CN203404104U - Turbocompressor - Google Patents
Turbocompressor Download PDFInfo
- Publication number
- CN203404104U CN203404104U CN200920291304.2U CN200920291304U CN203404104U CN 203404104 U CN203404104 U CN 203404104U CN 200920291304 U CN200920291304 U CN 200920291304U CN 203404104 U CN203404104 U CN 203404104U
- Authority
- CN
- China
- Prior art keywords
- pinion shaft
- turbocompressor
- compressor
- compressor operating
- wheel
- 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.)
- Expired - Lifetime
Links
- 239000012530 fluid Substances 0.000 claims abstract description 7
- 238000007789 sealing Methods 0.000 claims abstract description 6
- 238000005096 rolling process Methods 0.000 claims description 5
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical group [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 4
- 238000006243 chemical reaction Methods 0.000 claims description 3
- 230000013011 mating Effects 0.000 claims description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
Images
Classifications
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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
- 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
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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
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
- F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Provided is a turbocompressor including a casing device, a drive wheel device rotationally supported in the casing device, and a plurality of mutually axially parallel pinion shafts. The pinion shafts (30) comprise pinion sections (31) that stand in rotary drive connection with the drive wheel device. At least one end of the two ends of each pinion shaft is provided with a compressor running wheel which stands in rotary drive connection with the pinion shaft and is cooperated with the casing device to form a corresponding compressor stage of the turbocompressor. The pinion shafts are supported in the casing device through rotation bearings. The compressor stages are sealed by a sealing device against fluid entry to the pinion sections of the pinion shafts that support the corresponding compressor running wheels.
Description
Technical field
The utility model relates to a kind of turbocompressor, particularly relates to a kind of multistage turbocompressor with a plurality of compressor operating wheels, and these compressor operating wheels are supported on the axle of different parallel to an axiss.
Background technique
Multistage turbocompressor has a plurality of compressor operating wheels, and these compressor operating wheels are supported on the axle of different parallel to an axiss, and this multistage turbocompressor is known as gear compressor (Getriebekompressor) in the prior art.
Model utility content
The purpose of this utility model is, proposes a kind of turbocompressor, although it has a plurality of compressor stages on the axle that is distributed in a plurality of parallel to an axiss, but still compact structure, thereby save space.
This object realizes by the turbocompressor according to claim 1.In dependent claims, provided improvement of the present utility model.
According to the utility model, multistage turbocompressor or gear type turbocompressor have box body device, the driving-wheel device of rotary support in this box body device, the pinion shaft of a plurality of mutual parallel to an axiss, these pinion shafts have respectively the small gear section being connected in rotary drive with driving-wheel device, wherein at least one end in the two ends of each pinion shaft has compressor operating wheel, described compressor operating wheel is connected with pinion shaft rotary drive, and with box body device mating reaction, form accordingly independently (separat) compressor stage of turbocompressor, and each pinion shaft passes through two swivel bearing rotary supports in box body device, wherein each compressor stage is sealed by seal arrangement, to prevent that fluid from flowing to the small gear section of pinion shaft, described pinion shaft is supporting corresponding compressor operating wheel.
The pinion shaft according to the turbocompressor of the utility model structure with a plurality of parallel to an axiss, the compressor operating wheel of these pinion shafts forms a plurality of compressor stages.All pinion shafts all connect by the mutual rotary drive of driving-wheel device, thus can so that all pinion shafts or compressor stage are all passed through unique rotating actuator, (Drehantrieb) synchronously rotarilyd actuate.Compressor operating wheel is only arranged on the end of pinion shaft with cantilever mounting type, can adopt thus simple mode to realize and make flow axis to flowing to corresponding compressor stage.
According to a mode of execution of the present utility model, all compressor stages all interconnect, and use if desired interstage cooler or miscellaneous equipment assembly.
According to a mode of execution of the present utility model, at least one pinion shaft in a plurality of pinion shafts has respectively compressor operating wheel at its two ends, and wherein two of this pinion shaft swivel bearings are arranged between two compressor operating wheels.
According to this design of the present utility model, can adopt in a beneficial way and realize two synchronously driven compressor stages by a pinion shaft.
According to another mode of execution of the present utility model, the small gear section that is provided with each pinion shaft of compressor operating wheel at two ends is arranged between the swivel bearing of corresponding pinion shaft.
Adopt which to make spatially rotary drive be directed on pinion shaft for the special saving of corresponding pinion shaft.
According to another mode of execution of the present utility model, each seal arrangement be arranged on belong in the compressor operating wheel of corresponding compressor stage and two swivel bearings of pinion shaft along axially following between the swivel bearing of pinion shaft, described pinion shaft is supporting corresponding compressor operating wheel.
Adopt which, can realize and utilize a unique seal arrangement to make being protected with the non-directly related all component of fluid compression (Fluidkompression) of each compressor stage, in case fluid enters or be applied in fluid.
According to another mode of execution of the present utility model, driving-wheel device has at least one central axis, described central axis is rotatably supported in box body device, and with the central gear being connected with central axis rotary drive, the wherein small gear section of at least one pinion shaft in this central authorities' gear and a plurality of pinion shaft engagement.
Therefore according to this design of the present utility model, can be so that one of turbocompressor, a plurality of or all pinion shafts be connected with central gear rotary drive, thereby can rotary drive be directed on corresponding pinion shaft with very compact and joint space-efficient mode.
According to a mode of execution of the present utility model, driving-wheel device has two and is rotatably supported on respectively the central axis in box body device, wherein each central axis has the central gear being connected with its rotary drive, the wherein small gear section of at least one pinion shaft in each central gear and a plurality of pinion shafts engagement, thereby a central gear or another central gear engagement in the small gear section of each pinion shaft and two central gears.
According to this design of the present utility model, can for example realize for two groups of pinion shafts of turbocompressor or two different gear stages of compressor stage by two central axis
so the pinion shaft of a group corresponds respectively to a central axis in two central axis according to drive connection.
According to another mode of execution of the present utility model, two mutual rotary drives of central axis connect.This point can be realized by the direct engagement of two central gears, or for example also can realize by additional gear.
Adopt this design of the present utility model to guarantee, although rotary drive is assigned on two central axis, for turbocompressor, only need unique rotating actuator.
According to another mode of execution of the present utility model, the compressor stage of turbocompressor is axially structure type of radial structure type or half, wherein box body device has helical housing for each compressor operating wheel, described helical housing surrounds compressor operating wheel, and forms corresponding compressor stage together with corresponding rolling member.In other words, turbocompressor consists of the gear compressor of radial structure type.
According to another mode of execution of the present utility model, each seal arrangement can have the combination of two kinds in labyrinth sealing mechanism, carbon ring seal mechanism or dry gas seal mechanism or these seal types or the combination of all these seal types.
Can avoid reliably thus any process gas to enter into gear region (Getriebebereich) (small gear section and driving-wheel device) from corresponding compressor stage, vice versa.
According to another mode of execution of the present utility model, turbocompressor has 8,9 or 10 compressor stages.
According to the design proposal of this mode of execution of the present utility model, 4 pinion shafts respectively with two compressor operating wheels for example can be set thus, 5 pinion shafts can be set, 4 pinion shafts wherein have respectively two compressor operating wheels, another has a compressor operating wheel, or 5 pinion shafts respectively with two compressor operating wheels can be set.Can certainly adopt other design proposal.
According to mode of execution of the present utility model, turbocompressor or the gear compressor of radial structure type multistage, preferred 8-10 level have a plurality of pinion shafts, these pinion shafts are driven by a central gear or two intermeshing central gears, and respectively in one end at least, but also can be at two ends, have compressor operating wheel, these compressor operating wheels are connected with pinion shaft by suitable bindiny mechanism, preferred engaging mechanism and axial swell fixture or hot press mechanism or guard pins (Scherstifte).
According to mode of execution of the present utility model, these compressor operating wheels form each compressor stage together with their parts of encirclement, belong to the corresponding helical housing of particularly having of described parts and corresponding rolling member.These compressor stages can interconnect by intercoolant or other parts, realize thus high final pressure and the final temperature of permission, realize high whole efficiency simultaneously.
According to mode of execution of the present utility model, each compressor stage seals with respect to gear mechanism (Getriebe) by suitable sealing mechanism.At this, preferably can use labyrinth sealing mechanism, carbon ring seal mechanism or dry gas seal mechanism or their combination.One or more compressor stages can be provided with adjustable inlet guide cascade blade.
According to mode of execution of the present utility model, pinion shaft and central axis are supported in the box body device structure of formative gear casing, wherein preferably use sliding bearing.
According to mode of execution of the present utility model, for example, for motoring, directly by central axis, realize rotary drive, or for turbine drives, by one end of a pinion shaft, realize rotary drive.Under latter instance, this pinion shaft is useful on the coupling that transmits the power that drives turbine at described end band.
According to mode of execution of the present utility model, compressor operating wheel is utilized the pin bindiny mechanism of swell fixture or shrink fit mechanism or form fit and is connected with pinion shaft by engaging mechanism.
According to mode of execution of the present utility model, the end thrust (Axialschub) of compressor operating wheel is delivered to one or more central gears by Thrust ring (Druckkamm) from pinion shaft, wherein except radial bearing, wheel shaft is also provided with cod, or is provided with the axial/radial bearing of combination.
Accompanying drawing explanation
Below by preferred embodiment and contrast accompanying drawing and describe the utility model in detail.
Fig. 1 is the schematic stereogram according to the turbocompressor of mode of execution of the present utility model;
Fig. 2 is the schematic sectional view of the turbocompressor of Fig. 1;
Fig. 3 contains Fig. 3 A and 3B, and they are according to the schematic sectional view of the turbocompressor of mode of execution of the present utility model or schematic front view;
Fig. 4 contains Fig. 4 A and 4B, and they are according to the schematic sectional view of the turbocompressor of mode of execution of the present utility model or schematic front view.
Reference numerals list
1 turbocompressor
1 ' turbocompressor
1 " turbocompressor
2 compressor stages
10 box body devices
11 swivel bearings
12 swivel bearings
13 helical housings
14 box body devices
20 driving-wheel devices
30 pinion shafts
30 ' pinion shaft
30 " pinion shafts
31 small gear sections
31 ' small gear section
31 " small gear section
40 compressor operating wheels
41 rolling members
50 seal arrangements
60 central axis
60 ' central axis
60 " central axis
61 central gears
61 " central gear
The central gear of 61a '
The central gear of 61b '
70 central axis
71 central gears
80 Thrust rings
AR is axial
Embodiment
Fig. 1 and Fig. 2 are according to the schematic stereogram of the turbocompressor 1 of mode of execution of the present utility model or schematic sectional view.
As from Fig. 1 and Fig. 2, turbocompressor 1 is the gear compressor of radial structure type.
Each pinion shaft 30 has the small gear section 31 being connected in rotary drive with driving-wheel device 20.
Each pinion shaft 30 has two ends, on these ends, be fixed with compressor operating wheel 40, described compressor operating wheel 40 is connected with pinion shaft 30 rotary drives, and with box body device 10 mating reactions, the compressor stage 2 of the corresponding radial structure type of formation turbocompressor 1.
As a result, the turbocompressor shown in Fig. 11 has 10 independently compressor stages 2 of radial structure type.These compressor stages 2 can interconnect by interstage cooler (not shown), realize thus high final pressure and the final temperature of permission, realize high whole efficiency simultaneously.
As shown in Figure 2, each pinion shaft 30 passes through two swivel bearing 11 rotary supports at the gear housing of box body device 10
in 14, wherein two swivel bearings 11,11 of corresponding pinion shaft 30 are arranged between two compressor operating wheel 40,40, and the small gear section 31 of corresponding pinion shaft 30 is arranged between two swivel bearings 11,11.
In addition as seen from Figure 2, each compressor stage 2 is sealed by seal arrangement 50, and to prevent that fluid from flowing to the small gear section 31 of pinion shaft 30, described pinion shaft 30 is supporting corresponding compressor operating wheel 40.Seal arrangement 50 is arranged on and belongs to following along axial AR between the swivel bearing 11 of pinion shaft 30 in the compressor operating wheel 40 of corresponding compressor stage 2 and two swivel bearings 11,11 of pinion shaft 30 at this, and described pinion shaft 30 is supporting corresponding compressor operating wheel 40.
According to the mode of execution not being shown specifically of the present utility model, each seal arrangement 50 can have the combination of two kinds in labyrinth sealing mechanism, carbon ring seal mechanism or dry gas seal mechanism or these seal types or the combination of all these seal types.
Driving-wheel device 20 has two central axis 60 and 70, these central axis are rotatably supported in the gear housing 14 of box body device 10 by swivel bearing 12 respectively, and wherein each central axis 60,70 has the central gear 61 or 71 being connected with its rotary drive.
Corresponding small gear section 31 engagements of three pinion shafts 30 of top in the central gear 71 of the central axis 70 of top and Fig. 1 in Fig. 1, corresponding small gear section 31 engagements of two pinion shafts 30 of below in the central gear 61 of the central axis 60 of below and Fig. 1 in Fig. 1, thereby a central gear 61 or another central gear 71 engagements in the small gear section 31 of each pinion shaft 30 and two central gears 61,71.
Same as seen from Figure 1, in Fig. 1, the central gear 71 of top is Double-gear, central gear 61 engagements of below in the gear segment that wherein diameter is less and Fig. 1, thereby the mutual rotary drives of two central axis 60,70 connect, the larger gear segment of diameter with Fig. 1 in small gear section 31 engagements of pinion shaft 30 of top.
As from Fig. 1 and Fig. 1, box body device 10 has helical housing 13 for each compressor operating wheel 40, described helical housing 13 surrounds compressor operating wheel 40, and forms corresponding compressor stage 2 together with corresponding rolling member (Einlaufeinsatz) 41 (seeing Fig. 2).As Fig. 2 exemplarily illustrates, be arranged on bottom-right compressor stage 2 in Fig. 2 and be also provided with adjustable inlet guide cascade blade (Vorleitgitterschaufel) 42.Other compressor stage 2 also can be provided with adjustable inlet guide leaf grating, or these compressor stages 2 are not all provided with adjustable inlet guide leaf grating.
According to the model utility mode of execution shown in Fig. 1, rotary drive directly guides (einleiten) to one end of the central axis 60 of below in Fig. 1 by unshowned motor, wherein on this end, is provided with coupling (Kupplung) (not shown) that the power for motor transmits.
Fig. 3 A and 3B be turbocompressor 1 according to another mode of execution of the present utility model ' schematic sectional view (view of the arrow A from Fig. 3 B) or schematic front view.
According to the turbocompressor 1 of Fig. 3 A and 3B ' structure basic with identical according to the structure of the turbocompressor of Fig. 1 and 2, thereby similar parts indicate identical reference character, but these reference characters are with " ' ", and the main distinction is only described below.
Different from the mode of execution of Fig. 1 and 2, for according to the turbocompressor 1 of Fig. 3 A and 3B ' for, two central gear 61a ' and 61b ' be arranged on central axis 60 ' on, wherein the pinion shaft 30 in the middle of left in Fig. 3 B ' small gear section 31 ' with a central gear 61b ' and two other pinion shaft 30 ', 30 ' small gear section 31 ' engagement, three pinion shafts 30 of remainder ' small gear section 31 ' with another central gear 61a ' engagement.
Fig. 4 A4 and 4B are the turbocompressor 1 according to another mode of execution of the present utility model " schematic sectional view (view of the arrow A from Fig. 4 B) or schematic front view.
According to the turbocompressor 1 of Fig. 4 A and 4B " structure basic with identical according to the structure of the turbocompressor of Fig. 1 and 2, thereby similar parts indicate identical reference character, but these reference characters are with " " ", the main distinction is only described below.
Different from the mode of execution of Fig. 1 and 2, for according to the turbocompressor 1 of Fig. 4 A and 4B " for; it is upper that unique central gear 61 " is arranged on a unique central axis 60 ", wherein all pinion shafts 30 " small gear section 31 " all with the " engagement of central gear 61.
Claims (14)
1. a turbocompressor, has:
Box body device (10);
The driving-wheel device (20) of rotary support in described box body device (10);
The pinion shaft of a plurality of mutual parallel to an axiss, these pinion shafts have respectively the small gear section being connected with described driving-wheel device (20) rotary drive,
It is characterized in that,
At least one end in the two ends of each pinion shaft has compressor operating wheel (40), described compressor operating wheel is connected with described pinion shaft rotary drive, and with described box body device (10) mating reaction, form the corresponding compressor stage (2) of described turbocompressor, and each pinion shaft passes through two swivel bearings (11) rotary support in described box body device (10)
Each compressor stage (2) is sealed by seal arrangement (50), and to prevent that fluid from flowing to the small gear section of described pinion shaft, described pinion shaft is supporting corresponding compressor operating wheel (40).
2. turbocompressor as claimed in claim 1, is characterized in that, all compressor stages (2) all interconnect.
3. turbocompressor as claimed in claim 1 or 2, it is characterized in that, the two ends of at least one pinion shaft in described a plurality of pinion shaft have respectively compressor operating wheel (40), and two swivel bearings (11) of this pinion shaft are arranged between two compressor operating wheels (40).
4. turbocompressor as claimed in claim 1, is characterized in that, the small gear section that is provided with each pinion shaft of compressor operating wheel (40) at two ends is arranged between the swivel bearing (11) of corresponding pinion shaft.
5. turbocompressor as claimed in claim 1, it is characterized in that, each seal arrangement (50) be arranged on belong in the compressor operating wheel (40) of corresponding compressor stage (2) and two swivel bearings (11) of described pinion shaft along axially following between the swivel bearing (11) of pinion shaft, described pinion shaft is supporting corresponding compressor operating and is taking turns (40).
6. turbocompressor as claimed in claim 1, it is characterized in that, described driving-wheel device (20) has at least one and is rotatably supported on the central axis in described box body device (10), described central axis is with the central gear being connected with its rotary drive, and the small gear section of at least one pinion shaft in described central gear and described a plurality of pinion shaft meshes.
7. turbocompressor as claimed in claim 6, it is characterized in that, described driving-wheel device (20) has two central axis that are rotatably supported on respectively in described box body device (10), each central axis has the central gear being connected with its rotary drive, the small gear section engagement of at least one pinion shaft in each central gear and described a plurality of pinion shafts, thereby a central gear (61) or the engagement of another central gear (71) in the small gear section of each pinion shaft and two central gears.
8. turbocompressor as claimed in claim 7, is characterized in that, two mutual rotary drives of central axis connect.
9. turbocompressor as claimed in claim 1, it is characterized in that, the compressor stage of described turbocompressor (2) is radial structure type, described box body device (10) has helical housing (13) for each compressor operating wheel (40), described helical housing surrounds described compressor operating wheel (40), and forms corresponding compressor stage (2) together with corresponding rolling member (41).
10. turbocompressor as claimed in claim 1, it is characterized in that, each seal arrangement (50) has the combination of two kinds in labyrinth sealing mechanism, carbon ring seal mechanism or dry gas seal mechanism or these seal types or the combination of all these seal types.
11. turbocompressor as claimed in claim 1, is characterized in that, described turbocompressor has 8,9 or 10 compressor stages (2).
12. turbocompressor as claimed in claim 1, is characterized in that, described compressor operating wheel (40) utilizes the pin bindiny mechanism of swell fixture or shrink fit mechanism or form fit by engaging mechanism and is connected with described pinion shaft.
13. turbocompressor as claimed in claim 6, it is characterized in that, the end thrust of described compressor operating wheel (40) is delivered to one or more central gears by Thrust ring (80) from described pinion shaft, and except radial bearing, wheel shaft is also provided with cod.
14. turbocompressor as claimed in claim 2, is characterized in that, all compressor stages (2) are all used interstage cooler to interconnect.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE200910044959 DE102009044959A1 (en) | 2009-09-24 | 2009-09-24 | Multi-stage turbo-compressor i.e. eight to ten stage turbo-compressor, for use as radial transmission compressor, has compressor stages sealed using sealing arrangement against fluid entry to pinion sections of shafts that support wheel |
| DE102009044959.0 | 2009-09-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203404104U true CN203404104U (en) | 2014-01-22 |
Family
ID=43662567
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200920291304.2U Expired - Lifetime CN203404104U (en) | 2009-09-24 | 2009-09-30 | Turbocompressor |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN203404104U (en) |
| DE (1) | DE102009044959A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105863743A (en) * | 2015-02-06 | 2016-08-17 | 曼柴油机和涡轮机欧洲股份公司 | Geared Turbomachine |
| CN107906026A (en) * | 2017-11-27 | 2018-04-13 | 江苏金通灵流体机械科技股份有限公司 | Steam turbine directly drives gear up formula centrifugal compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013210497A1 (en) | 2013-06-06 | 2014-12-11 | Siemens Aktiengesellschaft | geared compressors |
| JP6395683B2 (en) | 2015-09-02 | 2018-09-26 | 株式会社神戸製鋼所 | Compressor |
| DE102021120100A1 (en) | 2021-08-03 | 2023-02-09 | Voith Patent Gmbh | spur gear |
-
2009
- 2009-09-24 DE DE200910044959 patent/DE102009044959A1/en not_active Withdrawn
- 2009-09-30 CN CN200920291304.2U patent/CN203404104U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105863743A (en) * | 2015-02-06 | 2016-08-17 | 曼柴油机和涡轮机欧洲股份公司 | Geared Turbomachine |
| CN107906026A (en) * | 2017-11-27 | 2018-04-13 | 江苏金通灵流体机械科技股份有限公司 | Steam turbine directly drives gear up formula centrifugal compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102009044959A1 (en) | 2011-03-31 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Augsburg Patentee after: Mann Energy Solutions Ltd. Address before: Augsburg Patentee before: Man Diesel & Turbo SE |
|
| CP01 | Change in the name or title of a patent holder | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140122 |
|
| CX01 | Expiry of patent term |