WO2016041026A1 - Method for controlling an oil-injected compressor device - Google Patents

Method for controlling an oil-injected compressor device Download PDF

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Publication number
WO2016041026A1
WO2016041026A1 PCT/BE2015/000046 BE2015000046W WO2016041026A1 WO 2016041026 A1 WO2016041026 A1 WO 2016041026A1 BE 2015000046 W BE2015000046 W BE 2015000046W WO 2016041026 A1 WO2016041026 A1 WO 2016041026A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
temperature
compressor element
outlet
cooler
Prior art date
Application number
PCT/BE2015/000046
Other languages
French (fr)
Inventor
Wim Moens
Andreas Mathias Jonas SEGHERS
Original Assignee
Atlas Copco Airpower, Naamloze Vennootschap
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 Atlas Copco Airpower, Naamloze Vennootschap filed Critical Atlas Copco Airpower, Naamloze Vennootschap
Priority to MX2017003608A priority Critical patent/MX2017003608A/en
Priority to RU2017113137A priority patent/RU2681402C2/en
Priority to NZ730649A priority patent/NZ730649A/en
Priority to ES15801983T priority patent/ES2834392T3/en
Priority to UAA201702380A priority patent/UA121483C2/en
Priority to KR1020177010215A priority patent/KR102069957B1/en
Priority to CA2960700A priority patent/CA2960700C/en
Priority to AU2015318763A priority patent/AU2015318763B2/en
Priority to CN201580050147.4A priority patent/CN107002683B/en
Priority to BR112017005500-7A priority patent/BR112017005500B1/en
Priority to US15/511,760 priority patent/US10480512B2/en
Priority to EP15801983.6A priority patent/EP3194784B1/en
Priority to JP2017515172A priority patent/JP6594964B2/en
Publication of WO2016041026A1 publication Critical patent/WO2016041026A1/en

Links

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
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/021—Control systems for the circulation of the lubricant
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • 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
    • F04C2270/18—Pressure
    • F04C2270/185—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
    • F04C2270/195—Controlled or regulated

Definitions

  • the present invention relates to & method for controlling an oil-injected compressor device.
  • the invention is intended for an oil- injected compressor device with at least one compressor element with an inlet for gas to be compressed and an outlet for compressed gas whereby the compressor device is provided with an oil circuit with an oil separator with an input that, is connected to the outlet of the compressor element and an output to which a consumer compressed gas network can be connected, whereby this oil separator comprises a pressure vessel in which the oil separated from the compressed gas is received and from which oil can be guided to a cooler and can then be injected into the compressor element, whereby this cooler is cooled by a coolant that is guided through the cooler by means of a fan or pump.
  • the speed of the compressor element cannot fail without limit, but is limited to a specific lower limit. This means that the flow rate cannot fall without limit either . If the flow must be further reduced, it could be chosen to apply an inlet throttle valve.
  • a butterfly valve for example that is affixed in the inlet pipe. This will ensure that the inlet pipe is partly closed off so that the gas flow supplied and thus also the flow rate delivered is reduced.
  • the compressor element and the fan that is used to cool the oil in the cooler both continue at a constant speed driven by a thermal engine, even when no cooling is required if the oil is entirely or partially diverted through the bypass pipe, which brings about an energy loss.
  • control to prevent condensation is limited to the distribution of the quantity of oil that is guided through the cooler and the quantity of oil that is injected directly into the compressor element without cooling.
  • Another method is known from GB 2.394.G25 whereby a thermostatic valve ensures that the temperature of the injected oil does not fall below a set value and whereby in addition a thermostatically controlled control valve is applied that controls the quantity of injected oil as a function of the temperature of the injected oil. Both controls are done simultaneously and independently frora one another and other controls.
  • the purpose of the present invention is to provide a solution to at least one of the aforementioned and other disadvantages.
  • the subject of the present invention is a method for controlling an oil -injected compressor device with at least one compressor element with an inlet for gas to be compressed and an outlet, for compressed gas and with a variable speed controller, whereby the compressor device is provided with an oil circuit with an oil separator with an input that is connected to the outlet of the compressor element and an output to which a compressed gas consumer network can be connected, whereby this oil separator comprises a pressure vessel in which the oil separated from the compressed gas is received and from which oil can be guided to a cooler and can then be injected into the compressor element, whereby this cooler is cooled by a coolant that is guided through the cooler by means of a fan or pump, with the characteristic that a bypass pipe for oil is provided across the cooler, whereby the method consists of determining the temperature at the outlet of the compressor element and when this determined temperature is less than a preset value, the following steps are taken successively:
  • the temperature at the outlet of the compressor element is determined again and, when this temperature at the outlet is still less than the preset value, the oil is driven through the bypass pipe to the compressor element or an increasing proportion of the oil is driven through the bypass pipe to the compressor element as long as the maximum quantity of oil has not beer, reached;
  • An advantage is that such a method will prevent the temperature of the compressor device becoming too low because the method will bring about a gradual reduction of the cooling capacity of the oil circuit, by implementing the various successive controls step by step. In this way the formation of condensate can be prevented, for example.
  • Such a method is very useful for application in a compressor element that comprises a controllable inlet throttle valve.
  • An additional advantage is that the fan or the pump is first switched off or adjusted when the cooling capacity roust be reduced, such that less energy is consumed.
  • Another advantage is that only in a last step is the oil supply reduced, so that the lubrication of the compressor element by the oil is not jeopardised.
  • the method according to the invention provides a control of. the temperature at the outlet to ensure that this temperature does not become higher than a 3et value, whereby the following steps are taken successively:
  • the temperature at the outlet of the compressor element is determined again and, when this temperature at the outlet is still higher than the set value, the fan or pump is switched on or its speed is increased.
  • figure 1 schematically shows an oil-injected compressor device for application in a method according to the invention
  • figure 2 schematically shows a possible embodiment of the inlet throttle valve.
  • the oil ⁇ injected compressor device 1 shown in figure 1 essentially comprises a compressor element 2, in this case of the known screw type with a housing 3 in which two enmeshed helical rotors 4 are driven by means of a variable speed controller 5.
  • the compressor element 2 can also be of a different type, such as a turbocompressor element, without departing from the scope of the invention.
  • this variable speed controller 5 is a motor 6 whose speed is variable.
  • the housing 3 is provided with an inlet 7 that is connected to an inlet pipe 8 for the supply of gas to be compressed, such as air or another gas or mixture of gases.
  • gas to be compressed such as air or another gas or mixture of gases.
  • the housing 3 is provided with an outlet 9 that is connected to an cutlet pipe 10 *
  • the outlet pipe 10 is connected, via a pressure vessel 11 of an oil separator 12 and a pressure pipe 13 connected thereto, to a downstream consumer network for the supply of various pneumatic tools or similar that are not shown here.
  • the compressor installation 1 is provided with an oil circuit 14 to inject oil 15 from, the pressure vessel 11, via a feed pipe 16 and injection pipe 17 into the compressor element 2 for the cooling and if applicable the lubrication and/or seal between the rotors 4 mutually and the rotors 4 and the housing 3.
  • the oil 13 that is injected can hereby pass through a cooler 18 to cool the oil 15 from the pressure vessel 11.
  • the cooler 18 is provided with & fan 19 to ensure the cooling, although it is not excluded that instead of using cooling air for the cooling, a .liquid coolant is used char is guided through the cooler by means of a pump.
  • the fan 19 is a controllable fan, i.e. the speed of the tan 19 can be controlled.
  • the oil 13 ⁇ 4 can also be guided to the compressor element 2 through a bypass pipe 20, whereby in this case the oil 15 does not pass via the cooler 18.
  • a three-way valve 22 is provided at the branch 21 of the bypass pipe 20, upstream from the cooler IS, in order to control the quantity of oil. 19 that can flow through the bypass pipe 20 and through the cooler 18.
  • throttle valve 24 is provided in the inlet pipe 8.
  • an inlet valve for the inlet throttle valve 24 that comprises a housing that contains an aperture 25 in the form of a number of strips 26 that are movably affixed in the housing, whereby the strips 26 are movable between a closed position whereby strips 26 close off the inlet pipe 8 and an open position whereby the stripe 26 are turned away from the inlet pipe 8.
  • a possible embodiment of such an inlet valve with an aperture 25 is shown in figure 2 . It is clear that such an inlet valve can be constructed in many different ways.
  • an advantage of such an inlet valve is that the stripe 26 can be completely turned away from the inlet pipe 8, and thus the inlet 7, such that in the open state the aperture 25 does not form an impediment for the supply of air to be compressed. This is in contrast to a butterfly valve for example, which even in a fully open state will partially block the passage of the inlet pipe 8.
  • the oil-injected compressor device i is also provided with means 27a to determine the temperature ? at the outlet 9 of the compressor element 2 and with means 27b to determine the pressure p in the pressure pipe 13.
  • These means 2?a and 2?b respectively can be a temperature sensor or a pressure sensor fox example.
  • a controller 28 is also previcted that ensures the control of the motor 6, the fan 1&, the three-way valve 22, the injection valve 23 in the injection pips 17 and the inlet throttle valve 24.
  • the controller 28 is also connected to the temperature sensor and the pressure sensor.
  • the compressor element 2 will compress gas that is supplied via the inlet pipe 8.
  • oil 15 will be injected into the compressor eiercent 2. This oil 15 is injected into the compressor element 2. via the feed pipe 16 and the injeer, ion pipe 17 under the influence of the pressure in the pressure vessel 1 2.
  • the compressed gas is guided to the pressure vessel 11 from the oil separator 12 via the outlet pipe 10.
  • the oil 15 that is present in the compressed gas is separated in the oil separator 12 and received in the pressure vessel 11.
  • the compressed gas that is now free of oil 15 is brought to a consumer network via the pressure pipe 13.
  • the pressure p downstream from the outlet 29 of the oil separator 12 is determined by the pressure sensor.
  • the signal from the pressure sensor is read by the controller 28.
  • the controller 28 will control the compressor device I, more specifically the raotor 6 and the inlet throttle valve 24, such that the required flow rate is delivered by the compressor element 2 to maintain the pressure p downstream front the outlet 23 of the oil separator 12 at a desired value pset.
  • the controller 28 When the pressure p is less than the desired value pset in other words when the consumption of compressed gas is greater than the flow rate delivered by the compressor device 1, the controller 28 will ensure that the delivered flow rate becomes greater by gradually opening the inlet throttle valve 24 in the first instance, if it is throttling the inlet 9 at that time, until the pressure p is again equal to the desired vaiue ⁇ asa.
  • the controller 28 When the pressure p is still less than the desired value pset when the inlet throttle valve 24 is fully open, the controller 28 will gradually increase the speed of the compressor element 2 so chat the flow rate delivered by the compressor element will rise until the pressure p downstream from the outlet 29 of the oil separator 21 is equal to the desired value pset. This means that at this time the demand for compressed gas is equal to the flow rate delivered.
  • the controller 28 When the pressure p is greater than a desired value pset. in ether words when the consumption of compressed gas is less than the flow rate delivered by the compressor device 1, the controller 28 will ensure that the delivered flow rate becomes smaller by gradually reducing the speed of the compressor element 2 in the first; instance so that the flow rate delivered by the compressor element 2 will fall until the pressure p is again equal to the desired value pset.
  • the controller 28 will, gradually close the inlet throttle valve 24 until the pressure p downstream from the outlet 25 of the oil separator 12 is equal to the desired value pset.
  • the inlet throttle valve 24 will be closed to a minimum opening. When the pressure p is still too high, the controller 28 will stop the compressor element. The inlet throttle valve 24 will then also fully close to prevent an air and oil flow in the opposite direction.
  • the compressor element 2 When the compressor device 1 is started up again, the compressor element 2 will operate at a minimum speed arid the inlet throttle valve 24 will be open to a minimum.
  • the controller 28 will then gradually open the inlet throttle valve 24 in order to limit the starting torque for the motor 6. Only if the inlet throttle valve 24 has been fully opened will the speed of the compressor element be increased.
  • An advantage of such a control of the pressure p at the outlet 29 is that it will lead r.o the inlet throttle valve 24 being kept open as much as possible. After all, when the flow rate must be reduced/ the speed of the compressor element 2 will first be reduced before adjusting the inlet throttle valve 24, and when the flow rate must be increased the inlet throttle valve 24 will first be opened if it is still not fully open.
  • the inlet throttle valve 24 in combination with the variable speed control, it is possible for the temperature T at the outlet 9 of the compressor element. 2 to fall when the compressor element 2 .is driven at a minimum speed and the inlet 7 is throttled.
  • the inlet throttle valve 24 will be fully open and the compressor element 2 will operate at its maximum speed.
  • the controller 28 will control the oil circuit 14 such that the cooling capacity is a maximum, i.e.:
  • the injection valve 23 is fully open so that the entire oil flow is injected
  • the fan 19 will op&rate at & maximum speed.
  • the speed of the compressor element 2 will fall to the minimum speed and additionally the inlet throttle valve 24 will throttle the inlet 7 of the compressor element 2 to attune the delivered flow rate to the demanded flow rate.
  • the controller. 28 will control the compressor installation 1 according to the following control :
  • the aforementioned preset value T set isof course preferably at least equal to the condensation temperature T-, preferably increased by a certain value, whereby T c can. have a fixed value or can be a value that is calculated on the basis of the measured ambient temperature, relative humidity and operating pressure or which can be estimated: subject to a few assumptions.
  • This specific value can be at least 1°C or at least S°C or at least 10°C, or in extremis also 0°C if it is to be operated at the safety limit.
  • the controller 28 will control the chree-way valve 22 such that at least a proportion of the oil flow is driven through the bypass pipe 20 instead of through the cooler 18.
  • the oil 15 that flows through the bypass pipe 20 will not be cooled so that the cooling capacity of the oil circuit 14 will decrease.
  • the controller 28 will ensure that an increasing proportion of the oil flow will be driven through the bypass pipe 20, in order to let the cooling capacity decrease and the temperature ? increase to above the preset value T set .
  • the controller 23 When all the oil is driven through the bypass pipe 20 and the temperature 7, after stabilisation or after expiry of a sec time, is stiii too low, the controller 23 will let the cooling capacity decrease by controlling the injection valve 23 in the injection pipe 17, so that the quantity of oil 15 that is injected is reduced. The quantity of oil 15 will be reduced until the temperature T is at least equal to the preset value T set so that condensate formation is prevented.
  • the cooling capacity can be continuously controlled, without the quantity of oil 15 that ia injected having to be changed for this purpose.
  • An analogous control can also be used to ensure that the temperature T at the outlet 9 does not become higher than a set value T set .
  • This control can be used alone or in combination with the control of the temperature described above relating to T set .
  • This set value Tmax ia limited by an ISO standard and its maximum is equal to the degradation temperature T d of the oil 19 for. example. If applicable the set value T max can be a few degrees leas than thia degradation temperature T d to build in a certain safety, for example 1°C, 5'C or 10°C, depending on the level of extra safety that i» desired or required.
  • the controller 23 will determine the temperature T at the outlet 9 and if. it. is higher: than the set value T m , the controller 28 will control the injection valve 23 to increase the quantity of oil 15 that is injected until the temperature T at the outlet 9 falls to the set value T max .
  • This next step involves controlling the three-way valve 22 so that at least a proportion of the oil flow is driven through the cooler 16.
  • the controller 3 ⁇ 48 will gradually drive a greater proportion of. the oil flow through the cooler 13 until the temperature T fails sufficiently.
  • the controller 3 ⁇ 48 will gradually drive a greater proportion of. the oil flow through the cooler 13 until the temperature T fails sufficiently.
  • the controller 28 will switch on the far; 19 or pump if applicable, whereby the speed is increased.
  • the speed of the fan 19 is increased until the temperature T at the outlet 9 is, at a maximum, equal to the set value

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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)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

Method for controlling a compressor device (1) with a compressor element (2) and oil circuit (14) with oil (15) that is injected into the compressor element (2) by a fan (19) via a cooler (18), with a bypass pipe (20) across the cooler (18), whereby when the temperature (T) of the compressor element (2) is less than a value (Tset) the method consists of taking the following steps: - the fan (19) is switched off; - when the temperature (T) is still less than Tset, the oil (15) is driven via the bypass pipe (20); - when the temperature (T) is still less than Tset, the quantity of oil (15) that is injected into the compressor element (2) is decreased until the temperature (T) is equal to Tset.

Description

Method for controlling an oil-injected compressor device.
The present invention relates to & method for controlling an oil-injected compressor device.
More specifically the invention is intended for an oil- injected compressor device with at least one compressor element with an inlet for gas to be compressed and an outlet for compressed gas whereby the compressor device is provided with an oil circuit with an oil separator with an input that, is connected to the outlet of the compressor element and an output to which a consumer compressed gas network can be connected, whereby this oil separator comprises a pressure vessel in which the oil separated from the compressed gas is received and from which oil can be guided to a cooler and can then be injected into the compressor element, whereby this cooler is cooled by a coolant that is guided through the cooler by means of a fan or pump.
It is known that to change the flow rate that such a compressor installation supplies, the speed of the compressor element can be changed by means of the variable speed controller.
By reducing the speed of the compressor element, the flow delivered will also fall.
The speed of the compressor element cannot fail without limit, but is limited to a specific lower limit. This means that the flow rate cannot fall without limit either . If the flow must be further reduced, it could be chosen to apply an inlet throttle valve.
The use of such an inlet throttle valve is known in compressor installations where the compressor element, .is driver, at a constant speed.
In order to throttle the inlet, use is made of a butterfly valve for example that is affixed in the inlet pipe. This will ensure that the inlet pipe is partly closed off so that the gas flow supplied and thus also the flow rate delivered is reduced.
The application of an inlet throttle valve in a compressor installation with a compressor element with a variable speed controller has turned out not to be possible in the past or is impractical to implement.
Due to the reduced flow rate supplied as a result of the throttling, less power will be absorbed by the compressor element .
As a result less heat will be generated, which can lead to problems when the temperature of the compressor installation becomes too low. After all it is necessary to keep the temperature within certain limits, as at too low a temperature condensation can occur., which can lead to problems throughout the entire machine, and at too high a temperature the oil used for cooling and lubrication will deteriorate more quickly.
Methods are already known that are provided to ensure that the temperature of the oil of an oil-injected compressor device with a constant speed does not become too low in order to prevent condensation in the oil.
Such a known method is described .in WO 2007/0450 52 by the same applicant, whereby a bypass pipe is provided across the oil cooler and a thermostatic controller that ensures that when the temperature of the oil threatens to become too low, at least a proportion of the oil to be injected is not driven entirely or partially through the cooler bur. is driven directly to the compressor element without cooling.
In this case, the compressor element and the fan that is used to cool the oil in the cooler both continue at a constant speed driven by a thermal engine, even when no cooling is required if the oil is entirely or partially diverted through the bypass pipe, which brings about an energy loss.
In this known way, the control to prevent condensation is limited to the distribution of the quantity of oil that is guided through the cooler and the quantity of oil that is injected directly into the compressor element without cooling. Another method is known from GB 2.394.G25 whereby a thermostatic valve ensures that the temperature of the injected oil does not fall below a set value and whereby in addition a thermostatically controlled control valve is applied that controls the quantity of injected oil as a function of the temperature of the injected oil. Both controls are done simultaneously and independently frora one another and other controls.
The purpose of the present invention is to provide a solution to at least one of the aforementioned and other disadvantages. The subject of the present invention is a method for controlling an oil -injected compressor device with at least one compressor element with an inlet for gas to be compressed and an outlet, for compressed gas and with a variable speed controller, whereby the compressor device is provided with an oil circuit with an oil separator with an input that is connected to the outlet of the compressor element and an output to which a compressed gas consumer network can be connected, whereby this oil separator comprises a pressure vessel in which the oil separated from the compressed gas is received and from which oil can be guided to a cooler and can then be injected into the compressor element, whereby this cooler is cooled by a coolant that is guided through the cooler by means of a fan or pump, with the characteristic that a bypass pipe for oil is provided across the cooler, whereby the method consists of determining the temperature at the outlet of the compressor element and when this determined temperature is less than a preset value, the following steps are taken successively:
- first the fan or pump is switched off or its speed is decreased for as long as the temperature at the outlet is less than the preset value and the minimum speed of the fan or pump is not reached;
- then the temperature at the outlet of the compressor element is determined again and, when this temperature at the outlet is still less than the preset value, the oil is driven through the bypass pipe to the compressor element or an increasing proportion of the oil is driven through the bypass pipe to the compressor element as long as the maximum quantity of oil has not beer, reached;
- then, when the maximum quantity of oil that is driven through the bypass pipe to the compressor, element is reached, the temperature at the outlet of the compressor element is determined again, and when this temperature at the outlet is less than the preset value, the quantity of oil that, is injected into the compressor element, is reduced until the temperature at the outlet is at least equal to the preset value or the minimum quantity of oil is reached.
An advantage is that such a method will prevent the temperature of the compressor device becoming too low because the method will bring about a gradual reduction of the cooling capacity of the oil circuit, by implementing the various successive controls step by step. In this way the formation of condensate can be prevented, for example. Such a method is very useful for application in a compressor element that comprises a controllable inlet throttle valve.
When such a compressor element rotates at a reduced or minimum speed, whereby the inlet throttle valve throttles the inlet so that less power is absorbed by the compressor element, the application of such a method will ensure that the temperature does not become too low.
In this way the minimum flow rate that a speed, controlled compressor device can deliver can be made lower through the application of an inlet throttle valve without the ris* of condensate formation and ail detrimental consequences thereof.
An additional advantage is that the fan or the pump is first switched off or adjusted when the cooling capacity roust be reduced, such that less energy is consumed.
Another advantage is that only in a last step is the oil supply reduced, so that the lubrication of the compressor element by the oil is not jeopardised.
Analogously the method according to the invention provides a control of. the temperature at the outlet to ensure that this temperature does not become higher than a 3et value, whereby the following steps are taken successively:
- first the quantity of oil that is injected into the compressor element is increased for as long as the set value of the temperature and the maximum quantity of injected oil have not been reached;
- then, when the maximum quantity of oil that is injected into the compressor element has been reached, the temperature at the outlet is determined again and, when this temperature is still higher than the set value, the oil is driven through the cooler to the compressor element;
- then the temperature at the outlet of the compressor element is determined again and, when this temperature at the outlet is still higher than the set value, the fan or pump is switched on or its speed is increased.
With the intention of. better showing the characteristics of the invention, a few preferred applications of the method according to the invention for controlling an oil-injected compressor device are described hereinafter by way of an example, without any limiting nature, with reference to the accompanying drawings, wherein: figure 1 schematically shows an oil-injected compressor device for application in a method according to the invention;
figure 2 schematically shows a possible embodiment of the inlet throttle valve.
The oil~injected compressor device 1 shown in figure 1 essentially comprises a compressor element 2, in this case of the known screw type with a housing 3 in which two enmeshed helical rotors 4 are driven by means of a variable speed controller 5. It is clear that the compressor element 2 can also be of a different type, such as a turbocompressor element, without departing from the scope of the invention. in this case this variable speed controller 5 is a motor 6 whose speed is variable.
The housing 3 is provided with an inlet 7 that is connected to an inlet pipe 8 for the supply of gas to be compressed, such as air or another gas or mixture of gases.
The housing 3 is provided with an outlet 9 that is connected to an cutlet pipe 10* The outlet pipe 10 is connected, via a pressure vessel 11 of an oil separator 12 and a pressure pipe 13 connected thereto, to a downstream consumer network for the supply of various pneumatic tools or similar that are not shown here. The compressor installation 1 is provided with an oil circuit 14 to inject oil 15 from, the pressure vessel 11, via a feed pipe 16 and injection pipe 17 into the compressor element 2 for the cooling and if applicable the lubrication and/or seal between the rotors 4 mutually and the rotors 4 and the housing 3.
The oil 13 that is injected can hereby pass through a cooler 18 to cool the oil 15 from the pressure vessel 11. In this case the cooler 18 is provided with & fan 19 to ensure the cooling, although it is not excluded that instead of using cooling air for the cooling, a .liquid coolant is used char is guided through the cooler by means of a pump. In this case, but not necessarily, the fan 19 is a controllable fan, i.e. the speed of the tan 19 can be controlled.
According to the invention the oil 1¾ can also be guided to the compressor element 2 through a bypass pipe 20, whereby in this case the oil 15 does not pass via the cooler 18.
In this case a three-way valve 22 is provided at the branch 21 of the bypass pipe 20, upstream from the cooler IS, in order to control the quantity of oil. 19 that can flow through the bypass pipe 20 and through the cooler 18.
It is clear that this can also be controlled in a different way than with a three-way valve 22.
Furthermore means are provided to be able to adjust the quantity of oil 15 that is injected into the compressor element 2, for example in the form of an injection valve 23 in the injection pipe 17, or by a suitable choice of diameter of injection pipe from a series of available diameters.
In this example an inlet, throttle valve 24 is provided in the inlet pipe 8.
In this case use is made of an inlet valve for the inlet throttle valve 24 that comprises a housing that contains an aperture 25 in the form of a number of strips 26 that are movably affixed in the housing, whereby the strips 26 are movable between a closed position whereby strips 26 close off the inlet pipe 8 and an open position whereby the stripe 26 are turned away from the inlet pipe 8. A possible embodiment of such an inlet valve with an aperture 25 is shown in figure 2 . It is clear that such an inlet valve can be constructed in many different ways.
An advantage of such an inlet valve is that the stripe 26 can be completely turned away from the inlet pipe 8, and thus the inlet 7, such that in the open state the aperture 25 does not form an impediment for the supply of air to be compressed. This is in contrast to a butterfly valve for example, which even in a fully open state will partially block the passage of the inlet pipe 8.
The oil-injected compressor device i is also provided with means 27a to determine the temperature ? at the outlet 9 of the compressor element 2 and with means 27b to determine the pressure p in the pressure pipe 13. These means 2?a and 2?b respectively can be a temperature sensor or a pressure sensor fox example.
Furthermore, in this case a controller 28 is also previcted that ensures the control of the motor 6, the fan 1&, the three-way valve 22, the injection valve 23 in the injection pips 17 and the inlet throttle valve 24. The controller 28 is also connected to the temperature sensor and the pressure sensor. The operation of the compressor device 1 and the method according to the invention for the control thereof is very simple and as follows.
During the operation of the compressor device 1 the compressor element 2 will compress gas that is supplied via the inlet pipe 8.
In order to guarantee the good operation of the compressor element 2, oil 15 will be injected into the compressor eiercent 2. This oil 15 is injected into the compressor element 2. via the feed pipe 16 and the injeer, ion pipe 17 under the influence of the pressure in the pressure vessel 12.
The compressed gas is guided to the pressure vessel 11 from the oil separator 12 via the outlet pipe 10.
The oil 15 that is present in the compressed gas is separated in the oil separator 12 and received in the pressure vessel 11.
The compressed gas that is now free of oil 15 is brought to a consumer network via the pressure pipe 13.
In order to ensure that the demand for compressed gas by the consumer network is satisfied, the pressure p downstream from the outlet 29 of the oil separator 12 is determined by the pressure sensor. The signal from the pressure sensor is read by the controller 28.
The controller 28 will control the compressor device I, more specifically the raotor 6 and the inlet throttle valve 24, such that the required flow rate is delivered by the compressor element 2 to maintain the pressure p downstream front the outlet 23 of the oil separator 12 at a desired value pset.
In this case this is done according to che following control of the motor 6 and the inlet throttle valve 24.
When the pressure p is less than the desired value pset in other words when the consumption of compressed gas is greater than the flow rate delivered by the compressor device 1, the controller 28 will ensure that the delivered flow rate becomes greater by gradually opening the inlet throttle valve 24 in the first instance, if it is throttling the inlet 9 at that time, until the pressure p is again equal to the desired vaiue ρasa.
When the pressure p is still less than the desired value pset when the inlet throttle valve 24 is fully open, the controller 28 will gradually increase the speed of the compressor element 2 so chat the flow rate delivered by the compressor element will rise until the pressure p downstream from the outlet 29 of the oil separator 21 is equal to the desired value pset. This means that at this time the demand for compressed gas is equal to the flow rate delivered.
When the pressure p is greater than a desired value pset. in ether words when the consumption of compressed gas is less than the flow rate delivered by the compressor device 1, the controller 28 will ensure that the delivered flow rate becomes smaller by gradually reducing the speed of the compressor element 2 in the first; instance so that the flow rate delivered by the compressor element 2 will fall until the pressure p is again equal to the desired value pset.
When the pressure p is still higher than the desired value Pset when the minimum speed has been reached, the controller 28 will, gradually close the inlet throttle valve 24 until the pressure p downstream from the outlet 25 of the oil separator 12 is equal to the desired value pset.
The inlet throttle valve 24 will be closed to a minimum opening. When the pressure p is still too high, the controller 28 will stop the compressor element. The inlet throttle valve 24 will then also fully close to prevent an air and oil flow in the opposite direction.
When the compressor device 1 is started up again, the compressor element 2 will operate at a minimum speed arid the inlet throttle valve 24 will be open to a minimum.
The controller 28 will then gradually open the inlet throttle valve 24 in order to limit the starting torque for the motor 6. Only if the inlet throttle valve 24 has been fully opened will the speed of the compressor element be increased.
An advantage of such a control of the pressure p at the outlet 29 is that it will lead r.o the inlet throttle valve 24 being kept open as much as possible. After all, when the flow rate must be reduced/ the speed of the compressor element 2 will first be reduced before adjusting the inlet throttle valve 24, and when the flow rate must be increased the inlet throttle valve 24 will first be opened if it is still not fully open.
Due to the use of the inlet throttle valve 24 in combination with the variable speed control, it is possible for the temperature T at the outlet 9 of the compressor element. 2 to fall when the compressor element 2 .is driven at a minimum speed and the inlet 7 is throttled.
As long as there is a high demand for compressed gas, the inlet throttle valve 24 will be fully open and the compressor element 2 will operate at its maximum speed. In this case the controller 28 will control the oil circuit 14 such that the cooling capacity is a maximum, i.e.:
- the injection valve 23 is fully open so that the entire oil flow is injected;
- all oil 15? will flow through the- cooler 13;
- the fan 19 will op&rate at & maximum speed.
However, if the demanded flow rate fails sharply, the speed of the compressor element 2 will fall to the minimum speed and additionally the inlet throttle valve 24 will throttle the inlet 7 of the compressor element 2 to attune the delivered flow rate to the demanded flow rate.
As a result the power absorbed by the compressor element 2 will fall and consequently also the temperature τ.
In order to resolve the problems that are coupled to this temperature drop, such as condensate formation for example, the controller. 28 according to the invention will control the compressor installation 1 according to the following control :
When the temperature T falls below a preset value Tset in the first instance the speed of the van 19 is gradually reduced. If this is not sufficient because the temperature T, after stabilisation or after expiry of a set time, remains too low, the fan 15 will finally be switched off.
If an on/off fan 19 is used, the fan is switched off immediately.
The aforementioned preset value Tset isof course preferably at least equal to the condensation temperature T-, preferably increased by a certain value, whereby Tc can. have a fixed value or can be a value that is calculated on the basis of the measured ambient temperature, relative humidity and operating pressure or which can be estimated: subject to a few assumptions.
This will ensure extra safety to prevent condensation. This specific value can be at least 1°C or at least S°C or at least 10°C, or in extremis also 0°C if it is to be operated at the safety limit.
This will depend on the level of extra safety that is desired to prevent the formation of condensate in the compressor device 1.
Then, when the temperature T at the outlet 9, after stabilisation or after expiry of a set time, is still below the preset value the controller 28 will control the chree-way valve 22 such that at least a proportion of the oil flow is driven through the bypass pipe 20 instead of through the cooler 18. The oil 15 that flows through the bypass pipe 20 will not be cooled so that the cooling capacity of the oil circuit 14 will decrease.
If necessary, the controller 28 will ensure that an increasing proportion of the oil flow will be driven through the bypass pipe 20, in order to let the cooling capacity decrease and the temperature ? increase to above the preset value Tset.
When all the oil is driven through the bypass pipe 20 and the temperature 7, after stabilisation or after expiry of a sec time, is stiii too low, the controller 23 will let the cooling capacity decrease by controlling the injection valve 23 in the injection pipe 17, so that the quantity of oil 15 that is injected is reduced. The quantity of oil 15 will be reduced until the temperature T is at least equal to the preset value Tset so that condensate formation is prevented.
Using the controllable fan 19, or if applicable using a controllable pump, and the oil circuit 14 whereby the oil 15 can be driven through the bypass pipe 20 and partially through the cooler 18, the cooling capacity can be continuously controlled, without the quantity of oil 15 that ia injected having to be changed for this purpose.
Moreover, only in the last instance is the quantity of injected oil IS reduced, so that the lubrication and seal between the rotors 4 and/or the rotors 4 and the housing 3 by the oil 15 does not decrease.
It is clear that the method described above is not only applicable when the inlet throttle valve 24 throttle© the inlet 7 of the compressor element 2, but also at any other time when the temperature T is lower than the preset value Tset, even if the inlet throttle valve 24 does not throttle the inlet 7 or even if there is no throttle valve in the case of a variable controlled compressor device.
An analogous control can also be used to ensure that the temperature T at the outlet 9 does not become higher than a set value Tset. This control can be used alone or in combination with the control of the temperature described above relating to Tset. This set value Tmax ia limited by an ISO standard and its maximum is equal to the degradation temperature Td of the oil 19 for. example. If applicable the set value Tmax can be a few degrees leas than thia degradation temperature Td to build in a certain safety, for example 1°C, 5'C or 10°C, depending on the level of extra safety that i» desired or required.
To this end the controller 23 will determine the temperature T at the outlet 9 and if. it. is higher: than the set value Tm, the controller 28 will control the injection valve 23 to increase the quantity of oil 15 that is injected until the temperature T at the outlet 9 falls to the set value Tmax.
I£ the maximum quantity of oil 19 is already being injected or if the temperature T at the outlet 9, after stabilisation or after expiry of a set time, is still too high when the maximum quantity of oil 15 is being injected, the controller 28 will take a subsequent 3tep to increase the cooling capacity.
This next step involves controlling the three-way valve 22 so that at least a proportion of the oil flow is driven through the cooler 16.
If this was already the case or if it is insufficient, the controller ¾8 will gradually drive a greater proportion of. the oil flow through the cooler 13 until the temperature T fails sufficiently. When it turns out to be necessary to drive the entire oil flow through the cooler 13 and the cooling capacity is still insufficient, to make the temperature T fall to the set value Tmax, after stabilisation or after expiry of a set time, the following control by the controller 28 will come into effect.
The controller 28 will switch on the far; 19 or pump if applicable, whereby the speed is increased.
As a result the oil 15 in the cooler 18 will be cooled more.
The speed of the fan 19 is increased until the temperature T at the outlet 9 is, at a maximum, equal to the set value
Due to a combination of both methods to control the temperature T, it can be ensured that the temperature T is Kept within certain limits in order to increase the lifetime of the oil 15 and the compressor installation 1.
Moreover such a method will ensure that the fan 19 or pump is always the first to be switched off or the last to be switched on when the cooling capacity of the oil circuit 1< has to be decreased or increased, which will ensure an energy saving.
The present invention is by no means limited to the embodiments described as an example and shown in the drawings, but such a method according to the invention for controlling an oil-injected compressor device can be realised according to different variants without departing from the scope of the invention.

Claims

Claims.
1.- Method for controlling an oil-injected compressor device (1) with at least one compressor element (2) with an inlet (7) for gas to be compressed and an outlet (9) for compressed gas and with a variable speed controller (5), whereby the compressor- device (1) is provided with an oil circuit (14) with an oil. separator (12) with an input that is connected to the outlet (9) of the compressor element (2) and an output to which a compressed gas consumer network can be connected, whereby this oij separator [12) comprises a pressure vessel (11) in which the oil (15) separated from the compressed gas is received and from which oil (15) can be guided to a cooler (18) and can then be injected into the compressor element (2), whereby this cooler (18) is cooled by a coolant that, is guided through the cooler by means of a fan (19) or pump, characterised in that a bypass pipe (20) for oil (15) is provided across the cooler (18), whereby the method consists of determining the temperature (T) at the outlet <9> of the compressor element (12) and when this determined temperature (T) is less than a preset value (Tmax) , the following steps are taken successively:
- first the fan (19) or pump is switched off or its speed is decreased for as long as the temperature (T) at the outlet (9) is less than the preset value Tmax and the minimum speed of the fan (19) or pump is not reached;
- then the temperature (T) at the outlet (9) of the compressor element (2) is determined again and, when this temperature(T) at the outlet (9) is still less than the preset value (Tset, the oil (15) is driven through the bypass pipe (20) to the compressor element (2) or an increasing proportion of the oil (15) is driven through the bypass pipe (20) to the compressor element. (2) for as long as the maximum quantity of oil (15) has not been reached; - then, when the maximum, quantity of oil that is driven through the bypass pipe (20) to the compressor element (2) is reached, r.he temperature (T) at the outlet (9) of the compressor element (2) is determined again, and when this temperature (T) at the outlet (9? is less than the preset value (Tset) , the quantity of oil (15) that is injected into the compressor element (2) is reduced until the temperature (T) at the outlet (9) is at least equal r.o the preset value (tset) or the minima's quantity of. oil is reached.
2. - Method according to claim 1, characterised in that after each of the aforementioned successive steps a subsequent step is only implemented after the temperature (T) at the outlet (9i of the compressor element (2) has stabilised or after expiry of a set period of time.
3. - Method according to claim 1 or 2, characterised in that the compressor element (2) comprises a controllable inlet throttle valve (24) and that at least when the inlet throttle valve (24) throttles the inlet (7) of the compressor element ( 2 ) , the aforementioned steps are implemented .
4. - Method according to any one of the previous claims, characterised in that when the temperature (T) at the outlet (9) is higher than a set value (I***) * the following successive steps are taken:
- first the quantity of oil ( 15 Ϊ that is injected into the compressor element (2) is increased for as long as the set value Tmax of the temperature and the maximum quantity of injected oil have nor. been reached;
- then, when the maximum quantity of oil (15) that is injected into the compressor element ( 2 ) has been reached, the temperature (T) at the outlet '95 is determined again and, when this temperature (T) is still higher than the set value (TMX), the oil (15) is driven through the cooler (18) to the compressor element (2);
- then the temperature it; at the outlet '9) of the compressor element (2; is determined again and, when this temperature (T; at the outlet (3) is still higher than the set value (Tmax), the fan (19) or. pump is switched on or its speed is increased.
5,- Method according to claim 4, characterised in that after each of the aforementioned successive steps a subsequent step is only implemented after the temperature (T) at the outlet (9) of the compressor element i Z ) has stabilised or after expiry of a set period of time.
6.- Method according to any one of the previous claims, characterised in that the fan (19) or pump is a controllable fan (19) or pump whose speed can be controlled, whereby for the step of the switching of. the fan (19) or pump, the speed of the fan (19} or pump is gradually decreased, whereby then, when the temperature (T) at. the outlet (9) remains below the preset value (Tset), the fan (29) or pump is switched off and/or whereby in the step of switching on the fan (19} or pump, the speed is gradually increased until the temperature (T) at the outlet (9) is, at a maximum, equal to the set value (Tmax) .
7. - Method according to ar.y one of the previous claims, characterised in that the oil circuit (14) is constructed such that the oil (15) car. be partly guided through the bypass pipe (20) and partly through the cooler (18) , whereby during the step of driving the oil (15; through the bypass pipe (20) , the following substaps are taken:
- at least a proportion of the oil flow is driven through the bypass pipe (20) ;
- then, when the temperature (7) at the outlet (9) of the compressor element (2) is still less than the preset value (Tset) , a larger, proportion of the oil flow is gradually driven through the bypass pipe (20);
and/or whereby during the step of driving the oil (15) to the compressor element (2) via the cooler (18), the following substeps are taken:
- at least a proportion, of the oil flow is driven through the cooler (18) ;
- then, when the temperature (T) at the outlet (9) of the compressor element (2) is still higher than the set value (?»«*} t a larger proportion of the oil f low is gradually driven through the cooler (18) .
8. - Method according to any one of tne previous claims, characterised in that the preset value (Tset) is above the condensation temperature (Te) by a certain value.
9. - Method according to claim 8, characterised in that the preset value is at least 0°C, more preferably at least 1°C, even more preferably at least 5°C or at least 10°C.
10- Method according to any one of the previous claims 4 tc 9, characterised in that, the set value is, at a maximum, is equal to the degradation temperature (T)· of the oil (15) or a value that is imposed by an ISO standard.
11. - Method according to any one of the previous claims 3 to 10, characterised in that the method comprises the step of determining the pressure (p) downstream from the outlet of the oil separator (12), whereby one of the following steps is taken:
- when the pressure (p) downstream from the outlet of the oil separator (12) is higher than a desired value (Pset) the speed of the compressor element (2) is gradually decreased and if applicable the inlet throttle valve (24) is also gradually closed until the aforementioned pressure (p) is equal, to the set value (Pset) ;
- when the pressure (p) downstream from the outlet of the oil separator (12) is less than the desired value (Pset) , the inlet throttle valve (24; is gradually opened and if applicable the speed of the compressor element (2) is increased until the aforementioned pressure (p) is equal to the ser. value (Pset) ·
12. - Method according to any one of the previous claims 3 to 11, characterised in that for the inlet throtwle valve (24) use is made of an inlet valve that comprises a housing that, contains an aperture (25) In the form of a number of strips (26) that are movably affixed in the housing, whereby the strips (26) are movable between a closed position whereby the strips (26) close off the inlet Π) of the compressor element (2) and an open position whereby the strips (26) are turned away from the inlet (?).
13. ~ Method according to any one of the previous claims, characterised in that the compressor element (2) is a screw compressor element .
14. - Method for controlling an oil-injected compressor device (1) with at least one compressor element (2) with an inlet (7) for gas to be compressed and an outlet '9; for compressed gas and with a variable speed controller (5) , whereby the compressor device (2) is provided with an oil circuit (14) with an oil separator (12) with an input that is connected to the outlet (9) of the compressor element (2) and an output to which a compressed gas consumer network can be connected, whereby this oil separator (12) comprises a pressure vessel (11) in which the oil (15) separated from the compressed gas is received and from which oil (19) can he guided to a cooler {1.8) and then can be injected into the compressor element (2), whereby this cooler (18) is cooled by a coolant that is guided through the cooler by means of a fan (19; or pump, characterised in that a bypass pipe (20) for oil (15) is provided across the cooler (18), whereby the method consists of determining the temperature (Ί) at the outlet (9) of the compressor element (2) and when this determined temperature (T) is higher than a preset value (Tmax). the following successive steps are taken:
- first the quantity of oil (15) that ie injected into the compressor element {2} is increased for as long as the set value (Tmax) of. the temperature and the maximum quantity of injected oil has net been reached;
·- then, when the maximum quantity of oil (15) that is injected into the compressor element (2) has been reached, the temperature (T) at the outlet (95 is determined again and, when this temperature (T ; is still higher than the 3et value (Tm)ax; , the oil ( 15 ) is driven through the cooler ( 18 ) to the compressor element (25;
- then, the temperature (T) at the outlet ( 9 ; of the compressor element (2) is determined again and, when this temperature (T) at. the outlet ( 9 ) is still higher than the set value (Tmax) the fan (19 ) or pump is switched on or its speed is increased.
15 . - Method according to claim 14 , characterised in that after each of the aforementioned successive steps a subsequent step is only implemented after the temperature it) at the outlet (9) of the compressor element (2) has stabilised or after expiry of a set period of time.
16- Method according to claim 14 or 15 , characterised in that the set value (Tmax) is, at a maximum, equal to the degradation temperature iTd) of the oil (155 or is a value is that is imposed by an ISO standard.
17- Method for controlling an oil-injected compressor device (1) with at least one compressor element (2) with an Inlet (7) for gas to be compressed and an outlet (9) for compressed gas and with a variable speed controller (.¾), whereby the compressor device (1) is provided with an oil circuit (14) with an oil separator (12) with an input that is connected to the outlet (9) of the compressor element (2) and an output to which a compressed gas consumer network can be connected, whereby this oil separator (12) comprises a pressure vessel (11) in which the oil (15) separated from the compressed gas is received and from which oil (15) can be guided to a cooler (18) and then can be injected into the compressor element (2?, whereby this cooler (18) is cooled by a coolant that is guided through the cooler by means of a fan (19) or pump, characterised in that a bypas3 pipe (20) for oil (15) is provided across the cooler (18), whereby the method consists of determining the temperature (T) at the outlet (9) of the compressor element (2) and when this determined temperature (Τ) is lower than a preset value (Tset) one or more of the following steps are implemented:
- the fan {19) or pump is switched off;
- then, when the temperature (T) at the outlet (9) is still less than the preset value (Tset) the oil (15) is driven through the bypass pipe (20) to the compressor element (2);
- then, when the temperature (!) at the outlet is still less than the preset value (Tset) , the quantity of oil (15? that is injected into the compressor element (2) is decreased until the temperature (?) at the outlet (9) is at least equal to the preset value Tset .
PCT/BE2015/000046 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device WO2016041026A1 (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
MX2017003608A MX2017003608A (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device.
RU2017113137A RU2681402C2 (en) 2014-09-19 2015-09-21 Method for regulating compressor device with oil injection (options)
NZ730649A NZ730649A (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
ES15801983T ES2834392T3 (en) 2014-09-19 2015-09-21 Method of controlling an oil-injected compressor device
UAA201702380A UA121483C2 (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
KR1020177010215A KR102069957B1 (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
CA2960700A CA2960700C (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
AU2015318763A AU2015318763B2 (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
CN201580050147.4A CN107002683B (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor installation
BR112017005500-7A BR112017005500B1 (en) 2014-09-19 2015-09-21 METHOD FOR CONTROLLING AN OIL-INJECTED COMPRESSOR DEVICE
US15/511,760 US10480512B2 (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
EP15801983.6A EP3194784B1 (en) 2014-09-19 2015-09-21 Method for controlling an oil-injected compressor device
JP2017515172A JP6594964B2 (en) 2014-09-19 2015-09-21 Method for controlling oil-cooled compressor equipment

Applications Claiming Priority (2)

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BE2014/0711 2014-09-19
BE2014/0711A BE1022403B1 (en) 2014-09-19 2014-09-19 METHOD FOR SENDING AN OIL-INJECTED COMPRESSOR DEVICE

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EP (1) EP3194784B1 (en)
JP (1) JP6594964B2 (en)
KR (1) KR102069957B1 (en)
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AU (1) AU2015318763B2 (en)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1026208B1 (en) * 2018-04-12 2019-11-13 Atlas Copco Airpower Naamloze Vennootschap Oil-injected screw compressor device
CN108895721A (en) * 2018-07-26 2018-11-27 青岛海尔空调器有限总公司 Compressor and air conditioner including the compressor
BE1026652B1 (en) 2018-09-25 2020-04-28 Atlas Copco Airpower Nv Oil-injected multi-stage compressor device and method for controlling such a compressor device
BE1027361B1 (en) * 2019-06-12 2021-01-20 Atlas Copco Airpower Nv Compressor plant and method for supplying compressed gas
CN110332119B (en) * 2019-07-10 2020-11-17 西安交通大学 Automatic control system and method for starting process of screw type refrigeration compressor
BE1028598B1 (en) * 2020-09-11 2022-04-11 Atlas Copco Airpower Nv Compressor device and method for controlling such compressor device
CN112963332B (en) * 2021-02-25 2023-08-18 胡红婷 Lubricating oil cooling system of air compressor and control method thereof
BE1030213B1 (en) * 2022-01-25 2023-08-21 Atlas Copco Airpower Nv Method of controlling a first reference temperature in a gas compressor
DE102022202574A1 (en) * 2022-03-15 2023-09-21 Kaeser Kompressoren Se Compressor device and method for operating a compressor device
CN115507025B (en) * 2022-10-18 2024-02-27 西安交通大学 High rotor axial temperature uniformity twin-screw compressor
CN115559904B (en) * 2022-10-18 2023-12-19 西安交通大学 Variable-lead double-screw machine and active adjusting and controlling method for axial liquid spraying of variable-lead double-screw machine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2394025A (en) 2001-12-07 2004-04-14 Compair Thermostatically controlled valve for lubricant-cooled gas compressor
US20050089432A1 (en) * 2002-02-08 2005-04-28 Truyens Francois L.J. Method for controlling the oil recirculation in an oil-injected screw-type compressor and compressor using this method
WO2007045052A1 (en) 2005-10-21 2007-04-26 Atlas Copco Airpower, Naamloze Vennootschap Device to prevent the formation of condensate in compressed gas and compressor unit equipped with such a device

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE30499E (en) * 1974-11-19 1981-02-03 Dunham-Bush, Inc. Injection cooling of screw compressors
US4123203A (en) * 1977-10-14 1978-10-31 Gardner-Denver Company Multistage helical screw compressor with liquid injection
JPS6213188A (en) 1985-07-11 1987-01-21 Fuji Photo Film Co Ltd Method for controlling exposure in image pickup device for color photograph
JPH06173878A (en) * 1992-12-03 1994-06-21 Hitachi Ltd Variable displacement type compressor
US5653585A (en) * 1993-01-11 1997-08-05 Fresco; Anthony N. Apparatus and methods for cooling and sealing rotary helical screw compressors
JPH06213188A (en) * 1993-01-18 1994-08-02 Kobe Steel Ltd Oil-cooled compressor
US5318151A (en) * 1993-03-17 1994-06-07 Ingersoll-Rand Company Method and apparatus for regulating a compressor lubrication system
JPH0687842U (en) * 1993-06-04 1994-12-22 株式会社クボタ Intake pressure control device for engine test facility
BE1007135A6 (en) * 1993-06-16 1995-04-04 Atlas Copco Airpower Nv Control device with start and stop device for screw compressors, and thus used start and stop device.
JPH084679A (en) * 1994-06-17 1996-01-09 Hitachi Ltd Oil cooling type compressor
JPH11117894A (en) * 1997-10-20 1999-04-27 Nkk Corp Gas compression facility and its operating method
CN1452690A (en) * 2000-05-23 2003-10-29 赫罗·普拉桑塔·维贾亚 Diaphragmed air valve system
JP2002039069A (en) 2000-07-21 2002-02-06 Kobe Steel Ltd Oil-cooled compressor
BE1013944A3 (en) * 2001-03-06 2003-01-14 Atlas Copco Airpower Nv Water injected screw compressor.
JP2002317786A (en) * 2001-04-18 2002-10-31 Kobe Steel Ltd Oil injection type compressor and operating method thereof
ATE410597T1 (en) * 2001-12-07 2008-10-15 Compair Uk Ltd OIL INJECTED COMPRESSOR
CN1542285A (en) * 2003-04-30 2004-11-03 德泰机电有限公司 Compressor exhaust temperature control system
JP2006525459A (en) * 2003-05-01 2006-11-09 ビショップ イノヴェーション リミテッド Throttle valve
US7255012B2 (en) * 2004-12-01 2007-08-14 Rosemount Inc. Process fluid flow device with variable orifice
JP5268317B2 (en) 2007-09-28 2013-08-21 株式会社日立産機システム Oil-cooled air compressor
BE1018075A3 (en) * 2008-03-31 2010-04-06 Atlas Copco Airpower Nv METHOD FOR COOLING A LIQUID-INJECTION COMPRESSOR ELEMENT AND LIQUID-INJECTION COMPRESSOR ELEMENT FOR USING SUCH METHOD.
TWI429823B (en) * 2010-08-05 2014-03-11 Nabtesco Corp Air Compressor for Railway Vehicles
US9441638B2 (en) * 2010-08-27 2016-09-13 Hitachi Industrial Equipment Systems Co., Ltd. Oil-cooled gas compressor
RU2445513C1 (en) * 2010-09-20 2012-03-20 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Screw-type oil-filled compressor unit

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2394025A (en) 2001-12-07 2004-04-14 Compair Thermostatically controlled valve for lubricant-cooled gas compressor
US20050089432A1 (en) * 2002-02-08 2005-04-28 Truyens Francois L.J. Method for controlling the oil recirculation in an oil-injected screw-type compressor and compressor using this method
WO2007045052A1 (en) 2005-10-21 2007-04-26 Atlas Copco Airpower, Naamloze Vennootschap Device to prevent the formation of condensate in compressed gas and compressor unit equipped with such a device

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106121970A (en) * 2016-08-16 2016-11-16 萨震压缩机（上海）有限公司 The adjustable air compressor machine of distributive value
WO2018131089A1 (en) * 2017-01-11 2018-07-19 三菱電機株式会社 Refrigeration cycle device
BE1024746B1 (en) * 2017-04-21 2018-06-18 Atlas Copco Airpower Nv Oil circuit and machine equipped with such an oil circuit.
EP3392478A1 (en) * 2017-04-21 2018-10-24 ATLAS COPCO AIRPOWER, naamloze vennootschap Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit
EP3392477A1 (en) * 2017-04-21 2018-10-24 ATLAS COPCO AIRPOWER, naamloze vennootschap Oil circuit and machine provided of such oil circuit
WO2018193325A1 (en) * 2017-04-21 2018-10-25 Atlas Copco Airpower, Naamloze Vennootschap Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit
WO2018193292A1 (en) * 2017-04-21 2018-10-25 Atlas Copco Airpower, Naamloze Vennootschap Oil circuit and machine provided of such oil circuit
US11085448B2 (en) 2017-04-21 2021-08-10 Atlas Copco Airpower, Naamloze Vennootschap Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit
US20210054836A1 (en) * 2018-02-23 2021-02-25 Atlas Copco Airpower, Naamloze Vennootschap Method for actuating a compressor system and a comp system
EP3755906B1 (en) * 2018-02-23 2021-11-17 ATLAS COPCO AIRPOWER, naamloze vennootschap Method for actuating a compressor system and a comp system
IT201900019031A1 (en) * 2019-10-16 2021-04-16 Atos Spa DEVICE AND CONTROL METHOD FOR THE PROTECTION OF FIXED DISPLACEMENT PUMPS IN HYDRAULIC CIRCUITS

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