Technical Field
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The present disclosure relates to a claw compressor.
Background Art
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The claw compressor includes a pair of rotors having hook-shaped claw parts inside a housing that forms a compression chamber. The pair of rotors are connected to each other via a timing gear. Each rotor rotates at the same speed in opposite directions without contact while maintaining a predetermined clearance, and the two rotors form a compression pocket and discharge a fluid compressed in the compression pocket. Such a claw-type compressor is mainly used as a vacuum pump or a blower (for example, see PTL 1).
Citation List
Patent Literature
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[PTL 1]
Japanese Patent No. 6845596 Summary of Invention
Technical Problem
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In a case where a vapor-generating heat pump is used as an alternative to a boiler and the generated vapor is compressed, an operation at a high load is required as compared with the vacuum pump or the blower. In a case of performing a high-load operation, such as compressing the vapor, a power transmission part (for example, a gear or the like) that transmits power from a driving shaft to a driven shaft, and a bearing part that supports each shaft, require lubrication with lubricating oil. In a case where the claw compressor is used for a vapor compression application in this manner, the following problems occur as compared with a vacuum pump application or a blower application.
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In the claw compressor, in a case where oil supply to the bearing part is performed by oil splashing caused by the power transmission part, it is necessary to provide an oil supply path that guides splashed lubricating oil to the bearing part. Meanwhile, in general, power for causing the lubricating oil to flow to the bearing part is only gravity. In such a situation, there is a possibility that reliability of the bearing part is reduced because the lubricating oil cannot be suitably guided to the bearing part.
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The present disclosure has been made in consideration of such circumstances, and an object of the present disclosure is to provide a claw compressor that can improve reliability of a bearing part.
Solution to Problem
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In order to solve the above-described problems, the claw compressor of the present disclosure adopts the following means.
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A claw compressor according to an aspect of the present disclosure includes a first rotor provided with a claw part protruding in a radial direction, a first rotating shaft that extends in a predetermined direction and rotatably supports the first rotor, a second rotor that rotates in a direction opposite to the first rotor and has a recessed part that receives the claw part during a compression step, a second rotating shaft that extends in the predetermined direction and rotatably supports the second rotor, a bearing part that rotatably supports the first rotating shaft and/or the second rotating shaft, a bearing chamber housing in which a bearing chamber that accommodates the bearing part is formed, and a rotating body housing in which a rotating body chamber that accommodates a rotating body and that is filled with lubricating oil is formed, in which a lubricating oil supply flow path that guides the lubricating oil filling the rotating body chamber to the bearing chamber and that is inclined downward with respect to a horizontal plane is formed inside the bearing chamber housing, an upstream end of the lubricating oil supply flow path is formed on an end surface of the bearing chamber housing on a side of the rotating body housing, and a mating surface between the rotating body housing and the bearing chamber housing is located closer to a side of the bearing part than a center of the rotating body in the predetermined direction.
Advantageous Effects of Invention
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According to the present disclosure, it is possible to improve the reliability of the bearing part.
Brief Description of Drawings
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- 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 taken along cutting line II-II of the claw compressor of FIG. 1.
- FIG. 3 is a cross-sectional view taken along cutting line III-III of FIG. 2.
- FIG. 4 is a cross-sectional view taken along cutting line IV-IV of the claw compressor of FIG. 2.
- FIG. 5 is an enlarged view of a V portion of the claw compressor of FIG. 4.
- FIG. 6 is an enlarged view of a VI portion of the claw compressor of FIG. 4.
- FIG. 7 shows a claw compressor according to a second embodiment of the present disclosure, and is a cross-sectional view corresponding to FIG. 3.
- FIG. 8 shows the claw compressor according to the second embodiment of the present disclosure, and is a cross-sectional view corresponding to FIG. 4.
Description of Embodiments
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Hereinafter, an embodiment according to the present disclosure will be described with reference to the drawings.
[First Embodiment]
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Hereinafter, a first embodiment of the present disclosure will be described. In the following description, a Z-axis direction indicates a vertical up-down direction. In addition, a Y-axis direction is a direction which is orthogonal to the Z-axis direction and in which a first rotating shaft 32 and a second rotating shaft 42 of a claw compressor 1 extend. In addition, an X-axis direction indicates a direction orthogonal to the Z-axis direction and the Y-axis direction.
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The claw compressor 1 according to the present embodiment is used for an application of compressing vapor. As shown in FIG. 1, the claw compressor 1 includes a compression part 3 in which a compression chamber 20 is formed, and a gear part (rotating body) 5 in which a timing gear is accommodated.
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The compression part 3 is formed by a first housing 7 and a second housing (bearing chamber housing) 9, and the gear part 5 is formed by the second housing 9 and a third housing (rotating body housing) 11. The claw compressor 1 is erected on an installation surface by, for example, four leg parts 12.
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The compression part 3 includes a suction port 13 that suctions vapor (fluid), and a discharge port 15 that discharges the vapor after compression. The vapor is, for example, water vapor. The vapor to be suctioned may be negative pressure or positive pressure.
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As shown in FIG. 2, the compression part 3 is configured such that the first housing 7 closes a recess formed at a front end (one end) of the second housing 9 and the compression chamber 20 is formed inside. The first housing 7 is airtightly attached to the second housing 9 via an O-ring 22.
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A pair of rotors, that is, a male rotor (first rotor) 24 and a female rotor (second rotor) 26, are provided in the compression chamber 20.
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As shown in FIG. 3, the male rotor 24 has a pair of hook-shaped claw parts 24a. The claw parts 24a are symmetrically provided about a first rotational axis O1. The male rotor 24 rotates counterclockwise (in a direction of an arrow A1) in FIG. 3.
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The female rotor 26 has a pair of hook-shaped claw parts 26a. The claw parts 26a are symmetrically provided about a second rotational axis O2. The female rotor 26 rotates clockwise (in a direction of an arrow A2) in FIG. 3.
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The claw parts 24a of the male rotor 24 and the claw parts 26a of the female rotor 26 mesh with each other in a non-contact manner. A recessed part 26b that receives the claw part 24a of the male rotor 24 during the compression step is formed in the female rotor 26. The compressed vapor is discharged from the discharge port 15 having a substantially triangular shape in FIG. 3.
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As shown in FIG. 3, the compression chamber 20 has a shape defined by an inner wall 9a of the second housing 9, and has a cross-sectional shape in which two circles, that is, a circle centered on the first rotational axis O1 and a circle centered on the second rotational axis O2, partially overlap each other. Tips of the claw parts 24a and 26a of the respective rotors 24 and 26 move along the inner wall 9a of the second housing 9 with a predetermined clearance.
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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 to the first rotating shaft 32 in a state where an axis of the first bolt 31 is aligned with the first rotational axis O1. A fastening structure (first bolt fastening part) is configured in a state where a central part of the male rotor 24 is interposed between the tip surface of the first rotating shaft 32 and a head of the first bolt 31. The head of the first bolt 31 is accommodated in a cylindrical recess 24c formed at the center of the male rotor 24.
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The female rotor 26 is fastened to the second rotating shaft 42 by a second bolt 41. Specifically, the second bolt 41 is screwed to the second rotating shaft 42 in a state where an axis of the second bolt 41 is aligned with the second rotational axis O2. The second rotating shaft 42 is provided in parallel to the first rotating shaft 32. That is, the first rotational axis O1 and the second rotational axis O2 are parallel to each other.
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A fastening structure (second bolt fastening part) is configured in a state where a central part of the female rotor 26 is interposed between the tip surface of the second rotating shaft 42 and a head of the second bolt 41. The head of the second bolt 41 is accommodated in a cylindrical recess 26c formed at the center of the female rotor 26. Therefore, before the female rotor 26 is fixed by the second bolt 41, the relative rotation between the female rotor 26 and the second rotating shaft 42 is allowed.
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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 part (not shown). As the drive part, for example, an electric motor is used. The first rotating shaft 32 rotates about the first rotational axis O1, and thus the male rotor 24 rotates in the compression chamber 20. The first rotating shaft 32 is rotatably supported at two locations of a tip-end-side bearing (bearing part) 37 and a rear-end-side bearing 38. The tip-end-side bearing 37 is provided in the second housing 9 and, for example, a double-row ball bearing is used. However, the tip-end-side bearing 37 is not limited to a double row or a ball bearing. The rear-end-side bearing 38 is located closer to a rear end side than the tip-end-side bearing 37 and is provided in the third housing 11. The rear-end-side bearing 38 is a single-row ball bearing, but is not limited to a single row or a ball bearing.
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A first timing gear 39 is fixed to the first rotating shaft 32 between a tip-end-side bearing (bearing part) 37 and the rear-end-side bearing 38. The first timing gear 39 is, for example, a spur gear and rotates about the first rotational 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 part 5.
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The first timing gear 39 is provided in the gear part 5 and is accommodated in a gear chamber (rotating body chamber) 21 formed between a rear end (other end) of the second housing 9 and a front end of the third housing 11. The second housing 9 and the third housing 11 are attached to each other in a liquid-tight manner via an O-ring 23 to seal the lubricating oil in the gear chamber 21.
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The inside of the gear chamber 21 (that is, the inside of the third housing 11) is in an oil atmosphere and lubricates the gear part 5.
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As described above, the first bolt fastening part to which the first bolt 31 is fastened is provided at the tip of the first rotating shaft 32. In addition, the rear end of the first rotating shaft 32 protrudes from the third housing 11. That is, 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 part (an electric motor or the like).
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The second rotating shaft 42 that supports the female rotor 26 has a tip located in the compression chamber 20, and a rear end terminated in the third housing 11. A space S in which a rear-end-side bearing 48 is accommodated is formed in the third housing 11. A seal part 35 is provided between the space S and the gear chamber 21.
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The second rotating shaft 42 rotates about the second rotational axis O2, and thus the female rotor 26 rotates in the compression chamber 20. The second rotating shaft 42 is rotatably supported at two locations of the tip-end-side bearing 47 and the rear-end-side bearing (bearing) 48. The tip-end-side bearing 47 is provided in the second housing 9 and, for example, a double-row ball bearing is used. However, the tip-end-side bearing 47 is not limited to a double row or a ball bearing. The rear-end-side bearing 48 is located closer to a rear end side than the tip-end-side bearing 47 and is provided on an outer side of the third housing 11. Specifically, the rear-end-side bearing 48 is provided in the space S adjacent to the gear chamber 21. The rear-end-side bearing 48 is a single-row ball bearing, but is not limited to a single row or a ball bearing.
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A second timing gear 49 is fixed to the second rotating shaft 42 between the tip-end-side bearing 47 and the rear-end-side bearing 48. The second timing gear 49 is, for example, a spur gear and rotates about the second rotational axis O2 together with the second rotating shaft 42.
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The second timing gear 49 is provided in the gear part 5 and is accommodated 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. Therefore, the first rotating shaft 32 is a driving shaft, and the second rotating shaft 42 is a driven shaft.
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As described above, the second bolt fastening part to which the second bolt 41 is fastened is provided at the tip of the second rotating shaft 42.
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As shown in FIGS. 2 and 4, an end surface 9b of the second housing 9 and an end surface 11a of the third housing 11 are in surface contact with each other. The mating surface between the second housing 9 and the third housing 11 is located closer to a side of the tip-end-side bearing 37 than the center of the gear part 5 in the Y-axis direction (predetermined direction). In the present embodiment, the mating surface between the second housing 9 and the third housing 11 is provided to match an end part of the tip-end-side bearing 37 on the side of the gear part 5.
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A bearing chamber 19 that accommodates the tip-end-side bearings 37 and 47 is formed inside the second housing 9.
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In addition, as shown in FIG. 6, a lubricating oil supply flow path 54 that guides the lubricating oil in the gear chamber 21 to the bearing chamber 19 is formed inside the second housing 9. The lubricating oil supply flow path 54 includes a first lubricating oil supply flow path 54a that has an upstream end connected to an opening formed in the end surface 9b of the second housing 9 and that is inclined downward with respect to a horizontal plane, a second lubricating oil supply flow path 54b that extends downward from a downstream end of the first lubricating oil supply flow path 54a, and a third lubricating oil supply flow path 54c that extends in a direction of the bearing chamber 19 to be inclined downward from a downstream end of the second lubricating oil supply flow path 54b.
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An inclination angle of the first lubricating oil supply flow path 54a with respect to the horizontal plane is, for example, 5 degrees or more. In addition, a downstream end of the third lubricating oil supply flow path 54c is connected to the bearing chamber 19.
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In addition, as shown in FIG. 5, the first rotating shaft 32 penetrates the second housing 9. An oil seal 50 and a water seal 52 that seal a space between an outer peripheral surface of the first rotating shaft 32 and the second housing 9 are provided between the bearing chamber 19 and the compression chamber 20. The oil seal 50 hinders the flow of the lubricating oil from the bearing chamber 19 toward the compression chamber 20. In addition, the water seal 52 hinders the flow of the vapor or the condensed water from the compression chamber 20 toward the bearing chamber 19.
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The oil seal 50 and the water seal 52 seal an oil-rich space R, such as the bearing chamber 19, and an oil-free space F, such as the compression chamber 20.
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An upstream end of a lubricating oil discharge flow path 56 is connected to a space between the oil seal 50 and the water seal 52. A downstream end of the lubricating oil discharge flow path 56 is connected to an oil reservoir (not shown) provided outside the second housing 9. An inside of the oil reservoir is at atmospheric pressure.
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The claw compressor 1 having the above-described configuration operates as follows.
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The first rotating shaft 32 is rotationally driven by the drive part (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 driving force is transmitted from the first timing gear 39 that rotates together with the first rotating shaft 32, and the female rotor 26 rotates in the compression chamber 20.
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The male rotor 24 and the female rotor 26 rotate in the compression chamber 20, and the vapor is suctioned from the suction port 13. The male rotor 24 rotates counterclockwise (in the direction of the arrow A1) in FIG. 3, takes in vapor into the compression pocket formed by the claw parts 24a, and moves downward along the outer periphery of the compression chamber 20. The female rotor 26 rotates clockwise (in the direction of the arrow A2) in FIG. 3, takes in vapor into the compression pocket formed by the claw parts 26a, and moves 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 merge at a center of a lower portion of the compression chamber 20, and the claw part 24a of the male rotor 24 enters the recessed part 26b of the female rotor 26 in the combined compression pocket (compression space) to compress the vapor. The compressed vapor is discharged from the discharge port 15 to the outside.
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In addition, the lubricating oil is sealed in the gear chamber 21. The lubricating oil is splashed by the rotation of the gear part 5 in the gear chamber 21. The splashed lubricating oil adheres to a ceiling part of the gear chamber 21, and a part of the lubricating oil flows into the lubricating oil supply flow path 54 from the opening formed in the end surface 9b of the second housing 9. The lubricating oil flowing into the lubricating oil supply flow path 54 flows through the first lubricating oil supply flow path 54a inclined downward (see an arrow A3 in FIG. 6). Thereafter, the lubricating oil is guided into the bearing chamber 19 through the second lubricating oil supply flow path 54b and the third lubricating oil supply flow path 54c (see arrows A4 and A5 in FIG. 6). The lubricating oil guided into the bearing chamber 19 lubricates the tip-end-side bearings 37 and 47.
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As shown in FIG. 5, a part of the lubricating oil guided into the bearing chamber 19 flows through a clearance formed between the outer peripheral surface of the first rotating shaft 32 and the second housing 9 and flows toward the compression chamber 20 (see an arrow A6). In particular, in a case where the compression chamber 20 is at negative pressure, the lubricating oil easily flows in the direction of the compression chamber 20. In the present embodiment, since the lubricating oil discharge flow path 56 of which the downstream end is connected to the oil reservoir at atmospheric pressure is provided, the lubricating oil flowing from the bearing chamber 19 toward the direction of the compression chamber 20 is guided to the oil reservoir through the lubricating oil discharge flow path 56 (see an arrow A7).
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According to the present embodiment, the following operations and effects are obtained.
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In the present embodiment, the mating surface between the third housing 11 and the second housing 9 is located closer to the side of the tip-end-side bearing 37 than the center of the gear part 5 in the Y-axis direction. In addition, the upstream end of the first lubricating oil supply flow path 54a is formed on the end surface 9b (that is, the mating surface) of the second housing 9. As a result, in a direction along the Y-axis direction, a separation distance between the upstream end and the downstream end of the first lubricating oil supply flow path 54a is shortened. In a case where the relative positions of the upstream end and the downstream end of the first lubricating oil supply flow path 54a in the height direction do not change, the inclination angle of the first lubricating oil supply flow path 54a increases as the separation distance in the Y-axis direction is shorter. Therefore, in the present embodiment, the inclination angle of the first lubricating oil supply flow path 54a can be increased. Therefore, the lubricating oil can be easily supplied to the bearing chamber 19 through the first lubricating oil supply flow path 54a, and thus the amount of the lubricating oil supplied to the bearing chamber 19 can be increased. Therefore, the tip-end-side bearing 37 can be suitably lubricated, and thus the reliability of the tip-end-side bearing 37 can be improved.
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In order to make the claw compressor 1 oil-free, the lubricating oil is sealed in the bearing chamber 19 or the gear chamber 21 in which the lubrication is necessary, and the seal (the oil seal 50 or the water seal 52) is installed so that the lubricating oil does not flow out to a side of the compression chamber 20. However, there is a risk that the lubricating oil leaks from the oil seal 50, and in a case where the lubricating oil flows into the compression chamber 20, the process of using the vapor proceeds, and the response such as the system cleaning is required, which may increase the cost.
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In the present embodiment, the lubricating oil discharge flow path 56 connected to the oil reservoir at atmospheric pressure is provided between the compression chamber 20 and the bearing chamber 19. As a result, even in a case where the lubricating oil in the bearing chamber 19 flows to the side of the compression chamber 20, the lubricating oil can be discharged to the oil reservoir through the lubricating oil discharge flow path 56. Therefore, it is possible to prevent the lubricating oil from flowing into the compression chamber 20. Therefore, it is possible to suppress the occurrence of a problem caused by the inflow of the lubricating oil into the oil-free compression chamber 20. Therefore, the maintainability can be improved, and thus the running cost can be reduced.
[Second Embodiment]
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Next, a second embodiment of the present disclosure will be described with reference to FIGS. 7 and 8.
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The present embodiment is different from the first embodiment in that a reduced-thickness space is formed in the second housing 9. The embodiment is similar to the first embodiment as to the other structures, and thus the same structures will be denoted by the same reference numerals with detailed description thereof omitted.
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In the second housing 9 according to the present embodiment, the reduced-thickness space is formed in a portion between the compression chamber 20 and the bearing chamber 19 (see a region P1 indicated by a dashed double-dotted line in FIG. 2). That is, in the second housing 9, in the portion between the compression chamber 20 and the bearing chamber 19, the entire region is not solid, and a space (reduced-thickness space) is formed in a partial region (region P2 described below). The reduced-thickness space is provided closer to a side of the discharge port 15 than a center line L in the up-down direction of the compression chamber 20 when viewed from the Y-axis direction.
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The reduced-thickness space may be a closed space or an open space in which a part is open. A method of forming the reduced-thickness space is not particularly limited. The reduced-thickness space may be formed by excavating the second housing 9, or the second housing 9 may be molded by a mold such that the reduced-thickness space is formed.
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The region P2 that forms the reduced-thickness space when viewed from the axial direction (X-axis direction) will be described with reference to FIG. 7. FIG. 7 shows a state in which the male rotor 24 and the female rotor 26 start compressing the vapor. That is, a timing at which the tip of the claw part 24a of the male rotor 24 and the tip of the claw part 26a of the female rotor 26 come into contact with each other is shown.
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Specifically, the region P2 (see a hatched portion in FIG. 7) that forms the reduced-thickness space is a region that overlaps a predetermined portion of the compression chamber 20 when viewed from the Y-axis direction.
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The predetermined portion is a region that is below the center line L of the compression chamber 20 in the Z-axis direction and that is on an outer side of a circular trajectory C1 described by the innermost peripheral portion of the male rotor 24 and of a circular trajectory C2 described by the innermost peripheral portion of the female rotor 26, in addition to the compression space (compression pocket) at the timing shown in FIG. 7. The predetermined portion is a portion that is particularly heated in a case of compressing the vapor in the compression chamber 20.
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In addition, the reduced-thickness space is provided to include a position that overlaps the compression space (compression pocket) immediately before communicating with the discharge port 15 when viewed from the predetermined direction.
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A fluid or a member having a lower heat transfer property than the second housing 9 is accommodated in the reduced-thickness space. The reduced-thickness space may be filled with air or may accommodate a heat insulating material.
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According to the present embodiment, the following operations and effects are obtained.
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In a case where the vapor is compressed by the claw compressor 1, when the compressed vapor is dissipated, the superheated vapor cannot be generated, and the heating capacity that can be used in the process is reduced, so that the compression efficiency is reduced. The heat dissipation path of the vapor includes a path for dissipating heat from a housing (the first housing 7 or the second housing 9) constituting the compression chamber 20 to the air, and a path for transferring heat from the compression chamber 20 through the second housing 9 to the bearing chamber 19. The heat dissipation to the air can be suppressed by attaching the heat insulating material to the outer side of the first housing 7 or the second housing 9. Meanwhile, in order to suppress the heat transfer to the bearing chamber 19 through the second housing 9, it is necessary to reduce the heat transfer area of the second housing 9. Meanwhile, in a case where the thickness-reduction of the second housing 9 is performed in order to reduce the heat transfer path of the second housing 9, the rigidity of the second housing 9 is reduced. Therefore, it is required to perform the thickness-reduction only at necessary locations of the second housing 9.
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In the present embodiment, the second housing 9 is provided with the reduced-thickness space between the compression chamber 20 and the bearing chamber 19. As a result, the heat of the compression chamber 20 can be prevented from being transferred to the bearing chamber 19 through the second housing 9 as compared with a case where the reduced-thickness space is not provided. Therefore, the amount of heat dissipation of the vapor compressed in the compression chamber 20 can be reduced, and thus the compression efficiency can be improved.
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In addition, in the present embodiment, the region P2 (see the hatched portion in FIG. 7) that forms the reduced-thickness space is a region that overlaps the predetermined portion that is particularly heated, when viewed from the Y-axis direction. Accordingly, the heat transfer can be more preferably hindered. In addition, by forming the reduced-thickness space at necessary locations and not forming the reduced-thickness space at other locations, the reduction in the rigidity of the second housing 9 can be suppressed.
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In addition, the vapor in the compression pocket is at the highest temperature immediately before communicating with the discharge port 15. In the present embodiment, the reduced-thickness space is provided to include a position that overlaps the compression pocket immediately before communicating with the discharge port 15 when viewed from the predetermined direction. As a result, the reduced-thickness space can be provided at a portion in contact with the fluid that is at the highest temperature. Therefore, the heat of the compression chamber 20 (specifically, the compression pocket) can be more suitably prevented from being transferred to the bearing chamber 19 through the second housing 9. Therefore, the amount of heat dissipation of the fluid compressed in the compression chamber 20 can be reduced, and thus the compression efficiency can be improved.
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In addition, in a case where the heat insulating material is provided in the reduced-thickness space, the heat insulating material hinders the heat transfer, and thus the heat of the compression chamber 20 can be more suitably prevented from being transferred to the bearing chamber 19. Therefore, the amount of heat dissipation of the fluid compressed in the compression chamber 20 can be further reduced, and thus the compression efficiency can be further improved.
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The present disclosure is not limited to each of the embodiments described above, and can be appropriately modified within a scope which does not depart from the gist of the present disclosure.
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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.
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The claw compressor described in the embodiments described above is understood as follows, for example.
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A claw compressor according to a first aspect of the present disclosure includes a first rotor (24) provided with a claw part (24a) protruding in a radial direction, a first rotating shaft (32) that extends in a predetermined direction and rotatably supports the first rotor, a second rotor (26) that rotates in a direction opposite to the first rotor and has a recessed part (26b) that receives the claw part during a compression step, a second rotating shaft (42) that extends in the predetermined direction and rotatably supports the second rotor, a bearing part (37, 47) that rotatably supports the first rotating shaft and/or the second rotating shaft, a bearing chamber housing (9) in which a bearing chamber (19) that accommodates the bearing part is formed, and a rotating body housing (11) in which a rotating body chamber (21) that accommodates a rotating body and that is filled with lubricating oil is formed, in which a lubricating oil supply flow path (54a) that guides the lubricating oil filling the rotating body chamber to the bearing chamber and that is inclined downward with respect to a horizontal plane is formed inside the bearing chamber housing, an upstream end of the lubricating oil supply flow path is formed on an end surface (9b) of the bearing chamber housing on a side of the rotating body housing, and a mating surface between the rotating body housing and the bearing chamber housing is located closer to a side of the bearing part than a center of the rotating body in the predetermined direction.
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In the above-described configuration, the mating surface between the rotating body housing and the bearing chamber housing is located closer to the side of the bearing part than the center of the rotating body in the predetermined direction. In addition, the upstream end of the lubricating oil supply flow path is formed on the end surface (that is, the mating surface) of the bearing chamber housing. As a result, in a direction along the predetermined direction, a separation distance between the upstream end and the downstream end of the lubricating oil supply flow path is shortened. In a case where the relative positions of the upstream end and the downstream end of the lubricating oil supply flow path in the height direction do not change, the inclination angle of the lubricating oil supply flow path increases as the separation distance in the predetermined direction is shorter. Therefore, in the above configuration, the inclination angle of the lubricating oil supply flow path can be increased. Therefore, the lubricating oil can be easily supplied to the bearing chamber through the lubricating oil supply flow path, and thus the amount of the lubricating oil supplied to the bearing chamber can be increased. Therefore, the bearing part can be suitably lubricated, and thus the reliability of the bearing part can be improved.
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In addition, a claw compressor according to a second aspect of the present disclosure includes a first rotor (24) provided with a claw part (24a) protruding in a radial direction, a first rotating shaft (32) that extends in a predetermined direction and rotatably supports the first rotor, a second rotor (26) that rotates in a direction opposite to the first rotor and has a recessed part (26b) that receives the claw part during a compression step, a second rotating shaft (42) that extends in the predetermined direction and rotatably supports the second rotor, a bearing part (37, 47) that rotatably supports the first rotating shaft and/or the second rotating shaft, a bearing chamber housing (9) in which a bearing chamber (19) that accommodates the bearing part is formed, and a rotating body housing (11) in which a rotating body chamber that accommodates a rotating body and that is filled with lubricating oil is formed, in which a lubricating oil supply flow path (54a) that guides the lubricating oil filling the rotating body chamber to the bearing chamber and that is inclined downward with respect to a horizontal plane is formed inside the bearing chamber housing, and an inclination angle of the lubricating oil supply flow path is 5 degrees or more.
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In the above-described configuration, the inclination angle of the lubricating oil supply flow path is 5 degrees or more. Therefore, the inclination angle of the lubricating oil supply flow path can be increased. Therefore, the lubricating oil can be easily supplied to the bearing chamber through the lubricating oil supply flow path, and thus the amount of the lubricating oil supplied to the bearing chamber can be increased. Therefore, the bearing part can be suitably lubricated, and thus the reliability of the bearing part can be improved.
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In addition, a claw compressor according to a third aspect of the present disclosure includes, in the first or second aspect, a compression chamber (20) that accommodates the first rotor and the second rotor, in which a lubricating oil discharge flow path (56) connected to an oil reservoir at atmospheric pressure is provided between the compression chamber and the bearing chamber.
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In the above configuration, the lubricating oil discharge flow path connected to the oil reservoir at atmospheric pressure is provided between the compression chamber and the bearing chamber. As a result, even in a case where the lubricating oil in the bearing chamber flows to the side of the compression chamber, the lubricating oil can be discharged to the oil reservoir through the lubricating oil discharge flow path. Therefore, it is possible to prevent the lubricating oil from flowing into the compression chamber. Therefore, for example, in a case where the compression chamber is oil-free, it is possible to suppress the occurrence of a problem caused by the inflow of the lubricating oil into the compression chamber. Therefore, the maintainability can be improved, and thus the running cost can be reduced.
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In addition, a claw compressor according to a fourth aspect of the present disclosure includes, in any one of the first to third aspects, a compression chamber (20) that accommodates the first rotor and the second rotor, in which the bearing chamber housing is provided with a reduced-thickness space between the compression chamber and the bearing chamber, and the reduced-thickness space is provided closer to a side of a discharge port (15) than a center of the compression chamber in an up-down direction when viewed from the predetermined direction.
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In the above configuration, the bearing chamber housing is provided with the reduced-thickness space between the compression chamber and the bearing chamber. As a result, the heat of the compression chamber can be prevented from being transferred to the bearing chamber through the bearing chamber housing as compared with a case where the reduced-thickness space is not provided. Therefore, the amount of heat dissipation of the fluid compressed in the compression chamber can be reduced, and thus the compression efficiency can be improved.
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In addition, in a claw compressor according to a fifth aspect of the present disclosure, in the fourth aspect, a heat insulating material is provided in the reduced-thickness space.
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In the above-described configuration, the heat insulating material is provided in the reduced-thickness space. As a result, since the heat insulating material hinders the heat transfer, the heat of the compression chamber can be more suitably prevented from being transferred to the bearing chamber through the bearing chamber housing. Therefore, the amount of heat dissipation of the fluid compressed in the compression chamber can be further reduced, and thus the compression efficiency can be further improved.
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In addition, in a claw compressor according to a sixth aspect of the present disclosure, in the fourth aspect, the first rotor and the second rotor form a compression space in which a fluid is compressed, and the reduced-thickness space is provided at a position that overlaps the compression space immediately before communicating with the discharge port when viewed from the predetermined direction.
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The compression space is at the highest temperature immediately before communicating with the discharge port. In the above configuration, the reduced-thickness space is provided at a position that overlaps the compression space immediately before communicating with the discharge port when viewed from the predetermined direction. As a result, the reduced-thickness space can be provided at a portion in contact with the fluid that is at the highest temperature. Therefore, the heat of the compression chamber (compression space) can be more suitably prevented from being transferred to the bearing chamber through the bearing chamber housing. Therefore, the amount of heat dissipation of the fluid compressed in the compression chamber can be reduced, and thus the compression efficiency can be improved.
Reference Signs List
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- 1: claw compressor
- 3: compression part
- 5: gear part (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 part
- 13: suction 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 part
- 24c: recess
- 26: female rotor
- 26a: claw part
- 26b: recessed part
- 26c: recess
- 31: first bolt
- 32: first rotating shaft
- 35: seal part
- 37: tip-end-side bearing (bearing part)
- 38: rear-end-side bearing
- 39: first timing gear
- 41: second bolt
- 42: second rotating shaft
- 47: tip-end-side bearing (bearing part)
- 48: rear-end-side bearing
- 49: second timing gear
- 50: oil seal
- 52: water seal
- 54: lubricating oil supply flow path
- 54a: first lubricating oil supply flow path
- 54b: second lubricating oil supply flow path
- 54c: third lubricating oil supply flow path
- 56: lubricating oil discharge flow path
- F: oil-free space
- L: center line
- O1: first rotational axis
- O2: second rotational axis
- P1: region
- P2: region
- R: oil-rich space
- S: space