 each have a regular shape of the groove pattern 43 (431, 432 and 433 in the figure, the groove in this embodiment). The pattern is an impeller shape), and the groove pattern 432 of the left end surface is mirror-symmetrical with the groove pattern 433 of the right end surface. The axial contour line of the groove pattern 431 located on the outer circumferential surface of the bearing inner sleeve 42 forms a one-to-one correspondence with the radial contour lines of the groove patterns (432 and 433) of the left and right end surfaces, and is mutually overlapped, that is, external The axially high bit line 4311 in the circumferential groove pattern 431 corresponds to the radial high bit lines (4321 and 4331) in the groove patterns (432 and 433) of the left and right end faces, and is chamfered before the end face is chamfered Interacting with each other; the axial center line 4312 in the groove pattern 431 of the outer circumferential surface corresponds to the radial center line (4322 and 4332) in the groove patterns (432 and 433) of the left and right end faces, and The front end is circumferentially chamfered to each other; the axially lower bit line 4313 in the groove pattern 431 of the outer circumferential surface and the radially lower line (4323 and 4333) in the groove patterns (432 and 433) of the left and right end faces are both Corresponding to each other and overlapping each other before the end face is chamfered.

By making the outer circumferential surface and the both end surfaces of the bearing inner sleeve 42 have regular groove patterns (431, 432, and 433), the groove pattern 432 of the left end surface and the groove pattern 433 of the right end surface are mirror-symmetrical and outer circumference. The axial contour line of the groove pattern 431 forms a one-to-one correspondence with the radial contour lines of the groove patterns (432 and 433) of the left and right end faces, and mutually intersects each other, thereby ensuring the groove pattern of the impeller shape at both end faces. The pressurized gas generated by (432 and 433) is transported from the axial direction of the shaft to the groove passage formed by the groove pattern 431 of the outer circumferential surface, so as to form a gas film required for supporting the high-speed running bearing more strongly, and The gas film is used as a lubricant for the dynamic pressure gas radial bearing, and thus is advantageous for achieving high-speed stable operation of the trough type dynamic pressure gas radial bearing 4 in an air floating state.

In addition, when the retaining ring 44 is respectively disposed at both ends of the bearing outer casing 41, the self-sealing action between the end faces of the bearing inner sleeve 42 and the retaining ring 44 can be achieved under the driving of the high-speed rotating shaft, so that the trough pattern is continuous. The generated dynamic pressure gas can be well sealed and stored in the entire matching clearance of the bearing, which fully ensures the lubrication of the high-speed running dynamic pressure gas radial bearing.

The matching gap between the bearing outer casing 41 and the bearing inner sleeve 42 is preferably 0.003 to 0.008 mm to further ensure Reliability and stability of high-speed bearing operation.

As shown in FIG. 6 , a hybrid dynamic pressure gas thrust bearing 5 provided in this embodiment includes: two side discs 51 with a middle disc 52 interposed between the two side discs 51 on each side. A foil-shaped elastic member 53 is disposed between the disk 51 and the intermediate plate 52; the left end surface of the intermediate plate 52 is provided with a groove pattern 521 having a regular shape, and the right end surface is provided with a groove pattern 522 having a regular shape.

7a and 7b, it can be seen that the groove pattern 521 of the left end surface of the middle plate 52 and the groove pattern 522 of the right end surface form a mirror symmetry, and the radial contour line and the right end surface of the groove pattern 521 of the left end surface are formed. The radial contours of the troughs 522 form a one-to-one correspondence.

The

troughs

521 and 522 have the same shape, and are in the shape of an impeller in this embodiment.

Further, it can be seen in conjunction with Figs. 8a and 8b that the foil-type elastic member 53 is fixed to the inner end surface of the corresponding side disk 51 (for example, the left side disk 511 to which the foil-type elastic member 53a is fixed as shown in Fig. 8a and the left side disk 511 shown in Fig. 8b The right side disc 512) to which the foil type elastic member 53b is fixed, and the foil type elastic member 53a fixed to the left side disc 511 is mirror-symmetrical with the foil type elastic member 53b fixed to the right side disc 512. There may be a plurality of foil-type elastic members on each of the side plates (four shown in the drawing), and are evenly distributed along the inner end faces of the side plates.

By providing the foil-type elastic member 53 between the side disk 51 and the intermediate disk 52, regular groove patterns (521 and 522) are provided on the left and right end faces of the middle plate 52, and the groove pattern 521 of the left end face is The groove pattern 522 of the right end surface is mirror-symmetrical, thereby obtaining a rigid characteristic of a high limit rotation speed of the groove type dynamic pressure gas thrust bearing, and a high impact resistance and load of the foil type dynamic pressure gas thrust bearing. The hybrid dynamic pressure gas thrust bearing of the flexible nature of the capability; because the foil-shaped elastic member 53 forms a wedge-shaped space with the intermediate disk 52, when the disk 52 rotates, the gas is driven by its own viscous action and is compressed to the wedge shape. In the space, the axial dynamic pressure can be significantly enhanced, compared with the existing simple foil dynamic pressure gas thrust bearing, which can have a limit rotation speed which is multiplied under the same load; meanwhile, due to the increased foil type The elastic member 53 can also significantly improve the bearing capacity, the impact resistance and the ability to suppress the whirl of the bearing under the elastic action, and can have the same in comparison with the existing simple groove type dynamic pressure gas thrust bearing. Doubling the speed of impact resistance and load capacity.

6 and FIG. 9 and FIG. 10, the foil-shaped elastic member 53 is composed of a wave foil 531 and a flat foil 532, and a top end of the curved protrusion 5311 of the wave foil 531 is attached to the flat foil 532. The inter-wave transition bottom edge 5312 of the wave foil 531 is in contact with the inner end surface of the corresponding side disk 51.

In order to further reduce the wear of the foil-type elastic member 53 of the intermediate plate 52 which is operated at a high speed to prolong the service life of the bearing, it is preferable to provide a wear-resistant coating on the mating surface of the foil-shaped elastic member 53 which is engaged with the intermediate plate 52 ( Not shown in the figure).

Example 2

As shown in FIG. 11a, 11b, and 12 to 16, a hybrid dynamic pressure gas thrust bearing provided by the embodiment is provided. The only difference from Embodiment 1 is that:

A groove pattern 523 is also provided on the outer circumferential surface of the intermediate disk 52, and the shape of the groove pattern 523 of the outer circumferential surface is the same as that of the groove patterns (521 and 522) of the left and right end faces (this embodiment) The axial contour of the groove pattern 523 of the outer circumferential surface and the radial contour lines of the groove patterns (521 and 522) of the left and right end faces are in one-to-one correspondence with each other and intersect with each other; :

The axially high bit line 5231 in the groove pattern 523 of the outer circumferential surface corresponds to the radial high line line 5211 in the groove pattern 521 of the left end surface, and is mutually overlapped before the end face is chamfered; the groove of the outer circumferential surface The axial center line 5232 in the pattern 523 corresponds to the radial center line 5212 in the groove pattern 521 of the left end surface, and is mutually overlapped before the end surface is chamfered; the groove pattern 523 in the outer circumference surface The axially lower bit line 5233 corresponds to the radially lower bit line 5213 in the groove pattern 521 of the left end face, and is mutually overlapped before the end face is chamfered (as shown in FIG. 14);

The axially high bit line 5231 in the groove pattern 523 of the outer circumferential surface corresponds to the radial high line 5221 in the groove pattern 522 of the right end face, and is mutually overlapped before the end face is chamfered; the groove of the outer circumferential surface The axial center line 5232 in the pattern 523 corresponds to the radial center line 5222 in the groove pattern 522 of the right end surface, and is mutually overlapped before the end surface is chamfered; the groove pattern 523 in the outer circumference surface The axially lower bit line 5233 corresponds to the radially lower bit line 5223 in the groove pattern 522 of the right end face, and is mutually overlapped before the end face is chamfered (as shown in FIG. 16).

A groove pattern is also provided on the outer circumferential surface of the intermediate disk 52, and the shape of the groove pattern 523 of the outer circumferential surface is the same as that of the groove patterns (521 and 522) of the left and right end faces, and When the axial contour line of the groove pattern 523 of the circumferential surface forms a one-to-one correspondence with the radial contour lines of the groove patterns (521 and 522) of the left and right end faces, the groove pattern of both end faces of the inner disk can be obtained. The pressurized gas generated by (521 and 522) is transported from the axial direction of the shaft to the groove passage formed by the groove pattern 523 of the outer circumferential surface so as to form a gas film which is stronger for supporting the high speed running bearing, and The gas film is used as a lubricant for the dynamic pressure gas thrust bearing, so that the high-speed stable operation of the hybrid dynamic pressure gas thrust bearing in the air-floating state can be further ensured, and further guarantee for realizing the high limit rotation speed of the motor.

A card slot 513 (shown in Fig. 12) for fixing the foil-type elastic member 53 is provided on the inner end surface of the side disk 51.

The fitting clearance of the foil-type elastic member 53 and the intermediate disk 52 is preferably 0.003 to 0.008 mm to further ensure the reliability and stability of the high-speed operation of the bearing.

In order to better meet the performance requirements of high speed operation, the foil-type elastic member 53 is preferably subjected to surface heat treatment.

It should be noted that the composition of the foil-type elastic member 53 of the present invention is not limited to that described in the above embodiments, and may be composed of a wave foil and a flat foil, but the transition edge between the wave arches of the wave foil is The flat foil is fitted, or it is composed of two flat foils directly, or other existing structures.

Example 3

1 and 17, the rotor 2 includes a rotor base 21, a magnetic steel 22 and a magnetic steel protective sleeve 23, the rotor base 21 is sleeved on the inner shaft 6, and the magnetic steel 22 is sleeved on the rotor. In the central portion of the base 21, the magnetic steel protective cover 23 is sleeved on the magnetic steel 22 to better satisfy the ultra-high speed rotation.

Example 4

1 and 18, the stator 3 includes a core 31 and a winding 32 fixed to an inner wall of the motor housing 1 above the rotor 2, the winding 32 being disposed on the core 31; the core 31 includes a stator lamination 312 formed by stacking a plurality of punching sheets 311 and end platens 313 fixed to both sides of the stator laminations 312.

As shown in FIG. 19, the punching piece 311 has a circular ring shape, and a plurality of cup-shaped through holes 3111 are formed at intervals in the annular portion. The cup mouth portion 3111a of the through hole 3111 is closed, and the bottom of the cup foot 3111b is open.

As shown in FIG. 20, the winding 32 is connected by a three-phase star type, the center line is not led out, and only three ends of A, B, and C are taken out; each phase winding is two coils, and each coil is made of an enamelled copper wire. Continuously wound.

Example 5

As shown in FIG. 21 and FIG. 22, a plurality of opening slots 11 are defined in the inner wall of the motor housing 1, and a plurality of vent holes 12 are formed in the end surface of the motor housing 1, and the opening slots 11 and the vent holes 12 are formed. Connected to facilitate the introduction and export of gas, on the one hand to achieve rapid heat dissipation and exhaust, on the other hand to achieve air supply to the bearing chamber.

In addition, a plurality of exhaust holes 9a1 are formed on the circumferential side of the left bearing chamber end cover 9a, and a plurality of air inlet holes 102 (shown in FIG. 23) are opened on the outer end surface of the fan casing 101 to further achieve rapid heat dissipation.

According to the test, the bearing provided by the invention can reach the limit rotation speed of 100,000-450,000 rpm in the air floating state, so the invention can significantly reduce the volume of the motor to achieve miniaturization for the same power requirement, and promote the miniaturization of high-tech. Development is of great value.

Finally, it is necessary to point out that the above content is only used to further explain the technical solutions of the present invention, and is not to be construed as limiting the scope of the present invention. Some of the above-mentioned contents of the present invention are made by those skilled in the art. All improvements and adjustments are within the scope of the invention.

Claims

An ultra-high speed motor comprising a motor housing, a rotor, a stator, two radial bearings, a thrust bearing, and an inner shaft and an outer shaft; wherein the radial bearing is a slot type dynamic pressure gas path a bearing, comprising a bearing sleeve and a bearing inner sleeve; the thrust bearing is a hybrid dynamic pressure gas thrust bearing comprising two side discs and a middle disc sandwiched between the two side discs, at each side disc A foil-type elastic member is disposed between the middle plate and the middle plate; the rotor is sleeved in the middle of the inner shaft, and two radial bearings are respectively sleeved on the outer shafts at the left and right ends of the rotor, and the thrust bearing sleeve is sleeved On the outer shaft on the right end and on the outer end side of the right-hand radial bearing.
The ultra high speed motor according to claim 1, wherein said super high speed motor further comprises a left radial bearing sleeve and a left bearing chamber end cover, said left bearing chamber end cover being connected to the left radial bearing sleeve The left radial bearing sleeve is coupled to the motor housing.
The ultra high speed motor according to claim 1 or 2, wherein said ultra high speed motor further comprises a right radial bearing sleeve, a right bearing chamber end cover, a heat dissipation fan and a fan housing, said fan housing and The right bearing chamber end cover is connected, the right bearing chamber end cover is connected to the right radial bearing sleeve, the right radial bearing sleeve is connected to the motor housing, and the cooling fan is sleeved in the right bearing chamber On the inner shaft between the end cap and the fan housing.
The ultra-high speed motor according to claim 3, wherein a plurality of exhaust holes are formed in a peripheral side of the left bearing chamber end cover, and a plurality of intake holes are formed in an outer end surface of the fan casing.
The ultra-high speed motor according to claim 1, wherein a plurality of open slots are formed in a peripheral side of the inner wall of the motor housing, and a plurality of vent holes are formed in an end surface of the motor housing, the open slots and the vent holes. Connected.
The ultra-high speed motor according to claim 1, wherein both the outer circumferential surface and the both end surfaces of the bearing inner sleeve have a regular groove pattern.
The ultra-high speed motor according to claim 6, wherein the groove pattern of one end surface of the bearing inner sleeve is mirror-symmetrical with the groove pattern of the other end surface, and the axial direction of the groove pattern of the outer circumferential surface. The contour line forms a one-to-one correspondence with the radial contour lines of the groove patterns on both end faces and intersects each other.
The ultra-high speed motor according to claim 7, wherein an axial high line in the groove pattern of the outer circumferential surface of the bearing inner sleeve corresponds to a radial high line in the groove pattern on both end faces. And intersecting each other before the circumferential chamfer of the end face; the axial median line in the groove pattern of the outer circumferential surface corresponds to the radial median line in the groove pattern on both end faces, and before the end face is chamfered Interacting with each other; the axially lower line in the groove pattern of the outer circumferential surface corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.
The ultra-high speed motor according to claim 1, wherein both end faces of the middle plate are provided with a regular pattern of groove patterns, and the groove pattern of one end face is mirror-symmetrical with the groove pattern of the other end face. .
The ultra high speed motor according to claim 9, wherein an outer circumferential surface of said intermediate disk is also provided a trough pattern, and the shape of the groove pattern on the outer circumferential surface is the same as the shape of the groove pattern on both end faces, and the axial contour of the groove pattern of the outer circumferential surface and the radial contour of the groove pattern on both end faces They all form one-to-one correspondence and cross each other.
The ultra-high speed motor according to claim 10, wherein the axial high line in the groove pattern of the outer circumferential surface of the intermediate disk corresponds to the radial high line in the groove pattern on both end faces, and The end faces are circumferentially chamfered to each other; the axial median line in the groove pattern of the outer circumferential surface corresponds to the radial median line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered; The axially lower bit line in the groove pattern of the outer circumferential surface corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.
The ultra high speed motor according to claim 1, wherein the foil-type elastic member fixed to one side disk is mirror-symmetrical to the foil-shaped elastic member fixed to the other side disk.
The ultra-high speed motor according to claim 1 or 12, wherein said foil-shaped elastic member is composed of a wave foil and a flat foil, and a curved convex top end of said wave foil is attached to the flat foil.
The ultra-high speed motor according to claim 1 or 12, wherein the foil-shaped elastic member is composed of a wave foil and a flat foil, and a transition edge between the wave arches of the wave foil is attached to the flat foil.
The ultra high speed motor according to claim 1 or 12, wherein said foil-type elastic member is composed of two flat foils.
The ultra-high speed motor according to claim 1, wherein the rotor comprises a rotor base, a magnetic steel and a magnetic steel protective sleeve, the rotor base is sleeved on the inner shaft, and the magnetic steel sleeve is set on the rotor base. In the central part, the magnetic steel protective sleeve is set on the magnetic steel.
The ultra high speed motor according to claim 1, wherein said stator comprises a core and a winding, said core being fixed to an inner wall of a motor housing located above said rotor, said winding being disposed on said core .
The ultra-high speed motor according to claim 17, wherein said core comprises a stator lamination formed by stacking a plurality of punching sheets and an end plate fixed to both sides of the stator lamination; said punching is round The ring shape is provided with a plurality of cup-shaped perforations at intervals in the annular portion, the mouth portion of the perforation is closed, and the bottom of the cup is open.
The ultra-high speed motor according to claim 17, wherein the winding is a three-phase star connection, the center line is not led out, and only three ends of A, B, and C are taken out.
The ultra high speed motor according to claim 19, wherein each phase winding is two coils, and each coil is continuously wound from an enamelled copper wire.