EP2466144A1 - Dispositif pour comprimé un gaz de procédé - Google Patents
Dispositif pour comprimé un gaz de procédé Download PDFInfo
- Publication number
- EP2466144A1 EP2466144A1 EP10015717A EP10015717A EP2466144A1 EP 2466144 A1 EP2466144 A1 EP 2466144A1 EP 10015717 A EP10015717 A EP 10015717A EP 10015717 A EP10015717 A EP 10015717A EP 2466144 A1 EP2466144 A1 EP 2466144A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gas
- pressure
- compressor
- compressor unit
- zone
- 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
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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
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
-
- 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
Definitions
- the present invention relates to a device for compressing a process gas.
- the WO 2009/034006 a compressor unit consisting of a drive motor and a single-stage or multi-stage turbo-compressor, wherein the drive motor and the compressor are arranged in a housing which is hermetically sealed from the outside. Since the area of the integrated drive motor is exposed to at least the same pressure as the intake area of the compressor, a seal is provided between the area of the drive motor and the compressor to avoid adverse effects due to increased gas density in the drive motor.
- an additional compressor unit is provided which conveys the gas flowing into the area of the drive motor back into the area of the compressor. Such compressor units are used in particular in the compression of natural gas.
- a compressor of similar type is from the DE 200 11 217 U1 known.
- the compressor described there is likewise arranged in a housing which is hermetically sealed to the outside together with the drive motor. Between compressor and drive motor, a seal is provided, which is so far permeable to let process gas, which is removed after the first compressor stage and introduced into the drive motor for cooling, again pass into the compressor area.
- the known compressors can not be used in areas in which it depends on a high purity of the process gas and the process gas must therefore never come into contact with the interior of the engine area to avoid contamination.
- high performance drives are used with magnetically levitated shafts, which operate at very high speeds.
- rotations of 60,000 to 80,000 rpm are possible.
- such a drive is subject to high operating requirements, in particular to the effect that the interior of the motor housing must be subject to stable pressure / temperature conditions and no bearing-contaminating foreign particles may penetrate.
- no such silicon particles may penetrate into the engine compartment, since these could cause damage to the shaft bearings.
- a pressure increase in the engine compartment must be avoided, and in particular must be avoided that the operating conditions in the engine compartment adopt a transcritical state for the gas in the engine compartment.
- the device according to the invention for compressing a process gas (referred to below briefly as the compression device) comprises at least one compressor unit and a drive motor arranged in a motor housing.
- the drive motor has a drive shaft for driving the at least one compressor unit.
- a so-called gas-dynamic barrier is provided, which is arranged in the region of the drive shaft between the compressor unit and the motor housing.
- a gas-dynamic barrier is understood to be an arrangement which, in order to prevent the penetration of process gas into the motor housing, generates a barrier which utilizes the specific gas dynamics of the compression device or threshold for the passing through a drive shaft passage from the compressor housing process gas.
- the gas-dynamic barrier is a gas barrier consisting of a specific pressure profile, wherein the pressure profile uses the so-called PNP effect, ie the lowest pressure prevails in the center of the barrier arrangement.
- PNP effect ie the lowest pressure prevails in the center of the barrier arrangement.
- the gas-dynamic barrier of the invention thus serves to avoid a passage of process gas into the motor housing (32).
- the gas-dynamic barrier comprises two zones (41, 43), namely a first zone pointing towards the compressor housing (compressor-side or impeller-side zone) with a pressure which is higher than a pressure of a second zone pointing towards the motor housing (drive-side or bearing-side zone). , whose pressure in turn is less than a pressure in the motor housing.
- the formation of the zones can take place by suitable measures, for example by means of gas throttling devices or the like, which bring about a throttling or reduction of the gas flow along the drive shaft.
- gas throttling devices or the like, which bring about a throttling or reduction of the gas flow along the drive shaft.
- the throttle devices o. arise the corresponding zones (or chambers).
- the throttle devices o. The like. Can be arranged annularly around the drive shaft.
- the pressure setting in the compressor-side first zone or chamber can be done by connecting to a pressure equalization line, the pressure level of the first zone the level of an upstream of a suction port of the compressor unit prevailing process gas pressure brings.
- the pressure setting in the drive-side second zone or chamber can be done by connecting to a suction device, which brings the pressure level of the second zone to a pressure level which is slightly below the pressure level inside the motor housing.
- the compaction device of the invention may comprise two compressor units. These can be connected in series. They can be arranged at the same end of the drive shaft or at the opposite ends of the drive shaft. Each compressor unit is assigned a gas-dynamic barrier according to the invention.
- the compressor-side chambers of the two gas-dynamic barriers can be interconnected (via a common line).
- the drive-side chambers of the two gas-dynamic barriers can be interconnected (via a common line).
- the compression device 10 comprises a first compressor unit 12.1 with an impeller 16.1 arranged in a housing 14.1.
- the compression device 10 further comprises a second compressor unit 12.2, which also has an arranged in a housing 14.2 impeller 16.2.
- the two compressor units 12.1 and 12.2 are arranged such that a drive motor 30 arranged in a hermetically or semi-hermetically sealed motor housing 32 comes to lie between them.
- the drive motor 30 drives a shaft 36 which is rotatably supported by bearings 34.
- the drive motor is of substantially known construction and therefore only shown very schematically.
- the bearings 34 are, for example, radial magnetic bearings.
- a first end 36.1 of the shaft 36 is fixedly connected to the impeller 16.1 of the first compressor unit 12.1, and a second end 36.2 of the shaft 36 is fixedly connected to the impeller 16.2 of the second compressor unit 12.2.
- the two compressor units 12.1, 12.2 are connected in series in the sense of a two-stage compression, i.
- Process gas supplied via a supply or feed line L1 to a suction opening 18.1 of the first compressor unit 12.1 is supplied after the first-stage compression via a connection line L2 connected to an outlet opening 20.1 of the first compressor unit 12.1 to an intake opening 18.2 of the second compressor unit 12.2 for the second-stage compression.
- a so-called gas-dynamic barrier GB.1, GB.2 is inventively provided in each case.
- a first gas-dynamic barrier GB.1 is arranged between the motor housing 32 and the housing 14.1 of the first compressor unit 12.1 in the region of the first end 36.1 of the shaft 36
- the second gas-dynamic barrier GB.2 is between the motor housing 32 and the housing 14.2 of the second Compressor unit 12.2 arranged in the region of the second end 36.2 of the shaft 36.
- the gas-dynamic barriers GB.1 and GB.2 are each arranged in a shaft casing 38.1 and 38.2, which serves the sheath of the drive shaft 36 in the region between the motor housing 32 and the compressor housing 14.
- Each of the gas-dynamic barriers GB.1, GB.2 comprises three gas throttling devices 40, 42, 44 arranged around the shaft 36 in their end regions 36.1, 36.2 (for better visibility in FIG FIG. 2 in section enlarged for the first gas-dynamic barrier GB.1).
- the structure of the gas-dynamic barrier is explained using the example of a barrier.
- mirror-symmetrically arranged gas-dynamic Barriers GB.1 and GB.2 are each provided with the suffixes ".1" and ".2" respectively.
- Gas throttle devices 40, 42, 44 respectively define chambers 41 and 43 located in pairs between adjacent throttle devices 40, 42 and 42, 44.
- Gas throttle device 40 compressor side or impeller side throttle device
- disposed in the direction of impeller 16 forms the central throttle device adjacent thereto 42 a first, impeller-side chamber 41.
- the arranged in the direction of the drive motor 30 and its shaft bearing 34 gas throttle 44 forms with the central throttle device 42, a second, bearing side chamber 43.
- the chambers 41, 43 are shown very schematically and are practiced so that process gas that has passed through a gas restrictor can be collected and removed in the chamber.
- the first, impeller-side chamber 41 is assigned a first discharge line L4, and the second, storage-side chamber 43 is assigned a second discharge line L5.
- the first discharge line L4 is - as described below - a pressure equalization line.
- the second discharge line L5 is - as also described below - a suction line.
- the two first discharge lines L4.1 and L4.2 of the impeller-side chambers 41.1, 41.2 of the two gas-dynamic barriers GB.1 and GB.2 are combined to form a return line L4 which is in the supply line L1 to the first compressor unit 12.1 in the region before the intake leads.
- the two second discharge lines L5.1 and L5.2 of the second chambers 43.1, 43.2 of the two gas-dynamic barriers GB.1 and GB.2 are via a suction device 50 to a common discharge line L5 merges, which leads into a region in front of the suction port 18.1 of the first compressor unit 12.1, which is a suitable point for returning the process gas in the compression process.
- a suitable location is determined by the person skilled in the art according to the pressure conditions. It is a location which is generally relatively far from the suction area of the first compressor unit and at which there is a pressure which is of the order of magnitude of the pressure provided by the suction device 50. In the presentation of the FIG. 1 this feedback at the end of the return line L5 is shown in dashed and branched lines in order to illustrate that the person skilled in the art has a choice here between several process-given possibilities.
- a first pressure P1 prevails in the supply line L1 to the intake port 18.1 of the first compressor unit 12.1.
- a second pressure (suction pressure) P2 which is slightly above the first pressure P1 or equal to the first pressure P1.
- the process gas is subject to a third pressure P3 in the region of the outlet opening 20.1 of the first compressor unit 12.1, which also rests on the intake pipe 18.2 of the second compressor unit 12.2 via the connecting line L2.
- the process gas at the outlet 20.2 of the second compressor unit 12.2 is subject to a target pressure P4.
- the pressure equalization line L4 mounted between the first impeller-side chamber 41 of each gas-dynamic barrier and the supply line L1 causes the pressure P1 to be present in each impeller-side chamber 41.1 and 41.2.
- the principle therefore is to place a pressure equalization line from the impeller-side chamber of each gas-dynamic barrier to a lowest pressure level of the areas of the overall apparatus that conduct the process gas regularly.
- This "gas leak" can be fed back to the actual process gas after being fed into the line L1.
- This can - as shown in the embodiment - in an area upstream of the intake of the first compressor unit, but also on any other (from the pressure conditions forth) made place.
- a line constriction In the presentation of the FIG. 1 is indicated at the point of recirculation of the process gas in the line L1, a line constriction. This constriction can prove advantageous in order to achieve an increase in speed in this line region according to Bernoulli in order to improve the effect of pressure equalization and process gas recirculation.
- the impeller-side first chamber 41 thus results in a pressure level P1, which is substantially lower than the process pressure P3 or P4 on the associated impeller in the region of the shaft ends 36.1, 36.2.
- the pressure on the back of the impeller of the compressor unit, ie in the region of the shaft end 36.1 or 36.2 of the drive shaft 36, is usually between the two pressures in the intake and in the discharge area (pairs of pressure P2, P3 in the first compressor or P3, P4 in the second compressor) and thus is definitely higher than the pressure P1 in the impeller-side first chamber.
- the throttling by means of the throttle devices 40.1, 42.1, 44.1 and 40.2, 42.2, 44.2 can be carried out without contact his.
- the measure according to the invention sets the same pressure P1 at each shaft end 36.1 and 36.2, even if both shaft ends are assigned a separate compressor unit. As a result, a flow through the drive unit with process gas is prevented.
- suction device 50 any known hermetically sealed suction device may be used, such as a diaphragm pump.
- an (adjustable) pressure level PM 'in the storage-side chamber 43 which is slightly below the prevailing in the drive unit pressure level PM.
- the amount of gas extracted can be returned to the compression process (via line L5) at another favorable location.
- the relationship between P1 ⁇ and P1 ultimately depends on the chosen extraction capacity and on where the return line L5 is reintroduced into the process.
- PM> P0 P0: ambient pressure, approx. 1 bar
- Typical magnitudes for the indicated pressures in the illustrated embodiment are, for example, about 29 to 30 bar for P1, 30 bar for P2, 70 bar for P3, 140 bar for P4 and 1.5 bar for PM, 1.3 bar for PM 'and 27.1 bar for P1'. It should be emphasized, however, that these pressure data relate only to one possible exemplary embodiment and serve exclusively to illustrate the mode of operation of the invention. The person skilled in the art can implement the invention with different pressure ratios depending on the field of application. Only the ranking of the pressure conditions is decisive.
- the gas-dynamic barriers GB.1, GB.2 should already be activated, i. In particular, the suction device 50 should be turned on. Even after completion of the compression process, a lag of the gas-dynamic barriers should be provided. This ensures correct functioning of the gas-dynamic barriers. In particular, it is ensured that process gas does not enter the engine area due to an incorrect pressure profile in the gas-dynamic barriers, or gases / air with particles from the engine area reach the compressor area.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP20100015717 EP2466144B1 (fr) | 2010-12-16 | 2010-12-16 | Dispositif pour comprimer un gaz de procédé |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP20100015717 EP2466144B1 (fr) | 2010-12-16 | 2010-12-16 | Dispositif pour comprimer un gaz de procédé |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP2466144A1 true EP2466144A1 (fr) | 2012-06-20 |
| EP2466144B1 EP2466144B1 (fr) | 2013-02-20 |
Family
ID=43927871
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP20100015717 Not-in-force EP2466144B1 (fr) | 2010-12-16 | 2010-12-16 | Dispositif pour comprimer un gaz de procédé |
Country Status (1)
| Country | Link |
|---|---|
| EP (1) | EP2466144B1 (fr) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3018353A1 (fr) | 2014-11-04 | 2016-05-11 | FIMA Maschinenbau GmbH | Compresseur ou turbodétendeur avec machine électrique (moteur ou générateur) refroidie par le gaz détendu de la turbomachine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2528127A1 (fr) * | 1982-06-04 | 1983-12-09 | Creusot Loire | Moto-compresseur centrifuge electrique integre a grande vitesse |
| DE20011217U1 (de) | 1999-07-16 | 2000-09-07 | Sulzer Turbo Ag Zuerich | Turboverdichter |
| EP1577561A1 (fr) | 2004-03-19 | 2005-09-21 | MAN Turbomaschinen AG Schweiz | Dispositif de circulation et de chauffage de gaz pour garnitures d' étanchéité dans compresseurs centrifuges |
| WO2009034006A1 (fr) | 2007-09-10 | 2009-03-19 | Siemens Aktiengesellschaft | Groupe compresseur |
-
2010
- 2010-12-16 EP EP20100015717 patent/EP2466144B1/fr not_active Not-in-force
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2528127A1 (fr) * | 1982-06-04 | 1983-12-09 | Creusot Loire | Moto-compresseur centrifuge electrique integre a grande vitesse |
| DE20011217U1 (de) | 1999-07-16 | 2000-09-07 | Sulzer Turbo Ag Zuerich | Turboverdichter |
| EP1577561A1 (fr) | 2004-03-19 | 2005-09-21 | MAN Turbomaschinen AG Schweiz | Dispositif de circulation et de chauffage de gaz pour garnitures d' étanchéité dans compresseurs centrifuges |
| WO2009034006A1 (fr) | 2007-09-10 | 2009-03-19 | Siemens Aktiengesellschaft | Groupe compresseur |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3018353A1 (fr) | 2014-11-04 | 2016-05-11 | FIMA Maschinenbau GmbH | Compresseur ou turbodétendeur avec machine électrique (moteur ou générateur) refroidie par le gaz détendu de la turbomachine |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2466144B1 (fr) | 2013-02-20 |
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