The present invention relates to a screw compressor for compressing a refrigerant gas or other gases.
Conventionally, there has been provided a screw compressor in which, as shown in an enlarged sectional view of
More specifically, as shown in
In
As shown in
However, in the above-described conventional screw compressor, as shown in
Accordingly, an object of the present invention is to provide a screw compressor which can be improved in compression performance by reducing leakage of the gas through a space between the tooth portions of the gate rotor.
In order to achieve the above object, a screw compressor according to the present invention comprises:
a casing having a cylinder;
a cylindrical-shaped screw rotor which is fitted to the cylinder and which has a plurality of spiral-shaped groove portions in its outer peripheral surface;
a gate rotor having, in its outer peripheral surface, a plurality of tooth portions which are engaged with the groove portions of the screw rotor, respectively, to define compression chambers; and
a seal portion placed not on compression chambers side of one surface of the gate rotor but on the other surface side of the gate rotor opposite to the one surface side, wherein
the seal portion blocks a space between neighboring tooth portions of the gate rotor.
According to the screw compressor of this invention, the seal portion is placed on the other surface side of the gate rotor, and the seal portion blocks the space between neighboring tooth portions. Therefore, the seal portion blocks the gas within each of the compression chambers from passing through the space between the neighboring tooth portions and going out from the one surface of the gate rotor to the other surface side.
Thus, gas leakage from the space between neighboring tooth portions of the gate rotor can be reduced, so that the compression performance can be improved.
In one embodiment of the screw compressor,
the casing has a seal surface faced to the one surface of the gate rotor, and
one surface of the seal portion faced to the seal surface has a shape substantially corresponding to a shape of part of the seal surface faced to the seal portion with the gate rotor interposed therebetween.
According to the screw compressor of this embodiment, the one surface of the seal portion faced to the seal surface with the gate rotor interposed therebetween has a shape substantially corresponding to a shape of part of the seal surface faced to the seal portion with the gate rotor interposed therebetween. Therefore, by making the shape of the seal portion corresponding to the shape of the seal surface, gas leakage can be prevented efficiently.
In one embodiment of the screw compressor,
gas is sucked from a suction side of one end of the screw rotor in its shaft direction, while the gas within each of the compression chambers is discharged from a discharge side of the other end of the screw rotor in the direction of the shaft, and
the seal portion is provided more on the discharge side in the shaft direction of the screw rotor than a plane containing a shaft of the gate rotor and perpendicular to the shaft of the screw rotor.
According to the screw compressor of this embodiment, the seal portion is provided more on the discharge side in the shaft direction of the screw rotor than a plane containing a shaft of the gate rotor and perpendicular to the shaft of the screw rotor. Therefore, the seal portion can be made smaller, so that space for mounting the seal portion can be reduced.
In one embodiment of the screw compressor, a material of the seal portion is polyphenylene sulfide resin.
According to the screw compressor of this embodiment, the material of the seal portion is polyphenylene sulfide resin. Therefore, even if the seal portion is brought into contact with the screw rotor or the gate rotor shaft, the seal portion is cut or chopped off so that mechanical damage thereof can be reduced.
According to the screw compressor of this invention, since the seal portion is placed on the other surface side of the gate rotor and the seal portion blocks the space between neighboring tooth portions, gas leakage from the space between neighboring tooth portions of the gate rotor can be reduced so that the compression performance can be improved.
Hereinbelow, the present invention will be described in detail by way of embodiments thereof illustrated in the accompanying drawings.
The screw rotor 2 has, on its outer peripheral surface, a plurality of spiral-shaped groove portions 21. The gate rotor 3 is disc-shaped and has, on its outer peripheral surface, a plurality of tooth portions 31 in a gear-like form. The groove portions 21 of the screw rotor 2 and the tooth portions 31 of the gate rotor 3 are engaged with each other, respectively.
By mutual engagement of the screw rotor 2 and the gate rotor 3, compression chambers C are defined. That is, these compression chambers C are spaces defined by the groove portions 21 of the screw rotor 2, the tooth portions of the gate rotor 3, and an inner surface of the cylinder 10 of the casing 1.
The gate rotor 3 is placed in one pair on the right and left hands of the screw rotor 2 in left-and-right point symmetry with respect to a shaft 2a of the screw rotor 2. The casing 1 has a through hole 12 extending through the cylinder 10, and the gate rotor 3 is coming into the cylinder 10 through this through hole 12.
The screw rotor 2 rotates in an arrow R direction about the shaft 2a, and along with this rotation of the screw rotor 2, the gate rotor 3 rotates to compress the gas within each of the compression chambers C. The screw rotor 2 is rotated by a (not shown) motor housed in the casing 1.
Into each of the compression chambers C, a low-pressure gas is sucked from the suction side of one end of the screw rotor 2 in the shaft 2a direction, and the low-pressure gas is compressed in the compression chamber C, and then the compressed high-pressure gas is discharged from a discharge hole 13 provided on the discharge side at the other end of the screw rotor 2 in the shaft 2a direction.
As shown in an enlarged sectional view of
In
The seal surface 11 of the casing 1 is a surface which adjoins the inner surface of the cylinder 10. The seal surface 11 of the casing 1 extends in a direction parallel to the shaft 2a of the screw rotor 2.
The one surface 30 of the gate rotor 3 forms part of inner surface of each of the compression chambers C. Between the seal surface 11 of the casing 1 and the one surface 30 of the gate rotor 3 is a gap of, for example, about 60 μm.
With regard to the width of the seal surface 11 of the casing 1, width on a gas-discharge side of the screw rotor 2 is larger than width on the gas-suction side of the screw rotor 2. In addition, with regard to the width of the seal surface 11, width on the gas-discharge side of the screw rotor 2 may be equal to width on the gas-suction side of the screw rotor 2.
The gate rotor 3 is mounted on a gate rotor shaft 4. The gate rotor shaft 4 has a base portion 41, and a shaft portion 42 attached to the base portion 41. The one surface 30 of the gate rotor 3 and the other surface 32 are attached to the base portion 41.
The base portion 41 has a shape corresponding to the shape of the gate rotor 3. That is, the tooth portions of the base portion 41 has a shape corresponding to the tooth portions 31 of the gate rotor 3 and also corresponding to a space S between neighboring tooth portions 31. The shaft portion 42 is supported by the casing 1.
On the other surface 32 side of the gate rotor 3 is placed a seal portion 5. That is, the seal portion 5 is faced to the seal surface 11 with the gate rotor 3 and the base portion 41 interposed therebetween. The seal portion 5 blocks the space S between neighboring tooth portions 31.
The seal portion 5 is a platy member fitted to the casing 1. The seal portion 5 is slightly apart from the base portion 41. A material of the seal portion 5 is, for example, polyphenylene sulfide resin.
One surface 50 of the seal portion 5 is faced to the seal surface 11 with the gate rotor 3 interposed therebetween. The one surface 50 has a shape substantially corresponding to part of the seal surface 11 faced to the seal portion 5 with the gate rotor 3 interposed therebetween. That is, with regard to the width of the one surface 50 of the seal portion 5, width on a gas-discharge side of the screw rotor 2 is larger than width on the gas-suction side of the screw rotor 2. In addition, with regard to the width of the one surface 50 of the seal portion 5, width on the gas-discharge side of the screw rotor 2 may be equal to width on the gas-suction side of the screw rotor 2.
The seal portion 5 is provided more on the discharge side in the shaft 2a direction of the screw rotor 2 than a plane P containing a shaft 3a of the gate rotor 3 and perpendicular to the shaft 2a of the screw rotor 2.
According to the screw compressor constructed as described above, the seal portion 5 is placed on the other surface 32 side of the gate rotor 3, and the seal portion 5 blocks the space S between neighboring tooth portions 31. Therefore, the seal portion 5 blocks the gas within each of the compression chambers C from passing through the neighboring tooth portions 31 and going out from the one surface 30 of the gate rotor 3 to the other surface 32 side. That is, the gas within each of the compression chambers C can be prevented from passing through the neighboring tooth portions 31 and leaking out to the low-pressure space S having the gate rotor 3 housed therein.
Thus, gas leakage from the space S between neighboring tooth portions 31 of the gate rotor 3 can be reduced, so that the compression performance can be improved.
Also, when the one surface 50 of the seal portion faced to the seal surface 11 with the gate rotor 3 interposed therebetween has a shape substantially corresponding to the shape of part of the seal surface 11 faced to the seal portion 5 with the gate rotor 3 interposed therebetween, the space S can be blocked so that gas leakage can be prevented efficiently.
Also, the seal portion 5 is provided more on the discharge side in the shaft 2a direction of the screw rotor than the plane P containing the shaft 3a of the gate rotor 3 and perpendicular to the shaft 2a of the screw rotor 2. Thus, the seal portion 5 can be made smaller, so that space for mounting the seal portion 5 can be reduced.
That is, since the gas pressure within the compression chambers C becomes higher on the discharge side of the screw rotor 2, most of gas leakage passing through the space S is from the discharge side (higher-pressure part in compression chamber C) of the screw rotor 2, and gas leakage from the suction side (lower-pressure part in compression chamber C) of the screw rotor 2 is small. Therefore, the seal portion 5 may be provided only on the discharge side (higher-pressure part in compression chamber C) of the screw rotor 2.
The material of the seal portion 5 is polyphenylene sulfide resin. Therefore, even if the seal portion 5 is brought into contact with the screw rotor 2 or the gate rotor shaft 4, the seal portion 5 is cut or chopped off so that mechanical damage thereof can be reduced.
The present invention is not limited to the above-described embodiment. For example, the one surface of the seal portion 5 may be formed into a shape different from that of the seal surface 11. The seal portion 5 may be provided also on the suction side in the shaft 2a direction of the screw rotor 2 than the plane P. The seal portion 5 may be provided as part of the casing 1. Further, the material of the seal portion 5 may be other than polyphenylene sulfide resin. The quantity of the gate rotor 3 may be increased or decreased.
As shown in
Number | Date | Country | Kind |
---|---|---|---|
2007-340540 | Dec 2007 | JP | national |
2008-328297 | Dec 2008 | JP | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
---|---|---|---|---|
PCT/JP2008/073759 | 12/26/2008 | WO | 00 | 6/25/2010 |