CN102057164A - Turbo blower and high speed rotating body used in same - Google Patents
Turbo blower and high speed rotating body used in same Download PDFInfo
- Publication number
- CN102057164A CN102057164A CN2009801215949A CN200980121594A CN102057164A CN 102057164 A CN102057164 A CN 102057164A CN 2009801215949 A CN2009801215949 A CN 2009801215949A CN 200980121594 A CN200980121594 A CN 200980121594A CN 102057164 A CN102057164 A CN 102057164A
- Authority
- CN
- China
- Prior art keywords
- bearing
- gearwheel
- oil
- turbo blower
- gear casing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
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, axial load in the time of particularly can making driving and radial load reach minimized turbo blower and are used for the high-speed rotary body of 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 that is used to increase rotational speed.
The high-speed rotary body of direct drive mode is supported by pneumatic bearing (air bearing) usually.But pneumatic bearing is because component durability is poor, so long-term use (for example, more than 3 years) can be subjected to a lot of restrictions.
The employed common gear speeder of high-speed rotary body of driving mode is made up of gearwheel (bullgear) and small gear (pinion gear) indirectly.Wherein, described gearwheel is combined on the engine shaft, and described small gear is arranged on the high-speed rotary body, and is meshed with gearwheel.Yet, when possessing the turbo blower work of gear speeder, will produce radial load and axial load on high-speed rotary body and the gearwheel, 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 the turbomachinery, not only need gear-box itself is made level-split type, and the bearing that supports above-mentioned two gear shafts need be made level-split type.
When so making gear-box by separate mode, it is relatively poor to make precision, and after turbomachinery assemble, for carrying out high speed rotating when gear shaft is carried out centering (centering), very difficult assurance assembly precision.In addition, because the number of components increases, can cause fabricating cost to become big.
For supplying lubricating oil, the turbo blower of driving mode need possess oil pump indirectly, has therefore increased the number of components.And in the prior art, gearwheel and engine shaft in the time need changing gearwheel owing to the reasons such as tooth portion wearing and tearing of gearwheel, exist the dismounting of gearwheel and the problem of assembling difficulty by shrink fit (shrinkfit) combination.
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 a kind of again 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 be built-in with the gearwheel that is combined in engine shaft and with the small gear of gearwheel engagement; Iii) high-speed rotary body, this high-speed rotary body is included in outer circumferential face and is provided with running shaft, the impeller that combines with an end of running shaft of small gear and is built-in with running shaft and small gear and at least one 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 the gear casing and with gear casing and combines; And iv) spiral case, this spiral case coats impeller and also exports pressurized air.
First combination bearing can comprise: i) built-up shaft bearing, this built-up shaft bearing possess plain bearing housing and the ball-bearing housing that one constitutes; Ii) sliding bearing axle, this plain bearing housing is arranged at the outer circumferential face of running shaft, and is built in the plain bearing housing to constitute sliding bearing with plain bearing housing; And iii) ball bearing, this ball bearing is built in ball-bearing housing.
First combination bearing is positioned at the both sides of small gear, and the gap that is provided with of sliding bearing can be greater than the gap that is provided with of ball bearing.The surface of sliding bearing axle tilts and is provided with a plurality of oil grooves and a plurality of awl groove, and forming oil film from the teeth outwards, 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, the end relative with impeller is provided with vent hole in the high-speed rotary body 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 drawing running shaft towards the opposite direction of impeller.
The internal face of gear casing is provided with the guiding lid with circular shape, and it centers on the part of gearwheel and has a plurality of oil guide slot, and the inside upper part of gear casing can be provided with the fuel tank that is connected with the end of guiding lid.
The inside of gear casing is provided with oil pipe, thereby supplies with the lubricant oil collect in the fuel tank to first combination bearing, and an end of oil pipe is connected with the oil drain out that is provided with on fuel tank, and the other end of oil pipe is connected with oil-feed port on being formed on first combination bearing.
The solid of rotation shell is provided with the steam outlet that is used to discharge oil vapor, and turbo blower further can comprise the oil vapor cooler that is connected with fuel tank with steam outlet.And the oil vapor that the oil vapor cooler can condensation be discharged from steam outlet also supplies in the fuel tank.
The bottom of gear casing is provided with oil storage tank, and the upper-lower position of oil storage tank sidewall is provided with pair of holes, and gear casing further can comprise the control valve that is used to be communicated with the connecting tube of pair of holes and is arranged at connecting tube.
Gearwheel is directly connected in engine shaft, and side relative with motor in the gear casing is provided with junction plane, and junction plane has the opening portion of diameter 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, and this running shaft outer circumferential face is provided with and the gearwheel pinion in mesh; Ii) impeller, this impeller combines with an end of running shaft; Iii) a pair of first combination bearing, this a pair of 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 first combination bearing, and the part of solid of rotation shell is broken away, so that small gear exposes.
A pair of first combination bearing can comprise respectively: i) built-up shaft bearing, this built-up shaft bearing possess plain bearing housing and the ball-bearing housing that one constitutes; Ii) sliding bearing axle, this sliding bearing axle is arranged on the outer circumferential face of running shaft, and is built in the plain bearing housing to constitute sliding bearing with plain bearing housing; And iii) ball bearing, this ball bearing is built in the ball-bearing housing.
Sliding bearing the be provided with gap of gap greater than ball bearing be set, the surperficial updip of sliding bearing axle tiltedly is provided with a plurality of oil grooves and a plurality of awl groove, to form oil film from the teeth outwards, and for absorbing the side pressure that gearwheel causes, 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 the engine shaft, and is provided with the mesopore that is used to install and fix axle at the center; Iii) second combination bearing, this second combination bearing is arranged between stationary axle and the gearwheel, and has at the tapered roller bearing and the ball bearing that face mutually on the direction side by side with engine shaft; And iv) high-speed rotary body, this high-speed rotary body has outer circumferential face and is provided with the running shaft of the small gear of gearwheel engagement and is incorporated into impeller on the end of running shaft.
Turbo blower further can comprise: i) hood, and this hood combines with motor, and is used to support engine shaft; And ii) gear casing, this gear casing is built-in with gearwheel and small gear, and is provided with the opening portion of diameter greater than the gearwheel diameter in the side that combines with hood.
The end outer circumferential face that engine shaft is relative with gearwheel is provided with flange, gearwheel is attached on the engine shaft by a plurality of joint bolts that connect gearwheel and flange, and the position that gear casing is relative with any one joint bolt in a plurality of joint bolts is provided with opening portion.Hood has towards the outstanding dimple (recess) of motor, and the part of high-speed rotary body is received in the dimple.
High-speed rotary body further can comprise: i) a pair of first combination bearing, and this a pair of 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 first combination bearing, and is installed on the gear casing, and part is broken away so that small gear exposes from gear casing inside.
First combination bearing can comprise respectively: i) built-up shaft bearing, this built-up shaft bearing possess plain bearing housing and the ball-bearing housing that one constitutes; Ii) sliding bearing axle, this sliding bearing axle is arranged on the outer circumferential face of running shaft, is built in simultaneously in the plain bearing housing to constitute sliding bearing with plain bearing housing; And iii) ball bearing, this ball bearing is built in ball-bearing housing.
Sliding bearing the be provided with gap of gap greater than ball bearing be set, the surperficial updip of sliding bearing axle tiltedly is provided with a plurality of oil grooves and a plurality of awl groove, to form oil film from the teeth outwards.
The internal face of gear casing is provided with the guiding lid of circular shape and the protuberance of stairstepping, wherein, the guiding lid is around the part of gearwheel, and protuberance is positioned at the outside, side of gearwheel, and protuberance forms interim accumulator tank in the assembly body inside 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.The position that gear casing is provided with interim accumulator tank is provided with first openings, and gear casing may further include first oil pipe, and first oil pipe is used to connect first openings and stationary axle in the outside of gear casing.
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 the engine shaft, thereby the lubricant oil that supplies to oilhole can be directed to second combination bearing.
The lower end of protuberance is provided with 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 second oil pipe that first openings is connected with the 3rd openings.
The inside of solid of rotation shell is provided with oil duct, be used for connecting first combination bearing and the 3rd openings of the impeller side of a pair of first combination bearing, and the outside of solid of rotation shell further can comprise the 3rd oil pipe, is used for connecting a pair of first combination bearing and first combination bearing and oil duct the impeller opposition side.
High-speed rotary body further can comprise at first combination bearing of impeller side and the bearing between the impeller, and bearing and solid of rotation shell are provided with oil drain out, the solid of rotation shell externally further can comprise the 4th oil pipe, be used to connect oil drain out and gear casing, thereby reclaim lubricant oil.
Turbo blower further can comprise: the direction away from gearwheel is arranged side by side in the outer circumferential face upper edge of engine shaft for i) bearing and Sealing, this bearing and Sealing; And ii) the 5th oil pipe, the 5th oil pipe is used to connect the inside of Sealing 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, fits together with hood simultaneously; Ii) gearwheel, this gearwheel releasably is incorporated on the engine shaft, and the center is provided with the mesopore that is used to be provided with stationary axle; Iii) high-speed rotary body, this high-speed rotary body comprises that outer circumferential face is provided with running shaft, the impeller that combines with running shaft one end of the small gear that meshes with gearwheel, is used at least one first combination bearing of supporting rotating shaft and is built-in with running shaft and first combination bearing, and a part is broken away so that the solid of rotation shell that small gear exposes; Iv) second combination bearing, this second combination bearing is arranged between stationary axle and the 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 the opening portion of diameter greater than the diameter of gearwheel in the side that combines with hood; And vi) spiral case, this spiral case is around impeller and export pressurized air.
According to the present invention, adopt combination bearing to absorb the 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 height of assembling, can obtain wide in range application in the turbo blower field thus.
According to the present invention, provide effective lubricant oil that system is provided, can the turbo blower that turn round steady in a long-term even do not use oil pump also can provide.
According to the present invention,, also can use a spot of parts that not only economic life but also long turbo blower also can be provided with transmission of power to gearwheel even do not use existing being used for the gearwheel running shaft of transmission of power to gearwheel.
According to the present invention, when needing replacing or maintenance gearwheel, can easily assemble and decompose high-speed rotary body and gearwheel and motor.
Description of drawings
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 turbo blower shown in Figure 1.
Fig. 3 is a stereogram of observing the gear casing the turbo blower shown in Figure 1 from impeller side.
Fig. 4 is from starting pusher side to observe the stereogram of the gear casing the turbo blower shown in Figure 1.
Fig. 5 is the sectional view that shows the high-speed rotary body of turbo blower shown in Figure 1.
Fig. 6 is the plan view of the running shaft of turbo blower shown in Figure 1.
Fig. 7 is the schematic representation that the sectional view of the front section view, side sectional view and the high-speed rotary body that utilize the gear casing of turbo blower shown in Figure 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 turbo blower shown in Figure 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 turbo blower middle gear shell shown in Figure 8 and gearwheel.
Figure 12 is a stereogram of observing hood the turbo blower shown in Figure 8 from the B direction.
Figure 13 is a stereogram of observing turbo blower middle gear shell shown in Figure 8 from the C direction.
Figure 14 is the sectional view of I-I line among Figure 13.
Figure 15 is a plan view of observing gear casing shown in Figure 13 from the D direction.
Figure 16 is a plan view of observing turbo blower shown in Figure 8 from the C direction.
Figure 17 is a right elevation of observing turbo blower shown in Figure 8 from the B direction.
Figure 18 is the plan view of turbo blower high speed solid of rotation shown in Figure 8.
Embodiment
Describe embodiments of the invention with reference to the accompanying drawings in detail, so that the technician of the technical field of the invention implements easily.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 turbo blower 100 shown in Figure 1.
See figures.1.and.2, 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 the support platform 10, and the part of high-speed rotary body described later 20 is positioned at the inside of gear casing 12.
In first embodiment's turbo blower 100, the engine shaft 14 of combination on the 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 the engine shaft 14, and running shaft 21 is provided with small gear 16, and gearwheel 15 and small gear 16 increase the power of motor 11 by engagement, drive high-speed rotary body 20 with this.
First embodiment has taked aforementioned power transmission structure, thereby can remove existing speedup with the Large Gear Shaft During that is used to support gearwheel in the gear-box, and having solved needs the problem that seals between motor and the gear-box, can reduce the number of components simultaneously, thereby reduces manufacture cost.
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 a side of motor 11, and degree that should be open is greater than gearwheel 15 diameters.And motor 11 is provided with the carriage 17 that is used for fixing gear casing 13.
Fig. 3 is a stereogram of observing turbo blower 100 middle gear shells 12 shown in Figure 1 from impeller 22, and Fig. 4 is a stereogram of observing turbo blower 100 middle gear shells 12 shown in Figure 1 from motor 11.
In Fig. 3, reference character 121 expressions are attached to high-speed rotary body 20 and spiral case 13 first junction plane of gear casing 12.In Fig. 4, reference character 122 expression is attached to itself gear casing 12 second junction plane on the carriage 17 of motor 11.
Can use the conventional mechanical bond mode of the combination etc. of screw bolt and nut carriage 17 in conjunction with high-speed rotary body 20 or motor 11 on first junction plane 121 of gear casing 12, second junction plane 122.In addition, first junction plane 121, second junction plane 122 are provided with conventional seal arrangements such as rubber bushing, are used to separate the outside and inner of gear casing 12, so that its inside is sealed.Described associated methods and seal arrangement are common structure, so omit its detailed description at this.
By said gear shell 12, can bigger gearwheel be installed on the engine shaft 14 diameter earlier in when assembling, and second junction plane 122 of gear casing 12 is installed on the carriage 17 of motor 11, on first junction plane 121 of gear casing 12, high-speed rotary body 20 and spiral case 13 are installed successively then.
Followingly describe high-speed rotary body 20 in detail with reference to Fig. 5.Fig. 5 is the sectional view of the high-speed rotary body 20 of turbo blower 100 shown in Figure 1, and dotted portion is the exploded view that shows 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 formation of running shaft 21, built-in described running shaft 21, the impeller 22 that combines 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.Be formed with in running shaft 21 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 that so exposes 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, and described flange 27 is provided with a plurality of joining holes 271, thereby solid of rotation shell 23 can be assembled on first junction plane 121 of gear casing 12.And solid of rotation shell 23 is provided with a plurality of holes, and this hole is given and will be described in the back be used for removal of lubricant first combination bearing, 26 supplying lubricating oils the time.About this hole, part is done and is specified in the back.
With the small gear 16 that is arranged on the running shaft 21 is the center, is respectively arranged with first combination bearing 26 in its both sides.First combination bearing 26 constitutes built-up shaft bearing 28 inside and is provided with sliding bearing axle 241 and ball bearing 25 simultaneously.
Shown in the dotted portion of Fig. 5, 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 is built in the plain bearing housing 281, and constitutes sliding bearing 24 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 and the interior wheel 253 of described ball 251, described ball 251 direct support load when low-speed running.
In the dotted portion of Fig. 5, the ring between built-up shaft bearing 28 and the solid of rotation shell 23 is fixed in reference character 261 expression, and reference character 262 expressions are attached to coupling collar on the built-up shaft bearing 28 with ball bearing 25.And reference character 263 expression is fixed in nut on the running shaft 21 with built-up shaft bearing 28.
In first embodiment's turbo blower 100, use the reasons are as follows of first combination bearing 26 on the high-speed rotary body 20:
If only use sliding bearing on the high-speed rotary body, though then the oil pressure (oilpressure) that produces by high speed rotating can support bigger load, but under non-high speed rotating state, promptly start, stop or the situation of low-speed running under, plain bearing housing will directly contact with running shaft.Therefore, not only be difficult to start, and the heating and the wear problem that can rub and cause.In order to address these problems, must use oil pump to force to be lubricated.
On the contrary, the friction problem that if on high-speed rotary body, only use ball bearing, then can solve startup, stop or taking place during low-speed running, and the advantage that only need provide under the oil-less pump state without the lubricant oil of pressurization is provided.Yet when high speed rotating, ball bearing will be born bigger load, so have the shortcoming that durability descends.
Therefore, in first embodiment's turbo blower 100, high-speed rotary body 20 has first combination bearing 26 that is made of sliding bearing 24 and ball bearing 25, thereby can solve above-mentioned all problems.
As mentioned above, if on high-speed rotary body 20, use first combination bearing 26, then 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 the driving of high-speed rotary bodies 20 by ball bearing 25 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 first combination bearing 26, when high-speed rotary body 20 drove, along with the difference of Operational Zone (rotational speed), load support effect meeting changed 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 on sliding bearing turns round under no load condition.Simultaneously, if rotational speed increases, the oil slick thickness that then is formed on sliding bearing 24 increases, and sliding bearing 24 is in the above support load of fixing speed, and 25 on ball bearing turns round under no load condition.
For this reason, the gap that is provided with of sliding bearing 24 forms the gap that is provided with greater than ball bearing 25.At this, the poor of the internal diameter of plain bearing housing 281 and sliding bearing axle 241 diameters represented in the gap that is provided with of sliding bearing 24, and ball bearing 25 the value that ball 251 diameters are represented to deduct from the difference of the external diameter of the internal diameter of foreign steamer 252 and interior wheel 253 in the gap is set.Below the described difference that the gap is set is described, when the gap is set is 0.2mm of sliding bearing 24, the gap that is provided with of ball bearing 25 can be 0.1mm.
In first embodiment, even oil pump additionally is not set, the sliding bearing 24 of 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 turbo blower 100 shown in Figure 1, and the left view and the right elevation of running shaft 21 is shown among the figure simultaneously.
With reference to Fig. 6, the surface that is arranged on the sliding bearing axle 241 on the running shaft 21 is provided with a plurality of oil grooves 242 and a plurality of awl groove 243, and described a plurality of oil grooves 242 and a plurality of awl groove 243 are used for supplying lubricating oil.Described a plurality of oil groove 242 and a plurality of awl 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 opposite with the true dip direction of oil groove 242 that is positioned at small gear 16 opposite sides and awl 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 shallow more.
So be arranged on sliding bearing axle 241 lip-deep oil grooves 242 and have the effect of supplying with oil, and bore the lubricant oil generation pressure that 243 pairs of grooves supply to oil groove 242, to form oil film.Therefore when running shaft 21 rotations, described oil groove 242 and awl groove 243 play the oil pump effect.
Promptly when running shaft 21 high speed rotating, on sense of rotation, can produce wedging effect (wedgingeffect), and parts of lubricating oil produces high pressure by centrifugal action on sliding bearing 24.As a result, separate from plain bearing housing 281 when running shaft 21 is suspended, thereby running shaft 21 can carry out high speed rotating under state of suspension.Under this state, if running shaft 21 high speed rotating, then because ball bearing 25 can not play bearing effect (that is, owing to can not contact with running shaft 21), the result can prolong the life-span of high-speed rotary body 20.
Therefore in turbo blower 100,,, also can solve the friction of high speed rotating generation and to all problems such as pressurization of lubricant oil even oil pump is not set as long as can give first combination bearing, 26 supplying lubricating oils.
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.This side pressure acts on the less small gear of diameter 16 sides from bigger gearwheel 15 sides of diameter usually.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 about 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.The internal surface of plain bearing housing 281 is provided with side pressure dashpot 29 (with reference to the dotted portion of Fig. 5) for this reason.Side pressure dashpot 29 is arranged in plain bearing housing 281 internal surfaces part (be the opposite direction of side pressure action direction) relative with gearwheel 15.The length of side pressure dashpot 29 and the degree of depth then decide by calculated load according to high-speed rotary body 20 specifications.Side pressure dashpot 29 can have and is equal to or less than 180 ° circular shape.
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 promptly is subjected to the side pressure effect forms oil film.Therefore, can remove the side pressure that gearwheel 15 causes, to carry out high speed rotating smoothly.
The method of removing the radial load that acts on high-speed rotary body 20 has been described above.But when high-speed rotary body 20 high speed rotating, owing to act on the poor of pressure that impeller 22 inlet and impeller 22 export, high-speed rotary body 20 can be subjected 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.
A side of running shaft 21 in the high-speed rotary body 20 (is punctual its left side with Fig. 5) is provided with impeller 22.Form negative pressure (-) in the ingress of impeller 22 this moment, and the outlet port of impeller 22 forms malleation (+).Therefore, be benchmark with running shaft 21, go up in the direction that is provided with impeller 22 (left side of Fig. 5) and produce axial load.
In order to remove axial load, first embodiment takes following scheme.1. in the end of the solid of rotation shell 23 relative vent hole 231 is set, 2. adjusts the helical gear direction that is arranged at the small gear 16 on the running shaft 21,3. ball bearing 25 is set on built-up shaft bearing 28 with impeller 22.
Secondly, the oil circulation system of turbo blower 100 is described with reference to Fig. 7.Oil circulation system has the effect of giving high-speed rotary body 20 circulation supplying lubricating oils under the oil-less pump state.
Fig. 7 comes summary to show oil circulation system by the positive view of turbo blower shown in Figure 1 100 middle gear shells 12 and the sectional view of sectional view and high-speed rotary body 20.
With reference to Fig. 7, the internal face of gear casing 12 is provided with the guiding lid 30 around gearwheel 15.Guiding is covered 30 and is provided with a plurality of oil guide slot 301.And the inside upper part of gear casing 12 is provided with guiding and covers the fuel tank 31 that 30 end is connected.
Therefore, if gearwheel 15 rotation, the lubricant oil that then is 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, it is interior and be collected to fall into fuel tank 31 with its gravity then.At this moment, remain in gearwheel 15 lip-deep lubricant oil play lubricated gearwheel 15 and small gear 16 in the moment that gearwheel 15 contacts with small gear 16 effect.
After collecting parts of lubricating oil in the fuel tank 31 and discharging by oil drain out 311, supply 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 with its gravity.
The lubricant oil that supplies to the oil-feed port 232 of solid of rotation shell 23 is divided into both direction, wherein supply to ball bearing 25 on a small quantity, and major part supplies to sliding bearing 24.When running shaft 21 high speed rotating, the lubricant oil that supplies to sliding bearing 24 is applied in pressure by the awl groove 243 on the sliding bearing axle 241 and forms oil film, with supporting rotating shaft 21.And sliding bearing 24 employed lubricant oil flow 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, fall into then in the oil storage tank 32 of gear casing 12 bottoms.
In addition, if high-speed rotary body 20 high speed rotating, the lubricant oil that then supplies to first combination bearing 26 can generate oil vapor when being evaporated.
Oil vapor is that the center is discharged to the inside of gear casing 12 and the outside of gear casing 12 with the flange 27 of solid of rotation shell 23.The oil vapor that is discharged to gear casing 12 inside supplies to first combination bearing 26 once more by the loop structure of lubricant oil, so other problem can not take place.Yet, need subtend gear casing 12 outside oil vapors of discharging to carry out subsequent treatment.
Be discharged to the oil vapor of gear casing 12 outsides towards impeller 22 directions from the inside of first combination bearing 26, its part is condensed, and remaining part keeps steam condition.Thus, the lubricant oil that is 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 was discharged by steam outlet 234, after the condensation, the cold oil supplying mouth 35 by fuel tank 31 supplied to fuel tank 31 again in oil vapor cooler 34.
So, the lubricant oil that supplies to fuel tank 31 by cold oil supplying mouth 35 is recovered in the oil storage tank 32 through oil pipe 36.In addition, the residual micro oil steam relief opening 37 by fuel tank 31 is discharged to the outside in the 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 and interim the storage by guiding covers 30 and the lubricant oil collected of oil guide slot 301 and from the lubricant oil that is condensed of oil vapor cooler 34 supplies.
In addition, store lubricant oil by gear casing 12 is sealed in the oil storage tank 32 that forms, and the above-below direction of oil storage tank 32 sidewalls is provided with the hole.And what be communicated with these holes is provided with control valve 39 connecting tube.Therefore, can keep being used in the oil storage tank 32 driving the required an amount of lubricant oil of high-speed rotary body 20 by adjusting control valve 39.
If further careful explanation then when high-speed rotary body 20 begins to drive, if consider dispersing of lubricant oil, needs more lubricant oil, if but closed control valve 39, then the lubricant oil of oil storage tank 32 is with exhaustion.Therefore, if suitably control supplies to the amount of lubricant oil of control valve 39, then can keep driving the required lubricant oil of high-speed rotary body 20.
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 first embodiment in the present embodiment have used identical reference character.
With reference to Fig. 8, second embodiment's turbo blower 110 comprises engine shaft 14, gearwheel 15, high-speed rotary body 20 and second combination bearing 42.
If engine shaft 14 rotates by motor 11 work, increase the power of motor 11 when then 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 sucking runner, and is accelerated by impeller 22 time and compresses, and pressurized gas is discharged to spiral case 13 by diffuser channel then.Arrow is represented the inflow direction of gas and is discharged direction among Fig. 8.
In the working procedure of described in front turbo blower 110, the load and the small gear 16 that produce gearwheel 15 self on the gearwheel 15 promote the radial load that gearwheels 15 cause, but also produce because the spiral-shaped axial load that causes of gearwheel 15 and small gear 16.The second following combination bearing 42 is at gearwheel 15 inner support gearwheels 15, so can effectively reduce radial load and the axial load that acts on gearwheel 15.
Fig. 9 is a sectional view of observing engine shaft 14 and gearwheel 15 turbo blower 110 shown in Figure 8 from the A direction, and Figure 10 is the partial enlarged drawing of Fig. 9.
Referring to Fig. 9 and Figure 10, 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, interior wheel 452 and the foreign steamer 453 that centers on roller 451.Ball bearing 46 comprises ball 461, centers on the interior wheel 462 and the foreign steamer 463 of ball 461.Interior wheel 462 is sheathed on the stationary axle 41, and 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 once more.Therefore, second embodiment's turbo blower 110 reduces radial load and the axial load that acts on gearwheel 15 to greatest extent by second combination bearing 42.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.
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 the described engine shaft 14.Gearwheel 15 can be fixed on the engine shaft 14 in the mechanical bond mode by utilizing a plurality of joint bolts 49 that connect gearwheel 15 and flange 141.At this moment, gearwheel 15 does not adopt permanent bond modes such as shrink fit, but is incorporated on the engine shaft 14 in mode removably, so change or during maintenance gearwheel 15, can carry out the assembling and the decomposition of gearwheel 15 and engine shaft 14 easily when needs.
Figure 11 is the partial enlarged drawing of turbo blower 110 middle gear shells 120 shown in Figure 8 and gearwheel 15.
With reference to Figure 11, with regard to gear casing 120, the position relative with any one joint bolt 49 in a plurality of joint bolts 49 is provided with opening portion 123.And, can put into instrument (not shown) by described opening portion 123 and come separating and combining bolt 49.That is, utilize after the instrument separating and combining bolt 49, rotate gearwheel 15, and other joint bolt 49 is put into opening portion 123 positions, and then put into instrument, with separating and combining bolt 49 with manually-operable.Thereby, can separate all a plurality of joint bolts 49 by said process repeatedly.
Behind all joint bolts 49 of complete removal, gearwheel 15 is supported by second combination bearing 42, if under this state disengage gears shell 120 and hood 43, then can decompose motor 11 and engine shafts 14 easily from gearwheel 15 and gear casing 120.
In second embodiment's turbo blower 110, the 26S Proteasome Structure and Function of the high-speed rotary body 20 and first combination bearing 26 is identical with foregoing first embodiment, so omit its detailed description at this.
Shape to hood 43 and gear casing 120 describes below.
Figure 12 is a stereogram of observing hood 43 turbo blower 110 shown in Figure 8 from the B direction.
With reference to Fig. 8 and Figure 12, hood 43 is provided with the mesopore 431 that is used to hold engine shaft 14, and has the 3rd junction plane 432, and described the 3rd junction plane 432 is combined on the motor 11 around mesopore 431.And hood 43 has towards the outstanding dimple (recess) 50 of motor 11 directions, thereby has 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 big more, and the length of running shaft 21 is just long more, so need to form the space that holds running shaft 21.In second embodiment's turbo blower 110,, the opposite side branch of the impeller in the high-speed rotary body 20 22 can be received in the dimple 50, so large high-speed solid of rotation 20 can also be set easily owing to be provided with dimple 50 at hood 43.
Figure 13 is a stereogram of observing the gear casing 110 the turbo blower 110 shown in Figure 8 from the C direction, and 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 to be incorporated into the degree of opening of that side of hood 43 greater than the shape of 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 and is used to hold the stationary axle 41 of gearwheel 15 and two mesopores of high-speed rotary body 20, and described sidewall 52 enlarges from the edge of vertical wall 51 towards hood 43.
Therefore, as shown in Figure 8, gearwheel 15 and engine shaft 41 are assembled, and gear casing 120 is fixed on the hood 43, with behind described gearwheel 15, again stationary axle 41 and high-speed rotary body 20 are installed in the gear casing 120, on solid of rotation shell 23, assemble spiral case 13 then successively.The decomposition process of described structure is opposite with foregoing assembling sequence.The present invention is owing to have the removably combining structure of gearwheel 15 and engine shaft 14 and the shape of the gear casing 120 that a side degree of opening is bigger, so the assembling of turbo blower 110 and decomposition process become simply.
The oil circulation system of the turbo blower 110 that second embodiment is related to describes below.
Figure 15 is a plan view of observing 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, and described guiding lid 30 is around the part of gearwheel 15.Guiding cover 30 and is given prominence to hood 43 from the internal surface of vertical wall 51, 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 120.30 the internal diameter diameter greater than gearwheel 15 is covered in guiding, and separated by a distance with gearwheel 15.
In Figure 15, the sense of rotation of gearwheel 15 is counterclockwise, and guiding to cover 30 be benchmark with Figure 15, have the shape that general left upper portion is cut open.The sense of rotation that 30 internal surface upper edge gearwheel 15 is covered in guiding is provided with oil guide slot 301.With engine shaft 14 direction side by side on, a plurality of described oil guide slot 301 settings separated by a distance (with reference to Figure 14).
And on the vertical wall 51 internal surface tops of gear casing 120, promptly the outside, the side of gearwheel 15 is provided with the protuberance 53 of stairstepping.Protuberance 53 constitutes the ladder that descends towards sidewall 52 directions.One end of protuberance 53 is connected with sidewall 52, and the other end is when being benchmark with Figure 15, and to cover 30 upper side ends separated by a distance with guiding on level and Vertical direction.The width of protuberance 53 equals to guide and covers 30 width.
If aforesaid gears shell 120 is incorporated on the hood 43, sidewall 52, guiding cover 30 and protuberance 53 just can be close to hood 43, and the inner space is scheduled in formation.Promptly, 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, and it is used to collect the lubricant oil that lubricant oil also circulates and collected once more.
Therefore, if gearwheel 15 rotation then is contained in the wheel tooth of lubricant oil by gearwheel 15 in the oil storage tank 32 when dispersing, the oil guide slot 301 of cover setting on 30 along guiding moves, fall on protuberance 53 with its gravity then, and be collected in the interim accumulator tank 54.And the lubricant oil of collecting in the interim accumulator tank 54 supplies to second combination bearing 42 of gearwheel 15 and 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 formation.Therefore, can avoid additionally making oil storage tank and interim accumulator tank after, and it is assembled in the trouble of gear casing inside, and with gear casing 120 and hood 43 with the tightness combinations of states, thereby oil storage tank 32 and interim accumulator tank 54 can be set easily.
Figure 16 is a plan view of observing turbo blower 100 shown in Figure 8 from the C direction, and its part with gear casing 120 outsides is illustrated in the dotted line.
With reference to Figure 15 and Figure 16, in vertical wall 51 outer installment of gear casing 120 first oil pipe 55 is arranged, described first oil pipe 55 is used to connect the stationary axle 41 of interim accumulator tank 54 and gearwheel 15.That is, be provided with first openings 56 with described interim accumulator tank 54 corresponding positions in the vertical wall 51 of gear casing 120, and an end of first oil pipe 55 is connected with first openings 56.And the other end of first oil pipe 55 is connected with oilhole 411 on being arranged at stationary axle 41.
With dashed lines shows the part of first oil pipe 55 that is connected with stationary axle 41 among Fig. 9.With reference to Fig. 9, first oil pipe 55 offers the oilhole 411 of stationary axle 41 with the lubricant oil of collecting in the interim accumulator tank 54, and the lubricant oil that supplies to oilhole 411 lubricated second combination bearing 42 when flowing through ball bearing 46 and tapered roller bearing 45 successively.Then, lubricant oil falls into oil storage tank 32 again, and collects its inside.
Figure 17 is a right elevation of observing the turbo blower 110 of Fig. 8 from the B direction, and shows the inside of the gear casing 120 after the part of cutting hood 43 open.Figure 18 is the plan view of turbo blower 110 high speed solid of rotation 20 shown in Figure 8.
With reference to Figure 17 and Figure 18, vertical wall 51 inside of gear casing 120 are provided with second oil pipe 57, and the lubricant oil that described second oil pipe 57 is used for collecting in the interim accumulator tank 54 passes to high-speed rotary body 20.For this reason, the lower end of protuberance 53 is provided with second openings 58, and an end of second oil pipe 57 is connected with second openings 58.And be provided with the 3rd openings 59 with solid of rotation shell 23 position overlapped on the vertical wall 51 of gear casing 120, and the other end of second oil pipe 57 is connected with the 3rd openings 59.
And, be provided with in the inside of solid of rotation shell 23 and be used for connecting first combination bearing 26 (with Figure 18 is punctual, is first combination bearing 26 in left side) that a pair of first combination bearing 26 is positioned at impeller 22 sides and the oil duct 60 of the 3rd openings 59.And, be useful on first combination bearing 26 (with Figure 18 is punctual, is 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 that is collected in the interim accumulator tank 54 supplies on the high-speed rotary body 20 by second oil pipe 57, and the lubricant oil of supplying with supplies to first combination bearing 26 of impeller 22 sides and first combination bearing 26 of impeller 22 opposition sides respectively by oil duct 60 and the 3rd oil pipe 61.
Lubricated described two bearings when the lubricant oil that supplies to impeller 22 sides first combination bearing 26 is flowed through sliding bearing 24 and ball bearing 25 successively.At this moment, between ball bearing 25 and the impeller 22 bearing 62 and be provided with lubrication hole 63 around 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, and it is used to connect lubrication hole 63 and gear casing 120.Therefore, employed lubricant oil flows in the gear casing 120 by the 4th oil pipe 64, and collects in the oil storage tank 32.
And the lubricant oil that supplies to by the 3rd oil pipe 61 on first combination bearing 26 of impeller 22 opposition sides supplies to sliding bearing 24 and ball bearing 25, with lubricated described two bearings.And the part of cutting open that employed lubricant oil exposes small gear 16 by being used in the middle of the solid of rotation shell 23 falls into oil storage tank 32 and collects in it.
With reference to Fig. 9, on direction, be arranged side by side bearing 65 and Sealing 66 on the outer circumferential face of engine shaft 14 away from gearwheel 15.In the rotary course of gearwheel 15, lubricant oil also disperses at a high speed to engine shaft 14, so can be enough to lubricating bearings 65 by the lubricant oil that disperses.Sealing 66 is provided with the 5th oil pipe 67, and it will be recovered in the oil storage tank 32 by the lubricant oil that bearing 65 arrives Sealing 66.
As mentioned above, even 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 second combination bearing 42 of gearwheel 15 and 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 the foregoing description, can have various embodiments and variation in not breaking away from spiritual scope of the present invention, these ought to belong in protection scope of the present invention.
Claims (30)
1. a turbo blower is characterized in that, comprising:
Motor, this motor has engine shaft;
Gear casing, this gear casing are built-in with gearwheel that is combined in described engine shaft and the small gear that meshes with described gearwheel;
High-speed rotary body, this high-speed rotary body is included in outer circumferential face and is provided with running shaft, the impeller that combines with an end of described running shaft of described small gear and is built-in with described running shaft, described small gear and at least one first combination bearing, 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 the described gear casing and with described gear casing and combines; And
Spiral case, this spiral case coat described impeller and export pressurized air.
2. turbo blower according to claim 1 is characterized in that, described first combination bearing comprises:
Built-up shaft bearing, this built-up shaft bearing possess plain bearing housing and the ball-bearing housing that one constitutes;
The sliding bearing axle, this sliding bearing axle is arranged on the outer circumferential face of described running shaft, and is built in the described plain bearing housing to constitute sliding bearing with described plain bearing housing; And
Ball bearing, this ball bearing is built in described ball-bearing housing.
3. turbo blower according to claim 2 is characterized in that,
Described first combination bearing is positioned at the both sides of described small gear, and described sliding bearing the be provided with gap of gap greater than described ball bearing be set.
4. turbo blower according to claim 3 is characterized in that,
Tilt on the surface of described sliding bearing axle and to be provided with a plurality of oil grooves and a plurality of awl groove, on described surface, to form oil film, and part relative with described gearwheel in the internal surface of described plain bearing housing is provided with the side pressure dashpot, to absorb the side pressure that described gearwheel causes.
5. turbo blower according to claim 4 is characterized in that,
The end relative with described impeller is provided with vent hole in the described solid of rotation shell of described high-speed rotary body, and described small gear forms helical gear shape, described helical gear direction is set to produce the power of drawing described running shaft towards the opposite direction of described impeller when described running shaft rotates.
6. according to any described turbo blower in the claim 1 to 5, it is characterized in that,
The internal face of described gear casing is provided with circular-arc guiding lid, and described guiding lid centers on the part of described gearwheel and has a plurality of oil guide slot, and the inside upper part of described gear casing is provided with the fuel tank that is connected with the end of described guiding lid.
7. turbo blower according to claim 6 is characterized in that,
The inside of described gear casing is provided with oil pipe, thereby supply with the lubricant oil of collecting in the described fuel tank to described first combination bearing, one end of described oil pipe is connected with oil drain out on being formed on described fuel tank, and the other end of described oil pipe is connected with oil-feed port on being formed on described first combination bearing.
8. turbo blower according to claim 7 is characterized in that,
Described solid of rotation shell is provided with the steam outlet that is used to discharge oil vapor,
Described turbo blower further comprises the oil vapor cooler that is 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 supplies in the described fuel tank.
9. turbo blower according to claim 8 is characterized in that,
Bottom at described gear casing is provided with oil storage tank, and the upper-lower position of described oil storage tank sidewall is provided with pair of holes, and described gear casing further comprises the control valve that is used to be communicated with the connecting tube of described pair of holes and is arranged at described connecting tube.
10. turbo blower according to claim 6 is characterized in that,
Described gearwheel directly combines with described engine shaft, and the side that described gear casing is relative with described motor is provided with junction plane, and described junction plane has the opening portion greater than described gearwheel diameter, and described junction plane combines with described motor.
11. according to any described turbo blower in the claim 7 to 9, it is characterized in that,
Described gearwheel directly combines with described engine shaft, the side that described gear casing is relative with described motor is provided with junction plane, described junction plane has the opening portion of diameter greater than described gearwheel diameter, and described junction plane combines with described motor.
12. a high-speed rotary body is characterized in that, comprising:
Running shaft, this running shaft outer circumferential face is provided with and the gearwheel pinion in mesh;
Impeller, this impeller combines with an end of described running shaft;
A pair of first combination bearing, this a pair of first combination bearing is arranged at the both sides of described small gear; And
Solid of rotation shell, this solid of rotation shell are built-in with described running shaft, described small gear and described a pair of first combination bearing, and the part of described solid of rotation shell is broken away, so that described small gear exposes.
13. high-speed rotary body according to claim 12 is characterized in that, described a pair of first combination bearing comprises respectively:
The built-up shaft bearing, this built-up shaft bearing possesses integrally formed plain bearing housing and ball-bearing housing;
The sliding bearing axle, this plain bearing housing is arranged on the outer circumferential face of described running shaft, and is built in the described plain bearing housing to constitute sliding bearing with described plain bearing housing; And
Ball bearing, this ball bearing is built in the described ball-bearing housing.
14. high-speed rotary body according to claim 13 is characterized in that,
Described sliding bearing the be provided with gap of gap greater than described ball bearing be set, the surperficial updip of described sliding bearing axle tiltedly is provided with a plurality of oil grooves and a plurality of awl groove, on described surface, to form oil film, and for absorbing the side pressure that described gearwheel causes, at the internal surface of described plain bearing housing, be provided with the side pressure dashpot with the opposite direction of described side pressure direction.
15. a turbo blower is characterized in that, comprising:
Motor, this motor has engine shaft;
Gearwheel, this gearwheel releasably is incorporated on the described engine shaft, and is provided with the mesopore that is used to install and fix axle at the center;
Second combination bearing, this second combination bearing is arranged between described stationary axle and the described gearwheel, and have with described engine shaft adjacent tapered roller bearing and ball bearing on the direction side by side; And
High-speed rotary body, this high-speed rotary body have the impeller that outer circumferential face is provided with the running shaft of the small gear that meshes with described gearwheel and is incorporated into an end of described running shaft.
16. turbo blower according to claim 15 is characterized in that, further comprises:
Hood, this hood combines with described motor, and is used to support described engine shaft; And
Gear casing, this gear casing are built-in with described gearwheel and described small gear, and are provided with the opening portion of diameter greater than described gearwheel diameter in the side that combines with described hood.
17. turbo blower according to claim 16 is characterized in that,
The end outer circumferential face that described engine shaft is relative with described gearwheel is provided with flange, described gearwheel is attached on the described engine shaft by a plurality of joint bolts that connect described gearwheel and described flange, and the position that described gear casing is relative with any one joint bolt in described a plurality of joint bolts is provided with opening portion.
18. turbo blower according to claim 16 is characterized in that,
Described hood has towards the outstanding dimple of described motor, and the part of described high-speed rotary body is received in the described dimple.
19., it is characterized in that described high-speed rotary body further comprises according to any described turbo blower in the claim 16 to 18:
A pair of first combination bearing, this a pair of first combination bearing is arranged at the both sides of described small gear; And
Solid of rotation shell, this solid of rotation shell are built-in with described running shaft and described a pair of first combination bearing, and are installed on the described gear casing, and part is broken away so that described small gear exposes from described gear casing inside.
20. turbo blower according to claim 19 is characterized in that, described a pair of first combination bearing comprises respectively:
Built-up shaft bearing, this built-up shaft bearing possess plain bearing housing and the ball-bearing housing that one constitutes;
The sliding bearing axle, this sliding bearing axle is arranged on the outer circumferential face of described running shaft, is built in simultaneously in the described plain bearing housing to constitute sliding bearing with described plain bearing housing; And
Ball bearing, this ball bearing is built in the described ball-bearing housing.
21. turbo blower according to claim 20 is characterized in that,
Described sliding bearing the be provided with gap of gap greater than described ball bearing be set, the surperficial updip of described sliding bearing axle tiltedly is provided with a plurality of oil grooves and a plurality of awl groove, to form oil film on described surface.
22. turbo blower according to claim 19 is characterized in that,
The internal face of described gear casing is provided with the guiding lid of circular shape and the protuberance of stairstepping, wherein, described guiding lid is around the part of described gearwheel, and described protuberance is positioned at the outside, side of described gearwheel, and described protuberance is at the interim accumulator tank of the inner formation of the assembly body of described gear casing and described hood.
23. turbo blower according to claim 22 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.
24. turbo blower according to claim 22 is characterized in that,
The position that described gear casing is provided with described interim accumulator tank is provided with first openings, and further comprises first oil pipe, and described first oil pipe is used to connect described first openings and described stationary axle in the outside of described gear casing.
25. turbo blower according to claim 24 is characterized in that,
Described stationary axle is incorporated into described gear casing, and described stationary axle is provided with oilhole in inside, is provided with runner between described stationary axle and the described engine shaft, and the lubricant oil that is used for supplying to described oilhole is directed to described second combination bearing.
26. turbo blower according to claim 22 is characterized in that,
The lower end of described protuberance is provided with second openings, the part of joining with described solid of rotation shell in the described gear casing is provided with the 3rd openings, and the inside of described gear casing further comprises second oil pipe that described first openings is connected with described the 3rd openings.
27. turbo blower according to claim 26 is characterized in that,
Described solid of rotation shell is provided with oil duct in inside, be used for connecting first combination bearing and described the 3rd openings of the described impeller side of described a pair of first combination bearing, and further comprise the 3rd oil pipe in the outside of solid of rotation shell, be used for connecting described a pair of first combination bearing and first combination bearing described impeller opposition side and described oil duct.
28. turbo blower according to claim 27 is characterized in that,
Described high-speed rotary body further comprises at first combination bearing of described impeller side and the bearing between the described impeller, and described bearing and described solid of rotation shell are provided with oil drain out, described solid of rotation shell externally further comprises the 4th oil pipe, be used to connect described oil drain out and described gear casing, thereby reclaim lubricant oil.
29. turbo blower according to claim 25 is characterized in that, further comprises:
The direction away from described gearwheel is arranged side by side in the outer circumferential face upper edge of described engine shaft for bearing and Sealing, this bearing and Sealing; And
The 5th oil pipe, the 5th oil pipe is used to connect the inside of described Sealing and described hood, to reclaim the lubricant oil that arrives described Sealing.
30. a turbo blower is characterized in that, comprising:
Motor, this motor has engine shaft, and fits together with hood;
Gearwheel, this gearwheel releasably is incorporated on the described engine shaft, and is provided with the mesopore that is used to be provided with stationary axle at the center;
High-speed rotary body, this high-speed rotary body is included in outer circumferential face and is provided with running shaft, the impeller that combines with described running shaft one end of the small gear of described gearwheel engagement, is used to support at least one first combination bearing of described running shaft and is built-in with described running shaft and described first combination bearing, and a part of being broken away so that the solid of rotation shell that described small gear exposes;
Second combination bearing, this second combination bearing is arranged between described stationary axle and the described gearwheel, and have with described engine shaft direction side by side on adjacent tapered roller bearing and ball bearing;
Gear casing, this gear casing are built-in with described gearwheel and described small gear, and are provided with the opening portion of diameter greater than the diameter of described gearwheel in the side that combines with described hood; And
Spiral case, this spiral case coat described impeller and export pressurized air.
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 true CN102057164A (en) | 2011-05-11 |
| CN102057164B CN102057164B (en) | 2014-01-01 |
Family
ID=41417225
Family Applications (1)
| 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 |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20120107099A1 (en) |
| EP (1) | EP2314879A2 (en) |
| JP (1) | JP5356513B2 (en) |
| CN (1) | CN102057164B (en) |
| WO (1) | WO2009151245A2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116255359A (en) * | 2023-01-17 | 2023-06-13 | 江苏精亚风机有限公司 | Centrifugal fan capable of adjusting lubrication speed according to operation conditions |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2218998B1 (en) * | 2009-02-03 | 2012-12-19 | Ipsen, Inc. | A sealing mechanism for a vacuum heat treating furnace |
| FR2968062B1 (en) * | 2010-11-26 | 2012-11-16 | Snecma | OIL DRAINING DEVICE AND TURBOMACHINE COMPRISING SUCH A DEVICE |
| EP2990661B1 (en) * | 2013-09-06 | 2018-11-07 | Mitsubishi Heavy Industries Compressor Corporation | Rotary machine |
| US20150369337A1 (en) * | 2014-06-23 | 2015-12-24 | Samsung Techwin Co., Ltd. | High-speed rotating machine |
| CN104613091B (en) * | 2015-01-28 | 2018-03-27 | 沈阳世润重工有限公司 | A kind of babbit Sliding bush lubrication system applied to booster engine |
| WO2016210119A1 (en) * | 2015-06-23 | 2016-12-29 | Howden Roots Llc | Gear drive system and implementation thereof |
| CA3148346A1 (en) * | 2019-09-10 | 2021-03-18 | David Charles Hokey | Air compressor and blower |
| CN113124000B (en) * | 2021-04-25 | 2022-12-30 | 浙江上风高科专风实业股份有限公司 | Magnetic suspension blower impeller assembling method |
| CN113028041B (en) * | 2021-04-29 | 2022-08-09 | 中国航发湖南动力机械研究所 | Speed reducer wind shield structure for preventing oil mixing of gear |
Citations (6)
| 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 |
| US20050092307A1 (en) * | 2003-10-31 | 2005-05-05 | Middlebrook James K. | 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 |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1720988A (en) * | 1925-06-05 | 1929-07-16 | Automotive Patent Holding Comp | Transmission gearing |
| US2223715A (en) * | 1937-03-11 | 1940-12-03 | Daimler Benz Ag | Hydraulic transmission control |
| GB767426A (en) * | 1953-11-09 | 1957-02-06 | Napier & Son Ltd | Transmission mechanism including bevel pinions |
| US2973894A (en) * | 1957-06-17 | 1961-03-07 | Turbo Res Corp | Centrifugal compressor for starting jet engines |
| US2987904A (en) * | 1958-05-28 | 1961-06-13 | Gen Motors Corp | Domestic appliance |
| US3424372A (en) * | 1966-11-30 | 1969-01-28 | Chicago Pneumatic Tool Co | Centrifugal gaseous medium compressor |
| JPS5514347A (en) * | 1978-07-17 | 1980-01-31 | Hitachi Ltd | Variable speed change device |
| JP2555374Y2 (en) * | 1992-02-04 | 1997-11-19 | 群馬日本電気株式会社 | Composite bearing |
| US5425345A (en) * | 1994-10-31 | 1995-06-20 | Chrysler Corporation | Mechanically driven centrifugal air compressor with hydrodynamic thrust load transfer |
| US5685699A (en) * | 1996-06-20 | 1997-11-11 | Carrier Corporation | Compressor transmission vent system |
| JPH11159697A (en) * | 1997-09-29 | 1999-06-15 | Nippon Seiko Kk | Oil-air lubricating device |
| DE10124560B4 (en) * | 2000-05-27 | 2017-01-05 | Brandenburgische Forschungs- Und Entwicklungsgesellschaft Cottbus Mbh | Rotary engine |
| JP3799979B2 (en) * | 2000-09-14 | 2006-07-19 | 日産自動車株式会社 | Infinite gear ratio continuously variable transmission |
| US6524081B2 (en) * | 2001-06-01 | 2003-02-25 | Chiang Fu. Wu | One-stage transmissible turbocharger |
| US20030156769A1 (en) * | 2002-02-19 | 2003-08-21 | Whang Cheol H. | Fluid suspended bearing |
-
2009
- 2009-06-08 US US12/996,810 patent/US20120107099A1/en not_active Abandoned
- 2009-06-08 EP EP09762632A patent/EP2314879A2/en not_active Withdrawn
- 2009-06-08 CN CN200980121594.9A patent/CN102057164B/en not_active Expired - Fee Related
- 2009-06-08 WO PCT/KR2009/003059 patent/WO2009151245A2/en active Application Filing
- 2009-06-08 JP JP2011513414A patent/JP5356513B2/en not_active Expired - Fee Related
Patent Citations (6)
| 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 |
| US20050092307A1 (en) * | 2003-10-31 | 2005-05-05 | Middlebrook James K. | 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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116255359A (en) * | 2023-01-17 | 2023-06-13 | 江苏精亚风机有限公司 | Centrifugal fan capable of adjusting lubrication speed according to operation conditions |
| CN116255359B (en) * | 2023-01-17 | 2024-04-16 | 江苏精亚风机有限公司 | Centrifugal fan capable of adjusting lubrication speed according to operation conditions |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009151245A2 (en) | 2009-12-17 |
| CN102057164B (en) | 2014-01-01 |
| JP5356513B2 (en) | 2013-12-04 |
| JP2011522994A (en) | 2011-08-04 |
| US20120107099A1 (en) | 2012-05-03 |
| WO2009151245A3 (en) | 2010-03-11 |
| EP2314879A2 (en) | 2011-04-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102057164B (en) | Turbo blower and high speed rotating body used in same | |
| US7063734B2 (en) | Air/oil separation system and method | |
| RU2443881C2 (en) | Gas turbine engine with stator mounted on gearbox of assembly units | |
| CA2809985C (en) | Deoiler seal | |
| JPS6085B2 (en) | Separation device | |
| CN106574619B (en) | Convolute-hydrodynamic mechanics and its maintaining method | |
| EP1256720B1 (en) | Rotary vacuum pump | |
| EP0073281B1 (en) | Bearing | |
| KR100895667B1 (en) | Turbo blower and high speed rotation body using for thereof | |
| CN217108167U (en) | Oil sealing structure of gear box | |
| US4936757A (en) | Multi-section vacuum pump | |
| CN207470441U (en) | Oil separator and horizontal compressor | |
| US6129531A (en) | Open drive scroll machine | |
| CN205101238U (en) | Compressor | |
| JP5478153B2 (en) | Screw compressor | |
| KR101095614B1 (en) | Turbo blower | |
| JP3964075B2 (en) | Roots intake and compressor | |
| CN115076107B (en) | Cantilever vertical screw vacuum pump | |
| CN218268474U (en) | Bearing lubricating device of screw blower | |
| CN213628809U (en) | Independent lubricating structure of derailleur bearing | |
| CN210660709U (en) | Fresh water pump for engine | |
| CN109944798B (en) | Six-blade Roots supercharger | |
| CN114542466A (en) | Full-automatic diesel power air compressor machine | |
| CN115451312A (en) | Self-lubricating screw air blower | |
| JP2006002596A (en) | Bearing device and pump device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140101 Termination date: 20150608 |
|
| EXPY | Termination of patent right or utility model |