EP2820307B1 - Verdrängungsschraubenverdichter - Google Patents

Verdrängungsschraubenverdichter Download PDF

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Publication number
EP2820307B1
EP2820307B1 EP13712324.6A EP13712324A EP2820307B1 EP 2820307 B1 EP2820307 B1 EP 2820307B1 EP 13712324 A EP13712324 A EP 13712324A EP 2820307 B1 EP2820307 B1 EP 2820307B1
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Prior art keywords
main body
oil
compression chamber
liquid
suited
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EP13712324.6A
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English (en)
French (fr)
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EP2820307A1 (de
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Virgilio Mietto
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Individual
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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
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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

Definitions

  • the present invention is related to the technical field of the devices for the generation of compressed gas, preferably compressed air.
  • the present invention concerns the technical field of volumetric compressors.
  • the present invention concerns an oil-injected volumetric screw compressor.
  • compressors are based on the intake of a gas, typically air, and the treatment of the same to increase its pressure while it flows towards an outlet.
  • the compressors of the known type are constituted by the so-called oil-injected volumetric screw compressors.
  • Said compressors typically comprise a casing that defines a compression chamber provided with a intake duct and a delivery duct. Inside the compression chamber there are two helical rotors, a male (generally driving) rotor and a female (generally driven) rotor that mesh with each other.
  • the compression chamber is fed with oil and the air to be compressed.
  • the compression of the air-oil mixture takes place in the volume included between the toothing of the two rotors and the casing.
  • the contact section included between the profile of the male rotor and that of the female rotor shifts. More particularly, said contact section shifts starting from the intake duct towards the delivery duct. In this way, the air-oil mixture included between the contact section and the delivery duct is compressed.
  • the air-oil mixture flowing out of the compression chamber is then subjected to a treatment to separate the oil from the compressed air.
  • the separated oil is then recovered in order to be re-used and re-introduced in the compression chamber.
  • the separation sector is thus arranged downstream of the compression chamber.
  • the separation sector typically comprises a tank.
  • the oil particles are separated from the compressed air due to a mechanical effect.
  • the air-oil mixture flowing out of the compression chamber is directed towards the tank through a channel, typically a pipe. Inside the tank the separated oil particles are deposited on the bottom of the tank, while the compressed air remains in the upper portion of the same.
  • the oil is collected from the bottom of the tank in order to recirculate it, as explained above, while on the other hand the compressed air is collected from the upper portion of the tank, further purified from any oil residues, and then made available to be let out at the desired pressure.
  • a drawback posed by the screw compressors of the known type lies in their construction complexity that is due to the need to channel the various flows along pre-determined paths, to feed oil and air into the compression chamber, to convey the oil-air mixture to the separation tank and to recirculate the oil.
  • a further drawback of said compressors is constituted by their considerable overall dimensions, in particular due to the size of the oil-air mixture separation tank.
  • the main object of the present invention is thus to solve or at least partially overcome the above mentioned problems that characterize the volumetric screw compressors known in the state of the art.
  • the present invention is based on the general consideration that the problems found in the art can be at least partially resolved by providing a gas compression device that uses a compression liquid, wherein one or more of the gas and/or liquid conveying elements are integrated in a single block or main body.
  • the subject of the present invention is thus a gas compression device of the type comprising:
  • the separation means are preferably housed at least partially in the main body. According to a preferred embodiment of the invention, the connection channel is completely made in the main body.
  • the separation means preferably comprise an element suited to convey the mixture against a surface of the main body.
  • the device comprises a tank arranged downstream of the separation means so as to receive at least the separated liquid of the mixture.
  • the tank is suited to be removably associated with the main body.
  • the device comprises a liquid recirculation circuit running from the tank to the compression chamber.
  • the recirculation circuit comprises a channel for injecting the liquid in the compression chamber, wherein the injection channel is at least partially made in the main body.
  • thermostatic valve is properly arranged along the liquid recirculation circuit.
  • the thermostatic valve comprises a body carried out in a single piece with the main body.
  • Means for filtering the liquid are preferably arranged along the liquid recirculation circuit.
  • the liquid filtering means comprise a filter that is accommodated in a supporting seat carried out in a single piece with the main body.
  • the device preferably comprises means for injecting the gas in the compression chamber.
  • the device comprises a valve body of the intake valve, wherein the valve body is carried out in a single piece with the main body.
  • the device preferably comprises conveying means arranged downstream of the separation means in order to convey the separated gas of the mixture to an oil separator filter.
  • the conveying means comprise a gas ejection channel, wherein the ejection channel is at least partially made in the main body.
  • the device comprises a liquid recovery channel suited to convey the liquid recovered by the oil separator filter to the compression chamber.
  • the liquid recovery channel is at least partially made in the main body.
  • the device comprises a viewing element for the inspection of the liquid recovery channel.
  • the compression means comprise two helical screws meshing with each other.
  • the helical screws are advantageously arranged along respective longitudinal rotation axes that are substantially parallel to each other.
  • the hydraulic connection channel comprises at least one section aligned along a corresponding axis that intersects one of the rotation axes of the helical springs.
  • the device comprises canalization means suited to convey the liquid used to lubricate the moving parts of the device.
  • liquid conveying means convey the liquid to the sliding bearings of the helical screws.
  • the canalization means preferably comprise one or more channels made inside the main body.
  • the liquid is preferably constituted by oil.
  • the gas is preferably constituted by air.
  • the present invention can be applied in particular to the production of volumetric compressors used in various sectors, for example in the mining sector, in building construction or in the industrial sector.
  • the present invention can be especially but not exclusively applied for the production of an oil-injected volumetric screw compressor powered by means of an electric motor.
  • the present invention is not limited to such application.
  • the present invention can be conveniently applied in all the cases requiring the use of a volumetric screw compressor, for example an engine-driven or motor-driven compressor (internal compression engine/motor).
  • an engine-driven or motor-driven compressor internal compression engine/motor
  • FIG 1 schematically shows the operating principle of a preferred embodiment of the oil-injected screw compressor 1 according to the present invention, hereinafter simply referred to as the "compressor".
  • the compressor 1 substantially carries out a compression treatment on an incoming gas flow Fi, typically air, with a compression liquid, typically oil, in order to obtain an outgoing flow of compressed gas Fu.
  • the oil-injected screw compressor 1 is a type of machinery of the volumetric rotary type. It is constituted by a compression chamber 2 containing two helical rotors, a male (generally driving) rotor and a female (generally driven) rotor that mesh with each other, as is explained in greater detail below.
  • the compression of the gas-oil mixture takes place in the volume included between the toothing of the two rotors and the body that defines the compression chamber 2; during rotation, the contact section included between the profile of the male rotor and the profile of the female rotor shifts starting from an intake side towards a delivery side, so that the quantity of air contained therein is compressed due to the reduction in the available volume.
  • the compressor 1 comprises an air intake valve 3, provided with an apposite intake filter 4, suited to convey the air into the compression chamber 2.
  • the compressor 1 comprises an oil supply inlet 5 suited to convey the oil into the compression chamber 2.
  • Moving means 6 allow the driving rotor to rotate inside the compression chamber 2.
  • the compressor 1 also comprises a separation sector 7 arranged downstream of the compression chamber 2, in which the compressed oil-air mixture is subjected to a separation treatment in order to provide, at the outlet, compressed air 8 on one side and oil 9 on the other side.
  • the separated oil 9 is recovered in order to be re-introduced in the compression chamber 2 through said supply inlet 5.
  • the re-introduction of said oil 9 into the compression chamber 2 is conditional on its previous passage in a thermostatic valve 10 that allows the oil 9 to flow through it towards the supply inlet 5 only if its temperature is below a pre-determined limit temperature. In fact, the oil inside the compression chamber 2 is subjected to a temperature increase.
  • the thermostatic valve therefore, allows only oil at the correct temperature to flow through it, while the oil at higher temperature is conveyed to an oil cooler 11 that lowers its temperature before it is re-introduced in the recirculation circuit.
  • Upstream of the oil supply inlet 5 there is preferably a filter 12 suited to purify the oil from any impurities.
  • the separated compressed air 8 is first conveyed to an oil separator filter 13 that separates any oil residues present in the compressed air.
  • the recovered residual oil is re-introduced in the compression chamber 2.
  • an oil recovery viewing element 14 that allows the oil to be monitored.
  • the purified compressed air flowing out of the oil separator filter 13 passes through a minimum pressure valve 15. Said valve 15 allows the passage of air through it only when the pre-determined rated pressure has been reached.
  • the air flowing out of the minimum pressure valve is preferably directed towards a cooler 16 where it is cooled down.
  • the cooled air is then conveyed to a usage tank 17, or alternatively directly to the user.
  • Part of the purified compressed air flowing out of the oil separator filter 13 is conveyed to the intake valve 3 through an apposite channel 58.
  • the air conveyed through said channel 58 represents the feedback signal that signals to the intake valve 3 when the air passage must be closed or opened.
  • the intake valve 3 is opened. If, on the contrary, the air pressure in said channel 58 is higher than or equal to the pre-determined rated pressure of the compressor, the intake valve 3 is closed.
  • the compressor 1 is described here below with reference to Figures from 2 to 12, indicating the various parts mentioned above.
  • the main body 30 is preferably produced by means of a permanent mold casting process, preferably through a metallic material casting process.
  • the metallic material preferably comprises aluminium.
  • the main body 30 can advantageously be obtained by sand casting of a cast iron alloy.
  • a tank 40 suited to collect the air 8 and the oil 9 generated downstream of the separation means 7.
  • the oil tank 40 is preferably suited to be connected to the main body 30 by means of screws, as shown in Figure 6 , in such a way as to obtain a removable structure.
  • the tank is advantageously provided with an oil discharge valve 80.
  • first rotor 21 with helical toothing, or male rotor and a second rotor 22 with helical toothing, or female rotor, which meshes with the first rotor 21.
  • the two rotors 21 and 22 are arranged substantially parallel to each other and rotate along corresponding rotation axes substantially parallel to the main axis X of the compression chamber 2.
  • the first rotor 21 is the driving rotor and is suited to be connected at one end 24 to the power means 6.
  • the second rotor 22 is the driven rotor and is set rotating by the first rotor 21.
  • the power means 6 preferably comprise an electric motor directly connected to the end 24 of the first rotor 21.
  • the power means may be of a different type, like for example a combustion engine, or they may be provided with an indirect, remote connection to a motor, for example through the interposition of a driving belt or gears.
  • the first rotor 21 preferably comprises four lobes suited to be engaged in seats provided in the second rotor 22. Said seats are five in the embodiment illustrated herein.
  • the number of lobes and/or seats of the two rotors 21, 22 may be different.
  • the top of the main body 30 is associated with the air intake valve 3 with the respective filter 4.
  • the air intake valve 3 comprises a valve body 31 that houses internal valve means, fixed to the valve body through suitable connection means, for example through screws.
  • the valve body 31 is preferably carried out in a single piece with the main body 30.
  • the air intake valve 3 communicates with the compression chamber 2 through an apposite air intake channel 32.
  • Said air intake channel 32 is preferably provided in the main body 30, as shown in Figure 9 .
  • this is achieved through a recirculation circuit that draws the oil from the bottom of the tank 40 in order to re-introduce it in the compression chamber 2.
  • the oil present on the bottom of the tank 40 is drawn, due to the effect of pressure inside the tank 40, through a suction pipe 41, visible in Figure 6 , and then conveyed to the thermostatic valve 10.
  • the thermostatic valve 10 directs the oil flow directly to the oil filter 12 and from there to the compression chamber 2. If the oil temperature exceeds the limit temperature, the thermostatic valve 10, instead, directs the oil flow towards a cooler, not illustrated herein, through a duct connected to an apposite outlet 42. The oil cooled by the cooler is re-introduced upstream of the thermostatic valve 10 through a duct connected to an apposite inlet 43.
  • the body 46 of the thermostatic valve 10 is preferably carried out in a single piece with the main body 30.
  • the supporting seat 55 of the oil filter 12 is preferably carried out in a single piece with the main body 30.
  • the oil flowing out of the oil filter 12 is conveyed to the compression chamber 2 through an oil injection channel 47, shown in Figure 8 .
  • the oil injection channel 47 is advantageously defined inside the main body 30.
  • the oil performs also a lubricating function with regard to some parts of the compressor.
  • the sliding elements, or bearings, that support the rotors 21, 22 need lubricating.
  • the oil in the system is also properly channelled in such a way as to reach those parts.
  • One of said lubrication channels 49 shown in Figure 9 , allows a minimum quantity of oil taken from the oil injection channel 47 to be conveyed to one end of the compression chamber, in the area where there are the bearings of the rotors 21, 22.
  • said lubrication channel 49 is defined inside the main body 30.
  • the oil-air mixture is thrust from the compression chamber 2 towards an outlet opening 50 by the combined action of the two rotors 21 and 22, as shown in Figure 9 .
  • the mixture is channelled from said outlet opening 50 towards the separation means 7.
  • the canalization of the mixture takes place through a hydraulic connection channel 51.
  • the hydraulic connection channel 51 is advantageously made in the main body 30.
  • the hydraulic connection channel 51 is substantially aligned along an inclined axis Y. Said axis Y of the hydraulic connection channel 51 intersects the main axis X of the compression chamber 2, as visible in Figure 9 , and thus intersects also the respective rotation axes of the first and second rotor 21 and 22.
  • the separation means 7, as illustrated in Figures 9 , 10 and 11 , are arranged under the compression chamber 2 and are preferably confined in a hollow portion 33 of the main body 30.
  • the hollow portion 33 is defined by a side perimeter wall 34 of the main body 30.
  • the side perimeter wall 34 is advantageously made in a single piece with the main body 30.
  • the separation means 7 comprise an injection element 52 suited to receive the pressurized mixture from the hydraulic connection channel 51 and to convey said mixture against the internal surface of the side perimeter wall 34.
  • the oil particles are separated from the compressed air due to a mechanical effect.
  • the flow of the mixture is directed towards a given route, indicatively shown by the arrow D1 in Figure 11 .
  • the special geometric configuration of the side wall 34 makes it possible to reduce the flow speed and thus to separate the oil particles from the air.
  • the compressed air separated from the oil instead, remains in the upper portion 40a of the tank 40.
  • the separation means 7 are partially defined by the lower portion of the main body 30 and positioned in proximity to the compression chamber 2.
  • the injection element may come in different shapes, and it may also be made in a single piece with the main body 30.
  • the separated compressed air 8 is in the upper portion 40a of the tank 40.
  • the compressed air is drawn from said area 40a through an ejection channel 60 in order to be conveyed to the oil separator filter 13.
  • Said filter 13 allows the purification of the compressed air through the elimination of residual oil particles left therein after the separation step.
  • the first portion 60a of the air ejection channel 60 is advantageously carried out inside the main body 30.
  • the oil separator filter 13 comprises a first outlet 61 for the purified compressed air and a second outlet 62 for the oil recovered after filtering, as can be seen in Figure 12 .
  • the recovered oil is re-introduced in the compression chamber 2 through a suitable oil recovery channel 62.
  • the oil recovery channel 62 is partially carried out inside the main body 30.
  • the oil recovery viewing element 14 is advantageously positioned along the oil recovery channel 62. Said viewing element 14 makes it possible to monitor the presence of oil inside the oil recovery channel 62 and thus inside the compressor 1.
  • the purified air flowing out of the oil separator filter 13 passes through the minimum pressure valve 15.
  • the outgoing flow of compressed air Fu can be preferably stored in a suitable air tank for future use.
  • the presence of a main body 30 provided with channels for the flow of oil and/or air and/or the air-oil mixture makes it possible to reduce to a minimum the length of the routes covered by said fluids and thus to reduce the pressure drops in the corresponding flows.
  • a further advantage obtained through the present invention derives from the integration of several parts of the compressor in the main body 30.
  • elements like the side perimeter wall 34 of the separation means 7, the valve body 31 of the air intake valve 3, the body 46 of the thermostatic valve 10, the supporting seat 55 of the oil filter 12 are advantageously carried out in a single piece with the main body 30.
  • the tank 40 can be associated with the main body 30 of the compressor 1 through screws. Furthermore, the separation means 7 are substantially confined in the overall volume of the main body 30. Said characteristics make the tank 40 easy to replace to equip the compressor with a tank having a different shape and/or volume.
  • the tank may be configured so that it can be placed in a remote position with respect to the main body 30, and in this case a collection element may be provided that can be applied to the underside of the main body 30 downstream of the separation means 7, for example a funnel-shaped element that collects the separated oil and conveys it to the remote tank.
  • a suitable suction unit will then be provided to bring the oil from the remote tank back to the compression chamber 2 so as to allow recirculation.
  • Figures 13 and 14 show a variant embodiment of the invention.
  • valve body 131 of the intake valve 3 constitutes a separate element that can be applied to the main body 130.
  • the other elements, that is, the side perimeter wall 34 of the separation means 7, the valve body 46 of the thermostatic valve 10 and the supporting seat 55 of the oil filter 12 are advantageously carried out in a single piece with the main body 130.
  • FIGS 15 and 16 show another variant embodiment of the invention.
  • the supporting seat of the oil filter 12 constitutes a separate element with respect to the main body 230.
  • the supporting seat of the oil filter 12 can be applied directly to the main body 230 in an apposite channel 231.
  • the supporting seat of the oil filter 12 is suited to be connected to the main body 230 through a duct connected to the same channel 231.
  • the other elements that is, the side perimeter wall 34 of the separation means 7 and the body 46 of the thermostatic valve 10, are advantageously carried out in a single piece with the main body 230.
  • Figures 17 and 18 show a further variant embodiment of the invention.
  • Said embodiment differs from the one previously described with reference to Figures 15 and 16 in that the body of the thermostatic valve, not illustrated herein, constitutes a separate element that can be applied to the main body 330.
  • the side perimeter wall 34 of the separation means 7 is advantageously made in a single piece with the main body 330.
  • the compressor that is the subject of the invention achieves all the set objects, and in particular achieves the object to provide a volumetric screw compressor having reduced size and weight compared to the compressors of the known type, though ensuring higher reliability and efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Supercharger (AREA)
  • Refuse Collection And Transfer (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Compressor (AREA)

Claims (18)

  1. Gasverdichtungsvorrichtung (1) des Typs, der Folgendes umfasst:
    - einen Hauptkörper (30; 130, 230; 330), der geeignet ist, eine Kompressionskammer (2) mit einem Einlass (32) für das besagte Gas zu definieren, wobei der besagte Hauptkörper ein einzelner Block ist;
    - eine Kompressionsflüssigkeit für das besagte Gas, dazu geeignet, in die besagte Kompressionskammer (2) eingespritzt zu werden, um ein Gemisch zu erzeugen, das die besagte Flüssigkeit und das besagte Gas enthält;
    - in der besagten Kompressionskammer (2) angeordnete Verdichtungsmittel (21, 22), die geeignet sind, das besagte Gemisch zu einem Auslass (50) der besagten Kompressionskammer (2) zu komprimieren;
    - stromabwärts des besagten Auslasses (50) angeordnete Abscheidemittel (7), die geeignet sind, das besagte Gemisch aufzunehmen und die besagte Flüssigkeit von dem besagten, im besagten Gemisch eingeschlossenen Gas abzuscheiden;
    - einen Verbindungskanal (51), dazu geeignet, den besagten Auslass (50) direkt mit den besagten Abscheidemitteln (7) zu verbinden,
    dadurch gekennzeichnet, dass der besagte Verbindungskanal (51) vollständig in dem besagten Hauptkörper (30; 130, 230; 330) ausgeführt ist.
  2. Vorrichtung gemäß Patentanspruch 1, dadurch gekennzeichnet, dass die besagten Abscheidemittel (7) wenigstens teilweise in den besagten Hauptkörper (30; 130, 230; 330) eingesetzt sind.
  3. Vorrichtung (1) gemäß eines jeden der vorstehenden Patentansprüche, dadurch gekennzeichnet, dass die besagten Abscheidemittel (7) ein Element (52) umfassen, das geeignet ist, das besagte Gemisch gegen eine Oberfläche des besagten Hauptkörpers (30; 130, 230; 330) zu leiten.
  4. Vorrichtung (1) gemäß eines jeden der vorstehenden Patentansprüche, dadurch gekennzeichnet, dass sie einen Behälter (40) umfasst, der stromabwärts von den besagten Abscheidemitteln (7) angeordnet ist, um wenigstens die besagte, abgeschiedene Flüssigkeit des besagten Gemischs aufzunehmen.
  5. Vorrichtung (1) gemäß Patentanspruch 4, dadurch gekennzeichnet, dass der besagte Behälter (40) abnehmbar mit dem besagten Hauptkörper (30; 130,230; 330) verbunden sein kann.
  6. Vorrichtung (1) gemäß Patentanspruch 4 oder 5, dadurch gekennzeichnet, dass sie einen Kreislauf für die Rezirkulation der besagten Flüssigkeit aus dem besagten Behälter (40) zu der besagten Kompressionskammer (2) umfasst.
  7. Vorrichtung (1) gemäß Patentanspruch 6, dadurch gekennzeichnet, dass der besagte Rezirkulationskreislauf einen Einspritzkanal (47) zum Einspritzen der besagten Flüssigkeit in die besagte Kompressionskammer (2) umfasst, wobei der besagte Einspritzkanal (47) wenigstens teilweise in dem besagten Hauptkörper (30; 130, 130, 230; 330) ausgeführt ist.
  8. Vorrichtung (1) gemäß Patentanspruch 6 oder 7, dadurch gekennzeichnet, dass ein Thermostatventil (10) entlang des besagten Rezirkulationskreislaufs der besagten Flüssigkeit angeordnet ist.
  9. Vorrichtung (1) gemäß Patentanspruch 8, dadurch gekennzeichnet, dass das besagte Thermostatventil (10) einen Körper (46) umfasst, der mit dem besagten Hauptkörper (30; 130, 230) eine Einheit bildet.
  10. Vorrichtung (1) gemäß eines jeden der Patentansprüche von 6 bis 9, dadurch gekennzeichnet, dass Mittel (12) zur Filterung der besagten Flüssigkeit entlang des besagten Rezirkulationskreislaufs angeordnet sind.
  11. Vorrichtung (1) gemäß Patentanspruch 10, dadurch gekennzeichnet, dass die besagten Filtermittel einen Filter (12) umfassen, der in eine Halterungsaufnahme (55) eingesetzt ist, welche mit dem besagten Hauptkörper (30;130) eine Einheit bildet.
  12. Vorrichtung (1) gemäß eines jeden der vorstehenden Patentansprüche, dadurch gekennzeichnet, dass sie Einspritzmittel (3) umfasst, die geeignet sind, das besagte Gas in die besagte Kompressionskammer (2) einzuspritzen.
  13. Vorrichtung (1) gemäß Patentanspruch 12, dadurch gekennzeichnet, dass die besagten Einspritzmittel (3) ein Einlassventil (3) für das besagte Gas umfassen.
  14. Vorrichtung (1) gemäß Patentanspruch 13, dadurch gekennzeichnet, dass sie einen Ventilkörper (31) des besagten Einlassventils (3) umfasst, wobei der besagte Ventilkörper (31) mit dem besagten Hauptkörper (30) eine Einheit bildet.
  15. Vorrichtung (1) gemäß eines jeden der vorstehenden Patentansprüche, dadurch gekennzeichnet, dass sie Fördermittel (60) umfasst, die stromabwärts von den besagten Abscheidemitteln (7) angeordnet sind, um das besagte, abgeschiedene Gas des besagten Gemisches zu einem Ölabscheidefilter (13) zu leiten.
  16. Vorrichtung (1) gemäß eines jeden der vorstehenden Patentansprüche, dadurch gekennzeichnet, dass sie Kanalisierungsmittel (49) umfasst, die geeignet sind, die besagte Flüssigkeit zur Schmierung der Bewegungsteile der besagten Vorrichtung (1) zu fördern.
  17. Vorrichtung (1) gemäß Patentanspruch 16, dadurch gekennzeichnet, dass die besagten Kanalisierungsmittel einen oder mehrere Kanäle (49) umfassen, die innerhalb des besagten Hauptkörpers (30; 130, 230; 330) ausgeführt sind.
  18. Vorrichtung (1) gemäß eines jeden der vorstehenden Patentansprüche, dadurch gekennzeichnet, dass die besagten Kompressionsmittel zwei spiralförmige Schrauben (21, 22) umfassen, die ineinander eingreifen.
EP13712324.6A 2012-02-14 2013-01-24 Verdrängungsschraubenverdichter Active EP2820307B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000036A ITVI20120036A1 (it) 2012-02-14 2012-02-14 Compressore volumetrico a vite.
PCT/IB2013/000088 WO2013121257A1 (en) 2012-02-14 2013-01-24 Volumetric screw compressor

Publications (2)

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EP2820307A1 EP2820307A1 (de) 2015-01-07
EP2820307B1 true EP2820307B1 (de) 2016-03-09

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EP (1) EP2820307B1 (de)
CN (1) CN104114868A (de)
BR (1) BR112014018802B1 (de)
ES (1) ES2569902T3 (de)
IT (1) ITVI20120036A1 (de)
RU (1) RU2610871C2 (de)
WO (1) WO2013121257A1 (de)

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CN105673498A (zh) * 2016-04-01 2016-06-15 浙江开山凯文螺杆机械有限公司 带常开进气阀的螺杆压缩机及其启动方法
DE202019104823U1 (de) 2018-09-14 2019-11-07 Atlas Copco Airpower, N.V. Gehäuse einer Flüssigkeitsabscheidungsvorrichtung zum Abscheiden einer Flüssigkeit aus einem Gas-Flüssigkeit-Gemisch
DE202019104824U1 (de) * 2018-09-14 2019-10-24 Atlas Copco Airpower, N.V. Gehäuse einer Flüssigkeitsabscheidungsvorrichtung zum Abscheiden einer Flüssigkeit aus einem Gas-Flüssigkeit-Gemisch
BE1026613B9 (nl) 2018-09-14 2020-06-08 Atlas Copco Airpower Nv Behuizing van een vloeistofafscheidingsinrichting voor het afscheiden van een vloeistof uit een gas-vloeistofmengsel
BE1027152B1 (nl) 2019-04-01 2020-10-26 Atlas Copco Airpower Nv Vloeistofafscheider voor het afscheiden van een vloeistof uit een gas-vloeistofmengsel

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Publication number Priority date Publication date Assignee Title
US3073514A (en) * 1956-11-14 1963-01-15 Svenska Rotor Maskiner Ab Rotary compressors
DE3149245A1 (de) * 1981-12-11 1983-06-16 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried "verdichteranlage"
JPH0642476A (ja) * 1992-07-24 1994-02-15 Daikin Ind Ltd スクリュー圧縮機
DE19739279C2 (de) * 1997-09-08 2001-02-01 Maid Ludwig Kompressor-Anlage
JP3994220B2 (ja) * 2000-09-01 2007-10-17 株式会社日立製作所 スクリュー圧縮機
JP4012706B2 (ja) * 2001-07-30 2007-11-21 株式会社日立産機システム 油冷式スクリュー圧縮機
BE1014611A3 (nl) * 2002-02-08 2004-01-13 Atlas Copco Airpower Nv Werkwijze voor het besturen van de olieterugvoer in een met olie geinjecteerde schroefcompressor en aldus bestuurde schroefcompressor.
JP4102891B2 (ja) * 2003-01-31 2008-06-18 株式会社日立製作所 スクリュー圧縮機
JP4043433B2 (ja) * 2003-11-14 2008-02-06 株式会社神戸製鋼所 空気圧縮機

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BR112014018802A8 (pt) 2017-07-11
BR112014018802A2 (de) 2017-06-20
RU2014137103A (ru) 2016-04-10
US20150023825A1 (en) 2015-01-22
EP2820307A1 (de) 2015-01-07
BR112014018802B1 (pt) 2021-11-16
ES2569902T3 (es) 2016-05-13
WO2013121257A1 (en) 2013-08-22
CN104114868A (zh) 2014-10-22
RU2610871C2 (ru) 2017-02-17
ITVI20120036A1 (it) 2012-05-15

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