CN104343698B - Multistage centrifugal compressor - Google Patents
Multistage centrifugal compressor Download PDFInfo
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- CN104343698B CN104343698B CN201410351897.2A CN201410351897A CN104343698B CN 104343698 B CN104343698 B CN 104343698B CN 201410351897 A CN201410351897 A CN 201410351897A CN 104343698 B CN104343698 B CN 104343698B
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- centrifugal impeller
- mentioned
- load
- fluid
- output shaft
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
- F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
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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
-
- 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
- F04D29/051—Axial thrust balancing
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
- F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
Abstract
The present invention provides a multistage centrifugal compressor of reducing the thrust generated in the output shaft of the load, being high efficiency and being high mechanical reliability. The multistage centrifugal compressor comprises: an input shaft driven by an engine (4); a main gear (20) provided on the input shaft (4); a pinion (21) engaged with the main gear wheel; an output shaft (5) for setting the pinion (21); a centrifugal impeller (11) at one end of the first stage of the output shaft; and a secondary centrifugal impeller (11) located at the other end (5) of the output shaft and located over the first stage centrifugal impeller (11 ) section 2 of the centrifugal impeller by fluid flow downstream side of the stage (12). In addition, the outer diameter (D1) of the first-stage centrifugal impeller (11) is larger than that of the second-stage centrifugal impeller (12).
Description
Technical field
The present invention relates to multistage centrifugal compressor, more particularly to possess by engine driving and the input of master gear is set
Axle and the centrifugal compressor that the multi-stage type of more than one output shaft of mill pinlon being engaged with master gear is set.
Background technology
As the background technology of the art, there is Japanese Unexamined Patent Publication 2008-231933 publication (patent document 1).At this
In publication, disclose following gear drive turbine compressor, i.e. this gear drive turbine compressor possesses: " by external drive
Device (engine) drives the gear wheel (master gear) 12 of rotation；Engage with gear wheel, the little gear (mill pinlon) 14 of high-speed rotation；
It is fixed on pinion shaft (output shaft) 13, the impeller 16 of high-speed rotation centered on its axle center；It is fixed on pinion shaft
On, it is capable of the side of slidably supporting gearwheel, transmit the thrust ring 18 of the thrust of pinion shaft to gear wheel；Supporting role in
The thrust bearing 20 of the thrust of Large Gear Shaft (input shaft)；And exceed regulation in the pinion shaft 13 being supported by thrust bearing 20
Threshold value and axle mobile when, limit the thrust direction amount of movement limiter 30 of this axle movement " (reference specification digest).
Additionally, recording in above-mentioned publication " because possessing the little tooth supporting in the thrust bearing 20 by Large Gear Shaft 11
Wheel shaft 13 exceedes threshold value a of regulation and when axle is mobile, limit the thrust direction amount of movement limiter 30 of this axle movement, so just
During normal operating, due to the thrust bearing 20 of Large Gear Shaft 11, the axle movement of pinion shaft 13 is below threshold value a of regulation, pushes away
Force direction amount of movement limiter 30 does not play a role, only in the case of the excessive shifting axle producing threshold value a exceeding regulation
Just play a role and limit this axle and move.Thus, in the case of Large Gear Shaft 11 being created to excessive axle movement, can
Impeller 16 is avoided to contact with the excessive of housing in itself." (with reference to 0031,0032 section).
Patent document 1: Japanese Unexamined Patent Publication 2008-231933 publication
But, patent document 1 record multistage centrifugal compressor be conceived to limit as output shaft pinion shaft to
The amount of movement of thrust direction (axial), does not consider to reduce the thrust load (load of thrust direction) resulting from output shaft.
Therefore, the multistage centrifugal compressor that patent document 1 is recorded is possible to the thrust load because resulting from output shaft, leads to
The reduction of the efficiency of the compressor of the friction loss based on sliding part, the reduction of the Mechanical Reliability of compressor.
Content of the invention
The present invention is to propose in view of the above circumstances, it is intended that providing a kind of reduction to result from output shaft
The high multistage centrifugal compressor of thrust load, high efficiency and Mechanical Reliability.
In order to realize above-mentioned purpose, the multistage centrifugal compressor of the present invention possesses: input shaft driven by the engine；If
Master gear in above-mentioned input shaft；The mill pinlon engaging with above-mentioned master gear；For arranging the output shaft of above-mentioned mill pinlon；Located at above-mentioned
1st centrifugal impeller of one end of output shaft；And the other end located at above-mentioned output shaft, lean on positioned at than above-mentioned 1st centrifugal impeller
2nd centrifugal impeller of the downstream stage side of the flowing of fluid, the external diameter of above-mentioned 1st centrifugal impeller is set than the above-mentioned 2nd centrifugation
The external diameter of impeller is big.
The effect of invention
According to the present invention, reduction is provided to result from the thrust load of output shaft, high efficiency and high multistage of Mechanical Reliability
Centrifugal compressor.
Brief description
Fig. 1 is the horizontal cross of the schematic configuration of multistage centrifugal compressor of the 1st embodiment representing the present invention.
Fig. 2 is the schematic diagram of the fluid-load of centrifugal impeller acting on the 1st grade for explanation along thrust direction.
Fig. 3 is to result from the thrust of output shaft for explanation due to the 1st grade of centrifugal impeller and the 2nd grade of centrifugal impeller
The schematic diagram of the fluid-load in direction.
Fig. 4 is the signal of the gear load being acted on along thrust direction due to the engagement of master gear and mill pinlon for explanation
Figure.
Fig. 5 is the horizontal cross of the multistage centrifugal compressor schematically showing the 1st embodiment.
Fig. 6 is the ratio and the 1st of the external diameter of centrifugal impeller with respect to the 1st grade for the external diameter of the centrifugal impeller representing the 2nd grade
The figure of the relation of the stress resulting from root of blade of the export department of centrifugal impeller of level.
Fig. 7 is the horizontal cross of the multistage centrifugal compressor schematically showing the 2nd embodiment.
Fig. 8 is the horizontal cross of the multistage centrifugal compressor schematically showing the 3rd embodiment.
Fig. 9 is the horizontal cross of the multistage centrifugal compressor schematically showing the 4th embodiment.
Figure 10 is the horizontal cross of the multistage centrifugal compressor schematically showing the 5th embodiment.
Figure 11 is the horizontal cross of the multistage centrifugal compressor schematically showing the 6th embodiment.
The explanation of reference
4 input shafts；5 output shafts；6 output shafts (the 2nd output shaft)；11 the 1st grades of centrifugal impeller；12 the 2nd grades of centrifugation leaf
Wheel；The centrifugal impeller of 13 3rd levels；14 the 4th grades of centrifugal impeller；20 master gears；21 mill pinlons；22 mill pinlons (the 2nd mill pinlon)；60、61
Composite bearing；66～69 thrust rings；D1～d4 external diameter；Fi1, fi2 fluid-load；Fp1, fp2 gear load.
Specific embodiment
For embodiments of the present invention, suitably referring to the drawings while explaining.
In addition, in drawings identified below, for identical component or suitable component, marking identical accompanying drawing mark
Note, suitably the repetitive description thereof will be omitted.Additionally, for convenience of description, the size and dimension of component sometimes deforms or exaggerates signal
Property ground represent.
[the 1st embodiment]
First, with reference to Fig. 1～Fig. 6 while the 1st embodiment of the present invention is described.
Fig. 1 is the horizontal cross of the schematic configuration of multistage centrifugal compressor of the 1st embodiment representing the present invention.
Multistage centrifugal compressor shown in Fig. 1 has: engine (not shown)；Booster engine portion 100, transmits this engine
Rotary driving force；The compressor section 1～3 of the 1st grade～3rd level, periodically compression fluid (gas)；Cooling device (is not schemed
Show), the fluid (gas) of high temperature is compressed and is become in cooling；And control unit (not shown), carry out unified control.
In the rotary shaft (not shown) of engine, via the shaft coupling input shaft connecting booster engine portion 100 (not shown)
4.Master gear 20 as gear wheel is provided with input shaft 4.On master gear 20, it is engaged with 2 sheding baby teeth as little gear
Wheel 21 and mill pinlon 22 (the 2nd mill pinlon).Here, from the viewpoint of reducing vibration and noise, master gear 20 and mill pinlon 21,22 make
With the contact-ratio helical gear bigger than spur gear.
Mill pinlon 21 and output shaft 5 form, and mill pinlon 22 and output shaft 6 (the 2nd output shaft) form.Input shaft
4 and 2 output shafts 5,6 configure respectively parallel to each other.Alternatively, it is also possible to each mill pinlon 21,22 is fabricated to and 5,6 points of output shaft
Body, they are separately fixed on output shaft 5,6.On 2 output shafts 5,6, hot jacket and be fixed with pushing away of substantially cylindrical shape
Power ring 66～69.
4,2 output shafts of input shaft 5,6, master gear 20, mill pinlon 21,22 and thrust ring 66～69 are booster engine portions 100
Composed component, is housed in housing 101.Housing 101 is horizontal plane segmentation construction, by with include input shaft 4 and output shaft 5,6
Central axis the roughly equal face of horizontal plane, be divided into upper shell and lower house.Upper shell and lower house bolt (are not schemed
Show) it is incorporated into together.
Input shaft 4 and master gear 20, using the composite bearing 60,61 being kept by housing 101, can rotatably be supported by.Multiple
Sympodium holds 60,61 load (the thrust loads being affected by the radially load (radial load) of (radial direction) and thrust direction (axial)
Lotus) and the bearing that supported.
On the other hand, it is respectively equipped with 2 output shafts 5,6 of mill pinlon 21,22, using the journal bearing being kept by housing 101
62～65, can rotatably be supported by.In addition, the thrust load producing in output shaft 5,6, born and propped up by thrust ring 66～69
Hold, this thrust ring 66～69 is configured to, clip master gear 20 across gap 71,72 (with reference to Fig. 5).
In order to composite bearing 60,61, journal bearing 62～65, thrust ring 66～69, master gear 20 and mill pinlon 21,22 etc.
It is lubricated, from lubricating oil system supply (not shown) lubricating oil.In order to composite bearing 60,61, journal bearing 62～65, push away
The lubricating oil that power ring 66～69, master gear 20 and mill pinlon 21,22 etc. are lubricated and use, is returned under engine
The fuel tank (not shown) in portion.
The gap 70 (with reference to Fig. 5) of the sliding surface of thrust direction of input shaft 4 and master gear 20 and composite bearing 60,61,
E.g. 0.2mm about.During the steady running of multistage centrifugal compressor, in composite bearing 60 and composite bearing 61 either one with
The sliding surface contact of master gear 20, the composite bearing of the opposing party keeps gap with the sliding surface of master gear 20.But, multistage from
The starting of heart compressor, when stopping, multistage centrifugal compressor exceed the operating compass of the small flow area being referred to as surge
In the case of ground operating, different according to operating condition at that time from the composite bearing of master gear 20 contact slide.
Output shaft 5,6 and mill pinlon 21,22 are radially supported by journal bearing 62～65.On the other hand, output shaft 5,6 and sheding baby teeth
The supporting of thrust direction of wheel 21,22 is carried out by thrust ring 66～69, and this thrust ring 66～69 is configured to, across gap 71,
Clip master gear 20 72 (with reference to Fig. 5).
Thrust ring 66 and 67 becomes following construction, i.e. to clip the side of master gear 20 across gap 71 (with reference to Fig. 5)
Formula, and is contacted with master gear 20 in the sliding surface positioned at respective axially inner side by hot jacket on output shaft 5.The cunning of thrust ring 66
Distance between the surface between the sliding surface of dynamic face and thrust ring 67, than the distance between the surface between two sliding surfaces of master gear 20 greatly for example
0.2mm about.That is, the gap 71 (with reference to Fig. 5) of the sliding surface of thrust direction of master gear 20 and thrust ring 66,67, e.g.
0.2mm about.During the steady running of multistage centrifugal compressor, either one in thrust ring 66 and thrust ring 67 is with master gear 20
Sliding surface contacts, and the sliding surface of the thrust ring of the opposing party keeps gap with the sliding surface of master gear 20.Additionally, thrust ring 66,67
With housing 101 keep 2～3mm about gap, will not contact.In addition, with regard to be fixed on output shaft 6 thrust ring 68,
69, due to being and the thrust ring 66 being fixed on output shaft 5,67 identical constructions, so omitting the description.
As described above, the multistage centrifugal compressor of present embodiment possesses: input shaft 4 driven by the engine；Located at defeated
Enter the master gear 20 of axle 4；The mill pinlon 21,22 engaging with master gear 20；And it is respectively provided with the output shaft 5,6 of mill pinlon 21,22.And
And, in one end of output shaft 5, it is provided with the 1st grade of centrifugal impeller (the 1st centrifugal impeller) 11, in the other end of output shaft 5, is provided with
Centrifugal impeller (the 2nd centrifugal impeller) positioned at the 2nd grade by the downstream stage side of flowing of fluid of the centrifugal impeller 11 than the 1st grade
12.Additionally, in one end of output shaft 6, being provided with the centrifugal impeller 13 of the 3rd level of most downstream level side of flowing positioned at fluid.
Fig. 2 is showing of fluid-load (fluid force) for the centrifugal impeller 11 acting on the 1st grade along thrust direction is described
It is intended to.
As shown in Fig. 2 possess the 1st grade of centrifugal impeller 11 on the top of output shaft 5.Protective cover housing 111 covers centrifugation
The outside of impeller 11, housing 101 covers the back side 16 of centrifugal impeller 11.Additionally, between housing 101 and output shaft 5, being provided with
Prevent compression fluid from leaking into the gland seal device 15 outside compressor.
Pressure due to the fluid in compressor boosts because of centrifugal impeller 11, so the upstream side phase with centrifugal impeller 11
The pressure in downstream is high for ratio.Additionally, acting on the pressure p 1 of the fluid at the back side 16 of centrifugal impeller 11, with centrifugal impeller 11
The pressure in downstream is roughly the same.Therefore, the pressure p 1 acting on the compression fluid at the back side 16 of centrifugal impeller 11 becomes leading
Property will thus produce the fluid-load acting on centrifugal impeller 11 along thrust direction.Thus, possess in centrifugal impeller 11
On output shaft 5, along the flow direction a rightabout with the fluid of the upstream side of centrifugal impeller 11, produce and carried by centrifugal impeller 11
The fluid-load fi of the thrust direction come.Reference b in Fig. 2, represents the flowing of the fluid in downstream of centrifugal impeller 11
Direction.In addition, with regard to the respective stream acting on the 2nd grade of centrifugal impeller 12 and the centrifugal impeller 13 of 3rd level along thrust direction
Body load, due to being produced based on the principle same with the 1st grade of centrifugal impeller 11, so omit the description.
Fig. 3 is to result from output shaft 5 for explanation due to the 1st grade of centrifugal impeller 11 and the 2nd grade of centrifugal impeller 12
The fluid-load of thrust direction schematic diagram.In addition, in figure 3, omitting the diagram of mill pinlon 21 grade.
As shown in figure 3, possess the 1st grade of centrifugal impeller 11 in one end of output shaft 5, possess in the other end of output shaft 5
2nd grade of centrifugal impeller 12.In this case, the pressure p 1 of compression fluid acts on the back side 16 of centrifugal impeller 11, compression stream
The pressure p 2 of body acts on the back side 17 of centrifugal impeller 12.Here, the back side with the centrifugal impeller 11 acting on upstream stage side
The pressure p 1 of 16 compression fluid is compared, and acts on the pressure p 2 of the compression fluid at the back side 17 of the centrifugal impeller 12 of downstream stage side
High.This is because, the fluid that be have compressed by the centrifugal impeller 11 of upstream stage side, risen further by the centrifugal impeller 12 of downstream stage side
Pressure.However, it is also possible to be configured to, the fluid that be have compressed by the centrifugal impeller 11 of upstream stage side, by (not shown) other from
Lobus cardiacus wheel boosts, and is boosted by the centrifugal impeller 12 of downstream stage side further.Thus, result from the thrust direction of output shaft 5 entirety
Fluid-load fi1, along from upstream stage side centrifugal impeller 11 downstream the centrifugal impeller 12 of level side direction produce.
Fig. 4 is the gear load (tooth being acted on along thrust direction due to the engagement of master gear 20 and mill pinlon 21 for explanation
Wheel power) schematic diagram.
Fig. 4 be the master gear 20 located at input shaft 4 viewed from above and located at output shaft 5 mill pinlon 21 thick by figure
The figure of the state of part 40 engagement that line represents.Here, master gear 20 is as shown by the arrow, contrary from engine
Side is observed, and is rotated clockwise.Additionally, as shown in figure 4, according to the reasons why aftermentioned, master gear 20 is to become pivot
Axis towards above-below direction from side observation in the case of, teeth directional upper left tilt left-handed helical gear, mill pinlon 21 is to make
Become the axis of pivot towards above-below direction in the case of the observation of side, the helical gear of the dextrorotation that teeth directional upper right tilts.
Thus, mill pinlon 21 is subject to the gear load fp1 of the thrust direction from master gear 20 right direction.As its reaction, master gear
The 20 gear load fb being subject to the thrust direction from mill pinlon 21 left direction.In addition, with regard to due to master gear 20 and mill pinlon 22
Engagement and along thrust direction effect gear load, due to based on because of the gear engaging and producing of master gear 20 and mill pinlon 21
Load identical principle and produce, so omitting the description.
Fig. 5 is the horizontal cross of the multistage centrifugal compressor schematically showing the 1st embodiment.
In Figure 5, illustrate only the housing 101 in booster engine portion 100, input shaft 4, master gear 20, composite bearing 60,61,
Output shaft 5,6, mill pinlon 21,22, thrust ring 66～69 and centrifugal impeller 11～13, for convenience of description, journal bearing 62～
65th, gland seal device 15 etc. omits diagram.Additionally, composite bearing 60,61 only illustrates the part of the load bearing thrust direction, bear
The part of the load of radial direction omits diagram.
In the present embodiment, the two ends of the output shaft 5 of the side in 2 output shafts 5,6, possess respectively the 1st grade and
2nd grade of centrifugal impeller 11,12.And, output shaft 5, mill pinlon 21, thrust ring 66,67 and centrifugal impeller 11,12 form low-pressure stage
Mill pinlon axle 80.In one end of the output shaft 6 of the opposing party, possesses the centrifugal impeller 13 of 3rd level.And, output shaft 6, mill pinlon 22, push away
Power ring 68,69 and centrifugal impeller 13 form hiigh pressure stage mill pinlon axle 81.In addition, in Figure 5, for multi-stage centrifugal compression easy to understand
The gap 70 of the thrust direction between the operating state of machine, input shaft 4 and master gear 20 and composite bearing 60,61, master gear 20
Thrust direction between the gap 71 of the thrust direction and thrust ring 66,67 between and master gear 20 and thrust ring 68,69
Gap 72 exaggeration expand ground represent.
The fluid-load fi2 ratio resulting from the thrust direction of hiigh pressure stage mill pinlon axle 81 results from pushing away of low-pressure stage mill pinlon axle 80
The fluid-load fi1 of force direction is big.This is because, result from low-pressure stage mill pinlon axle 80 thrust direction fluid-load fi1,
The pressure p 1 (with reference to Fig. 3) acting on the back side 16 of the 1st grade of centrifugal impeller 11 and the back of the body of the centrifugal impeller 12 acting on the 2nd grade
The direction of the pressure p 2 (with reference to Fig. 3) in face 17 is rightabout, mutually offsets.Also as acting on the centrifugal impeller 13 of 3rd level
The back side pressure ratio act on the 1st grade and the 2nd grade the pressure p 1 at the back side 16,17 of centrifugal impeller 11,12, p2 high.Therefore,
Set the master gear 20 of multistage centrifugal compressor and the helical gear rotation direction of mill pinlon 21,22, consideration is to reduce to result from first
The thrust load of hiigh pressure stage mill pinlon axle 81.
In the present embodiment, the fluid-load fi2 of thrust direction resulting from hiigh pressure stage mill pinlon axle 81 is along from engine
The direction of lateral engine opposition side produces.Thus, in order to offset this fluid-load fi2, with gear load fp2 along from engine
The mode that the direction of lateral engine side produces on the contrary, determines the helical gear rotation direction of master gear 20 and mill pinlon 22.In this enforcement
In mode, input shaft 4 and master gear 20 are observed from engine opposition side, are rotated clockwise.Therefore, master gear 20 must be left
The helical gear of rotation, the mill pinlon 22 of hiigh pressure stage mill pinlon axle 81 must be the helical gear of dextrorotation.On the other hand, low-pressure stage mill pinlon axle 80
Mill pinlon 21 is the helical gear of unique dextrorotation, and gear load fp1 produces along from the direction of engine lateral engine side on the contrary.This
Outward, result from the direction of the fluid-load fi1 of the thrust direction of low-pressure stage mill pinlon axle 80, be described above as from engine opposition side
Direction (with reference to Fig. 3) to engine side.
Result from the thrust load of low-pressure stage mill pinlon axle 80, be that the mill pinlon 21 of low-pressure stage mill pinlon axle 80 bears from master gear 20
The gear load fp1 of thrust direction and act on low-pressure stage mill pinlon axle 80 the fluid-load fi1 of thrust direction make a concerted effort.Cause
And, the thrust load acting on low-pressure stage mill pinlon axle 80 is direction from engine lateral engine side on the contrary, by thrust ring 66
Supporting.
On the other hand, result from the thrust load of hiigh pressure stage mill pinlon axle 81, be the mill pinlon 22 of hiigh pressure stage mill pinlon axle 81 from master
The gear load fp2 of the thrust direction that gear 20 bears and act on hiigh pressure stage mill pinlon axle 81 thrust direction fluid-load
Fi2 makes a concerted effort.Because usual fluid-load fi2 is more much bigger than gear load fp2, so acting on pushing away of hiigh pressure stage mill pinlon axle 81
Power load is the direction from engine side to engine opposition side, is supported by thrust ring 69.
Act on the thrust load of master gear 20, be the thrust load born from the thrust ring 66 of low-pressure stage mill pinlon axle 80 and
Resultant load f of the thrust load born from the thrust ring 69 of hiigh pressure stage mill pinlon axle 81.Here, act on hiigh pressure stage mill pinlon axle
The thrust load that 81 thrust load is compared to for low-pressure stage mill pinlon axle 80 is big.Thus, sheded baby teeth by low-pressure stage mill pinlon axle 80, hiigh pressure stage
The gear train that wheel shaft 81 and master gear 20 are constituted is overall, along from engine side to bearing thrust load in the direction of engine opposition side
(resultant load f).
So, the gear train of the multistage centrifugal compressor of present embodiment is overall, and the thrust bearing the left direction to Fig. 5 carries
Lotus.As a result, becoming operating state as shown in Figure 5.That is, the composite bearing 61 support teeth train by engine opposition side is whole
The thrust load of body.And, act on the thrust load of low-pressure stage mill pinlon axle 80, by pushing away of the 1st grade of centrifugal impeller 11 side
Power ring 66 contacts with master gear 20, slides and is supported by.Additionally, acting on the thrust load of hiigh pressure stage mill pinlon axle 81, by with
The thrust ring 69 of centrifugal impeller 13 opposition side of 3rd level contacts with master gear 20, slides and is supported by.
Here, if the fluid-load fi1 of the thrust direction resulting from low-pressure stage mill pinlon axle 80, low-pressure stage can be reduced
The thrust ring 66 of mill pinlon axle 80 is low with the contact surface pressure drop of the contact of master gear 20, sliding surface, and friction loss reduces, multistage centrifugal
The overall efficiency of compressor improves.
In the present embodiment, in order that the fluid-load fi1 resulting from the thrust direction of low-pressure stage mill pinlon axle 80 reduces,
The outside diameter d 1 (also referring to Fig. 2 and Fig. 3) of the 1st grade of centrifugal impeller 11 is set the outside diameter d 2 of the centrifugal impeller 12 than the 2nd grade
(also referring to Fig. 3) is big.And, the external diameter of the centrifugal impeller 11 with respect to the 1st grade for the outside diameter d 2 of preferably the 2nd grade of centrifugal impeller 12
The ratio of d1, that is, external diameter ratio (d2/d1) be set to more than 0.8 and less than 1.0.
Then, the action effect of multistage centrifugal compressor being configured as described above is described.
Present embodiment makes the outside diameter d 2 of the centrifugal impeller 12 of 1 to the 2 grade of outside diameter d of the 1st grade of centrifugal impeller 11 big.Cause
And, the compression area acting on the pressure p 1 of the fluid at the back side 16 of the 1st grade of centrifugal impeller 11 becomes big, thus, along from starting
The fluid-load that pusher side acts on the 1st grade of centrifugal impeller 11 to the thrust direction of engine opposition side becomes big.If additionally, increasing
The outside diameter d 1 of the 1st grade of centrifugal impeller 11, then the pressure rising in the 1st grade of compressor section 1 becomes big, therefore, it is possible to reduce
The pressure of the 2nd grade of compressor section 2 rises.That is, the outside diameter d 2 of the 2nd grade of centrifugal impeller 12 can be reduced.As a result, acting on
The compression area of the pressure p 2 at the back side 17 of the 2nd grade of centrifugal impeller 12 diminishes, thus, along from engine lateral engine on the contrary
The fluid-load that the thrust direction of side acts on the 2nd grade of centrifugal impeller 12 diminishes.
Thus, low-pressure stage mill pinlon axle 80 is acted on due to the centrifugal impeller 12 of the 1st grade of centrifugal impeller 11 and the 2nd grade
Relatively diminish from the fluid-load of the engine thrust direction of lateral engine side on the contrary.That is, result from the thrust of output shaft 5
Load is lowered.
Thus, thrust ring 66 diminishes with the contact of master gear 20, the friction loss of sliding part, the effect of multistage centrifugal compressor
Rate improves.Additionally, the Mechanical Reliability of the thrust ring 66 on output shaft 5 improves by hot jacket, and due to thrust ring 66 and master
The abrasion amount of the sliding surface of gear 20 is lowered, so the overall Mechanical Reliability of compressor also improves.
That is, according to present embodiment, using the teaching of the invention it is possible to provide reduce and result from the thrust load of output shaft 5, high efficiency and machinery can
By the high multistage centrifugal compressor of property.
Additionally, in the present embodiment, the outside diameter d 2 of the 2nd grade of centrifugal impeller 12 centrifugal impeller 11 with respect to the 1st grade
Outside diameter d 1 ratio, be preferably set to more than 0.8 and less than 1.0.
Fig. 6 is the ratio of the outside diameter d 1 of centrifugal impeller 11 with respect to the 1st grade for the outside diameter d 2 of the centrifugal impeller 12 representing the 2nd grade
Rate, i.e. external diameter ratio (d2/d1) and stress produced by the root of blade c (with reference to Fig. 2) of the 1st grade of the export department of centrifugal impeller 11
The figure of the relation of σ.Here, result from the stress of centrifugal impeller 11 due to centrifugal force, become maximum in root of blade c.
From reduce act on low-pressure stage mill pinlon axle 80 thrust direction the such viewpoint of fluid-load, preferably the 1st grade
Centrifugal impeller 11 outside diameter d 1 as big as possible, additionally, the outside diameter d 2 of the 2nd grade of centrifugal impeller 12 is as little as possible.That is, from reduction
Act on output shaft 5 thrust load such from the viewpoint of, preferably external diameter ratio (d2/d1) is as little as possible.But, as Fig. 6 institute
Show, diminish with external diameter ratio (d2/d1), be centrifuged produced by the root of blade c of the export department based on the 1st grade of centrifugal impeller 11
The stress σ of power becomes big, if external diameter ratio (d2/d1) is less than 0.8, exceedes the feasible value (allowable stress) of material.As centrifugation leaf
The material of wheel, such as using stainless steel.Conventional value shown in Fig. 6, be produce in the case of external diameter ratio (d2/d1)=1 should
Force value.
As can be seen from Figure 6, as long as not changing the condition of the intensity with regard to material etc., in order to be less than the appearance of material in stress σ
Permitted in the range of value, to make the outside diameter d 1 of the 1st grade of centrifugal impeller 11 more than the outside diameter d 2 of the 2nd grade of centrifugal impeller 12, made external diameter
It is more than 0.8 and less than 1.0 than (d2/d1).According to constituting in this wise, using the teaching of the invention it is possible to provide suppression results from centrifugal impeller
The increase of 11 stress, reduces thrust load, high efficiency and the high multistage centrifugal of Mechanical Reliability resulting from output shaft 5
Compressor.
Additionally, in the present embodiment, master gear 20 and mill pinlon 21,22 are helical gears.And, sheded baby teeth with acting on vertically
The fluid of the gear load fp2 of wheel 22 and the centrifugal impeller 13 acting on the 3rd level positioned at most downstream level side along thrust direction carries
Lotus fi2 becomes rightabout mode, sets the helical gear rotation direction of master gear 20 and mill pinlon 21,22.
According to constituting in this wise, by using helical gear, can seek to vibrate the reduction with noise, and fluid-load
Fi2 and gear load fp2 mutually offsets, and pushes away produced by the output shaft 6 that can reduce the centrifugal impeller 13 possessing most downstream level
Power load.Thus, thrust ring 69 diminishes with the contact of master gear 20, the friction loss of sliding part, the effect of multistage centrifugal compressor
Rate improves.Additionally, being improved by the Mechanical Reliability of thrust ring 69 on output shaft 6 for the hot jacket and master gear 20, and, thrust ring
69 and master gear 20 sliding surface abrasion amount reduce.Further, since resulting from the overall thrust load (resultant load of gear train
F) reduce, so master gear 20 also diminishes with the contact of composite bearing 61, the friction loss of sliding part.Thus, it is possible to further
Improve the Mechanical Reliability of multistage centrifugal compressor.
[the 2nd embodiment]
Then, with reference to Fig. 7, the 2nd embodiment to the present invention, in the point different from the 1st above-mentioned embodiment being
The heart illustrates, and suitably omits the explanation of identical point.
Fig. 7 is the horizontal cross of the multistage centrifugal compressor schematically showing the 2nd embodiment.
As shown in fig. 7, on this point the multistage centrifugal compressor of the 2nd embodiment is 4 grades of compressors, and it is 3 grades
1st embodiment of compressor is different.That is, in one end of output shaft 6, it is provided with the centrifugal impeller 13 of 3rd level, in output shaft 6
The other end, is provided with the 4th grade of the most downstream level side of flowing positioned at fluid of centrifugal impeller 14.
In the 2nd embodiment, identically with the 1st embodiment, the outside diameter d 1 of the 1st grade of centrifugal impeller 11 is set
The outside diameter d 2 of the centrifugal impeller 12 than the 2nd grade is big.Additionally, the outside diameter d 3 of the centrifugal impeller 13 of 3rd level is set the 4th grade of ratio
The outside diameter d 4 of centrifugal impeller 14 is big.Thus, act on defeated due to the centrifugal impeller 12 of the 1st grade of centrifugal impeller 11 and the 2nd grade
The fluid-load fi1 of the thrust direction of shaft 5 relatively diminishes, and the thrust load resulting from output shaft 5 reduces.Further, since
The centrifugal impeller 14 of the centrifugal impeller 13 of 3rd level and the 4th grade and act on the fluid-load fi2 phase of the thrust direction of output shaft 6
Diminish over the ground, the thrust load resulting from output shaft 6 reduces.
Additionally, in the 2nd embodiment, being made with along thrust direction with the gear load fp2 acting on mill pinlon 22 vertically
Become the mode of equidirectional for the fluid-load positioned at the 4th grade of most downstream level side of centrifugal impeller 14, set master gear
20 and the helical gear rotation direction of mill pinlon 21,22.This is to be used with the 1st embodiment identical master gear and mill pinlon as premise.
Here, act on along thrust direction the 4th grade centrifugal impeller 14 fluid-load than along thrust direction act on 3rd level from
The fluid-load of lobus cardiacus wheel 13 is big.Direction accordingly, as the fluid-load fi2 of the thrust direction in output shaft 6 for the mass action
Identical with the direction of the fluid-load of the centrifugal impeller 14 acting on the 4th grade along thrust direction, it is laterally to send out on the contrary from engine
The direction of motivation side.
So, according to the 2nd embodiment it is also possible to the present invention is applied to 4 grades of compressors, can obtain and the 1st enforcement
Mode identical effect.
[the 3rd embodiment]
Then, with reference to Fig. 8, third embodiment of the present invention, with the point different from the 2nd above-mentioned embodiment be
Center illustrates, the suitable explanation omitting common point.
Fig. 8 is the horizontal cross of the multistage centrifugal compressor schematically showing the 3rd embodiment.
As shown in figure 8, the multistage centrifugal compressor of the 3rd embodiment, it is contrary this in the rotation direction of main wheel and mill pinlon
On point, different from the 2nd embodiment.That is, master gear is the helical gear of dextrorotation, and mill pinlon is left-handed helical gear.
In the 3rd embodiment, identically with the 2nd embodiment, the outside diameter d 1 of the 1st grade of centrifugal impeller 11 is set
The outside diameter d 2 of the centrifugal impeller 12 than the 2nd grade is big.Additionally, the outside diameter d 3 of the centrifugal impeller 13 of 3rd level is set the 4th grade of ratio
The outside diameter d 4 of centrifugal impeller 14 is big.Thus, act on defeated due to the centrifugal impeller 12 of the 1st grade of centrifugal impeller 11 and the 2nd grade
The fluid-load fi1 of the thrust direction of shaft 5 relatively diminishes, and the thrust load resulting from output shaft 5 reduces.Further, since
The centrifugal impeller 14 of the centrifugal impeller 13 of 3rd level and the 4th grade and act on the fluid-load fi2 of the thrust direction of output shaft 6
Relatively diminish, the thrust load resulting from output shaft 6 reduces.
Additionally, in the 3rd embodiment, being made with along thrust direction with the gear load fp2 acting on mill pinlon 22 vertically
Fluid-load for the centrifugal impeller 14 positioned at the 4th grade of most downstream level side becomes rightabout mode, sets master gear
20 and the helical gear rotation direction of mill pinlon 21,22.Here, the fluid acting on the 4th grade of centrifugal impeller 14 along thrust direction carries
Lotus is bigger than the fluid-load of the centrifugal impeller 13 acting on 3rd level along thrust direction.Accordingly, as mass action in output shaft 6
The fluid-load fi2 of thrust direction direction, with the fluid-load of the centrifugal impeller 14 acting on the 4th grade along thrust direction
Direction is identical, is the direction from engine lateral engine side on the contrary.Thus, in the 3rd embodiment, master gear 20 is set as
The helical gear of dextrorotation, mill pinlon 21,22 is set as left-handed helical gear.Thus, fluid-load fi2 and gear load fp2 mutually offsets
Pin, can reduce the thrust load produced by output shaft 6 of the centrifugal impeller 14 possessing most downstream level.Additionally, in the 3rd embodiment party
In formula, act on the gear load fp1 of mill pinlon 21 vertically, the stream with the centrifugal impeller 12 acting on the 2nd grade along thrust direction
Body load is rightabout.Thus, fluid-load fi1 and gear load fp1 mutually offsets, can reduce possess the 2nd grade from
The thrust load produced by output shaft 5 of lobus cardiacus wheel 12.
[the 4th embodiment]
Then, with reference to Fig. 9, fourth embodiment of the present invention, with the point different from the 2nd above-mentioned embodiment be
Center illustrates, the suitable explanation omitting common point.
Fig. 9 is the horizontal cross of the multistage centrifugal compressor schematically showing the 4th embodiment.
As shown in figure 9, the multistage centrifugal compressor of the 4th embodiment, in the leaf of the impeller 13 possessing 3rd level and the 4th grade
On this point position of wheel 14 is contrary, different from the 2nd embodiment.
In the 4th embodiment, identically with the 2nd embodiment, the outside diameter d 1 of the 1st grade of centrifugal impeller 11 is set
The outside diameter d 2 of the centrifugal impeller 12 than the 2nd grade is big.Additionally, the outside diameter d 3 of the centrifugal impeller 13 of 3rd level is set the 4th grade of ratio
The outside diameter d 4 of centrifugal impeller 14 is big.Thus, act on defeated due to the centrifugal impeller 12 of the 1st grade of centrifugal impeller 11 and the 2nd grade
The fluid-load fi1 of the thrust direction of shaft 5 relatively diminishes, and the thrust load resulting from output shaft 5 reduces.Further, since
The centrifugal impeller 14 of the centrifugal impeller 13 of 3rd level and the 4th grade and act on the fluid-load fi2 phase of the thrust direction of output shaft 6
Diminish over the ground, the thrust load resulting from output shaft 6 reduces.
Additionally, in the 4th embodiment, being made with along thrust direction with the gear load fp2 acting on mill pinlon 22 vertically
Fluid-load for the centrifugal impeller 14 positioned at the 4th grade of most downstream level side becomes rightabout mode, sets master gear
20 and the helical gear rotation direction of mill pinlon 21,22.Here, the fluid acting on the 4th grade of centrifugal impeller 14 along thrust direction carries
Lotus is bigger than the fluid-load of the centrifugal impeller 13 acting on 3rd level along thrust direction.Accordingly, as mass action in output shaft 6
The fluid-load fi2 of thrust direction direction, with the fluid-load of the centrifugal impeller 14 acting on the 4th grade along thrust direction
Direction is identical, is the direction from engine side to engine opposition side.Thus, in the 4th embodiment, master gear 20 is set as
The helical gear of dextrorotation, mill pinlon 21,22 is set as left-handed helical gear.Thus, fluid-load fi2 and gear load fp2 mutually offsets
Pin, can reduce the thrust load produced by output shaft 6 of the centrifugal impeller 14 possessing most downstream level.
Additionally, in the 4th embodiment, act on centrifugal impeller 14 positioned at the 4th grade of most downstream level side vertically
Fluid-load, the fluid-load with the centrifugal impeller 12 acting on the 2nd grade vertically is rightabout.Thus, with the 1st embodiment party
In the same manner, fluid-load fi1 and fluid-load fi2 mutually offset formula, can reduce the thrust load of input shaft 4 generation.
[the 5th embodiment]
Then, with reference to Figure 10, fifth embodiment of the present invention, with the point different from the 1st above-mentioned embodiment be
Center illustrates, the suitable explanation omitting common point.
Figure 10 is the horizontal cross of the multistage centrifugal compressor schematically showing the 5th embodiment.
As shown in Figure 10, on this point multistage centrifugal compressor in the 5th embodiment is 2 grades of compressors, is compressed with 3 grades
1st embodiment of machine is different.That is, with respect to the 1st embodiment possess 2 output shafts the 5,6, the 5th embodiment possess 1 defeated
Shaft 5.
In the 5th embodiment, identically with the 1st embodiment, the outside diameter d 1 of the 1st grade of centrifugal impeller 11 is set
The outside diameter d 2 of the centrifugal impeller 12 than the 2nd grade is big.Thus, due to the 1st grade of centrifugal impeller 11 and the 2nd grade centrifugal impeller 12 and
The fluid-load fi1 acting on the thrust direction of output shaft 5 relatively diminishes, and the thrust load resulting from output shaft 5 reduces.
Additionally, in the 5th embodiment, being made with along thrust direction with the gear load fp1 acting on mill pinlon 21 vertically
Become the mode of equidirectional for the fluid-load positioned at the 2nd grade of most downstream level side of centrifugal impeller 12, set master gear
20 and the helical gear rotation direction of mill pinlon 21.This is to be used with the 1st embodiment identical master gear and mill pinlon as premise.?
Here, act on the fluid-load of the 2nd grade of centrifugal impeller 12 along thrust direction, than along thrust direction act on the 1st grade from
The fluid-load of lobus cardiacus wheel 11 is big.Accordingly, as the direction of the fluid-load fi1 of the thrust direction in output shaft 5 for the mass action,
Identical with the direction of the fluid-load of the centrifugal impeller 12 acting on the 2nd grade along thrust direction, it is laterally to send out on the contrary from engine
The direction of motivation side.
So, according to the 5th embodiment it is also possible to the present invention is applied to 2 grades of compressors, can obtain and the 1st enforcement
Mode identical effect.
[the 6th embodiment]
Then, with reference to Figure 11, sixth embodiment of the present invention, with the point different from the 5th above-mentioned embodiment be
Center illustrates, the suitable explanation omitting common point.
Figure 11 is the horizontal cross of the multistage centrifugal compressor schematically showing the 6th embodiment.
As shown in figure 11, the multistage centrifugal compressor of the 6th embodiment, is contrary this in the rotation direction of master gear and mill pinlon
On a bit, different from the 5th embodiment.That is, master gear is the helical gear of dextrorotation, and mill pinlon is left-handed helical gear.
In the 6th embodiment, identically with the 5th embodiment, the outside diameter d 1 of the 1st grade of centrifugal impeller 11 is set
The outside diameter d 2 of the centrifugal impeller 12 than the 2nd grade is big.Thus, due to the 1st grade of centrifugal impeller 11 and the 2nd grade centrifugal impeller 12 and
The fluid-load fi1 acting on the thrust direction of output shaft 5 relatively diminishes, and the thrust load resulting from output shaft 5 reduces.
Additionally, in the 6th embodiment, being made with along thrust direction with the gear load fp1 acting on mill pinlon 21 vertically
Fluid-load for the centrifugal impeller 12 positioned at the 2nd grade of most downstream level side becomes rightabout mode, sets gear 20
Helical gear rotation direction with mill pinlon 21.Here, the fluid-load of the 2nd grade of centrifugal impeller 12 is acted on along thrust direction, than
The fluid-load acting on the 1st grade of centrifugal impeller 11 along thrust direction is big.Accordingly, as mass action pushing away in output shaft 5
The direction of the fluid-load fi1 of force direction, the direction with the fluid-load of the centrifugal impeller 12 acting on the 2nd grade along thrust direction
Identical, it is the direction from engine lateral engine side on the contrary.Thus, in the 6th embodiment, master gear 20 is set as dextrorotation
Helical gear, mill pinlon 21 is set as left-handed helical gear.Thus, fluid-load fi1 and gear load fp1 mutually offsets, can
Reduce the thrust load produced by output shaft 5 of the centrifugal impeller 12 possessing most downstream level.
More than, the present invention is illustrated based on embodiment, but the present invention is not limited to above-mentioned embodiment, comprises
Various modifications example.For example, it is described in detail by above-mentioned embodiment for the present invention easy to understand, be not limited to necessary
Possesses all of structure illustrating.Furthermore it is possible to a part for the structure of certain embodiment is replaced into other enforcements
The structure of mode, it is further possible to add the structure of other embodiments in the structure of certain embodiment.Additionally, closing
In a part for the structure of each embodiment, adding, eliminate, replacing of other structures can be carried out.
For example in the above-described embodiment, illustrate that multistage centrifugal compressor is the situation of 2～4 grades of compressors, but
The present invention is not limited to these.That is, the present invention can be applied to the input shaft possessing by engine driving and being provided with master gear,
With the centrifugal compressor of the multi-stage type of the more than one output shaft being provided with the mill pinlon engaging with master gear, for example, also can be suitable for
Multistage centrifugal compressor more than 5 grades.
Claims (7)
1. a kind of multistage centrifugal compressor it is characterised in that
This multistage centrifugal compressor possesses:
Input shaft, by engine driving；
Master gear, located at above-mentioned input shaft；
Mill pinlon, is engaged with above-mentioned master gear；
Output shaft, for arranging above-mentioned mill pinlon；
1st centrifugal impeller, located at one end of above-mentioned output shaft；And
2nd centrifugal impeller, located at the other end of above-mentioned output shaft, under the flowing leaning on fluid than above-mentioned 1st centrifugal impeller
Trip level side,
The external diameter of above-mentioned 1st centrifugal impeller is set bigger than the external diameter of above-mentioned 2nd centrifugal impeller.
2. multistage centrifugal compressor according to claim 1 it is characterised in that
The ratio of the external diameter with respect to above-mentioned 1st centrifugal impeller for the external diameter of above-mentioned 2nd centrifugal impeller, be set to more than 0.8 and
Less than 1.0.
3. multistage centrifugal compressor according to claim 1 and 2 it is characterised in that
This multistage centrifugal compressor possesses:
2nd mill pinlon, is engaged with above-mentioned master gear；
2nd output shaft, for arranging above-mentioned 2nd mill pinlon；And
Centrifugal impeller, located at above-mentioned 2nd output shaft, positioned at the downstream stage side of the flowing of the fluid of above-mentioned 2nd centrifugal impeller.
4. multistage centrifugal compressor according to claim 3 it is characterised in that
Above-mentioned master gear, above-mentioned mill pinlon and above-mentioned 2nd mill pinlon are helical gears,
To act on the gear load of above-mentioned 2nd mill pinlon and the centrifugal impeller acting on vertically positioned at most downstream level side vertically
Fluid-load become rightabout mode, set above-mentioned helical gear rotation direction.
5. multistage centrifugal compressor according to claim 4 it is characterised in that
The gear load acting on above-mentioned mill pinlon vertically and the fluid-load acting on above-mentioned 2nd centrifugal impeller vertically are phase
Opposite direction.
6. multistage centrifugal compressor according to claim 4 it is characterised in that
Act on the fluid-load of the centrifugal impeller positioned at above-mentioned most downstream level side vertically with act on vertically the above-mentioned 2nd from
The fluid-load of lobus cardiacus wheel is rightabout.
7. multistage centrifugal compressor according to claim 1 and 2 it is characterised in that
Above-mentioned master gear and above-mentioned mill pinlon are helical gears,
In the case of the centrifugal impeller of the most downstream level side being in the flowing of fluid in above-mentioned 2nd centrifugal impeller, with vertically
Act on the gear load of above-mentioned mill pinlon and the fluid-load acting on above-mentioned 2nd centrifugal impeller vertically becomes rightabout
Mode, sets above-mentioned helical gear rotation direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013161009A JP6137983B2 (en) | 2013-08-02 | 2013-08-02 | Multistage centrifugal compressor |
| JP2013-161009 | 2013-08-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104343698A CN104343698A (en) | 2015-02-11 |
| CN104343698B true CN104343698B (en) | 2017-01-18 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410351897.2A Expired - Fee Related CN104343698B (en) | 2013-08-02 | 2014-07-23 | Multistage centrifugal compressor |
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| Country | Link |
|---|---|
| JP (1) | JP6137983B2 (en) |
| CN (1) | CN104343698B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2018011917A1 (en) * | 2016-07-13 | 2018-01-18 | 三菱電機株式会社 | Electric blower and electrical apparatus |
| CN109404302A (en) * | 2018-11-29 | 2019-03-01 | 中国船舶重工集团公司第七0四研究所 | Multiple shafting high-lift centrifugal pump |
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|---|---|---|---|---|
| US4285631A (en) * | 1978-11-20 | 1981-08-25 | Plessey Handel Und Investments Ag | Radial flow centrifugal impeller |
| US5062766A (en) * | 1988-09-14 | 1991-11-05 | Hitachi, Ltd. | Turbo compressor |
| JPH11153097A (en) * | 1997-11-21 | 1999-06-08 | Hitachi Ltd | Single shaft multistage centrifugal compressor and turbo refrigerator |
| CN1789727A (en) * | 2004-12-14 | 2006-06-21 | 海巴（巴拿马）鼓风机公司 | High-pressure multistage centrifugal blower |
| JP2010001868A (en) * | 2008-06-23 | 2010-01-07 | Toyota Motor Corp | Centrifugal compressor |
| CN201963596U (en) * | 2011-02-18 | 2011-09-07 | 长沙赛尔机泵有限公司 | Centrifugal compressor and impeller thereof |
| CN202579249U (en) * | 2012-05-15 | 2012-12-05 | 长沙埃尔压缩机有限责任公司 | Centrifugal compressor with multiple shafts |
| WO2013021664A1 (en) * | 2011-08-05 | 2013-02-14 | 三菱重工コンプレッサ株式会社 | Centrifugal compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3826587A (en) * | 1973-04-10 | 1974-07-30 | Ingersoll Rand Co | Centrifugal gas compressor unit |
| JPS5817358B2 (en) * | 1978-03-07 | 1983-04-06 | 川崎重工業株式会社 | Multi-stage turbo compressor |
-
2013
- 2013-08-02 JP JP2013161009A patent/JP6137983B2/en not_active Expired - Fee Related
-
2014
- 2014-07-23 CN CN201410351897.2A patent/CN104343698B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4285631A (en) * | 1978-11-20 | 1981-08-25 | Plessey Handel Und Investments Ag | Radial flow centrifugal impeller |
| US5062766A (en) * | 1988-09-14 | 1991-11-05 | Hitachi, Ltd. | Turbo compressor |
| JPH11153097A (en) * | 1997-11-21 | 1999-06-08 | Hitachi Ltd | Single shaft multistage centrifugal compressor and turbo refrigerator |
| CN1789727A (en) * | 2004-12-14 | 2006-06-21 | 海巴（巴拿马）鼓风机公司 | High-pressure multistage centrifugal blower |
| JP2010001868A (en) * | 2008-06-23 | 2010-01-07 | Toyota Motor Corp | Centrifugal compressor |
| CN201963596U (en) * | 2011-02-18 | 2011-09-07 | 长沙赛尔机泵有限公司 | Centrifugal compressor and impeller thereof |
| WO2013021664A1 (en) * | 2011-08-05 | 2013-02-14 | 三菱重工コンプレッサ株式会社 | Centrifugal compressor |
| CN202579249U (en) * | 2012-05-15 | 2012-12-05 | 长沙埃尔压缩机有限责任公司 | Centrifugal compressor with multiple shafts |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6137983B2 (en) | 2017-05-31 |
| JP2015031202A (en) | 2015-02-16 |
| CN104343698A (en) | 2015-02-11 |
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