CN102057164B - Turbo blower and high speed rotating body used in same - Google Patents

Abstract

This invention relates to a turbine blower and a high-speed rotating body used therein. The turbine blower includes: i) an engine having an engine shaft; ii) a gear housing housing a large gear fixed to the engine shaft and a small gear meshing with the large gear; iii) a high-speed rotating body including a rotating shaft with the small gear disposed on its outer circumferential surface, an impeller coupled to one end of the rotating shaft, and a rotating body housing housing the rotating shaft, the small gear, and at least one first combined bearing, partially cut open to expose the small gear, and a portion of the high-speed rotating body being housed within and coupled to the gear housing; and iv) a volute surrounding the impeller and outputting compressed air.

Description

Turbo blower and high-speed rotating body used for the blower

technical field

The present invention relates to a turbo blower, in particular to a turbo blower capable of minimizing axial load and radial load during driving and a high-speed rotating body used for the blower.

Background technique

In order to obtain small volume and high output, turbo blowers generally use high-speed rotating bodies. The high-speed rotating body can be divided into direct drive mode and indirect drive mode according to its drive mode. Among them, the direct drive method is directly connected with a high-speed engine, and the indirect drive method is connected with a general engine through a gear speed increaser for increasing the rotational speed.

The high-speed rotating body of the direct drive method is usually supported by air bearings. However, air bearings have many limitations in long-term use (for example, 3 years or more) due to poor component durability.

A common gear speed increaser used in a high-speed rotating body of an indirect drive method consists of a bull gear and a pinion gear. Wherein, the large gear is combined on the engine shaft, and the small gear is arranged on the high-speed rotating body and meshed with the large gear. However, when a turbo blower equipped with a gear speed increaser is in operation, radial and axial loads will be generated on the high-speed rotating body and the large gear, so it is necessary to improve the structure in order to reduce the load.

Furthermore, a turbo blower equipped with a gear speed increaser uses a gearbox with a large gear and a small gear built in, and in order to mount the gearbox to the turbomachinery, not only the gearbox itself needs to be made horizontally separated, but also the The bearings supporting the above two gear shafts are made into a horizontal split type.

When manufacturing the gearbox in such a separate manner, the manufacturing accuracy is poor, and after the turbomachinery is assembled, it is difficult to ensure the assembly accuracy when centering the gear shaft for high-speed rotation. In addition, due to the increase in the number of components, the production cost will increase.

In order to supply lubricating oil, an indirect drive type turbo blower needs an oil pump, which increases the number of components. Moreover, in the prior art, the bull gear and the engine shaft are combined by shrinkfit. When the bull gear needs to be replaced due to wear and other reasons of the teeth of the bull gear, there is a problem that the bull gear is difficult to disassemble and assemble.

Contents of the invention

An object of the present invention is to provide a turbo blower capable of minimizing the axial load and radial load acting on a high-speed rotating body and a gearwheel.

The present invention also provides a turbo blower capable of circulating and supplying lubricating oil to a high-speed rotating body without providing an oil pump for supplying lubricating oil by forming an oil circulation structure in the turbo blower.

The present invention also provides a turbo blower which can simplify the assembly and disassembly of the high-speed rotating body, the large gear and the engine.

A turbo blower related to an embodiment of the present invention includes: i) an engine with an engine shaft; ii) a gear housing with a built-in bull gear coupled to the engine shaft and a pinion meshing with the bull gear; iii) A high-speed rotating body, the high-speed rotating body includes a rotating shaft provided with a pinion on the outer peripheral surface, an impeller combined with one end of the rotating shaft, and a built-in rotating shaft and pinion and at least one first combination bearing, and is partially covered by A rotating body casing that is cut open to expose the pinion gear, and a part of the high-speed rotating body is built in and combined with the gear casing; and iv) a volute that wraps the impeller and outputs compressed air.

The first combined bearing may include: i) a combined bearing seat, which is provided with a sliding bearing seat and a ball bearing seat integrally formed; ii) a sliding bearing shaft, which is arranged on the outer peripheral surface of the rotating shaft and built into In the sliding bearing housing, a sliding bearing is formed together with the sliding bearing housing; and iii) a ball bearing, which is built into the ball bearing housing.

The first combination bearing is located on both sides of the pinion, and the setting gap of the sliding bearing may be larger than that of the ball bearing. A plurality of oil grooves and a plurality of taper grooves are arranged obliquely on the surface of the sliding bearing shaft to form an oil film on the surface, and a side pressure buffer groove is arranged on the inner surface of the sliding bearing seat opposite to the large gear, so that it can absorb Side pressure caused by large gears.

In addition, the high-speed rotating body is provided with ventilation holes on the end of the rotating body casing opposite to the impeller, and the pinion gear is formed in the shape of a helical gear. The force pulling the axis of rotation.

A guide cover with a circular arc shape is provided on the inner wall of the gear housing, which surrounds a part of the large gear and has a plurality of oil guide grooves, and the inner upper part of the gear housing can be provided with a guide cover connected to the end of the guide cover. tank.

An oil pipe is provided inside the gear housing to supply lubricating oil collected in the oil tank to the first composite bearing. One end of the oil pipe is connected to the oil discharge port provided on the oil tank, and the other end of the oil pipe is connected to the first composite bearing. connected to the oil supply port on the

The casing of the rotating body is provided with a steam discharge port for discharging oil vapor, and the turbo blower may further include an oil vapor cooler connected with the steam discharge port and the oil tank. Also, the oil vapor cooler can condense the oil vapor discharged from the vapor discharge port and supply it into the oil tank.

The lower part of the gear housing is provided with an oil storage tank, and the oil storage tank is provided with a pair of holes on the upper and lower positions of the side wall. The gear housing may further include a communication pipe for connecting the pair of holes and a control valve arranged in the communication pipe.

The bull gear is directly connected to the engine shaft, and the gear housing is provided with a joint surface on the side opposite to the engine, and the joint surface has an opening with a diameter larger than that of the bull gear, and the joint surface can be combined with the engine.

A high-speed rotating body according to an embodiment of the present invention includes: i) a rotating shaft, a pinion gear meshing with a large gear is arranged on the outer peripheral surface of the rotating shaft; ii) an impeller, which is combined with one end of the rotating shaft; iii) A pair of first combination bearings, the pair of first combination bearings are arranged on both sides of the pinion; and iv) a rotating body housing, the rotation body casing has a rotating shaft, a pinion, and a pair of first combination bearings built in, and rotates A portion of the body shell is cut away to expose the pinion.

A pair of first composite bearings may respectively include: i) a composite bearing seat, which is provided with a sliding bearing seat and a ball bearing seat integrally formed; ii) a sliding bearing shaft, which is arranged on the outer peripheral surface of the rotating shaft , and built into the sliding bearing housing to constitute the sliding bearing together with the sliding bearing housing; and iii) a ball bearing, which is built into the ball bearing housing.

The setting clearance of the sliding bearing is larger than that of the ball bearing, and the surface of the sliding bearing shaft is provided with a plurality of oil grooves and a plurality of tapered grooves obliquely to form an oil film on the surface, and in order to absorb the side pressure caused by the large gear, when sliding The inner surface of the bearing seat may be provided with a side pressure buffer groove in a direction opposite to the side pressure direction.

Another embodiment of the present invention relates to a turbo blower comprising: i) an engine having an engine shaft; ii) a large gear that is detachably coupled to the engine shaft, and is provided with a center shaft for mounting a fixed shaft; iii) a second combined bearing, which is disposed between the fixed shaft and the bull gear, and has a tapered roller bearing and a ball bearing adjacent to the engine shaft in a side-by-side direction; and iv) a high-speed A rotating body, the high-speed rotating body has a rotating shaft provided on an outer peripheral surface with a pinion gear meshed with a large gear, and an impeller coupled to one end of the rotating shaft.

The turbo blower may further include: i) an engine cover which is integrated with the engine and serves to support the engine shaft; and ii) a gear housing which houses a large gear and a pinion and is on the side where the engine cover is integrated An opening having a diameter larger than that of the bull gear is provided.

The engine shaft is provided with a flange on the outer peripheral surface of the end opposite to the bull gear, and the bull gear is combined with the engine shaft through a plurality of joint bolts passing through the bull gear and the flange. Openings are provided at positions opposite to the coupling bolts. The engine cover has a recess protruding toward the engine, and accommodates a part of the high-speed rotating body into the recess.

The high-speed rotating body may further include: i) a pair of first combined bearings, the pair of first combined bearings are arranged on both sides of the pinion; A composite bearing mounted on the gear housing and partially cut away to expose the pinion from inside the gear housing.

The first combined bearing may respectively include: i) a combined bearing seat, which is provided with a sliding bearing seat and a ball bearing seat integrally formed; ii) a sliding bearing shaft, which is arranged on the outer peripheral surface of the rotating shaft, built into the sliding bearing housing to constitute the sliding bearing together with the sliding bearing housing; and iii) a ball bearing built into the ball bearing housing.

The installation gap of the sliding bearing is larger than that of the ball bearing, and a plurality of oil grooves and a plurality of tapered grooves are obliquely arranged on the surface of the sliding bearing shaft to form an oil film on the surface.

An arc-shaped guide cover and a stepped protrusion are arranged on the inner wall of the gear housing, wherein the guide cover surrounds a part of the bull gear, and the protrusion is located outside the side of the bull gear, and the protrusion is between the gear housing and The interior of the assembly of the engine cover forms a temporary storage tank.

The inner surface of the guide cover may be provided with a plurality of oil guide grooves, and the plurality of oil guide grooves extend along the rotation direction of the bull gear. The gear housing is provided with a first through opening at the position where the temporary storage tank is provided, and the gear housing may further include a first oil pipe, and the first oil pipe is used to connect the first through opening and the fixed shaft outside the gear housing.

The fixed shaft is combined with the gear housing, and the fixed shaft is provided with an oil hole inside, and a flow channel is provided between the fixed shaft and the engine shaft, so that the lubricating oil supplied to the oil hole can be guided to the second combined bearing.

The lower end of the protruding part is provided with a second through opening, and the part of the gear housing that is in contact with the rotating body housing is provided with a third through opening, and the inside of the gear housing may further include a connection between the first through opening and the third through opening. Second tubing.

The inside of the casing of the rotating body is provided with an oil passage for connecting the first combination bearing on the impeller side of the pair of first combination bearings and the third through port, and the outside of the casing of the rotating body may further include a third oil pipe for connecting The first combined bearing and the oil passage on the side opposite to the impeller in the pair of first combined bearings.

The high-speed rotating body can further include a support between the first combined bearing on the impeller side and the impeller, and an oil discharge port is arranged on the support and the rotating body casing, and the rotating body casing can further include a fourth oil pipe on the outside for Connect the oil drain to the gear housing to recover the lubricating oil.

The turbo blower may further include: i) a bearing and a seal, which are arranged side by side on the outer peripheral surface of the engine shaft in a direction away from the bull gear; and ii) a fifth oil pipe, which is used to connect the seal parts and the inside of the engine cover to recover lubricating oil that reaches the seals.

Still another embodiment of the present invention relates to a turbo blower comprising: i) an engine having an engine shaft and being assembled with an engine cover; ii) a bull gear detachably coupled to the engine shaft, and The center is provided with a middle hole for setting a fixed shaft; iii) a high-speed rotating body, which includes a rotating shaft whose outer peripheral surface is provided with a pinion gear meshed with a large gear, an impeller combined with one end of the rotating shaft, and used to support the rotating shaft At least one first combined bearing of the at least one combined bearing, and a rotating body housing with a built-in rotating shaft and the first combined bearing, and a part of which is cut away to expose the pinion; iv) a second combined bearing, which is provided on the fixed shaft and the bull gear, and have adjacent tapered roller bearings and ball bearings along the direction alongside the engine shaft; v) the gear housing, which houses the bull gear and pinion, and is combined with the engine cover and vi) a volute that surrounds the impeller and outputs compressed air.

According to the present invention, the combination bearing is used to absorb the axial load and the radial load of the high-speed rotating body and the large gear, and the integral combination bearing seat is used to make the assembly precision high, so that it can be widely used in the field of turbo blower.

According to the present invention, an efficient lubricating oil supply system is provided, and a turbo blower capable of stable operation for a long period of time can be provided without using an oil pump.

According to the present invention, power can be transmitted to the bull gear without using the conventional bull gear rotating shaft for transmitting power to the bull gear, and an economical and long-lasting turbo blower can be provided using a small number of parts.

According to the present invention, when the large gear needs to be replaced or repaired, the high-speed rotating body, the large gear and the engine can be easily assembled and disassembled.

Description of drawings

Fig. 1 is a front view of a turbo blower according to a first embodiment of the present invention.

Fig. 2 is a left side view of the turbo blower shown in Fig. 1 .

Fig. 3 is a perspective view of a gear housing in the turbo blower shown in Fig. 1 viewed from the impeller side.

Fig. 4 is a perspective view of a gear housing in the turbo blower shown in Fig. 1 viewed from the engine side.

Fig. 5 is a cross-sectional view showing a high-speed rotating body of the turbo blower shown in Fig. 1 .

Fig. 6 is a front view of a rotating shaft of the turbo blower shown in Fig. 1 .

7 is a schematic diagram showing a lubricating oil circulation system using a front sectional view, a side sectional view, and a sectional view of a high-speed rotating body of the turbo blower shown in FIG. 1 .

Fig. 8 is a plan view of a turbo blower according to a second embodiment of the present invention.

Fig. 9 is a cross-sectional view of the engine shaft and the bull gear of the turbo blower shown in Fig. 8 as viewed in the A direction.

FIG. 10 is a partially enlarged view of FIG. 9 .

Fig. 11 is a partially enlarged view of the gear casing and the large gear in the turbo blower shown in Fig. 8 .

Fig. 12 is a perspective view of the engine cover of the turbo blower shown in Fig. 8 viewed from direction B.

Fig. 13 is a perspective view of the gear housing in the turbo blower shown in Fig. 8 viewed from direction C.

Fig. 14 is a cross-sectional view of line I-I in Fig. 13 .

Fig. 15 is a front view of the gear housing shown in Fig. 13 viewed from the direction D.

Fig. 16 is a front view of the turbo blower shown in Fig. 8 viewed from the direction C.

Fig. 17 is a right side view of the turbo blower shown in Fig. 8 as viewed from B direction.

Fig. 18 is a front view of the high-speed rotating body in the turbo blower shown in Fig. 8 .

Detailed ways

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings, so that those skilled in the art of the present invention can easily implement them. The present invention can be implemented in various ways and is not limited to the embodiments shown here.

FIG. 1 is a front view of a turbo blower 100 according to the first embodiment of the present invention, which shows a section of a high-speed rotating body 20 in section. FIG. 2 is a left side view of turbo blower 100 shown in FIG. 1 .

Referring to FIGS. 1 and 2 , the turbo blower 100 of the first embodiment includes a supporting platform 10 , a motor 11 , a gear housing 12 and a volute 13 . An engine 11 and a gear housing 12 are fixed to the support base 10 , and a part of a high-speed rotating body 20 described later is located inside the gear housing 12 .

In the turbo blower 100 of the first embodiment, the engine shaft 14 coupled to the engine 11 is not directly connected to the rotating shaft 21 of the high-speed rotating body 20, but both are offset. That is, the engine shaft 14 is directly connected with the bull gear 15 , and the rotating shaft 21 is provided with the pinion gear 16 , and the bull gear 15 and the pinion gear 16 increase the power of the engine 11 through engagement to drive the high-speed rotating body 20 .

The first embodiment adopts the aforementioned power transmission structure, so that the large gear shaft used to support the large gear in the existing speed-increasing gearbox can be eliminated, and the problem of sealing between the engine and the gearbox can be solved, and components can be reduced at the same time quantity, thereby reducing manufacturing costs.

In order to directly combine the large gear 15 on the engine shaft 14, as shown in Figures 3 and 4, the gear housing 12 is integrally made, and the side of the gear housing 12 fixed to the engine 11 is open, and the degree of opening is greater than that of the large gear 15 diameter. Furthermore, a bracket 17 for fixing the gear housing 13 is provided on the engine 11 .

3 is a perspective view of the gear housing 12 in the turbo blower 100 shown in FIG. 1 viewed from the impeller 22 , and FIG. 4 is a perspective view of the gear housing 12 in the turbo blower 100 shown in FIG. 1 viewed from the engine 11 .

In FIG. 3 , reference numeral 121 denotes a first coupling surface coupling the high-speed rotating body 20 and the volute 13 to the gear housing 12 . In FIG. 4 , reference numeral 122 denotes a second bonding surface for bonding the gear housing 12 itself to the bracket 17 of the engine 11 .

The high-speed rotating body 20 or the bracket 17 of the engine 11 can be combined on the first joint surface 121 and the second joint surface 122 of the gear housing 12 using conventional mechanical joint methods such as the joint of bolts and nuts. In addition, conventional sealing devices such as rubber gaskets are provided on the first joint surface 121 and the second joint surface 122 to separate the outside and the inside of the gear housing 12 to seal the inside. The combination method and sealing device are common structures, so the detailed description thereof is omitted here.

Through the above-mentioned gear housing 12, the large gear with a larger diameter can be installed on the engine shaft 14 earlier when assembling, and the second joint surface 122 of the gear housing 12 is installed on the bracket 17 of the engine 11, and then the gear housing The high-speed rotating body 20 and the volute 13 are sequentially installed on the first joint surface 121 of the 12 .

The high-speed rotating body 20 will be described in detail below with reference to FIG. 5 . FIG. 5 is a cross-sectional view of the high-speed rotating body 20 of the turbo blower 100 shown in FIG. 1 , and the dotted line part is an exploded view showing the first combined bearing 26 .

Referring to Fig. 5, the high-speed rotating body 20 comprises a rotating shaft 21, a rotating body casing 23 with the rotating shaft 21 built in, a pair of first combination bearings 26 integrally formed of a sliding bearing 24 and a ball bearing 25, and a pair of combined bearings combined with one end of the rotating shaft 21. impeller 22.

The rotating body casing 23 is formed in a cylindrical shape as a whole, and unlike the separate type used in conventional high-speed rotating bodies, the rotating body casing 23 of the present invention is integrally produced. At a portion of the rotating shaft 21 where the pinion gear 16 is formed, a part of the rotating body casing 23 is cut away so that the pinion gear 16 is exposed to the outside of the rotating body casing 23 . The pinion 16 thus exposed meshes with the large gear 15 inside the gear housing 12 .

Moreover, a flange 27 is provided at the middle part of the rotating body housing 23 , and a plurality of coupling holes 271 are provided on the flange 27 , so that the rotating body housing 23 can be assembled on the first coupling surface 121 of the gear housing 12 . Furthermore, a plurality of holes are provided in the rotating body housing 23 for supplying lubricating oil to a first combination bearing 26 to be described later and for discharging lubricating oil. This hole will be described in detail later.

With the pinion gear 16 provided on the rotating shaft 21 as the center, first combination bearings 26 are respectively provided on both sides thereof. The first combined bearing 26 is configured such that a sliding bearing shaft 241 and a ball bearing 25 are provided inside one combined bearing housing 28 .

As shown by the dotted line in FIG. 5 , the first composite bearing 26 includes a composite bearing housing 28 , a sliding bearing shaft 241 and a ball bearing 25 . The combined bearing seat 28 has a sliding bearing seat 281 and a ball bearing seat 282, and the two bearing seats are integrally structured. Further, the sliding bearing shaft 241 is provided on the outer peripheral surface of the rotating shaft 21 and is built in the sliding bearing housing 281 to constitute the sliding bearing 24 together with the sliding bearing housing 281 . The ball bearing 25 is disposed inside the ball bearing housing 282 . The ball bearing 25 includes balls 251 , and an outer ring 252 and an inner ring 253 surrounding the balls 251 , and the balls 251 directly support a load during low-speed operation.

In the dotted line portion of FIG. 5 , reference numeral 261 denotes a ring fixed between the composite bearing housing 28 and the rotating body housing 23 , and reference numeral 262 denotes a coupling ring coupling the ball bearing 25 to the composite bearing housing 28 . Also, reference numeral 263 denotes a nut for fixing the combined bearing housing 28 to the rotating shaft 21 .

In the turbo blower 100 of the first embodiment, the reasons for using the first combination bearing 26 on the high-speed rotating body 20 are as follows:

If only sliding bearings are used on the high-speed rotating body, although the oil pressure generated by high-speed rotation can support a large load, in the non-high-speed rotating state, that is, in the case of starting, stopping or low-speed operation, the sliding The housing and the rotating shaft will be in direct contact. Therefore, not only is it difficult to start, but also heat and wear problems caused by friction will occur. In order to solve these problems, an oil pump must be used to force lubrication.

On the contrary, if only ball bearings are used on the high-speed rotating body, it can solve the friction problem when starting, stopping or running at low speed, and has the advantage of only needing to provide unpressurized lubricating oil in the state of no oil pump. However, when rotating at a high speed, the ball bearing bears a large load, so there is a disadvantage in that the durability decreases.

Therefore, in the turbo blower 100 of the first embodiment, the high-speed rotating body 20 has the first combination bearing 26 composed of the sliding bearing 24 and the ball bearing 25, so that all the above-mentioned problems can be solved.

As mentioned above, if the first combination bearing 26 is used on the high-speed rotating body 20, the rotating shaft 21 and the combination bearing housing 28 will not be in direct structural contact due to the presence of the ball bearing 25 . Therefore, when the turbo blower 100 of the present invention is driven at a low speed in the initial state, the ball bearing 25 can support the driving of the high-speed rotating body 20 , and when it is driven at a high speed, the sliding bearing 24 can support the driving of the high-speed rotating body 20 .

According to the above-mentioned structure of the first combination bearing 26, when the high-speed rotating body 20 is driven, the load supporting function is automatically changed according to the operating range (rotating speed). That is, at the time of low-speed driving including start-up operation and stop operation, a load is applied to the balls 251 so that the ball bearing 25 supports the load, and the slide bearing 24 operates in a no-load state. At the same time, if the rotation speed increases, the thickness of the oil film formed on the sliding bearing 24 increases, the sliding bearing 24 supports the load at a predetermined speed or more, and the ball bearing 25 operates under no load.

For this reason, the installation gap of the slide bearing 24 is formed larger than the installation gap of the ball bearing 25 . Here, the installation clearance of the sliding bearing 24 means the difference between the inner diameter of the sliding bearing housing 281 and the diameter of the sliding bearing shaft 241, and the installation clearance of the ball bearing 25 means subtracting the ball from the difference between the inner diameter of the outer ring 252 and the outer diameter of the inner ring 253. 251 diameter value. The difference in the setting clearance will be described below. When the setting clearance of the sliding bearing 24 is 0.2 mm, the setting clearance of the ball bearing 25 may be 0.1 mm.

In addition, in the first embodiment, even without an additional oil pump, the sliding bearing 24 of the first combination bearing 26 can form an oil film. This part will be described below with reference to FIG. 6 .

FIG. 6 is a front view of the rotary shaft 21 of the turbo blower 100 shown in FIG. 1 , showing both a left view and a right view of the rotary shaft 21 .

Referring to FIG. 6 , a plurality of oil grooves 242 and a plurality of tapered grooves 243 for supplying lubricating oil are provided on the surface of the sliding bearing shaft 241 provided on the rotating shaft 21 . The plurality of oil grooves 242 and the plurality of tapered grooves 243 are arranged obliquely in the direction of the rotation axis 21 . The inclination direction of the oil groove 242 and the tapered groove 243 on one side of the pinion 16 is opposite to that of the oil groove 242 and the tapered groove 243 on the other side of the pinion 16 . Moreover, the part where each tapered groove 243 meets the oil groove 242 is deep, and the farther away from the oil groove 242 , the depth becomes shallower.

The oil groove 242 thus provided on the surface of the sliding bearing shaft 241 has a function of supplying oil, and the tapered groove 243 exerts pressure on the lubricating oil supplied to the oil groove 242 to form an oil film. Therefore, when the rotating shaft 21 rotates, the oil groove 242 and the tapered groove 243 function as an oil pump.

That is, when the rotating shaft 21 rotates at a high speed, a wedging effect will occur in the direction of rotation, and part of the lubricating oil will generate high pressure on the sliding bearing 24 through centrifugal action. As a result, the rotating shaft 21 is separated from the slide bearing housing 281 while being suspended, so that the rotating shaft 21 can rotate at a high speed in a suspended state. In this state, if the rotating shaft 21 rotates at a high speed, the life of the high-speed rotating body 20 can be extended because the ball bearing 25 does not function as a bearing (ie, does not come into contact with the rotating shaft 21 ).

Therefore, in the turbo blower 100, as long as the lubricating oil can be supplied to the first combination bearing 26, all problems such as friction caused by high-speed rotation and pressurization of the lubricating oil can be solved even without an oil pump.

In addition, since the turbo blower 100 has a structure in which the rotational speed of the rotating shaft 21 is increased by the large gear 15 and the pinion 16, side pressure due to gear driving is inevitably generated. This lateral pressure is normally applied from the side of the larger diameter bull gear 15 to the side of the smaller diameter pinion 16 . In addition, the substantial action direction of the lateral pressure is not the 3 o'clock direction (representing the clockwise direction) forming a right angle with the vertical line at the center of the rotation shaft 21 , but the approximately 5 o'clock direction below it.

Therefore, a structure capable of buffering the lateral pressure acting on the pinion gear 16 of the rotary shaft 21 should be used. For this reason, a lateral pressure buffer groove 29 is provided on the inner surface of the sliding bearing housing 281 (refer to the dotted line portion in FIG. 5 ). The side pressure buffer groove 29 is arranged on the part of the inner surface of the sliding bearing housing 281 opposite to the bull gear 15 (ie the direction opposite to the side pressure action direction). The length and depth of the lateral pressure buffer groove 29 are determined by calculating the load according to the specifications of the high-speed rotating body 20 . The side pressure buffer groove 29 may have an arc shape equal to or less than 180°.

The part where the lateral pressure buffer groove 29 is provided in the combined bearing housing 28 does not form an oil film, but only forms an oil film on the opposite side, that is, the side that is subjected to the lateral pressure. Therefore, the lateral pressure caused by the large gear 15 can be released to smoothly perform high-speed rotation.

The method for releasing the radial load acting on the high-speed rotating body 20 has been described above. However, when the high-speed rotating body 20 rotates at a high speed, the high-speed rotating body 20 will be subjected to an axial load due to the pressure difference between the inlet of the impeller 22 and the outlet of the impeller 22 . Therefore, a method for releasing the axial load acting on the high-speed rotating body 20 will be described below.

An impeller 22 is provided on one side of the rotating shaft 21 in the high-speed rotating body 20 (the left side thereof with reference to FIG. 5 ). At this time, a negative pressure (-) is formed at the inlet of the impeller 22, and a positive pressure (+) is formed at the outlet of the impeller 22. Therefore, an axial load is generated in the direction (the left side in FIG. 5 ) in which the impeller 22 is provided with reference to the rotating shaft 21 .

In order to release the axial load, the first embodiment takes the following measures. ①A vent hole 231 is provided at the end of the rotating body housing 23 opposite to the impeller 22 , ②Adjust the direction of the helical gear of the pinion 16 arranged on the rotating shaft 21 , ③A ball bearing 25 is provided on the combined bearing housing 28 .

The positive pressure (+) formed on the rear side of the impeller 22 is removed through the ventilation holes 231 of the rotor housing 23 . The pinion 16 is in the shape of a helical gear. The direction of the helical gear is set so that when the rotating shaft 21 rotates, the helical gear can generate a force that pulls the rotating shaft 21 in the opposite direction of the impeller 22 (the right side in FIG. 5 ), thereby releasing the axial load. The axial load is relieved by a supporting force for supporting the basic axial load of the ball bearing 25 as necessary.

Next, the lubricating oil circulation system of the turbo blower 100 will be described with reference to FIG. 7 . The lubricating oil circulation system has the function of circulating and supplying lubricating oil to the high-speed rotating body 20 in the state of no oil pump.

FIG. 7 schematically shows the lubricating oil circulation system through the front sectional view and side sectional view of the gear housing 12 in the turbo blower 100 shown in FIG. 1 and the sectional view of the high-speed rotating body 20 .

Referring to FIG. 7 , a guide cover 30 surrounding the large gear 15 is provided on the inner wall of the gear housing 12 . The guide cover 30 is provided with a plurality of oil guide grooves 301 . Moreover, an oil tank 31 connected to the end of the guide cover 30 is provided on the inner upper portion of the gear housing 12 .

Therefore, if the large gear 15 rotates, the lubricating oil contained in the oil storage tank 32 at the bottom of the gear housing 12 is scattered by the gear teeth of the large gear 15, and simultaneously moves with the guide cover 30 and the oil guide groove 301, and then falls into it by its gravity. In the fuel tank 31 and collected. At this time, the lubricating oil remaining on the surface of the bull gear 15 acts to lubricate the bull gear 15 and the pinion gear 16 at the moment when the bull gear 15 and the pinion gear 16 contact.

Part of the lubricating oil collected in the oil tank 31 is discharged through the oil discharge port 311 by its gravity, and then supplied to the oil supply port 232 provided on the rotating body casing 23 of the high-speed rotating body 20 along the oil pipe.

The lubricating oil supplied to the oil supply port 232 of the rotating body casing 23 is divided into two directions, a small amount of which is supplied to the ball bearing 25 , and most of which is supplied to the slide bearing 24 . When the rotating shaft 21 rotates at a high speed, lubricating oil supplied to the sliding bearing 24 is pressed through the tapered groove 243 on the sliding bearing shaft 241 to form an oil film to support the rotating shaft 21 . The lubricating oil used for the sliding bearing 24 flows in the direction opposite to the supply direction, is discharged from the cutout portion of the rotating body housing 23 where the pinion gear 16 is exposed, and then falls into the oil storage tank 32 at the bottom of the gear housing 12 .

In addition, if the high-speed rotating body 20 rotates at a high speed, the lubricating oil supplied to the first combination bearing 26 is evaporated and oil vapor may be generated.

The oil vapor is discharged to the inside of the gear housing 12 and the outside of the gear housing 12 around the flange 27 of the rotor housing 23 . The oil vapor discharged to the inside of the gear housing 12 is supplied again to the first combination bearing 26 through the circulation structure of the lubricating oil, so no other problem occurs. However, post-processing of the oil vapor discharged to the outside of the gear housing 12 is required.

Of the oil vapor discharged from the inside of the first combined bearing 26 toward the direction of the impeller 22 to the outside of the gear housing 12 , a part thereof is condensed, while the rest remains in a vapor state. Thus, the condensed lubricating oil is recovered to the oil recovery port 33 of the oil storage tank 32 through the recovery port 233 . The oil vapor in the vapor state is discharged through the vapor discharge port 234 , condensed in the oil vapor cooler 34 , and supplied to the oil tank 31 through the condensed oil supply port 35 of the oil tank 31 .

In this way, the lubricating oil supplied to the oil tank 31 through the condensed oil supply port 35 is recovered into the oil storage tank 32 through the oil pipe 36 . In addition, a small amount of oil vapor remaining in the oil tank 31 is discharged to the outside through the exhaust port 37 of the oil tank 31 . Here, the oil tank 31 is provided with a barrier wall 38 whose upper part is open and has a through hole inside. Accordingly, the oil tank 31 may substantially separate and temporarily store lubricating oil collected through the guide cover 30 and the oil guide groove 301 and condensed lubricating oil supplied from the oil vapor cooler 34 .

In addition, lubricating oil is stored in the oil storage tank 32 formed by sealing the gear housing 12, and holes are provided in the vertical direction on the side wall of the oil storage tank 32. As shown in FIG. Also, a control valve 39 is provided on a communication pipe that communicates with these holes. Therefore, an appropriate amount of lubricating oil required for driving the high-speed rotating body 20 can be maintained in the oil storage tank 32 by adjusting the control valve 39 .

When the high-speed rotating body 20 starts to drive, more lubricating oil is needed considering the scattering of lubricating oil, but if the control valve 39 is closed, the lubricating oil in the oil storage tank 32 will be exhausted. Therefore, if the amount of lubricating oil supplied to the control valve 39 is properly controlled, lubricating oil necessary for driving the high-speed rotating body 20 can be maintained.

Reference numeral 40 in FIG. 7 denotes a pressure regulating valve, which communicates with the ventilation hole 231 to adjust the pressure difference between the front and back of the impeller 22 .

FIG. 8 is a partial cross-sectional top view of a turbo blower 110 according to a second embodiment of the present invention. Components in this embodiment that are the same as those in the first embodiment described above are assigned the same reference numerals.

Referring to FIG. 8 , a turbo blower 110 of the second embodiment includes an engine shaft 14 , a large gear 15 , a high-speed rotating body 20 and a second combination bearing 42 .

The engine shaft 14 is combined with the engine 11, and the engine 11 rotates at a high speed when it works. The bull gear 15 is detachably combined on the engine shaft 14, and is provided with a middle hole for installing the fixed shaft 41 and the second combined bearing 42 in its center. The high-speed rotating body 20 includes a rotating shaft 21 and an impeller 22 , wherein the rotating shaft 21 is provided with a pinion 16 meshing with the bull gear 15 , and the impeller 22 is combined with one end of the rotating shaft 21 .

The turbo blower 110 further includes an engine cover 43 , a gear housing 120 , an inlet guide vane 44 (Inlet Guide Vane) and a volute 13 . The engine cover 43 is combined in front of the engine 11 opposite to the impeller 22 , and the gear housing 120 is combined in front of the engine cover 43 opposite to the impeller 22 . The engine shaft 14 , the integral bull gear 15 and a part of the high-speed rotating body 20 are located inside the assembled body of the engine cover 43 and the gear housing 120 . The inlet guide vane 44 is disposed on the suction channel to regulate the flow of gas flowing into the impeller 22 .

If the engine shaft 14 is rotated by the operation of the engine 11 , the large gear 15 and the pinion gear 16 rotate while increasing the power of the engine 11 , thereby driving the high-speed rotating body 20 . Therefore, the external air flows into the rotating impeller 22 through the suction passage, and is accelerated and compressed while passing through the impeller 22 , and then the compressed air is discharged to the volute 13 through the diffuser passage. Arrows in FIG. 8 indicate the inflow direction and the discharge direction of gas.

During the working process of the turbo blower 110 mentioned above, the load of the bull gear 15 itself and the radial load caused by the pinion 16 pushing the bull gear 15 are generated on the bull gear 15, and the load caused by the bull gear 15 and the pinion 16 is also generated. The axial load caused by the helical shape. The second combination bearing 42 described below supports the bull gear 15 inside the bull gear 15 , so the radial load and axial load acting on the bull gear 15 can be effectively reduced.

FIG. 9 is a cross-sectional view of the engine shaft 14 and the bull gear 15 in the turbo blower 110 shown in FIG. 8 viewed from direction A, and FIG. 10 is a partially enlarged view of FIG. 9 .

Referring to FIGS. 9 and 10 , the second combination bearing 42 includes a tapered roller bearing 45 and a ball bearing 46 , and the two bearings are arranged between the fixed shaft 41 and the bull gear 15 in a direction parallel to the engine shaft 14 . The tapered roller bearing 45 includes a roller 451 inserted in an oblique direction, an inner ring 452 and an outer ring 453 surrounding the roller 451 . The ball bearing 46 includes a ball 461 , an inner ring 462 and an outer ring 463 surrounding the ball 461 . The inner wheel 462 is sheathed on the fixed shaft 41 , and the outer wheel 463 is combined with the large gear 15 .

Also, the tapered roller bearing 45 reduces both the radial load and the axial load acting on the bull gear 15 , and the ball bearing 46 again reduces the radial load acting on the bull gear 15 . Therefore, the turbo blower 110 of the second embodiment minimizes the radial load and the axial load acting on the bull gear 15 through the second combination bearing 42 . As a result, noise due to position shift of the bull gear 15, damage of the bull gear 15, and deformation of the engine shaft 14 can be prevented.

The fixed shaft 41 is fixed to the gear housing 120 by a fixed block 47 and a bolt 48 , and its center coincides with the center of the engine shaft 14 . An oil hole 411 is formed inside the fixed shaft 41 along a direction parallel to the fixed shaft 41 for supplying lubricating oil to the second combination bearing 42 . At this time, there is a predetermined distance between the fixed shaft 41 and the engine shaft 14 to form a flow channel for guiding lubricating oil to the second combined bearing 42 .

In addition, the engine shaft 14 does not overlap with the large gear 15 , and a flange 141 is fixed on the outer peripheral surface of the end of the engine shaft 14 opposite to the large gear 15 . The large gear 15 can be mechanically fixed on the engine shaft 14 by utilizing a plurality of fastening bolts 49 passing through the large gear 15 and the flange 141 . At this time, the bull gear 15 does not adopt a permanent combination such as heat press fit, but is combined on the engine shaft 14 in a detachable manner, so when the bull gear 15 needs to be replaced or maintained, the bull gear 15 and Assembly and disassembly of the engine shaft 14.

FIG. 11 is a partially enlarged view of the gear housing 120 and the large gear 15 in the turbo blower 110 shown in FIG. 8 .

Referring to FIG. 11 , in the gear case 120 , an opening 123 is provided at a position facing any one of the plurality of fastening bolts 49 . Furthermore, a tool (not shown) can be inserted through the opening 123 to separate the fastening bolt 49 . That is, after separating the fastening bolts 49 with a tool, the large gear 15 is rotated manually, and the other fastening bolts 49 are placed at the positions of the openings 123 , and then the tool is put in to separate the fastening bolts 49 . Therefore, all of the plurality of coupling bolts 49 can be separated by repeating the above-mentioned process.

After all the joint bolts 49 are completely removed, the large gear 15 is supported by the second combination bearing 42, if the gear housing 120 and the engine cover 43 are separated in this state, the engine 11 and the engine shaft can be easily disassembled from the large gear 15 and the gear housing 120 14.

In the turbo blower 110 of the second embodiment, the structures and functions of the high-speed rotating body 20 and the first combination bearing 26 are the same as those of the first embodiment described above, so detailed description thereof will be omitted here.

Next, the shapes of the engine cover 43 and the gear housing 120 will be described.

FIG. 12 is a perspective view of the engine cover 43 of the turbo blower 110 shown in FIG. 8 viewed from the B direction.

Referring to FIG. 8 and FIG. 12 , the engine cover 43 is provided with a central hole 431 for receiving the engine shaft 14 , and has a third coupling surface 432 which is coupled to the engine 11 along the periphery of the central hole 431 . Also, the engine cover 43 has a recess 50 protruding toward the engine 11 , thereby enlarging the inner space of the assembly of the engine cover 43 and the gear housing 120 toward the engine 11 .

The larger the capacity of the turbo blower 110 is, the longer the length of the rotating shaft 21 is, so it is necessary to form a space for accommodating the rotating shaft 21 . In the turbo blower 110 of the second embodiment, since the engine cover 43 is provided with the recess 50, the part on the opposite side of the impeller 22 in the high-speed rotating body 20 can be accommodated in the recess 50, so it is also possible to easily install a large fan. High-speed rotating body 20.

FIG. 13 is a perspective view of the gear housing 110 in the turbo blower 110 shown in FIG. 8 viewed from the direction C, and FIG. 14 is a cross-sectional view taken along line I-I of FIG. 13 .

Referring to FIGS. 13 and 14 , the structure of the gear housing 120 is a shape in which the opening degree of the side combined with the engine cover 43 is greater than the diameter of the large gear 15 . That is, the gear housing 120 includes a vertical wall 51 and a side wall 52 , and has a completely open structure on the side fixed to the engine cover 43 . Wherein, the vertical wall 51 is provided with two middle holes for accommodating the fixed shaft 41 of the large gear 15 and the high-speed rotating body 20 , and the side wall 52 expands from the edge of the vertical wall 51 toward the engine cover 43 .

Therefore, as shown in Figure 8, the large gear 15 and the engine shaft 41 are assembled, and the gear housing 120 is fixed on the engine cover 43 to surround the large gear 15, and then the fixed shaft 41 and the high-speed rotating body 20 Installed in the gear housing 120 , and then assemble the volute 13 on the rotating body housing 23 sequentially. The decomposition process of the structure is the reverse of the assembly sequence described above. Because the present invention has the detachable combination structure of the bull gear 15 and the engine shaft 14 and the shape of the gear casing 120 with a relatively large opening on one side, the assembly and disassembly process of the turbo blower 110 becomes simple.

Next, the lubricating oil circulation system of turbo blower 110 according to the second embodiment will be described.

FIG. 15 is a front view of the gear housing 120 shown in FIG. 13 viewed from the direction D.

Referring to FIG. 14 and FIG. 15 , the inner surface of the vertical wall 51 of the gear housing 120 is provided with a guide cover 30 roughly in the shape of an arc, and the guide cover 30 surrounds a part of the large gear 15 . The guide cover 30 protrudes from the inner surface of the vertical wall 51 toward the engine cover 43 and has a width w1 (see FIG. 14 ) corresponding to a width w2 (see FIG. 14 ) of the side wall 52 of the gear housing 120 . The inner diameter of the guide cover 30 is larger than the diameter of the bull gear 15 and is separated from the bull gear 15 by a certain distance.

In FIG. 15 , the rotation direction of the large gear 15 is counterclockwise, and the guide cover 30 has a roughly cut-away upper left side shape based on FIG. 15 . An oil guide groove 301 is provided on the inner surface of the guide cover 30 along the rotation direction of the bull gear 15 . A plurality of the oil guide grooves 301 are arranged at a certain distance in a direction parallel to the engine shaft 14 (see FIG. 14 ).

Also, a stepped protrusion 53 is provided on the upper inner surface of the vertical wall 51 of the gear case 120 , that is, on the outer side of the large gear 15 . The protruding portion 53 forms a step descending toward the side wall 52 . One end of the protrusion 53 is connected to the side wall 52 , and the other end is separated from the upper end of the guide cover 30 by a certain distance in the horizontal and vertical directions when referring to FIG. 15 . The width of the protrusion 53 is equal to the width of the guide cover 30 .

If the aforementioned gear housing 120 is combined with the engine cover 43, the side wall 52, the guide cover 30 and the protruding portion 53 can be tightly attached to the engine cover 43 and form a predetermined internal space. That is, the lower part of the assembly of the gear housing 120 and the engine cover 43 is provided with an oil storage tank 32, an oil passage is provided between the bull gear 15 and the guide cover 30, and a temporary storage tank 54 is provided above the protrusion 53, which is used for Collect the lubricating oil and recirculate the collected lubricating oil.

Therefore, if the large gear 15 rotates, the lubricating oil contained in the oil storage tank 32 is scattered through the gear teeth of the large gear 15, moves along the oil guide groove 301 provided on the guide cover 30, and then falls on the protruding surface by its gravity. part 53 and collected into the temporary storage tank 54. And, lubricating oil collected in the temporary storage tank 54 is supplied to the second combination bearing 42 of the large gear 15 and the first combination bearing 26 of the high-speed rotating body 20 through a circulation structure described below.

In the aforementioned structure of the gear housing 120 , the guide cover 30 and the protruding portion 53 are integrally formed with the gear housing 120 . Therefore, it is possible to avoid the trouble of additionally making the oil storage tank and the temporary storage tank and assembling them inside the gear housing, and the gear housing 120 and the engine cover 43 are combined in an airtight state, so that the oil storage tank 32 and the temporary storage tank can be easily arranged. Storage tank 54.

FIG. 16 is a front view of the turbo blower 100 shown in FIG. 8 viewed from the direction C, and a part of the outside of the gear case 120 is shown within a dotted line.

Referring to FIG. 15 and FIG. 16 , a first oil pipe 55 is provided outside the vertical wall 51 of the gear housing 120 , and the first oil pipe 55 is used to connect the temporary storage tank 54 and the fixed shaft 41 of the bull gear 15 . That is, a first through opening 56 is provided at a position corresponding to the temporary storage tank 54 in the vertical wall 51 of the gear housing 120 , and one end of the first oil pipe 55 is connected to the first through opening 56 . Moreover, the other end of the first oil pipe 55 is connected to the oil hole 411 provided on the fixed shaft 41 .

A part of the first oil pipe 55 connected to the fixed shaft 41 is shown by dotted lines in FIG. 9 . 9, the first oil pipe 55 supplies the lubricating oil collected in the temporary storage tank 54 to the oil hole 411 of the fixed shaft 41, and the lubricating oil supplied to the oil hole 411 flows through the ball bearing 46 and the tapered roller bearing 45 in sequence. At the same time, the second combination bearing 42 is lubricated. Then, the lubricating oil falls into the oil sump 32 again, and is collected inside it.

FIG. 17 is a right side view of the turbo blower 110 of FIG. 8 viewed from a direction B, and shows the inside of the gear case 120 with a part of the engine cover 43 cut away. FIG. 18 is a front view of the high-speed rotating body 20 in the turbo blower 110 shown in FIG. 8 .

Referring to FIG. 17 and FIG. 18 , a second oil pipe 57 is provided inside the vertical wall 51 of the gear housing 120 , and the second oil pipe 57 is used to transfer the lubricating oil collected in the temporary storage tank 54 to the high-speed rotating body 20 . For this purpose, a second through hole 58 is provided at the lower end of the protruding portion 53 , and one end of the second oil pipe 57 is connected to the second through hole 58 . Moreover, a third through-hole 59 is provided at a position overlapping the rotating body housing 23 on the vertical wall 51 of the gear housing 120 , and the other end of the second oil pipe 57 is connected to the third through-hole 59 .

And, the inside of the rotating body casing 23 is provided with a first combination bearing 26 (taking FIG. 18 as a standard, that is, the first combination bearing 26 on the left side) and The oil passage 60 of the third through port 59 . Moreover, the outside of the rotating body housing 23 is provided with a third oil pipe 61 for connecting the first combination bearing 26 on the opposite side of the impeller 22 (taking FIG. .

Therefore, the lubricating oil collected in the temporary storage tank 54 is supplied to the high-speed rotating body 20 through the second oil pipe 57, and the supplied lubricating oil is supplied to the first combined bearing on the side of the impeller 22 through the oil passage 60 and the third oil pipe 61, respectively. 26 and the first composite bearing 26 on the opposite side of the impeller 22.

The lubricating oil supplied to the first combination bearing 26 on the side of the impeller 22 lubricates the two bearings while flowing through the sliding bearing 24 and the ball bearing 25 in sequence. At this time, lubricating holes 63 are provided on the bearing 62 between the ball bearing 25 and the impeller 22 and the rotating body housing 23 surrounding the bearing 62, and a fourth oil pipe 64 is arranged on the outside of the rotating body housing 23 , which is used to connect the lubricating hole 63 and the gear housing 120 . Therefore, the lubricating oil used flows into the gear housing 120 through the fourth oil pipe 64 and is collected into the oil storage tank 32 .

Also, lubricating oil supplied to the first combined bearing 26 on the opposite side of the impeller 22 through the third oil pipe 61 is supplied to the sliding bearing 24 and the ball bearing 25 to lubricate the two bearings. And the lubricating oil used falls into the oil sump 32 through the cut-away portion in the middle of the rotating body housing 23 for exposing the pinion gear 16 and is collected therein.

Referring to FIG. 9 , a bearing 65 and a seal 66 are arranged side by side on the outer peripheral surface of the engine shaft 14 in a direction away from the bull gear 15 . During the rotation of the bull gear 15 , lubricating oil is also scattered toward the engine shaft 14 at a high speed, so that the lubricating oil passing through is sufficient to lubricate the bearing 65 . A fifth oil pipe 67 is arranged on the sealing member 66 , which recovers the lubricating oil reaching the sealing member 66 through the bearing 65 into the oil storage tank 32 .

As mentioned above, even if the turbo blower 110 of the second embodiment is not additionally provided with an oil pump for supplying lubricating oil, it can still circulate and supply lubricating oil to the second combination bearing 42 of the bull gear 15 and the first combined bearing 42 of the high-speed rotating body 20 . Combined bearing 26. Therefore, the present invention can reduce the number of components by simplifying the lubricating oil supply structure.

The preferred embodiments of the present invention have been described above in conjunction with the accompanying drawings, but the present invention is not limited to the above-mentioned embodiments, and can have multiple embodiments and modified examples without departing from the scope of the spirit of the present invention, and these should belong to the protection scope of the present invention Inside.

Claims (19)

1. a turbo blower, is characterized in that, comprising:

Motor, this motor has engine shaft;

Gear casing, this gear casing is built-in with the gearwheel that is combined in described engine shaft and the small gear meshed with described gearwheel;

High-speed rotary body, this high-speed rotary body is included on outer circumferential face running shaft, the impeller combined with an end of described running shaft that is provided with described small gear and is built-in with described running shaft, described small gear and is positioned at the first combination bearing of described small gear both sides, and part is broken away so that the solid of rotation shell that described small gear exposes, and the part of described high-speed rotary body is built in described gear casing and combines with described gear casing; And

Spiral case, this spiral case coats described impeller output squeezing air,

Wherein, described the first combination bearing comprises: the built-up shaft bearing possesses plain bearing housing and ball-bearing housing that one forms; The sliding bearing axle, be arranged on the outer circumferential face of described running shaft, and be built in described plain bearing housing together with described plain bearing housing, to form sliding bearing; Ball bearing, be built in described ball-bearing housing,

Described sliding bearing the gap that arranges that gap is greater than described ball bearing is set,

Described sliding bearing axle is tiltedly installed with a plurality of oil grooves and a plurality of cone groove in its surface, on described surface, to form oil film, and be provided with the side pressure dashpot, the side pressure caused to absorb described gearwheel on the part relative with described gearwheel on the internal surface of described plain bearing housing.

2. turbo blower according to claim 1, is characterized in that,

Described high-speed rotary body is provided with vent hole on the end relative with described impeller in described solid of rotation shell, and described small gear forms helical gear shape, described helical gear direction is set to, when described running shaft rotation, produce the power of towards the opposite direction of described impeller, drawing described running shaft.

3. turbo blower according to claim 1 and 2, is characterized in that,

Be provided with circular-arc guiding lid on the internal face of described gear casing, described guiding is covered around the part of described gearwheel and is had a plurality of oil guide slot, and the inside upper part of described gear casing is provided with the fuel tank be connected with the end of described guiding lid.

4. turbo blower according to claim 3, is characterized in that,

The inside of described gear casing is provided with oil pipe, thereby supply with and collect the lubricant oil in described fuel tank to described the first combination bearing, one end of described oil pipe is connected with the oil drain out on being formed on described fuel tank, and the other end of described oil pipe is connected with the oil-feed port on being formed on described the first combination bearing.

5. turbo blower according to claim 4, is characterized in that,

On described solid of rotation shell, be provided with for discharging the steam outlet of oil vapor,

Described turbo blower further comprises the oil vapor cooler be connected with described fuel tank with described steam outlet, and the oil vapor that the condensation of described oil vapor cooler is discharged from described steam outlet also is supplied in described fuel tank.

6. turbo blower according to claim 5, is characterized in that,

Bottom at described gear casing is provided with oil storage tank, and described oil storage tank is provided with pair of holes on the upper-lower position of sidewall, and described gear casing further comprises the connecting tube for being communicated with described pair of holes and is arranged at the control valve of described connecting tube.

7. turbo blower according to claim 3, is characterized in that,

Described gearwheel directly combines with described engine shaft, and described gear casing is provided with junction plane on the side relative with described motor, and described junction plane has the opening portion that is greater than described gearwheel diameter, and described junction plane combines with described motor.

8. turbo blower according to claim 1 and 2, is characterized in that,

Described gearwheel releasably is incorporated on described engine shaft, and at center, is provided with for the mesopore of stationary axle is installed;

Be provided with the second combination bearing between described stationary axle and described gearwheel, this second combination bearing have with described engine shaft adjacent tapered roller bearing and ball bearing on direction side by side.

9. turbo blower according to claim 8, is characterized in that,

Be provided with and be combined with described motor and for supporting the hood of described engine shaft,

Described gear casing is provided with in the side with described hood is combined the opening portion that diameter is greater than described gearwheel diameter.

10. turbo blower according to claim 9, is characterized in that,

Described engine shaft is provided with flange on the end outer circumferential face relative with described gearwheel, described gearwheel is attached on described engine shaft by a plurality of joint bolts that connect described gearwheel and described flange, and described gear casing is provided with opening portion on the position relative at any one joint bolt with in described a plurality of joint bolts.

11. turbo blower according to claim 9, is characterized in that,

Described hood has the dimple outstanding towards described motor, and the part of described high-speed rotary body is received in described dimple.

12. turbo blower according to claim 9, is characterized in that,

Be provided with the guiding lid of circular shape and the protuberance of stairstepping on the internal face of described gear casing, wherein, described guiding lid is around the part of described gearwheel, and described protuberance is positioned at the outside, side of described gearwheel, described protuberance is at the interim accumulator tank of the inner formation of assembly body of described gear casing and described hood.

13. turbo blower according to claim 12, is characterized in that,

Internal surface at described guiding lid is provided with a plurality of oil guide slot, and described a plurality of oil guide slot are extended along the sense of rotation of described gearwheel.

14. turbo blower according to claim 12, is characterized in that,

Described gear casing is provided with the first openings being provided with on the position of described interim accumulator tank, and further comprises the first oil pipe, described the first oil pipe in the outside of described gear casing for connecting described the first openings and described stationary axle.

15. turbo blower according to claim 14, is characterized in that,

Described stationary axle is incorporated into described gear casing, and described stationary axle is provided with oilhole in inside, between described stationary axle and described engine shaft, is provided with runner, for the lubricant oil that will be supplied to described oilhole, is directed to described the second combination bearing.

16. turbo blower according to claim 12, is characterized in that,

The lower end of described protuberance is provided with the second openings, be provided with the 3rd openings on the part of joining with described solid of rotation shell in described gear casing, and the inside of described gear casing further comprises the second oil pipe that described the second openings is connected with described the 3rd openings.

17. turbo blower according to claim 16, is characterized in that,

Described solid of rotation shell is provided with oil duct in inside, for connecting the first combination bearing and described the 3rd openings of described impeller side of described a pair of the first combination bearing, and further comprise the 3rd oil pipe in the outside of solid of rotation shell, for connecting described a pair of the first combination bearing and the first combination bearing described impeller opposition side and described oil duct.

18. turbo blower according to claim 17, is characterized in that,

Described high-speed rotary body further comprises at the first combination bearing of described impeller side and the bearing between described impeller, and be provided with oil drain out on described bearing and described solid of rotation shell, described solid of rotation shell externally further comprises the 4th oil pipe, for connecting described oil drain out and described gear casing, thereby reclaim lubricant oil.

19. turbo blower according to claim 15, is characterized in that, further comprises:

Bearing and Sealing, this bearing and Sealing are arranged side by side along the direction away from described gearwheel on the outer circumferential face of described engine shaft; And

The 5th oil pipe, the 5th oil pipe is for connecting the inside of described Sealing and described hood, to reclaim the lubricant oil that arrives described Sealing.

Images