This application claims priority from German Patent Application No. 10 2005 058 698.8, filed Dec. 8, 2005, and PCT Application No. PCT/LP2006/005559, filed Jun. 9, 2006, both of which are incorporated by reference herein.
The invention pertains to a screw compressor with the features indicated in the preamble of claim 1.
Screw compressors of this type are known from EP 0 993 553 B1 and EP 1 163 452 B1, for example. In these references, a vent channel that is open to the atmosphere is connected to the relief chamber of the sealing arrangement.
The present invention has particular advantages when applied to a screw compressor that compresses a gaseous medium such as air to very high pressures, for example in the range of 30 to 50 bar, and in particular where the application involves the high pressure stage of a two or three stage compressor system. The invention relates to such a multi-stage screw compressor system, in particular a three-stage screw compressor system.
Due to the high compression in the compressor, the sealing arrangements that seal the pressurized side of the rotor shafts in the rotor housing are subjected to a very high pressure load. Even if the sealing arrangement consists of a large number of sequentially arranged seal rings, the pressure drop across the entirety of the sealing arrangement is not even, but rather it occurs primarily at the seal rings located external to the rotor, i.e. the farthest ones from it. Consequently, they are subjected to a higher mechanical load.
The object of the invention is to construct the sealing arrangement on the pressurized side of the shaft of a screw compressor of the type indicated such that the pressure drop along the sealing arrangement can be controlled and smoothed out so that the reliability of the seal can be improved, especially for very high final pressures in the screw compressor.
The solution to this objective is indicated in claim 1. The dependent claims refer to further advantageous features of the invention.
According to the invention, it was found that by providing a defined intermediate pressure at a defined intermediate position in the sealing arrangements on the pressurized side of the rotor shafts, the pressure in the sealing arrangement drops in a controlled, even manner. The result is an especially effective and reliable seal, and the minimization of pressure losses as a result of gas leakage.
In one construction, the invention provides a screw compressor with a rotor housing (1) in which two screw rotors (3, 5) are rotatably held with parallel axes. The rotors mesh into one another with screw-shaped ribs and grooves and which convey a gaseous medium during operation, in particular air, from a suction-side end toward a pressurized end of the rotors, thereby compressing it, wherein each of the rotors has a shaft pin (7a, 7b, 9a, 9b) at its suction-side end and its pressure-side end, respectively. The pins are held in the rotor housing (1) by means of bearings (13, 15) and are sealed by means of respective sealing arrangements. The sealing arrangement (11, 11′) of each pressure-side shaft pin has an annular relief chamber (51) to which a vent channel (53) is connected. The screw compressor characterized in that the vent channel (53) connects the relief chamber (51) to a chamber (10) within the screw compressor in which a pressure exists during operation of the screw compressor that is higher than atmospheric pressure but lower than the outlet pressure of the screw compressor.
One embodiment of the invention is explained in more detail with the help of the drawings. Shown are:
The screw compressor shown in
The upper rotor 3 in
When the screw compressor shown in
Rotor housing 1 is surrounding by a cooling jacket or cooling housing 21, which is for the most part designed as one-piece together with rotor housing 1, surrounding the same at a distance. Above and below, the cooling housing 21 has large openings that are closed off using a cover plate 23 and a base plate 25 fastened with bolts. Between the rotor housing 1 and the cooling housing 21, 23, 25 is an annular cooling space 27 that surrounds the rotor housing 1.
The cooling housing 21 has an inlet opening 31 and an outlet opening 33 for coolant fluid, e.g. cooling water or oil. The inlet opening 31 opens up into a perpendicular entrance channel 35 that runs vertically upward, the upper exit opening 35′ of which is situated opposite the bottom of the separating wall 29 at a distance. Prior to the outlet opening 33 is a perpendicular exit channel 37, the lower entrance opening 37′ of which is situated opposite the top of the separating wall 29 at a distance.
The black arrow in
There is a small vent opening 41 in the wall 39 that separates the exit channel 37 from the cooling chamber 27 at a height that roughly corresponds to the upper edge of the outlet opening 33. While filling the cooling chamber 27 with coolant, this vent opening 41 allows air to escape, as indicated in
A very small bleed opening 47 is placed in the wall 45 that separates the entrance channel 35 from the cooling chamber 27 at the level of the lower edge of the inlet opening 31. When the cooling fluid is emptied from the cooling chamber 27, cooling fluid can drain out (as indicated by the lower dotted arrow in
The relief chamber 51 is connected to the intake chamber 10 of the screw compressor via a connection channel 53 incorporated into the rotor housing 1 running parallel to the rotor axis. The annular relief chamber 51 is thus exposed to the intake pressure of the screw compressor present in the intake chamber 10. In the preferred use of the screw compressor as a high pressure stage of a multistage compressor system, the air fed to the intake chamber 10 can have already been pre-compressed by the upstream compressor stages to a pressure of between 10 and 15 bar, for example, in particular about 12 bar. This, then, is the pressure that is present in the relief chamber 51. As the compressor is operated, the high final pressure produced by the rotors, for example 40 bar, must drop to zero through the sealing arrangement 11a, 11b. It has been shown that this pressure drop is not linear, but concentrates primarily on the outer radial seal rings 11b that are some distance away from the profile section 7, 9 and therefore these seals are very heavily loaded mechanically. A defined intermediate pressure is established, by way of the first relief chamber 51 being exposed to the pressure at the inlet to the compressor, at a defined point of the sealing arrangement, and thus the pressure drop along the entire sealing arrangement 11a, 11b is smoothed out. This mechanically relieves the seals 11b.
A second annular relief chamber 55 is provided at the far end of the sealing arrangement 11 away from the rotor. This chamber is connected to the atmosphere in a known fashion. The purpose of this second relief chamber 55 is to maintain the oil system that lubricates the bearings 15 and the synchronization gears 17, 19 at zero pressure and to prevent bleed gas from passing through the sealing arrangement 11 through to the oil-lubrication areas.
As can be seen from
As shown in
Not shown in
The screw compressor 80 of the third stage is a screw compressor according to the invention according to
Number | Date | Country | Kind |
---|---|---|---|
10 2005 058 698 | Dec 2005 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
---|---|---|---|---|
PCT/EP2006/005559 | 6/9/2006 | WO | 00 | 5/20/2008 |
Publishing Document | Publishing Date | Country | Kind |
---|---|---|---|
WO2007/065487 | 6/14/2007 | WO | A |
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Number | Date | Country | |
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20090004036 A1 | Jan 2009 | US |