TW201706511A - Ultra-high speed turbocharger - Google Patents

Abstract

An ultra-high speed turbocharger, comprising a turbine machine, a compressor, a rotary shaft, two radial bearings, a thrust bearing and a main housing, the radial bearings being groove-type dynamic pressure gas radial bearings, the thrust bearing being a mixed-type dynamic pressure gas thrust bearing, the main housing being sleeved at a central portion of the rotary shaft, the two radial bearings being respectively sleeved on the rotary shaft within the main housing, the thrust bearing being sleeved on the rotary shaft between the main housing and a pressure wheel. The ultra-high speed turbocharger implements an ultra-high speed stable operation in an air state, and with regard to identical power requirements, enables the size of the turbocharger to be significantly reduced for miniaturisation.

Description

Ultra high speed blower

This invention relates to the field of high precision mechanical technology, and more particularly to an ultra high speed blower.

The air blower is mainly used in a part of an office automation equipment that requires a large amount of air, and the hot air generated inside the device is discharged outward by the wind generated by rotating the impeller, and the device is internally cooled and cooled. The traditional blower usually uses the speed increasing system to drive the compressor impeller to rotate after the speed increase of the ordinary power frequency motor. The main defects are as follows: 1 The speed increasing system is very complicated, the weight is large, the floor space is large, and the cost is expensive; Specially equipped oil system, and easy to leak oil problem, limited application range; 3 gear transmission noise is large, there is a certain mechanical loss, and ordinary power frequency motor has low power density, large volume and weight, high noise; Both the speed system and the ordinary power frequency motor need to apply the bearing. Due to the friction and life of the bearing, the rotation speed cannot be very high, resulting in low overall power density and large volume of the system. It is difficult to match the power of the compressor impeller. 5 Because the speed of the power frequency motor is constant, if the air supply volume of the air blower is to be adjusted, a very complicated air intake control system must be added to increase the manufacturing cost and control difficulty.

In order to solve the above-mentioned defects of the conventional motor blower, the Chinese patent document CN102200136 B discloses an air suspension gas supply adjustable high speed motor direct drive blower, which comprises a compressor impeller, a permanent magnet synchronous motor rotor, a motor stator, and a front Radial air bearing, rear radial air bearing, axial thrust air bearing, volute and motor housing; one end of the permanent magnet synchronous motor rotor is connected to the compressor impeller, and the motor stator drives the permanent magnet synchronous motor rotor to rotate, the front diameter The air bearing, the rear radial air bearing and the axial thrust air bearing are suspended to support the permanent magnet synchronous motor rotor, and the scroll is disposed at the periphery of the compressor impeller, and the motor housing is located at the motor stator, the front radial air bearing, and the rear radial Air bearing, axial thrust air bearing and the periphery of the permanent magnet synchronous motor rotor. Although the patented technology directly drives the compressor impeller through the permanent magnet synchronous motor rotor of the high-speed motor, the utility model has the advantages of high efficiency, low loss, environmental protection, wide applicable range, and the like, but the patent technology still has the following problems: 1. The rotational speed is still limited. At present, it can only achieve a speed of up to 100,000 rpm; 2. It can not be operated for a long time: the heat generated by high-speed operation cannot be effectively exported, so that the continuous working time cannot be very long; 3. The stability of high-speed operation is not good, so that the actual operating efficiency is up to Not ideal goals; 4, the structure is still relatively complex, large size, can not meet the requirements of today's miniaturization development.

In view of the above problems existing in the prior art, an object of the present invention is to provide an ultrahigh speed blower which has high operation efficiency, high speed operation stability, and can work for a long time.

In order to achieve the above object, the technical solution adopted by the present invention is as follows: An ultra-high-speed air blower comprising an impeller and an electric motor, the electric machine comprising a rotor, a stator, a rotating shaft, an end cover and a casing; and characterized in that: further comprising a rotating connecting member and a trough dynamic pressure gas radial bearing, and the casing is an annular cylindrical structure in which two cavities are formed by inner and outer cylinders, and the rotary connecting member is a cylindrical structure having a cavity. The rotating connecting member is sleeved on a rotating shaft close to the impeller, and is respectively coupled with the end of the impeller and the rotating shaft, and the side of the rotating connecting member is located in a cavity formed by the outer cylinder and the inner cylinder of the casing. The slotted dynamic pressure gas radial bearing and the rotating shaft are both located in the inner cylinder cavity of the casing, and the slot type dynamic pressure gas radial bearing is sleeved on the rotating shaft; the stator is fixed in the inner cylinder of the casing On the outer wall, the rotor is fixed to the side inner wall of the rotary joint.

Preferably, a plurality of air guide vanes are provided at a side of the rotary joint located above the air flow passage formed at the end of the rotary shaft and the slotted dynamic gas radial bearing.

As a further preferred solution, a plurality of air inlet holes and a plurality of heat dissipation vent holes are formed on the outer circumference side of the outer casing of the casing.

Preferably, the impeller is fixedly connected to the rotating connecting member and the rotating shaft by a locking bolt.

As a further preferred solution, the rotating shaft and the locking bolt are both provided with a cavity to reduce the weight of the blower.

Preferably, the ultra high speed blower further comprises an impeller casing, the impeller casing being fixedly connected to the outer cylinder of the casing by bolts.

Preferably, the trough dynamic pressure gas radial bearing comprises a bearing outer casing and a bearing inner sleeve, and the outer circumferential surface and the opposite end surfaces of the inner bearing sleeve have regular groove patterns.

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.

In one embodiment, the ultra high speed blower further includes a hybrid dynamic pressure gas thrust bearing, the hybrid dynamic pressure gas thrust bearing comprising two side plates and being sandwiched between the two side plates The middle plate has a foil-type elastic member disposed between each of the side plates and the middle plate, and the hybrid dynamic pressure gas thrust bearing is located in a cavity formed by the housing and the end cover, and is sleeved on the rotating shaft.

Preferably, the end cap is fixedly connected to the middle disc adjusting ring of the hybrid dynamic pressure gas thrust bearing and the tail of the housing by bolts.

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 of the both end faces, and the axis of the groove pattern of the outer circumferential surface The one-to-one correspondence is made to the radial contour lines of the groove pattern of the contour line and the both end faces, and they are mutually connected.

As a further preferred embodiment, 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 is mutually overlapped before the end face is chamfered; the outer circumferential surface The axial median line in the trough 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 axial direction in the groove pattern of the outer circumferential surface The lower bit 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.

In still another embodiment, the foil-type elastic member is composed of two flat foils, wherein the flat foil near the end surface of the side disk has a plurality of bubbles, and the curved convex top end of the bubble is attached to the other flat foil. Hehe.

The above-mentioned groove patterns are all impeller shapes.

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

Compared with the prior art, the present invention has the following beneficial effects: The air blower provided by the present invention uses gas as a lubricant for the bearing, so that it has not only pollution-free, low friction loss, long use time, wide application range, and energy saving and environmental protection. And many advantages, and the use of the structure, the heat dissipation effect is good, can ensure stable operation for a long time; in particular, the air bearing of the structure can achieve ultra-high speed operation under air-floating state (tested, up to 100,000~ 450,000 rpm limit speed), therefore, the present invention can significantly reduce the volume of the blower to achieve miniaturization for the same power requirement, has the advantages of small footprint, convenient use, etc., and is of great value for promoting the development of miniaturization high-tech, relatively Significant progress has been made in the prior art.

The technical solution of the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. Example 1

1 to 5: an ultra-high speed blower provided by the embodiment includes an impeller 1 and a motor 2, the motor 2 including a rotor 21, a stator 22, a rotating shaft 23, an end cover 24 and a casing 25, which are characterized. It is further comprised of a rotary joint 3, a trough dynamic gas radial bearing 4 and a hybrid dynamic pressure thrust bearing 5.

The housing 25 is an annular cylindrical structure in which two cavities are formed by inner and outer cylinders, and the rotary connecting member 3 is a cylindrical structure having a cavity, and the rotating connecting member 3 is sleeved close to The rotating shaft 23 of the impeller 1 is coupled to the end of the impeller 1 and the rotating shaft 23, and the side portion 31 of the rotating connecting member 3 is located in a cavity formed by the outer cylinder 251 and the inner cylinder 252 of the casing; The slotted dynamic pressure gas radial bearing 4 and the rotating shaft 23 are both located in the cavity of the inner cylinder 252 of the casing, and the slot type dynamic pressure gas radial bearing 4 is sleeved on the rotating shaft 23; the stator 22 is fixed On the outer wall of the inner cylinder 252 of the casing, the rotor 21 is fixed to the inner wall of the side portion 31 of the rotary joint 3.

The trough dynamic pressure gas radial bearing 4 includes a bearing outer casing 41 and a bearing inner sleeve 42; the hybrid dynamic pressure gas thrust bearing 5 includes two side discs 51 and a middle disc sandwiched between the two side discs 52, a foil-type elastic member 53 is disposed between each of the side plates 51 and the intermediate plate 52, and the hybrid dynamic pressure gas thrust bearing 5 is located in a cavity formed by the housing 25 and the end cover 24, and is sleeved. It is arranged on the rotating shaft 23.

A plurality of air guide vanes 32 are formed in the side portion 31 of the rotary link 3 above the air flow passage formed at the end of the rotary shaft 23 and the slot type dynamic pressure gas radial bearing 4.

A plurality of intake holes 253 and a plurality of heat dissipation vent holes 254 are opened on the circumferential side of the outer cylinder 251 of the casing, and the intake holes 253 communicate with the air guide vanes 32.

The impeller 1 is connected and fixed to the rotary joint 3 and the rotating shaft 23 by a locking bolt 6.

In order to further reduce the weight of the blower, the rotating shaft 23 and the locking bolt 6 both open a cavity (231/61).

Preferably, the ultra high speed blower further comprises an impeller casing 11 which is fixedly connected to the outer cylinder 251 of the casing by bolts 7. The end cap 24 is fixedly coupled to the middle disc adjusting ring 54 of the hybrid dynamic pressure gas thrust bearing 5 and the tail portion of the housing 25 by bolts 8.

6 to 9, 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 fitting clearance between the bearing outer casing 41 and the bearing inner sleeve 42 is preferably 0.003 to 0.008 mm to further ensure the reliability and stability of the bearing at high speed.

As shown in FIG. 10, a hybrid dynamic pressure gas thrust bearing provided by the embodiment includes: two side discs 51, and a middle disc 52 is interposed between the two side discs 51, and each side disc 51 is A foil-shaped elastic member 53 is disposed between the intermediate discs 52; a left-hand end surface of the intermediate disc 52 is provided with a regular groove pattern 521, and a right end surface is provided with a regular-shaped groove pattern 522.

Referring to FIG. 11a and FIG. 11b, 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 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 groove pattern 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.

12a and 12b, 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. 12a and the left side disk 511 shown in FIG. 12b. 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 intermediate disk 52, and the groove pattern 521 and the right end face of the left end face are provided. The trough pattern 522 is mirror-symmetrical, thereby obtaining a high-limit rotational speed characteristic of the slot type dynamic pressure gas thrust bearing, and high impact resistance and load capacity of the foil type dynamic pressure gas thrust bearing. A flexible dynamic pressure gas thrust bearing; since the foil-shaped elastic member 53 forms a wedge-shaped space with the intermediate plate 52, when the disk 52 rotates, the gas is driven by its own viscous action and compressed into the wedge-shaped space. Therefore, the axial dynamic pressure can be significantly enhanced, and the conventional simple foil-type dynamic pressure gas thrust bearing can have a limit rotation speed which is multiplied under the same load; meanwhile, since the foil-type elastic member 53 is added, Under the action of its elasticity, the load capacity, impact resistance and the ability to suppress the eddy of the bearing can be significantly improved. Compared with the existing simple trough dynamic pressure gas thrust bearing, it can have the phase. Double the impact resistance and load capacity at the same speed.

As shown in FIG. 10 and FIG. 13 and FIG. 14 , the foil-shaped elastic member 53 is composed of a wave foil 531 and a flat foil 532 , and the top end of the curved protrusion 5311 of the wave foil 531 is in contact with 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 at a high speed to extend the service life of the bearing, it is preferable to provide a wear-resistant coating on the mating surface of the foil-type elastic member 53 that cooperates with the intermediate plate 52 (in the figure) Not shown). Example 2

As can be seen in conjunction with Figures 15a, 15b, 16 to 20, a hybrid dynamic pressure gas thrust bearing provided by this embodiment differs from Embodiment 1 only in 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 (in 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 are mutually connected;

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 axial low bit line 5233 corresponds to the radially lower bit line 5213 in the groove pattern 521 of the left end face, and overlaps each other before the end face is chamfered (as shown in FIG. 18);

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. 20).

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 the outer circumference. When the axial contour of the groove pattern 523 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 and are mutually connected, the groove pattern on 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 required for supporting the high-speed running bearing, and the gas The membrane acts as a lubricant for the dynamic pressure gas thrust bearing, thereby further ensuring high-speed stable operation of the hybrid dynamic pressure gas thrust bearing in an air-floating state, further providing a guarantee for achieving a high limit rotation speed of the air blower.

A card slot 513 (shown in Fig. 16) 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 Flat foil is attached; or, directly composed of two flat foils, wherein the flat foil near the end surface of the side disc has a plurality of bubbling, and the curved convex top end of the bubbling is attached to another flat foil; or Other existing structures.

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 air blower 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. Intrinsic improvements and adjustments are within the scope of the invention.

1‧‧‧ Impeller
11‧‧‧The impeller shell
2‧‧‧Motor
21‧‧‧Rotor
22‧‧‧ Stator
23‧‧‧ shaft
231‧‧‧ Cavity
24‧‧‧End cover
25‧‧‧shell
251‧‧‧Outer tube
252‧‧‧ inner tube
253‧‧‧Air intake
254‧‧‧Heat vents
3‧‧‧Rotating connectors
31‧‧‧ side
32‧‧‧air guide vanes
4‧‧‧ trough dynamic pressure gas radial bearing
41‧‧‧ bearing jacket
42‧‧‧ bearing inner sleeve
43‧‧‧ trough pattern
431‧‧‧Slot pattern on the outer circumferential surface
4311‧‧‧ axial high line
4312‧‧‧ axial center line
4313‧‧‧ axial low line
432‧‧‧ trough pattern on the left end
4321‧‧‧radial high line
4322‧‧‧radial median line
4323‧‧‧radial low bit line
433‧‧‧ trough pattern on the right end
4331‧‧‧ radial high position line
4332‧‧‧radial center line
4333‧‧‧radial low line
44‧‧‧End ring
5‧‧‧Combined dynamic pressure gas thrust bearing
51‧‧‧ side disk
511‧‧‧left disk
512‧‧‧right disk
513‧‧‧ card slot
52‧‧‧ mid-disc
521‧‧‧ trough pattern on the left end
5211‧‧‧radial high line
5212‧‧‧radial center line
5213‧‧‧radial low line
522‧‧‧Slot pattern on the right end face
5221‧‧‧radial high line
5222‧‧‧radial center line
5223‧‧‧radial low line
523‧‧‧Slot pattern on the outer circumferential surface
5231‧‧‧ axial high line
5232‧‧‧Axial center line
5233‧‧‧Axis low line
53, 53a, 53b‧‧‧Foil type elastic parts
531‧‧‧Foil foil
5311‧‧‧Arc-shaped bulge
5312‧‧‧Transition hem between the arches
532‧‧‧Flat foil
54‧‧‧ mid-plate adjustment ring
6, 7, 8‧ ‧ bolts
61‧‧‧ cavity

1 is a front perspective view of a super high-speed air blower provided in the first embodiment; FIG. 2 is a front view of the super high speed air blower provided in the first embodiment; FIG. 3 is a view taken along line AA of FIG. 1 is a schematic perspective view of a rotary joint provided by FIG. 5; FIG. 5 is a perspective structural view of the housing provided in the first embodiment; FIG. 6 is a partially divided left-view solid structure of the slot type dynamic pressure gas radial bearing provided in the first embodiment. Figure 7 is a partial enlarged view of the portion B of Figure 6; Figure 8 is a schematic view of a partially divided right perspective view of the slot type dynamic pressure gas radial bearing provided in Embodiment 1; Figure 9 is a partial enlarged view of C in Figure 8 Figure 10 is a cross-sectional structural view of the hybrid dynamic pressure gas thrust bearing provided in Embodiment 1. Figure 11a is a left side view of the center disk described in Embodiment 1; Figure 11b is a right side view of the center disk described in Embodiment 1. Figure 12a 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 12b is a left side view of the right side disk to which the foil-type elastic member is fixed as described in Embodiment 1; The foil-type elastic member provided in Embodiment 1 Figure 14 is a schematic perspective view of a three-dimensional structure of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 2; Figure 15b is a schematic view of a three-dimensional structure of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 2; 2 is a schematic view of a right-hand perspective structure of a hybrid dynamic pressure gas thrust bearing provided; FIG. 16 is a partially divided perspective structural view of the hybrid dynamic pressure gas thrust bearing provided in Embodiment 2; FIG. 17 is a description of Embodiment 2 FIG. 18 is a partially enlarged perspective view of the middle disk of the embodiment 2; FIG. 20 is a partial enlarged view of the E of FIG.

1‧‧‧ Impeller

11‧‧‧The impeller shell

2‧‧‧Motor

21‧‧‧Rotor

22‧‧‧ Stator

23‧‧‧ shaft

231‧‧‧ Cavity

24‧‧‧End cover

25‧‧‧shell

251‧‧‧Outer tube

252‧‧‧ inner tube

253‧‧‧Air intake

254‧‧‧Heat vents

3‧‧‧Rotating connectors

31‧‧‧ side

32‧‧‧air guide vanes

4‧‧‧ trough dynamic pressure gas radial bearing

41‧‧‧ bearing jacket

42‧‧‧ bearing inner sleeve

44‧‧‧End ring

5‧‧‧Combined dynamic pressure gas thrust bearing

51‧‧‧ side disk

52‧‧‧ mid-disc

53‧‧‧Foil type elastic parts

54‧‧‧ mid-plate adjustment ring

6, 7, 8‧ ‧ bolts

61‧‧‧ cavity

Claims (14)

An ultra-high speed blower comprising an impeller, a motor, a rotary joint and a slotted dynamic gas radial bearing, the motor comprising a rotor, a stator, a rotating shaft, an end cover and a casing, the casing being an inner and outer cylinder Forming an annular cylindrical structure of two cavities, the rotating connecting member is a cylindrical structure having a cavity, the rotating connecting member is sleeved on a rotating shaft close to the impeller, and is respectively opposite to the end of the impeller and the rotating shaft a side joint is located in a cavity formed by the outer cylinder and the inner cylinder of the casing; the slotted dynamic gas radial bearing and the rotating shaft are both located in the inner cylinder cavity of the casing, and the groove The dynamic pressure gas radial bearing is sleeved on the rotating shaft; the stator is fixed on the outer wall of the inner cylinder of the casing, and the rotor is fixed on the inner wall of the side of the rotating connecting member. The ultrahigh-speed air blower according to claim 1, wherein a plurality of air guide vanes are provided at a side of the rotary joint located above the air flow passage formed at the end of the rotary shaft and the trough dynamic gas radial bearing. The ultrahigh-speed air blower according to claim 2, wherein a plurality of air intake holes and a plurality of heat dissipation vent holes are formed in a peripheral side of the outer cylinder of the casing. The ultrahigh-speed air blower according to claim 1, wherein the slot type dynamic pressure gas radial bearing comprises a bearing outer casing and a bearing inner sleeve, and the outer circumferential surface and both end surfaces of the inner bearing sleeve have a regular shape groove type. Pattern. The ultrahigh-speed air blower according to claim 4, wherein the groove pattern on one end surface of the bearing inner sleeve is mirror-symmetrical with the groove pattern on the other end surface, and the axial direction of the groove pattern on 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 ultrahigh-speed air blower according to claim 5, wherein an axial high line in the groove pattern on 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 on the outer circumferential surface corresponds to the radial median line in the groove pattern on both end faces, and is chamfered at the end face circumference The front sides are mutually interconnected; the axial lower line in the groove pattern on 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 blower according to any one of claims 1 to 6, wherein said super high speed blower further comprises a hybrid dynamic pressure gas thrust bearing, said hybrid dynamic pressure gas thrust bearing comprising two a side plate and a middle plate sandwiched between the two side plates, a foil-type elastic member is disposed between each of the side plates and the middle plate, and the hybrid dynamic pressure gas thrust bearing is located at the housing and the end cover The cavity is formed and sleeved on the rotating shaft. The ultra-high-speed air blower according to claim 7, wherein a groove pattern of a regular shape is provided on both end faces of the intermediate plate, and the groove pattern on one end surface is mirror-symmetrical with the groove pattern on the other end surface. The ultrahigh-speed air blower according to claim 8, wherein the outer circumferential surface of the intermediate disk is also provided with a groove pattern, and the groove pattern on the outer circumferential surface has the same shape as the groove pattern on both end faces. And the axial contour line of the groove pattern on the outer circumferential surface and the radial contour line of the groove pattern on both end faces form a one-to-one correspondence and mutually overlap. The ultrahigh-speed air blower according to claim 9, wherein the axial high line in the groove pattern on the outer circumferential surface of the middle disk corresponds to the radial high line in the groove pattern on both end faces, and is on the end face circumference The chamfers are mutually overlapped; the axial center line in the groove pattern on the outer circumferential surface corresponds to the radial center 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 on 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 ultrahigh-speed air blower according to claim 7, wherein the foil-type elastic member fixed to one side disk is mirror-symmetrical to the foil-type elastic member fixed to the other side disk. The ultrahigh-speed air blower according to claim 7, wherein the foil-shaped 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, and the wave foil is waved. The transition bottom edge is in contact with the inner end surface of the corresponding side disc. The ultrahigh-speed air blower according to claim 7, wherein the foil-type elastic member is composed of a wave foil and a flat foil, and a transition edge of the wave arch of the wave foil is attached to the flat foil. The ultrahigh-speed air blower of claim 7, wherein the foil-type elastic member is composed of two flat foils, wherein the flat foil adjacent to the end surface of the side disk has a plurality of bubbling, and the arcuate convex top end of the bubbling Another flat foil fits.