Screw type fluid machine and method of manufacturing the same

Abstract

To suppress leakage of compressed gas through a shaft hole.SOLUTION: The screw compressor 1 includes a male rotor 10 and a female rotor 20 each having a main body portion 13,23 having spiral teeth and a shaft portion 12,22 serving as a rotation shaft of the main body portion 13,23, a casing 30 defining a compression chamber 42 accommodating the main body portion 13,23 and a shaft hole 54,55 communicating with the compression chamber 42 and through which the shaft portion 12,22 passes, and a partition member 70 disposed so as to block communication between the compression chamber 42 and the shaft hole 54,55. The partitioning member 70 is in contact with the high pressure side end surface 13b, 23b of the main body portion 1323 of at least one of the male rotor 10 and the female rotor 20, and the high pressure side facing surface 53a of the casing 30 facing the high pressure side end surface 13b, 23b.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a screw-type fluid machine and a method for manufacturing the same. [Background technology]

[0002] A screw compressor, which is one type of screw-type fluid machine, compresses gas by rotating and meshing male and female rotors inside a casing. The casing has an intake port at one end and a discharge port at the other end. A screw compressor draws gas in through the intake port, compresses the gas in a compression chamber inside the casing, and discharges the compressed gas from the discharge port. Therefore, the pressure of the gas inside the casing gradually increases from one end to the other.

[0003] The high-pressure side (other end) of the casing is provided with not only a discharge port but also a shaft hole through which the shaft of the screw rotor passes. Therefore, there is a risk that high-pressure gas in the compression chamber may leak through the shaft hole. Various shaft seals have been devised to prevent such gas leakage.

[0004] For example, Patent Document 1 discloses a screw compressor having a seal ring in a shaft seal. The seal ring is arranged to fill the gap between the shaft on the discharge side and the shaft hole, and is pressed into place by the differential pressure between the inside and outside of the compression chamber. This prevents gas leakage from the gap. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Application Laid-Open No. 2018-105144 Summary of the Invention [Problem to be solved by the invention]

[0006] In a screw compressor, the discharge pressure of the compressor fluctuates depending on the demand. When such pressure fluctuations occur, the pressure differential in the structure of Patent Document 1 is released, which can cause the seal ring to tilt. This can cause the seal in the gap between the shaft and the axial hole to be released, which can lead to leakage of compressed gas through the axial hole.

[0007] An object of the present invention is to suppress leakage of compressed gas through the axial hole. [Means for solving the problem]

[0008] The present invention provides a male rotor and a female rotor, each having a main body with spiral teeth and a shaft serving as a rotation axis of the main body; a casing that defines a compression chamber that accommodates the main body portion and a shaft hole that communicates with the compression chamber and through which the shaft portion passes; a partition member disposed to block communication between the compression chamber and the axial hole; Equipped with The present invention provides a screw-type fluid machine, wherein the partition member is in contact with the high-pressure side end surface of the main body portion of at least one of the male rotor and the female rotor and the high-pressure side opposing surface of the casing that faces the high-pressure side end surface.

[0009] With this configuration, the partition member can block communication between the compression chamber and the axial bore, thereby suppressing leakage of compressed gas through the axial bore. In particular, the partition member is sandwiched between the high-pressure end face and the high-pressure opposing surface, so its position and orientation do not change. This ensures that the gap between the high-pressure end face and the high-pressure opposing surface is filled reliably, sealing the compression chamber. Here, the partition member contacts the high-pressure end face of the rotating main body and the high-pressure opposing surface of the non-rotating casing, resulting in friction between them. Therefore, the present invention may be applied to a liquid-cooled screw-type fluid machine in which a liquid such as oil or water can be supplied to the partition member to lubricate and cool the frictional areas.

[0010] The material of the partition member may be softer than the material of the main body and the casing.

[0011] According to this configuration, the partition member is subjected to friction as described above, and because it is relatively soft, it is worn down to reduce its thickness and make its surface smooth, thereby reducing rotational resistance.

[0012] The screw type fluid machine may be an oil-cooled type.

[0013] According to this configuration, the partition member can be lubricated with oil, thereby reducing the friction. In particular, oil has a higher boiling point than other liquids such as water, making it suitable for use at high temperatures.

[0014] The high-pressure side opposing surface may be provided with a recess in which the partition member is disposed.

[0015] According to this configuration, the partition member can be disposed in the recess, and therefore the storage capacity of the partition member is improved compared to when there is no recess.

[0016] The partition member may be arranged to entirely cover at least one of the high-pressure side end face of the male rotor and the high-pressure side end face of the female rotor.

[0017] According to this configuration, the gap between the high-pressure side end surface and the high-pressure side opposing surface of at least one of the male rotor and the female rotor can be filled and sealed with the partition member.

[0018] The partition member may have a shape that follows an inner circumferential surface of the casing that defines the compression chamber.

[0019] With this configuration, the entire gap between the high-pressure side end surface and the high-pressure side opposing surface can be sealed.

[0020] The screw type fluid machine may further include a low-pressure port through which a relatively low-pressure fluid passes and a high-pressure port through which a relatively high-pressure fluid passes, The partition member may be provided with a high pressure port through hole that is connected to the high pressure port.

[0021] This configuration can prevent the flow of compressed gas from the compression chamber to the high-pressure port from being obstructed.

[0022] The present invention provides a male rotor and a female rotor, each having a main body with spiral teeth and a shaft serving as a rotation axis of the main body, a compression chamber for accommodating the main body, a casing defining an axial hole communicating with the compression chamber and through which the shaft passes, and a partition member; The male rotor and the female rotor are housed in the compression chamber; The partition member is arranged so as to block communication between the compression chamber and the axial hole while being in contact with a high-pressure side end surface of the main body portion of at least one of the male rotor and the female rotor and a high-pressure side opposing surface of the casing opposing the high-pressure side end surface. The present invention provides a method for manufacturing a screw-type fluid machine, which includes: [Effects of the Invention]

[0023] According to the present invention, leakage of compressed gas through the axial hole can be suppressed. [Brief explanation of the drawings]

[0024] [Figure 1] 1 is a perspective view of a screw compressor according to a first embodiment. [Figure 2] 1 is an exploded perspective view of a screw compressor according to a first embodiment. [Figure 3] 1 is a cross-sectional view of a screw compressor according to a first embodiment. [Figure 4] FIG. 6 is an exploded perspective view of a screw compressor according to a second embodiment. [Figure 5] FIG. 5 is a cross-sectional view of a screw compressor according to a second embodiment. [Figure 6] FIG. 10 is an exploded perspective view of a screw compressor according to a third embodiment. [Figure 7] FIG. 10 is a cross-sectional view of a screw compressor according to a third embodiment. [Figure 8] FIG. 10 is an exploded perspective view of a screw compressor according to a fourth embodiment. [Figure 9] FIG. 10 is a cross-sectional view of a screw compressor according to a fourth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0025] Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

[0026] (First embodiment) 1 to 3, a screw type fluid machine 1 according to a first embodiment of the present invention is, for example, a screw type compressor. Therefore, hereinafter, the screw type fluid machine 1 will also be referred to as a screw type compressor 1.

[0027] In each drawing, the X direction is the left-right direction, the Y direction is the front-rear direction, and the Z direction is the up-down direction. However, this does not limit the arrangement direction of the screw compressor 1, but is for convenience of explanation.

[0028] The screw compressor 1 takes in external air, compresses it internally, and discharges it, but may compress any gas other than air.

[0029] The screw compressor 1 has a male rotor 10 and a female rotor 20 having helical teeth that mesh with each other, and a casing 30 that houses the male rotor 10 and the female rotor 20 so that they can rotate.

[0030] The male rotor 10 has a shaft portion 11 at one end (rear side), a shaft portion 12 at the other end (front side), and a central main body portion 13. The female rotor 20 has a shaft portion 21 at one end (rear side), a shaft portion 22 at the other end (front side), and a central main body portion 23. The shaft portions 11, 21 at one end and the shaft portions 12, 22 at the other end form the rotation axes of the main bodies 13, 23.

[0031] In this embodiment, the shaft portion 11 on one end of the male rotor 10 is mechanically connected to a motor (not shown). The male rotor 10 is rotated by the motor, and the female rotor 20 is rotated in conjunction with the rotation of the male rotor 10.

[0032] Due to the rotational meshing of the male rotor 10 and the female rotor 20, the air compressed by the male rotor 10 and the female rotor 20 gradually becomes higher in pressure from one end to the other end in the main bodies 13, 23. Hereinafter, the end faces on one end of the main bodies 13, 23 will be referred to as low-pressure end faces 13a, 23a, respectively, and the end faces on the other end will be referred to as high-pressure end faces 13b, 23b, respectively.

[0033] In this embodiment, the casing 30 has a rotor casing 40 disposed on the rear side and a discharge casing 50 disposed on the front side.

[0034] The rotor casing 40 has an intake port (low-pressure port) 41 through which air at relatively low pressure (atmospheric pressure in this embodiment) passes. In the example shown, the intake port 41 is provided in the upper part of the rotor casing 40. The rotor casing 40 defines a compression chamber 42 that houses the main bodies 13, 23 of the male rotor 10 and the female rotor 20. The compression chamber 42 communicates with the intake port 41. In addition, an annular flange portion 43 that forms the joint with the discharge casing 50 is provided in the front part of the rotor casing 40.

[0035] The discharge casing 50 has a discharge port (high-pressure port) 51 (see FIG. 1 ) through which air at a relatively high pressure (higher than atmospheric pressure in this embodiment) passes. In this embodiment, the discharge port 51 is provided so as to open at the rear and lower part of the discharge casing 50, and is connected to the compression chamber 42 at the rear part and is open to the outside of the casing 30 at the lower part. In addition, an annular flange portion 52 is provided at the rear part of the discharge casing 50, which forms a joint with the rotor casing 40. The flange portion 52 forms the periphery of a flat end wall 53 provided at the rear part of the discharge casing 50.

[0036] The discharge casing 50 is provided with shaft holes 54, 55, and the end wall 53 is provided with openings on one end sides of the shaft holes 54, 55. The shaft holes 54, 55 are cylindrical through-holes through which the shaft portions 12, 22 on the other end sides (front sides) of the male rotor 10 and the female rotor 20 pass, respectively. In front of the shaft holes 54, 55 are provided bearing chambers 56, 57 that house bearings 58, 59, respectively. The bearings 58, 59 journal the shaft portions 12, 22, respectively. The bearings 58, 59 are, for example, rolling bearings. Specifically, the bearings 58, 59 may be angular contact ball bearings, ball bearings, or cylindrical roller bearings.

[0037] Furthermore, the surface of end wall 53 that faces high-pressure side end surfaces 13b, 23b is referred to as high-pressure side facing surface 53a. A gap D (see FIG. 3) exists between high-pressure side end surfaces 13b, 23b and high-pressure side facing surface 53a. Gap D fluidly connects compression chamber 42 and axial holes 54, 55. Therefore, gap D needs to be filled in order to seal compression chamber 42 from axial holes 54, 55.

[0038] In this embodiment, communication between the compression chamber 42 and the axial holes 54, 55 is blocked by partition members 71, 72 arranged in the gap D. The partition members 71, 72 are, for example, annular washers. The partition member 71 is arranged around the shaft portion 12 of the male rotor 10. The partition member 71 contacts the high-pressure side end face 13b of the main body portion 13 of the male rotor 10 and the high-pressure side opposing surface 53a of the casing 2 that faces the high-pressure side end face 13b. The inner diameter of the partition member 71 is larger than the outer diameter of the shaft portion 12. The outer diameter of the partition member 71 is smaller than the tooth root diameter and tooth tip diameter of the main body portion 13 and larger than the inner diameter of the axial hole 54. The partition member 72 is also arranged around the shaft portion 22 of the female rotor 20. The partition member 72 is in contact with the high-pressure side end surface 23b of the main body 23 of the female rotor 20 and the high-pressure side opposing surface 53a of the casing 2 that faces the high-pressure side end surface 23b. The inner diameter of the partition member 72 is larger than the outer diameter of the shaft portion 22. The outer diameter of the partition member 72 is smaller than the tooth root diameter and tooth tip diameter of the main body 23 and larger than the inner diameter of the axial hole 55. In this manner, the gap D (see FIG. 3) between the high-pressure side end surfaces 13b, 23b and the high-pressure side opposing surface 53a is sealed by the partition members 71, 72. When there is no need to distinguish between the partition members 71, 72, they may be collectively referred to as the partition member 70. This also applies to the following embodiments.

[0039] In this embodiment, the high-pressure side opposing surface 53a is provided with recesses 61, 62 having shapes complementary to the partition members 71, 72. The recesses 61, 62 are annularly formed along the edges of the axial holes 54, 55, respectively. The depths of the recesses 61, 62 are smaller than the thicknesses of the partition members 71, 72, respectively. That is, the partition members 71, 72 protrude from the high-pressure side opposing surface 53a when disposed in the recesses 61, 62, respectively. The amount of protrusion is equal to the size of the gap D between the high-pressure side end faces 13b, 23b and the high-pressure side opposing surface 53a. When it is not necessary to distinguish between the recesses 61, 62, they may be collectively referred to as the recess 60. This also applies to the following embodiments.

[0040] In this embodiment, the material of the partition member 70 is softer than the materials of the main bodies 13, 23 and the casing 30. For example, the main bodies 13, 23 are made of steel, the casing 30 is made of cast iron, and the partition member 70 is made of a softer metal or resin. Specific examples of the metal material of the partition member 70 include copper-based alloys, white metal, aluminum-based alloys, and wear-resistant cast iron. Specific examples of the resin material of the partition member 70 include polytetrafluoroethylene (PTFE), polyacetal resin (POM), polyether ether ketone resin (PEEK), polyphenylene sulfide resin (PPS), polyester-based elastomer resin (TPEE / TPC), polyamide resin (PA), and resins containing these as their main components.

[0041] In the illustrated example, the partition member 70 is provided for both the male rotor 10 and the female rotor 20, but the partition member 70 may be provided for only one of the male rotor 10 and the female rotor 20. In other words, the partition member 70 may be provided for at least one of the male rotor 10 and the female rotor 20.

[0042] In this embodiment, a liquid such as oil or water is used to cool the compression chamber 42 and to lubricate the bearings 58, 59 and the partition members 71, 72. Generally, there are two types of compressors: a liquid-cooled type in which a liquid such as oil or water is injected into the compression chamber, and an oil-free type in which a liquid such as oil or water is not injected into the compression chamber. The screw-type compressor 1 of this embodiment is a liquid-cooled type in which a liquid is used for lubrication and cooling, and in particular, an oil-cooled type in which oil is used as the liquid.

[0043] Oil supply passages 53b, 53c through which oil flows are formed in discharge casing 50. Oil supply passages 53b, 53c fluidly connect an oil supply source (not shown) provided outside casing 30 to axial holes 54, 55, allowing oil to flow from the supply source to axial holes 54, 55. Note that the configuration of oil supply passages 53b, 53c is not limited to that shown in the drawing and may be any configuration.

[0044] The screw-type fluid machine 1 of this embodiment can be manufactured by inserting the male rotor 10 and the female rotor 20, each having partition members 71 and 72 attached to the shaft portions 12 and 22, into the rotor casing 40, and then assembling the discharge casing 50 to the rotor casing 40. This manufacturing method allows the partition members 70 (71 and 72) to come into contact with the high-pressure side end faces 13b and 23b and the high-pressure side opposing surface 53a.

[0045] The screw compressor 1 of this embodiment provides the following advantages.

[0046] Partition member 70 can block communication between compression chamber 42 and axial holes 54, 55, thereby suppressing leakage of compressed air through axial holes 54, 55. In particular, partition member 70 is disposed between high-pressure side end faces 13b, 23b and high-pressure side opposing surface 53a, and therefore can seal gap D between high-pressure side end faces 13b, 23b and high-pressure side opposing surface 53a without changing its position or posture, thereby suppressing leakage of compressed air from compression chamber 42 to axial holes 54, 55.

[0047] Furthermore, the partition member 70 is subjected to friction because it comes into contact with the high-pressure side end faces 13b, 23b of the rotating main bodies 13, 23 and the high-pressure side opposing surface 53a of the non-rotating casing 30. Therefore, because the material of the partition member 70 is softer than the materials of the main bodies 13, 23 and the casing 30, the thickness of the partition member 70 is reduced by abrasion and the surface becomes smooth, thereby reducing rotational resistance.

[0048] Furthermore, since the screw compressor 1 is oil-cooled, the partition member 70 can be lubricated with oil, thereby reducing the friction. In particular, oil has a higher boiling point than other liquids such as water, and is therefore suitable for use at high temperatures.

[0049] Furthermore, since the partition member 70 can be disposed in the recess 60, the storage capacity of the partition member 70 is improved compared to when the recess 60 is not present.

[0050] (Second embodiment) 4 and 5, the screw type fluid machine 1 of the second embodiment does not have the recess 60 of the first embodiment. Other than this, the screw type fluid machine 1 is substantially the same as the first embodiment. Therefore, the description of the parts shown in the first embodiment may be omitted.

[0051] In this embodiment, the high-pressure side opposing surface 53b does not have the recess 60 (see FIG. 2). Therefore, the thickness of the partition members 71, 72 is equal to the size of the gap D between the high-pressure side end surfaces 13b, 23b and the high-pressure side opposing surface 53a.

[0052] When the screw type fluid machine 1 is assembled (manufactured), the thickness of the partition members 71, 72 is thicker than or approximately the same as the size of the gap D between the high-pressure side end faces 13b, 23b and the high-pressure side opposing surface 53a. The partition members 71, 72 are assembled by being pressed against the high-pressure side end faces 13b, 23b and the high-pressure side opposing surface 53a. As the screw type fluid machine 1 operates and the male rotor 10 and the female rotor 20 rotate, the sliding surfaces of the partition members 71, 72 with the high-pressure side end faces 13b, 23b and the sliding surface with the high-pressure side opposing surface 53a become more compliant.

[0053] (Third embodiment) 6 and 7, the screw type fluid machine 1 of the third embodiment has a recess 60 and a partition member 70 whose shapes are changed from those of the first embodiment. Other than these, the screw type fluid machine 1 is substantially the same as the first embodiment. Therefore, the description of the parts shown in the first embodiment may be omitted.

[0054] In this embodiment, the partition member 73 (70) has a shape that follows the inner circumferential surface of the casing 30 that defines the compression chamber 42. Specifically, it has a shape that follows the inner circumferential surface of the rotor casing 40. The partition member 73 (70) has a roughly elliptical plate-shaped base 73a and a protruding portion 73b that protrudes rearward from the center of the base 73a. The protruding portion 73b has an outer shape of two consecutive circles that follows the inner wall surface of the rotor casing 40 that defines the compression chamber 42. The partition member 73 is fitted into the rotor casing 40, and the protruding portion 73b contacts the high-pressure side end faces 13b, 23b. The base 73a is fixed to the discharge casing 50 around the protruding portion 73b with bolts or the like, and is sandwiched between the discharge casing 50 and the rotor casing 40.

[0055] The partition member 73 is provided with shaft hole through holes 73c and 73d that are connected to the shaft holes 54 and 55, respectively. The partition member 73 also has a high-pressure port through hole 73e that is connected to the discharge port 51.

[0056] The high-pressure side opposing surface 53a is provided with a recess 63 (60) having a shape complementary to the partition member 73 (specifically, the base 73a). When the partition member 73 is disposed in the recess 63, it protrudes from the high-pressure side opposing surface 53a by the thickness of the protrusion 73b. The protrusion amount of the protrusion 73b matches the size of the gap D between the high-pressure side end surfaces 13b, 23b and the high-pressure side opposing surface 53a.

[0057] According to the screw compressor 1 of this embodiment, the entire gap between the high-pressure side end faces 13b, 23b and the high-pressure side opposing surface 53a can be sealed.

[0058] Furthermore, even if the entire gap between high-pressure side end faces 13b, 23b and high-pressure side opposing surface 53a is sealed, high-pressure port through-hole 73c is provided, so discharge port 51 is not blocked. Therefore, obstruction of the flow of compressed air from compression chamber 42 to discharge port 51 can be suppressed.

[0059] (Fourth embodiment) 8 and 9, the screw type fluid machine 1 of the fourth embodiment has a recess 60 and a partition member 70 whose shapes are changed from those of the first embodiment. Other than these, the screw type fluid machine 1 is substantially the same as the first embodiment. Therefore, the description of the parts shown in the first embodiment may be omitted.

[0060] In this embodiment, the partition member 74 (70) is provided only for the male rotor 10. In other words, the female rotor 20 is not provided with a partition member.

[0061] The partition member 74 is arranged so as to cover the entire high-pressure side end face 13b of the male rotor 10. The partition member 74 is annular and has a diameter equal to or greater than the tooth tip diameter of the main body 13 of the male rotor 10 (in the illustrated example, this diameter is the same as the tooth tip diameter). Specifically, the partition member 74 has a disk-shaped base 74a and a protruding portion 74b that protrudes rearward from the center of the base 74a, and the diameters of both the base 74a and the protruding portion 74b are equal to or greater than the tooth tip diameter. The protruding portion 74b comes into contact with the high-pressure side end face 13b. The partition member 63 seals the gap between the high-pressure side end face 13b and the high-pressure side opposing surface 53a.

[0062] The partition member 74 is provided with a shaft hole through-hole 74c that is connected to the shaft hole 54 and that accommodates the shaft portion 12.

[0063] The high-pressure side opposing surface 53a is provided with a recess 64 (60) having a shape complementary to the partition member 74 (specifically, the base 74a). When the partition member 74 is disposed in the recess 64, it protrudes from the high-pressure side opposing surface by the thickness of the protrusion 74b. The protrusion amount of the protrusion 74b is the same as the size of the gap D between the high-pressure side end surface 13b and the high-pressure side opposing surface 53a.

[0064] Alternatively, the partition member 60 may be provided for the female rotor 20, or for both the male rotor 10 and the female rotor 20. That is, the partition member 60 may be provided for at least one of the male rotor 10 and the female rotor 20.

[0065] According to the screw compressor 1 of this embodiment, the partition member 74 is positioned so as to completely cover the high-pressure side end surface 13b of the male rotor 10, thereby sealing the gap D between the high-pressure side end surface 13b and the high-pressure side opposing surface 53a.

[0066] While specific embodiments of the present invention and their modifications have been described above, the present invention is not limited to the above-described embodiments and can be implemented with various modifications within the scope of the present invention. For example, an appropriate combination of the contents of the individual embodiments may be considered as one embodiment of the present invention.

[0067] For example, in the above embodiment, the screw type fluid machine 1 is a compressor, but the screw type fluid machine 1 may be a screw type expander. In this case, the high-pressure port serves as an air inlet, and the low-pressure port serves as an exhaust port.

[0068] For example, in the above embodiment, the rotor casing 40 accommodates the shaft portion 11 and main body portion 13 of the male rotor 10 and the shaft portion 21 and main body portion 23 of the female rotor 20, and the discharge casing 50 accommodates the shaft portions 12 and 22. The casing 30 may be divided into a rotor casing that accommodates the shaft portion 12 and main body portion 13 of the male rotor 10 and the shaft portion 22 and main body portion 23 of the female rotor 20, and a suction casing (not shown) that accommodates the shaft portions 11 and 21. The casing 30 may also be divided midway at the portion that accommodates the main bodies 13 and 23.

[0069] The present disclosure may include the following aspects. (Aspect 1) a male rotor and a female rotor, each having a main body with spiral teeth and a shaft serving as a rotation axis of the main body; a casing that defines a compression chamber that accommodates the main body portion and a shaft hole that communicates with the compression chamber and through which the shaft portion passes; a partition member disposed to block communication between the compression chamber and the axial hole; Equipped with a partition member in contact with a high-pressure side end surface of the main body of at least one of the male rotor and the female rotor and a high-pressure side opposing surface of the casing opposing the high-pressure side end surface; (Aspect 2) 2. The screw type fluid machine according to aspect 1, wherein the material of the partition member is softer than the materials of the main body and the casing. (Aspect 3) 3. The screw type fluid machine according to embodiment 1 or 2, which is an oil-cooled type. (Aspect 4) Aspect 4. The screw fluid machine according to any one of aspects 1 to 3, wherein the high-pressure side opposing surface is provided with a recess in which the partition member is disposed. (Aspect 5) Aspect 5. The screw type fluid machine according to any one of aspects 1 to 4, wherein the partition member is arranged to cover the entire surface of at least one of the high-pressure side end face of the male rotor and the high-pressure side end face of the female rotor. (Aspect 6) Aspect 5. The screw type fluid machine according to any one of aspects 1 to 4, wherein the partition member has a shape that follows an inner circumferential surface of the casing that defines the compression chamber. (Aspect 7) a low-pressure port through which a relatively low-pressure fluid passes and a high-pressure port through which a relatively high-pressure fluid passes; Aspect 7. The screw fluid machine according to any one of aspects 1 to 6, wherein the partition member is provided with a high-pressure port through-hole communicating with the high-pressure port. (Aspect 8) a male rotor and a female rotor, each having a main body with spiral teeth and a shaft serving as a rotation axis of the main body, a compression chamber for accommodating the main body, a casing defining an axial hole communicating with the compression chamber and through which the shaft passes, and a partition member; The male rotor and the female rotor are housed in the compression chamber; The partition member is arranged so as to block communication between the compression chamber and the axial hole while being in contact with a high-pressure side end surface of the main body portion of at least one of the male rotor and the female rotor and a high-pressure side opposing surface of the casing opposing the high-pressure side end surface. A method for manufacturing a screw type fluid machine, comprising: [Explanation of symbols]

[0070] 1. Screw compressor (screw fluid machinery) 10 Male Rotor 11,12 Shaft section 13 Main body 13a Low pressure side end face 13b High pressure side end face 20 female rotors 21,22 Shaft section 23 Main body 23a Low pressure side end face 23b High pressure side end face 30 Casing 40 rotor casing 41 Intake port (low pressure port) 42 Compression chamber 43 Flange 50 Discharge casing 51 Discharge port (high pressure port) 52 flange 53 End Wall 53a High pressure side facing surface 53b, 53c fuel line 54,55 Shaft hole 56,57 Bearing chamber 58,59 Bearings 60(61,62,63,64) Recess 70 (71, 72, 73, 74) Partition member 73a base 73b Protrusion 73c,73d Through hole for shaft hole 73e High pressure outlet through hole 74a base 74b Protrusion 74c Through hole for shaft hole

Claims

1. a male rotor and a female rotor, each having a main body with spiral teeth and a shaft serving as a rotation axis of the main body; a casing that defines a compression chamber that accommodates the main body portion and a shaft hole that communicates with the compression chamber and through which the shaft portion passes; a partition member disposed to block communication between the compression chamber and the axial hole; Equipped with a partition member in contact with a high-pressure side end surface of the main body of at least one of the male rotor and the female rotor and a high-pressure side opposing surface of the casing opposing the high-pressure side end surface;

2. The screw type fluid machine according to claim 1 , wherein the material of the partition member is softer than the materials of the main body and the casing.

3. 3. The screw type fluid machine according to claim 1, which is an oil-cooled type.

4. The screw type fluid machine according to claim 1 or 2, wherein the high-pressure side opposing surface is provided with a recess in which the partition member is disposed.

5. 3. The screw type fluid machine according to claim 1, wherein the partition member is arranged so as to entirely cover at least one of the high-pressure side end face of the male rotor and the high-pressure side end face of the female rotor.

6. 3. The screw type fluid machine according to claim 1, wherein the partition member has a shape that follows an inner circumferential surface of the casing that defines the compression chamber.

7. a low-pressure port through which a relatively low-pressure fluid passes and a high-pressure port through which a relatively high-pressure fluid passes; The screw type fluid machine according to claim 1 or 2, wherein the partition member is provided with a high-pressure port through-hole communicating with the high-pressure port.

8. a male rotor and a female rotor, each having a main body with spiral teeth and a shaft serving as a rotation axis of the main body, a compression chamber for accommodating the main body, a casing defining an axial hole communicating with the compression chamber and through which the shaft passes, and a partition member; The male rotor and the female rotor are housed in the compression chamber; The partition member is arranged so as to block communication between the compression chamber and the axial hole while being in contact with a high-pressure side end surface of the main body portion of at least one of the male rotor and the female rotor and a high-pressure side opposing surface of the casing opposing the high-pressure side end surface. A method for manufacturing a screw type fluid machine, comprising:

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