CN102057164B - Turbo blower and high speed rotating body used in same - Google Patents
Turbo blower and high speed rotating body used in same Download PDFInfo
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- CN102057164B CN102057164B CN200980121594.9A CN200980121594A CN102057164B CN 102057164 B CN102057164 B CN 102057164B CN 200980121594 A CN200980121594 A CN 200980121594A CN 102057164 B CN102057164 B CN 102057164B
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- oil
- bearing
- gearwheel
- turbo blower
- gear casing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/057—Bearings hydrostatic; hydrodynamic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/059—Roller bearings
Abstract
The present invention relates to a turbo blower and a high speed rotating body used in same. The turbo blower includes i) a motor having a motor shaft, ii) a bull gear coupled to the motor shaft, and a gear housing provided with a pinion gear to engage the bull gear, iii) a high speed rotating body including a rotating shaft having an outer circumferential surface with a pinion gear, an impeller to be coupled to one end of the rotating shaft, and a rotating body housing for accommodating the rotating shaft, the pinion gear, and at least one first composite bearing, and which has a portion cut out to expose the pinion gear, wherein the high speed rotating body is partially built-in and coupled to the gear housing, and iv) a scroll unit which covers the impeller and discharges compressed air.
Description
Technical field
The present invention relates to a kind of turbo blower, the axial load in the time of particularly can making to drive and radial load reach minimized turbo blower and reach the high-speed rotary body for this blower.
Background technique
For obtaining the high output of small volume, turbo blower generally uses high-speed rotary body.High-speed rotary body can be divided into direct drive mode and indirect driving mode according to its driving mode.Wherein, described direct drive mode directly is connected with high speed engine, and described indirect driving mode is connected with general motor by the gear speeder for increasing rotational speed.
The high-speed rotary body of direct drive mode is supported by pneumatic bearing (air bearing) usually.For example, but pneumatic bearing, because component durability is poor, is used (, more than 3 years) can be subject to a lot of restrictions so long-term.
The common gear speeder that the high-speed rotary body of driving mode is used indirectly is comprised of gearwheel (bullgear) and small gear (pinion gear).Wherein, described gearwheel is combined on engine shaft, and described small gear is arranged on high-speed rotary body, and is meshed with gearwheel.Yet, when possessing the turbo blower work of gear speeder, on high-speed rotary body and gearwheel, will produce radial load and axial load, institute thinks that reducing described load need improve structure.
And, the turbo blower that possesses gear speeder uses the gear-box that is built-in with gearwheel and small gear, and for gear-box is installed on turbomachinery, not only need gear-box itself is made to level-split type, and the bearing that supports above-mentioned two gear shafts need to be made to level-split type.
While so by separate mode, making gear-box, make precision poor, and after turbomachinery assemble, for carrying out high-speed rotary then when gear shaft is carried out to centering (centering), be difficult to the assurance assembly precision.In addition, because the number of components increases, can cause fabricating cost to become large.
For supplying lubricating oil, the turbo blower of driving mode need to possess oil pump indirectly, has therefore increased the number of components.And in the prior art,, by shrink fit (shrinkfit) combination, when the reasons such as tooth section wearing and tearing due to gearwheel need to be changed gearwheel, there are the dismounting of gearwheel in gearwheel and engine shaft and assemble difficult problem.
Summary of the invention
The object of the present invention is to provide a kind of axial load and radial load of acting on high-speed rotary body and gearwheel of can making to reach minimized turbo blower.
The present invention also provides a kind of oily loop structure that forms in turbo blower, even be not provided for the oil pump of supplying lubricating oil, and still can be to the circulate turbo blower of supplying lubricating oil of high-speed rotary body.
The present invention provides again a kind of can make the assembly and disassembly of high-speed rotary body and gearwheel and motor become simple turbo blower.
The turbo blower that one embodiment of the invention relates to comprises: i) motor, and this motor has engine shaft; Ii) gear casing, this gear casing is built-in with the gearwheel that is combined in engine shaft and the small gear meshed with gearwheel; Iii) high-speed rotary body, this high-speed rotary body is included on outer circumferential face running shaft, the impeller combined with an end of running shaft that is provided with small gear and is built-in with running shaft and small gear and at least one the first combination bearing, and part is broken away so that the solid of rotation shell that small gear exposes, and the part of high-speed rotary body is built in gear casing and combines with gear casing; And iv) spiral case, this spiral case coats impeller output squeezing air.
The first combination bearing can comprise: i) built-up shaft bearing, and this built-up shaft bearing possesses plain bearing housing and the ball-bearing housing that one forms; Ii) sliding bearing axle, this plain bearing housing is arranged at the outer circumferential face of running shaft, and is built in plain bearing housing to form sliding bearing together with plain bearing housing; And iii) ball bearing, this ball bearing is built in ball-bearing housing.
The first combination bearing is positioned at the both sides of small gear, and sliding bearing the gap that arranges that gap can be greater than ball bearing is set.The surface of sliding bearing axle tilts and is provided with a plurality of oil grooves and a plurality of cone groove, and to form from the teeth outwards oil film, and the part relative with gearwheel is provided with the side pressure dashpot in the internal surface of plain bearing housing, thereby can absorb the side pressure that gearwheel causes.
In addition, high-speed rotary body is provided with vent hole on the end relative with impeller in the solid of rotation shell, and small gear forms helical gear shape, and helical gear direction is set to when running shaft rotates, and produces the power of towards the opposite direction of impeller, drawing running shaft.
Be provided with the guiding lid with circular shape on the internal face of gear casing, its part around gearwheel also has a plurality of oil guide slot, and the inside upper part of gear casing can be provided with the fuel tank be connected with the end of guiding lid.
The inside of gear casing is provided with oil pipe, thereby supplies with and collect the lubricant oil in fuel tank to the first combination bearing, and an end of oil pipe is connected with the oil drain out arranged on fuel tank, and the other end of oil pipe is connected with the oil-feed port on being formed on the first combination bearing.
On the solid of rotation shell, be provided with for discharging the steam outlet of oil vapor, turbo blower further can comprise the oil vapor cooler be connected with fuel tank with steam outlet.And the oil vapor that the oil vapor cooler can condensation be discharged from steam outlet also is supplied in fuel tank.
The bottom of gear casing is provided with oil storage tank, and oil storage tank is provided with pair of holes on the upper-lower position of sidewall, and gear casing further can comprise the connecting tube for being communicated with pair of holes and be arranged at the control valve of connecting tube.
Gearwheel is directly connected in engine shaft, be provided with junction plane in gear casing on the side relative with motor, and junction plane has the opening portion that diameter is greater than the gearwheel diameter, and junction plane can combine with motor.
The high-speed rotary body that one embodiment of the invention relates to comprises: i) running shaft is provided with the small gear be meshed with gearwheel on this running shaft outer circumferential face; Ii) impeller, this impeller combines with an end of running shaft; Iii) a pair of the first combination bearing, this pair of the first combination bearing is arranged at the both sides of small gear; And iv) solid of rotation shell, this solid of rotation shell is built-in with running shaft, small gear and a pair of the first combination bearing, and the part of solid of rotation shell is broken away, so that small gear exposes.
A pair of the first combination bearing can comprise respectively: i) built-up shaft bearing, and this built-up shaft bearing possesses plain bearing housing and the ball-bearing housing that one forms; Ii) sliding bearing axle, this sliding bearing axle is arranged on the outer circumferential face of running shaft, and is built in plain bearing housing to form sliding bearing together with plain bearing housing; And iii) ball bearing, this ball bearing is built in ball-bearing housing.
Sliding bearing the gap that arranges that gap is greater than ball bearing is set, the surperficial updip of sliding bearing axle tiltedly is provided with a plurality of oil grooves and a plurality of cone groove, to form from the teeth outwards oil film, and the side pressure caused for absorbing gearwheel, at the internal surface of plain bearing housing, and can be provided with the side pressure dashpot on the opposite direction of side pressure direction.
The turbo blower that another embodiment of the present invention relates to comprises: i) motor, and this motor has engine shaft; Ii) gearwheel, this gearwheel releasably is incorporated on engine shaft, and at center, is provided with for the mesopore of stationary axle is installed; Iii) the second combination bearing, this second combination bearing is arranged between stationary axle and gearwheel, and has at the tapered roller bearing and the ball bearing that face mutually on direction side by side with engine shaft; And iv) high-speed rotary body, this high-speed rotary body has the impeller on the running shaft that is provided with the small gear meshed with gearwheel on outer circumferential face and an end that is incorporated into running shaft.
Turbo blower further can comprise: i) hood, and this hood is combined with motor, and for the supporting engines axle; And ii) gear casing, this gear casing is built-in with gearwheel and small gear, and is provided with in the side of being combined with hood the opening portion that diameter is greater than the gearwheel diameter.
Engine shaft is provided with flange on the end outer circumferential face relative with gearwheel, gearwheel is attached on engine shaft by a plurality of joint bolts that connect gearwheel and flange, and gear casing is provided with opening portion on the position relative at any one joint bolt with in a plurality of joint bolts.Hood has the dimple outstanding towards motor (recess), and the part of high-speed rotary body is received in dimple.
High-speed rotary body further can comprise: i) a pair of the first combination bearing, and this pair of the first combination bearing is arranged at the both sides of small gear; And ii) solid of rotation shell, this solid of rotation shell is built-in with running shaft and a pair of the first combination bearing, and is arranged on gear casing, and part is broken away so that small gear exposes from gear casing inside.
The first combination bearing can comprise respectively: i) built-up shaft bearing, and this built-up shaft bearing possesses plain bearing housing and the ball-bearing housing that one forms; Ii) sliding bearing axle, this sliding bearing axle is arranged on the outer circumferential face of running shaft, is built in plain bearing housing to form sliding bearing together with plain bearing housing simultaneously; And iii) ball bearing, this ball bearing is built in ball-bearing housing.
Sliding bearing the gap that arranges that gap is greater than ball bearing is set, the surperficial updip of sliding bearing axle tiltedly is provided with a plurality of oil grooves and a plurality of cone groove, to form from the teeth outwards oil film.
Be provided with the guiding lid of circular shape and the protuberance of stairstepping on the internal face of gear casing, wherein, the guiding lid is around the part of gearwheel, and protuberance is positioned at the outside, side of gearwheel, and protuberance is at the interim accumulator tank of the inner formation of assembly body of gear casing and hood.
The internal surface of guiding lid can be provided with a plurality of oil guide slot, and a plurality of oil guide slot are along extending on the sense of rotation of gearwheel.Gear casing is provided with the first openings being provided with on the position of interim accumulator tank, and gear casing may further include the first oil pipe, and the first oil pipe in the outside of gear casing for connecting the first openings and stationary axle.
Stationary axle is incorporated into gear casing, and stationary axle is provided with oilhole in inside, and is provided with runner between stationary axle and engine shaft, thereby the lubricant oil that is supplied to oilhole can be directed to the second combination bearing.
The lower end of protuberance is provided with the second openings, and the part of joining with the solid of rotation shell in gear casing is provided with the 3rd openings, and the inside of gear casing further can comprise the second oil pipe that the first openings is connected with the 3rd openings.
The inside of solid of rotation shell is provided with oil duct, for connecting the first combination bearing and the 3rd openings of impeller side of a pair of the first combination bearing, and the outside of solid of rotation shell further can comprise the 3rd oil pipe, for connecting a pair of the first combination bearing and the first combination bearing and oil duct the impeller opposition side.
High-speed rotary body further can comprise at the first combination bearing of impeller side and the bearing between impeller, and be provided with oil drain out on bearing and solid of rotation shell, the solid of rotation shell externally further can comprise the 4th oil pipe, for connecting oil drain out and gear casing, thereby reclaim lubricant oil.
Turbo blower further can comprise: i) bearing and Sealing, and this bearing and Sealing are arranged side by side along the direction away from gearwheel on the outer circumferential face of engine shaft; And ii) the 5th oil pipe, the 5th oil pipe is for the inside of connection sealing element and hood, to reclaim the lubricant oil that arrives Sealing.
The turbo blower that another embodiment of the present invention relates to comprises: i) motor, and this motor has engine shaft, with hood, fits together simultaneously; Ii) gearwheel, this gearwheel releasably is incorporated on engine shaft, and center is provided with for the mesopore of stationary axle is set; Iii) high-speed rotary body, this high-speed rotary body comprises that outer circumferential face is provided with the running shaft of the small gear of gearwheel engagement, the impeller of being combined with running shaft one end, at least one first combination bearing of supporting rotating shaft and be built-in with running shaft and the first combination bearing, and a part of being broken away so that the solid of rotation shell that small gear exposes; Iv) the second combination bearing, this second combination bearing is arranged between stationary axle and gearwheel, and have along with engine shaft direction side by side on adjacent tapered roller bearing and ball bearing; V) gear casing, this gear casing is built-in with gearwheel and small gear, and is provided with in the side of being combined with hood the opening portion that diameter is greater than the diameter of gearwheel; And vi) spiral case, this spiral case is around impeller output squeezing air.
According to the present invention, adopt combination bearing to absorb axial load and the radial load of high-speed rotary body and gearwheel, use one-piece type built-up shaft bearing to make the precision of assembling high, can obtain in the turbo blower field wide in range application thus.
According to the present invention, provide effective lubricant oil that system is provided, can the turbo blower turned round steady in a long-term even do not use oil pump also can provide.
According to the present invention, though do not use existing for by transmission of power to the gearwheel running shaft of gearwheel, also can, by transmission of power to gearwheel, use a small amount of parts that not only economic life but also long turbo blower also can be provided.
According to the present invention, while needing replacing or maintenance gearwheel, can easily assemble and decompose high-speed rotary body and gearwheel and motor.
The accompanying drawing explanation
Fig. 1 is the plan view of the turbo blower that relates to of first embodiment of the invention.
Fig. 2 is the left view of the turbo blower shown in Fig. 1.
Fig. 3 observes the stereogram of the gear casing the turbo blower shown in Fig. 1 from impeller side.
Fig. 4 is from starting pusher side to observe the stereogram of the gear casing the turbo blower shown in Fig. 1.
Fig. 5 is the sectional view that shows the high-speed rotary body of the turbo blower shown in Fig. 1.
Fig. 6 is the plan view of the running shaft of the turbo blower shown in Fig. 1.
Fig. 7 is the schematic diagram that the sectional view of the front section view, side sectional view and the high-speed rotary body that utilize the gear casing of the turbo blower shown in Fig. 1 shows oil circulation system.
Fig. 8 is the plan view of the turbo blower that relates to of second embodiment of the invention.
Fig. 9 observes the engine shaft of the turbo blower shown in Fig. 8 and the sectional view of gearwheel in the A direction.
Figure 10 is the partial enlarged drawing of Fig. 9.
Figure 11 is the partial enlarged drawing of the middle gear shell of turbo blower shown in Fig. 8 and gearwheel.
Figure 12 is the stereogram of hood from turbo blower shown in B direction observation Fig. 8.
Figure 13 observes the stereogram of turbo blower middle gear shell shown in Fig. 8 from the C direction.
Figure 14 is the sectional view of I-I line in Figure 13.
Figure 15 observes the plan view of gear casing shown in Figure 13 from the D direction.
Figure 16 observes the plan view of turbo blower shown in Fig. 8 from the C direction.
Figure 17 observes the right elevation of turbo blower shown in Fig. 8 from the B direction.
Figure 18 is the plan view of the high speed of turbo blower shown in Fig. 8 solid of rotation.
Embodiment
Describe with reference to the accompanying drawings embodiments of the invention in detail, so that those skilled in the art easily implement.The present invention can implement in every way, is not limited in the embodiment shown in this.
Fig. 1 is the plan view of the turbo blower 100 that relates to of first embodiment of the invention, and it is cut open and has shown high-speed rotary body 20 parts.Fig. 2 is the left view of the turbo blower 100 shown in Fig. 1.
See figures.1.and.2, the first embodiment's turbo blower 100 comprises support platform 10, motor 11, gear casing 12 and spiral case 13.Be fixed with motor 11 and gear casing 12 on support platform 10, and the part of high-speed rotary body described later 20 is positioned at the inside of gear casing 12.
In the first embodiment's turbo blower 100, the engine shaft 14 of combination on motor 11 directly is not connected with the running shaft 21 of high-speed rotary body 20, and both are offset setting.That is, directly be connected with gearwheel 15 on engine shaft 14, and be provided with small gear 16 on running shaft 21, and gearwheel 15 and small gear 16 increase the power of motor 11 by engagement, with this, drive high-speed rotary body 20.
The first embodiment has taked aforementioned power transmission structure, thereby it is interior for supporting the Large Gear Shaft During of gearwheel with gear-box to remove existing speedup, and solved between motor and gear-box the problem that needs sealing, can reduce the number of components, thereby reduced manufacture cost simultaneously.
For on engine shaft 14 so directly in conjunction with gearwheel 15, as shown in Figure 3 and Figure 4, integral production gear casing 12, and it is open that gear casing 12 is fixed in to a side of motor 11, and the degree of this opening is greater than gearwheel 15 diameters.And, be provided with the carriage 17 for fixed gear shell 13 on motor 11.
Fig. 3 observes the stereogram of turbo blower 100 middle gear shells 12 shown in Fig. 1 from impeller 22, Fig. 4 observes the stereogram of turbo blower 100 middle gear shells 12 shown in Fig. 1 from motor 11.
In Fig. 3, reference character 121 expressions are attached to high-speed rotary body 20 and spiral case 13 the first junction plane of gear casing 12.In Fig. 4, reference character 122 means gear casing 12 itself is attached to the second junction plane on the carriage 17 of motor 11.
Can use screw bolt and nut in conjunction with etc. conventional mechanical bond mode on the first junction plane 121 of gear casing 12, the second junction plane 122 in conjunction with the carriage 17 of high-speed rotary body 20 or motor 11.In addition, be provided with the conventional seal arrangements such as rubber bushing on the first junction plane 121, the second junction plane 122, for separating the outside and inner of gear casing 12, so that its inside is sealed.Described associated methods and seal arrangement are common structure, therefore description is omitted at this.
By said gear shell 12, can first diameter, larger gearwheel be installed on engine shaft 14 in when assembling, and the second junction plane 122 of gear casing 12 is installed on the carriage 17 of motor 11, then on the first junction plane 121 of gear casing 12, high-speed rotary body 20 and spiral case 13 are installed successively.
Describe high-speed rotary body 20 in detail referring to Fig. 5.Fig. 5 is the sectional view of the high-speed rotary body 20 of the turbo blower 100 shown in Fig. 1, and dotted portion is the exploded view that shows the first combination bearing 26.
With reference to Fig. 5, high-speed rotary body 20 comprises solid of rotation shell 23, sliding bearing 24 and a pair of first combination bearing 26 of ball bearing 25 one formations of running shaft 21, built-in described running shaft 21, the impeller 22 of being combined with running shaft 21 1 ends.
Solid of rotation shell 23 is constituted as cylindric on the whole, and and conventional high-speed rotary body in the separated type used differently, solid of rotation shell 23 integral productions of the present invention form.In running shaft 21, be formed with on the part of small gear 16, the part of solid of rotation shell 23 is broken away, so that small gear 16 is exposed to the outside of solid of rotation shell 23.The small gear 16 so exposed is meshed with the gearwheel 15 of gear casing 12 inside.
And the intermediate portion of solid of rotation shell 23 is provided with flange 27, is provided with a plurality of joining holes 271 on described flange 27, thereby solid of rotation shell 23 can be assembled on the first junction plane 121 of gear casing 12.And be provided with ，Gai hole, a plurality of hole give in the back in described the first combination bearing 26 supplying lubricating oils for removal of lubricant on solid of rotation shell 23.About this hole, part is done and is illustrated in the back.
To be arranged on centered by the small gear 16 on running shaft 21, be respectively arranged with the first combination bearing 26 in its both sides.The first combination bearing 26 is configured to built-up shaft bearing 28 inside and is provided with sliding bearing axle 241 and ball bearing 25 simultaneously.
As shown in the dotted portion of Fig. 5, the first combination bearing 26 comprises built-up shaft bearing 28, sliding bearing axle 241 and ball bearing 25.Built-up shaft bearing 28 has plain bearing housing 281 and ball-bearing housing 282, and described two bearing supports are structure as a whole.And sliding bearing axle 241 is arranged on the outer circumferential face of running shaft 21, and be built in plain bearing housing 281, and form sliding bearing 24 together with plain bearing housing 281.Ball bearing 25 is arranged at ball-bearing housing 282 inside.Ball bearing 25 comprises ball 251 and surrounds the foreign steamer 252 of described ball 251 and interiorly take turns 253, described ball 251 direct support load when low-speed running.
In the dotted portion of Fig. 5, reference character 261 means to be fixed in the ring between built-up shaft bearing 28 and solid of rotation shell 23, and reference character 262 means ball bearing 25 is attached to the coupling collar on built-up shaft bearing 28.And reference character 263 means built-up shaft bearing 28 is fixed in to the nut on running shaft 21.
In the first embodiment's turbo blower 100, use the reasons are as follows of the first combination bearing 26 on high-speed rotary body 20:
If only use sliding bearing on high-speed rotary body, although the oil pressure produced by High Rotation Speed (oilpressure) can support larger load, but under non-High Rotation Speed state, in the situation that start, stop or low-speed running, plain bearing housing will directly contact with running shaft.Therefore, not only be difficult to start, and heating and the wear problem that friction causes can occur.In order to address these problems, must force to be lubricated with oil pump.
On the contrary, the friction problem that if only use ball bearing on high-speed rotary body, can solve startup, stop or occurring during low-speed running, and have advantages of under the oil-less pump state and only need to provide the lubricant oil without pressurization.Yet, when High Rotation Speed, ball bearing will be born larger load, so there is the shortcoming that durability descends.
Therefore, in the first embodiment's turbo blower 100, high-speed rotary body 20 has the first combination bearing 26 consisted of sliding bearing 24 and ball bearing 25, thereby can solve above-mentioned all problems.
As mentioned above, if use the first combination bearing 26 on high-speed rotary body 20, owing to there being ball bearing 25, so running shaft 21 structurally can directly not contact with built-up shaft bearing 28.Therefore, turbo blower 100 of the present invention during driven at low speed, can be supported by ball bearing 25 driving of high-speed rotary bodies 20 under initial state, and when high-speed driving, can be by the driving of sliding bearing 24 support high-speed rotary bodies 20.
According to the said structure of the first combination bearing 26, when high-speed rotary body 20 drives, along with the difference of Operational Zone (rotational speed), load support effect meeting changes automatically.That is, when comprising the driven at low speed that starts running and shut down, load is applied to ball 251, thus ball bearing 25 support load, and 24, sliding bearing turns round under no load condition.Simultaneously, if rotational speed increases, the oil slick thickness that is formed on sliding bearing 24 increases, and sliding bearing 24 is in the above support load of fixing speed, and 25, ball bearing turns round under no load condition.
For this reason, the gap that arranges of sliding bearing 24 forms the gap that arranges that is greater than ball bearing 25.At this, the gap that arranges of sliding bearing 24 means the poor of the internal diameter of plain bearing housing 281 and sliding bearing axle 241 diameters, and ball bearing 25 the value that gap means to deduct from the internal diameter of foreign steamer 252 and interior difference of taking turns 253 external diameter ball 251 diameters is set.Below the described difference that gap is set is described, when gap is set is 0.2mm of sliding bearing 24, the gap that arranges of ball bearing 25 can be 0.1mm.
In the first embodiment, even oil pump additionally is not set, the sliding bearing 24 of the first combination bearing 26 also can form oil film in addition.Below with reference to Fig. 6, this part is described.
Fig. 6 is the plan view of the running shaft 21 of the turbo blower 100 shown in Fig. 1, and left view and the right elevation of running shaft 21 is shown in figure simultaneously.
With reference to Fig. 6, be arranged on the surface of the sliding bearing axle 241 on running shaft 21 and be provided with a plurality of oil grooves 242 and a plurality of cone groove 243, described a plurality of oil grooves 242 and a plurality of cone groove 243 are for supplying lubricating oil.Described a plurality of oil groove 242 and a plurality of cone groove 243 are in the setting that tilts of the direction of running shaft 21.The oil groove 242 that is positioned at small gear 16 1 sides is contrary with the true dip direction of the oil groove 242 that is positioned at small gear 16 opposite sides and cone groove 243 with the true dip direction of boring groove 243.And it is darker with the part that oil groove 242 joins that each bores groove 243, and, away from oil groove 242, its degree of depth is more shallow.
So be arranged on the lip-deep oil groove 242 of sliding bearing axle 241 and there is the effect for oil supply, and bore the lubricant oil generation pressure that 243 pairs of grooves are supplied to oil groove 242, to form oil film.Therefore when running shaft 21 rotation, described oil groove 242 and cone groove 243 play the oil pump effect.
When running shaft 21 High Rotation Speed, can produce wedging effect (wedgingeffect) on sense of rotation, and parts of lubricating oil produces high pressure by centrifugal action on sliding bearing 24.As a result, when running shaft 21 is suspended, from plain bearing housing 281, separate, thereby running shaft 21 can carry out High Rotation Speed under state of suspension.Under this state, if running shaft 21 High Rotation Speeds,, because ball bearing 25 can not play bearing effect (that is, owing to can not contacting with running shaft 21), result can extend the life-span of high-speed rotary body 20.
Therefore in turbo blower 100, as long as can give the first combination bearing 26 supplying lubricating oils, even oil pump is not set, also can solve the friction of High Rotation Speed generation and to all problems such as pressurization of lubricant oil.
In addition, turbo blower 100 has the structure that increases running shaft 21 rotational speeies by gearwheel 15 and small gear 16, so will inevitably produce the side pressure that gear drive causes.Usually from diameter, larger gearwheel 15 sides act on small gear 16 sides that diameter is less in this side pressure.And the substantial role direction of side pressure is not and rectangular 3 directions of the veritcal linearity at running shaft 21 centers (expression clockwise), but approximately 5 directions of its downside.
Therefore, should use can buffer function in the structure of the side pressure of the small gear 16 of running shaft 21.Be provided with side pressure dashpot 29 (with reference to the dotted portion of Fig. 5) on the internal surface of plain bearing housing 281 for this reason.Side pressure dashpot 29 is arranged on part relative with gearwheel 15 in plain bearing housing 281 internal surfaces (being the opposite direction of side pressure action direction).The length of side pressure dashpot 29 and the degree of depth decide by calculated load according to high-speed rotary body 20 specifications.Side pressure dashpot 29 can have the circular shape that is equal to or less than 180 °.
The part that is provided with side pressure dashpot 29 in built-up shaft bearing 28 can not form oil film, and, only at its opposition side, a side that is subject to the side pressure effect forms oil film.Therefore, can remove the side pressure that gearwheel 15 causes, to carry out smoothly High Rotation Speed.
The above has illustrated the method for removing the radial load that acts on high-speed rotary body 20.But, when high-speed rotary body 20 High Rotation Speed, poor due to the pressure that acts on 22 outlets of impeller 22 entrances and impeller, high-speed rotary body 20 can be subject to the effect of axial load.Therefore, the following describes the method for removing the axial load that acts on high-speed rotary body 20.
Be provided with impeller 22 on a side of running shaft 21 in high-speed rotary body 20 (take Fig. 5 as punctual its left side).Now in the ingress of impeller 22, form negative pressure (-), the outlet port of impeller 22 forms malleation (+).Therefore, take running shaft 21 as benchmark, at the upper axial load that produces of the direction that is provided with impeller 22 (left side of Fig. 5).
In order to remove axial load, the first embodiment takes following scheme.1. in the end of the solid of rotation shell 23 relative with impeller 22, vent hole 231 is set, 2. adjusts the helical gear direction that is arranged at the small gear 16 on running shaft 21,3. ball bearing 25 is set on built-up shaft bearing 28.
Secondly, the oil circulation system of turbo blower 100 is described with reference to Fig. 7.Oil circulation system has under the oil-less pump state effect to high-speed rotary body 20 circulation supplying lubricating oils.
Fig. 7 comes summary to show oil circulation system by the positive view of the turbo blower 100 middle gear shells 12 shown in Fig. 1 and the sectional view of sectional view and high-speed rotary body 20.
With reference to Fig. 7, be provided with the guiding lid 30 around gearwheel 15 on the internal face of gear casing 12.Guiding is covered on 30 and is provided with a plurality of oil guide slot 301.And the inside upper part of gear casing 12 is provided with and the fuel tank 31 of guiding the end of covering 30 and being connected.
Therefore, if gearwheel 15 rotation, the lubricant oil be contained in the oil storage tank 32 of gear casing 12 bottoms is dispersed by the wheel tooth of gearwheel 15, simultaneously with guiding cover 30 and oil guide slot 301 move, then with its gravity, fall into fuel tank 31 interior and be collected.Now, remaining in moment that the lip-deep lubricant oil of gearwheel 15 contacts with small gear 16 at gearwheel 15 plays the effect of lubricated gearwheel 15 and small gear 16.
After collecting parts of lubricating oil in fuel tank 31 and discharging by oil drain out 311 with its gravity, be supplied to the oil-feed port 232 on the solid of rotation shell 23 that is arranged on high-speed rotary body 20 along oil pipe.
The lubricant oil that is supplied to the oil-feed port 232 of solid of rotation shell 23 is divided into both direction, wherein be supplied on a small quantity ball bearing 25, and major part is supplied to sliding bearing 24.When running shaft 21 High Rotation Speed, the lubricant oil that is supplied to sliding bearing 24 is applied in pressure by the cone groove 243 on sliding bearing axle 241 and forms oil film, with supporting rotating shaft 21.And the lubricant oil that sliding bearing 24 is used flows to the opposite direction of the feeding direction, and discharge from the part of cutting open of the solid of rotation shell 23 that exposes small gear 16, then fall in the oil storage tank 32 of gear casing 12 bottoms.
In addition, if high-speed rotary body 20 High Rotation Speeds, the lubricant oil that is supplied to the first combination bearing 26 can generate oil vapor when being evaporated.
Oil vapor is discharged to the inside of gear casing 12 and the outside of gear casing 12 centered by the flange 27 of solid of rotation shell 23.The oil vapor that is discharged to gear casing 12 inside is supplied to the first combination bearing 26 again by the loop structure of lubricant oil, so other problem can not occur.Yet, need the outside oil vapor of discharging of subtend gear casing 12 to carry out subsequent treatment.
From the inside of the first combination bearing 26, towards impeller 22 directions, be discharged to the oil vapor of gear casing 12 outsides, its part is condensed, and remaining part keeps steam condition.Thus, the lubricant oil be condensed reclaims mouth 33 by reclaiming mouthful 233 oil that are recovered to oil storage tank 32.And, after the oil vapor of steam condition is discharged by steam outlet 234, in oil vapor cooler 34 after condensation, then be supplied to fuel tank 31 by the cold oil supplying mouth 35 of fuel tank 31.
So, the lubricant oil that is supplied to fuel tank 31 by cold oil supplying mouth 35 is recovered in oil storage tank 32 through oil pipe 36.In addition, the interior residual micro oil steam of fuel tank 31 is discharged to outside by the relief opening 37 of fuel tank 31.At this, fuel tank 31 is provided with barrier 38, and its top is open state, and inside is provided with through hole.Therefore, but fuel tank 31 substantial separation interim the storage by guiding covers 30 and the lubricant oil of oil guide slot 301 collections and from the lubricant oil be condensed of oil vapor cooler 34 supplies.
In addition, by the oil storage tank 32 that gear casing 12 sealings are formed, storing lubricant oil, and on the above-below direction of oil storage tank 32 sidewalls, arrange porose.And, be communicated with on connecting tube in these holes and be provided with control valve 39.Therefore, can keep in oil storage tank 32 for driving the required appropriate lubricant oil of high-speed rotary body 20 by adjusting control valve 39.
If further carefully explanation,, when high-speed rotary body 20 starts to drive, if consider dispersing of lubricant oil, need more lubricant oil, if but closed control valve 39, the lubricant oil of oil storage tank 32 is by exhaustion.Therefore, if suitably control the amount of the lubricant oil that is supplied to control valve 39, can keep the lubricant oil that drives high-speed rotary body 20 required.
In Fig. 7, reference character 40 means pressure regulator valves, and it is connected with vent hole 231, poor with regulating action in the pressure of impeller 22 front and back.
Fig. 8 is the part section plan view of the turbo blower 110 that relates to of second embodiment of the invention.Parts identical with foregoing the first embodiment in the present embodiment have been used identical reference character.
With reference to Fig. 8, the second embodiment's turbo blower 110 comprises engine shaft 14, gearwheel 15, high-speed rotary body 20 and the second combination bearing 42.
If engine shaft 14 rotates by motor 11 work, increase the power of motor 11 when gearwheel 15 and small gear 16 rotate, thereby drive high-speed rotary body 20.Therefore, extraneous gas flows in the impeller 22 of rotation by suction passage, and accelerated and compression by impeller 22 time, and then pressurized gas is discharged to spiral case 13 by diffuser channel.In Fig. 8, arrow means the inflow direction of gas and discharges direction.
In front in the working procedure of described turbo blower 110, the load and the small gear 16 that produce gearwheel 15 self on gearwheel 15 promote the radial load that gearwheels 15 cause, but also produce the spiral-shaped axial load caused due to gearwheel 15 and small gear 16.The second following combination bearing 42 is at gearwheel 15 inner support gearwheels 15, so the effective reducing effect of meeting is in radial load and the axial load of gearwheel 15.
Fig. 9 observes shown in Fig. 8 the sectional view of engine shaft 14 and gearwheel 15 turbo blower 110 from the A direction, Figure 10 is the partial enlarged drawing of Fig. 9.
Referring to Fig. 9 and Figure 10, the second combination bearing 42 comprises tapered roller bearing 45 and ball bearing 46, described two bearings between stationary axle 41 and gearwheel 15 along with engine shaft 14 direction setting side by side.Tapered roller bearing 45 comprises the roller 451 that plugs with true dip direction, around interior wheel 452 and the foreign steamer 453 of roller 451.Ball bearing 46 comprises ball 461, around interior wheel 462 and the foreign steamer 463 of ball 461.Inside take turns 462 and be sheathed on stationary axle 41, foreign steamer 463 combines with gearwheel 15.
And tapered roller bearing 45 reduces radial load and the axial load that acts on gearwheel 15 simultaneously, and ball bearing 46 reduces the radial load that acts on gearwheel 15 again.Therefore, the second embodiment's turbo blower 110 reduces by the second combination bearing 42 radial load and the axial load that acts on gearwheel 15 to greatest extent.As a result, can prevent because the noise of generation, the damage of gearwheel 15 and the distortion of engine shaft 14 are moved in the position of gearwheel 15.
It is consistent with engine shaft 14 center that stationary axle 41 utilizes fixed block 47 and bolt 48 to be fixed in gear casing 120 ，Qie Qi centers.The inside of stationary axle 41 is along with stationary axle 41 direction side by side, being formed with oilhole 411, and it is for giving the second combination bearing 42 supplying lubricating oils.Now, between stationary axle 41 and engine shaft 14, there is predetermined spacing, to form to the runner of the second combination bearing 42 guiding lubricant oil.
In addition, engine shaft 14 is not overlapping with gearwheel 15, and is fixed with flange 141 on the end outer circumferential face relative with gearwheel 15 in described engine shaft 14.A plurality of joint bolts 49 that gearwheel 15 can connect gearwheel 15 and flange 141 by utilization are fixed on engine shaft 14 in the mechanical bond mode.Now, gearwheel 15 does not adopt the permanent bond modes such as shrink fit, but is incorporated on engine shaft 14 in mode removably, so change or during maintenance gearwheel 15, can easily carry out assembling and the decomposition of gearwheel 15 and engine shaft 14 when needs.
Figure 11 is the partial enlarged drawing of the 110 middle gear shells 120 of turbo blower shown in Fig. 8 and gearwheel 15.
With reference to Figure 11, with regard to gear casing 120, at any one joint bolt 49 with in a plurality of joint bolts 49, on relative position, be provided with opening portion 123.And, can separate joint bolt 49 by described opening portion 123 inserters (not shown).That is, after utilizing instrument separation joint bolt 49, with manually-operable rotation gearwheel 15, and other joint bolt 49 is put into to opening portion 123 positions, and then inserter, to separate joint bolt 49.Thereby, can separate all a plurality of joint bolts 49 by said process repeatedly.
After all joint bolts 49 of complete removal, gearwheel 15 is supported by the second combination bearing 42, if under this state disengage gears shell 120 and hood 43, can easily decompose motor 11 and engine shaft 14 from gearwheel 15 and gear casing 120.
In the second embodiment's turbo blower 110, the 26S Proteasome Structure and Function of high-speed rotary body 20 and the first combination bearing 26 is identical with foregoing the first embodiment, so description is omitted at this.
Below the shape of hood 43 and gear casing 120 described.
Figure 12 is the stereogram of hood 43 from turbo blower 110 shown in B direction observation Fig. 8.
With reference to Fig. 8 and Figure 12, hood 43 is provided with the mesopore 431 for holding engine shaft 14, and has the 3rd junction plane 432, and described the 3rd junction plane 432 is combined on motor 11 around mesopore 431.And hood 43 has the dimple (recess) 50 outstanding towards motor 11 directions, thereby enlarged the inner space of the assembly body of hood 43 and gear casing 120 towards motor 11 directions.
The capacity of turbo blower 110 is larger, and the length of running shaft 21 is just longer, so need to form the space that holds running shaft 21.In the second embodiment's turbo blower 110, owing at hood 43, being provided with dimple 50, the opposite side of the impeller 22 in high-speed rotary body 20 can be divided and is received in dimple 50, so large high-speed solid of rotation 20 can also easily be set.
Figure 13 observes the stereogram of the gear casing 110 turbo blower 110 shown in Fig. 8 from the C direction, Figure 14 is the I-I line sectional view of Figure 13.
With reference to Figure 13 and Figure 14, the structure of gear casing 120 is shapes that the degree of opening that is incorporated into that side of hood 43 is greater than gearwheel 15 diameters.That is, gear casing 120 comprises vertical wall 51 and sidewall 52, and has the wide-open structure of that side that is fixed in hood 43.Wherein, described vertical wall 51 is provided with stationary axle 41 for holding gearwheel 15 and two mesopores of high-speed rotary body 20, and described sidewall 52 enlarges towards hood 43 from the edge of vertical wall 51.
Therefore, as shown in Figure 8, gearwheel 15 and engine shaft 41 are assembled, and gear casing 120 is fixed on hood 43, with after described gearwheel 15, again stationary axle 41 and high-speed rotary body 20 are installed in gear casing 120, then on solid of rotation shell 23, assemble successively spiral case 13.The decomposition process of described structure is contrary with foregoing assembling sequence.The present invention is due to the shape of the removably combining structure with gearwheel 15 and engine shaft 14 and the larger gear casing 120 of a side degree of opening, so the assembling of turbo blower 110 and decomposition process become simply.
The oil circulation system of the turbo blower 110 below the second embodiment related to describes.
Figure 15 observes the plan view of gear casing 120 shown in Figure 13 from the D direction.
With reference to Figure 14 and Figure 15, vertical wall 51 internal surfaces of gear casing 120 are provided with the guiding lid 30 that probably is circular shape, described guiding lid 30 parts around gearwheel 15.It is outstanding to hood 43 that 30 internal surfaces from vertical wall 51 are covered in guiding, and its width w1 (with reference to Figure 14) is consistent with the width w2 (with reference to Figure 14) of the sidewall 52 of gear casing 120.Guide the diameter that the internal diameter that covers 30 is greater than gearwheel 15, and separated by a distance with gearwheel 15.
In Figure 15, the sense of rotation of gearwheel 15 is counterclockwise, and guiding covers 30 and take Figure 15 as benchmark, has the shape that general left upper portion is cut open.Guide the sense of rotation along gearwheel 15 on the internal surface that covers 30 and be provided with oil guide slot 301.With engine shaft 14 direction side by side on, a plurality of described oil guide slot 301 setting separated by a distance (with reference to Figure 14).
And, on the vertical wall 51 internal surface tops of gear casing 120, on the outside, side of gearwheel 15, be provided with the protuberance 53 of stairstepping.Protuberance 53 forms the ladder descended towards sidewall 52 directions.One end of protuberance 53 is connected with sidewall 52, and the other end be take Figure 15 during as benchmark, and on level and Vertical direction, with guiding, to cover 30 upper side ends separated by a distance.The width of protuberance 53 equals guiding and covers 30 width.
If aforesaid gears shell 120 is incorporated on hood 43, sidewall 52, guiding cover 30 and protuberance 53 just can be close to hood 43, and inner space is scheduled in formation.; the assembly body bottom of gear casing 120 and hood 43 is provided with oil storage tank 32; gearwheel 15 and guiding are provided with oil duct between covering 30, and are provided with interim accumulator tank 54 above protuberance 53, its lubricant oil for collecting lubricant oil and again circulating and collected.
Therefore, if gearwheel 15 rotation, when being contained in lubricant oil in oil storage tank 32 wheel tooth by gearwheel 15 and dispersing, the oil guide slot 301 of cover setting on 30 along guiding moves, then fall on protuberance 53 with its gravity, and be collected in interim accumulator tank 54.And the lubricant oil of collecting in interim accumulator tank 54 is supplied to the second combination bearing 42 of gearwheel 15 and the first combination bearing 26 of high-speed rotary body 20 by the loop structure of following explanation.
In foregoing gear casing 120 structures, guiding cover 30 and protuberance 53 and gear casing 120 one formations.Therefore, after can avoiding additionally making oil storage tank and interim accumulator tank, and it is assembled in to the trouble of gear casing inside, and by gear casing 120 and hood 43 with the tightness combinations of states, thereby oil storage tank 32 and interim accumulator tank 54 can easily be set.
Figure 16 observes the plan view of turbo blower 100 shown in Fig. 8 from the C direction, its part by gear casing 120 outsides is illustrated in dotted line.
With reference to Figure 15 and Figure 16, in vertical wall 51 outer installment of gear casing 120, the first oil pipe 55 is arranged, described the first oil pipe 55 is for connecting the stationary axle 41 of interim accumulator tank 54 and gearwheel 15.That is, be provided with the first openings 56 in the vertical wall 51 of gear casing 120 with on the corresponding position of described interim accumulator tank 54, and an end of the first oil pipe 55 is connected with the first openings 56.And the other end of the first oil pipe 55 is connected with the oilhole 411 on being arranged at stationary axle 41.
Show the part of the first oil pipe 55 be connected with stationary axle 41 in Fig. 9 with dotted line.With reference to Fig. 9, the first oil pipe 55 offers the oilhole 411 of stationary axle 41 by the lubricant oil of collecting in interim accumulator tank 54, and the lubricant oil that is supplied to oilhole 411 lubricated second combination bearing 42 when flowing through successively ball bearing 46 and tapered roller bearing 45.Then, lubricant oil falls into oil storage tank 32 again, and collects its inside.
Figure 17 observes the right elevation of the turbo blower 110 of Fig. 8 from the B direction, and shows the inside of the gear casing 120 after a part of cutting hood 43 open.Figure 18 is the plan view of the 110 high speed solid of rotation 20 of turbo blower shown in Fig. 8.
With reference to Figure 17 and Figure 18, vertical wall 51 inside of gear casing 120 are provided with the second oil pipe 57, and described the second oil pipe 57 passes to high-speed rotary body 20 for the lubricant oil by interim accumulator tank 54 interior collections.For this reason, the lower end of protuberance 53 is provided with the second openings 58, and an end of the second oil pipe 57 is connected with the second openings 58.And be provided with the 3rd openings 59 on the vertical wall 51 of gear casing 120 with on the overlapping position of solid of rotation shell 23, and the other end of the second oil pipe 57 is connected with the 3rd openings 59.
And, be provided with the oil duct 60 of the first combination bearing 26 of being positioned at impeller 22 sides for connecting a pair of the first combination bearing 26 (take Figure 18 as punctual, be first combination bearing 26 in left side) and the 3rd openings 59 in the inside of solid of rotation shell 23.And, be useful on first combination bearing 26 (take Figure 18 as punctual, be first combination bearing 26 on right side) of connection impeller 22 opposition sides and the 3rd oil pipe 61 of oil duct 60 in the outer installment of solid of rotation shell 23.
Therefore, the lubricant oil be collected in interim accumulator tank 54 is supplied on high-speed rotary body 20 by the second oil pipe 57, and the lubricant oil of supplying with is supplied to respectively the first combination bearing 26 of impeller 22 sides and the first combination bearing 26 of impeller 22 opposition sides by oil duct 60 and the 3rd oil pipe 61.
Lubricated described two bearings when the lubricant oil that is supplied to impeller 22 side the first combination bearings 26 is flowed through sliding bearing 24 and ball bearing 25 successively.Now, between ball bearing 25 and impeller 22 bearing 62 and be provided with lubrication hole 63 on solid of rotation shell 23 positions of described bearing 62, and the outer installment of solid of rotation shell 23 has the 4th oil pipe 64, it is for connecting lubrication hole 63 and gear casing 120.Therefore, the lubricant oil used flows in gear casing 120 by the 4th oil pipe 64, and collects in oil storage tank 32.
And the lubricant oil be supplied to by the 3rd oil pipe 61 on the first combination bearing 26 of impeller 22 opposition sides is supplied to sliding bearing 24 and ball bearing 25, to lubricate described two bearings.And the lubricant oil used falls into oil storage tank 32 and collects in it by the part of cutting open for exposing small gear 16 in the middle of solid of rotation shell 23.
With reference to Fig. 9, on the outer circumferential face of engine shaft 14, on the direction away from gearwheel 15, bearing 65 and Sealing 66 have been arranged side by side.In the rotary course of gearwheel 15, lubricant oil also disperses at a high speed to engine shaft 14, so can be enough to by the lubricant oil dispersed lubricating bearings 65.Be provided with the 5th oil pipe 67 on Sealing 66, its lubricant oil that will arrive Sealing 66 by bearing 65 is recovered in oil storage tank 32.
As mentioned above, even the second embodiment's turbo blower 110 additionally is not provided for the oil pump of supplying lubricating oil, still lubrication oil circulation can be supplied to the second combination bearing 42 of gearwheel 15 and the first combination bearing 26 of high-speed rotary body 20.Therefore, the present invention can reduce the number of components by the supply structure of simplifying lubricant oil.
Top accompanying drawings the preferred embodiments of the present invention, but the present invention is not limited to above-described embodiment, within not breaking away from spiritual scope of the present invention, can have various embodiments and variation, these ought to belong in protection scope of the present invention.
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.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020080053860A KR100895667B1 (en) | 2008-06-09 | 2008-06-09 | Turbo blower and high speed rotation body using for thereof |
| KR10-2008-0053860 | 2008-06-09 | ||
| KR10-2009-0035014 | 2009-04-22 | ||
| KR1020090035014A KR101095614B1 (en) | 2009-04-22 | 2009-04-22 | Turbo blower |
| PCT/KR2009/003059 WO2009151245A2 (en) | 2008-06-09 | 2009-06-08 | Turbo blower and high speed rotating body used in same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102057164A CN102057164A (en) | 2011-05-11 |
| CN102057164B true CN102057164B (en) | 2014-01-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980121594.9A Expired - Fee Related CN102057164B (en) | 2008-06-09 | 2009-06-08 | Turbo blower and high speed rotating body used in same |
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| Country | Link |
|---|---|
| US (1) | US20120107099A1 (en) |
| EP (1) | EP2314879A2 (en) |
| JP (1) | JP5356513B2 (en) |
| CN (1) | CN102057164B (en) |
| WO (1) | WO2009151245A2 (en) |
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| US7128061B2 (en) * | 2003-10-31 | 2006-10-31 | Vortech Engineering, Inc. | Supercharger |
-
2009
- 2009-06-08 US US12/996,810 patent/US20120107099A1/en not_active Abandoned
- 2009-06-08 WO PCT/KR2009/003059 patent/WO2009151245A2/en active Application Filing
- 2009-06-08 EP EP09762632A patent/EP2314879A2/en not_active Withdrawn
- 2009-06-08 JP JP2011513414A patent/JP5356513B2/en not_active Expired - Fee Related
- 2009-06-08 CN CN200980121594.9A patent/CN102057164B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2089991U (en) * | 1990-02-18 | 1991-12-04 | 李联奎 | Energy saving two-purpose blower |
| US6192871B1 (en) * | 1998-10-30 | 2001-02-27 | Vortech Engineering, Inc. | Compact supercharger |
| KR100723040B1 (en) * | 2005-08-18 | 2007-05-30 | 주식회사 에어젠 | Bearing assembly for high speed rotary body |
| CN2913682Y (en) * | 2006-05-23 | 2007-06-20 | 谢明顺 | Four-leaf Roots blower |
| CN200989303Y (en) * | 2006-12-27 | 2007-12-12 | 王绍全 | Opening and closing Roots blower |
Also Published As
| Publication number | Publication date |
|---|---|
| US20120107099A1 (en) | 2012-05-03 |
| WO2009151245A2 (en) | 2009-12-17 |
| WO2009151245A3 (en) | 2010-03-11 |
| JP2011522994A (en) | 2011-08-04 |
| EP2314879A2 (en) | 2011-04-27 |
| JP5356513B2 (en) | 2013-12-04 |
| CN102057164A (en) | 2011-05-11 |
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