Rotary expansible chamber devices – Heat exchange or non-working fluid lubricating or sealing – Intermixed incoming working and non-working fluids
Reexamination Certificate
1999-08-27
2001-04-17
Vrablik, John J. (Department: 3748)
Rotary expansible chamber devices
Heat exchange or non-working fluid lubricating or sealing
Intermixed incoming working and non-working fluids
C418S152000, C418S197000
Reexamination Certificate
active
06217304
ABSTRACT:
BACKGROUND OF THE INVENTION
The present invention relates to helical screw type compressors. More specifically, the present invention relates to a multi-screw compressor having, e.g., a male rotor and at least two female rotors.
Helical type compressors are well known in the art. One such helical compressor employs one male rotor axially aligned with and in communication with one female rotor. The pitch diameter of the female rotor is greater than the pitch diameter of the male rotor. Typically, the male rotor is the drive rotor, however compressors have been built with the female rotor being the drive rotor. The combination of one male rotor and one female rotor in a compressor is commonly referred to as a twin screw or rotor, such is well know in the art and has been in commercial use for decades. An example of one such twin rotor commonly employed with compressors in the HVAC (heating, ventilation and air conditioning) industry is shown in
FIG. 1
herein, labeled prior art. Referring to
FIG. 1
herein, a cross sectional view of a male rotor
10
which drives an axially aligned female rotor
12
is shown. Male rotor
10
is driven by a motor, not shown, as is well known. Male rotor
10
has four lobes
14
-
17
with a 300° wrap and female rotor
12
has six flutes
18
-
23
with a 200° wrap. Accordingly, the compression-discharge phase of the axial sweep with respect to male rotor
10
occupies about 300° of rotation. The resulting gap between the male and female rotors requires oil to be introduced into the compression area for sealing, however, the oil also provides cooling and lubricating, as is well known. However, the introduction of this oil requires the use of an oil separation device, to separate the oil from the refrigerant being compressed in HVAC compressors. The primary benefit of the twin rotor configuration is the low interface velocity between the male and female rotors during operation. However, the twin rotor configuration is not balanced and therefore incurs large radial bearing loads and thrust loads. The obvious solution to alleviating the bearing load problem would be to install sufficiently sized bearings. This is not a feasible solution, since the relative diameters of the rotors in practice result in the rotors being too close together to allow installation of sufficiently sized bearings.
The prior art has addressed this problem, with the introduction of compressors employing ‘so-called’ single screw technology. Referring to
FIGS. 2 and 3
herein, labeled prior art, a drive rotor
24
with two opposing axially perpendicular gate rotors
26
and
28
is shown. Rotor
24
is driven by a motor, not shown, as is well known. Rotor
24
has six grooves
30
and each gate rotor
26
,
28
has eleven teeth
32
,
34
, respectively, which intermesh with grooves
30
. The gate rotors
26
and
28
are generally comprised of a composite material which allows positioning of the gate rotor at a small clearance from the drive rotor. This clearance is small enough that the liquid refrigerant itself provides sufficient sealing, the liquid refrigerant also provides cooling and lubrication. The rearward positioning of gate rotors
26
and
28
and the positioning on opposing sides of drive rotor
24
, (1) allows equalizing suction of pressure at both ends of rotor
24
thereby virtually eliminating the thrust loads encountered with the above described twin screw system and (2) balances the radial loading on rotor
24
thereby minimizing radial bearing loads. However, the interface velocity between the gate rotors and the drive rotor are very high. Accordingly, a common problem with this system is the extensive damage suffered by the rotors when lubrication is lost, due to the high interface velocities of the rotors.
SUMMARY OF THE INVENTION
The above-discussed and other drawbacks and deficiencies of the prior art are overcome or alleviated by the multi-rotor compressor of the present invention. In accordance with the present invention, the compressor includes a male rotor which is axially aligned with and in communication with at least two female rotors. The male rotor is driven by a motor, in other words the male rotor is the drive rotor. The male rotor has a plurality of lobes which intermesh with a plurality of flutes on each of the female rotors. The pitch diameters of the female rotors are now less than the pitch diameter of the male rotor.
The male rotor comprises an inner cylindrical metal shaft with an outer composite material ring mounted thereon. The ring includes the lobes of the male rotor integrally depending therefrom. The lobes of the male rotor being comprised of a composite material allows positioning of the female rotors at a small clearance from the male drive rotor. This clearance is small enough that the liquid refrigerant itself provides sufficient sealing, however, the liquid refrigerant also provides cooling and lubrication.
The positioning of the female rotors on opposing sides of the male rotor balances the radial loading on the male rotor thereby minimizing radial bearing loads. Further, due to a larger diameter male drive rotor as compared to the male drive rotor in the prior art twin screw compressors, and therefore, additional distance between the rotors, any female radial bearing loads can be easily accommodated with sufficiently sized bearings. It will also be appreciated, that interface velocity between the male and female rotors during operation is very low, whereby the extensive damage suffered by the prior art single screw compressors when lubrication is lost, due to the high interface velocities of the rotors, is reduced.
The above-discussed and other features and advantages of the present invention will be appreciated and understood by those skilled in the art from the following detailed description and drawings.
REFERENCES:
patent: 2481527 (1949-09-01), Nilsson
patent: 2652192 (1953-09-01), Chilton
patent: 2868442 (1959-01-01), Nilsson
patent: 4515540 (1985-05-01), Pillis
patent: 4776779 (1988-10-01), Crump
patent: 5165881 (1992-11-01), Wicen
patent: 5653585 (1997-08-01), Fresco
patent: 2409554 (1975-09-01), None
patent: 648055 (1950-12-01), None
patent: 60-56104 (1985-04-01), None
patent: 4-203383 (1992-07-01), None
Cantor & Colburn LLP
Vrablik John J.
LandOfFree
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