JP2025023726A - Claw Compressor - Google Patents

Abstract

To improve the reliability of a bearing part.SOLUTION: A claw compressor comprises: a male rotor 24; a first rotating shaft 32 which rotatably supports the male rotor 24; a female rotor 26 which rotates in a direction opposite to the male rotor 24; a second rotating shaft 42 which rotatably supports the female rotor 26; a tip-side bearing 37 which rotatably supports the first rotating shaft 32; a second housing 9 in which a bearing chamber 19 for accommodating the tip-side bearing 37 is formed; and a third bearing 11 which accommodates a gear part 5, and in which a gear chamber 21 which is fully filled with a lubricant is formed. An inclined first lubricant supply flow passage for introducing the lubricant which fully fills the gear chamber 21 to the bearing chamber 19 is formed in the second housing 9. An upstream-side end of the lubricant supply flow passage is formed at an end face 9b of the second housing 9. A mating face between the third housing 11 and the second housing 9 is located at the tip-side bearing 37 side rather than a center of the gear part 5.SELECTED DRAWING: Figure 2

Description

This disclosure relates to claw compressors.

A claw compressor has a pair of rotors with hook-shaped claws formed inside a housing that forms a compression chamber. The pair of rotors are connected via a timing gear. Each rotor rotates at the same speed in opposite directions without contact while maintaining a specified clearance, forming a compression pocket between the two rotors, and discharging the fluid compressed in this compression pocket. Such claw compressors are often used mainly as vacuum pumps and blowers (see, for example, Patent Document 1).

Patent No. 6845596

When using a steam generation heat pump as an alternative to a boiler to compress the generated steam, it is necessary to operate it under a higher load than a vacuum pump or blower. When operating under high load, such as when compressing steam, it is necessary to lubricate the power transmission parts (e.g. gears, etc.) that transmit power from the drive shaft to the driven shaft, and the bearing parts that support each shaft with lubricating oil. When using a claw compressor for steam compression purposes, the following issues arise compared to vacuum pump and blower applications.

In a claw compressor, when oil is supplied to the bearings by splashing it from the power transmission unit, it is necessary to provide an oil supply path to guide the splashed lubricating oil to the bearings. However, generally, the only power available to drive the lubricating oil to the bearings is gravity. Under such circumstances, the lubricating oil cannot be properly guided to the bearings, which can reduce the reliability of the bearings.

This disclosure was made in light of these circumstances, and aims to provide a claw compressor that can improve the reliability of the bearing section.

In order to solve the above problems, the claw compressor of the present disclosure employs the following measures.
a claw compressor according to one aspect of the present disclosure, the claw compressor comprising: a first rotor provided with claw portions protruding in a radial direction; a first rotating shaft extending in a predetermined direction and supporting the rotation of the first rotor; a second rotor rotating in a direction opposite to the first rotor and having recesses for receiving the claw portions during a compression process; a second rotating shaft extending in the predetermined direction and supporting the rotation of the second rotor; a bearing portion rotatably supporting the first rotating shaft and/or the second rotating shaft; a bearing chamber housing having a bearing chamber formed therein for accommodating the bearing portion; and a rotor housing having a rotor chamber formed therein for accommodating a rotor and filled with lubricating oil, the bearing chamber housing has a lubricating oil supply passage formed therein for guiding the lubricating oil filling the rotor chamber to the bearing chamber and being inclined downward with respect to a horizontal plane, the upstream end of the lubricating oil supply passage being formed on the end face of the bearing chamber housing facing the rotor housing, and the mating surface between the rotor housing and the bearing chamber housing is located on the bearing portion side of the center of the rotor in the predetermined direction.

This disclosure makes it possible to improve the reliability of the bearing section.

FIG. 1 is a perspective view showing a claw compressor according to a first embodiment of the present disclosure. FIG. 2 is a cross-sectional view of the claw compressor of FIG. 1 taken along line II-II. 3 is a cross-sectional view taken along line III-III in FIG. 2. FIG. 4 is a cross-sectional view of the claw compressor of FIG. 1 taken along line IV-IV. FIG. 5 is an enlarged view of a V portion of the claw compressor of FIG. FIG. 5 is an enlarged view of a portion VI of the claw compressor of FIG. 4 . FIG. 4 is a cross-sectional view corresponding to FIG. 3 , showing a claw compressor according to a second embodiment of the present disclosure. FIG. 5 is a cross-sectional view corresponding to FIG. 4, showing a claw compressor according to a second embodiment of the present disclosure.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings.
[First embodiment]
Hereinafter, a first embodiment of the present disclosure will be described. 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.

The claw compressor 1 according to this embodiment is used for compressing steam. As shown in Fig. 1, the claw compressor 1 includes a compression section 3 having a compression chamber 20 formed therein, and a gear section (rotating body) 5 housing a timing gear.
The compression section 3 is formed by a first housing 7 and a second housing (bearing chamber housing) 9, and the gear section 5 is formed by the second housing 9 and a third housing (rotor housing) 11. The claw compressor 1 is supported on an installation surface by, for example, four legs 12.

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 in steam may be at negative or positive pressure.

As shown in FIG. 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.

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

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.

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

The claws 24a of the male rotor 24 and the claws 26a of the female rotor 26 are adapted to mesh without contact. The female rotor 26 is formed with a recess 26b that receives the claws 24a of the male rotor 24 during the compression process. The compressed steam is discharged from the discharge port 15, which is approximately triangular in shape as shown in FIG. 3.

As shown in FIG. 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, one centered on the first rotation axis O1 and the other centered on the second rotation 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.

As shown in FIG. 2, the male rotor 24 is fastened to the first rotating shaft 32 by the 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 rotating 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.

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. In other words, the first rotating axis O1 and the second rotating axis O2 are parallel.

The fastening structure (second bolt fastening portion) is configured with the center 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.

The first rotating shaft 32 that supports the male rotor 24 has a tip located in the compression chamber 20 and a 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 around the first rotation axis O1, which causes the male rotor 24 to rotate in the compression chamber 20. The first rotating shaft 32 is supported rotatably at two points, a tip bearing (bearing portion) 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 a double-row or 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 a single-row or ball bearing.

A first timing gear 39 is fixed to the first rotating shaft 32 between the tip end bearing (bearing portion) 47 and the rear end bearing 38. The first timing 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 the second rotating shaft 42 via the gear portion 5.

The first timing gear 39 is provided in the gear portion 5, and is accommodated in a gear chamber (rotating body 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 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, which lubricates the gear portion 5.

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).

The second rotating 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 the rear end bearing 48. A seal portion 35 is provided between the space S and the gear chamber 21.

The second rotating shaft 42 rotates around the second rotation axis O2, which rotates the female rotor 26 in the compression chamber 20. The second rotating shaft 42 is supported rotatably 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 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 or ball bearing.

A second timing gear 49 is fixed to the second rotating shaft 42 between the leading end bearing 47 and the trailing end bearing 48. The second timing gear 49 is, for example, a spur gear, and rotates together with the second rotating shaft 42 around the second rotation axis O2.

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

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

As shown in Figures 2 and 4, the end face 9b of the second housing 9 and the end face 11a of the third housing 11 are in surface contact. The mating surface between the second housing 9 and the third housing 11 is located on the tip bearing 37 side of the center of the gear portion 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 bearing 37 on the gear portion 5 side.

A bearing chamber 19 for accommodating the tip end bearings 37 and 47 is formed inside the second housing 9 .
6, a lubricating oil supply passage 54 is formed inside the second housing 9 to guide the lubricating oil in the gear chamber 21 to the bearing chamber 19. The lubricating oil supply passage 54 has a first lubricating oil supply passage 54a whose upstream end is connected to an opening formed in the end face 9b of the second housing 9 and which is inclined downward with respect to the horizontal plane, a second lubricating oil supply passage 54b which extends downward from the downstream end of the first lubricating oil supply passage 54a, and a third lubricating oil supply passage 54c which extends toward the bearing chamber 19 so as to incline downward from the downstream end of the second lubricating oil supply passage 54b.
The inclination angle of the first lubricant oil supply passage 54a with respect to the horizontal plane is, for example, 5 degrees or more. The downstream end of the third lubricant oil supply passage 54c is connected to the bearing chamber 19.

5, 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 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.
The oil seal 50 and the water seal 52 provide a seal between an oil-rich space R such as the bearing chamber 19 and an oil-free space F such as the compression chamber 20 .

The upstream end of the lubricating oil discharge passage 56 is connected to the space between the oil seal 50 and the water seal 52. The downstream end of the lubricating oil discharge passage 56 is connected to an oil reservoir (not shown) provided outside the second housing 9. The inside of the oil reservoir is at atmospheric pressure.

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.

The male rotor 24 and the female rotor 26 rotate in the compression chamber 20, and steam is sucked in from the intake port 13. The male rotor 24 rotates counterclockwise (in the direction of arrow A1) in FIG. 3, and 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, and 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. The compression pocket formed by the male rotor 24 and the compression pocket formed by the female rotor 26 join in the center of the lower part of the compression chamber 20, and in the resulting combined compression pocket (compression space), the claws 24a of the male rotor 24 penetrate into 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.

The gear chamber 21 is filled with lubricating oil. When the gear portion 5 in the gear chamber 21 rotates, the lubricating oil splashes up. The splashed lubricating oil adheres to the ceiling of the gear chamber 21, and a portion of the lubricating oil flows into the lubricating oil supply passage 54 from an opening formed in the end surface 9b of the second housing 9. The lubricating oil that flows into the lubricating oil supply passage 54 flows through the first lubricating oil supply passage 54a, which is inclined downward (see arrow A3 in FIG. 6). It is then guided into the bearing chamber 19 via the second lubricating oil supply passage 54b and the third lubricating oil supply passage 54c (see arrows A4 and A5 in FIG. 6). The lubricating oil guided into the bearing chamber 19 lubricates the tip bearings 37 and 47.

As shown in FIG. 5, a portion of the lubricating oil introduced into the bearing chamber 19 flows through the gap formed between the outer circumferential surface of the first rotating shaft 32 and the second housing 9 toward the compression chamber 20 (see arrow A6). In particular, when the compression chamber 20 is under negative pressure, the lubricating oil tends to flow toward the compression chamber 20. In this embodiment, a lubricating oil discharge passage 56 is provided whose downstream end is connected to an oil reservoir at atmospheric pressure, so that the lubricating oil flowing from the bearing chamber 19 toward the compression chamber 20 is guided to the oil reservoir via the lubricating oil discharge passage 56 (see arrow A7).

According to this embodiment, the following advantageous effects are obtained.
In this embodiment, the mating surface between the third housing 11 and the second housing 9 is located closer to the tip-side bearing 37 than the center of the gear portion 5 in the Y-axis direction. The upstream end of the first lubricating oil supply passage 54a is formed on the end surface 9b (i.e., the mating surface) of the second housing 9. As a result, the separation distance between the upstream end and the downstream end of the first lubricating oil supply passage 54a in the direction along the Y-axis direction is shortened. When the relative positions in the height direction between the upstream end and the downstream end of the first lubricating oil supply passage 54a do not change, the shorter the separation distance in the Y-axis direction, the larger the inclination angle of the first lubricating oil supply passage 54a. Therefore, in this embodiment, the inclination angle of the first lubricating oil supply passage 54a can be increased. As a result, it is possible to easily supply lubricating oil to the bearing chamber 19 through the first lubricating oil supply passage 54a, and therefore the amount of lubricating oil supplied to the bearing chamber 19 can be increased. As a result, the tip-side bearing 37 can be suitably lubricated, and therefore the reliability of the tip-side bearing 37 can be improved.

To make the claw compressor 1 oil-free, lubricating oil is sealed in the bearing chamber 19 and the gear chamber 21, which require lubrication, but seals (oil seal 50 and water seal 52) are installed to prevent the lubricating oil from leaking into the compression chamber 20. However, there is a risk that the lubricating oil will leak from the oil seal 50, and if the lubricating oil flows into the compression chamber 20, it will flow into the process that uses steam, and measures such as system cleaning will be required, which may increase costs.
In this embodiment, a lubricating oil discharge passage 56 that connects to an oil reservoir at atmospheric pressure is provided between the compression chamber 20 and the bearing chamber 19. As a result, even if the lubricating oil in the bearing chamber 19 flows toward the compression chamber 20, the lubricating oil can be discharged to the oil reservoir via the lubricating oil discharge passage 56. This makes it difficult for the lubricating oil to flow into the compression chamber 20. This makes it possible to suppress the occurrence of problems caused by the flow of the lubricating oil into the oil-free compression chamber 20. This makes it possible to improve maintainability and reduce running costs.

[Second embodiment]
Next, a second embodiment of the present disclosure will be described with reference to FIGS.
This embodiment differs from the first embodiment in that a reduced-wall space is formed in the second housing 9. The other structures are similar to those of the first embodiment, so the same structures are denoted by the same reference numerals and detailed descriptions thereof will be omitted.

In the second housing 9 according to this embodiment, a reduced-wall space is formed in a portion between the compression chamber 20 and the bearing chamber 19 (see region P1 indicated by a two-dot chain line in FIG. 2). That is, the entire region of the second housing 9 between the compression chamber 20 and the bearing chamber 19 is not solid, and a space (reduced-wall space) is formed in a partial region (region P2 described below). When viewed from the Y-axis direction, the reduced-wall space is provided on the discharge port 15 side of the vertical center line L of the compression chamber 20.
The thin-wall space may be a closed space or may be an open space with a part opened. The method for forming the thin-wall space is not particularly limited. The thin-wall space may be formed by excavating the second housing 9, or the second housing 9 may be molded with a die so as to form the thin-wall space.

The region P2 that forms the thinning space when viewed from the axial direction (X-axis direction) will be described with reference to Fig. 7. Fig. 7 shows the state in which the male rotor 24 and the female rotor 26 start compressing steam. In other words, it shows the timing when the tip of the claw portion 24a of the male rotor 24 and the tip of the claw portion 26a of the female rotor 26 come into contact with each other.
In detail, an area P2 (see the hatched portion in FIG. 7) forming the thin-wall space is an area that overlaps with a predetermined portion of the compression chamber 20 when viewed from the Y-axis direction.
7, the predetermined portion is a region below the center line L in the Z-axis direction of the compression chamber 20 and outside the circular locus C1 drawn by the innermost peripheral portion of the male rotor 24 and the circular locus C2 drawn by the innermost peripheral portion of the female rotor 26. The predetermined portion is a portion that is particularly heated when steam is compressed in the compression chamber 20.

The reduced-wall space is also provided so as to include a position that overlaps with the compression space (compression pocket) immediately before it communicates with the discharge port 15 when viewed from a specified direction.

The reduced-wall space contains a fluid or a component that has lower thermal conductivity than the second housing 9. The reduced-wall space may be filled with air or may contain a thermal insulating material.

According to this embodiment, the following advantageous effects are obtained.
When compressing steam with the claw compressor 1, if the compressed steam dissipates heat, superheated steam cannot be generated, and the heating capacity available for the process is reduced, resulting in a decrease in compression efficiency. The heat dissipation path of the steam includes a path of heat dissipation from the housing (the first housing 7 or the second housing 9) constituting the compression chamber 20 to the air, and a path of heat transfer from the compression chamber 20 to the bearing chamber 19 via the second housing 9. Heat dissipation to the air can be suppressed by attaching a heat insulating material to the outside of the first housing 7 or the second housing 9. On the other hand, in order to suppress heat transfer to the bearing chamber 19 via the second housing 9, it is necessary to reduce the heat transfer area of the second housing 9. However, if the second housing 9 is thinned in order to reduce the heat transfer path of the second housing 9, the rigidity of the second housing 9 is reduced. For this reason, it is required to thin the second housing 9 only where necessary.

In this embodiment, the second housing 9 has a reduced-wall space formed between the compression chamber 20 and the bearing chamber 19. This makes it more difficult for heat from the compression chamber 20 to be transferred to the bearing chamber 19 via the second housing 9 compared to when there is no reduced-wall space. This reduces the amount of heat dissipated from the steam compressed in the compression chamber 20, improving compression efficiency.

In addition, in this embodiment, the area P2 (see the hatched portion in FIG. 7) that forms the reduced-metal space is an area that overlaps with a specific portion that is particularly prone to temperature rise when viewed from the Y-axis direction. This makes it possible to more effectively inhibit heat transfer. Also, by forming reduced-metal spaces where they are needed and not forming reduced-metal spaces in other locations, it is possible to prevent a reduction in the rigidity of the second housing 9.

The steam in the compression pocket is hottest immediately before it communicates with the discharge port 15. In this embodiment, a reduced-wall space is provided to include a position that overlaps with the compression pocket immediately before it communicates with the discharge port 15 when viewed from a specified direction. This allows the reduced-wall space to be provided in the portion that comes into contact with the hottest fluid. This makes it more preferable that the heat in the compression chamber 20 (specifically, the compression pocket) is less likely to be transmitted to the bearing chamber 19 via the second housing 9. This reduces the amount of heat dissipated by the fluid compressed in the compression chamber 20, improving compression efficiency.

In addition, if a heat insulating material is provided in the reduced-wall space, the heat insulating material inhibits heat transfer, making it more difficult for heat from the compression chamber 20 to be transferred to the bearing chamber 19. This makes it possible to further reduce the amount of heat dissipated by the fluid compressed in the compression chamber 20, thereby further improving the compression efficiency.

The present disclosure is not limited to the above-described embodiments, and various modifications are possible without departing from the spirit and scope of the present disclosure.
For example, in each of the above-described embodiments, the male rotor 24 is the driving side and the female rotor 26 is the driven side, but the male rotor 24 may be the driven side and the female rotor 26 may be the driving side.

The claw compressor according to the embodiment described above can be understood, for example, as follows.
A claw compressor according to a first aspect of the present disclosure includes a first rotor (24) provided with claw portions (24a) projecting in a radial direction, a first rotating shaft (32) extending in a predetermined direction and supporting the first rotor in rotation, a second rotor (26) rotating in a direction opposite to that of the first rotor and having recesses (26b) for receiving the claw portions during a compression process, a second rotating shaft (42) extending in the predetermined direction and supporting the second rotor in rotation, bearing portions (37, 47) for rotatably supporting the first rotating shaft and/or the second rotating shaft, and a bearing chamber housing in which a bearing chamber (19) for accommodating the bearing portions is formed. The bearing chamber housing has a rotor chamber (21) formed therein for accommodating a rotor and filled with lubricating oil, and a lubricating oil supply passage (54a) is formed inside the bearing chamber housing for guiding the lubricating oil filling the rotor chamber to the bearing chamber and slanting downward with respect to the horizontal plane, the upstream end of the lubricating oil supply passage is formed on the end face (9b) of the bearing chamber housing facing the rotor housing, and the mating surface between the rotor housing and the bearing chamber housing is located on the bearing portion side relative to the center of the rotor in the specified direction.

In the above configuration, the mating surface between the rotor housing and the bearing chamber housing is located closer to the bearing portion than the center of the rotor in the specified direction. The upstream end of the lubricant supply passage is formed on the end face (i.e., the mating surface) of the bearing chamber housing. This shortens the distance between the upstream end and downstream end of the lubricant supply passage in the specified direction. If the relative positions in the height direction between the upstream end and downstream end of the lubricant supply passage do not change, the shorter the distance in the specified direction, the larger the inclination angle of the lubricant supply passage. Therefore, in the above configuration, the inclination angle of the lubricant supply passage can be increased. This makes it easier to supply lubricant to the bearing chamber through the lubricant supply passage, and therefore the amount of lubricant supplied to the bearing chamber can be increased. This allows the bearing portion to be suitably lubricated, thereby improving the reliability of the bearing portion.

In addition, the claw compressor according to the second aspect of the present disclosure includes a first rotor (24) provided with a claw portion (24a) protruding in the radial direction, a first rotating shaft (32) extending in a predetermined direction and supporting the first rotor in rotation, a second rotor (26) rotating in the opposite direction to the first rotor and having a recess (26b) for receiving the claw portion during the compression process, a second rotating shaft (42) extending in the predetermined direction and supporting the second rotor in rotation, and a shaft (42) supporting the first rotating shaft and/or the second rotating shaft in a freely rotatable manner. The bearing includes a bearing portion (37, 47) that supports the rotor, a bearing chamber housing (9) that has a bearing chamber (19) formed therein for accommodating the bearing portion, and a rotor housing (11) that accommodates a rotor and has a rotor chamber filled with lubricating oil formed therein. Inside the bearing chamber housing, a lubricating oil supply passage (54a) is formed that guides the lubricating oil that fills the rotor chamber to the bearing chamber and is inclined downward with respect to the horizontal plane, and the inclination angle of the lubricating oil supply passage is 5 degrees or more.

In the above configuration, the inclination angle of the lubricating oil supply passage is set to 5 degrees or more. This allows the inclination angle of the lubricating oil supply passage to be increased. This makes it easier to supply lubricating oil to the bearing chamber through the lubricating oil supply passage, and therefore the amount of lubricating oil supplied to the bearing chamber can be increased. This allows the bearing portion to be suitably lubricated, thereby improving the reliability of the bearing portion.

The claw compressor according to the third aspect of the present disclosure is the first or second aspect described above, and includes a compression chamber (20) that houses the first rotor and the second rotor, and a lubricating oil discharge passage (56) that connects to an oil reservoir at atmospheric pressure is provided between the compression chamber and the bearing chamber.

In the above configuration, a lubricating oil discharge passage is provided between the compression chamber and the bearing chamber, which connects to an oil reservoir at atmospheric pressure. This allows the lubricating oil in the bearing chamber to be discharged to the oil reservoir via the lubricating oil discharge passage, even if the lubricating oil in the bearing chamber flows toward the compression chamber. This makes it difficult for the lubricating oil to flow into the compression chamber. Therefore, for example, when the compression chamber is oil-free, it is possible to suppress the occurrence of problems caused by the flow of lubricating oil into the compression chamber. This improves maintainability, thereby reducing running costs.

The claw compressor according to the fourth aspect of the present disclosure is any one of the first to third aspects described above, and includes a compression chamber (20) that houses the first rotor and the second rotor, and the bearing chamber housing has a reduced-wall space formed between the compression chamber and the bearing chamber, and the reduced-wall space is located closer to the discharge port (15) than the vertical center of the compression chamber when viewed from the specified direction.

In the above configuration, the bearing chamber housing has a reduced-wall space formed between the compression chamber and the bearing chamber. This makes it more difficult for heat from the compression chamber to be transmitted to the bearing chamber via the bearing chamber housing, compared to when there is no reduced-wall space. This reduces the amount of heat dissipated by the fluid compressed in the compression chamber, improving compression efficiency.

The claw compressor according to the fifth aspect of the present disclosure is the fourth aspect described above, in which a heat insulating material is provided in the reduced-wall space.

In the above configuration, a heat insulating material is provided in the reduced-wall space. This inhibits heat transfer, making it more difficult for heat from the compression chamber to be transferred to the bearing chamber via the bearing chamber housing. This makes it possible to further reduce the amount of heat dissipated by the fluid compressed in the compression chamber, thereby further improving compression efficiency.

In addition, the claw compressor according to the sixth aspect of the present disclosure is the fourth aspect, in which the first rotor and the second rotor form a compression space that compresses the fluid, and the reduced-wall space is provided at a position that overlaps with the compression space immediately before it communicates with the discharge port when viewed from the specified direction.

The compression space is hottest immediately before it communicates with the discharge port. In the above configuration, a reduced-wall space is provided at a position that overlaps with the compression space immediately before it communicates with the discharge port when viewed from a specified direction. This allows the reduced-wall space to be provided in the portion that comes into contact with the hottest fluid. This makes it more preferable that heat from the compression chamber (compression space) is less likely to be transmitted to the bearing chamber via the bearing chamber housing. This reduces the amount of heat dissipated by the fluid compressed in the compression chamber, improving compression efficiency.

1: Claw compressor 3: Compression section 5: Gear section (rotating body)
7: First housing 9: Second housing (bearing chamber housing)
9a: inner wall 9b: end surface 11: third housing (rotating body housing)
11a: end surface 12: leg portion 13: intake port 15: discharge port 19: bearing chamber 20: compression chamber 21: gear chamber (rotating body chamber)
22: O-ring 23: O-ring 24: Male rotor 24a: Claw portion 24c: Recess 26: Female rotor 26a: Claw portion 26b: Recess 26c: Recess 31: First bolt 32: First rotating shaft 35: Seal portion 37: Tip side bearing (bearing portion)
38: Rear end bearing 39: First timing gear 41: Second bolt 42: Second rotating shaft 47: Front end bearing (bearing portion)
48: Rear end bearing 49: Second timing gear 50: Oil seal 52: Water seal 54: Lubricant oil supply passage 54a: First lubricant oil supply passage 54b: Second lubricant oil supply passage 54c: Third lubricant oil supply passage 56: Lubricant oil discharge passage F: Oil-free space L: Center line O1: First rotation axis O2: Second rotation axis P1: Region P2: Region R: Oil-rich space S: Space

Claims (6)

a first rotor provided with claws protruding in a radial direction;
a first rotating shaft extending in a predetermined direction and supporting the first rotor;
a second rotor that rotates in a direction opposite to that of the first rotor and has a recess that receives the claw portion during a compression stroke;
a second rotating shaft extending in the predetermined direction and rotatably supporting the second rotor;
a bearing portion that rotatably supports the first rotating shaft and/or the second rotating shaft;
a bearing chamber housing having a bearing chamber formed therein for accommodating the bearing portion;
a rotor housing that houses the rotor and has a rotor chamber formed therein that is filled with lubricating oil;
Equipped with
A lubricating oil supply passage is formed inside the bearing chamber housing to guide the lubricating oil filling the rotor chamber to the bearing chamber and to be inclined downward with respect to a horizontal plane,
an upstream end of the lubricating oil supply passage is formed in an end surface of the bearing chamber housing on the rotor housing side,
A claw compressor, wherein a mating surface between the rotor housing and the bearing chamber housing is located closer to the bearing portion than a center of the rotor in the predetermined direction. a first rotor provided with claws protruding in a radial direction;
a first rotating shaft extending in a predetermined direction and supporting the first rotor;
a second rotor that rotates in a direction opposite to that of the first rotor and has a recess that receives the claw portion during a compression stroke;
a second rotating shaft extending in the predetermined direction and rotatably supporting the second rotor;
a bearing portion that rotatably supports the first rotating shaft and/or the second rotating shaft;
a bearing chamber housing having a bearing chamber formed therein for accommodating the bearing portion;
a rotor housing that accommodates the rotor and has a rotor chamber formed therein that is filled with lubricating oil;
Equipped with
A lubricating oil supply passage is formed inside the bearing chamber housing to guide the lubricating oil filling the rotor chamber to the bearing chamber and to be inclined downward with respect to a horizontal plane,
The inclination angle of the lubricating oil supply passage is 5 degrees or more. a compression chamber that accommodates the first rotor and the second rotor,
3. The claw compressor according to claim 1, wherein a lubricating oil discharge passage is provided between the compression chamber and the bearing chamber, the lubricating oil discharge passage being connected to an oil reservoir at atmospheric pressure. a compression chamber that accommodates the first rotor and the second rotor,
The bearing chamber housing has a reduced-wall space formed between the compression chamber and the bearing chamber,
The claw compressor according to claim 1 or 2, wherein the wall-reduced space is provided closer to the discharge port than the center of the compression chamber in the vertical direction when viewed from the predetermined direction. The claw compressor according to claim 4, wherein the thinned space is provided with a heat insulating material. the first rotor and the second rotor form a compression space for compressing a fluid,
The claw compressor according to claim 4 , wherein the wall-reduced space is provided at a position overlapping with the compression space immediately before communicating with the discharge port when viewed from the predetermined direction.