Patent Grant
8992195
This U.S. National stage application claims priority under 35 U.S.C §119 (a) to Japanese Patent Application No. 2007-329094, filed in Japan on Dec. 20, 2007, the entire contents of which are hereby incorporated herein by reference.
The present invention relates to a screw compressor.
As described in Japanese Unexamined Patent Application Publication Nos. 2000-257578 an 2003-286986 a conventional screw compressor that comprises a screw rotor, which has helical grooves, and a gate rotor, which comprises a plurality of teeth that meshes with the helical grooves, is known.
In such a screw compressor, driving a screw rotor with a motor compresses a compression medium, which is sucked from one end of the screw rotor into a casing, in compression chambers, which are formed by the casing, the grooves of the screw rotor, and the teeth of the gate rotor, and, after the teeth of the gate rotor disengage from the grooves, high pressure gas is discharged from the other end side of the screw rotor.
However, in both of the conventional screw compressors recited in the abovementioned Japanese Unexamined Patent Application Publication Nos. 200-257578 and 2003-286986, because sucking occurs from one end side of the screw rotor and discharging from the other end side, the compression medium leaks from, for example, a labyrinth seal, which is a high pressure side seal portion provided in the vicinity of the high pressure side of the screw rotor between the screw rotor and the casing, thereby causing a decline in performance.
In addition, regarding the balance of pressure applied to the screw rotor, a thrust load is continuously applied to the screw rotor in one direction from the low pressure side to the high pressure side, and therefore the structure makes completely eliminating the thrust load difficult.
Furthermore, normally, if the capacity of the screw compressor is increased, then compressor efficiency improves; however, if the capacity exceeds a certain level, then pressure loss, leakage at the seal portion, and the like will occur, all of which reduces compressor efficiency. Accordingly, it is difficult to improve the performance of a large capacity screw compressor because larger capacities cause the compression medium to leak at the seal portion.
An object of the present invention is to provide a screw compressor that can reduce leakage on the high pressure side and reduce the thrust load.
A screw compressor according to a first aspect of the present invention comprises a rotatable screw rotor and a plurality of gate rotors. The rotatable screw rotor has helical grooves in its outer circumferential surface. In the gate rotors, a plurality of teeth that meshes with the grooves of the screw rotor is radially disposed. The helical grooves comprise: a first screw groove, which compresses a fluid from one end side of the screw rotor to an other end side; and a second screw groove, which compresses the fluid from the other end side of the screw rotor to the one end side.
Here, the helical grooves of the screw rotor, namely, the two types of screw grooves, comprise the first screw groove, which compresses the fluid from one end side of the screw rotor to the other end side, and the second screw groove, which compresses the fluid from the other end side to the one end side of the screw rotor. Thereby, it is possible to reduce, in the vicinities of thrust bearings at end parts of a conventional screw rotor, the leakage of a refrigerant on a high pressure side; thereby, it is possible to manufacture a compact, high efficiency, large capacity, single screw compressor.
A screw compressor according to a second aspect of the present invention is the screw compressor according to the first aspect of the present invention, wherein the first screw groove and the second screw groove are disposed such that they are arrayed in a rotational axis direction of the screw rotor and are planarly symmetric.
Here, the first screw groove and the second screw groove are disposed such that they are arrayed in the rotational axis direction of the screw rotor and are planarly symmetric; thereby, it is possible to reduce, in the vicinities of the thrust bearings at the end parts of a conventional screw rotor, leakage of the refrigerant on the high pressure side, which makes it possible to manufacture a high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor in the direction leading from the low pressure side to the high pressure side of the first screw groove and in the direction leading from the low pressure side to the high pressure side of the second screw groove.
A screw compressor according to a third aspect of the present invention is the screw compressor according to the second aspect of the present invention, wherein the plurality of the gate rotors are disposed corresponding to the first screw groove and the second screw groove of the screw rotor such that they are arrayed in the rotational axis direction of the screw rotor and are planarly symmetric.
Here, the plurality of the gate rotors correspond to the first screw groove and the second screw groove of the screw rotor and are disposed such that they are arrayed in the rotational axis direction of the screw rotor and are planarly symmetric to one another; thereby, it is possible to reduce, in the vicinities of the thrust bearings at the end parts of a conventional screw rotor, leakage of the refrigerant gas on the high pressure side, which makes it possible to manufacture a high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor in a direction leading from the low pressure side to the high pressure side of the first screw groove and in a direction leading from the low pressure side to the high pressure side of the second screw groove.
A screw compressor according to the fourth aspect of the present invention is the screw compressor according to any one aspect of the first through third aspects of the present invention that further comprises an intermediate bearing. The intermediate bearing is disposed between a portion at which the first screw groove of the screw rotor is formed and a portion at which the second screw groove of the screw rotor is formed.
Here, the present aspect further comprises the intermediate bearing disposed between a portion at which the first screw groove is formed in the screw rotor and a portion at which the second screw groove is formed in the screw rotor; therefore, the thrust loads that act on the screw rotor can be received by the single intermediate bearing; moreover, fewer parts are needed in the portion at which the screw rotor is supported.
A screw compressor according a fifth aspect of the present invention is the screw compressor according to any one aspect of the first through third aspects of the present invention that further comprises twin bearings. The twin bearings are disposed on opposite ends of the screw rotor.
Here, the present aspect further comprises the twin bearings that are disposed on opposite ends of the screw rotor, which makes it possible to share the inlet ports or the discharge ports of the intermediate portion of the screw rotor and thereby to develop a compact, high efficiency, large capacity compressor.
A screw compressor according a sixth aspect of the present invention is the screw compressor according to any one aspect of the first through fifth aspects of the present invention that further comprising a casing that houses the screw rotor. The casing comprises inlet ports and discharge ports. The inlet ports are formed in the vicinity of both sides of the screw rotor. The inlet ports suck a compression medium into the casing. The discharge ports are formed in the vicinity of an intermediate point of the portions at which the first screw groove and the second screw groove of the screw rotor are formed. The discharge ports discharge the compression medium compressed inside the casing.
Here, the inlet ports are formed in the vicinity of both sides of the screw rotor, and the discharge ports are formed in the vicinity of the intermediate point of the portions at which the first screw groove and the second screw groove of the screw rotor are formed. Thereby, providing the inlet ports on both sides of the screw rotor makes it possible to cool the motor easily. In the case of an open type compressor, which is a compressor wherein a motor is housed in a space separate from the spaces wherein a screw rotor is housed, providing inlet ports on both sides makes it possible to reduce the leakage of the compressed gas from a seal portion of a shaft.
A screw compressor according to a seventh aspect of the present invention is the screw compressor according to any one aspect of the first through fifth aspects of the present invention that further comprises a casing that houses the screw rotor. The casing comprises discharge ports and inlet ports. The discharge ports are formed in the vicinity of both sides of the screw rotor. The discharge ports discharge a compression medium that was compressed in the casing. The inlet ports are formed in the vicinity of an intermediate point of the portions at which the first screw groove and the second screw groove of the screw rotor are formed. The inlet ports suck the compression medium into the casing.
Here, forming the inlet ports in the vicinity of the intermediate point of the portions at which the first screw groove and the second screw groove of the screw rotor are formed and forming the discharge ports in the vicinity of both sides of the screw rotor makes it possible to reduce losses in inlet pressure and to manufacture a high efficiency, single screw compressor.
A screw compressor according to an eighth aspect of the present invention is the screw compressor according to any one aspect of the first through third, sixth, and seventh aspects of the present invention, wherein the screw rotor is shaped such that it narrows from its intermediate portion to each of its ends.
Here, the screw rotor is shaped such that it narrows from its intermediate portion to each of its ends, which makes it possible to reduce, in the vicinities of the thrust bearings of the end parts of a conventional screw rotor, the leakage of the refrigerant on the high pressure side; thereby, it is possible to manufacture a compact, high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor in the direction leading from the low pressure side to the high pressure side of the first screw groove and in the direction leading from the low pressure side to the high pressure side of the second screw groove. In particular, in such a planarly symmetric, tapered screw rotor, there is no need to provide notches of, for example, the discharge cutoffs in the discharge portions on the large diameter side in order to offset the thrust loads. Moreover, in the screw compressor, the number of parts as well as the manufacturing cost can be reduced more than is the case for a conventional two-stage compression screw compressor and the like.
According to the first aspect of the present invention, it is possible to reduce, in the vicinities of thrust bearings at end parts of a conventional screw rotor, the leakage of a refrigerant on a high pressure side; thereby, it is possible to manufacture a compact, high efficiency, large capacity, single screw compressor.
According to the second aspect of the present invention, it is possible to reduce, in the vicinities of the thrust bearings at the end parts of a conventional screw rotor, leakage of the refrigerant on the high pressure side, which makes it possible to manufacture a high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor in the direction leading from the low pressure side to the high pressure side of the first screw groove and in the direction leading from the low pressure side to the high pressure side of the second screw groove.
According to the third aspect of the present invention, it is possible to reduce, in the vicinities of the thrust bearings at the end parts of a conventional screw rotor, leakage of the refrigerant on the high pressure side, which makes it possible to manufacture a high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor in a direction leading from the low pressure side to the high pressure side of the first screw groove and in a direction leading from the low pressure side to the high pressure side of the second screw groove.
According to the fourth aspect of the present invention, the thrust loads that act on the screw rotor can be received by the single intermediate bearing; moreover, fewer parts are needed in the portion at which the screw rotor is supported.
According to the fifth aspect of the present invention, it is possible to share the inlet ports or the discharge ports with the intermediate portion of the screw rotor and thereby to develop a compact, high efficiency, large capacity compressor.
According to the sixth aspect of the present invention, providing the inlet ports on both sides of the screw rotor makes it possible to cool the motor easily. In the case of an open type compressor, which is a compressor wherein the motor is housed in the space separate from the spaces wherein the screw rotor is housed, providing the inlet ports on both sides makes it possible to reduce the leakage of the compressed medium from the seal portion of the shaft.
According to the seventh aspect of the present invention, it is possible to reduce losses in inlet pressure and to manufacture a high efficiency, single screw compressor.
According to the eighth aspect of the present invention, it is possible to reduce, in the vicinities of the thrust bearings of the end parts of a conventional screw rotor, the leakage of the refrigerant on the high pressure side; thereby, it is possible to manufacture a compact, high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor in the direction leading from the low pressure side to the high pressure side of the first screw groove and in the direction leading from the low pressure side to the high pressure side of the second screw groove. In particular, in such a planarly symmetric, tapered screw rotor, there is no need to provide notches of, for example, the discharge cutoffs in the discharge portions on the large diameter side in order to offset the thrust loads. Moreover, in the screw compressor, the number of parts as well as the manufacturing cost can be reduced more than is the case for a conventional two-stage compression screw compressor and the like.
The following text explains embodiments of a screw compressor of the present invention, referencing the drawings.
<First Embodiment>
<Entire Configuration of Single Screw Compressor 1>
A single screw compressor 1 shown in
In addition, the screw compressor 1 of the first embodiment further comprises, in addition to the intermediate bearing 13, bearings 17, which support both ends of the shaft 4, as shown in
<Configuration of Screw Rotor 2>
The screw rotor 2 is a columnar rotor that has helical grooves 11a, 11b in its outer circumferential surface. The screw rotor 2 can rotate integrally with the shaft 4 inside the casing 3.
The helical grooves 11a, 11b comprise the first screw groove 11a, which compresses a fluid from one end side of the screw rotor 2 (i.e., the right side in
In addition, the first screw groove 11a and the second screw groove 11b are disposed such that they are arrayed in the rotational axis direction of the screw rotor 2 (i.e., the direction that extend along the shaft 4) and are planarly symmetric. Namely, in
The screw rotor 2 is supported by the intermediate bearing 13. The outer circumferential surface of the intermediate bearing 13 mates with an inner wall of a cylindrical portion 3d of the casing 3.
The intermediate bearing 13 is disposed between a portion at which the first screw groove 11a is formed in the screw rotor 2 and a portion at which the second screw groove 11b is formed in the screw rotor 2. Thereby, the thrust loads that act on the screw rotor 2 can be received by the single intermediate bearing 13.
The shaft 4 is coupled to the screw rotor 2, and one end of the shaft 4 is linked to a drive motor 14, which is external to the casing 3. In addition, the shaft 4 is supported on both ends by the bearings 17, which are fixed inside the casing 3.
<Configuration of Gate Rotors 5a Through 5d>
Each of the four gate rotors 5a, 5b, 5c, 5d is a rotary body wherein multiple teeth 12, which mesh with the grooves 11a, 11b of the screw rotor 2, are radially disposed and is capable of rotating around a gate rotor shaft 8. The gate rotor shaft 8 is rotatably supported by the inner wall of the casing 3. The teeth of the gate rotors 5a, 5b, 5c, 5d mesh with the grooves 11a, 11b of the screw rotor 2 through a slit 3e, which is formed in the cylindrical portion 3d of the casing 3.
The plurality of the gate rotors 5a, 5b, 5c, 5d are disposed such that they are planarly symmetric to one another and arrayed in the rotational axis direction of the screw rotor 2 corresponding to the first screw groove 11a and the second screw groove 11b of the screw rotor 2.
The gate rotor shafts 8 are inserted in respective openings 21 of the four gate rotors 5a, 5b, 5c, 5d and rotatably support the gate rotors 5a, 5b, 5c, 5d. Specifically, gate rotor supports 27, which support the gate rotors 5a, 5b, 5c, 5d, are coaxially fixed to the gate rotor shafts 8. The shape of the gate rotor supports 27 is substantially similar to, though dimensionally slightly smaller than, that of the gate rotors 5a, 5b, 5c, 5d. The gate rotors 5a, 5b, 5c, 5d are fixed by pins 24 such that they cannot rotate with respect to the gate rotor supports 27. The gate rotor shafts 8 are orthogonal to the shaft 4 of the screw rotor 2.
The teeth 12 of the gate rotors 5a, 5b, 5c, 5d are capable of meshing, through the slit 3e formed in the casing 3, with the helical grooves 11 of the screw rotor 2 in the casing 3. The four gate rotors 5a, 5b, 5c, 5d are symmetric with respect to the center of rotation of the screw rotor 2, are disposed such that they are arrayed in the rotational axis direction of the screw rotor 2 and are planarly symmetric to one another.
If the screw rotor 2 is rotated, then the teeth 12 of the gate rotors 5a, 5b, 5c, 5d can mesh sequentially with the plurality of the grooves 11.
The casing 3 has inlet ports 15 and discharge ports 16. The inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2. The inlet ports 15 suck the compression medium into the casing 3. In the casing 3 shown in
The discharge ports 16, which are on the high pressure (HP) side, are formed in the vicinity of an intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed. The discharge ports 16 discharge the compression medium compressed by compression chambers—which are formed and enclosed by the cylindrical portion 3d inside the casing 3, the screw grooves 11a, 11b, and the teeth 12 of the gate rotors 5a, 5b, 5c, 5d—to the outside of the casing 3.
Specifically, as shown in
<Explanation of Operation of Single Screw Compressor 1>
The single screw compressor 1 shown in
First, when the shaft 4 receives a rotational driving force from the motor 14 external to the casing 3, the screw rotor 2 rotates in the direction indicated by arrows R1. At this time, the teeth 12 of the gate rotors 5a, 5b, which mesh with the helical groove 11a of the screw rotor 2, are pressed to the inner wall of the helical grooves 11, and thereby the gate rotors 5a, 5b rotate in the directions of arrows R2. Moreover, the teeth 12 of the gate rotors 5c, 5d, which mesh with the helical groove 11b that is planarly symmetric with the groove 11a, are pressed to the inner wall of the helical grooves 11, and thereby the gate rotors 5c, 5d rotate in the directions of arrows R3.
At this time, the volumes of the compression chambers, which are formed and partitioned by the inner surface of the cylindrical portion 3d of the casing 3, the grooves 11a, 11b of the screw rotor 2, and the teeth 12 of the gate rotors 5a through 5d, are reduced at each of four locations of the screw rotor 2—above, below, to the left, and to the right.
Taking advantage of the reduction of the volumes of the four compression chambers corresponding to the gate rotors 5a through 5d, the refrigerant introduced from the chamber portions 3a to the low pressure spaces 3b via the inlet ports 15 of the casing 3 prior to compression is guided to the compression chambers immediately before the grooves 11 and the teeth 12 mesh with one another, the refrigerant is compressed by the reduction of the volumes of the compression chambers while the grooves 11 and the teeth 12 mesh, and, immediately after the grooves 11 and the teeth 12 unmesh, the compressed refrigerant is discharged to the outside of the casing 3 via the discharge ports 16, which open on both the upper and lower sides of the screw rotor 2.
<Characteristics of the First Embodiment>
(1)
The helical grooves 11a, 11b comprise the first screw groove 11a, which compresses the fluid from the one end side of the screw rotor 2 (i.e., the right side in
(2)
In addition, in the screw compressor 1 of the first embodiment, the first screw groove 11a and the second screw groove 11b are disposed such that they are arrayed in the rotational axis direction of the screw rotor 2 (i.e., the direction that extend along the shaft 4) and are planarly symmetric. Namely, in
(3)
In the screw compressor 1 of the first embodiment, the plurality of the gate rotors 5a, 5b, 5c, 5d correspond to the first screw groove 11a and the second screw groove 11b of the screw rotor 2 and are disposed such that they are arrayed in the rotational axis direction of the screw rotor 2 and are planarly symmetric to one another.
Thereby, it is possible to reduce, in the vicinities of the thrust bearings at the end parts of a conventional screw rotor, leakage of the refrigerant gas on the high pressure side (particularly leakage of the refrigerant from the labyrinth seal), which makes it possible to manufacture a high efficiency, large capacity, single screw compressor. In addition, it is possible to completely balance the thrust loads that act on the screw rotor 2 in the direction leading from the low pressure side to the high pressure side of the first screw groove 11a and in the direction leading from the low pressure side to the high pressure side of the second screw groove 11b (e.g., in the directions that lead from both ends of the screw rotor 2 to the intermediate bearing 13).
(4)
The screw compressor 1 of the first embodiment further comprises the intermediate bearing 13 disposed between the portion at which the first screw groove 11a is formed in the screw rotor 2 and the portion at which the second screw groove 11b is formed in the screw rotor 2. Thereby, the thrust loads that act on the screw rotor 2 can be received by the single intermediate bearing 13; moreover, fewer parts are needed in the portion at which the screw rotor 2 is supported.
(5)
In the screw compressor 1 of the first embodiment, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed. Thereby, providing the inlet ports 15 (i.e., inlet ports) on both sides of the screw rotor 2 makes it possible to cool the motor 14 easily. In the case of an open type compressor, which is a compressor wherein the motor 14 is housed in the space 3a separate from the low pressure spaces 3b wherein the screw rotor 2 is housed, providing the inlet ports 15 (i.e., inlet ports) on both sides makes it possible to reduce the leakage of the refrigerant gas from the seal portion of the shaft 4.
<Modified Example of the First Embodiment>
(A)
In the abovementioned first embodiment, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed, but the present invention is not limited thereto; for example, the arrangement of the inlet ports 15 and the discharge ports 16 may be switched.
Namely, in a modified example of the first embodiment of the screw compressor 1, as shown in
Thus, forming the inlet ports 15 in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed and forming the discharge ports 16 in the vicinity of both sides of the screw rotor 2 makes it possible to reduce losses in inlet pressure and to manufacture a high efficiency, single screw compressor.
<Second Embodiment>
The abovementioned first embodiment explained an exemplary case wherein the screw compressor comprises the intermediate bearing 13 disposed between the portion at which the first screw groove 11a of the screw rotor 2 is formed and the portion at which the second screw groove 11b of the screw rotor 2 is formed, but the present invention is not limited thereto.
As shown in
In addition, in the screw compressor 31, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed.
<Characteristics of the Second Embodiment>
(1)
The screw compressor 31 of the second embodiment further comprises the twin bearings 18a, 18b, which are disposed on opposite sides of the screw rotor 2, which makes it possible to share the inlet ports 15 or the discharge ports 16 with the intermediate portion of the screw rotor 2 and thereby to develop a compact, high efficiency, large capacity compressor.
(2)
In addition, in the screw compressor 31 of the second embodiment, as in the first embodiment, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed; therefore, providing the inlet ports 15 (i.e., inlet ports) on both sides of the screw rotor 2 makes it possible to cool the motor 14 easily. In the case of an open type compressor, which is a compressor wherein the motor 14 is housed in the space 3a separate from the low pressure spaces 3b wherein the screw rotor 2 is housed, providing the inlet ports 15 (i.e., inlet ports) on both sides makes it possible to reduce the leakage of the refrigerant gas from the seal portion of the shaft 4.
<Modified Example of the Second Embodiment>
(A)
In the abovementioned second embodiment, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed, but the present invention is not limited thereto; for example, as in the first embodiment, the arrangement of the inlet ports 15 and the discharge ports 16 may be switched.
In this case, too, as shown in
<Third Embodiment>
The abovementioned first and second embodiments explained exemplary cases wherein the columnar screw rotor 2 is adopted, but the present invention is not limited thereto; for example, it is possible to use screw rotors of various shapes.
For example, in a screw compressor 51 of the third embodiment shown in
In addition, in the screw compressor 51, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 2, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 2 are formed. Accordingly, the refrigerant is introduced from the low pressure side of both ends of the bilaterally tapered screw rotor 52, which is planarly symmetric, to the first screw groove 11a and the second screw groove 11b, and high pressure refrigerant is discharged on the high pressure side of the portion of the intermediate portion at which the girth is widest, thereby offsetting the thrust load generated on the first screw groove 11a side and the thrust load generated on the second screw groove 11b side.
In addition, as shown in
<Characteristics of the Third Embodiment>
(1)
In the screw compressor 51 of the third embodiment, the screw rotor 52 is shaped such that it narrows from its intermediate portion to each of its ends, which makes it possible to reduce, in the vicinities of the thrust bearings of the end parts of a conventional screw rotor, the leakage of the refrigerant on the high pressure side (particularly leakage of the refrigerant from the labyrinth seal); thereby, it is possible to manufacture a compact, high efficiency, large capacity, single screw compressor.
(2)
In addition, it is possible to completely balance the thrust loads that act on the screw rotor 2 in the direction leading from the low pressure side to the high pressure side of the first screw groove 11a and in the direction leading from the low pressure side to the high pressure side of the second screw groove 11b (e.g., in directions that lead from both ends of the screw rotor 52 to the intermediate bearing 13). In particular, in such a planarly symmetric, tapered screw rotor 52, there is no need to provide notches of, for example, the discharge cutoffs in the discharge portions on the large diameter side in order to offset the thrust loads.
(3)
Moreover, in the screw compressor 51, the number of parts as well as the manufacturing cost can be reduced more than is the case for a conventional two-stage compression screw compressor and the like.
(4)
In addition, in the screw compressor 51 of the third embodiment, as in the first embodiment, the inlet ports 15 are formed in the vicinity of both sides of the screw rotor 52, and the discharge ports 16 are formed in the vicinity of the intermediate point of the portions at which the first screw groove 11a and the second screw groove 11b of the screw rotor 52 are formed; thereby, providing the inlet ports 15 (i.e., inlet ports) on both sides of the screw rotor 52 makes it possible to cool the motor 14 easily. In the case of an open type compressor, which is a compressor wherein the motor 14 is housed in the space 3a separate from the low pressure spaces 3b wherein the screw rotor 52 is housed, providing the inlet ports 15 (i.e., inlet ports) on both sides makes it possible to reduce the leakage of the refrigerant gas from the seal portion of the shaft 4.
The present invention can be widely adapted a screw compressor that comprises a screw rotor and gate rotors.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2007-329094 | Dec 2007 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2008/072808 | 12/16/2008 | WO | 00 | 6/17/2010 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2009/081788 | 7/2/2009 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 30400 | Zimmern | Oct 1860 | A |
| 1735477 | Stuart | Nov 1929 | A |
| 3205874 | Renshaw | Sep 1965 | A |
| 4036567 | Sato | Jul 1977 | A |
| 4261691 | Zimmern et al. | Apr 1981 | A |
| 6398532 | Zha et al. | Jun 2002 | B1 |
| Number | Date | Country |
|---|---|---|
| 60-187785 | Sep 1985 | JP |
| 60-249689 | Dec 1985 | JP |
| 60249689 | Dec 1985 | JP |
| 03-099888 | Oct 1991 | JP |
| 08-144972 | Jun 1996 | JP |
| 2000-145675 | May 2000 | JP |
| 2000-257578 | Sep 2000 | JP |
| 2000257578 | Sep 2000 | JP |
| 2001-153074 | Jun 2001 | JP |
| 2001-182680 | Jul 2001 | JP |
| 2003-286986 | Oct 2003 | JP |
| Entry |
|---|
| Definitions of ‘Backflow’ and ‘Bilateral Symmetry’ as found in the American Heritage Dictionary of English Language located on the Internet. |
| International Preliminary Report of corresponding PCT Application No. PCT/JP2008/072808. |
| International Search Report of corresponding PCT Application No. PCT/JP2008/072808. |
| Japanese Office Action of corresponding Japanese Application No. 2007-329094 dated Oct. 6, 2009. |
| Number | Date | Country | |
|---|---|---|---|
| 20100260639 A1 | Oct 2010 | US |
