EP3234370A1 - Compression unit for high and low pressure services - Google Patents

Compression unit for high and low pressure services

Info

Publication number
EP3234370A1
EP3234370A1 EP15801858.0A EP15801858A EP3234370A1 EP 3234370 A1 EP3234370 A1 EP 3234370A1 EP 15801858 A EP15801858 A EP 15801858A EP 3234370 A1 EP3234370 A1 EP 3234370A1
Authority
EP
European Patent Office
Prior art keywords
unit
compression unit
driver
overhung
shaft
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
Application number
EP15801858.0A
Other languages
German (de)
French (fr)
Other versions
EP3234370B1 (en
Inventor
Stefano Bresciani
Lorenza Sassolini
Nicola Banchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nuovo Pignone Technologie SRL
Original Assignee
Nuovo Pignone SpA
Nuovo Pignone SRL
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nuovo Pignone SpA, Nuovo Pignone SRL filed Critical Nuovo Pignone SpA
Publication of EP3234370A1 publication Critical patent/EP3234370A1/en
Application granted granted Critical
Publication of EP3234370B1 publication Critical patent/EP3234370B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04012—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling
    • F25J3/04018—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling of main feed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04012—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling
    • F25J3/04024—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling of purified feed air, so-called boosted air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04109—Arrangements of compressors and /or their drivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04109—Arrangements of compressors and /or their drivers
    • F25J3/04145—Mechanically coupling of different compressors of the air fractionation process to the same driver(s)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04151—Purification and (pre-)cooling of the feed air; recuperative heat-exchange with product streams
    • F25J3/04163—Hot end purification of the feed air
    • F25J3/04169—Hot end purification of the feed air by adsorption of the impurities
    • F25J3/04175—Hot end purification of the feed air by adsorption of the impurities at a pressure of substantially more than the highest pressure column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/20—Integrated compressor and process expander; Gear box arrangement; Multiple compressors on a common shaft

Definitions

  • the present invention relates to a compression unit for supplying a complete pressure service to a plant, the single compression unit being capable of supplying high and low pressure services.
  • a main drawback of the prior art is the complexity of the overall architecture and configuration of the compression units, this leading to bulky apparatus.
  • each of such compression units comprising a dedicated driver and associated impellers which increase the overall dimensions of the units.
  • a first embodiment of the present invention relates to a single compression unit for supplying a complete compression service consisting of high and low pressure gas to a process plant.
  • the compression unit is configured to supply high and low pressure gas flow with a simple architecture and with a configuration which reduces overall dimensions and weight of the unit, and also has an increased efficiency with respect to the state of the art.
  • impellers having a large diameter can process a high flow rate but work with reduced rotational speed and, therefore, a l imited compression ratio.
  • the term "low" pressure here indicates rating values within a typical range comprised between 1 50 and 300, while the impeller can process a flow rate which could be comprised in a range between 50.000 and 200.000 m 3 per hour.
  • a typical speed value of an impeller processing said flow rates is 5.000 to 1 .800 rounds per minute thus indicated for a direct coupled solution .
  • high pressure here ind icates typical rating values comprised between 300 and 2500, with an inlet pressure value between 3 and 50 bar for the first impeller.
  • the impeller processes low flow rates, typically less than 50.000 m 3 per hour.
  • FIG. 1 is a schematic representation of one embodiment of the compression unit according to the present invention.
  • FIG. 2 is a schematic representation of the compression unit of the present invention according to a different embodiment.
  • Such compression unit 1 comprises a single driver 2 associated with two driver shaft-ends preferably projecting apart from said driver 2 along opposite directions, a first driver shaft end 3 and a second driver shaft end 4.
  • the driver 2 divides the compression unit into two sides; on one side, a first unit 1 0 is operatively connected to the first driver shaft-end 3, while a second unit 20 is operatively connected to the second driver shaft-end 4.
  • said first unit 10 comprises an impeller 1 1
  • said second unit comprises a bull gear 21 in an integrally geared-compressor arrangement.
  • said impeller 1 1 of said first unit 1 0 is an overhung impeller directly connected to the first driver shaft-end 3, preferably by means of a flanged connection or a flexible coupl ing .
  • an overhung impeller is an impeller having no bearing/s on the opposite side with respect to the driver, thus all bearing/s of the overhang impeller are arranged between the impeller and the driver.
  • the impeller 1 1 of the first unit is the "low" pressure source unit: typical values of flow rate processed by the overhung impeller are about 50.000 m 3 per hour, with an inlet pressure value of around 1 bar and an outlet pressure value of about 2 or 3 bar.
  • the bull gear 21 is preferably connected by means of a flanged connection, or a flexible coupling, to said second driver shaft- end 4.
  • said second unit 20 comprises the bull gear 21 which drives at least one driven shaft 22, 23 through pinions in a typical integrally geared-compressor arrangement.
  • the bull gear 21 comprises two or more driven shafts, for example a first driven shaft 22 and a second driven shaft 23, which are drivingly connected to the bull gear 21 by means of respectively pinions.
  • Said pinions are teethed wheels having a diameter smaller than the diameter of the bull gear. The pinions are engaged directly on the bull gear so that the rotation of the latter produces the rotation of pinions.
  • Each of said driven shafts supports at its opposite ends an overhung impeller 22a, 22b, 23a, 23b.
  • the two driven shafts 22, 23 are configured to rotate at different rotary speed.
  • Typical flow rate values for the second unit 20 are about 50.000 and 200.000 m 3 per hour, with casing rating varying between ANSI 300 and 1 500.
  • the driver 2 drives the single overhung impeller 1 1 connected to said first driver shaft 3.
  • the same driver 2 drives the bull gear 21 which comprises preferably two driven shafts 22, 23, the first driven shaft 22 supports at its ends a couple of first overhung impellers 22a, 22b, the second driven shaft 23 supports at its ends a couple of second overhung impellers 23a, 23b.
  • the first overhung impellers 22a, 22b and the second overhung impellers 23a, 23b are fluidly connected so that the gas flow passes through the first overhung impellers 22a, 22b of the first driven shaft 22 and then through the second overhung impellers of the second driven shaft 23, thus forming a first multi stage compression unit for compressing a small flow rate up to high pressure values.
  • This configuration is illustrated in Figure 1 by means of dashed lines indicated with the reference number 40 which represent the hydraulic connection between the impellers.
  • the outlet of the overhung impeller 1 1 of the first unit 10 is fluidly connected to the inlet of the second unit 20, thus forming a second multi stage compression unit.
  • This configuration is represented in Figure 1 by means of dashed line 30 which represent the hydraul ic connection between the units.
  • the first unit 1 0 provides the gas flow rate to the second unit 20 thus obtaining a compression unit apt to elaborate large flow rates with an high overall compression rate.
  • the first unit 1 0 comprises an overhung impeller 1 1 which is connected to said first driver shaft 3 by means of a gear arrangement, instead that flanged to said first driver shaft.
  • the first unit 1 0 comprises a beam compressor. Said beam compressor may be flanged to said first driver shaft 3 or, alternatively, the beam compressor may be connected to said first driver shaft 3 by means of a gear arrangement.
  • Typical beam compressor casing rating varies from ANSI 600 to API 1 5000.
  • the inlet of the beam compressor may be hydraulically connected to the output of the bull gear 21 of the second unit 20.
  • the first unit 1 0 receives the flow rate coming from the output of the second unit 20, thus forming a third multi stage compression unit allowing to reach h igher compression rates.
  • the hydraulic connection between the first 1 0 and the second 20 unit is represented in Figure 2 by means of the dashed line 50.
  • the compression unit according to the present invention therefore solves the drawbacks afflicting the prior art.
  • One of the results achieved with the compression unit according to the present invention is to reduce the footprint of the apparatus, with an extremely versatile configuration .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Compression unit (1) for supplying high and low pressure services to a plant comprising a single driver (2) associated with two driver shaft-ends (3, 4) projecting apart from said driver (2), a first driver shaft end (3) and a second driver shaft end (4), a first unit (10) being operatively connected to the first driver shaft-end (3) and a second unit (20) being operatively connected to the second driver shaft-end (4).

Description

COMPRESSION UN IT FOR H IGH AND LOW PRESSURE SERVICES
DESCRIPTION
The present invention relates to a compression unit for supplying a complete pressure service to a plant, the single compression unit being capable of supplying high and low pressure services.
Within a process plant, to supply high pressure gas and low pressure gas several different units are usually provided to process different flow rates at different pressure values.
A main drawback of the prior art is the complexity of the overall architecture and configuration of the compression units, this leading to bulky apparatus.
In fact, usually separate units are used to provide gas at different pressure values to a process plant, each of such compression units comprising a dedicated driver and associated impellers which increase the overall dimensions of the units.
SUMMARY
A first embodiment of the present invention relates to a single compression unit for supplying a complete compression service consisting of high and low pressure gas to a process plant. The compression unit is configured to supply high and low pressure gas flow with a simple architecture and with a configuration which reduces overall dimensions and weight of the unit, and also has an increased efficiency with respect to the state of the art.
In order to better clarify what is to be intended with the terms "high" and "low" pressure reference to the compressor flanges rating, accord ing to ANSI, will be done hereafter. As known in the art, technical limits exist while designing an impeller. One of these l imits is represented by the peripheral speed of the impeller.
It is known in the art that impellers having a large diameter can process a high flow rate but work with reduced rotational speed and, therefore, a l imited compression ratio. In order to give typical values, the term "low" pressure here indicates rating values within a typical range comprised between 1 50 and 300, while the impeller can process a flow rate which could be comprised in a range between 50.000 and 200.000 m3 per hour.
A typical speed value of an impeller processing said flow rates is 5.000 to 1 .800 rounds per minute thus indicated for a direct coupled solution .
The term "high" pressure here ind icates typical rating values comprised between 300 and 2500, with an inlet pressure value between 3 and 50 bar for the first impeller. In order to reach very high compression rates, the impeller processes low flow rates, typically less than 50.000 m3 per hour.
Further details and specific embodiments will refer to the attached drawing, in which : - Figure 1 is a schematic representation of one embodiment of the compression unit according to the present invention;
- Figure 2 is a schematic representation of the compression unit of the present invention according to a different embodiment.
DETAILED DESCRIPTION The following description of exemplary embodiments refers to the accompanying drawings. The following detailed description does not limit the invention . Instead, the scope of the invention is defined by the appended claims.
Reference throughout the specification to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment is included in at least one embodiment of the subject matter disclosed . Thus, the appearance of the phrases "in one embodiment" or "in an embodiment" in various places throughout the specification is not necessarily referring to the same embodiment. Further, the particular features, structures or characteristics may be combined in any suitable manner in one or more embodiments.
Such compression unit 1 comprises a single driver 2 associated with two driver shaft-ends preferably projecting apart from said driver 2 along opposite directions, a first driver shaft end 3 and a second driver shaft end 4.
In order to better describe the preferred embodiment of the compression unit according to the present invention, it can be considered that the driver 2 divides the compression unit into two sides; on one side, a first unit 1 0 is operatively connected to the first driver shaft-end 3, while a second unit 20 is operatively connected to the second driver shaft-end 4.
According to a first preferred embodiment of the present invention, said first unit 10 comprises an impeller 1 1 , and said second unit comprises a bull gear 21 in an integrally geared-compressor arrangement. More preferably, according to the first embodiment said impeller 1 1 of said first unit 1 0 is an overhung impeller directly connected to the first driver shaft-end 3, preferably by means of a flanged connection or a flexible coupl ing . According to the present invention, an overhung impeller is an impeller having no bearing/s on the opposite side with respect to the driver, thus all bearing/s of the overhang impeller are arranged between the impeller and the driver. In this case, the impeller 1 1 of the first unit is the "low" pressure source unit: typical values of flow rate processed by the overhung impeller are about 50.000 m3 per hour, with an inlet pressure value of around 1 bar and an outlet pressure value of about 2 or 3 bar.
On the other side, the bull gear 21 is preferably connected by means of a flanged connection, or a flexible coupling, to said second driver shaft- end 4.
According to the first embodiment shown in Figure 1 , said second unit 20 comprises the bull gear 21 which drives at least one driven shaft 22, 23 through pinions in a typical integrally geared-compressor arrangement. Preferably, in order to obtain higher outlet pressure values, the bull gear 21 comprises two or more driven shafts, for example a first driven shaft 22 and a second driven shaft 23, which are drivingly connected to the bull gear 21 by means of respectively pinions. Said pinions are teethed wheels having a diameter smaller than the diameter of the bull gear. The pinions are engaged directly on the bull gear so that the rotation of the latter produces the rotation of pinions.
Each of said driven shafts supports at its opposite ends an overhung impeller 22a, 22b, 23a, 23b. According to an embodiment of the present invention, the two driven shafts 22, 23 are configured to rotate at different rotary speed. Typical flow rate values for the second unit 20 are about 50.000 and 200.000 m3 per hour, with casing rating varying between ANSI 300 and 1 500.
According to the first embodiment of the compression unit 1 shown in Figure 1 , the driver 2 drives the single overhung impeller 1 1 connected to said first driver shaft 3.
On the other side of the compression unit 1 , the same driver 2 drives the bull gear 21 which comprises preferably two driven shafts 22, 23, the first driven shaft 22 supports at its ends a couple of first overhung impellers 22a, 22b, the second driven shaft 23 supports at its ends a couple of second overhung impellers 23a, 23b.
According to the scheme of Figure 1 , the first overhung impellers 22a, 22b and the second overhung impellers 23a, 23b are fluidly connected so that the gas flow passes through the first overhung impellers 22a, 22b of the first driven shaft 22 and then through the second overhung impellers of the second driven shaft 23, thus forming a first multi stage compression unit for compressing a small flow rate up to high pressure values. This configuration is illustrated in Figure 1 by means of dashed lines indicated with the reference number 40 which represent the hydraulic connection between the impellers.
According to a second embodiment of the present invention, the outlet of the overhung impeller 1 1 of the first unit 10 is fluidly connected to the inlet of the second unit 20, thus forming a second multi stage compression unit. This configuration is represented in Figure 1 by means of dashed line 30 which represent the hydraul ic connection between the units.
In this configuration, the first unit 1 0 provides the gas flow rate to the second unit 20 thus obtaining a compression unit apt to elaborate large flow rates with an high overall compression rate. According to a third embodiment of the present invention not shown in the drawings, the first unit 1 0 comprises an overhung impeller 1 1 which is connected to said first driver shaft 3 by means of a gear arrangement, instead that flanged to said first driver shaft. According to a fourth embodiment of the present invention shown in Figure 2, the first unit 1 0 comprises a beam compressor. Said beam compressor may be flanged to said first driver shaft 3 or, alternatively, the beam compressor may be connected to said first driver shaft 3 by means of a gear arrangement. Typical beam compressor casing rating varies from ANSI 600 to API 1 5000.
When the first unit 1 0 comprises a beam compressor, the inlet of the beam compressor may be hydraulically connected to the output of the bull gear 21 of the second unit 20. According to this arrangement, the first unit 1 0 receives the flow rate coming from the output of the second unit 20, thus forming a third multi stage compression unit allowing to reach h igher compression rates. The hydraulic connection between the first 1 0 and the second 20 unit is represented in Figure 2 by means of the dashed line 50. The compression unit according to the present invention therefore solves the drawbacks afflicting the prior art.
One of the results achieved with the compression unit according to the present invention is to reduce the footprint of the apparatus, with an extremely versatile configuration .

Claims

CLAIMS:
1 . Compression unit (1 ) for supplying high and low pressure services to a plant comprising a single driver (2) associated with two driver shaft- ends (3, 4) projecting apart from said driver (2), a first driver shaft end (3) and a second driver shaft end (4), a first unit (1 0) being directly operatively connected to the first driver shaft-end (3) and a second unit (20) being operatively connected to the second driver shaft-end (4), wherein said first unit is an overhung impeller, and said second unit (20) is an integrally geared-compressor arrangement comprising a bull gear (21 ) and a plurality of pinions engaged with the bull gear (21 ), wherein the diameter of bull gear (21 ) is larger than the diameter of pinions.
2. Compression unit (1 ) according to claim 1 , wherein said overhung impeller (1 1 ) of said first unit (10) is an impeller connected to said first driver shaft-end (3) by means of a gear arrangement.
3. Compression unit (1 ) according to one or more of the preceding claims, wherein said bull gear (21 ) is connected by means of a flanged connection to said second driver shaft-end (4).
4. Compression unit (1 ) according to one or more of the preceding claims, wherein integrally geared-compressor arrangement comprises at least one driven shaft (22, 23).
5. Compression unit (1 ) according to claim 4, wherein at the opposite ends of said at least one driven shaft (22, 23) are provided overhung impellers (22a, 22b, 23a, 23b).
6. Compression unit (1 ) according to claim 4 or 5, wherein said bull gear (21 ) comprises two driven shaft (22, 23), a first driven shaft (22) and a second driven shaft (23), each of said first (22) and second (23) driven shaft being provided at its ends with a couple of overhung impellers, respectively first overhung impellers (22a, 22b) and second overhung impellers (23a, 23b).
7. Compression unit (1 ) according to one or more of the preceding claims, wherein said first overhung impellers (22a, 22b) and second overhung impellers (23a, 23b) are fluidly connected thus forming a first multi stage compression unit.
8. Compression unit (1 ) according to one or more of the preceding claims, wherein an outlet of said first unit (1 0) is fluidly connected to an inlet of said second unit (20) thus forming a second multi stage compression unit.
9. Compression unit (1 ) according to one or more of the preceding claims, wherein the inlet of said first unit (1 0) is fluidly connected to the outlet of said second unit (20) thus forming a third multi stage compression unit.
1 0. Compression unit (1 ) according to one or more of the preceding claims, wherein said driver shaft-ends (3, 4) are the ends of a single driver shaft.
1 1 . Compression unit (1 ) according to one or more of the preceding claims, wherein the two driven shafts (22,23) are configured to rotate at different rotary speeds.
EP15801858.0A 2014-12-16 2015-11-30 Compression unit for high and low pressure services Active EP3234370B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI20142145 2014-12-16
PCT/EP2015/078072 WO2016096386A1 (en) 2014-12-16 2015-11-30 Compression unit for high and low pressure services

Publications (2)

Publication Number Publication Date
EP3234370A1 true EP3234370A1 (en) 2017-10-25
EP3234370B1 EP3234370B1 (en) 2024-02-21

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP15801858.0A Active EP3234370B1 (en) 2014-12-16 2015-11-30 Compression unit for high and low pressure services

Country Status (6)

Country Link
US (1) US20170356451A1 (en)
EP (1) EP3234370B1 (en)
JP (1) JP2018503766A (en)
CN (1) CN107429702A (en)
DK (1) DK3234370T3 (en)
WO (1) WO2016096386A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201800000620A1 (en) * 2018-01-08 2019-07-08 Nuovo Pignone Tecnologie Srl AMMONIA PRODUCTION PLANT
EP3617519A1 (en) * 2018-08-27 2020-03-04 Siemens Aktiengesellschaft Radially compressor rotor, radial compressor, gear-driven compressor
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EP3234370B1 (en) 2024-02-21
WO2016096386A1 (en) 2016-06-23
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US20170356451A1 (en) 2017-12-14
CN107429702A (en) 2017-12-01
DK3234370T3 (en) 2024-04-08

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