Claw compressor

Abstract

To realize high compression efficiency even in a steam compression application.SOLUTION: A claw compressor comprises a male rotor 24, a female rotor, a compression part 3, and a seal part. The compression part 3 forms a compression chamber 20 between a housing surface 9b and a housing surface 7a. The seal part enhances airtightness of at least one of a first gap CL1 between the housing surface 9b and an end surface 24d of the male rotor opposed to the housing surface 9b, a second gap between the housing surface 9b and an end surface of the female rotor opposed to the housing surface 9b, a third gap CL3 between the housing surface 7a and an end surface 24e of the male rotor 24 opposed to the housing surface 7a, and a fourth gap between the housing surface 7a and an end surface of the female rotor opposed to the housing surface 7a.SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present disclosure relates to claw compressors. [Background technology]

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

[0003] [Patent Document 1] Patent No. 6845596 Summary of the Invention [Problem to be solved by the invention]

[0004] When using a steam generating heat pump as an alternative to a boiler to compress the generated steam, the pressure difference between the suction pressure and the discharge pressure is large and leakage is large compared to a vacuum pump or a blower, so it is necessary to reduce the gap during the compression process in order to increase efficiency. However, in the case of a claw compressor used as a vacuum pump or a blower, the pressure difference between the suction pressure and the discharge pressure is small, so the problem of reducing the gap during the compression process does not arise, and sufficient measures have not been taken.

[0005] The present disclosure has been made in consideration of the above circumstances, and has an object to provide a claw compressor that can achieve high compression efficiency even in vapor compression applications. [Means for solving the problem]

[0006] A claw compressor according to one aspect of the present disclosure includes a first rotor having a plurality of first 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 a plurality of second claw portions protruding in the radial direction, a second rotating shaft that rotatably supports the second rotor, a compression section that forms a compression chamber that accommodates the first rotor and the second rotor, and a seal section that enhances airtightness of a gap between the first rotor and the second rotor and the compression section, wherein the first rotor has a plurality of first recesses that receive the plurality of second claw portions, and the second rotor has and a plurality of second recesses that receive a plurality of the first claw portions, the compression portion forms the compression chamber between a first accommodating surface and a second accommodating surface perpendicular to the first rotation axis and the second rotation axis, and the sealing portion enhances airtightness of at least one of a first gap between the first accommodating surface and an end face of the first rotor facing the first accommodating surface, a second gap between the first accommodating surface and an end face of the second rotor facing the first accommodating surface, a third gap between the second accommodating surface and the end face of the first rotor facing the second accommodating surface, and a fourth gap between the second accommodating surface and the end face of the second rotor facing the second accommodating surface. Effect of the Invention

[0007] According to the present disclosure, it is possible to provide a claw compressor that can achieve high compression efficiency even in vapor compression applications. [Brief description of the drawings]

[0008] [Figure 1] FIG. 1 is a perspective view showing a claw compressor according to a first embodiment of the present disclosure. [Diagram 2] FIG. 2 is a cross-sectional view of the claw compressor taken along line II-II of FIG. 1. [Diagram 3] FIG. 3 is a cross-sectional view taken along line III-III in FIG. [Figure 4] 3 is a partially enlarged view showing the vicinity of a male rotor of the claw compressor shown in FIG. 2. [Diagram 5] 3 is a partially enlarged view showing the vicinity of a female rotor of the claw compressor shown in FIG. 2. [Figure 6] 3 is a view of the male rotor and the female rotor shown in FIG. 2 as viewed from the gear portion side. [Figure 7] 3 is a view of the male rotor and the female rotor shown in FIG. 2 as viewed from the discharge port side. [Figure 8] FIG. 2 is a diagram showing a first modified example of the injection port according to the first embodiment of the present disclosure. [Figure 9] FIG. 11 is a diagram showing a second modified example of the injection port of the first embodiment of the present disclosure. [Figure 10] FIG. 13 is a diagram showing a third modified example of the injection port of the first embodiment of the present disclosure. [Figure 11] FIG. 13 is a diagram showing a fourth modified example of the injection port of the first embodiment of the present disclosure. [Figure 12] FIG. 11 is a cross-sectional view showing the vicinity of a male rotor of a claw compressor according to a second embodiment of the present disclosure. [Figure 13] FIG. 11 is a cross-sectional view showing the vicinity of a female rotor of a claw compressor according to a second embodiment of the present disclosure. [Figure 14] 14 is a view of the male rotor and the female rotor shown in FIG. 12 and FIG. 13 as viewed from the gear portion side. FIG. [Figure 15] 14 is a view of the male rotor and the female rotor shown in FIG. 12 and FIG. 13 as viewed from the discharge port side. FIG. [Figure 16] FIG. 11 is a cross-sectional view showing the vicinity of a male rotor of a claw compressor according to a modified example of the second embodiment of the present disclosure. [Figure 17] FIG. 11 is a cross-sectional view showing the vicinity of a female rotor of a claw compressor according to a modified example of the second embodiment of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. [First embodiment] A first embodiment of the present disclosure will be described below. As shown in Fig. 1, a claw compressor 1 includes a compression section 3 having a compression chamber formed therein, and a gear section 5 in which a timing gear is housed. 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 erected on an installation surface by, for example, four legs 12.

[0010] The compression section 3 has an intake port 13 for drawing in steam (fluid) and an exhaust 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.

[0011] 2, the compression section 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.

[0012] The first housing 7 has a housing surface (second housing surface) 7a that is perpendicular to the first rotation shaft 32 and the second rotation shaft 42 and is disposed on the discharge port 15 side. The second housing 9 has a housing surface (first housing surface) 9b that is perpendicular to the first rotation shaft 32 and the second rotation shaft 42 and is disposed on the gear unit 5 side. The compression unit 3 forms a compression chamber 20 between the housing surface 9b and the housing surface 7a.

[0013] 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.

[0014] As shown in Fig. 3, the male rotor 24 has a pair of hook-shaped claws (first claws) 24a. The claws 24a protrude in a radial direction perpendicular to the first rotation axis O1 and are provided symmetrically about the first rotation axis O1. The male rotor 24 rotates counterclockwise (in the direction of arrow A1) in Fig. 3.

[0015] The female rotor 26 has a pair of hook-shaped claws (second claws) 26a. The claws 26a protrude in a radial direction perpendicular to the second rotation axis O2 and are provided symmetrically about the second rotation axis O2. The female rotor 26 rotates clockwise (in the direction of arrow A2) in FIG. 3.

[0016] The claw portions 24a of the male rotor 24 and the claw portions 26a of the female rotor 26 are adapted to mesh with each other without contacting each other. The male rotor 24 is formed with a recess (first recess) 24b for receiving the claw portions 26a of the female rotor 26 during the compression stroke. The female rotor 26 is formed with a recess (second recess) 26b for receiving the claw portions 24a of the male rotor 24 during the compression stroke. The compressed steam is discharged from a discharge port 15 which is substantially triangular in shape in FIG. 3.

[0017] 3, the shape of the compression chamber 20 is determined by the inner wall 9a of the second housing 9, and has a cross-sectional shape in which two circles, a circle centered on the first rotational axis O1 and a circle centered on the second rotational axis O2, are partially overlapped. The tips of the claws 24a, 26a of the rotors 24, 26 run along the inner wall 9a of the second housing 9 with a predetermined clearance.

[0018] 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 (first bolt fastening portion) 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.

[0019] A key 35 (anti-rotation portion) is provided between the male rotor 24 and the tip end of the first rotating shaft 32. The key 35 is fitted into key grooves formed in the male rotor 24 and the first rotating shaft 32, and prevents relative rotation between the male rotor 24 and the first rotating shaft 32.

[0020] The female rotor 26 is fastened to the second rotating shaft 42 by the second bolt 41. Specifically, the second bolt 41 is screwed into the second rotating shaft 42 with the axis of the second bolt 41 coinciding with the second rotating axis O2. The second rotating shaft 42 is provided parallel to the first rotating shaft 32. That is, the first rotating axis O1 and the second rotating axis O2 are parallel to each other.

[0021] 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. The key 35 provided between the male rotor 24 and the first rotating shaft 32 is not provided between the female rotor 26 and the second rotating shaft 42. 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.

[0022] The first rotating shaft 32 supporting the male rotor 24 has a tip end located within the compression chamber 20 and a rear end connected to a drive unit (not shown). An electric motor, for example, is used as the drive unit. The first rotating shaft 32 rotates about a 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 points, a tip-side bearing 37 and a rear-end bearing 38.

[0023] The front end bearing 37 is provided in the second housing 9, and for example, a double row ball bearing is used. However, the front end bearing 37 is not limited to a double row or ball bearing. The rear end bearing 38 is located further rearward than the front end bearing 37, and is provided in the third housing 11. The rear end bearing 38 is a single row ball bearing, but is not limited to a single row or ball bearing.

[0024] A first timing gear 39 is fixed to the first rotating shaft 32 between the front end bearing 47 and the rear end bearing 38. The first timing gear 39 is, for example, a spur gear, and rotates together with the first rotating shaft 32 about the first rotation axis O1.

[0025] The first timing gear 39 is provided in the gear portion 5, and is accommodated in a gear chamber 21 formed between the rear end (the other 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.

[0026] The second rotating shaft 42 supporting the female rotor 26 has a leading end located within the compression chamber 20 and a rear end terminated in the third housing 11 .

[0027] The second rotating shaft 42 rotates about the second rotation axis O2, thereby rotating the female rotor 26 inside the compression chamber 20. The second rotating shaft 42 is rotatably supported at two locations, a front end 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 or ball bearing. The rear end bearing 48 is located on the rear end side of the front end bearing 47, and is provided in the third housing 11. The rear end bearing 48 is a single row ball bearing, but is not limited to a single row or ball bearing.

[0028] A second timing gear 49 is fixed to the second rotating shaft 42 between the front end bearing 47 and the rear end bearing 48. The second timing gear 49 is, for example, a spur gear, and rotates together with the second rotating shaft 42 about the second rotation axis O2.

[0029] The second timing gear 49 is provided in the gear portion 5 and housed in the gear chamber 21. The second timing gear 49 meshes with the first timing gear 39, and receives a driving force from the first timing gear 39. Therefore, the first rotating shaft 32 serves as a driving shaft, and the second rotating shaft 42 serves as a driven shaft.

[0030] The claw compressor 1 having the above configuration operates as follows. The first rotating shaft 32 is rotationally driven by a drive unit (not shown), and the male rotor 24 rotates in the compression chamber 20. The second rotating shaft 42 is rotated by the second timing gear 49 to which a rotational drive force is transmitted from the first timing gear 39, which rotates together with the first rotating shaft 32, and the female rotor 26 rotates in the compression chamber 20.

[0031] As the male rotor 24 and the female rotor 26 rotate within the compression chamber 20, steam is sucked in from the suction port 13. The male rotor 24 rotates counterclockwise (in the direction of arrow A1) in Fig. 3, takes in steam into the compression pocket formed by the claws 24a, and moves 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, takes in steam into the compression pocket formed by the claws 26a, and moves it downward along the outer periphery of the compression chamber 20.

[0032] The compression pocket formed by the male rotor 24 and the compression pocket formed by the female rotor 26 join together in the center of the lower part of the compression chamber 20, and in this combined compression pocket, the claws 24a of the male rotor 24 enter the recesses 26b of the female rotor 26 to compress the steam. The compressed steam is discharged to the outside from the discharge port 15.

[0033] When assembling the claw compressor, the phase adjustment of the rotors 24, 26 is performed as follows. First, with the tip side (compression chamber 20 side) of the second housing 9 open, the key 35 is attached between the male rotor 24 and the first rotating shaft 32. This prevents rotation by the key 35, and uniquely determines the relative position of the male rotor 24 in the rotational direction with respect to the first rotating shaft 32. Then, the male rotor 24 is fastened to the first rotating shaft 32 by the first bolt 31.

[0034] Next, the female rotor 26 is fastened to the second rotating shaft 42 using the second bolts 41. At this time, the position in the rotational direction relative to the second rotating shaft 42 is adjusted to a desired value, and then fastening is performed using the second bolts 41. Then, the first housing 7 is attached to the tip side of the second housing 9 to form the compression chamber 20.

[0035] Next, the seal portion 50 for improving the airtightness of the gap between the male rotor 24 and the female rotor 26 and the compression section 3 to improve the compression efficiency will be described with reference to the drawings. Fig. 4 is a partially enlarged view showing the vicinity of the male rotor 24 of the claw compressor 1 shown in Fig. 2. Fig. 5 is a partially enlarged view showing the vicinity of the female rotor 26 of the claw compressor 1 shown in Fig. 2. Fig. 6 is a view of the male rotor 24 and the female rotor 26 shown in Fig. 2 as viewed from the gear section 5 side. Fig. 7 is a view of the male rotor 24 and the female rotor 26 shown in Fig. 2 as viewed from the discharge port 15 side.

[0036] The seal portion 50 of this embodiment has a tip seal 51, a tip seal 52, and a tip seal 53. The tip seals 51, 52, and 53 are members formed of a highly wear-resistant resin material (e.g., polyphenylene sulfide (PPS) and polytetrafluoroethylene (PTFE)). As shown in Figs. 4 and 6, the tip seal 51 is a member that air-tightly seals a first gap CL1 between the housing surface 9b of the compression portion 3 and an end face 24d of the male rotor 24 facing the housing surface 9b. The tip seal 51 is disposed in a first groove portion 24d1 formed in the end face 24d.

[0037] 5 and 6, the tip seal 52 is a member that air-tightly seals the second gap CL2 between the housing surface 9b of the compression section 3 and the end face 26d of the female rotor 26 facing the housing surface 9b. The tip seal 52 is disposed in a second groove portion 26d1 formed in the end face 26d.

[0038] 4 and 7, the tip seal 53 is a member that hermetically seals the third gap CL3 between the housing surface 7a of the compression section 3 and the end face 24e of the male rotor 24 facing the housing surface 7a. The tip seal 53 is disposed in a third groove portion 24e1 formed in the end face 24e.

[0039] As shown in Figures 5 and 7, a tip seal is not disposed in the fourth gap CL4 between the housing surface 7a of the compression section 3 and the end face 26e of the female rotor 26 facing the housing surface 7a. The reason why a tip seal is not disposed in the fourth gap CL4 is that the discharge port 15 for discharging the compressed steam is formed between the claw portion 24a of the male rotor 24 and the recessed portion 26b of the female rotor 26 or between the claw portion 26a of the female rotor 26 and the recessed portion 24b of the male rotor 24 in the region facing the end face 26e of the female rotor 26 of the housing surface 7a of the compression section 3. If a tip seal is disposed in the fourth gap CL4, the tip seal will come into contact with the corner of the boundary portion between the discharge port 15 and the housing surface 7a and will be worn out.

[0040] In this embodiment, the tip seals are arranged in the first gap CL1, the second gap CL2, and the third gap CL3, and no tip seal is arranged in the fourth gap CL4, but other configurations are also possible. For example, a tip seal may be arranged in at least one of the first gap CL1, the second gap CL2, the third gap CL3, and the fourth gap CL4. When a tip seal is arranged in the fourth gap CL4, a groove for accommodating the tip seal is provided in the end face 26e of the female rotor 26.

[0041] As shown in Figures 3 and 5, the claw compressor 1 of this embodiment has an injection port (fluid supply port) 60 that supplies a fluid (e.g., water) to the compression chamber 20 to lower the temperature of the steam compressed between the claw portion 24a of the male rotor 24 and the recessed portion 26b of the female rotor 26 or between the claw portion 26a of the female rotor 26 and the recessed portion 24b of the male rotor 24.

[0042] The injection port 60 of this embodiment discharges fluid into the fourth gap CL4 between the housing surface 7a of the compression section 3 and the end face 26e of the female rotor 26 facing the housing surface 7a. The injection port 60 is located on the housing surface 7a facing the fourth gap CL4 because no tip seal is located on the end face 26e of the female rotor 26 facing the fourth gap CL4. Since no tip seal is located on the end face 26e of the female rotor 26, the tip seal is not worn down due to contact with the injection port 60.

[0043] The injection port 60 of this embodiment may be arranged to discharge the fluid into the third gap CL3, for example, when the tip seal 53 is not arranged on the end face 24e of the male rotor 24 facing the third gap CL3. In this case, the claw compressor 1 includes a tip seal 51 arranged in the first groove portion 24d1 and a tip seal 52 arranged in the second groove portion 26d1. The injection port 60 supplies the fluid from the accommodation surface 7a to the third gap CL3 and the fourth gap CL4.

[0044] The claw compressor 1 of this embodiment includes a temperature sensor (not shown) that detects the temperature of steam discharged from the discharge port 15, a flow control valve (not shown) that is disposed in a pipe that communicates with the injection port 60, and a control unit (not shown) that controls the aperture of the flow control valve. The control unit controls the aperture of the flow control valve so that the temperature detected by the temperature sensor is maintained within a predetermined temperature range (for example, a range of 140°C or higher and 160°C or lower).

[0045] The claw compressor 1 of the present embodiment described above provides the following actions and effects. According to the claw compressor of this embodiment, the seal portion 50 enhances the airtightness of at least one of the first gap CL1 between the housing surface 9b and the end face 24d of the male rotor 24 facing the housing surface 9b, the second gap CL2 between the housing surface 9b and the end face 26d of the female rotor 26 facing the housing surface 9b, the third gap CL3 between the housing surface 7a and the end face 24e of the male rotor 24 facing the housing surface 7a, and the fourth gap CL4 between the housing surface 7a and the end face 26e of the female rotor 26 facing the housing surface 7a. Therefore, when the claw compressor 1 is used for vapor compression, high compression efficiency can be achieved.

[0046] Furthermore, according to the claw compressor 1 of this embodiment, by arranging the tip seal 51 in the first groove portion 24d1, the tip seal 52 in the second groove portion 26d1, and the tip seal 53 in the third groove portion 24e1, it is possible to improve the airtightness of the first gap CL1, the second gap CL2, and the third gap CL3. Furthermore, since no tip seal is arranged in the fourth gap CL4, by arranging a tip seal in the fourth gap CL4, it is possible to prevent the tip seal from coming into contact with the corner of the boundary portion between the discharge port 15 and the storage surface 7a and becoming worn.

[0047] [First Modification] In this embodiment, the injection port 60 is configured to discharge the fluid into the fourth gap CL4 between the housing surface 7a of the compression section 3 and the end surface 26e of the female rotor 26 facing the housing surface 7a, but may be configured in other ways. For example, the injection port 60 may be an injection port 60A of a first modified example shown in Fig. 8. Fig. 8 is a diagram showing a first modified example of the injection port 60 of the first embodiment of the present disclosure.

[0048] The injection port 60A of the first modified example shown in FIG. 8 is a port that supplies fluid (e.g., water) from a supply source (not shown) of the fluid to the compression chamber 20 via the internal flow passage 42A of the second rotating shaft 42 and the internal flow passage 26f of the female rotor 26. The internal flow passage 26f supplies the fluid toward the bottom surface of the second groove portion 26d1 in which the tip seal 52 is housed. The tip seal 52 is pressed toward the housing surface 9b by the pressure of the fluid flowing from the internal flow passage 26f into the second groove portion 26d1. A biasing force toward the housing surface 9b acts on the tip seal 52, improving the airtightness between the tip seal 52 and the housing surface 9b.

[0049] The injection port 60A of the first modified example shown in FIG. 8 supplies the fluid toward the bottom surface of the second groove portion 26d1 in which the tip seal 52 is housed, but other embodiments may be used. For example, the injection port 60A may supply the fluid toward the bottom surface of the first groove portion 24d1 in which the tip seal 51 is housed. The injection port 60A may also supply the fluid toward the bottom surface of the third groove portion 24e1 in which the tip seal 53 is housed. The injection port 60A may supply the fluid to at least one of the first groove portion 24d1, the second groove portion 26d1, and the third groove portion 24e1.

[0050] [Second Modification] In this embodiment, the injection port 60 is configured to discharge the fluid into the fourth gap CL4 between the housing surface 7a of the compression section 3 and the end surface 26e of the female rotor 26 facing the housing surface 7a, but may be configured in other ways. For example, it may be an injection port 60B of a second modified example shown in Fig. 9. Fig. 9 is a diagram showing a second modified example of the injection port 60 of the first embodiment of the present disclosure.

[0051] The injection port 60B shown in Figure 9 is a port that communicates with a recess 7b formed in the first housing 7 to communicate the first space S1 and the second space S2 within the compression chamber 20 when the suction process is performed to suck steam into the compression chamber 20 from the suction port 13 after the compression process is completed in which compressed steam is discharged from the discharge port 15.

[0052] The first space S1 is a space that generates negative pressure, and if this space is kept sealed, excessive power is required to rotate the male rotor 24 and the female rotor 26. Therefore, a recess 7b is formed in the first housing 7 to communicate the first space S1 with the second space S2. If the injection port 60B communicates with the space in which the steam compressed in the compression process of the compression chamber 20 is sealed, the compressed steam will flow back into the injection port 60B. Therefore, in the second modified example, the injection port 60B is provided so as to communicate with the recess 7b, thereby making it possible to appropriately prevent the compressed steam from flowing back.

[0053] [Third Modification] In this embodiment, the injection port 60 is configured to discharge the fluid into the fourth gap CL4 between the housing surface 7a of the compression section 3 and the end surface 26e of the female rotor 26 facing the housing surface 7a, but may be configured in other ways. For example, it may be an injection port 60C of a third modified example shown in Fig. 10. Fig. 10 is a diagram showing a third modified example of the injection port 60 of the first embodiment of the present disclosure.

[0054] The claw compressor 1 of the third modified example includes an injection port 60C that supplies a fluid to the compression chamber 20 to reduce the temperature of the steam compressed by the male rotor 24 and the female rotor 26. The second housing 9 of the compression section 3 has a connecting surface 9c that connects the accommodation surface 7a and the accommodation surface 9b and is arranged to radially surround the compression chamber 20. The injection port 60C supplies a fluid (e.g., water) from the outside of the connecting surface 9c toward a gap CL5 between the female rotor 26 of the compression chamber 20 and the connecting surface 9c along a radial direction perpendicular to the first rotating shaft 32 and the second rotating shaft 42.

[0055] [Fourth Modification] Although the claw compressor 1 of the third modified example is provided with the injection port 60C that supplies fluid from the outside of the connecting surface 9c toward the compression chamber 20, other configurations may be used. For example, the injection port 60D of the fourth modified example shown in FIG. 11 may be used. FIG. 11 is a diagram showing a fourth modified example of the injection port 60 of the first embodiment of the present disclosure. The injection port 60D of the fourth modified example shown in FIG. 11 is a port that supplies fluid from a fluid (e.g., water) supply source (not shown) to the compression chamber 20 via the internal flow path 42D of the second rotating shaft 42 and the internal flow path 26g of the female rotor 26.

[0056] The injection port 60D of the fourth modified example branches the fluid guided from the internal flow path 42D of the second rotating shaft 42 in three directions in the internal flow path 26g, guides it in a radial direction perpendicular to the second rotating shaft 42, and supplies the fluid (e.g., water) from the tip of the claw portion 26a toward the gap CL5 between the female rotor 26 and the connecting surface 9c.

[0057] Second Embodiment Next, a claw compressor 1 according to a second embodiment of the present disclosure will be described with reference to the drawings. The claw compressor 1 according to the first embodiment enhances the airtightness of the gaps between the male rotor 24 and the female rotor 26 and the inner circumferential surface of the compression chamber 20 by arranging a tip seal in at least one of the first gap CL1, the second gap CL2, the third gap CL3, and the fourth gap CL4. In contrast, the claw compressor 1 according to the present embodiment enhances the airtightness of the gaps between the male rotor 24 and the female rotor 26 and the inner circumferential surface of the compression chamber 20 by supplying a fluid to at least one of the first gap CL1, the second gap CL2, the third gap CL3, and the fourth gap CL4.

[0058] Fig. 12 is a cross-sectional view showing the vicinity of the male rotor 24 of the claw compressor 1 according to the second embodiment of the present disclosure. Fig. 13 is a cross-sectional view showing the vicinity of the female rotor 26 of the claw compressor 1 according to the second embodiment of the present disclosure. Fig. 14 is a view of the male rotor 24 and the female rotor 26 shown in Figs. 12 and 13 as viewed from the gear portion 5 side. Fig. 15 is a view of the male rotor 24 and the female rotor 26 shown in Figs. 12 and 13 as viewed from the discharge port 15 side.

[0059] As shown in Fig. 12, a first groove portion 24d1 is formed in an end face 24d of the male rotor 24 facing the housing surface 9b, and a third groove portion 24e1 is formed in an end face 24e of the male rotor 24 facing the housing surface 7a. As shown in Fig. 13, a second groove portion 26d1 is formed in an end face 26d of the female rotor 26 facing the housing surface 9b, and a fourth groove portion 26e1 is formed in an end face 26e of the female rotor 26 facing the housing surface 7a.

[0060] 12, the claw compressor 1 of this embodiment has an injection port 60E that supplies a fluid (e.g., water) from a supply source (not shown) of the fluid to the compression chamber 20 via the internal flow passage 32E of the first rotating shaft 32 and the internal flow passage 24f of the male rotor 24. The injection port 60E is a port that supplies a fluid (e.g., water) to the compression chamber 20 to reduce the temperature of the steam compressed by the male rotor 24 and the female rotor 26. The internal flow passage 24f supplies the fluid toward the bottom surface of the first groove portion 24d1 and the bottom surface of the third groove portion 24e1.

[0061] The fluid supplied to the bottom surface of the first groove portion 24d1 is supplied to the area of ​​the first gap CL1 between the housing surface 9b and the end surface 24d of the male rotor 24, which faces the first groove portion 24d1, and forms a first seal area Se1 that corresponds to the shape of the first groove portion 24d1. Therefore, the airtightness between the first groove portion 24d1 and the housing surface 9b is improved. As shown in FIG. 14, the first seal area Se1 has a shape that corresponds to the first groove portion 24d1.

[0062] The fluid supplied to the bottom surface of the third groove portion 24e1 is supplied to the area of ​​the third gap CL3 between the housing surface 7a and the end surface 24e of the male rotor 24, which faces the third groove portion 24e1, and forms a third seal area Se3 that corresponds to the shape of the third groove portion 24e1. Therefore, the airtightness between the third groove portion 24e1 and the housing surface 7a is improved. As shown in FIG. 15, the third seal area Se3 has a shape that corresponds to the third groove portion 24e1.

[0063] 13, the claw compressor 1 of this embodiment has an injection port 60F that supplies a fluid (e.g., water) from a supply source (not shown) of the fluid to the compression chamber 20 via the internal flow passage 42F of the second rotating shaft 42 and the internal flow passage 26g of the female rotor 26. The injection port 60F is a port that supplies a fluid (e.g., water) to the compression chamber 20 to reduce the temperature of the steam compressed by the male rotor 24 and the female rotor 26. The internal flow passage 26g supplies the fluid toward the bottom surface of the second groove portion 26d1 and the bottom surface of the fourth groove portion 26e1.

[0064] The fluid supplied to the bottom surface of the second groove portion 26d1 is supplied to a region of the second gap CL2 between the housing surface 9b and the end surface 26d of the female rotor 26, which faces the second groove portion 26d1, and forms a second seal region Se2 that corresponds to the shape of the second groove portion 26d1. Therefore, the airtightness between the second groove portion 26d1 and the housing surface 9b is improved. As shown in FIG. 14, the second seal region Se2 has a shape that corresponds to the second groove portion 26d1.

[0065] The fluid supplied to the bottom surface of the fourth groove portion 26e1 is supplied to the area of ​​the fourth gap CL4 between the housing surface 7a and the end surface 26e of the female rotor 26, which faces the fourth groove portion 26e1, and forms a fourth seal area Se4 that corresponds to the shape of the fourth groove portion 26e1. Therefore, the airtightness between the fourth groove portion 26e1 and the housing surface 7a is improved. As shown in FIG. 15, the fourth seal area Se4 has a shape that corresponds to the fourth groove portion 26e1.

[0066] According to the claw compressor 1 of the present embodiment, by supplying a fluid for lowering the temperature of the steam to the first groove portion 24d1, the second groove portion 26d1, the third groove portion 24e1, and the fourth groove portion 26e1, it is possible to maintain at an appropriate temperature the temperature of the steam discharged from the discharge port 15. In addition, by forming a seal region corresponding to the shapes of the first groove portion 24d1, the second groove portion 26d1, the third groove portion 24e1, and the fourth groove portion 26e1 by the fluid, it is possible to increase the airtightness of the first gap CL1, the second gap CL2, the third gap CL3, and the fourth gap CL4.

[0067] [Modifications] The claw compressor 1 of the present embodiment includes the injection port 60E that supplies fluid from the internal passage 32E of the first rotating shaft 32 to the internal passage 24f of the male rotor 24, and the injection port 60F that supplies fluid from the internal passage 42F of the second rotating shaft 42 to the internal passage 26g of the female rotor 26, but may be in other forms. For example, the claw compressor 1 may include an injection port 60G that supplies fluid from the first housing 7 side to the internal passage 24g of the male rotor 24, and an injection port 60H that supplies fluid from the first housing 7 side to the internal passage 26h of the female rotor 26.

[0068] Fig. 16 is a cross-sectional view showing the vicinity of the male rotor 24 of the claw compressor 1 according to a modified example of the second embodiment of the present disclosure. Fig. 17 is a cross-sectional view showing the vicinity of the female rotor 26 of the claw compressor 1 according to a modified example of the second embodiment of the present disclosure.

[0069] 16, the claw compressor 1 according to the modified example includes an injection port 60G that supplies fluid to the recess 24c of the male rotor 24 from the first housing 7 side. The fluid supplied from the injection port 60G to the recess 24c is guided to the third groove 24e1 via the grooves 24e2 and 24e3 formed in the end face 24e of the male rotor 24. The fluid guided to the third groove 24e1 is guided to the first groove 24d1 via the internal flow path 24g.

[0070] 17, the claw compressor 1 according to the modified example includes an injection port 60H that supplies fluid to the recess 26c of the female rotor 26 from the first housing 7 side. The fluid supplied from the injection port 60H to the recess 26c is guided to the fourth groove 26e1 via the grooves 26e2 and 26e3 formed in the end face 26e of the female rotor 26. The fluid guided to the fourth groove 26e1 is guided to the second groove 26d1 via the internal flow path 26h.

[0071] Other Embodiments In the above, the male rotor 24 has a pair of claws 24a and a pair of recesses 24b, and the female rotor 26 has a pair of claws 26a and a pair of recesses 26b, but other configurations are also possible. For example, the male rotor 24 may have three or more claws 24a and three or more recesses 24b, and the female rotor 26 may have three or more claws 26a and three or more recesses 26b.

[0072] By doing so, the compression stroke occurs regardless of the timing when the male rotor 24 rotates once about the first rotating shaft 32 and the female rotor 26 rotates once about the second rotating shaft 42. Therefore, it is possible to prevent errors caused by backlash due to disengagement of the gear portion 5 caused by timing when the compression stroke does not occur.

[0073] The claw compressors described in the above-described embodiments can be understood, for example, as follows. A claw compressor according to a first aspect of the present disclosure includes a first rotor (24) having a plurality of first claw portions (24a) protruding in a radial direction, a first rotating shaft (32) that rotatably supports the first rotor, a second rotor (26) that rotates in a direction opposite to the first rotor and has a plurality of second claw portions (26a) protruding in a radial direction, a second rotating shaft (42) that rotatably supports the second rotor, a compression section (3) that forms a compression chamber (20) that houses the first rotor and the second rotor, and a seal section (50) that enhances airtightness of a gap between the first rotor and the second rotor and the compression section, wherein the first rotor has a plurality of first recesses (24b) that receive the plurality of second claw portions, and the second rotor has a plurality of second recesses (24b) that receive the plurality of second claw portions. The compression portion has a plurality of second recesses (26b) that receive first claw portions, and the compression portion forms the compression chamber between a first accommodating surface (9b) and a second accommodating surface (7a) that are perpendicular to the first rotation axis and the second rotation axis, and the sealing portion enhances airtightness of at least one of a first gap (CL1) between the first accommodating surface and an end face (24d) of the first rotor facing the first accommodating surface, a second gap (CL2) between the first accommodating surface and an end face (26d) of the second rotor facing the first accommodating surface, a third gap (CL3) between the second accommodating surface and an end face (24e) of the first rotor facing the second accommodating surface, and a fourth gap (CL4) between the second accommodating surface and an end face (26e) of the second rotor facing the second accommodating surface.

[0074] According to the claw compressor according to the first aspect of the present disclosure, the seal portion enhances airtightness of at least one of a first gap between the first accommodating surface and the end face of the first rotor facing the first accommodating surface, a second gap between the first accommodating surface and the end face of the second rotor facing the first accommodating surface, a third gap between the second accommodating surface and the end face of the first rotor facing the second accommodating surface, and a fourth gap between the second accommodating surface and the end face of the second rotor facing the second accommodating surface, thereby achieving high compression efficiency when the claw compressor is used for vapor compression purposes.

[0075] The claw compressor according to a second aspect of the present disclosure is the first aspect, and further includes the following configuration: That is, the seal portion has a first tip seal (51) arranged in a first groove portion (24d1) formed in an end face of the first rotor facing the first accommodating surface, a second tip seal (52) arranged in a second groove portion (26d1) formed in an end face of the second rotor facing the first accommodating surface, and a third tip seal (53) arranged in a third groove portion (24e1) formed in the end face of the first rotor facing the second accommodating surface, and a discharge port (15) for discharging steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess is formed in a region of the second accommodating surface facing the end face of the second rotor.

[0076] According to the claw compressor of the second aspect of the present disclosure, the first tip seal is disposed in the first groove, the second tip seal is disposed in the second groove, and the third tip seal is disposed in the third groove, thereby improving the airtightness of the first gap, the second gap, and the third gap. Also, since no tip seal is disposed in the fourth gap, disposing a tip seal in the fourth gap can prevent the tip seal from coming into contact with the corner of the boundary between the discharge port and the second storage surface and becoming worn.

[0077] The claw compressor according to a third aspect of the present disclosure is the second aspect, and further includes the following configuration: That is, the claw compressor has a fluid supply port (60A) that supplies a fluid for reducing a temperature of the steam to at least one of the first groove portion, the second groove portion, and the third groove portion. According to the claw compressor of the third aspect of the present disclosure, a fluid for lowering the temperature of the steam is supplied to at least one of the first groove portion, the second groove portion, and the third groove portion, so that the temperature of the steam discharged from the discharge port can be maintained at an appropriate temperature. Also, a biasing force of the fluid acts on at least one of the first tip seal, the second tip seal, and the third tip seal, so that the sealing performance of the tip seals is improved.

[0078] The claw compressor according to a fourth aspect of the present disclosure is the second aspect, and further includes the following configuration: A fluid supply port (60) that supplies a fluid to the compression chamber for reducing a temperature of the steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess, and the fluid supply port supplies a fluid from the second housing surface to the fourth gap. According to the claw compressor of the fourth aspect of the present disclosure, fluid is supplied from the second accommodating surface to the fourth gap in which no tip seal is disposed, so that there is no problem in that the tip seal is worn down by the fluid supply port provided on the second accommodating surface.

[0079] The claw compressor according to a fifth aspect of the present disclosure is the first aspect, and further includes the following configuration: the claw compressor includes a fluid supply port (60) that supplies, to the compression chamber, a fluid for lowering a temperature of steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess, the seal portion includes a first tip seal (51) arranged in a first groove portion (24d1) formed in an end face of the first rotor facing the first accommodating surface and a second tip seal (52) arranged in a second groove portion (26d1) formed in an end face of the second rotor facing the first accommodating surface, and the fluid supply port supplies a fluid from the second accommodating surface to the third gap and the fourth gap.

[0080] According to the claw compressor of the fifth aspect of the present disclosure, fluid is supplied from the second accommodating surface to the third and fourth gaps where no tip seal is disposed, so that there is no problem in that the tip seal is worn down by the fluid supply port provided on the second accommodating surface.

[0081] The claw compressor according to a sixth aspect of the present disclosure is the first aspect, and further includes the following configuration: the claw compressor includes a fluid supply port (60C) that supplies to the compression chamber a fluid for lowering a temperature of the steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess, the compression portion has a connecting surface (9c) that connects the first accommodating surface and the second accommodating surface and is arranged to surround the compression chamber, and the fluid supply port supplies a fluid from the connecting surface to the compression chamber along a radial direction perpendicular to the first rotation axis and the second rotation axis.

[0082] According to the claw compressor of the sixth aspect of the present disclosure, by supplying fluid from the connecting surface to the compression chamber along a radial direction perpendicular to the first rotating shaft and the second rotating shaft, the fluid can be supplied to the compression chamber without wearing out the tip seal, and the temperature of the steam discharged from the discharge port can be maintained at an appropriate temperature.

[0083] The claw compressor according to a seventh aspect of the present disclosure is the first aspect, and further includes the following configuration: A fluid supply port (60A) that supplies a fluid for reducing a temperature of steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess to the compression chamber via an internal flow path (26f) formed inside the second rotor. According to the claw compressor of the seventh aspect of the present disclosure, the fluid supply port supplies fluid to the compression chamber through the internal flow path (26f) formed inside the second rotor, thereby making it possible to maintain the temperature of the steam discharged from the discharge port at an appropriate temperature.

[0084] The claw compressor according to an eighth aspect of the present disclosure is the seventh aspect, and further includes the following configuration: the compression chamber has a connecting surface (9c) that connects the first and second accommodating surfaces and is arranged so as to surround the compression chamber, and the fluid supply port (60C) supplies fluid to a gap between the second rotor and the connecting surface. According to the claw compressor of the eighth aspect of the present disclosure, by supplying fluid to the gap between the second rotor and the connecting surface via the internal flow path (26f) formed inside the second rotor, it is possible to supply fluid to the compression chamber without wearing down the tip seal, and to maintain the temperature of the steam discharged from the discharge port at an appropriate temperature.

[0085] The claw compressor according to a ninth aspect of the present disclosure is the first aspect, and further includes the following configuration: a first groove portion (24d1) is formed in an end face of the first rotor facing the first accommodating surface, a second groove portion (26d1) is formed in an end face of the second rotor facing the first accommodating surface, a third groove portion (24e1) is formed in an end face of the first rotor facing the second accommodating surface, a fourth groove portion (26e1) is formed in an end face of the second rotor facing the second accommodating surface, and the seal portion has fluid supply ports (60E, 60F) that supply a fluid for lowering a temperature of the steam to the first groove portion, the second groove portion, the third groove portion, and the fourth groove portion.

[0086] According to the claw compressor of the ninth aspect of the present disclosure, the temperature of the steam discharged from the discharge port can be maintained at an appropriate temperature by supplying a fluid for lowering the temperature of the steam to the first groove portion, the second groove portion, the third groove portion, and the fourth groove portion. Also, a seal area corresponding to the shapes of the first groove portion, the second groove portion, the third groove portion, and the fourth groove portion is formed by the fluid, and the airtightness of the first gap, the second gap, the third gap, and the fourth gap can be improved.

[0087] The claw compressor according to a tenth aspect of the present disclosure is the claw compressor of any one of the third to ninth aspects, further comprising the following configuration: a regulating valve that adjusts the amount of fluid supplied from the fluid supply port to the compression chamber in response to a temperature of the fluid discharged from the compression chamber. According to the claw compressor of the tenth aspect of the present disclosure, the temperature of the fluid discharged from the compression chamber can be maintained within an appropriate range by adjusting the amount of fluid supplied from the fluid supply port to the compression chamber in accordance with the temperature of the fluid discharged from the compression chamber. [Explanation of symbols]

[0088] 1 Claw compressor 3 Compression section 5 Gear section 7 First Housing 7a Storage area 7b recess 9 Second Housing 9a Inner wall 9b Storage surface 9c Connecting surface 11 Third Housing 13 Intake port 15 Outlet 20 Compression chamber 21 Gear Room 24 Osrotor (First Rotor) 24a,26a Claw part 24b, 26b Recess 24c,26c recess 24d,24e,26d,26e end face 24d1 First groove 24e2,24e3,26e2,26e3 Groove 24e1 Third groove 24f, 24g, 26f, 26g, 26h, 32E, 42A, 42D, 42F Internal flow path 26 Female rotor (second rotor) 26d1 Second groove 26e1 4th groove 32 First Rotation Axis 42 Second Rotation Axis 50 Seal part 51, 52, 53 Chip seal 60,60A,60B,60C,60D,60E,60F,60G,60H Fluid supply port CL1 First gap CL2 Second gap CL3 3rd gap CL4 4th gap O1 First rotation axis O2 Second rotation axis S1 1st space S2 2nd space Se1 First seal area Se2 Second seal area Se3 3rd seal area Se4 4th seal area

Claims

1. a first rotor having a plurality of first claws protruding in a radial direction; a first rotating shaft that rotatably supports the first rotor; a second rotor rotating in a direction opposite to that of the first rotor and having a plurality of second claws protruding in the radial direction; a second rotating shaft that rotatably supports the second rotor; a compression section that defines a compression chamber that accommodates the first rotor and the second rotor; a seal portion for enhancing airtightness of a gap between the first rotor and the compression portion, and ... second rotor and the compression portion, the first rotor has a plurality of first recesses that receive the plurality of second claws, the second rotor has a plurality of second recesses that receive the plurality of first claws, The compression section defines the compression chamber between a first housing surface and a second housing surface perpendicular to the first rotation axis and the second rotation axis, The sealing portion increases the airtightness of at least one of a first gap between the first accommodating surface and an end face of the first rotor facing the first accommodating surface, a second gap between the first accommodating surface and an end face of the second rotor facing the first accommodating surface, a third gap between the second accommodating surface and an end face of the first rotor facing the second accommodating surface, and a fourth gap between the second accommodating surface and an end face of the second rotor facing the second accommodating surface.

2. The seal portion is a first tip seal disposed in a first groove formed in an end surface of the first rotor facing the first housing surface; a second tip seal disposed in a second groove formed in an end surface of the second rotor facing the first housing surface; a third tip seal disposed in a third groove formed in an end surface of the first rotor facing the second housing surface, 2. The claw compressor according to claim 1, wherein a discharge port is formed in a region of the second accommodating surface facing an end face of the second rotor, the discharge port discharging steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess.

3. 3. The claw compressor according to claim 2, further comprising a fluid supply port for supplying a fluid for lowering a temperature of the steam to at least one of the first groove portion, the second groove portion, and the third groove portion.

4. a fluid supply port that supplies a fluid to the compression chamber for reducing a temperature of the steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess, The claw compressor according to claim 2 , wherein the fluid supply port supplies the fluid from the second housing surface to the fourth gap.

5. a fluid supply port that supplies a fluid to the compression chamber for reducing a temperature of the steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess, The seal portion is a first tip seal disposed in a first groove formed in an end surface of the first rotor facing the first housing surface; a second tip seal disposed in a second groove formed in an end surface of the second rotor facing the first housing surface, The claw compressor according to claim 1 , wherein the fluid supply port supplies the fluid from the second storage surface to the third gap and the fourth gap.

6. a fluid supply port that supplies a fluid to the compression chamber for reducing a temperature of the steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess, the compression portion has a connecting surface that connects the first storage surface and the second storage surface and is arranged to surround the compression chamber, The claw compressor according to claim 1 , wherein the fluid supply port supplies the fluid from the connection surface to the compression chamber along a radial direction perpendicular to the first rotation axis and the second rotation axis.

7. 2. The claw compressor according to claim 1, further comprising a fluid supply port that supplies a fluid for lowering a temperature of the steam compressed between the first claw portion and the first recess or between the second claw portion and the second recess to the compression chamber via an internal flow passage formed inside the second rotor.

8. The compression chamber has a connecting surface that connects the first storage surface and the second storage surface and is arranged to surround the compression chamber, The claw compressor according to claim 7 , wherein the fluid supply port supplies fluid to a gap between the second rotor and the connecting surface.

9. a first groove portion is formed in an end surface of the first rotor facing the first housing surface; a second groove portion is formed in an end surface of the second rotor facing the first housing surface, a third groove portion is formed in an end surface of the first rotor facing the second housing surface, a fourth groove portion is formed in an end surface of the second rotor facing the second housing surface, 2. The claw compressor according to claim 1, wherein the seal portion has a fluid supply port that supplies a fluid for lowering a temperature of the steam to the first groove portion, the second groove portion, the third groove portion, and the fourth groove portion.

10. The claw compressor according to any one of claims 3 to 9, further comprising an adjustment valve that adjusts a supply amount of fluid supplied from the fluid supply port to the compression chamber in accordance with a temperature of the fluid discharged from the compression chamber.

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