EP4027016A1 - Procédé de réglage de la vitesse d'un compresseur/pompe à vide - Google Patents

Procédé de réglage de la vitesse d'un compresseur/pompe à vide Download PDF

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Publication number
EP4027016A1
EP4027016A1 EP22159108.4A EP22159108A EP4027016A1 EP 4027016 A1 EP4027016 A1 EP 4027016A1 EP 22159108 A EP22159108 A EP 22159108A EP 4027016 A1 EP4027016 A1 EP 4027016A1
Authority
EP
European Patent Office
Prior art keywords
compressor
speed
vacuum element
value
vacuum
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.)
Pending
Application number
EP22159108.4A
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German (de)
English (en)
Inventor
Joeri COECKELBERGS
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.)
Atlas Copco Airpower NV
Original Assignee
Atlas Copco Airpower NV
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
Priority claimed from BE2015/5072A external-priority patent/BE1023111B1/nl
Priority claimed from BE2015/5073A external-priority patent/BE1022715B1/nl
Application filed by Atlas Copco Airpower NV filed Critical Atlas Copco Airpower NV
Priority claimed from PCT/BE2016/000004 external-priority patent/WO2016112441A1/fr
Publication of EP4027016A1 publication Critical patent/EP4027016A1/fr
Pending 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0092—Removing solid or liquid contaminants from the gas under pumping, e.g. by filtering or deposition; Purging; Scrubbing; Cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular
    • F04C2270/0525—Controlled or regulated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature

Definitions

  • This invention relates to a method for regulating the speed of a compressor/vacuum pump, said compressor/vacuum pump being provided with a pressure regulating valve mounted on an influence channel, said influence channel being in direct fluid communication with the compressor/vacuum element, said valve regulating the pressure within the compressor/vacuum element by adjusting the volume of fluid flowing between a process channel and the vacuum element relative to the difference between the pressure value within said compressor/vacuum element and a set pressure value.
  • the speed of the compressor is determined based on the pressure ratio that lies along a peak efficiency operating line of the centrifugal compressor, and is increased when this parameter is less than a minimum allowable value or decreased when this parameter is greater than or equal to a minimum allowable value.
  • Another drawback of the proposed method consists in that, because the speed is compared with a minimum allowable value, in a real operation mode, this will generate frequent speed fluctuations and accordingly a premature wear of the motor.
  • the noise generated by the compressor/vacuum system also fluctuates in intensity, generating an unwanted noise effect and an instable behavior.
  • Yet another object of the present invention is to use the motor driving the compressor/vacuum pump at its maximum capacity and without experiencing malfunctions or jeopardizing the motor's life span.
  • the present invention further aims at reducing the frequency of maintenance interventions and increasing the efficiency of a compressor/vacuum pump without increasing the complexity of the design.
  • the present invention solves at least one of the above and/or other problems by providing a method for regulating the speed of a compressor/vacuum element, said method comprising the steps of:
  • the method according to the present invention comprises the step of connecting the compressor/vacuum element to a process channel after the speed of the compressor/vacuum element reaches a preset value, the compressor/vacuum element has enough time to reach a relatively lower pressure than the value measured when the system is started, increasing the responsiveness of the system when it is connected to the process channel.
  • the system comprises a vacuum element
  • another benefit of connecting the vacuum element to the process channel after the speed within the vacuum element reaches a preset value consists in that a purge cycle can be applied at the inlet of the vacuum element before it is connected to the process channel, allowing for a system clean-up.
  • the time interval in which the pressure regulating valve keeps the vacuum element not connected to the process channel allows the vacuum element to reach lower values for the modulus of the torque which will allow the system to reach higher speeds when connected to the process channel while keeping the value of the power relatively constant. If the vacuum element would be connected to the process channel immediately after it is started, the system would reach a high speed much later because of the high value of the modulus of the torque and accordingly would be less efficient.
  • the system does not experience significant speed fluctuations that could have been caused by pressure variations. Accordingly, if the pressure at the inlet of the vacuum element is higher than the set value, the pressure regulating valve will maintain the pressure within the vacuum element relatively constant. Accordingly, the motor driving the vacuum pump is used at a relatively constant speed and at high efficiency, fact that increases its life span, and the life span of all rotating elements within the system.
  • the compressor/vacuum element is connected to the process channel after the speed of the compressor/vacuum element reaches a preset speed value, the yield of the compressor/vacuum pump is increased.
  • the present invention is further directed to a controller unit, being configured to regulate the speed of a compressor/vacuum element, the controller unit comprising:
  • the present invention is further directed to a compressor/vacuum pump being provided with a pressure regulating valve and a controller unit according to the present invention.
  • the present invention is further directed to a use of a controller unit according to the present invention for maintaining the speed of a compressor/vacuum element between a first maximum speed variance graph and a second maximum speed variance graph.
  • the present invention is directed to a method for regulating the speed of a compressor/vacuum element 1, said method comprising the steps of starting the compressor/vacuum element 1 ( Figure 1 ) and regulating the pressure within the compressor/vacuum element 1 by adjusting the volume of fluid flowing between a process channel 4 and the compressor/vacuum element 1 relative to the difference between the pressure value within said compressor/vacuum element 1 and a preset pressure value.
  • the pressure value at the level of the compressor/vacuum element 1 determines the motor driving said compressor/vacuum element 1 to work at high power. Said power being dependent on the torque and the rotational speed of at least one rotor within the compressor/vacuum element 1.
  • the torque should be understood as a measured ability of a rotating element, as of a gear, a shaft or a rotor to overcome turning resistance.
  • the modulus of the torque at the level of the at least one rotor within the compressor/vacuum element 1 is considerably high due to a high pressure at the level of the influence channel 5, and accordingly even if the motor 2 functions at high power, the rotational speed of the rotor(s) is low.
  • the modulus of the torque will gradually decrease, and accordingly the speed of the rotor(s) within the compressor/vacuum element 1 can be gradually increased by the system.
  • the method according to the present invention adjusts the speed of the compressor/vacuum element 1 such that the power of said compressor/vacuum element 1 is maintained at a relatively constant value, once the torque lowers, the speed is allowed to increase. Accordingly, the motor 2 does not experience significant variations while the pressure regulating valve 3 is adjusting the volume of fluid flowing between a process channel 4 and the compressor/vacuum element 1 and the system reaches a high yield in a minimum time interval, increasing the efficiency and decreasing the waiting time interval.
  • the motor 2 used by the compressor/vacuum element 1 is allowed to work within a high range of working parameters for a significantly long amount of time. Because of this, the motor 2 is neither overloaded nor under-loaded, increasing the efficiency of the compressor or vacuum pump and, at the same time, protecting the motor 2.
  • the method according to the present invention allows the motor 2 driving the compressor/vacuum element 1 to work within the high range of working parameters throughout the entire functioning interval when a request for compressed air or vacuum is encountered.
  • a compressor/vacuum element 1 is part of a compressor or vacuum pump which can be selected from a group comprising: a single screw compressor, a double screw compressor, a scroll compressor, a turbo compressor, a single toothed vacuum pump, a double toothed vacuum pump, a single screw vacuum pump, a double screw vacuum pump, a scroll vacuum pump, a turbo vacuum pump, a rotary vane vacuum pump, etc.
  • a compressor or vacuum pump which can be selected from a group comprising: a single screw compressor, a double screw compressor, a scroll compressor, a turbo compressor, a single toothed vacuum pump, a double toothed vacuum pump, a single screw vacuum pump, a double screw vacuum pump, a scroll vacuum pump, a turbo vacuum pump, a rotary vane vacuum pump, etc.
  • Each of the above identified types of compressor/vacuum elements 1 can be oil injected or oil free.
  • a compressor/vacuum element 1 comprises at least a rotor enclosed within a chamber.
  • the rotational speed of the at least one rotor of the compressor/vacuum element 1 is hereinafter referred to as the speed of the compressor/vacuum element 1.
  • the method further comprises the step of providing a pressure regulating valve 3 on an influence channel (not shown), said influence channel being in direct fluid communication with the compressor/vacuum element 1, said valve 3 regulating the pressure within the compressor/vacuum element 1 by adjusting the volume of fluid flowing between a process channel 4 and the compressor/vacuum element 1 relative to the difference between the pressure value within said compressor/vacuum element 1 and a preset pressure value.
  • the method comprises the step of providing a pressure regulating valve 3 on the influence channel, and because the compressor/vacuum element 1 is connected to the process channel 4 after the speed of the compressor/vacuum element 1 reaches a preset speed value, the motor 3 has a sufficient amount of time to reach a state in which the modulus of the torque is low enough to allow the motor 3 to considerably increase the rotational speed of the rotor(s).
  • the pressure regulating valve 3 is preferably kept in a closed state or in an approximately closed state during the time interval in which the compressor/vacuum element 1 reaches said preset speed.
  • the compressor element can be connected to the process channel 4 immediately after the compressor element is started.
  • the pressure regulating valve 3 ( Figure 4 or Figure 5 ) is comprising a housing V5 delimiting a first chamber V6 and a second chamber V7 separated by a wall V8.
  • the first chamber V6 comprises a movable element V9 that defines a first cavity V6a and a second cavity V6b fluidly sealed from each other.
  • the first cavity V6a comprising an inlet channel V10 connected to a first supply of a fluid, and means for exerting a force on the movable element V9.
  • said wall V8 acts as a separation between the second chamber V7 and the second cavity V6b of the first chamber V6.
  • the housing V5 can for example comprise a lid V5a.
  • the inlet channel V10 is provided centrally on the lid V5a opposite from the second cavity V6b.
  • the second chamber V7 is in direct communication with a process channel 4 of a supply of a fluid and further comprises therein a valve body V11 having a distal end V11a extending into the first cavity V6a of the first chamber V6 and a proximal end V11b, said valve body V11 being movable between an initial closed state in which the proximal end V11b is pushed against a sealing flange V12 and a second, opened state, in which a fluid flows between the process channel 4 and the influence channel 5 of the compressor/vacuum element 1.
  • housing V5 can be made by one integral part or several separate parts.
  • the valve body V11 is slidably mounted in the wall V8 in such a way as to prevent a fluid flow between the second chamber V7 and the second cavity V6b of the first chamber V6.
  • the sealing flange V11 is forming an opening towards the influence channel 5 of the compressor/vacuum element 1.
  • valve body V11 is mounted within a guide V13, in this case in the shape of a pipe-shaped element, comprising a seal V14 and a bushing V15 mounted at the level of the guide V13 to eliminate the risk of encountering any residual fluid flow between the second cavity V6b of the first chamber V6 and the second chamber V7.
  • valve body V11 comprises a fluid channel V16 extending through said valve body V11 allowing a fluid flow between the first cavity V6a and the influence channel 5 of the compressor/vacuum element 1. Accordingly, the pressure within the first cavity V6a will have the same value as the pressure value of the fluid at the influence channel 5 of the compressor/vacuum element 1.
  • the movable element V9 can for example be in the shape of a membrane, or a piston, or a metal plate.
  • said means for exerting a force on the movable element V9 can be in the shape of: a spring, a piston or a metal plate such as a steel plate for which exerting a force on the movable element V9 is intrinsic in the material properties.
  • the force generated on the movable element V9 can either be compressive or tensile.
  • the means for exerting a force on the movable element V9 comprise a spring V17 positioned in the first cavity V6a and pushing on said movable element V9.
  • the spring V17 can be, for example, positioned centrally within said cavity V6a of the first chamber V6 and pushing on a centrally positioned surface on the movable element V9.
  • the housing V5 comprises a collar V18 around the inlet channel V10 for positioning said spring V17 and keeping it in a stable central position.
  • the inlet channel V10 can be positioned concentrically with respect to said collar V18.
  • the inlet channel V10 can be positioned on the lateral sides of the lid V5a.
  • the spring V17 is generating in an initial closed state a force F 1 of less than 3000N (Newton), more preferably the spring V17 is generating a force F 1 of less than 2000N, even more preferably, the spring V17 is generating a force F 1 of 1000N or less.
  • a force F 1 of less than 3000N Newton
  • the spring V17 is generating a force F 1 of less than 2000N, even more preferably, the spring V17 is generating a force F 1 of 1000N or less.
  • the spring V17 is generating in an initial closed state a force F1 in the range from 500 - 2000N.
  • the proximal end V11b pushing against the sealing flange V12 is, in this example, in the shape of a frustum of a cone with rounded edges having the base with the biggest diameter at the end facing the second chamber V7 and the base with the smallest diameter at the end facing influence channel 5 of the compressor/vacuum element 1.
  • the proximal end V11b has a hollow cavity V19 at the end facing the influence channel 5 of the compressor/vacuum element 1.
  • the pressure regulating valve 3 preferably comprises two guiding elements V20 and V21 for guiding the movable element V9: the first guiding element V20 being positioned in the second cavity V6b of the first chamber V6 between the movable element V9 and the wall V8 separating the first chamber V6 and the second chamber V7, and the second guiding element V21 being positioned in the first cavity V6a of the first chamber V6, between the movable element V9 and the spring V17.
  • the movable element V9 can be in the shape of a piston, or a metal plate.
  • the movable element V9 is a membrane fixed in the housing V5 of the first chamber V6.
  • the first guiding element V20 is in the shape of a cylindrical block with a hollow carving created on the side facing the wall V8 for receiving the guide V13 therein.
  • the first guiding element V20 is in the shape of a disk having a hole therein for receiving the valve body V11.
  • the second guiding element V21 can be in the shape of a disk against which, on one side the spring V17 is resting, and has a hole therein for receiving the valve body V11.
  • the guiding element V21 comprises a circumferential rim extending towards the lid V5a.
  • the second cavity V6b of the first chamber V6 further comprises an inlet channel V22 fluidly connecting said second cavity V6b to a supply of a first fluid at pressure P 1 .
  • the first fluid is preferably air and P 1 is preferably the atmospheric pressure.
  • the inlet channel V10 of the first cavity V6a of the first chamber V6 further comprises means for sealing said first cavity V6a from the fluid flow at pressure P 1 .
  • said means for sealing said first cavity 6a from the fluid flow is a valve 10.
  • the system comprises a vacuum pump
  • said vacuum pump is preferably subjected to a purge cycle before being connected to the process channel 4 for cleaning the system of impurities.
  • the influence channel is integrally comprised or in direct fluid communication with the inlet channel of the vacuum pump.
  • the pressure regulating valve 3 when the vacuum element is subjected to a purge cycle, the pressure regulating valve 3 is maintained in a closed state. Once the vacuum element is connected to an external process, the pressure regulating valve 3 will control the volume of fluid flowing between the process channel 4 and the vacuum element as will be further explained.
  • valve body V11 slidably moves against the force generated by the spring V17 in the direction of the first chamber V6, lifting the proximal end V11b of the valve body V11 from the sealing flange V12) and allowing a fluid flow between the process channel 4 and the inlet channel of the vacuum element.
  • the pressure value at which the proximal end V11b of the valve body V11 is lifted from the sealing flange V12 and/or is pushed against the sealing flange V12 is adjusted depending on the application at which the vacuum pump is connected to.
  • the proximal end V11b is pressing against the sealing flange V12 and a flow of fluid flows through the fluid channel V16.
  • the valve 10 closes and no fluid flows through the fluid channel V16, the pressure regulating valve 3 entering in a modulating state.
  • the pressure P element and the pressure value within the process channel 4 is influenced in such a state by the variable speed drive unit or inverter, part of the driving means of the vacuum pump.
  • said driving means can be a combustion engine or an electrical motor, a turbine such as a water turbine or a steam turbine, or the like.
  • the driving means can be directly driven or can be driven by an intermediate transmission system like a coupling or a gear box.
  • the vacuum pump according to the present invention uses a pressure regulating valve 3 as described above, a permanent flow of fluid throughout the valve body V8 can be maintained during the purge cycles, increasing the volume of fluid flowing throughout the vacuum element and increasing the reliability of such purge cycles. Accordingly the time intervals allocated for performing the purge cycles can be reduced.
  • the pressure regulating valve 3 is of a type as described in patent application BE 2015/5072 , which is herein incorporated by reference in its entirety.
  • valves having a different structure can be used as well.
  • the system will preferably reduce said speed to a set speed before connecting the vacuum element to the external process.
  • Said set speed can be any value of the speed selected in the interval 500 - 4600 rpm (revolutions per minute).
  • the set speed can be selected as being approximately 3500 rpm.
  • said valve 10 is connected to a supply of a purge gas through a nozzle (not shown).
  • the nozzle of valve 10 has a diameter much bigger than the nozzle at the level of the distal end V11a of the pressure regulating valve 3. Because of this, when the valve 10 is opened, a fluid flow is kept from the valve 10, through the pressure regulating valve 3 and into the influence channel 5 of the vacuum element 1.
  • the system when the vacuum element 1 is subjected to a purge cycle, the system will function at a relatively high speed for a predetermined time interval in order to achieve a preset temperature.
  • Said predetermined time interval can be selected for example between 1 minute and 3 hours, depending on the requirements of each process.
  • Said preset temperature can be selected between 60 - 105 0 C, like for example, the preset temperature can be 80°C, or said temperature can be 103 0 C.
  • the system maintains the pressure within the vacuum element 1 at a desired value.
  • a value can be any value selected between 5 - 1000 mbar, depending on the requirements on the process channel 4.
  • the valve 10 when the vacuum element 1 is connected to the external process, the valve 10 is brought in a closed state, such that the vacuum element 1 influences the pressure within the process channel 4 with a maximum yield.
  • the speed of the compressor/vacuum element 1 is regulated according to a pre-determined first maximum speed variance graph 6 ( Figure 2 ).
  • the speed of the compressor/vacuum element 1 is regulated according to a pre-determined second maximum speed variance graph 7.
  • the method further comprises a step in which a minimum allowed speed 8 for the compressor/vacuum element 1 is determined, as the limit until which the compressor/vacuum element 1 is maintained within nominal working parameters.
  • said minimum allowed speed 8 is different than the pre-determined first maximum speed variance graph 6 and/or the second maximum speed variance graph 7.
  • the system according to the present invention does not use a linear speed limit, but a first maximum speed variance graph 6 and/or a second maximum speed variance graph 7, the frequency of speed variations of the motor 2 driving the compressor/vacuum element 1 is kept to a minimum. Accordingly, when the compressor/vacuum element 1 experiences pressure variations, and because the power is kept at a relatively constant value, the rotational speed of the rotor(s) will also suffer variations. If the system would apply a single maximum speed variance graph, the motor 2 would experience oscillations each time the rotational speed of the rotor(s) would reach a higher or lower value than the one of the limit. This effect would increase the chances for the motor 2 to experience malfunctions and will also create fluctuations of sound intensity, limiting the applications in which the system could be used.
  • the system will not adjust the speed of the rotor(s) immediately when a change in pressure is sensed, but when the value of the speed is equal with or lower than and/or equal with the values on the border line of the second maximum speed variance graph 7 and/or the first maximum speed variance graph 6.
  • the speed when the system experiences a decrease in pressure, the speed is adjusted after the second maximum variance graph 7 and/or when the system experiences an increase in pressure, the speed is adjusted after the first speed variance graph 6.
  • the first maximum speed variance graph 6 and the second maximum speed variance graph 7 determine a hysteresis type of behavior for the speed of the compressor/vacuum element 1. Because of this, the method according to the present invention is maintaining the motor 2 in a high range of functional parameters, keeping the yield of the system high.
  • the method further comprises the steps of: keeping the speed of the compressor/vacuum element 1 relatively constant until the preset pressure value of the pressure regulating valve 3 is reached; and after said pressure value is reached: increasing the speed of the compressor/vacuum element 1 in accordance with the second maximum speed variance graph 7; and/or decreasing the speed of the compressor/vacuum element 1 in accordance with the first maximum speed variance graph 6.
  • the pressure value at the level of the compressor/vacuum element 1 is maintained at a relatively constant value until optimal working parameters are reached. Because the pressure at the level of the compressor/vacuum element 1 is kept constant, the power of the motor 2 is also kept at a relatively constant value.
  • the fluid channel V10 is preferably disconnected from the supply of fluid, causing the valve 3 to be brought into an open state and the pressure within the process channel 4 to be directly influenced by said compressor/vacuum element 1 at a maximum yield.
  • the pressure within the vacuum element 1 is maintained at a relatively a constant value, until a preset pressure value is reached at the level of the influence channel 5.
  • the preset pressure value is less than 600 mbar, more preferably less than 500 mbar and most preferably is approximately 400 mbar.
  • the preset pressure value can be selected depending on either the pressure value at which the vacuum element 1 is starting, or the requirements on the process channel 4, or the pressure difference between the pressure value at which the vacuum element 1 is starting and the desired pressure at the level of the process channel 4.
  • the pressure value at which the vacuum element 1 is starting is atmospheric pressure, and the preset pressure value is selected as being approximately 400 mbar, the system encounters a pressure difference of approximately 600 mbar, which is sufficient for maintaining oil injection within an oil injected vacuum pump.
  • the motor will drive the rotor(s) at a predetermined starting speed and will gradually increase the speed until the set speed is reached and the vacuum element 1 is then connected to the process channel 4, as previously explained.
  • said predetermined starting speed is not higher than the maximum speed of the motor reachable at the preset pressure value.
  • Said predetermined starting speed can be selected as any value comprised between 600 and 4600 rpm, depending on the compressor/vacuum element 1 used.
  • said speed can be for example and not limiting to, approximately 3500 rpm.
  • the second maximum speed variance graph 7 does not reach a minimum preset speed value 8 of the compressor/vacuum element 1. Accordingly, the compressor or vacuum pump can be maintained within optimal working parameters.
  • the method according to the present invention applies the step of measuring the current passing through the motor windings; and comparing said measured current with a maximum allowed current. In one embodiment according to the present invention, if the measured current is lower than the maximum allowed current then the speed of the motor is increased according to the first maximum speed variance graph 6 or the second maximum speed variance graph 7.
  • the speed of the motor is decreased according to the first maximum speed variance graph 6 or the second maximum speed variance graph 7.
  • the inverter, part of the motor 2 is not experiencing any trips.
  • Such an effect is undesired because it can cause the system to reset which would mean a delay for reaching the desired pressure value on the process channel 4 and accordingly a reduced efficiency of the compressor of vacuum pump.
  • Another effect of performing such a step consists in that the motor 2 of the compressor or vacuum pump is kept within optimal parameters, without the risk to be overloaded. Accordingly, the yield of the system can be maintained within the high range throughout the complete functioning cycle without endangering the life span of the motor 2.
  • the first maximum speed variance graph 6 or the second maximum speed variance graph 7 is translated to lower values ( Figure 3 ) and/or the minimum preset speed value 8 of the compressor/vacuum element 1 is translated to higher values. Furthermore, if the current passing through the motor windings is lower than the maximum allowed current, the first maximum speed variance graph 6 or the second maximum speed variance graph 7 is translated to higher values and/or the minimum preset speed value 8 of the compressor/vacuum element 1 is translated to lower values.
  • the method according to the present invention does not influence the speed of the compressor/vacuum element 1 directly, but the first maximum speed variance graph 6 and/or the second maximum speed variance graph 7 and/or the minimum present allowed speed 8 value which create the speed limits between which the compressor/vacuum element 1 is allowed to function.
  • the compressor or vacuum pump translates the first maximum speed variance graph 6 and/or the second maximum speed variance graph 7 and/or the minimum preset speed value 8 allowed when the current measured through the motor windings reaches a value higher than a maximum allowed current plus a tolerance selected between 0.1 - 2 A (Ampere).
  • the controller unit is measuring the pressure on the influence channel at a sampling rate selected between 100 - 400 msec (milliseconds), more preferably the controller unit is measuring the pressure on the influence channel 5 at a sampling rate of 200 msec.
  • the controller unit comprises a pressure controller, a speed controller and a limiting function.
  • the pressure controller compares the measured pressure value within the process channel 4 with the requested pressure value and calculates the required speed of the element to reach the requested pressure value.
  • the requested pressure value should be understood as the pressure value needed at the level of the external process and selected by the user of the compressor/vacuum element 1.
  • the limiting function determines two speed values for each pressure value measured: one maximum speed value corresponding to the value found on the borderline of the first maximum speed variance graph 6 or the second maximum speed variance graph 7 if a virtual line parallel to the speed axis is drawn through that measured pressure value, and a second minimum value found on the minimum preset speed value 8 graph, determined at the intersection between said virtual line and the minimum preset speed value 8 graph.
  • the limiting function further compares the requested speed with the two determined maximum and minimum speed values. If said requested speed is higher than the maximum speed value, then a set speed is preferably adjusted to said maximum speed value.
  • the set speed is preferably adjusted to said minimum value.
  • the limiting function preferably does not influence the set speed which will be equal to the requested speed.
  • the speed controller compares the set speed with the measured speed and adjusts the speed of the motor to match the set speed.
  • the controller unit preferably measures the current passing through the motor windings and compares said measured value with a predetermined maximum value. If the value of the measured current is higher than the predetermined maximum value, the controller unit preferably modifies the maximum speed value and/or the minimum speed value.
  • the controller unit if the measured current is higher than the predetermined maximum value, the controller unit preferably translates the maximum speed value to lower values and/or the minimum speed value to higher values.
  • a translation of a value should be understood as a lower or higher value found on a virtually drawn line on a graph, said virtually drawn line being parallel with one of the axis, in this case with the speed axis, and being drawn as striking through the measured value.
  • controller unit is an electronic module capable of modifying a state of at least one component of the compressor/vacuum element 1.
  • the controller unit influences the state of a component in a particular way such as for example and not limiting to: increases or decreases the speed of at motor of the compressor/vacuum element 1, or connects the compressor/vacuum element 1 to the process channel 4, the controller unit then generates a signal, for example an electrical signal, that changes the state of the at least one component.
  • the controller unit further compares said measured current value with a predetermined minimum value. If said measured value is lower than the predetermined minimum value, the controller unit translates the maximum speed value to higher values and/or the minimum speed value to lower values.
  • the controller unit modifies the maximum speed value and/or the minimum speed value of the compressor/vacuum element 1 even if the measured speed is not higher than said maximum speed value or lower than the minimum value. Because of this a compressor/vacuum element 1 using a controller unit according to the present invention can function at high values of the modulus of the torque at both high and low speeds.
  • the controller unit considers a tolerance between 0.1 - 2 A (Ampere) before it modifies the maximum speed value and/or the minimum speed value.
  • the controller unit performs such a comparison, the speed of the compressor/vacuum element 1 is not directly and immediately modified as is the case of existing systems, but the maximum speed value and/or the minimum speed value are being modified, which results in less speed fluctuations for the compressor/vacuum element 1 and accordingly less noise fluctuations.
  • the speed limitation S1 ( Figure 2 ) is determined by the mechanical limitation of the compressor/vacuum element 1, such as the limitation imposed by any of the following elements: motor 2, inverter, switching frequency of the inverter, bearings, materials used for rotor(s) or casing, noise limit, or the like.
  • the speed limitation S2 is determined by the pressure regulating valve 3.
  • first maximum speed variance graph 6, the second maximum speed variance graph 7, the speed limitation S1 and/or the speed limitation S2 can be selected depending on the compressor/vacuum element 1 used and/or the requirements on the influence channel 5.
  • the present invention is further directed to a controller unit, being configured to regulate the speed of a compressor/vacuum element 1.
  • said controller unit can be an integral part of the compressor or vacuum pump or can be an external module communicating with said compressor or vacuum pump.
  • the controller unit comprises a data communication interface for receiving parameters relating to the current of a motor driving the compressor/vacuum element 1.
  • the controller unit further comprises means of comparing the data received from said motor 2 with a predetermined current value saved within a database.
  • Said means of comparing the data received from said motor 2 with a predetermined current value can be for example a processor mounted at the level of the controller unit or at an external location.
  • the compressor or vacuum pump comprises a pressure regulating valve 3 ( Figure 4 or Figure 5 ) intended to be mounted on an influence channel 5, said influence channel 5 being in direct fluid communication with the compressor/vacuum element 1.
  • said valve 3 is preferably regulating the pressure within the vacuum element 1 by adjusting the volume of fluid flowing between a process channel 4 and the vacuum element 1 relative to the difference between the pressure value within said vacuum element 1 and a preset pressure value.
  • the preset pressure value can be selected depending on the requirements for the pressure value at the level of the process channel 4.
  • a value can be any selected value comprised within the interval, and not limiting to: 200-800 mbar.
  • the preset pressure value is approximately 400 mbar.
  • the pressure regulating valve 3 maintains the pressure value within the vacuum element 1 at a relatively constant value before the pressure value on the influence channel 5 reaches a preset pressure value. Accordingly, the torque at the level of the vacuum element 1 decreases and the speed of the vacuum element 1 is able to increase, without jeopardizing the life span of the motor 2 and without experiencing any significant fluctuations in speed and/or sound intensity.
  • the vacuum element 1 After said preset pressure value is reached, the vacuum element 1 reaches nominal functioning parameters and the controller unit preferably comprises means for connecting the vacuum element 1 to a process channel 4. Because of this, the vacuum element 1 is able to reach a relatively high speed and yield until it is connected to the process channel 4.
  • said means for connecting the compressor/vacuum element 1 to a process channel 4 comprises an electrical signal generated by said controller unit.
  • the system comprises a compressor element 1
  • said compressor element 1 can be connected to the process channel 4 immediately after the system is turned on.
  • the controller unit further comprises a data communication channel for sending a control signal to said motor 2 for increasing or decreasing the rotational speed of the motor 2 if the received current parameters are not between a predetermined maximum and/or a minimum current value.
  • said data communication channel can be a wired or a wireless data channel.
  • the rotational speed of the motor 2 is decreased according to a first pre-determined maximum speed variance graph 6 and/or increased according to a second pre-determined maximum speed variance graph 7.
  • the second maximum speed variance graph 7 and the first maximum speed variance graph 6 determine a hysteresis type of behavior for the speed of the compressor/vacuum element ( Figure 2 ). Because of this the frequency of speed and noise intensity fluctuations are reduced.
  • the speed of said compressor/vacuum element 1 is relatively high and the torque is relatively low, such that the pressure at the level of the process channel 4 is influenced with a maximum yield.
  • the controller unit preferably reduces the speed of the compressor/vacuum element 1 and allows for said pressure value to be maintained. If the pressure value at the level of the process channel 4 changes, then the controller unit according to the present invention regulates the speed of the compressor/vacuum element 1 according to the first maximum speed variance graph 6 and/or the second maximum speed variance graph 7, as previously described.
  • the controller unit comprises means for translating the first maximum speed variance graph 6 to lower values and/or translating the minimum preset speed value 8 of the compressor/vacuum element 1 to higher values, if the current passing through the motor windings is higher than the maximum allowed current. Furthermore, the controller unit comprises means for translating the first maximum speed variance graph 6 to higher values and/or translating the minimum preset speed value 8 of the compressor/vacuum element 1 to lower values if the current passing through the motor windings is lower than the maximum allowed current.
  • said means comprises an algorithm performed by said processor.
  • the controller unit according to the present invention does not influence the speed of the compressor/vacuum element 1 directly, but the first maximum speed variance graph 6 and/or the second maximum speed variance graph 7 and/or the minimum present speed value 8, which create the speed limits between which the compressor/vacuum element 1 is allowed to function.
  • the controller unit further comprises means of applying a tolerance selected between 0.1 - 2 A (Ampere) before translating the first maximum speed variance graph 6 and/or the second maximum speed variance graph 7 and/or the minimum preset speed value 8.
  • a tolerance selected between 0.1 - 2 A (Ampere) before translating the first maximum speed variance graph 6 and/or the second maximum speed variance graph 7 and/or the minimum preset speed value 8.
  • the controller unit when the current passing through the motor windings is higher or lower than a maximum allowed current, the controller unit translates only one value of the speed of the first maximum variance graph 6 and/or of the minimum preset speed value 8. Because of this, a lower computational power is needed.
  • the present invention is further directed to a compressor or vacuum pump being provided with a pressure regulating valve 3 and a controller unit according to the present invention.
  • the present invention is further directed to a use of a controller unit according to the present invention for maintaining the speed of a compressor/vacuum element 1 between a first maximum speed variance graph 6 and a second maximum speed variance graph 7.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP22159108.4A 2015-01-15 2016-01-07 Procédé de réglage de la vitesse d'un compresseur/pompe à vide Pending EP4027016A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US201562103761P 2015-01-15 2015-01-15
US201562103723P 2015-01-15 2015-01-15
BE2015/5072A BE1023111B1 (nl) 2015-01-15 2015-02-11 Inlaatklep en vacuümpomp voorzien van een dergelijke inlaatklep.
BE2015/5073A BE1022715B1 (nl) 2015-01-15 2015-02-11 Werkwijze voor het regelen van de snelheid van een compressor/vacuümpomp
PCT/BE2016/000004 WO2016112441A1 (fr) 2015-01-15 2016-01-07 Procédé pour commander la vitesse d'un compresseur/pompe à vide
EP16712187.0A EP3245403B1 (fr) 2015-01-15 2016-01-07 Procédé pour commander la vitesse d'un compresseur/pompe à vide

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EP4027016A1 true EP4027016A1 (fr) 2022-07-13

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EP16712187.0A Active EP3245403B1 (fr) 2015-01-15 2016-01-07 Procédé pour commander la vitesse d'un compresseur/pompe à vide

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2116754A (en) * 1982-03-05 1983-09-28 Hoerbiger Ventilwerke Ag Suction control valve for rotary compressors
US4664601A (en) * 1984-07-25 1987-05-12 Hitachi, Ltd. Operation control system of rotary displacement type vacuum pump
US4699570A (en) * 1986-03-07 1987-10-13 Itt Industries, Inc Vacuum pump system
EP0338764A2 (fr) * 1988-04-22 1989-10-25 The BOC Group plc Pompes à vide
WO2004038222A1 (fr) * 2002-10-24 2004-05-06 The Boc Group Plc Ameliorations en matiere de pompes seches
WO2007019651A2 (fr) * 2005-08-17 2007-02-22 Atlas Copco Airpower, Naamloze Vennootschap Dispositif ameliore pour l'adaptation du debit d'un compresseur mobile de type a vis a injection d'huile
US20120164017A1 (en) * 2010-12-24 2012-06-28 Hitachi Industrial Equipment Systems Co., Ltd. Oil Free Screw Compressor
US20130323082A1 (en) 2012-05-31 2013-12-05 Andrew C. Rosinski Anti-surge speed control

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2116754A (en) * 1982-03-05 1983-09-28 Hoerbiger Ventilwerke Ag Suction control valve for rotary compressors
US4664601A (en) * 1984-07-25 1987-05-12 Hitachi, Ltd. Operation control system of rotary displacement type vacuum pump
US4699570A (en) * 1986-03-07 1987-10-13 Itt Industries, Inc Vacuum pump system
EP0338764A2 (fr) * 1988-04-22 1989-10-25 The BOC Group plc Pompes à vide
WO2004038222A1 (fr) * 2002-10-24 2004-05-06 The Boc Group Plc Ameliorations en matiere de pompes seches
WO2007019651A2 (fr) * 2005-08-17 2007-02-22 Atlas Copco Airpower, Naamloze Vennootschap Dispositif ameliore pour l'adaptation du debit d'un compresseur mobile de type a vis a injection d'huile
US20120164017A1 (en) * 2010-12-24 2012-06-28 Hitachi Industrial Equipment Systems Co., Ltd. Oil Free Screw Compressor
US20130323082A1 (en) 2012-05-31 2013-12-05 Andrew C. Rosinski Anti-surge speed control

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EP3245403A1 (fr) 2017-11-22

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