WO2005042980A1 - Improved water-injected screw-type compressor - Google Patents

Improved water-injected screw-type compressor Download PDF

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Publication number
WO2005042980A1
WO2005042980A1 PCT/BE2004/000149 BE2004000149W WO2005042980A1 WO 2005042980 A1 WO2005042980 A1 WO 2005042980A1 BE 2004000149 W BE2004000149 W BE 2004000149W WO 2005042980 A1 WO2005042980 A1 WO 2005042980A1
Authority
WO
WIPO (PCT)
Prior art keywords
water
type compressor
motor
injected screw
compressor according
Prior art date
Application number
PCT/BE2004/000149
Other languages
French (fr)
Other versions
WO2005042980A8 (en
Inventor
Anton Van Hal
Bart Anton Lode Talboom
Willy Joseph Rosa Bodart
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
Publication of WO2005042980A1 publication Critical patent/WO2005042980A1/en
Publication of WO2005042980A8 publication Critical patent/WO2005042980A8/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/086—Carter
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present invention concerns an improved water-injected screw-type compressor.
  • the invention concerns a water- injected screw-type compressor whose co-operating rotors are provided with hydrostatic and/or hydrodynamic bearings .
  • a water-injected screw-type compressor is usually mainly composed of a motor or another drive and a compressor element which is provided with two cooperating rotors .
  • the above-mentioned hydrostatic and/or hydrodynamic bearings are usually provided on either side of the rotor concerned, more particularly on the shaft onto which the rotor is fixed, and they are usually connected to pressure channels for the supply of water under pressure.
  • Said bearings compensate the axial as well as the radial forces which act on the rotors, resulting among others from the built-up pressure differences in the screw- type compressor or caused by the mutual operation of the rotors.
  • the radial forces are usually compensated by hydrodynamic and hydrostatic bearings, and the axial forces are usually absorbed by a combination of hydrostatic bearings and a pressure chamber at the height of the crosscut far ends of the bearings on the " shafts.
  • One of both rotors is usually provided with a shaft, what is called the primary shaft, which is driven either directly or via a transmission by a motor or with any other driving means .
  • Said primary shaft is hereby exposed to forces resulting from the motor, whereby especially the axially directed forces cannot be absorbed by the above-mentioned water- lubricated bearings.
  • a known solution to this problem consists in that a belt transmission is provided between the motor or the other driving means and the primary shaft, and that extra bearings are provided at the height of the primary shaft.
  • a disadvantage is that such a combination of a belt transmission and bearings occupies much space and is expensive, and that the torque to be transmitted is restricted.
  • the present invention aims an improved water- injected screw-type compressor which excludes the above- mentioned and other disadvantages.
  • An advantage is that forces resulting from the motor or the like are absorbed by the elastic coupling, such that no complex devices are required to absorb the axial forces exerted by the motor.
  • a reduction is provided between the elastic coupling and the motor, which can be provided more in particular in a compartment of the above-mentioned housing and which is separated from a compartment in which the elastic coupling is provided, whereby the housing is configured such that the compressor element is situated at a distance from the reduction, such that there is a separation between the water-injected compressor element and the oil-lubricated reduction.
  • This . embodiment of the water-injected screw-type compressor is particularly suitable when the motor speed cannot be variably controlled.
  • figure 1 schematically represents a water-injected screw-type compressor according to the invention, seen as a section;
  • figure 2 represents a section according to line 11 -I I in figure 1;
  • figure 3 represents a view similar to that in figure 1, but for a variant of the embodiment.
  • the water-injected compressor as represented in figure 1, is mainly composed of a compressor element 1, a transmission 2 and a motor 3 or the like.
  • the motor 3 is in this case a motor with a variable rotational speed, and it is equipped with a motor shaft forming the driving shaft 4 of the compressor element 1 and with a fastening flange 5 for the transmission 2.
  • the motor 3 and the compressor element 1 are connected to each other by means of an elastic coupling 6 which is part of the transmission 2.
  • the driving shaft 4 is provided on a first coupling part 7 which mainly consists of a bush 8 with which is connected a flange 9 on one far end, whereby, crosswise to the flange 9, are provided axially directed fingers 10.
  • the driving shaft 4 is provided with a disc 11 on its crosscut far end, which is provided 'on the driving shaft 4 by means of a bolt 12 in order to fix the bush 8 on the driving shaft .
  • the primary shaft 16 and the secondary shaft 17 ' are provided with different water-lubricated bearings 18 on either side of the rotors 14, 15 respectively, which are provided in the housing 13 of the compressor element 1, whereby the bearings 18 on the far ends of the shafts 16 and 17 are provided the farthest away from the transmission in a pressure chamber 19.
  • the above-mentioned water-lubricated bearings 18 and also the pressure chambers 19 are connected to the pressure channels.
  • the primary shaft 16 is led through an opening 20 in the housing 13, where the primary shaft 16 is provided with a sealing 21 which is connected to the housing 13 by means of a lid 22.
  • the primary shaft 16 which is situated in the prolongation of the driving shaft 4 of the motor 3, extends over a distance in relation to the connecting wall 23 of the housing 13 of the compressor element 1, and is provided with a second coupling part 24 of the elastic coupling 6 on this free end, which works in conjunction with the coupling part 7 in an axially shifting manner.
  • the ring 26 is in this case connected to the bush 25 at the height of one far end, whereby, between the above- mentioned bush 25 and the ring 26, a cavity 27 is created which is open on the crosscut end of the second coupling part 24.
  • Figure 2 shows how the outer wall of the bush 25 is provided with axially directed grooves 28 in the cavity 27. In a similar manner, opposite to each of the above- mentioned grooves 28, is provided a corresponding groove 29 on the inner wall of the ring 26.
  • the cavity 27 has a knurled inner and outer casing.
  • an elastic ring 30 whose inner wall is provided with teeth 31 which can work in conjunction with the grooves 28 in the outer wall of the bush 25, and whose outer wall is provided with teeth 32 which can work in conjunction with the grooves 29 in the inner wall of the ring 26. Further, the elastic ring 30 is provided with axially directed reces ses 33 which are open on the cro s s cut end of the second coupling part 24 .
  • a housing 34 of the transmission 2 On the flange 5 , which is provided with screw holes near • its circumferential edge , is provided a housing 34 of the transmission 2 , in this case by means of bolts .
  • the housing 34 which is directed crosswise to the driving shaft 4 of the motor 3 at the height of the connection with the f lange 5 , and which is further mainly parallel to the driving shaft 4 of the motor 3 , reaches up to a distance D of the flange 5 , where the hous ing 34 i s again directly mainly cros swise to the driving shaft 4 , and is connected in a suitable manner to the connecting wall 23 of the housing 13 of the compressor element 1.
  • the fingers 10 of the first coupling part 7 are in this case situated in a circle whose diameter corresponds to the diameter of the cavity 27.
  • the dimensions and the mutual positions of the fingers 10 correspond to the dimensions and the mutual positioning of the axially directed recesses 33.
  • the first coupling part 7 and the second coupling part 24 are provided such on the driving shaft 4, on the primary shaft 16 respectively, that the fingers 10 work in conjunction with the axially directed recesses 33, such that both coupling parts 7 and 24 can be moved practically freely in relation to each other in the axial direction, such that forces and vibrations in the axial direction must not be mutually transmitted at all or hardly.
  • the housing 34 of the transmission 2 forms a sheathing around the elastic coupling 6 and also functions as a spacer sleeve in this case between the compressor element 1 and the motor 3.
  • the space which is confined by the housing 34 is preferably connected to the ambient pressure via one or several openings 34 A at the bottom of the housing 34.
  • the housing 34 hereby guarantees a physical distance D between the flange 5 of the motor 3 and the connecting wall 23 of the housing 13 of the compressor element 1, such that oil or grease, possibly coming from the motor 3, is prevented from ending up in the compressor element 1 of the water-injected screw-type compressor.
  • the housing 34 is provided with a partition wall 36, such that an oil-lubricated compartment 37 is created which is covered by a lid 38 with which the housing 34 is fixed to the motor 3, and an oil-free compartment 39 in which the elastic coupling 6 is provided.
  • the intermediate shaft 42 in this case forms the driving shaft of the compressor element 1, whereby the elastic coupling 6 forms the connection between this driving shaft and the primary shaft 16.
  • the working of this variant differs from the first embodiment in that a reduction 35 is present in this case, whereby the compressor element 1 is being driven at a higher speed than the rotational speed of the motor 3.
  • the distance between the partition wall 36 and the connecting wall 23 of the housing 13 of the compressor element 1 is equal to D.
  • the distance D between the oil-lubricated compartment 37 and the compre s sor element 1 prevents that oil which would seep anyhow via the seal ing element 45 in the oil-free compartment 39 would end up in the compressor element 1 of the water-inj ected screw-type compressor .
  • the oil-free compartment 39 is preferably connected to the ambient pressure by means of a bottom opening 34A.
  • the elastic coupling 6 can also be built differently, for example by providing the first coupling part 7 and the second coupling part 24 with fingers 10 which are positioned differently and having either or not a different shape , with cavities 27 which are positioned differently and having either or not a different shape respectively .
  • housing 34 may assume other shapes , as long as a rigid structure is provided between the compressor element 1 and the motor 3 of the reduction 35 , if the latter is provided, and that this housing 34 can for example be made of several pieces .
  • the housing 34 is preferably configured such that the above-mentioned distance D between the water-injected compressor element 1 and the oil-lubricated motor 3 of the oil-lubricated reduction 35 is larger than 5 centimetres, preferably larger than 10 centimetres, and better still larger than 15 centimetres.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Water-injected screw-type compressor which is mainly composed of a compressor element (1) and a motor (3) or the like and a transmission (2) situated in between, characterised in that the transmission is formed of a housing (34) with which the compressor element (1) and the motor (3) are fixed to each other at a distance from each other, and of an elastic coupling (6) between the compressor element (1) and the motor (3).

Description

Improved water-injected screw-type compressor.
The present invention concerns an improved water-injected screw-type compressor.
More particularly, the invention concerns a water- injected screw-type compressor whose co-operating rotors are provided with hydrostatic and/or hydrodynamic bearings .
A water-injected screw-type compressor is usually mainly composed of a motor or another drive and a compressor element which is provided with two cooperating rotors . The above-mentioned hydrostatic and/or hydrodynamic bearings are usually provided on either side of the rotor concerned, more particularly on the shaft onto which the rotor is fixed, and they are usually connected to pressure channels for the supply of water under pressure.
Said bearings compensate the axial as well as the radial forces which act on the rotors, resulting among others from the built-up pressure differences in the screw- type compressor or caused by the mutual operation of the rotors.
The radial forces are usually compensated by hydrodynamic and hydrostatic bearings, and the axial forces are usually absorbed by a combination of hydrostatic bearings and a pressure chamber at the height of the crosscut far ends of the bearings on the" shafts.
One of both rotors is usually provided with a shaft, what is called the primary shaft, which is driven either directly or via a transmission by a motor or with any other driving means .
Said primary shaft is hereby exposed to forces resulting from the motor, whereby especially the axially directed forces cannot be absorbed by the above-mentioned water- lubricated bearings.
A known solution to this problem consists in that a belt transmission is provided between the motor or the other driving means and the primary shaft, and that extra bearings are provided at the height of the primary shaft.
A disadvantage is that such a combination of a belt transmission and bearings occupies much space and is expensive, and that the torque to be transmitted is restricted.
Another known solution makes use of a complex gearbox with a mechanism which compensates the axial forces exerted by the rotors .
Also this solution is expensive, occupies much space and moreover is liable to wear. Besides, such amechanism is oil-lubricated, and the proximity of oil- lubricated parts is undesirable in case of the water- injected compressor element and not tolerable in this application .
The present invention aims an improved water- injected screw-type compressor which excludes the above- mentioned and other disadvantages.
To this end, the invention concerns a water-injected screw-type compressor which is mainly composed of a compressor element and a motor or the like, and a transmission situated in between, whereby the transmission consists of a housing with which the compressor element and the motor are fixed to each other at a distance from each other, and of an elastic coupling between the compressor element and the motor.
An advantage is that forces resulting from the motor or the like are absorbed by the elastic coupling, such that no complex devices are required to absorb the axial forces exerted by the motor.
Another advantage is that a certain distance is maintained between the water-i jected compressor element and the oil-lubricated motor, such that oil or grease possibly originating from the motor cannot end up in the air or water circuit of the compressor element, and that, vice versa, water from the compressor element cannot mix with the lubricating oil or grease of the motor, as a result of which the lubrication qualities of the oil or grease would be lost.
According to a special embodiment, a reduction is provided between the elastic coupling and the motor, which can be provided more in particular in a compartment of the above-mentioned housing and which is separated from a compartment in which the elastic coupling is provided, whereby the housing is configured such that the compressor element is situated at a distance from the reduction, such that there is a separation between the water-injected compressor element and the oil-lubricated reduction.
This . embodiment of the water-injected screw-type compressor is particularly suitable when the motor speed cannot be variably controlled.
In order to better explain the characteristics of the invention, the following preferred embodiments of a water-injected screw-type compressor according to the invention are described as an example only without being limitative in any way, with reference to the accompanying drawings, in which:
figure 1 schematically represents a water-injected screw-type compressor according to the invention, seen as a section; figure 2 represents a section according to line 11 -I I in figure 1; figure 3 represents a view similar to that in figure 1, but for a variant of the embodiment.
The water-injected compressor, as represented in figure 1, is mainly composed of a compressor element 1, a transmission 2 and a motor 3 or the like. The motor 3 is in this case a motor with a variable rotational speed, and it is equipped with a motor shaft forming the driving shaft 4 of the compressor element 1 and with a fastening flange 5 for the transmission 2.
The motor 3 and the compressor element 1 are connected to each other by means of an elastic coupling 6 which is part of the transmission 2.
To this end, the driving shaft 4 is provided on a first coupling part 7 which mainly consists of a bush 8 with which is connected a flange 9 on one far end, whereby, crosswise to the flange 9, are provided axially directed fingers 10.
Further, the driving shaft 4 is provided with a disc 11 on its crosscut far end, which is provided 'on the driving shaft 4 by means of a bolt 12 in order to fix the bush 8 on the driving shaft .
The compressor element 1 which is provided in the prolongation of the above-mentioned driving shaft 4 mainly consists of a housing 13 with two co-operating rotors provided therein, a first rotor 14 and a second rotor 15, provided on a primary shaft 16, a secondary shaft 17 respectively .
The primary shaft 16 and the secondary shaft 17 'are provided with different water-lubricated bearings 18 on either side of the rotors 14, 15 respectively, which are provided in the housing 13 of the compressor element 1, whereby the bearings 18 on the far ends of the shafts 16 and 17 are provided the farthest away from the transmission in a pressure chamber 19.
The above-mentioned water-lubricated bearings 18 and also the pressure chambers 19 are connected to the pressure channels.
Farther removed from the first rotor 14, more particularly on the side opposite to the pressure chamber 19, the primary shaft 16 is led through an opening 20 in the housing 13, where the primary shaft 16 is provided with a sealing 21 which is connected to the housing 13 by means of a lid 22.
The primary shaft 16, which is situated in the prolongation of the driving shaft 4 of the motor 3, extends over a distance in relation to the connecting wall 23 of the housing 13 of the compressor element 1, and is provided with a second coupling part 24 of the elastic coupling 6 on this free end, which works in conjunction with the coupling part 7 in an axially shifting manner.
The second coupling part 24 mainly consists of a bush 25 with which a ring 26 is connected in a coaxial manner and concentrically with the bush 25.
The ring 26 is in this case connected to the bush 25 at the height of one far end, whereby, between the above- mentioned bush 25 and the ring 26, a cavity 27 is created which is open on the crosscut end of the second coupling part 24. Figure 2 shows how the outer wall of the bush 25 is provided with axially directed grooves 28 in the cavity 27. In a similar manner, opposite to each of the above- mentioned grooves 28, is provided a corresponding groove 29 on the inner wall of the ring 26.
In other words, the cavity 27 has a knurled inner and outer casing.
In the cavity 27 is provided an elastic ring 30 whose inner wall is provided with teeth 31 which can work in conjunction with the grooves 28 in the outer wall of the bush 25, and whose outer wall is provided with teeth 32 which can work in conjunction with the grooves 29 in the inner wall of the ring 26. Further, the elastic ring 30 is provided with axially directed reces ses 33 which are open on the cro s s cut end of the second coupling part 24 .
On the flange 5 , which is provided with screw holes near • its circumferential edge , is provided a housing 34 of the transmission 2 , in this case by means of bolts .
The housing 34 , which is directed crosswise to the driving shaft 4 of the motor 3 at the height of the connection with the f lange 5 , and which is further mainly parallel to the driving shaft 4 of the motor 3 , reaches up to a distance D of the flange 5 , where the hous ing 34 i s again directly mainly cros swise to the driving shaft 4 , and is connected in a suitable manner to the connecting wall 23 of the housing 13 of the compressor element 1.
The working of the above-described water-injected screw-type compressor according to the invention is very simple and as follows .
The working of the motor 3 and of the compressor element 1 is well known and does not require any further explanation, such that especially the working of the elastic coupling 6 will be illustrated hereafter.
The fingers 10 of the first coupling part 7 are in this case situated in a circle whose diameter corresponds to the diameter of the cavity 27.
More particularly, the dimensions and the mutual positions of the fingers 10 correspond to the dimensions and the mutual positioning of the axially directed recesses 33.
In the axial direction as well, the first coupling part 7 and the second coupling part 24 are provided such on the driving shaft 4, on the primary shaft 16 respectively, that the fingers 10 work in conjunction with the axially directed recesses 33, such that both coupling parts 7 and 24 can be moved practically freely in relation to each other in the axial direction, such that forces and vibrations in the axial direction must not be mutually transmitted at all or hardly.
Also the deviations from the ideal mutual position whereby the driving shaft 4 is perfectly aligned with the primary shaft 16 of the compressor element 1 are absorbed by the elastic ring 30.
When the motor 3 excites the driving shaft 4, possible sudden angular rotations will be transmitted to the primary shaft 16 of the compressor element 1 in a merely damped manner.
Naturally, the damping characteristic depends on the material out of which the elastic ring 30 is made.
The housing 34 of the transmission 2 forms a sheathing around the elastic coupling 6 and also functions as a spacer sleeve in this case between the compressor element 1 and the motor 3. The space which is confined by the housing 34 is preferably connected to the ambient pressure via one or several openings 34 A at the bottom of the housing 34.
The housing 34 hereby guarantees a physical distance D between the flange 5 of the motor 3 and the connecting wall 23 of the housing 13 of the compressor element 1, such that oil or grease, possibly coming from the motor 3, is prevented from ending up in the compressor element 1 of the water-injected screw-type compressor.
Figure 3 represents a variant whereby a reduction 35 is provided between the transmission 2 and the motor 3.
To this end, the housing 34 is provided with a partition wall 36, such that an oil-lubricated compartment 37 is created which is covered by a lid 38 with which the housing 34 is fixed to the motor 3, and an oil-free compartment 39 in which the elastic coupling 6 is provided.
The reduction 35 is in this case formed of a first gear wheel 40 fixed to the outgoing shaft 4 of the motor 3 and a second gear wheel 41 working in conjunction with it which is provided on an intermediate shaft 42, which intermediate shaft 42 is bearing-mounted in the partition wall 36 and in the lid 38, by means of a bearing 43 and a bearing 44 respectively, whereby the intermediate shaft 42 forming the outgoing shaft of the reduction 35, protrudes through the partition wall 36 with one far end and whereby the passage of this intermediate shaft is printed by means of a sealing element 45.
The intermediate shaft 42 in this case forms the driving shaft of the compressor element 1, whereby the elastic coupling 6 forms the connection between this driving shaft and the primary shaft 16.
The working of this variant differs from the first embodiment in that a reduction 35 is present in this case, whereby the compressor element 1 is being driven at a higher speed than the rotational speed of the motor 3.
In this embodiment, the distance between the partition wall 36 and the connecting wall 23 of the housing 13 of the compressor element 1 is equal to D. The distance D between the oil-lubricated compartment 37 and the compre s sor element 1 prevents that oil which would seep anyhow via the seal ing element 45 in the oil-free compartment 39 would end up in the compressor element 1 of the water-inj ected screw-type compressor .
The oil-free compartment 39 is preferably connected to the ambient pressure by means of a bottom opening 34A.
It is clear that the elastic coupling 6 can also be built differently, for example by providing the first coupling part 7 and the second coupling part 24 with fingers 10 which are positioned differently and having either or not a different shape , with cavities 27 which are positioned differently and having either or not a different shape respectively .
It is also clear that the housing 34 may assume other shapes , as long as a rigid structure is provided between the compressor element 1 and the motor 3 of the reduction 35 , if the latter is provided, and that this housing 34 can for example be made of several pieces .
The housing 34 is preferably configured such that the above-mentioned distance D between the water-injected compressor element 1 and the oil-lubricated motor 3 of the oil-lubricated reduction 35 is larger than 5 centimetres, preferably larger than 10 centimetres, and better still larger than 15 centimetres.
The present invention is by no means limited to the above-described embodiment represented in the figures; on the contrary, such an improved water- injected screw-type compressor can be made in different shapes and dimensions while still remaining within the scope of the invention.

Claims

Claims .
1. Water-injected screw-type compressor which is mainly composed of a compressor element (1) and a motor (3) or the like and a transmission (2) situated in between, characterised in that the transmission is formed of a housing (34) with which the compressor element (1) and the motor (3) are fixed to each other at a distance from each other, and of an elastic coupling (6) between the compressor element (1) and the motor (3) .
2. Water-injected screw-type compressor according to claim 1, characterised in that the elastic coupling (6) is mainly formed of a first coupling part (7) connected to the motor (3) or the like; and a second coupling part (24) connected to the compressor element (1), which coupling parts (7-24) work in conjunction in an axially shifting manner, in order to make sure that axial forces resulting from the motor (3) are absorbed by the elastic coupling (6).
3. Water-injected screw-type compressor according to claim 1, characterised in that between the elastic coupling (6) and the motor (3) is provided a reduction (35.
4. Water-injected screw-type compressor according to claim 3, characterised in that the housing (34) is divided, by means of a partition wall (36), in a compartment (37) for the above-mentioned reduction (35) and in a compartment (39) in which the above- mentioned elastic coupling (6) is provided.
5. Water-injected screw-type compressor according to claim 4, characterised in that the reduction (35) is formed of at least two co-operating gear wheels (40- 41), one gear wheel (40) of which is fixed to the driving shaft (4) of the motor (3) and the other gear wheel of which is fixed to the outgoing shaft (42) of the reduction (35), which outgoing shaft (42) protrudes through an opening in the partition wall (36) in the compartment (39) of the coupling (6) .
6. Water-injected screw-type compressor according to claim 5, characterised in that, around the outgoing shaft (42) of the reduction (35), is provided a sealing element (45) to seal the above-mentioned opening in the partition wall (36) .
7. Water-injected screw-type compressor according to claim 1, characterised in that at the bottom of the housing (34) of the transmission (2) is provided a passage (34A) which forms a connection between the compartment (39) of the coupling (6) and the environment.
8. Water-injected screw-type compressor according to claims 2 and 5, characterised in that the first coupling part (7) is provided on the driving shaft (4) of the motor (3) or on the outgoing shaft (42) of the reduction (35) , whereas the second coupling part (24) is provided on the primary ingoing shaft (16) of the compressor element (1) .
9. Water-injected screw-type compressor according to claim 2, characterised in that the first coupling part (7) is mainly formed of a bush (8) which is provided with at least one axially directed protrusion (10) ; and in that the second coupling part (24) is mainly formed of a bush (25) in which is provided at least one axially directed cavity (27) .
10. Water-injected screw-type compressor according to claim 8, characterised in that in the cavity (27) is provided an elastic ring (30) in which is provided at least one mainly axially directed recess (33) .
11. Water-injected screw-type compressor according to claim 2, characterised in that the second coupling part (24) is mainly formed of a bush (25) with which is connected a ring (26), in a coaxial manner, and concentrically to the bush (25), whereby the space between the bush (25) and the ring (26) is at least partly open on one far end and thus forms a mainly axial cavity (27) .
12. Water-injected screw-type compressor according to claim 11, characterised in that the outer wall of the bush (25) is provided with axially directed grooves
(28); that the inner wall of the ring (26) is provided with grooves (29) ; and that an elastic ring (30) is provided in the cavity (27) whose inner wall is provided with teeth (31) which can work in conjunction with the grooves (28), and whose outer wall is provided with teeth (32) which can work in conjunction with the grooves (29); and in that the ring (26) is provided with mainly axially directed recesses (33).
13. Water-injected screw-type compressor according to claim 1, characterised in that the distance (D) between the compressor element (1) and the motor (3) is larger than 5 centimetres, preferably larger than 10 centimetres, better still larger than 15 centimetres .
14. Water-injected screw-type compressor according to claim 5, characterised in that the distance (D) between the compressor element (1) and the reduction (35) is larger than 5 centimetres, preferably larger than 10 centimetres, and better still larger than 15 centimetres.
PCT/BE2004/000149 2003-10-28 2004-10-21 Improved water-injected screw-type compressor WO2005042980A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BE2003/0575A BE1015752A3 (en) 2003-10-28 2003-10-28 Improved water injected screw compressor.
BE2003/0575 2003-10-28

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITVI20130021A1 (en) * 2013-01-31 2013-05-02 Virgilio Mietto VOLUMETRIC COMPRESSOR EQUIPPED WITH A IMPROVED LUBRICATION SYSTEM.
WO2015137028A1 (en) * 2014-03-10 2015-09-17 株式会社神戸製鋼所 Screw compressor
CN106567920A (en) * 2015-10-07 2017-04-19 阿特拉斯·科普柯空气动力股份有限公司 Transmission and compressor device of the same
EP3516221B1 (en) 2016-09-21 2022-04-20 KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH Screw compressor system for a utility vehicle

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GB645848A (en) * 1947-04-03 1950-11-08 Ljungstroms Angturbin Ab Improvements in or relating to elastic fluid actuated power systems
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JPH06193573A (en) * 1992-12-24 1994-07-12 Hitachi Ltd Inverter-driven screw compressor and assembly thereof
US20010036417A1 (en) * 2000-04-28 2001-11-01 Yasuhiro Hioki Screw compressor
US20020049089A1 (en) * 2000-10-25 2002-04-25 Yasuo Tabuchi Flexible joint

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GB645848A (en) * 1947-04-03 1950-11-08 Ljungstroms Angturbin Ab Improvements in or relating to elastic fluid actuated power systems
GB847462A (en) * 1958-12-30 1960-09-07 Atlas Copco Ab Improvements in screw-rotor compressors
US3407996A (en) * 1966-06-22 1968-10-29 Atlas Copco Ab Screw compressor units
GB1190977A (en) * 1967-08-19 1970-05-06 Holset Engineering Co Flexible Coupling
DE4033154C1 (en) * 1990-10-12 1992-01-09 Zwickauer Maschinenfabrik Gmbh, O-9541 Zwickau, De Air cooled screw compressor - has motor housing and air compressor block flanges coupled via connector
JPH06193573A (en) * 1992-12-24 1994-07-12 Hitachi Ltd Inverter-driven screw compressor and assembly thereof
US20010036417A1 (en) * 2000-04-28 2001-11-01 Yasuhiro Hioki Screw compressor
US20020049089A1 (en) * 2000-10-25 2002-04-25 Yasuo Tabuchi Flexible joint

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITVI20130021A1 (en) * 2013-01-31 2013-05-02 Virgilio Mietto VOLUMETRIC COMPRESSOR EQUIPPED WITH A IMPROVED LUBRICATION SYSTEM.
WO2015137028A1 (en) * 2014-03-10 2015-09-17 株式会社神戸製鋼所 Screw compressor
JP2015169180A (en) * 2014-03-10 2015-09-28 株式会社神戸製鋼所 screw compressor
CN106062370A (en) * 2014-03-10 2016-10-26 株式会社神户制钢所 Screw compressor
CN106062370B (en) * 2014-03-10 2018-10-16 株式会社神户制钢所 Screw compressor
US10167868B2 (en) 2014-03-10 2019-01-01 Kobe Steel, Ltd. Screw compressor
CN106567920A (en) * 2015-10-07 2017-04-19 阿特拉斯·科普柯空气动力股份有限公司 Transmission and compressor device of the same
CN106567920B (en) * 2015-10-07 2021-08-17 阿特拉斯·科普柯空气动力股份有限公司 Transmission and compressor installation provided with said transmission
EP3516221B1 (en) 2016-09-21 2022-04-20 KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH Screw compressor system for a utility vehicle

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