US20170298935A1 - Vacuum-generating pumping system and pumping method using this pumping system - Google Patents
Vacuum-generating pumping system and pumping method using this pumping system Download PDFInfo
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- US20170298935A1 US20170298935A1 US15/512,883 US201415512883A US2017298935A1 US 20170298935 A1 US20170298935 A1 US 20170298935A1 US 201415512883 A US201415512883 A US 201415512883A US 2017298935 A1 US2017298935 A1 US 2017298935A1
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- 238000000034 method Methods 0.000 title claims abstract description 20
- 239000007789 gas Substances 0.000 claims abstract description 51
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- 239000000126 substance Substances 0.000 claims description 5
- 239000004065 semiconductor Substances 0.000 claims description 3
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- 230000009471 action Effects 0.000 description 2
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- 238000005516 engineering process Methods 0.000 description 2
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- 238000004364 calculation method Methods 0.000 description 1
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- 230000004048 modification Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000001771 vacuum deposition Methods 0.000 description 1
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Classifications
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- 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
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
- F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/06—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
- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps 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
- F04C2/16—Rotary-piston machines or pumps 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
-
- 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
- F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
-
- 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
- F04C2220/00—Application
- F04C2220/10—Vacuum
- F04C2220/12—Dry running
-
- 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
Definitions
- the present invention relates to the field of vacuum technology. More precisely, it concerns a pumping system comprising a dry screw pump as well as a pumping method by means of this pumping system.
- the speed of rotation of the pump plays a very important role by defining the operation of the pump during the different successive phases in the course of evacuation of the vacuum chamber.
- the necessary electrical power in the first pumping phases when the pressure at the suction end is between atmospheric pressure and about 100 mbar, that is to say during strong mass flow rate operation, will be very high if the speed of rotation of the pump cannot be reduced.
- the common solution is to use a variable speed drive which makes possible reduction or increase of the speed and consequently of the power as a function of different criteria of the type pressure, maximal current, limit torque, temperature, etc.
- the state of the art concerning the pumping systems which aim to improve the final vacuum and to increase the flow rate also comprise booster pumps of Roots type arranged upstream from main dry pumps.
- This type of systems is bulky, operates either with by-pass valves presenting problems of reliability or by employing means of measurement, control, adjustment or servo-control.
- these means of control, adjustment or servo-control must be controlled in an active way, which necessarily results in an increase in the number of components of the system, its complexity and its cost.
- the present invention has as object to permit a better vacuum to be obtained (on the order of 0.0001 mbar) than that which a single dry vacuum pump of screw type is able to generate in a vacuum chamber.
- the present invention also has as object obtaining a draining or evacuation rate which is greater at low pressure than that which can be obtained with the aid of a single dry vacuum pump of screw type during a pumping to achieve a vacuum in a vacuum chamber.
- the present invention likewise has as object to permit a reduction of the electrical energy necessary for the evacuation of a vacuum chamber and for maintaining the vacuum as well as to achieve a decrease in the temperature of the exit gas.
- a pumping system for generating a vacuum comprising a main vacuum pump which is a dry screw pump having a gas suction inlet connected to a vacuum chamber and gas discharge outlet leading into a gas evacuation conduit in the direction of a gas exhaust outlet outside the pumping system.
- the pumping system further comprises
- the auxiliary vacuum pump can be of the type dry screw pump, claw pump, multi-stage Roots pump, diaphragm pump, dry rotary vane pump, lubricated rotary vane pump.
- the invention likewise has as subject matter a pumping method by means of a pumping system such as previously defined. This method comprises steps in which:
- the auxiliary pump is operated continuously all the while that the main vacuum pump of dry screw type evacuates the vacuum chamber, but also all the while that the main dry screw vacuum pump maintains a defined pressure (for example the final vacuum) in the chamber by evacuating the gases through its discharge end.
- the coupling of the main vacuum pump of dry screw type and of the auxiliary pump can be carried out without requiring specific measures or apparatuses (for example sensors for pressure, temperature, current, etc.), nor servo-controls, nor data management and without calculation. Consequently the pumping system suitable for implementing the pumping method according to the present invention can comprise only a minimal number of components, can have great simplicity and can cost considerably less compared with existing systems.
- the main vacuum pump of dry screw type can operate at a single constant speed, that of the power grid, or turn at variable speeds in accordance with its own mode of operation. Consequently, the complexity and the cost of the pumping system suitable for implementing the pumping method according to the present invention can be reduced even more.
- the auxiliary pump integrated in the pumping system can always operate according to the pumping method of the invention without damage. Its dimensioning is conditioned by a minimal energy consumption for the operation of the device. Its nominal flow rate is selected as a function of the volume of the evacuation conduit between the main dry screw vacuum pump and the non-return valve. This flow rate can be advantageously from 1/500 to 1/20 of the nominal flow rate of the main dry screw vacuum pump, but can also be less than or greater than these values, in particular from 1/500 to 1/10 or even from 1/500 to 1 ⁇ 5 of the nominal flow rate of the main vacuum pump.
- the non-return valve placed in the conduit downstream from the main dry screw vacuum pump, can be a standard commercially available element. It is dimensioned according to the nominal flow rate of the main dry screw vacuum pump. In particular, it is foreseen that the non-return valve closes when the pressure at the suction end of the main dry screw vacuum pump is between 500 mbar absolute and the final vacuum (for example 100 mbar).
- the auxiliary pump can have high chemical resistance to substances and gases commonly used in the semiconductor industry.
- the auxiliary pump is preferably of small size.
- the auxiliary vacuum pump always pumps in the volume between the gas discharge outlet of the main vacuum pump and the non-return valve.
- the actuation of the auxiliary vacuum pump is controlled in an “all or nothing” way.
- the control consists in measuring one or more parameters and following certain rules to actuate the auxiliary vacuum pump or to stop it.
- the parameters provided by suitable sensors, are, for example, the current of the motor of the main dry screw vacuum pump, the temperature or the pressure of the gases at its exhaust end, i.e. in the space upstream from the non-return valve in the evacuation conduit, or a combination of these parameters.
- the dimensioning of the auxiliary vacuum pump aims to achieve a minimal energy consumption of its motor. Its nominal flow rate is selected as a function of the flow rate of the main dry screw vacuum pump, but also taking into account the volume which the gas evacuation conduit delimits between the main vacuum pump and the non-return valve. This flow rate can be from 1/500 to 1/20 of the nominal flow rate of the main dry screw vacuum pump, but can also be less than or greater than these values.
- the pressure there is high for example equal to the atmospheric pressure.
- the pressure of the gases discharged at its exit is higher than the atmospheric pressure (if the gases at the exit of the main pump are discharged directly into the atmosphere) or higher than the pressure at the inlet of another apparatus connected downstream. This causes the opening of the non-return valve.
- FIG. 1 represents in a diagrammatic way a pumping system suitable for implementation of a pumping method according to a first embodiment of the present invention
- FIG. 2 represents in a diagrammatic way a pumping system suitable for implementation of a pumping method according to a second embodiment of the present invention.
- FIG. 1 represents a pumping system SP for generating a vacuum, which is suitable for implementing a pumping method according to a first embodiment of the present invention.
- This pumping system SP comprises a chamber 1 , which is connected to the suction end 2 of a main vacuum pump constituted by a dry screw pump 3 .
- the gas discharge outlet of the main dry screw vacuum pump 3 is connected to an evacuation conduit 5 .
- a non-return discharge valve 6 is placed in the evacuation conduit 5 , which, after this non-return valve, continues into the gas exit conduit 8 .
- the non-return valve 6 when it is closed, permits the formation of a volume 4 , contained between the gas discharge outlet of the main vacuum pump 3 and itself.
- the pumping system SP also comprises the auxiliary vacuum pump 7 , connected in parallel to the non-return valve 6 .
- the suction end of the auxiliary vacuum pump is connected to the space 4 of the evacuation conduit 5 and its discharge end is connected to the conduit 8 .
- the auxiliary vacuum pump 7 is itself actuated.
- the main dry screw vacuum pump 3 suctions the gases in the chamber 1 through the conduit 2 connected at its inlet and compresses them in order to discharge them subsequently at its exit in the evacuation conduit 5 through the non-return valve 6 .
- the closure pressure for the non-return valve 6 When the closure pressure for the non-return valve 6 is reached, it closes.
- the pumping of the auxiliary vacuum pump 7 makes the pressure in the space 4 drop progressively to the value of its pressure limit.
- the power consumed by the main dry screw vacuum pump 3 decreases progressively. This takes place in a short time period, for example for a certain cycle in 5 to 10 seconds.
- the auxiliary vacuum pump 7 is itself a dry screw pump.
- the main pump and the auxiliary pump can be of the same type, which simplifies the operation and the handling.
- this combination of pumps permits the pumping system SP to be used for all the applications where only a dry screw pump can be used.
- the auxiliary vacuum pump 7 is a claw pump, a multi-stage Roots pump, a diaphragm pump, a dry rotary vane pump or a lubricated rotary vane pump. All these combinations of pumps have the advantages connected with the specific properties of each type of individual pumps.
- FIG. 2 represents a pumping system SPP suitable for implementation of a pumping method according to a second embodiment of the present invention.
- the system shown in FIG. 2 represents the controlled pumping system SPP, further comprising suitable sensors 11 , 12 , 13 which check either the current of the motor (sensor 11 ) of the main dry screw vacuum pump 3 , or the pressure (sensor 13 ) of the gases in the space of the exit conduit of the main dry screw vacuum pump, limited by the non-return valve 6 , or the temperature (sensor 12 ) of the gases in the space of the exit conduit at the exit of the main dry screw vacuum pump, limited by the non-return valve 6 , or a combination of these parameters.
- the main dry screw vacuum pump 3 begins to pump the gases of the vacuum chamber 1 , the parameters such as the current of its motor, the temperature and the pressure of the gases in the space of the exit conduit 4 begin to change and reach threshold values detected by the sensors. After a time lag, this causes the startup of the auxiliary vacuum pump 7 . When these parameters return to the initial ranges (outside the set values), with a time lag the auxiliary vacuum pump is stopped.
- the auxiliary vacuum pump can be of type dry screw, claw, multi-stage Roots, diaphragm, dry rotary vane or lubricated rotary vane, as in the first embodiment of the invention of FIG. 1 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
- The present invention relates to the field of vacuum technology. More precisely, it concerns a pumping system comprising a dry screw pump as well as a pumping method by means of this pumping system.
- The general objectives to increase the performance of vacuum pumps, to reduce the costs of installations and the consumption of energy in industries such as the chemical industry, the pharmaceutical industry, the vacuum deposition industry, the semiconductor industry, etc., have led to significant developments in terms of performance, energy economy, bulkiness, in the drives, etc.
- The state of the art shows that to improve the final vacuum supplementary stages must be added in vacuum pumps of the multi-stage Roots or multi-stage claw type. For the dry vacuum pumps of screw type it is known that additional turns of the screw must be provided and/or the rate of internal compression increased.
- The speed of rotation of the pump plays a very important role by defining the operation of the pump during the different successive phases in the course of evacuation of the vacuum chamber. With the internal compression rates of the pumps available on the market (the order of magnitude of which is between 2 and 20, for example), the necessary electrical power in the first pumping phases, when the pressure at the suction end is between atmospheric pressure and about 100 mbar, that is to say during strong mass flow rate operation, will be very high if the speed of rotation of the pump cannot be reduced. The common solution is to use a variable speed drive which makes possible reduction or increase of the speed and consequently of the power as a function of different criteria of the type pressure, maximal current, limit torque, temperature, etc. But during the periods of operation at reduced rotation speed there are decreases in flow rate at high pressure, the flow rate being proportional to the rotation speed. Speed variation by variable speed drive entails additional costs and more bulkiness. Another common solution is the use of valves of by-pass type at certain stages, in the multi-stage vacuum pumps of Roots or claw type, or at certain well defined places along the screw in the dry vacuum pumps of screw type. This solution requires numerous parts and presents problems of reliability.
- The state of the art concerning the pumping systems which aim to improve the final vacuum and to increase the flow rate also comprise booster pumps of Roots type arranged upstream from main dry pumps. This type of systems is bulky, operates either with by-pass valves presenting problems of reliability or by employing means of measurement, control, adjustment or servo-control. However, these means of control, adjustment or servo-control must be controlled in an active way, which necessarily results in an increase in the number of components of the system, its complexity and its cost.
- The present invention has as object to permit a better vacuum to be obtained (on the order of 0.0001 mbar) than that which a single dry vacuum pump of screw type is able to generate in a vacuum chamber.
- The present invention also has as object obtaining a draining or evacuation rate which is greater at low pressure than that which can be obtained with the aid of a single dry vacuum pump of screw type during a pumping to achieve a vacuum in a vacuum chamber.
- The present invention likewise has as object to permit a reduction of the electrical energy necessary for the evacuation of a vacuum chamber and for maintaining the vacuum as well as to achieve a decrease in the temperature of the exit gas.
- These objects of the present invention are achieved with the aid of a pumping system for generating a vacuum comprising a main vacuum pump which is a dry screw pump having a gas suction inlet connected to a vacuum chamber and gas discharge outlet leading into a gas evacuation conduit in the direction of a gas exhaust outlet outside the pumping system. The pumping system further comprises
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- a non-return valve positioned between the gas discharge outlet and the gas exhaust outlet, and
- an auxiliary vacuum pump connected in parallel to the non-return valve.
- The auxiliary vacuum pump can be of the type dry screw pump, claw pump, multi-stage Roots pump, diaphragm pump, dry rotary vane pump, lubricated rotary vane pump.
- The invention likewise has as subject matter a pumping method by means of a pumping system such as previously defined. This method comprises steps in which:
-
- the main vacuum pump is started up in order to pump the gases contained in the vacuum chamber and to discharge these gases through its gas discharge outlet;
- simultaneously the auxiliary vacuum pump is started up; and
- the auxiliary vacuum pump continues to pump all the while that the main vacuum pump pumps the gases contained in the vacuum chamber and/or all the while that the main vacuum pump maintains a defined pressure in the vacuum chamber.
- In the method according to the invention, the auxiliary pump is operated continuously all the while that the main vacuum pump of dry screw type evacuates the vacuum chamber, but also all the while that the main dry screw vacuum pump maintains a defined pressure (for example the final vacuum) in the chamber by evacuating the gases through its discharge end.
- Thanks to the method according to the invention, the coupling of the main vacuum pump of dry screw type and of the auxiliary pump can be carried out without requiring specific measures or apparatuses (for example sensors for pressure, temperature, current, etc.), nor servo-controls, nor data management and without calculation. Consequently the pumping system suitable for implementing the pumping method according to the present invention can comprise only a minimal number of components, can have great simplicity and can cost considerably less compared with existing systems.
- Thanks to the method according to the invention, the main vacuum pump of dry screw type can operate at a single constant speed, that of the power grid, or turn at variable speeds in accordance with its own mode of operation. Consequently, the complexity and the cost of the pumping system suitable for implementing the pumping method according to the present invention can be reduced even more.
- By its nature, the auxiliary pump integrated in the pumping system can always operate according to the pumping method of the invention without damage. Its dimensioning is conditioned by a minimal energy consumption for the operation of the device. Its nominal flow rate is selected as a function of the volume of the evacuation conduit between the main dry screw vacuum pump and the non-return valve. This flow rate can be advantageously from 1/500 to 1/20 of the nominal flow rate of the main dry screw vacuum pump, but can also be less than or greater than these values, in particular from 1/500 to 1/10 or even from 1/500 to ⅕ of the nominal flow rate of the main vacuum pump.
- The non-return valve, placed in the conduit downstream from the main dry screw vacuum pump, can be a standard commercially available element. It is dimensioned according to the nominal flow rate of the main dry screw vacuum pump. In particular, it is foreseen that the non-return valve closes when the pressure at the suction end of the main dry screw vacuum pump is between 500 mbar absolute and the final vacuum (for example 100 mbar).
- According to still another variant, the auxiliary pump can have high chemical resistance to substances and gases commonly used in the semiconductor industry.
- The auxiliary pump is preferably of small size.
- Preferably, according to the pumping method employing the pumping system according to the invention, the auxiliary vacuum pump always pumps in the volume between the gas discharge outlet of the main vacuum pump and the non-return valve.
- According to another variant of the method of the present invention, to fulfil specific requirements, the actuation of the auxiliary vacuum pump is controlled in an “all or nothing” way. The control consists in measuring one or more parameters and following certain rules to actuate the auxiliary vacuum pump or to stop it. The parameters, provided by suitable sensors, are, for example, the current of the motor of the main dry screw vacuum pump, the temperature or the pressure of the gases at its exhaust end, i.e. in the space upstream from the non-return valve in the evacuation conduit, or a combination of these parameters.
- The dimensioning of the auxiliary vacuum pump aims to achieve a minimal energy consumption of its motor. Its nominal flow rate is selected as a function of the flow rate of the main dry screw vacuum pump, but also taking into account the volume which the gas evacuation conduit delimits between the main vacuum pump and the non-return valve. This flow rate can be from 1/500 to 1/20 of the nominal flow rate of the main dry screw vacuum pump, but can also be less than or greater than these values.
- Starting from a cycle of evacuation of the chamber, the pressure there is high, for example equal to the atmospheric pressure. Considering the compression in the main dry screw vacuum pump, the pressure of the gases discharged at its exit is higher than the atmospheric pressure (if the gases at the exit of the main pump are discharged directly into the atmosphere) or higher than the pressure at the inlet of another apparatus connected downstream. This causes the opening of the non-return valve.
- When this non-return valve is open, the action of the auxiliary vacuum pump is felt very slightly since the pressure at its suction end is almost equal to that at its discharge end. On the other hand, when the non-return valve closes at a certain pressure (because the pressure in the chamber has dropped in the meantime), the action of the auxiliary vacuum pump causes a progressive reduction of the difference in pressure between the vacuum chamber and the evacuation conduit upstream from the valve. The pressure at the exit of the main dry screw vacuum pump becomes that at the inlet of the auxiliary vacuum pump, that of its exit always being the pressure in the conduit after the non-return valve. The more the auxiliary vacuum pump pumps, the more the pressure at the exit of the main dry screw vacuum pump, in the space limited by the closed non-return valve, drops and consequently the difference in pressure between the chamber and the exit of the main dry screw vacuum pump decreases.
- This slight difference reduces the internal leaks in the main dry screw vacuum pump and causes a reduction of the pressure in the chamber, which improves the final vacuum. In addition, the main dry screw vacuum pump consumes less and less energy for the compression and produces less and less compression heat.
- On the other hand, it is also evident that the study of the mechanical concept seeks to reduce the space between the gas discharge outlet of the main dry screw vacuum pump and the non-return valve with the aim of being able to lower the pressure there more quickly.
- The features and the advantages of the present invention will appear with more details within the context of the description which follows with example embodiments, given by way of illustration and in a non-limiting way, with reference to the attached drawings:
-
FIG. 1 represents in a diagrammatic way a pumping system suitable for implementation of a pumping method according to a first embodiment of the present invention; and -
FIG. 2 represents in a diagrammatic way a pumping system suitable for implementation of a pumping method according to a second embodiment of the present invention. -
FIG. 1 represents a pumping system SP for generating a vacuum, which is suitable for implementing a pumping method according to a first embodiment of the present invention. - This pumping system SP comprises a
chamber 1, which is connected to thesuction end 2 of a main vacuum pump constituted by adry screw pump 3. The gas discharge outlet of the main dryscrew vacuum pump 3 is connected to anevacuation conduit 5. A non-return discharge valve 6 is placed in theevacuation conduit 5, which, after this non-return valve, continues into thegas exit conduit 8. The non-return valve 6, when it is closed, permits the formation of avolume 4, contained between the gas discharge outlet of themain vacuum pump 3 and itself. - The pumping system SP also comprises the
auxiliary vacuum pump 7, connected in parallel to the non-return valve 6. The suction end of the auxiliary vacuum pump is connected to thespace 4 of theevacuation conduit 5 and its discharge end is connected to theconduit 8. - Already with the actuation of the main dry
screw vacuum pump 3, theauxiliary vacuum pump 7 is itself actuated. The main dryscrew vacuum pump 3 suctions the gases in thechamber 1 through theconduit 2 connected at its inlet and compresses them in order to discharge them subsequently at its exit in theevacuation conduit 5 through the non-return valve 6. When the closure pressure for the non-return valve 6 is reached, it closes. Starting from this moment the pumping of theauxiliary vacuum pump 7 makes the pressure in thespace 4 drop progressively to the value of its pressure limit. In parallel, the power consumed by the main dryscrew vacuum pump 3 decreases progressively. This takes place in a short time period, for example for a certain cycle in 5 to 10 seconds. - With a clever adjustment of the flow rate of the
auxiliary vacuum pump 7 and of the closure pressure of the non-return valve 6 as a function of the flow rate of the main dryscrew vacuum pump 3 and the volume of thechamber 1, it is moreover possible to reduce the time before the closure of the non-return valve 6 with respect to the duration of the evacuation cycle and thus reduce the quantity of energy consumed during this time of operation of theauxiliary pump 7 without effect on the pumping. On the other hand, the advantage of simplicity gives an excellent reliability to the system. - According to a first possibility, the
auxiliary vacuum pump 7 is itself a dry screw pump. Thus, the main pump and the auxiliary pump can be of the same type, which simplifies the operation and the handling. Also, this combination of pumps permits the pumping system SP to be used for all the applications where only a dry screw pump can be used. - According to the other possibilities, the
auxiliary vacuum pump 7 is a claw pump, a multi-stage Roots pump, a diaphragm pump, a dry rotary vane pump or a lubricated rotary vane pump. All these combinations of pumps have the advantages connected with the specific properties of each type of individual pumps. -
FIG. 2 represents a pumping system SPP suitable for implementation of a pumping method according to a second embodiment of the present invention. - With respect to the system shown in
FIG. 1 , the system shown inFIG. 2 represents the controlled pumping system SPP, further comprisingsuitable sensors screw vacuum pump 3, or the pressure (sensor 13) of the gases in the space of the exit conduit of the main dry screw vacuum pump, limited by the non-return valve 6, or the temperature (sensor 12) of the gases in the space of the exit conduit at the exit of the main dry screw vacuum pump, limited by the non-return valve 6, or a combination of these parameters. In effect, when the main dryscrew vacuum pump 3 begins to pump the gases of thevacuum chamber 1, the parameters such as the current of its motor, the temperature and the pressure of the gases in the space of theexit conduit 4 begin to change and reach threshold values detected by the sensors. After a time lag, this causes the startup of theauxiliary vacuum pump 7. When these parameters return to the initial ranges (outside the set values), with a time lag the auxiliary vacuum pump is stopped. - In the second embodiment of the invention of
FIG. 2 , the auxiliary vacuum pump can be of type dry screw, claw, multi-stage Roots, diaphragm, dry rotary vane or lubricated rotary vane, as in the first embodiment of the invention ofFIG. 1 . - Although diverse embodiments have been described, it is well understood that it is not conceivable to identify in an exhaustive way all the possible embodiments. Of course replacing a described means with an equivalent means can be envisaged without departing from the scope of the present invention. All these modifications form part of the common knowledge of one skilled in the art in the field of vacuum technology.
Claims (18)
Applications Claiming Priority (1)
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PCT/EP2014/070691 WO2016045753A1 (en) | 2014-09-26 | 2014-09-26 | Vacuum-generating pumping system and pumping method using this pumping system |
Publications (1)
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US20170298935A1 true US20170298935A1 (en) | 2017-10-19 |
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Family Applications (1)
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US15/512,883 Abandoned US20170298935A1 (en) | 2014-09-26 | 2014-09-26 | Vacuum-generating pumping system and pumping method using this pumping system |
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Country | Link |
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US (1) | US20170298935A1 (en) |
EP (1) | EP3198148B1 (en) |
JP (1) | JP2017531125A (en) |
KR (2) | KR20170063839A (en) |
CN (1) | CN107002680A (en) |
AU (1) | AU2014406724B2 (en) |
BR (1) | BR112017005927B1 (en) |
CA (1) | CA2961977A1 (en) |
DK (1) | DK3198148T3 (en) |
ES (1) | ES2780873T3 (en) |
PL (1) | PL3198148T3 (en) |
PT (1) | PT3198148T (en) |
RU (1) | RU2670640C9 (en) |
TW (1) | TWI725943B (en) |
WO (1) | WO2016045753A1 (en) |
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IT201800021148A1 (en) * | 2018-12-27 | 2020-06-27 | D V P Vacuum Tech S P A | VOLUMETRIC AUXILIARY PUMP FOR VACUUM GENERATION. |
WO2021122360A1 (en) * | 2019-12-19 | 2021-06-24 | Leybold France S.A.S. | Lubricant-sealed vacuum pump, lubricant filter and method |
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BE1027005B9 (en) | 2019-01-30 | 2020-10-19 | Atlas Copco Airpower Nv | Method of controlling a compressor to an unloaded state |
FR3094762B1 (en) * | 2019-04-05 | 2021-04-09 | Pfeiffer Vacuum | Dry type vacuum pump and pumping installation |
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- 2014-09-26 BR BR112017005927-4A patent/BR112017005927B1/en active IP Right Grant
- 2014-09-26 CN CN201480082186.8A patent/CN107002680A/en active Pending
- 2014-09-26 JP JP2017516050A patent/JP2017531125A/en active Pending
- 2014-09-26 EP EP14777077.0A patent/EP3198148B1/en not_active Revoked
- 2014-09-26 PL PL14777077T patent/PL3198148T3/en unknown
- 2014-09-26 AU AU2014406724A patent/AU2014406724B2/en active Active
- 2014-09-26 ES ES14777077T patent/ES2780873T3/en active Active
- 2014-09-26 DK DK14777077.0T patent/DK3198148T3/en active
- 2014-09-26 CA CA2961977A patent/CA2961977A1/en active Pending
- 2014-09-26 RU RU2017114347A patent/RU2670640C9/en active
- 2014-09-26 PT PT147770770T patent/PT3198148T/en unknown
- 2014-09-26 US US15/512,883 patent/US20170298935A1/en not_active Abandoned
- 2014-09-26 KR KR1020177011372A patent/KR20170063839A/en not_active IP Right Cessation
- 2014-09-26 KR KR1020217025124A patent/KR20210102478A/en not_active Application Discontinuation
- 2014-09-26 WO PCT/EP2014/070691 patent/WO2016045753A1/en active Application Filing
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2015
- 2015-09-21 TW TW104131132A patent/TWI725943B/en active
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Also Published As
Publication number | Publication date |
---|---|
CA2961977A1 (en) | 2016-03-31 |
TW201623801A (en) | 2016-07-01 |
DK3198148T3 (en) | 2020-04-06 |
RU2670640C9 (en) | 2018-12-04 |
BR112017005927A2 (en) | 2017-12-19 |
AU2014406724B2 (en) | 2019-09-19 |
EP3198148A1 (en) | 2017-08-02 |
EP3198148B1 (en) | 2020-02-26 |
PT3198148T (en) | 2020-04-02 |
WO2016045753A1 (en) | 2016-03-31 |
BR112017005927B1 (en) | 2022-07-12 |
PL3198148T3 (en) | 2020-08-10 |
AU2014406724A1 (en) | 2017-04-13 |
TWI725943B (en) | 2021-05-01 |
KR20210102478A (en) | 2021-08-19 |
CN107002680A (en) | 2017-08-01 |
KR20170063839A (en) | 2017-06-08 |
ES2780873T3 (en) | 2020-08-27 |
RU2670640C1 (en) | 2018-10-24 |
JP2017531125A (en) | 2017-10-19 |
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