WO2016184416A1

WO2016184416A1 - Ultra-high speed turbocharger

Info

Publication number: WO2016184416A1
Application number: PCT/CN2016/082713
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: CN106026517B; WO2016184404A1; CN205858494U; WO2016184414A1; CN205858479U; CN205858948U; CN106014641A; TW201706511A; WO2016184410A1; CN105889097A; TW201706516A; TWI704751B; CN105889314A; WO2016184408A1; WO2016184406A1; CN205864143U; CN105889313B; CN105889097B; CN106026492A; CN205864174U

Abstract

An ultra-high speed turbocharger, comprising a turbine machine (1), a compressor (2), a rotary shaft (3), two radial bearings (4), a thrust bearing (5) and a main housing (6), the radial bearings (4) being groove-type dynamic pressure gas radial bearings, the thrust bearing (5) being a mixed-type dynamic pressure gas thrust bearing, the main housing (6) being sleeved at a central portion of the rotary shaft (3), the two radial bearings (4) being respectively sleeved on the rotary shaft (3) within the main housing (6), the thrust bearing (5) being sleeved on the rotary shaft (3) between the main housing (6) and a pressure wheel (21). 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 turbocharger

Technical field

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

Background technique

The engine generates power by burning fuel in the cylinder. The amount of fuel input is limited by the amount of air sucked into the cylinder, and the generated power is also limited. If the running performance of the engine is at its best, increase it. The output power can only increase the amount of fuel by compressing more air into the cylinder, increasing the combustion function. Under the current technical conditions, the turbocharger is the only mechanical device that can increase the output power of the engine under the same working efficiency. The working principle of the turbocharger is to use the inertial force of the exhaust gas from the engine to push the turbine in the turbine chamber. The turbine drives the coaxial impeller. The impeller pushes the air sent by the air cleaner pipe to pressurize it into the cylinder. When the engine speed increases, the exhaust gas discharge speed and the turbine speed also increase synchronously. The impeller compresses more air into the cylinder. The pressure and density of the air increase to burn more fuel, correspondingly increase the fuel amount and adjust the engine. The speed of the engine can increase the output of the engine.

Since the key component of the turbocharger is the bearing, the current turbocharger usually uses rolling bearings and plain bearings. The following problems exist: due to the use of lubricating oil, oil leakage is inevitable, resulting in leakage of oil through the oil seal. The problem of contamination with the working surface of the intercooler; due to the presence of friction, the rotor speed is low and the efficiency is low; and the bearing life is short due to the presence of wear; it is difficult to adapt to high speed conditions; and, the larger mass of the rotor It also consumes a lot of exhaust energy.

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 turbocharger that can operate stably for a long period of time.

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

An ultra-high speed turbocharger comprising a turbine, a compressor, a rotating shaft, two radial bearings, a thrust bearing and a main casing, the turbine including a turbine, a turbine deflector and a turbine casing, The compressor includes a pressure wheel, a compressor diffuser and a compressor housing; wherein the radial bearing is a slot type dynamic pressure gas radial bearing, including a bearing sleeve and a bearing inner sleeve; the thrust bearing a hybrid dynamic pressure gas thrust bearing comprising two side plates and a middle plate sandwiched between the two side plates, and a foil-type elastic member is disposed between each of the side plates and the middle plate; The casing is sleeved in the middle of the rotating shaft, and the two radial bearings are respectively sleeved on the rotating shaft located in the main casing, and the thrust bearing is sleeved on the main casing and On the shaft between the pressure rollers.

In a further embodiment, the small micro-turbocharger further includes a turbine deflector housing, a rotating sleeve and a left bearing chamber end cover and a right bearing chamber end cover, the rotating shaft sleeve is disposed on the rotating shaft, and the radial bearing And the thrust bearing are sleeved on the rotating sleeve; the turbine housing is fixedly connected with the turbine deflector housing, the turbine deflector housing is fixedly connected with the left bearing chamber end cover, and the left bearing chamber end cover and the main housing The fixed connection; the compressor housing is fixedly connected to the right bearing chamber end cover, and the right bearing chamber end cover is fixedly connected to the main housing.

Preferably, the surface of the rotating shaft is provided with a heat dissipation spiral groove to facilitate heat dissipation of the rotating shaft and the bearing chamber.

Preferably, a plurality of vent holes are formed on the inner circumference of the inner casing of the main casing to facilitate the introduction and discharge of gas, and on the one hand, rapid heat dissipation and exhaust are realized, and on the other hand, air supply to the bearing chamber is realized.

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.

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

The turbocharger provided by the present invention uses gas as a lubricant for the bearing, and therefore has not only pollution-free, low friction loss, long use time, wide application range, energy saving and environmental protection, but also adopts the above 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 realize ultra-high-speed stable operation under air-floating state (tested, the limit speed can reach 100,000-450,000 rpm), so With the same power requirement, the invention can significantly reduce the volume of the turbocharger 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 is remarkable compared with the prior art. Progress.

DRAWINGS

1 is a schematic cross-sectional structural view of a super high speed turbocharger 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 rotating shaft provided in Embodiment 3;

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

The figures in the figure are as follows:

1. Turbine; 11, turbine; 12, turbine deflector; 13, turbine housing; 14, turbine deflector housing; 2, compressor; 21, pressure wheel; 22, compressor diffuser; , compressor housing; 3, shaft; 31, shaft sleeve; 32, heat sink spiral groove; 4, slot type dynamic pressure gas radial bearing; 4a, left end radial bearing; 4b, right end 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, left end Grooved pattern; 4321, radial high position line; 4322, radial middle position line; 4323, radial low position line; 433, groove pattern on the right end surface; 4331, radial high position line; 4332, radial center line; 4333, radial low position line; 44, stop ring; 5, hybrid dynamic pressure gas thrust bearing; 51, side plate; 511, left side disk; 512, right side disk; 513, card slot; 52, middle plate; 521, trough pattern on the left end surface; 5211, radial high position line; 5212, radial middle position line; 5213, radial low position line; 522, trough pattern on the right end surface; 5221 Radial high position line; 5222, radial middle position line; 5223, radial low position line; 523, groove pattern of outer circumferential surface; 5231, axial high position line; 5232, axial center line; 5233, axial low position 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 disk; 531, wave foil; 5311, curved protrusion; 5312 , the transition between the wave arch bottom edge; 532, flat foil; 6, the main housing; 7a, the left bearing chamber end cover; 7b, the right bearing chamber 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

As shown in FIG. 1 , an ultra-high speed turbocharger provided by the embodiment includes a turbine 1 , a compressor 2 , a rotating shaft 3 , two radial bearings 4 , a thrust bearing 5 , and a main casing 6 . The turbine 1 includes a turbine 11 , a turbine deflector 12 and a turbine casing 13 , the compressor 2 including a pressure wheel 21 , a compressor diffuser 22 and a compressor casing 23; The bearing 4 is a slot type dynamic pressure gas radial bearing, comprising a bearing sleeve 41 and a bearing inner sleeve 42; the thrust bearing 5 is a hybrid dynamic pressure gas thrust bearing, comprising two side discs 51 and sandwiched between two A middle plate 52 between the side plates, a foil-type elastic member 53 is disposed between each of the side plates 51 and the middle plate 52; the main casing 6 is sleeved in the middle of the rotating shaft 3, and two radial bearings 4 is respectively sleeved on a rotating shaft 3 located in the main casing 6, and the thrust bearing 5 is sleeved on the rotating shaft 3 between the main casing 6 and the pressing wheel 21.

The small micro turbocharger further includes a turbine deflector housing 14, a rotating sleeve 31 and a left bearing chamber end cover 7a and a right bearing chamber end cover 7b. The rotating sleeve 31 is sleeved on the rotating shaft 3, and the diameter The bearing 4 and the thrust bearing 5 are sleeved on the rotating sleeve 31; the turbine housing 13 is fixedly connected with the turbine deflector housing 14, and the turbine deflector housing 14 is fixedly connected with the left bearing chamber end cover 7a. The left bearing chamber end cover 7a is fixedly coupled to the main housing 6; the compressor housing 23 is fixedly coupled to the right bearing chamber end cover 7b, and the right bearing chamber end cover 7b is fixedly coupled to the main housing 6.

In addition, a plurality of vent holes (not shown) are provided on the inner side of the inner cylinder of the main casing, which can facilitate the introduction and discharge of gas, and on the one hand, can realize rapid heat dissipation and exhaust, and the other side can realize the bearing chamber. Air supply.

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 of the groove pattern 431 and the radial contours of the groove patterns (432 and 433) of the left and right end faces are in one-to-one correspondence with each other and The transfer can ensure that the pressurized gas generated by the groove pattern (432 and 433) of the impeller shape on both end faces is continuously transported from the axial center to the groove passage formed by the groove pattern 431 of the outer circumferential surface, so as to form The gas film required for the high-speed running bearing is more strongly supported, and the gas film is used as the lubricant of the dynamic pressure gas radial bearing, thereby facilitating the high-speed stability of the slot type dynamic pressure gas radial bearing 4 in the air floating state. Running.

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. 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 make the load capacity, the impact resistance and the shaft whirl of the bearing under the elasticity of the bearing. The ability is significantly improved, compared to the existing simple trough dynamic pressure gas thrust bearing, which can have multiple times of impact resistance and load capacity at the same speed.

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 can be seen in conjunction with FIGS. 11a, 11b, 12 to 16, a hybrid dynamic pressure gas thrust bearing provided by the present 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 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, thereby further ensuring the hybrid dynamic pressure gas thrust The high-speed and stable operation of the bearing in the air-floating state provides further guarantee for the high limit 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

As shown in FIG. 17 and FIG. 18, a heat dissipating spiral groove 32 is formed on the surface of the rotating shaft 3 to facilitate heat dissipation of the rotating shaft and the bearing chamber.

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 turbocharger to achieve miniaturization for the same power requirement, and promote miniaturization. The development of high technology has important 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 turbocharger comprising a turbine, a compressor, a rotating shaft, two radial bearings, a thrust bearing and a main casing, the turbine including a turbine, a turbine deflector and a turbine casing, The compressor includes a pressure wheel, a compressor diffuser and a compressor housing; wherein the radial bearing is a slot type dynamic pressure gas radial bearing, including a bearing sleeve and a bearing inner sleeve; the thrust bearing a hybrid dynamic pressure gas thrust bearing comprising two side plates and a middle plate sandwiched between the two side plates, and a foil-type elastic member is disposed between each of the side plates and the middle plate; The casing is sleeved in the middle of the rotating shaft, and the two radial bearings are respectively sleeved on the rotating shaft located in the main casing, and the thrust bearing sleeve is sleeved on the rotating shaft between the main casing and the pressure roller.
The super-high speed turbocharger according to claim 1, wherein said small micro-turbocharger further comprises a turbine deflector housing, a rotating sleeve and a left bearing chamber end cover and a right bearing chamber end cover The rotating shaft sleeve is disposed on the rotating shaft, and the radial bearing and the thrust bearing are sleeved on the rotating shaft sleeve; the turbine housing is fixedly connected with the turbine deflector housing, and the turbine deflector housing and the left bearing chamber end are respectively The cover is fixedly connected, and the left bearing chamber end cover is fixedly connected with the main housing; the compressor housing is fixedly connected with the right bearing chamber end cover, and the right bearing chamber end cover is fixedly connected with the main housing.
The super high speed turbocharger according to claim 1 or 2, characterized in that the surface of the rotating shaft is provided with a heat dissipating spiral groove.
The super-high speed turbocharger according to claim 1 or 2, wherein a plurality of vent holes are formed in a peripheral side of the inner cylinder of the main casing.
The super-high speed turbocharger according to claim 1, wherein both the outer circumferential surface and the both end surfaces of the bearing inner sleeve have regular groove patterns.
The super-high speed turbocharger according to claim 5, 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 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.
The super-high speed turbocharger according to claim 6, wherein an axial high line in the groove pattern of the outer circumferential surface of the bearing inner sleeve and a radial high position line in the groove pattern on both end faces Corresponding to each other 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 is on the end face circumference The chamfers are mutually overlapped; 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 super high speed turbocharger according to claim 1, wherein both end faces of the intermediate plate are provided with a regular pattern of groove patterns, and a groove pattern of one end face and a groove pattern of the other end face. Form mirror symmetry.
The super-high speed turbocharger according to claim 8, wherein a groove pattern is also provided on an outer circumferential surface of the intermediate disk, and a groove pattern of the outer circumferential surface and a groove type on both end faces are provided. The shape of the pattern is the same, as well as the outer circle 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 patterns on both end faces and intersects each other.
The super-high speed turbocharger according to claim 9, 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 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 super-high speed turbocharger 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 super high speed turbocharger according to claim 1 or 11, wherein said foil-shaped elastic member is composed of a wave foil and a flat foil, and the curved convex top end of said wave foil is fitted to the flat foil. .
The super high speed turbocharger according to claim 1 or 11, 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. Hehe.
The super high speed turbocharger according to claim 1 or 11, wherein said foil-type elastic member is composed of two flat foils.