EP3511569A1 - Procédé de compression d'un fluide et sous-ensemble compresseur - Google Patents

Procédé de compression d'un fluide et sous-ensemble compresseur Download PDF

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Publication number
EP3511569A1
EP3511569A1 EP18020012.3A EP18020012A EP3511569A1 EP 3511569 A1 EP3511569 A1 EP 3511569A1 EP 18020012 A EP18020012 A EP 18020012A EP 3511569 A1 EP3511569 A1 EP 3511569A1
Authority
EP
European Patent Office
Prior art keywords
pump
pump speed
compressor
fluid
speed
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.)
Withdrawn
Application number
EP18020012.3A
Other languages
German (de)
English (en)
Inventor
Robert Adler
Sascha Dorner
Christoph Nagl
Sarah Gruber
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.)
Linde GmbH
Original Assignee
Linde GmbH
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 Linde GmbH filed Critical Linde GmbH
Priority to EP18020012.3A priority Critical patent/EP3511569A1/fr
Publication of EP3511569A1 publication Critical patent/EP3511569A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids

Definitions

  • the invention relates to a method for compressing a fluid and a compressor assembly, in particular for carrying out the method according to the invention.
  • hydraulically driven compressors also known as piston compressors
  • piston compressors have a movable piston in the compressor (also referred to as separator piston), which separates a first compressor chamber from a second compressor chamber.
  • a fluid provided in the first compressor room may be compressed by introducing a hydraulic fluid into the second compressor room by means of a hydraulic fluid pump (for example, an axial piston machine, a radial piston machine or a gear pump) and moving the piston by the introduced hydraulic fluid.
  • a hydraulic fluid pump for example, an axial piston machine, a radial piston machine or a gear pump
  • a first aspect of the invention relates to a method for compressing a fluid, wherein the fluid is provided in a first compressor space, which is separated from a second compressor chamber by means of a movable piston of a compressor, wherein a hydraulic fluid is introduced into the second compressor chamber by means of a pump, so that the piston moves and the fluid in the first compressor space is compressed while reducing the volume of the first compressor space, wherein a pump speed of the pump during the compression of the fluid controlled so, in particular reduced, that the mathematical product of the pump speed and a Pump torque of the pump remains constant or substantially constant, the pump torque depends on the prevailing pressure in the first compressor chamber.
  • the pump torque is the moment which the compressor opposes to a motor driving the pump. This depends (in particular linear) on the back pressure of the hydraulic fluid in the second compressor chamber, wherein the back pressure of the hydraulic fluid in equilibrium corresponds to the pressure of the fluid in the first compressor chamber.
  • the pump torque which is increased when the backpressure increases, is compensated for by a reduction in the pump speed, so that during the method the pump power or the delivery rate of the pump always remains constant.
  • the compressor delivery rate during a compressor stroke ie a movement of the piston in the compressor
  • the engine speed and thus the pump speed is always kept at a maximum (for the relevant backpressure), whereby the maximum power of the engine at the relevant speed point is kept at a maximum.
  • the compaction time can thus be shortened, in particular in hydraulically driven systems. This is possible with only a small additional cost compared to systems with constant speed.
  • the method according to the invention allows the pump to be operated at a maximum pump speed at the beginning of a compressor stroke with a relatively low backpressure. This allows for faster compression than in prior art processes where the pump speed is maintained at a constant lower level throughout the compressor stroke.
  • the fluid is in particular a gas.
  • the fluid may also be formed by a liquid-gas mixture.
  • the pump has a pumping speed rotating or moving component or assembly for compressing the fluid.
  • the pump may be formed as axial piston machine, radial piston machine or gear pump.
  • the pump speed is linearly reduced with time during the compression of the fluid. In this way, with an increase in the back pressure according to the adiabatic equation (assuming isentropic compression), at least approximately a constant product of pump speed and pump torque can always be achieved.
  • the pump speed is kept constant in a precompression phase, the pump speed being reduced in a compression phase following the precompression phase, in particular linear with respect to time.
  • the pressure of the fluid increases only insignificantly according to isentropic compression. Therefore, it is possible at this stage to keep the pump speed constant in this phase.
  • the subsequent compression phase a greater increase in the back pressure, which is compensated by the reduction of the pump speed.
  • the pump speed in the precompression phase corresponds to a maximum pump speed of the pump.
  • the pump is configured during normal use to be operated at the maximum pump speed at most. That is, when the maximum pump speed is exceeded, the pump may e.g. may be damaged, it may be e.g. pose a safety risk to the user or the delivery rate of the pump may e.g. If the maximum speed is exceeded, this can not be increased by design.
  • the pump speed in the compression phase is reduced to a minimum pump speed.
  • the minimum pump speed corresponds in particular to that speed at which, at a maximum pressure (in particular compression end pressure) of the fluid in the first compressor chamber, the (constant) product results from pump torque and pump speed.
  • a freewheel valve is opened, in particular when reaching the minimum speed, so that the load is taken from the pump.
  • the pump speed is maintained at the minimum pump speed in a stop phase subsequent to the compression phase.
  • the pump speed is increased to the maximum pump speed before the precompression phase in a start phase, in particular linear with respect to the time.
  • the pump speed in the starting phase is first increased to the minimum speed, wherein the pump speed is kept constant after reaching the minimum pump speed, and wherein the pump speed is then increased, in particular linear with respect to the time, to the maximum pump speed.
  • the pump speed is set on the basis of a predetermined speed curve over time.
  • the pressure of the fluid in the first compressor space is determined or measured, the pump speed being set as a function of the determined or measured pressure.
  • the determination of the pressure may e.g. by direct pressure measurement in the first compression chamber or alternatively by measuring the pressure of the hydraulic fluid in the second compression chamber or in a hydraulic fluid line downstream of the pump.
  • a second aspect of the invention relates to a compressor assembly, in particular for carrying out the method according to the first aspect, comprising a compressor having a piston movable in the compressor, which can be arranged in the compressor so that it separates a first compressor chamber from a second compressor chamber, a hydraulic fluid reservoir for receiving a hydraulic fluid communicable with the second compressor chamber, a pump configured to deliver the hydraulic fluid from the hydraulic fluid reservoir and introduce it into the second compressor chamber so that the piston moves and in the first compressor chamber compressed fluid, wherein the compressor assembly comprises a controller configured to control a pump speed of the pump during the compression of the fluid so that the mathematical product of the pump speed and a pump torque of the pump constant or remains substantially constant, wherein the pump torque depends on the pressure prevailing in the first compressor chamber.
  • the pump has a pumping speed rotating or moving component or assembly for compressing the fluid.
  • the pump may be formed as axial piston machine, radial piston machine or gear pump.
  • control device is configured to adjust the pump speed based on a predetermined time pump speed curve.
  • This speed curve can be stored for example in a memory unit of the control device.
  • the compressor assembly has at least one pressure sensor for determining or measuring the pressure of the fluid in the first compressor chamber, wherein the controller is configured to adjust the pump speed as a function of the determined or measured pressure.
  • Fig. 1 shows a schematic representation of a compressor assembly 1 according to the invention in longitudinal section.
  • the compressor assembly 1 has a compressor 3 with a piston 30, which separates a first compressor chamber 31 of the compressor 3 for receiving a fluid F from a second compressor chamber 32 of the compressor 3 for receiving a hydraulic fluid H.
  • the compressor assembly 1 further comprises a hydraulic fluid H partially filled hydraulic fluid reservoir 9 and a pump 11 which is configured to convey the hydraulic fluid H from the hydraulic fluid reservoir 9 and to introduce via a hydraulic valve 6 in the second compressor chamber 32 of the compressor 3.
  • the piston 30 is movably arranged in the compressor 3, so that the piston 30 in the illustration of Fig. 1 can move to the right when the hydraulic fluid H is introduced into the second compressor chamber 32.
  • the volume of the second compressor chamber 32 increases and the volume of the first compressor chamber 31 decreases correspondingly, so that fluid F in the first compressor chamber 31 is at such a movement of the piston 30 due to the reduction of the volume of the first Compressor space 31 is compressed.
  • the second compressor chamber 32 is further connected via the hydraulic valve 6 and a hydraulic return valve 8 to the hydraulic fluid reservoir 9, so that upon movement of the piston 30 to the left as shown in FIG Fig. 1 (For example, when the first compressor chamber 31 is filled with the fluid F) the hydraulic fluid H displaced from the second compressor chamber 32 by means of the piston 30 can flow back into the hydraulic fluid container 9 via the hydraulic valve 6 and the hydraulic return valve 8.
  • a broken line represents an exemplary level of the hydraulic fluid H in the hydraulic fluid reservoir 9. Further, the arrows indicate the flow direction of the hydraulic fluid.
  • the pump 11 is designed in particular as an axial piston machine, radial piston machine or gear pump, thus has rotating components with a pump speed n (which can be given in the unit s -1 , for example), the delivery rate of the pump 11 is greater, the higher the pump speed n is.
  • pump 11 (or its rotating components) are driven by a motor 10.
  • the motor 10 thus sets the said rotating components of the pump 11 in rotary motion.
  • the motor 10 is connected to a control device 12, so that by means of the control device 12, the speed of the motor 10 and thus the pump speed n of the pump 11 is controllable.
  • hydraulic fluid H is introduced by means of the pump 11 from the hydraulic fluid reservoir 9 in the second compressor chamber 32 of the compressor 3, so that the piston 30 as shown in the Fig. 1 moved to the right, whereby the volume V of the first compressor chamber 31 is reduced and thus the fluid contained in the first compressor chamber 31 F is compressed.
  • the FIG. 2 shows a common time / pump speed and time / pressure diagram.
  • the abscissa of the graph represents the time t and the ordinate of the graph represents the pump speed n of the pump 11 with respect to a pump speed curve n (M) and the pressure p of the fluid F with respect to a pressure curve p (V, ⁇ ) first compressor chamber 31 of the compressor 3 during the process according to the invention as a function of time t.
  • speed curve n (M) shows that in the example of the method shown here, the pump speed n is controlled so that during a start phase t start the pump speed n is first increased linearly from zero to a minimum pump speed n min (minimum operating speed) (wherein said linear increase is also referred to as a launch ramp or first ramp), then held constant for a period of time at the minimum pump speed n min (also referred to as a first plateau) and subsequently linearly increased to the maximum pump speed n max (also referred to as second ramp).
  • minimum pump speed n min minimum operating speed
  • n max also referred to as second ramp
  • the precompression of the fluid F follows, the pump speed n constantly corresponding to the maximum pump speed n max (also referred to as the second plateau). It can be seen from the pressure curve p (V, ⁇ ) that the pressure p in the first compression chamber 31 remains virtually constant during the precompression phase t predverd .
  • the pump speed n during a compression phase t Verd in particular proportional to the pressure prevailing in the first compression chamber 31 back pressure p, is reduced, so that there is an at least approximately linear relationship between time and pump speed n for the compression phase t Verd .
  • the product of pump torque M and pump speed n remains constant according to the invention, so that in each case the maximum pump output at the current counter-pressure results.
  • the minimum pump speed n min (the minimum pump speed also depends on manufacturer-specific information, these usually relate to a rotation-induced minimum lubrication), which occurs simultaneously with the achievement of the maximum back pressure p max in the first compressor chamber 31 is, for example by opening a Freewheel valve, the load taken from the pump 11. Subsequently, the pump speed n is kept constant in a stop phase t stop at the minimum pump speed n min . After the end of the stop phase t Stop , the pump speed n is reduced to 0 in a further ramp.
  • V 1 denotes the maximum volume of the first compressor chamber 31 of the compressor 3 and V2 denotes the maximum volume of the first compressor chamber 31 minus the number of pump revolutions (N pump ) multiplied by the volumetric displacement of the pump 11 (V pump ).
  • p 1 denotes the back pressure of the fluid F in the first compression space 31 at the volume V 1 and p 2 denotes the back pressure of the fluid F in the first compression space 31 at the volume V2.
  • p ⁇ V ⁇ const
  • V 2 V 1 - N pump ⁇ V pump
  • the individual times or phases t start , t predverd , t Verd and t stop can be calculated.
  • the control of the pump speed n can, for example, based on a predetermined speed curve (such as in Fig. 2 shown).
  • a predetermined speed curve such as in Fig. 2 shown.
  • the back pressure of the hydraulic fluid H or the pressure of the fluid F in the first compressor chamber 31 may be measured during the process, with the pump speed n being set as a function of the measured pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP18020012.3A 2018-01-10 2018-01-10 Procédé de compression d'un fluide et sous-ensemble compresseur Withdrawn EP3511569A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18020012.3A EP3511569A1 (fr) 2018-01-10 2018-01-10 Procédé de compression d'un fluide et sous-ensemble compresseur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18020012.3A EP3511569A1 (fr) 2018-01-10 2018-01-10 Procédé de compression d'un fluide et sous-ensemble compresseur

Publications (1)

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EP3511569A1 true EP3511569A1 (fr) 2019-07-17

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EP18020012.3A Withdrawn EP3511569A1 (fr) 2018-01-10 2018-01-10 Procédé de compression d'un fluide et sous-ensemble compresseur

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29816811U1 (de) * 1998-09-21 1999-10-07 Wiedemann Helmut System zur Speicherung von brennbaren Kraftgasen wie z.B. Erdgas und Wasserstoff in einem volumenveränderlichen Speicher zum Zwecke der Betankung von mobilen Behältern für Kraftfahrzeugantriebe
US20150013829A1 (en) * 2013-07-12 2015-01-15 Whirlpool Corporation Multi-stage home refueling appliance and method for supplying compressed natural gas
DE102013016696A1 (de) * 2013-10-08 2015-04-09 Linde Aktiengesellschaft Speichereinrichtung, Gas-Speichereinheit und Verfahren zur zumindest teilweisen Befüllung oder Entleerung einer Gas-Speichereinheit
EP2908044A2 (fr) * 2014-01-17 2015-08-19 Michael Feldmann Procédé et installations pour une station de gaz destinés à la distribution de volume optimisé de carburant gazeux à des utilisateurs mobiles

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29816811U1 (de) * 1998-09-21 1999-10-07 Wiedemann Helmut System zur Speicherung von brennbaren Kraftgasen wie z.B. Erdgas und Wasserstoff in einem volumenveränderlichen Speicher zum Zwecke der Betankung von mobilen Behältern für Kraftfahrzeugantriebe
US20150013829A1 (en) * 2013-07-12 2015-01-15 Whirlpool Corporation Multi-stage home refueling appliance and method for supplying compressed natural gas
DE102013016696A1 (de) * 2013-10-08 2015-04-09 Linde Aktiengesellschaft Speichereinrichtung, Gas-Speichereinheit und Verfahren zur zumindest teilweisen Befüllung oder Entleerung einer Gas-Speichereinheit
EP2908044A2 (fr) * 2014-01-17 2015-08-19 Michael Feldmann Procédé et installations pour une station de gaz destinés à la distribution de volume optimisé de carburant gazeux à des utilisateurs mobiles

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