WO2016184404A1

WO2016184404A1 - Ultra-high speed blower

Info

Publication number: WO2016184404A1
Application number: PCT/CN2016/082676
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: CN205858730U; CN106026492B; CN205858494U; CN105889313A; CN205864143U; CN105889314B; WO2016184406A1; CN106026517B; CN105888818A; CN105889097B; WO2016184410A1; TW201706516A; CN205864174U; CN205858948U; CN106014641A; CN106014641B; CN105889097A; TWI704751B; TWI694210B; CN105889314A

Abstract

An ultra-high speed blower, comprising an impeller (1), a motor (2), a rotating connecting piece (3) and a groove-type dynamic pressure gas radial bearing (4). The motor comprises a rotor (21), a stator (22), a rotary shaft (23), an end cover (24) and a housing (25), the housing (25) being an annular cylindrical structure formed of an inner cylinder and an outer cylinder and having two cavities, the rotating connecting piece (3) being a cylindrical structure having a single cavity, the rotating connecting piece being sleeved on the rotary shaft (23) near to the impeller (1), and being respectively fitted with and connected to the impeller (1) and an end portion of the rotary shaft (23), a side portion (31) of the rotating connecting piece being located within a cavity formed by the outer cylinder (251) and the inner cylinder (252) of the housing. The groove-type dynamic pressure gas radial bearing (4) and the rotary shaft (23) are located within a cavity of the inner cylinder (252) of the housing, and the groove-type dynamic pressure gas radial bearing (4) is sleeved on the rotary shaft (23). The stator (22) is fixed on an outer wall of the inner cylinder (252) of the housing, and the rotor (21) is fixed on an inner wall of the side portion (31) of the rotating connecting piece (3). The blower implements an ultra-high speed operation in an air state, and with regard to identical power requirements, the size of the blower is significantly reduced for miniaturisation.

Description

Ultra high speed blower

Technical field

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

Background technique

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 many defects of the conventional motor blower, Chinese Patent Publication No. CN102200136B 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.

Summary of the invention

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 a motor, the motor comprising a rotor, a stator, a rotating shaft, an end cover and a casing; and further comprising: a rotary connecting member and a slot type dynamic pressure gas radial bearing, and The housing is an annular cylindrical structure formed by two inner and outer cylinders, the rotary connecting member is a cylindrical structure having a cavity, and the rotating connecting member is sleeved on a rotating shaft close to the impeller Up, and respectively coupled with the impeller and the end of the rotating shaft, 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 slot type dynamic pressure gas radial bearing and The rotating shaft is 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 on the outer cylinder outer wall of the casing, and the rotor is fixed on the rotating connecting member On the inner wall of the side.

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.

As an embodiment, the ultra high speed blower further includes a hybrid dynamic pressure gas thrust bearing, the hybrid dynamic pressure gas thrust bearing includes two side plates and is sandwiched between the two side plates a middle plate, 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 formed at the housing and the end cover Inside the cavity, and sleeved on the 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 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.

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 in phase with the other flat foil. fit.

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 blower provided by the present invention uses gas as a lubricant for the bearing, so that it has not only pollution-free, friction Low loss, long use time, wide application range, energy saving and environmental protection, etc., and adopting the structure, the heat dissipation effect is good, and the stable operation can be ensured for a long time; in particular, the air bearing of the structure can be realized in an air floating state. Under the ultra-high speed operation (tested, the limit speed can reach 100,000 ~ 450,000 rpm), so for the same power requirements, the present invention can significantly reduce the volume of the blower to achieve miniaturization, has the advantages of small footprint, convenient use, and the like. It is of great value to promote the development of miniaturized high-tech, and has significant progress compared to the prior art.

DRAWINGS

1 is a front perspective view of a super high speed blower provided in Embodiment 1;

Figure 2 is a front elevational view showing the structure of the super high speed blower provided in the first embodiment;

Figure 3 is a view taken along line A-A of Figure 2;

4 is a schematic perspective structural view of a rotary joint provided in Embodiment 1;

Figure 5 is a perspective view showing the structure of the housing provided in Embodiment 1;

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

Figure 7 is a partial enlarged view of B in Figure 6;

Figure 8 is a partially exploded right perspective view showing the slot type dynamic pressure gas radial bearing provided in Embodiment 1;

Figure 9 is a partial enlarged view of C in Figure 8;

10 is a schematic cross-sectional structural view of a 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 with the foil-type elastic member fixed in Embodiment 1;

Figure 13 is a schematic cross-sectional view showing the foil-type elastic member provided in Embodiment 1;

Figure 14 is a perspective view showing the structure of the foil-type elastic member provided in Embodiment 1;

Figure 15a is a left side perspective structural view of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 2;

Figure 15b is a right perspective view showing the hybrid dynamic pressure gas thrust bearing of the second embodiment;

Figure 16 is a partially sectional perspective structural view of the hybrid dynamic pressure gas thrust bearing provided in the second embodiment;

Figure 17 is a left perspective view showing the middle plate of the second embodiment;

Figure 18 is a partial enlarged view of D in Figure 17;

Figure 19 is a right perspective view showing the center disk of the second embodiment;

Figure 20 is a partial enlarged view of E in Figure 19.

The figures in the figure are as follows:

1, impeller; 11, impeller shell; 2, motor; 21, rotor; 22, stator; 23, shaft; 231, shaft cavity; 24, end cover; 25, housing; 251, housing outer cylinder; , the inner cylinder of the casing; 253, the air inlet hole; 254, the heat dissipation vent hole; 3, the rotating connection member; 31, the side portion of the rotating connection member; 32, the air guiding blade; 4, the slot type dynamic pressure gas radial Bearing; 41, bearing jacket; 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 line 432, trough pattern on the left end face; 4321, radial high bit line; 4322, radial center line; 4323, radial low line; 433, trough pattern on the right end face; 4331, radial high line; 4332 Radial neutral line; 4333, radial low line; 44, stop ring; 5, hybrid dynamic pressure gas thrust bearing; 51, side disc; 511, left side disc; 512, right side disc; 513, card slot 52, middle plate; 521, trough pattern on the left end face; 5211, radial high position line; 5212, radial center line; 5213, radial low line; 522, trough pattern on the right end face; Radial high position line; 5222, radial center line; 5223, radial low line; 523, groove pattern of outer circumferential surface; 5231, axial high line; 5232, axial center line; 5233, axial a lower position line; 53, a foil-type elastic member; 53a, a foil-type elastic member fixed on the left side disk; 53b, a foil-type elastic member fixed on the right side disk; 531, a wave foil; a curved protrusion; 5312, the transition bottom edge between the arches; 532, flat foil; 54, the middle disc adjustment ring; 6, the locking bolt; 61, the locking bolt cavity; 7, the bolt fixing the impeller shell; 8, the bolt fixing the end cover .

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

1 to 5: an ultrahigh 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, It is characterized in that it further comprises a rotary joint 3, a trough dynamic pressure gas radial bearing 4 and a hybrid dynamic pressure gas 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 is interposed between the two side discs Disk 52, in each side disk 51 and middle plate 52 A foil-type elastic member 53 is disposed therebetween, and the hybrid dynamic pressure gas thrust bearing 5 is disposed in a cavity formed by the housing 25 and the end cover 24, and is sleeved 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. Dynamic pressure gas generated It is well sealed and stored in the entire fit clearance of the bearing, which fully guarantees the lubrication of the high-speed 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, at each side disc A foil-shaped elastic member 53 is disposed between the 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.

11a and 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 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.

12a and 12b, it can be seen that the foil-type elastic member 53 is fixed on 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 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.

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 prolong the service life of the bearing, Preferably, a wear-resistant coating (not shown) is provided on the mating surface of the foil-type elastic member 53 which is engaged with the intermediate plate 52.

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 (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 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 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 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.

In addition, 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. It is also possible to use a wave foil and a flat foil composition, but the transition edge between the wave arches of the wave foil is bonded to the flat foil; or, directly, two flat foils are used, wherein the flat foil near the end surface of the side disk has a plurality of bubbling The bubbled convex top end is conformed to the other flat foil; or other existing structures are employed.

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 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. All improvements and adjustments are within the scope of the invention.

Claims

An ultra-high-speed air blower comprising an impeller and a motor, the motor comprising a rotor, a stator, a rotating shaft, an end cover and a casing; and further comprising: a rotary connecting member and a slot type dynamic pressure gas radial bearing, and The housing is an annular cylindrical structure formed by two inner and outer cylinders, the rotary connecting member is a cylindrical structure having a cavity, and the rotating connecting member is sleeved on a rotating shaft close to the impeller Up, and respectively coupled with the impeller and the end of the rotating shaft, 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 slot type dynamic pressure gas radial bearing and The rotating shaft is 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 on the outer cylinder outer wall of the casing, and the rotor is fixed on the rotating connecting member On the inner wall of the side.
The ultrahigh-speed air blower according to claim 1, wherein a plurality of air guide vanes are provided at a side portion of the rotary joint member above the air flow passage formed at the end of the rotary shaft and the slot type dynamic pressure gas radial bearing. .
The ultrahigh-speed air blower according to claim 2, wherein a plurality of 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 said slot type dynamic pressure gas radial bearing comprises a bearing outer casing and a bearing inner sleeve, and said bearing inner sleeve has a rule on an outer circumferential surface and both end surfaces The groove pattern of the shape.
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 groove pattern on 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.
The ultrahigh-speed air blower according to claim 5, wherein an axially high bit line in the groove pattern on the outer circumferential surface of the bearing inner sleeve and a radial high line in the groove pattern on both end faces are both Corresponding to each other 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 at the end face The circumferential chamfers are mutually overlapped; the axially 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 ultrahigh 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 The utility model comprises two side plates and a middle plate sandwiched between the two side plates, wherein 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 The housing is formed in the cavity formed by the end cover and sleeved on the rotating shaft.
The ultrahigh-speed air blower according to claim 7, wherein both end faces of the intermediate plate are provided with a regular groove pattern, and the groove pattern on one end surface and the groove pattern on the other end surface Form mirror symmetry.
The ultrahigh-speed air blower according to claim 8, wherein a groove pattern is also provided on an outer circumferential surface of the intermediate disk, and a groove pattern on the outer circumferential surface and a groove pattern on both end faces are provided. The shape of the pattern is the same, and the outside The axial contour of the groove pattern on the circumferential surface forms a one-to-one correspondence with the radial contour lines of the groove pattern on both end faces and intersects each other.
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 intermediate disk corresponds to the 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 super high speed blower according to claim 7, 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 ultrahigh-speed air blower according to claim 7, 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 a flat foil, said wave foil The transition bottom edge of the wave arch is matched with the inner end surface of the corresponding side disk.
The ultrahigh-speed air blower according to claim 7, wherein said foil-type 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 ultrahigh-speed air blower according to claim 7, wherein said foil-shaped elastic member is composed of two flat foils, wherein a flat foil adjacent to an end surface of the side disk has a plurality of bubbling, said bubbling arc convex The top end is fitted to another flat foil.