Claw compressor and method for assembling same

Abstract

Provided is a claw compressor capable of reducing leakage of compressed fluid as much as possible by optimizing a gap in the rotation-axis direction of a rotor. A claw compressor (1) comprises: a male rotor (24); a first rotating shaft (32); a female rotor; a second rotating shaft; a first housing (7) for accommodating the male rotor (24) and the female rotor; a key (33) and a key groove (24d) for fixing the male rotor (24) inside the first housing (7) so as to be capable of moving in the axial direction of a first rotation axis (O1) while restricting the male rotor (24) in a rotation direction about the first rotation axis (O1); and a key and a key groove for fixing the female rotor inside the first housing (7) so as to be capable of moving in the axial direction of a second rotation axis of the second rotating shaft while restricting the female rotor in the rotation direction about the second rotation axis.

Description

Claw compressor and assembly method thereof

[0001] The present disclosure relates to a claw compressor and a method for assembling the same.

[0002] A claw compressor includes a pair of rotors with hook-shaped claws formed inside a housing that defines a compression chamber. The rotors rotate at the same speed in opposite directions without contact while maintaining a predetermined clearance. The two rotors form a compression pocket, and the compressed fluid is discharged from the compression pocket. Such claw compressors are often used primarily as vacuum pumps and blowers (see, for example, Patent Document 1).

[0003] Patent Document 1 discloses a structure in which a plurality of discharge ports are provided so that the temperature inside the cylinder can be kept low under high vacuum conditions when used as a vacuum pump.

[0004] Patent No. 6845596

[0005] When a claw compressor is used to compress steam, it must be oil-free to prevent oil from mixing with the steam. The claw compressor shown in Patent Document 1 is also oil-free because it is used in a vacuum pump, but compared to when compressing steam, the differential pressure between the suction pressure and the discharge pressure is small, and loss due to leakage of compressed gas during the compression stroke is small. In steam compression applications, the differential pressure is large, resulting in large leakage, so it is necessary to reduce the gap during the compression stroke to achieve high efficiency.

[0006] Furthermore, when a claw compressor is used for vapor compression, the temperature of the claw compressor is higher than when used for vacuum pumps, and the temperature difference between the housing and the shaft is large, which leads to a unique phenomenon in which the gap between the rotor and the housing changes from the time of assembly. In particular, when the rotor and the housing are made of different materials, it is preferable for the gaps on both sides of the rotor's rotation axis (axial gap) to be the same during operation due to cost and manufacturing precision considerations, but assembling them in this manner is difficult. For example, during startup, the rotor and the rotating shaft heat up before the housing, which can lead to differential thermal expansion.

[0007] The present disclosure has been made in consideration of the above circumstances, and aims to provide a claw compressor and an assembly method thereof that can optimize the gap in the direction of the rotor's rotation axis and minimize leakage of compressed fluid.

[0008] A claw compressor according to one aspect of the present disclosure includes: a first rotor provided with claw portions protruding radially; a first rotating shaft that rotationally supports the first rotor; a second rotor that rotates in the opposite direction to the first rotor and has recesses that receive the claw portions; a second rotating shaft that rotationally supports the second rotor; a first housing that accommodates the first rotor and the second rotor; a first rotor fixing portion that fixes the first rotor inside the first housing while restraining it in a rotational direction about a first rotation axis of the first rotating shaft and allowing it to move in the axial direction of the first rotation axis; and a second rotor fixing portion that fixes the second rotor inside the second housing while restraining it in a rotational direction about a second rotation axis of the second rotating shaft and allowing it to move in the axial direction of the second rotation axis.

[0009] A method of assembling a claw compressor according to one aspect of the present disclosure includes assembling a first rotor provided with claw portions protruding in a radial direction, a first rotating shaft that rotatably supports the first rotor, a second rotor that rotates in the opposite direction to the first rotor and has recesses that receive the claw portions, a second rotating shaft that rotatably supports the second rotor, a first housing that accommodates the first rotor and the second rotor, a first rotor fixing part that fixes the first rotor inside the first housing so as to be movable in the axial direction of the first rotation axis while restraining the first rotor in the rotation direction about a first rotation axis of the first rotating shaft, a second rotor fixing part that fixes the second rotor inside the second housing so as to be movable in the axial direction of the second rotation axis while restraining the second rotor in the rotation direction about a second rotation axis of the second rotating shaft, and an axial part of the first rotating shaft. a first intermediate component provided at an end of the first rotating shaft, a first intermediate component fixing member that fixes the first intermediate component to the shaft end of the first rotating shaft; a second intermediate component provided at the shaft end of the second rotating shaft, and a second intermediate component fixing member that fixes the second intermediate component to the shaft end of the second rotating shaft, the method comprising: fixing the first rotor to the first intermediate component using the first rotor fixing portion; fixing the second rotor to the second intermediate component using the second rotor fixing portion; assembling the first rotating shaft, fixing the first intermediate component to the shaft end of the first rotating shaft using the first intermediate component fixing member; and assembling the second rotating shaft, fixing the second intermediate component to the shaft end of the second rotating shaft using the second intermediate component fixing member.

[0010] A method of assembling a claw compressor according to one aspect of the present disclosure includes assembling a first rotor provided with claw portions projecting in a radial direction, a first rotating shaft that rotatably supports the first rotor, a second rotor that rotates in a direction opposite to the first rotor and has recesses that receive the claw portions, a second rotating shaft that rotatably supports the second rotor, a first housing that accommodates the first rotor and the second rotor, a first rotor fixing part that fixes the first rotor inside the first housing so as to be movable in an axial direction of the first rotation axis while restraining the first rotor in a rotation direction about a first rotation axis of the first rotating shaft, and A method for assembling a claw compressor including: a second rotor fixing portion that fixes the second rotating shaft inside a housing so as to be movable in the axial direction of the second rotating shaft while restraining the second rotating shaft in the rotational direction about the second rotational axis; a first wedge member fixed to a first wedge gap formed between the first rotating shaft and the first rotor; and a second wedge member fixed to a second wedge gap formed between the second rotating shaft and the second rotor, wherein the first rotor is fixed using the first rotor fixing portion, and then the first wedge member is fixed; and the second rotor is fixed using the second rotor fixing portion, and then the second wedge member is fixed.

[0011] By optimizing the clearance in the direction of the rotor's rotation axis, leakage of compressed fluid can be minimized.

[0012] 17 is a perspective view showing a basic form of a claw compressor according to each embodiment of the present disclosure. FIG. 17 is a cross-sectional view of the claw compressor taken along the section line II-II of FIG. 1. FIG. 17 is a cross-sectional view of the claw compressor taken along the section line III-III of FIG. 2. FIG. 17 is a cross-sectional view of the claw compressor taken along the section line IV-IV of FIG. 2. FIG. 17 is a cross-sectional view of the claw compressor according to the first embodiment, corresponding to FIG. 4. FIG. 17 is a front view of the first rotating shaft of FIG. 4, viewed from the front. FIG. 17 is a graph showing the leakage amount versus the axial clearance ratio. FIG. 17 is a front view of a modified example of FIG. 6. FIG. 17 is a partially enlarged vertical cross-sectional view of a modified example of a rotor fixing portion. FIG. 17 is a partially enlarged vertical cross-sectional view of a modified example of FIG. 9. FIG. 17 is a cross-sectional view of a claw compressor according to a second modified example, corresponding to FIG. 5. FIG. 17 is a cross-sectional view of a claw compressor according to a second modified example, corresponding to FIG. 3. FIG. 17 is a cross-sectional view of a claw compressor according to a third modified example, corresponding to FIG. 4. FIG. 17 is a cross-sectional view of a claw compressor according to a second embodiment of the present disclosure, corresponding to FIG. 4. FIG. 17 is a partially enlarged cross-sectional view of the periphery of the restriction pin of FIG. 15. FIG. 17 is a cross-sectional view of a claw compressor according to a third embodiment of the present disclosure, corresponding to FIG. 4. FIG. 17 is a front view showing the attachment position of the first wedge member about the first rotation axis of FIG. 17. FIG. 18 is an enlarged perspective view showing the first wedge member of FIG. 17. FIG. 19 is a side cross-sectional view showing an installation process of the first wedge member of FIG. 17. FIG. 20 is a side view showing a modified example of the first wedge member of FIG. 17. FIG. 21 is a cross-sectional view showing a claw compressor according to a fourth embodiment of the present disclosure, corresponding to FIG. 4. FIG. 22 is a cross-sectional view showing a claw compressor according to a fifth embodiment of the present disclosure, corresponding to FIG. 2. FIG. 23 is a graph showing an axial gap ratio. FIG. 24 is a graph showing an axial gap ratio.

[0013] Hereinafter, multiple embodiments according to the present disclosure will be described with reference to the drawings. In the following description, the Z-axis direction indicates the vertical direction. The Y-axis direction is a direction perpendicular to the Z-axis direction and indicates the direction in which the first rotating shaft 32 and the second rotating shaft 42 of the claw compressor 1 extend. The X-axis direction is a direction perpendicular to the Z-axis direction and the Y-axis direction.

[0014] <Basic Structure> The basic structure of the claw compressor 1 will be described below. The claw compressor 1 is used to compress steam. As shown in FIG. 1, the claw compressor 1 includes a compression section 3 having a compression chamber 20 (see FIG. 2) formed therein, and a gear section 5 accommodating gears 39 and 49 (see FIG. 2). The compression section 3 is formed by a first housing 7 and a second housing 9, and the gear section 5 is formed by the second housing 9 and a third housing 11. The claw compressor 1 is installed upright on an installation surface using, for example, four legs 12.

[0015] The compression section 3 has an intake port 13 for drawing in steam (fluid) and an outlet port 15 for discharging the steam after compression. The steam is, for example, water vapor. The drawn steam may be under negative pressure or positive pressure.

[0016] 2, the compression unit 3 is configured such that a compression chamber 20 is formed inside by covering a recess formed in the front end (one side end) of the second housing 9 with the first housing 7. The first housing 7 is airtightly attached to the second housing 9 via an O-ring 22.

[0017] The compression chamber 20 is provided with a pair of rotors, namely a male rotor (first rotor) 24 and a female rotor (second rotor) 26 .

[0018] As shown in Fig. 3, the male rotor 24 has a pair of hook-shaped claws 24a. The claws 24a are arranged symmetrically about the first rotation axis O1. The male rotor 24 rotates counterclockwise (in the direction of arrow A1) in Fig. 3.

[0019] The female rotor 26 has a pair of hook-shaped claws 26a. The claws 26a are provided symmetrically about the second rotation axis O2. The female rotor 26 rotates clockwise (in the direction of arrow A2) in FIG. 3 .

[0020] The claws 24a of the male rotor 24 and the claws 26a of the female rotor 26 are adapted to mesh without contacting each other. The female rotor 26 is formed with recesses 26b that receive the claws 24a of the male rotor 24 during the compression stroke. The compressed steam is discharged from the discharge port 15, which is approximately triangular in shape in Figure 3.

[0021] 3, the shape of compression chamber 20 is defined by inner wall 9a of second housing 9, and has a cross-sectional shape formed by partially overlapping two circles, one centered on first rotational axis O1 and the other centered on second rotational axis O2. The tips of claws 24a, 26a of rotors 24, 26 run along inner wall 9a of second housing 9 with a predetermined clearance.

[0022] As shown in Fig. 2, the male rotor 24 is fastened to the first rotating shaft 32 by a first bolt 31. Specifically, as shown in Fig. 2, the first bolt 31 is screwed onto the first rotating shaft 32 with the axis of the first bolt 31 coinciding with the first rotation axis O1. A fastening structure is configured with the center of the male rotor 24 sandwiched between the tip surface of the first rotating shaft 32 and the head of the first bolt 31. The head of the first bolt 31 is housed in a cylindrical recess 24c formed in the center of the male rotor 24.

[0023] The female rotor 26 is fastened to the second rotation shaft 42 by a second bolt 41. Specifically, the second bolt 41 is screwed onto the second rotation shaft 42 with the axis of the second bolt 41 coinciding with the second rotation axis O2. The second rotation shaft 42 is provided parallel to the first rotation shaft 32. In other words, the first rotation axis O1 and the second rotation axis O2 are parallel to each other.

[0024] A fastening structure (second bolt fastening portion) is configured with the center portion of the female rotor 26 sandwiched between the tip surface of the second rotating shaft 42 and the head of the second bolt 41. The head of the second bolt 41 is housed in a cylindrical recess 26c formed in the center of the female rotor 26. Therefore, before the female rotor 26 is fixed by the second bolt 41, relative rotation between the female rotor 26 and the second rotating shaft 42 is permitted.

[0025] The first rotating shaft 32 supporting the male rotor 24 has its tip located within the compression chamber 20 and its rear end connected to a drive unit (not shown). For example, an electric motor is used as the drive unit. The first rotating shaft 32 rotates about the first rotation axis O1, thereby rotating the male rotor 24 within the compression chamber 20. The first rotating shaft 32 is rotatably supported at two locations: a tip bearing (first bearing) 37 and a rear bearing 38. The tip bearing 37 is provided in the second housing 9 and is, for example, a double-row ball bearing. However, the tip bearing 37 is not limited to being a double-row ball bearing or a ball bearing. The rear bearing 38 is located rearward of the tip bearing 37 and is provided in the third housing 11. The rear bearing 38 is a single-row ball bearing, but is not limited to being a single-row ball bearing or a ball bearing.

[0026] A first gear 39 is fixed to the first rotating shaft 32 between a front-end bearing 37 and a rear-end bearing 38. The first gear 39 is, for example, a spur gear, and rotates around the first rotation axis O1 together with the first rotating shaft 32. The first rotating shaft 32 is connected to a second rotating shaft 42 at a gear portion 5.

[0027] The first gear 39 is provided in the gear portion 5 and is housed in a gear chamber 21 formed between the rear end (other side end) of the second housing 9 and the front end of the third housing 11. The second housing 9 and the third housing 11 are attached liquid-tightly via an O-ring 23 so as to seal in the lubricating oil in the gear chamber 21. The interior of the gear chamber 21 (i.e., the interior of the third housing 11) is an oil atmosphere that lubricates the gear portion 5.

[0028] As described above, the tip of the first rotating shaft 32 is provided with a first bolt fastening portion to which the first bolt 31 is fastened. The rear end of the first rotating shaft 32 protrudes from the third housing 11. In other words, the rear end of the first rotating shaft 32 is provided outside the third housing 11. The rear end of the first rotating shaft 32 is connected to a drive unit (such as an electric motor).

[0029] The second rotary shaft 42 that supports the female rotor 26 has its tip located within the compression chamber 20 and its rear end terminated in the third housing 11. A space S is formed in the third housing 11 to accommodate a rear end bearing 48. A seal 35 is provided between the space S and the gear chamber 21.

[0030] The second rotary shaft 42 rotates about the second rotation axis O2, causing the female rotor 26 to rotate within the compression chamber 20. The second rotary shaft 42 is rotatably supported at two locations: a front-end bearing (second bearing) 47 and a rear-end bearing 48. The front-end bearing 47 is provided in the second housing 9 and is, for example, a double-row ball bearing. However, the front-end bearing 47 is not limited to a double-row ball bearing. The rear-end bearing 48 is located rearward of the front-end bearing 47 and is provided outside the third housing 11. Specifically, the rear-end bearing 48 is provided in the space S adjacent to the gear chamber 21. The rear-end bearing 48 is a single-row ball bearing, but is not limited to a single-row ball bearing.

[0031] A second gear 49 is fixed to the second rotating shaft 42 between the front-end bearing 47 and the rear-end bearing 48. The second gear 49 is, for example, a spur gear, and rotates together with the second rotating shaft 42 around the second rotation axis O2.

[0032] The second gear 49 is provided in the gear unit 5 and housed in the gear chamber 21. The second gear 49 is in mesh with the first gear 39, and receives driving force from the first gear 39. Therefore, the first rotating shaft 32 serves as a driving shaft, and the second rotating shaft 42 serves as a driven shaft.

[0033] As described above, the tip of the second rotating shaft 42 is provided with the second bolt fastening portion to which the second bolt 41 is fastened.

[0034] 2 and 4 , an end surface 9b of the second housing 9 and an end surface 11a of the third housing 11 are in surface contact with each other. The mating surface between the second housing 9 and the third housing 11 is located closer to the tip-side bearing 37 than the center of the gear unit 5 in the Y-axis direction (predetermined direction). In this embodiment, the mating surface between the second housing 9 and the third housing 11 is arranged to coincide with the end of the tip-side bearing 37 on the gear unit 5 side.

[0035] A bearing chamber 19 for accommodating the tip end bearings 37 and 47 is formed inside the second housing 9 .

[0036] As shown in Fig. 4, the first rotating shaft 32 passes through the second housing 9. An oil seal 50 and a water seal 52 are provided between the bearing chamber 19 and the compression chamber 20 to seal the gap between the outer circumferential surface of the first rotating shaft 32 and the second housing 9. The oil seal 50 blocks the flow of lubricating oil from the bearing chamber 19 to the compression chamber 20. The water seal 52 blocks the flow of steam and condensed water from the compression chamber 20 to the bearing chamber 19.

[0037] The claw compressor 1 configured as described above operates as follows: The first rotary shaft 32 is rotationally driven by a drive unit (not shown), causing the male rotor 24 to rotate within the compression chamber 20. The second rotary shaft 42 is rotated by the second gear 49, to which a rotational driving force is transmitted from the first gear 39, which rotates together with the first rotary shaft 32, causing the female rotor 26 to rotate within the compression chamber 20.

[0038] As the male rotor 24 and female rotor 26 rotate within the compression chamber 20, steam is drawn in through the suction port 13. The male rotor 24 rotates counterclockwise (in the direction of arrow A1) in FIG. 3 , taking steam into a compression pocket formed by its claws 24a and moving it downward along the outer periphery of the compression chamber 20. The female rotor 26 rotates clockwise (in the direction of arrow A2) in FIG. 3 , taking steam into a compression pocket formed by its claws 26a and moving it downward along the outer periphery of the compression chamber 20. The compression pocket formed by the male rotor 24 and the compression pocket formed by the female rotor 26 then merge in the center of the lower part of the compression chamber 20, and in this combined compression pocket (compression space), the claws 24a of the male rotor 24 penetrate into the recesses 26b of the female rotor 26, compressing the steam. The compressed steam is discharged to the outside through the discharge port 15.

[0039] [First embodiment] The first embodiment differs from the basic structure of the claw compressor 1 described above in the connection structure between the rotary shafts 32, 42 and the rotors 24, 26. The other structures are the same, so a description thereof will be omitted.

[0040] As shown in Figure 5, the tip end 32a of the first rotating shaft 32 is inserted into the central hole of the male rotor 24. The tip end 32a has a smaller diameter than the main body of the first rotating shaft 32. A key 33 is embedded and fixed in the side periphery of the tip end 32a. A key groove 24d is formed in the central hole of the male rotor 24 corresponding to the key 33 in the direction of the first rotation axis O1. Figure 6 shows a front view of the first rotating shaft 32 as seen from the tip end 32a side.

[0041] The key 33 and the key groove 24d allow the male rotor 24 to move in the direction of the first rotation axis O1 while being constrained in the rotational direction about the first rotation axis O1 relative to the first rotation shaft 32. In other words, the key 33 and the key groove 24d serve as the first rotor fixing portion. By using this fixing method, the axial clearance h on both sides of the male rotor 24 in the direction of the first rotation axis O1 is variable. The axial clearance h is the gap between both end faces of the male rotor 24 in the direction of the first rotation axis O1 and the corresponding inner wall surfaces of the first housing 7, and is shown by a thick line in FIG. 5.

[0042] Similarly, a second rotor fixing portion is provided by providing a key on the second rotary shaft 42 and forming a key groove in the female rotor 26 .

[0043] The claw compressor 1 according to this embodiment has the following advantages. Figure 7 shows the change in leakage amount versus the ratio of axial clearances h1 and h2 on both sides of the rotational axes O1 and O2 of the rotors 24 and 26. In the figure, the horizontal axis represents the ratio of axial clearances h1 and h2 on both sides of the rotational axes O1 and O2 of the rotors 24 and 26, and the vertical axis represents the leakage amount. Q1 represents the leakage amount through one axial clearance h1 on the rotational axes O1 and O2, Q2 represents the leakage amount through the other axial clearance h2, and Q_total represents the sum of Q1 and Q2. As can be seen from Figure 7, the total leakage amount Q_total is minimized when h1 / h2 = 0.5, i.e., when the axial clearances h1 and h2 on both sides are equal.

[0044] In this embodiment, by employing a rotor fixing section using a key 33 and a key groove 24d, the male rotor 24 and the female rotor 26 are allowed to move in the directions of the rotation axes O1 and O2 while being restricted in their rotational directions. As a result, even if an axial gap h is generated between each rotor 24, 26 and the first housing 7 in the directions of the rotation axes O1 and O2, the dynamic pressure of the fluid flowing through the axial gap h during operation of the claw compressor 1 moves each rotor 24, 26 to a central position in the directions of the rotation axes O1 and O2, thereby achieving balance. This makes the axial gaps h on both sides equal, minimizing leakage of the compressed fluid (steam).

[0045] In the above-described embodiment, the key 33 and the key groove 24d are used as the rotor fixing portion, but the present invention is not limited to this. For example, as shown in Fig. 8, the cross-sectional shape of the first rotating shaft 32 may be non-circular (elliptical) instead of circular. Alternatively, although not shown, a two-face width, a D-cut surface, serrations, or the like may be used.

[0046] <Modification 1> Instead of a configuration using a key 33 and key groove 24d as the rotor fixing portion, a rotor fixing portion as shown in Fig. 9 can also be applied. Like the basic structure shown in Fig. 4, Fig. 9 has in common the use of a first bolt 31 that threads onto the first rotating shaft 32. Furthermore, in this modification, a first intermediate part 55 is used to fix the first bolt (first intermediate part fixing portion) 31 and the male rotor 24. A key 33 is fixed to the first intermediate part 55, and the key 33 is inserted into the key groove 24d of the male rotor 24.

[0047] In this manner, in this modification, the first rotor fixing part includes the first bolt 31, the first intermediate part 55, the key 33, and the key groove 24d. By using such a first rotor fixing part, as in the first embodiment, the male rotor 24 can be made movable in the direction of the first rotation axis O1 while being constrained in the rotational direction about the first rotation axis O1.

[0048] The same structure as above can be adopted for the second rotary shaft 42 and the female rotor 26.

[0049] This modification provides the following advantageous effects. By fixing the first intermediate component 55 with the first bolt 31, the male rotor 24 is fixed to the first intermediate component 55 so as to be axially movable while being restricted from rotating. The first intermediate component 55 is fixed to the shaft end (tip portion) of the first rotating shaft 32. With this configuration, when fixing the first intermediate component 55 to the first rotating shaft 32 with the first bolt 31, the phase of the rotational direction of the first intermediate component 55, i.e., the male rotor 24, relative to the first rotating shaft 32 can be determined. This allows the phase of the male rotor 24 to be determined as desired using the first intermediate component 55 after assembling the first rotating shaft 32, enabling accurate and easy assembly. Furthermore, by employing a second intermediate component having a similar structure for the female rotor 26, similar advantageous effects can be achieved.

[0050] A first intermediate part 55' shown in FIG. 10 may be used instead of the first intermediate part 55 shown in FIG. 9. The first intermediate part 55' is used for the first rotating shaft 32 having the non-circular cross-sectional shape shown in FIG. 8. The first intermediate part 55' is used in which a hole having a shape corresponding to the non-circular lateral end face shape of the first rotating shaft 32 is formed. By fixing the first intermediate part 55' with the first bolt 31, the male rotor 24 is fixed to the first intermediate part 55 so as to be axially movable while being restricted from rotation. Furthermore, by using a second intermediate part having a similar structure for the female rotor 26, similar effects can be achieved.

[0051] <Modification 2> As shown in Fig. 11, a first through hole 24e is provided in the male rotor 24, penetrating in the direction of the first rotation axis O1. It is preferable to provide a plurality of first through holes 24e, for example, three, at equal angular intervals around the first rotation axis O1, as shown in Fig. 12. Similarly, a second through hole 26e is provided in the female rotor 26, as shown in Fig. 12.

[0052] As in this modified example, by providing the through holes 24e, 26e that penetrate in the direction of the rotational axes O1, O2 in each of the rotors 24, 26, it is possible to equalize the pressure in the axial gaps h located on both sides in the direction of the rotational axes O1, O2 of each of the rotors 24, 26. This makes it possible to reliably balance each of the rotors 24, 26 at a central position in the direction of the rotational axes O1, O2 during operation of the claw compressor 1.

[0053] <Modification 3> As shown in Fig. 13, a first thrust bearing 24f is provided on each of both end faces of the male rotor 24 on the first rotation axis O1 so as to face the axial gap h. As shown in Fig. 14, the first thrust bearing 24f is provided in an annular shape over the entire circumferential direction. As shown in Fig. 14, a second thrust bearing 26f is similarly provided on the female rotor 26. For example, a tapered land bearing, a step land bearing, or the like can be used as the thrust bearings 24f, 26f.

[0054] According to this modified example, by providing thrust bearings 24f, 26f on both sides of each rotor 24, 26 in the direction of the rotational axis O1, O2, the axial gap h is adjusted by dynamic pressure during operation of the claw compressor 1, and the rotors 24, 26 can be balanced at a central position in the direction of the rotational axis O1, O2.

[0055] The thrust bearings 24f, 26f may be provided on the rotors 24, 26 as described above, or on the first housing 7 side. They may also be provided on the seal pressing member 58 (see FIG. 13 ) that presses the water seal (sealing member) 52 that seals around the rotating shafts 32, 42.

[0056] Second Embodiment The second embodiment differs from the basic structure of the claw compressor 1 described above (see, for example, FIG. 4 ) in the connection structure between the rotary shafts 32, 42 and the rotors 24, 26. The other structures are the same, so a description thereof will be omitted.

[0057] As shown in Fig. 15 , a first regulating pin 59 is provided between the male rotor 24 and the first rotating shaft 32. The first regulating pins 59 extend in the direction of the first rotation axis O1, and a plurality of first regulating pins 59 are provided, for example, at equal angular intervals around the first rotation axis O1. As shown in Fig. 16 , one end of the first regulating pin 59 is fitted and fixed to the end face of the tip of the first rotating shaft 32, and the other end is inserted into a blind hole 24g formed in the male rotor 24. The blind hole 24g has a larger diameter than the regulating pin 59, and a predetermined gap is formed between the first regulating pin 59 and the first regulating pin 59.

[0058] The male rotor 24 is fixed to the first rotating shaft 32 mainly by the first bolt 31. The first restricting pin 59 is intended to restrict displacement beyond the gap between the bottomed hole 24g when an external force greater than that imposed by the first bolt 31 is applied to the male rotor 24.

[0059] The female rotor 26 is also provided with a second restriction pin and a blind hole similar to the first restriction pin 59 and the blind hole 24g.

[0060] This embodiment has the following advantages: Even if excessive force is applied to the rotors 24, 26 due to some abnormality, such as liquid compression, causing the rotors 24, 26 to move relative to the rotating shafts 32, 42, the restricting pin 59 can keep the relative movement below a predetermined value (below the gap with the bottomed hole 24g), thereby preventing breakdowns in the claw compressor 1.

[0061] When the rotors 24, 26 are fixed to the rotary shafts 32, 42 using the intermediate parts 55, 55' as shown in FIGS. 9 and 10, a regulating pin is provided between the rotary shafts 32, 42 and the intermediate parts 55, 55'.

[0062] [Third Embodiment] The third embodiment differs from the basic structure of the claw compressor 1 described above (see, for example, FIG. 4 ) in the connection structure between the rotary shafts 32, 42 and the rotors 24, 26. The other structures are the same, so a description thereof will be omitted.

[0063] As shown in Fig. 17, a first wedge member 61 is fitted onto the outer periphery of the first rotation shaft 32. As shown in Fig. 18, the first wedge members 61 extend in the direction of the first rotation axis O1, and a plurality of first wedge members 61, for example, two first wedge members 61, are provided around the first rotation axis O1 at equal angular intervals.

[0064] 19 shows an enlarged perspective view of the first wedge member 61. As shown in the figure, the first wedge member 61 has a half portion 61a at the tip end (rotation shaft side) that has a shape obtained by splitting a cylinder in half, and a cylindrical portion 61b at the rear end (male rotor 24 side) that is also cylindrical. An inner peripheral surface 61a1 of the half portion 61a is a cylindrical surface that corresponds to the shape of the outer peripheral surface of the first rotation shaft 32, which is the surface that comes into contact with it.

[0065] 20, the first wedge member 61 is inserted into the wedge hole 24h formed in the male rotor 24, and then inserted so as to form an interference fit with the half portion 61a contacting the outer peripheral surface of the first rotating shaft 32. In other words, the space between the wedge hole 24h and the first rotation axis O1 becomes the wedge gap.

[0066] The first wedge member 61 is attached after the male rotor 24 is fixed to the first rotation shaft 32 with the first bolts 31 and the phase of the male rotor 24 about the first rotation axis O1 is determined. This firmly fixes the male rotor 24 to the first rotation shaft 32 so that it does not rotate about the first rotation axis O1.

[0067] The female rotor 26 is also provided with a second wedge member and a wedge hole similar to the first wedge member 61 and the wedge hole 24h.

[0068] This embodiment has the following advantages: The wedge members 61 are fixed in the wedge gaps formed between the rotating shafts 32, 42 and the rotors 24, 26, thereby firmly fixing the rotating shafts 32, 42 and the rotors 24, 26. This makes it possible to prevent as much as possible misalignment of the rotors 24, 26 in the rotational direction.

[0069] When the rotors 24, 26 are fixed to the rotary shafts 32, 42 using the intermediate parts 55, 55' as shown in FIGS. 9 and 10, a wedge member 61 is fixed between the rotary shafts 32, 42 and the intermediate parts 55, 55'.

[0070] 21, the half portion 61a of the wedge member 61 may be tapered toward the tip side (the first rotating shaft 32 side), which allows the half portion 61a to be more easily and firmly fixed when inserted into the wedge gap.

[0071] [Fourth embodiment] The fourth embodiment differs from the basic structure of the claw compressor 1 described above (see, for example, FIG. 4 ) in the connection structure between the rotary shafts 32, 42 and the rotors 24, 26. The other structures are the same, so a description thereof will be omitted.

[0072] 22, a shim (high friction coefficient portion) 63 is inserted between the mating surface of the tip end surface of the first rotating shaft 32 and the male rotor 24. The shim 63 has an annular shape with a central hole through which the first bolt 31 is inserted, and both surfaces (front and back) are roughened to provide a high friction coefficient. The roughening treatment is not particularly limited as long as the surface is roughened to increase the friction coefficient, and for example, a coating of electroless nickel mixed with diamond particles is used.

[0073] Although not shown, a similar shim 63 is also provided for the female rotor 26 .

[0074] This embodiment has the following advantages: The shims 63 further securely fix the rotating shafts 32, 42 to the rotors 24, 26, restricting relative movement between the rotating shafts 32, 42 and the rotors 24, 26. This makes it possible to prevent misalignment of the rotors 24, 26 in the rotational direction as much as possible.

[0075] Instead of the shim 63, the contact surfaces of the rotary shafts 32, 42 and the rotors 24, 26 may be surface treated to have a high coefficient of friction.

[0076] When the rotors 24, 26 are fixed to the rotary shafts 32, 42 using the intermediate parts 55, 55' as shown in FIGS. 9 and 10, shims 63 are provided between the rotary shafts 32, 42 and the intermediate parts 55, 55'.

[0077] In the fifth embodiment, materials are selected to optimize the axial clearance h for the basic structure of the claw compressor 1 (see, for example, FIG. 4 ) and the structure having intermediate parts 55, 55′ (see FIGS. 9 and 10 ). The rest of the structure is the same, so a description thereof will be omitted.

[0078] In FIG. 23, the axial gap h between the rotors 24, 26 and the first housing 7 in the direction of the rotation axes O1, O2 is indicated by a thick line.

[0079] When the claw compressor 1 starts operation from room temperature, the temperature of the axial clearance h rises due to the heat of compression of the compressed fluid (steam) and frictional heat caused by sliding friction. The rotating shafts 32, 42 thermally expand in the direction of arrow L1 from the position where they are fixed to the second housing 9 by the tip-side bearings 37, 47 toward the tip (toward the first housing 7). The starting point of arrow L1 is the center position of the rotation axes O1, O2 of the tip-side bearings 37, 47. The rotors 24, 26 also thermally expand in accordance with the temperature rise because compression heat is directly transferred to them. Even when intermediate parts 55, 55' are used as shown in Figures 9 and 10, the intermediate parts 55, 55' also thermally expand.

[0080] In contrast, the first housing 7 and the second housing 9 (hereinafter referred to as "housings") are exposed to the outside air and therefore do not rise in temperature as much as the rotors 24, 26, the rotating shafts 32, 42, and the intermediate parts 55, 55' (hereinafter referred to as "rotors, etc."), and therefore their thermal expansion is relatively small. In this way, the axial clearance h changes due to the difference in thermal expansion between the rotors, etc. and the housing. This axial clearance h can be kept within a desired range by appropriately combining the materials of the rotors, etc. and the housing.

[0081] FIG. 24 shows the change in axial clearance when the combination of the material of the rotor, etc. and the material of the housing is changed.

[0082] In the figure, the horizontal axis represents the ratio of the linear expansion coefficient of the rotor, etc. to that of the housing, and the vertical axis represents the axial clearance ratio, which is the ratio of the distance from the center of the tip-end bearings 37, 47 (starting point of arrow L1 in Figure 23), which is the support point for the rotating shafts 32, 42, to the axial clearance h, to the size of the axial clearance h.

[0083] In the same figure, the solid line indicates the axial clearance ratio of the axial clearance h on the base end side (upper side in Figure 23) of the rotating shafts 32, 42, and the dashed line indicates the axial clearance ratio of the axial clearance h on the tip end side (lower side in Figure 23) of the rotating shafts 32, 42.

[0084] The threshold value of the axial clearance ratio in the figure is determined based on the allowable leakage amount of compressed fluid (steam) when the discharge fluid temperature is 100°C or higher and the difference between the discharge fluid temperature and the suction fluid temperature is 15°C or higher. Specifically, the axial clearance ratio is ±1.6×10 -3 is.

[0085] As can be seen from Figure 24, it is preferable that the ratio of the linear expansion coefficient of the rotor, etc. to that of the housing be 1.8 or less. In this case, the material combinations are as follows: When the rotor, etc. and the housing are made of the same material: Linear expansion coefficient ratio 1.00 When the rotor, etc.: SUS316, the housing: SUS403: Linear expansion coefficient ratio 1.08 When the rotor, etc.: SUS403, the housing: FC material: Linear expansion coefficient ratio 0.86 When the rotor, etc.: SUS403, the housing: SUS304: Linear expansion coefficient ratio 0.57 When the rotor, etc.: SUS316, the housing: SUS304: Linear expansion coefficient ratio 0.92 When the rotor, etc.: SUS304, the housing: FC material: Linear expansion coefficient ratio 1.50 When the rotor, etc.: SUS304, the housing: SUS403: Linear expansion coefficient ratio 1.75

[0086] As shown in Fig. 25, when the threshold value of the axial gap ratio is further narrowed to further reduce the amount of steam leakage, the ratio of the linear expansion coefficients is preferably 0.5 or more and 1.2 or less. Specifically, the axial gap ratio in this case is ±6.1 × 10 -4 is.

[0087] This embodiment provides the following advantageous effects. The claw compressor 1, which is at room temperature during startup, rises in temperature and thermally expands during rated operation. This thermal expansion changes the axial clearance h in the direction of the rotational axes O1 and O2 of the rotors and the like. By setting the ratio of the linear expansion coefficients of the rotors 24 and 26 and the rotating shafts 32 and 42 to the housings 7 and 9 to 1.8 or less, the axial clearance h can be kept below an allowable value. This reduces the change in the axial clearance h due to thermal expansion to a level equivalent to the assembly precision, thereby improving the efficiency of the claw compressor 1 and enhancing its marketability.

[0088] The claw compressor and the assembly method thereof described in each of the above-described embodiments can be understood, for example, as follows.

[0089] A claw compressor (1) according to a first aspect of the present disclosure includes: a first rotor (24) provided with claw portions protruding in the radial direction; a first rotating shaft (32) that rotatably supports the first rotor; a second rotor (26) that rotates in the opposite direction to the first rotor and has recesses that receive the claw portions; a second rotating shaft (42) that rotatably supports the second rotor; a first housing (7) that houses the first rotor and the second rotor; a first rotor fixing portion (33, 24d) that fixes the first rotor inside the first housing so as to be movable in the axial direction of the first rotation axis while restraining it in the rotation direction about a first rotation axis of the first rotating shaft; and a second rotor fixing portion that fixes the second rotor inside the first housing so as to be movable in the axial direction of the second rotation axis while restraining it in the rotation direction about a second rotation axis of the second rotating shaft.

[0090] The first rotor and the second rotor are each restricted in their rotational direction but are movable in the axial direction. As a result, even if a gap occurs between each rotor and the first housing in the axial direction, the dynamic pressure of the fluid flowing through the gap during operation of the claw compressor causes each rotor to move to a central position in the axial direction and achieve balance. This equalizes the gaps on both sides of each rotor in the axial direction, minimizing leakage. The first rotor fixing portion and the second rotor fixing portion can use, for example, a key and key groove, a width across flats, a D-cut surface, serrations, or the like.

[0091] A claw compressor according to a second aspect of the present disclosure is the claw compressor of the first aspect described above, further comprising: a first intermediate component (55, 55′) provided at the axial end of the first rotating shaft; and a first intermediate component fixing member (31) that fixes the first intermediate component to the axial end of the first rotating shaft, wherein the first rotor fixing portion fixes the first rotor to the first intermediate component; and further comprising: a second intermediate component provided at the axial end of the second rotating shaft; and a second intermediate component fixing member that fixes the second intermediate component to the axial end of the second rotating shaft, wherein the second rotor fixing portion fixes the second rotor to the second intermediate component.

[0092] By fixing the intermediate part and the rotor with the rotor fixing part, the rotor is fixed so as to be movable in the axial direction while being restricted from rotating relative to the intermediate part. The intermediate part is fixed to the shaft end of the rotating shaft. With this configuration, when fixing the intermediate part to the rotating shaft with the intermediate part fixing member, the phase of the rotational direction of the intermediate part, i.e., the rotor, relative to the rotating shaft can be determined. As a result, after assembling the rotating shaft, the phase of the rotor can be determined as desired using the intermediate part, allowing for easy and accurate assembly.

[0093] In the claw compressor according to the third aspect of the present disclosure, in the first or second aspect, the first rotor is formed with a first through hole (24e) penetrating in the direction of the first rotational axis, and the second rotor is formed with a second through hole penetrating in the direction of the second rotational axis.

[0094] By providing each rotor with a through hole extending in the direction of the rotation axis, the pressure in the gaps located on both sides of each rotor in the direction of the rotation axis can be made equal, thereby ensuring that each rotor is balanced in a central position in the direction of the rotation axis during operation of the claw compressor.

[0095] The claw compressor according to a fourth aspect of the present disclosure is, in any one of the first to third aspects, provided with first thrust bearings (24f) on both sides in the axial direction of the first rotational axis of the first rotor, and with second thrust bearings (26f) on both sides in the axial direction of the second rotational axis of the second rotor.

[0096] By providing thrust bearings on both sides of each rotor in the direction of the rotation axis, the gap is adjusted by dynamic pressure during operation of the claw compressor, allowing the rotors to be balanced at a central position in the direction of the rotation axis. Examples of thrust bearings that can be used include tapered land bearings and step land bearings. The thrust bearings may be provided on the rotor side or the first housing side. Furthermore, they may also be provided on a seal pressing member that presses down on a seal member that seals around the rotation axis.

[0097] The claw compressor according to a fifth aspect of the present disclosure is any one of the first to fourth aspects, in which a first regulating pin (59) is provided to regulate the relative movement between the first rotating shaft and the first rotor to a predetermined value or less, and a second regulating pin is provided to regulate the relative movement between the second rotating shaft and the second rotor to a predetermined value or less.

[0098] Even if an excessive force is applied to the rotor due to some abnormality such as liquid compression, causing the rotor to move relative to the rotating shaft, the restricting pin can keep the relative movement below a predetermined value. This can prevent malfunction of the claw compressor. When the rotor is fixed to the rotating shaft using an intermediate part, a restricting pin is provided between the rotating shaft and the intermediate part.

[0099] A claw compressor according to a sixth aspect of the present disclosure is any one of the first to fifth aspects, in which a first wedge member (61) is fixed to a first wedge gap formed between the first rotating shaft and the first rotor, and a second wedge member is fixed to a second wedge gap formed between the second rotating shaft and the second rotor.

[0100] The rotor and the rotating shaft are firmly fixed to each other by fixing a wedge member in the wedge gap formed between the rotor and the rotating shaft. This makes it possible to prevent the rotor from misaligning in the rotational direction as much as possible. When the rotor is fixed to the rotating shaft using an intermediate part, a wedge member is fixed between the rotor and the intermediate part.

[0101] A claw compressor according to a seventh aspect of the present disclosure is any one of the first to sixth aspects, in which a first high friction coefficient portion (63) is provided on the contact surface between the first rotating shaft and the first rotor, and a second high friction coefficient portion is provided on the contact surface between the second rotating shaft and the second rotor.

[0102] The high friction coefficient portion securely fastens the rotor to the rotating shaft, restricting relative movement between the two. This minimizes misalignment of the rotor in the direction of rotation. The high friction coefficient portion may be, for example, a roughened surface, such as a surface coated with electroless nickel mixed with diamond particles. A shim with such a roughened surface may be sandwiched between the contact surfaces.

[0103] The claw compressor according to an eighth aspect of the present disclosure is, in any one of the first to seventh aspects, such that the ratio of the linear expansion coefficients of the first rotor and the first rotating shaft to the first housing is 1.8 or less, and the ratio of the linear expansion coefficients of the second rotor and the second rotating shaft to the first housing is 1.8 or less.

[0104] A claw compressor, which is kept at room temperature during startup, heats up and thermally expands during rated operation. Thermal expansion changes the clearance in the direction of the rotor's rotational axis. By setting the ratio of the linear expansion coefficients of the rotor and the rotating shaft to the housing to 1.8 or less, the clearance in the direction of the rotor's rotational axis can be kept below an allowable value. This reduces the change in the clearance due to thermal expansion to a level equivalent to the assembly precision, thereby improving the efficiency of the claw compressor and enhancing its marketability. For example, this is effective when the discharge fluid temperature of the claw compressor is 100°C or higher and the difference between the discharge fluid temperature and the suction fluid temperature is 15°C or higher. Furthermore, the linear expansion coefficient ratio is preferably 0.5 or higher and 1.2 or lower.

[0105] A method of assembling a claw compressor according to a first aspect of the present disclosure includes assembling a first rotor provided with claw portions protruding in a radial direction, a first rotating shaft that rotatably supports the first rotor, a second rotor that rotates in a direction opposite to the first rotor and has recesses that receive the claw portions, a second rotating shaft that rotatably supports the second rotor, a first housing that accommodates the first rotor and the second rotor, a first rotor fixing part that fixes the first rotor inside the first housing so as to be movable in the axial direction of the first rotation axis while restraining the first rotor in a rotation direction about a first rotation axis of the first rotating shaft, a second rotor fixing part that fixes the second rotor inside the first housing so as to be movable in the axial direction of the second rotation axis while restraining the second rotor inside the first housing so as to be movable in the axial direction of the second rotation axis, and a first intermediate component provided at a shaft end, a first intermediate component fixing member that fixes the first intermediate component to the shaft end of the first rotating shaft; a second intermediate component provided at a shaft end of the second rotating shaft, and a second intermediate component fixing member that fixes the second intermediate component to the shaft end of the second rotating shaft, the method comprising: fixing the first rotor to the first intermediate component using the first rotor fixing portion; fixing the second rotor to the second intermediate component using the second rotor fixing portion; assembling the first rotating shaft, fixing the first intermediate component to the shaft end of the first rotating shaft using the first intermediate component fixing member; and assembling the second rotating shaft, fixing the second intermediate component to the shaft end of the second rotating shaft using the second intermediate component fixing member.

[0106] A method of assembling a claw compressor according to a second aspect of the present disclosure includes assembling a first rotor provided with claw portions projecting in a radial direction, a first rotating shaft that rotatably supports the first rotor, a second rotor that rotates in the opposite direction to the first rotor and has recesses that receive the claw portions, a second rotating shaft that rotatably supports the second rotor, a first housing that accommodates the first rotor and the second rotor, a first rotor fixing part that fixes the first rotor inside the first housing so as to be movable in an axial direction of the first rotation axis while restraining the first rotor in a rotation direction about a first rotation axis of the first rotating shaft, and A method for assembling a claw compressor including: a second rotor fixing portion that fixes the second rotating shaft inside a first housing so as to be movable in the axial direction of the second rotating shaft while restraining the second rotating shaft in the rotational direction about the second rotational axis; a first wedge member that is fixed in a first wedge gap formed between the first rotating shaft and the first rotor; and a second wedge member that is fixed in a second wedge gap formed between the second rotating shaft and the second rotor, wherein the first rotor is fixed using the first rotor fixing portion, and then the first wedge member is fixed, and the second rotor is fixed using the second rotor fixing portion, and then the second wedge member is fixed.

[0107] REFERENCE SIGNS LIST 1 Claw compressor 3 Compression section 5 Gear section 7 First housing 9 Second housing 9a Inner wall 9b End face 11 Third housing 11a End face 12 Leg section 13 Intake port 15 Discharge port 19 Bearing chamber 20 Compression chamber 21 Gear chamber 22 O-ring 23 O-ring 24 Male rotor 24a Claw section 24c Recess 24d Key groove 24e First through hole 24f First thrust bearing 24g Bottomed hole 24h Wedge hole 26 Female rotor 26a Claw section 26b Recess 26c Recess 26e Second through hole 26f Second thrust bearing 31 First bolt 32 First rotating shaft 32a Tip portion 33 Key 35 Seal section 37 Front end bearing (first bearing) 38 Rear end bearing 39 First gear 41 Second bolt 42 Second rotating shaft 47 Front end bearing (second bearing) 48 Rear end bearing 49 Second gear 50 Oil seal 52 Water seal 55 First intermediate part 55' First intermediate part 58 Seal pressing member 59 First regulating pin 61 First wedge member 61a Half portion 61a1 Inner peripheral surface 61b Cylindrical portion 63 Shim O1 First rotation axis O2 Second rotation axis h Axial clearance

Claims

1. A claw compressor comprising: a first rotor provided with claws protruding in the radial direction; a first rotating shaft that rotatably supports the first rotor; a second rotor that rotates in the opposite direction to the first rotor and has recesses that receive the claws; a second rotating shaft that rotatably supports the second rotor; a first housing that houses the first rotor and the second rotor; a first rotor fixing part that fixes the first rotor inside the first housing, restraining it in the rotation direction about a first rotation axis of the first rotating shaft, while allowing it to move in the axial direction of the first rotation axis; and a second rotor fixing part that fixes the second rotor inside the first housing, restraining it in the rotation direction about a second rotation axis of the second rotating shaft, while allowing it to move in the axial direction of the second rotation axis.

2. A claw compressor as described in claim 1, comprising: a first intermediate component provided on the axial end of the first rotating shaft; and a first intermediate component fixing member that fixes the first intermediate component to the axial end of the first rotating shaft, wherein the first rotor fixing portion fixes the first rotor to the first intermediate component; and a second intermediate component provided on the axial end of the second rotating shaft; and a second intermediate component fixing member that fixes the second intermediate component to the axial end of the second rotating shaft, wherein the second rotor fixing portion fixes the second rotor to the second intermediate component.

3. A claw compressor as set forth in claim 1 or 2, wherein the first rotor is formed with a first through-hole penetrating in the direction of the first rotational axis, and the second rotor is formed with a second through-hole penetrating in the direction of the second rotational axis.

4. A claw compressor as set forth in claim 1 or 2, wherein a first thrust bearing is provided on each side of the first rotation axis of the first rotor in the axial direction, and a second thrust bearing is provided on each side of the second rotation axis of the second rotor in the axial direction.

5. A claw compressor as claimed in claim 1 or 2, wherein a first restricting pin is provided to restrict the relative movement between the first rotating shaft and the first rotor to a predetermined value or less, and a second restricting pin is provided to restrict the relative movement between the second rotating shaft and the second rotor to a predetermined value or less.

6. A claw compressor as claimed in claim 1 or 2, wherein a first wedge member is fixed in a first wedge gap formed between the first rotating shaft and the first rotor, and a second wedge member is fixed in a second wedge gap formed between the second rotating shaft and the second rotor.

7. A claw compressor according to claim 1 or 2, wherein a first high friction coefficient portion is provided on the contact surface between the first rotating shaft and the first rotor, and a second high friction coefficient portion is provided on the contact surface between the second rotating shaft and the second rotor.

8. A claw compressor as set forth in claim 1 or 2, wherein the ratio of the linear expansion coefficient of the first rotor and the first rotating shaft to the first housing is 1.8 or less, and the ratio of the linear expansion coefficient of the second rotor and the second rotating shaft to the first housing is 1.8 or less.

9. A first rotor provided with claws protruding in the radial direction; a first rotating shaft that rotatably supports the first rotor; a second rotor that rotates in the opposite direction to the first rotor and has recesses that receive the claws; a second rotating shaft that rotatably supports the second rotor; a first housing that houses the first rotor and the second rotor; a first rotor fixing part that fixes the first rotor inside the first housing so as to be movable in the axial direction of the first rotation axis while restraining it in the rotation direction about the first rotation axis of the first rotating shaft; a second rotor fixing part that fixes the second rotor inside the first housing so as to be movable in the axial direction of the second rotation axis while restraining it in the rotation direction about the second rotation axis of the second rotating shaft; a first intermediate part provided on the axial end of the first rotating shaft; a first intermediate part fixing member that fixes the first intermediate part to the axial end of the first rotating shaft; and a second intermediate part provided on the axial end of the second rotating shaft. a second intermediate component fixing member that fixes the second intermediate component to the shaft end portion of the second rotating shaft, the method comprising: fixing the first rotor to the first intermediate component using the first rotor fixing portion; fixing the second rotor to the second intermediate component using the second rotor fixing portion; after assembling the first rotating shaft, fixing the first intermediate component to the shaft end portion of the first rotating shaft using the first intermediate component fixing member; and after assembling the second rotating shaft, fixing the second intermediate component to the shaft end portion of the second rotating shaft using the second intermediate component fixing member.

10. A first rotor provided with claws protruding in the radial direction, a first rotating shaft that rotatably supports the first rotor, a second rotor that rotates in the opposite direction to the first rotor and has recesses that receive the claws, a second rotating shaft that rotatably supports the second rotor, a first housing that houses the first rotor and the second rotor, a first rotor fixing part that fixes the first rotor inside the first housing so as to be movable in the axial direction of the first rotation axis while restraining it in the rotation direction about the first rotation axis of the first rotating shaft, a second rotor fixing part that fixes the second rotor inside the first housing so as to be movable in the axial direction of the second rotation axis while restraining it in the rotation direction about the second rotation axis of the second rotating shaft, a first wedge member fixed in a first wedge gap formed between the first rotating shaft and the first rotor, and a second wedge member fixed in a second wedge gap formed between the second rotating shaft and the second rotor. a claw compressor assembly including: fixing the first rotor using the first rotor fixing portion, and then fixing the first wedge member; and fixing the second rotor using the second rotor fixing portion, and then fixing the second wedge member.

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