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. 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 generated vapor is compressed, a differential pressure between a suction pressure and a discharge pressure is large and leakage is large as compared with the vacuum pump or the blower. Therefore, in order to increase efficiency, it is necessary to reduce a clearance during a compression step. Meanwhile, in the claw-type compressor used as the vacuum pump or the blower, since the differential pressure between the suction pressure and the discharge pressure is small, there is no problem of reducing the clearance during the compression step, and sufficient countermeasures have not been taken.
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The present disclosure is made in view of the above-described circumstances, and an object of the present disclosure is to provide a claw compressor which can achieve high compression efficiency even in a vapor compression application. Solution to Problem
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A claw compressor according to an aspect of the present disclosure includes a first rotor that has a plurality of first claw parts 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 parts protruding in the radial direction, a second rotating shaft that rotatably supports the second rotor, a compression part that forms a compression chamber accommodating the first rotor and the second rotor, and a seal part that increases air-tightness of clearances between the first rotor and the compression part and between the second rotor and the compression part, in which the first rotor has a plurality of first recessed parts that receive the plurality of second claw parts, the second rotor has a plurality of second recessed parts that receive the plurality of first claw parts, the compression part forms the compression chamber between a first accommodation surface and a second accommodation surface that are orthogonal to the first rotating shaft and the second rotating shaft, and the seal part increases air-tightness of at least one of a first clearance between the first accommodation surface and an end surface of the first rotor that faces the first accommodation surface, a second clearance between the first accommodation surface and an end surface of the second rotor that faces the first accommodation surface, a third clearance between the second accommodation surface and an end surface of the first rotor that faces the second accommodation surface, and a fourth clearance between the second accommodation surface and an end surface of the second rotor that faces the second accommodation surface.
Advantageous Effects of Invention
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According to the present disclosure, it is possible to provide the claw compressor that can achieve high compression efficiency even in the vapor compression application.
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 partially enlarged view showing a vicinity of a male rotor of the claw compressor shown in FIG. 2.
- FIG. 5 is a partially enlarged view showing a vicinity of a female rotor of the claw compressor shown in FIG. 2.
- FIG. 6 is a view of the male rotor and the female rotor which are shown in FIG. 2 as viewed from a side of a gear part.
- FIG. 7 is a view of the male rotor and the female rotor which are shown in FIG. 2 as viewed from a side of a discharge port.
- FIG. 8 is a view showing a first modification example of an injection port of the first embodiment of the present disclosure.
- FIG. 9 is a view showing a second modification example of the injection port of the first embodiment of the present disclosure.
- FIG. 10 is a view showing a third modification example of the injection port of the first embodiment of the present disclosure.
- FIG. 11 is a view showing a fourth modification example of the injection port of the first embodiment of the present disclosure.
- FIG. 12 is a cross-sectional view showing a vicinity of a male rotor of a claw compressor according to a second embodiment of the present disclosure.
- FIG. 13 is a cross-sectional view showing a vicinity of a female rotor of the claw compressor according to the second embodiment of the present disclosure.
- FIG. 14 is a view of the male rotor and the female rotor which are shown in FIGS. 12 and 13 as viewed from the side of the gear part.
- FIG. 15 is a view of the male rotor and the female rotor which are shown in FIGS. 12 and 13 as viewed from the side of the discharge port.
- FIG. 16 is a cross-sectional view showing a vicinity of a male rotor of a claw compressor according to a modification example of the second embodiment of the present disclosure.
- FIG. 17 is a cross-sectional view showing a vicinity of a female rotor of the claw compressor according to the modification example of the second embodiment of the present disclosure.
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. As shown in FIG. 1, a claw compressor 1 includes a compression part 3 in which a compression chamber is formed, and a gear part 5 in which a timing gear is accommodated. The compression part 3 is formed by a first housing 7 and a second housing 9, and the gear part 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 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 a 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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The first housing 7 has an accommodation surface (second accommodation surface) 7a that is orthogonal to a first rotating shaft 32 and a second rotating shaft 42 and that is disposed on a side of the discharge port 15. The second housing 9 has an accommodation surface (first accommodation surface) 9b that is orthogonal to the first rotating shaft 32 and the second rotating shaft 42 and that is disposed on a side of the gear part 5. The compression part 3 forms the compression chamber 20 between the accommodation surface 9b and the accommodation surface 7a.
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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 (first claw parts) 24a. The claw parts 24a protrude in a radial direction orthogonal to a first rotational axis O1 and are symmetrically provided about the 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 (second claw parts) 26a. The claw parts 26a protrude in a radial direction orthogonal to a second rotational axis O2 and are symmetrically provided about the 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 (first recessed part) 24b that receives the claw part 26a of the female rotor 26 during the compression step is formed in the male rotor 24. A recessed part (second 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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A key 35 (rotation prevention part) is provided between the male rotor 24 and a tip part of the first rotating shaft 32. The key 35 is fitted to a key groove formed in the male rotor 24 and the first rotating shaft 32 and prevents the male rotor 24 and the first rotating shaft 32 from rotating relative to each other.
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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. 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, 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 37 and a rear-end-side bearing 38.
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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 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.
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The first timing gear 39 is provided in the gear part 5 and is accommodated in a gear 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 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.
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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 a rear-end-side 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 in the third housing 11. 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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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.
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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 to compress the vapor. The compressed vapor is discharged from the discharge port 15 to the outside.
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The phase adjustment of each of the rotors 24 and 26 during the assembly of the claw compressor is performed as follows.
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First, the key 35 is attached between the male rotor 24 and the first rotating shaft 32 in a state where the tip side (side of compression chamber 20) of the second housing 9 is open. As a result, the rotation is prevented by the key 35, and the relative position of the male rotor 24 in the rotation direction with respect to the first rotating shaft 32 is uniquely determined. The male rotor 24 is fastened to the first rotating shaft 32 by the first bolt 31.
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Next, the female rotor 26 is fastened to the second rotating shaft 42 by the second bolt 41. In this case, the second bolt 41 is used to perform the fastening after the position in the rotation direction with respect to the second rotating shaft 42 is adjusted to a desired value. The first housing 7 is attached to the tip side of the second housing 9 to form the compression chamber 20.
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Next, a seal part 50 that increases the air-tightness of the clearances between the male rotor 24 and the compression part 3 and between the female rotor 26 and the compression part 3 to improve the compression efficiency will be described with reference to the drawings. FIG. 4 is a partially enlarged view showing a vicinity of the male rotor 24 of the claw compressor 1 shown in FIG. 2. FIG. 5 is a partially enlarged view showing a 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 which are shown in FIG. 2 as viewed from the side of the gear part 5. FIG. 7 is a view of the male rotor 24 and the female rotor 26 which are shown in FIG. 2 as viewed from the side of the discharge port 15.
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The seal part 50 of the present embodiment includes 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 resin material having high wear resistance (for example, polyphenylene sulfide (PPS) or polytetrafluoroethylene (PTFE)). As shown in FIGS. 4 and 6, the tip seal 51 is a member that airtightly seals a first clearance CL1 between the accommodation surface 9b of the compression part 3 and an end surface 24d of the male rotor 24 that faces the accommodation surface 9b. The tip seal 51 is disposed in a first groove part 24d1 formed in the end surface 24d.
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As shown in FIGS. 5 and 6, the tip seal 52 is a member that airtightly seals a second clearance CL2 between the accommodation surface 9b of the compression part 3 and an end surface 26d of the female rotor 26 that faces the accommodation surface 9b. The tip seal 52 is disposed in a second groove part 26d1 formed in the end surface 26d.
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As shown in FIGS. 4 and 7, the tip seal 53 is a member that airtightly seals a third clearance CL3 between the accommodation surface 7a of the compression part 3 and an end surface 24e of the male rotor 24 that faces the accommodation surface 7a. The tip seal 53 is disposed in a third groove part 24e1 formed in the end surface 24e.
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As shown in FIGS. 5 and 7, the tip seal is not disposed in a fourth clearance CL4 between the accommodation surface 7a of the compression part 3 and an end surface 26e of the female rotor 26 that faces the accommodation surface 7a. The tip seal is not disposed in the fourth clearance CL4 because the discharge port 15 that discharges the vapor compressed between the claw part 24a of the male rotor 24 and the recessed part 26b of the female rotor 26 or between the claw part 26a of the female rotor 26 and the recessed part 24b of the male rotor 24 is formed in a region of the accommodation surface 7a of the compression part 3 that faces the end surface 26e of the female rotor 26. In a case where the tip seal is disposed in the fourth clearance CL4, the tip seal comes into contact with a corner part of a boundary portion between the discharge port 15 and the accommodation surface 7a and is worn.
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In the present embodiment, the tip seal is disposed in the first clearance CL1, the second clearance CL2, and the third clearance CL3, and the tip seal is not disposed in the fourth clearance CL4; however, other aspects may also be adopted. For example, the tip seal may be disposed in at least one of the first clearance CL1, the second clearance CL2, the third clearance CL3, and the fourth clearance CL4. In a case where the tip seal is disposed in the fourth clearance CL4, a groove part for accommodating the tip seal is provided in the end surface 26e of the female rotor 26.
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As shown in FIGS. 3 and 5, the claw compressor 1 of the present embodiment includes an injection port (fluid supply port) 60 that supplies a fluid (for example, water) for reducing a temperature of the vapor compressed between the claw part 24a of the male rotor 24 and the recessed part 26b of the female rotor 26 or between the claw part 26a of the female rotor 26 and the recessed part 24b of the male rotor 24 to the compression chamber 20.
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The injection port 60 of the present embodiment discharges the fluid to the fourth clearance CL4 between the accommodation surface 7a of the compression part 3 and the end surface 26e of the female rotor 26 that faces the accommodation surface 7a. The injection port 60 is disposed on the accommodation surface 7a facing the fourth clearance CL4 because the tip seal is not disposed on the end surface 26e of the female rotor 26 that faces the fourth clearance CL4. Since the tip seal is not disposed on the end surface 26e of the female rotor 26, the tip seal is not worn by contact with the injection port 60.
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The injection port 60 of the present embodiment may be disposed to discharge the fluid to the third clearance CL3 in a case where the tip seal 53 is not disposed on the end surface 24e of the male rotor 24 that faces the third clearance CL3, for example. In this case, the claw compressor 1 includes the tip seal 51 disposed in the first groove part 24d1, and the tip seal 52 disposed in the second groove part 26d1. The injection port 60 supplies the fluid from the accommodation surface 7a to the third clearance CL3 and the fourth clearance CL4.
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The claw compressor 1 of the present embodiment includes a temperature sensor (not shown) that detects a temperature of the vapor discharged from the discharge port 15, a flow regulation valve (not shown) disposed in a pipe communicating with the injection port 60, and a control part (not shown) that controls an opening degree of the flow regulation valve. The control part controls the opening degree of the flow regulation valve such that the temperature detected by the temperature sensor is maintained in a predetermined temperature range (for example, a range of 140°C or higher and 160°C or lower).
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According to the claw compressor 1 of the present embodiment described above, the following operational effects are achieved.
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According to the claw compressor of the present embodiment, the air-tightness of at least one of the first clearance CL1 between the accommodation surface 9b and the end surface 24d of the male rotor 24 that faces the accommodation surface 9b, the second clearance CL2 between the accommodation surface 9b and the end surface 26d of the female rotor 26 that faces the accommodation surface 9b, the third clearance CL3 between the accommodation surface 7a and the end surface 24e of the male rotor 24 that faces the accommodation surface 7a, and the fourth clearance CL4 between the accommodation surface 7a and the end surface 26e of the female rotor 26 that faces the accommodation surface 7a is increased by the seal part 50. Therefore, in a case where the claw compressor 1 is used for the vapor compression application, high compression efficiency can be achieved.
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In addition, according to the claw compressor 1 of the present embodiment, the tip seal 51 is disposed in the first groove part 24d1, the tip seal 52 is disposed in the second groove part 26d1, and the tip seal 53 is disposed in the third groove part 24e1, so that the air-tightness of the first clearance CL1, the second clearance CL2, and the third clearance CL3 can be increased. In addition, since the tip seal is not disposed in the fourth clearance CL4, it is possible to prevent a problem in which the tip seal wears by the contact with the corner part of the boundary portion between the discharge port 15 and the accommodation surface 7a by disposing the tip seal in the fourth clearance CL4.
[First Modification Example]
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The injection port 60 in the present embodiment discharges the fluid to the fourth clearance CL4 between the accommodation surface 7a of the compression part 3 and the end surface 26e of the female rotor 26 that faces the accommodation surface 7a; however, other aspects may also be adopted. For example, an injection port 60A of the first modification example shown in FIG. 8 may be used. FIG. 8 is a view showing a first modification example of the injection port 60 of the first embodiment of the present disclosure.
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The injection port 60A of the first modification example shown in FIG. 8 is a port that supplies the fluid (for example, water) from a supply source (not shown) of the fluid to the compression chamber 20 through an internal flow path 42A of the second rotating shaft 42 and an internal flow path 26f of the female rotor 26. The internal flow path 26f supplies the fluid to a bottom surface of the second groove part 26d1 in which the tip seal 52 is accommodated. The tip seal 52 is pressed toward the accommodation surface 9b by a pressure of the fluid flowing from the internal flow path 26f to the second groove part 26d1. Since a biasing force toward the accommodation surface 9b acts on the tip seal 52, the air-tightness between the tip seal 52 and the accommodation surface 9b is improved.
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The injection port 60A of the first modification example shown in FIG. 8 supplies the fluid to the bottom surface of the second groove part 26d1 in which the tip seal 52 is accommodated; however, other aspects may also be adopted. For example, the injection port 60A may supply the fluid to the bottom surface of the first groove part 24d1 in which the tip seal 51 is accommodated. In addition, the injection port 60A may supply the fluid to the bottom surface of the third groove part 24e1 in which the tip seal 53 is accommodated. The injection port 60A may supply the fluid to at least one of the first groove part 24d1, the second groove part 26d1, and the third groove part 24e1.
[Second Modification Example]
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The injection port 60 in the present embodiment discharges the fluid to the fourth clearance CL4 between the accommodation surface 7a of the compression part 3 and the end surface 26e of the female rotor 26 that faces the accommodation surface 7a; however, other aspects may also be adopted. For example, an injection port 60B of the second modification example shown in FIG. 9 may be used. FIG. 9 is a view showing a second modification example of the injection port 60 of the first embodiment of the present disclosure.
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The injection port 60B shown in FIG. 9 is a port that communicates with a recess 7b formed in the first housing 7 in order to cause a first space S1 and a second space S2 in the compression chamber 20 to communicate with each other in a case where a suction step of suctioning the vapor from the suction port 13 into the compression chamber 20 is executed after a compression step of discharging the compressed vapor from the discharge port 15 is completed.
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The first space S1 is a space in which negative pressure is generated, and in a case where the space is sealed, an excessive amount of power is required to rotate the male rotor 24 and the female rotor 26. Therefore, the recess 7b is formed in the first housing 7, and the first space S1 and the second space S2 communicate with each other. In a case where the injection port 60B communicates with a space in which the vapor compressed during the compression step of the compression chamber 20 is sealed, the compressed vapor flows back to the injection port 60B. Therefore, in the second modification example, the injection port 60B is provided to communicate with the recess 7b, so that the backflow of the compressed vapor can be appropriately prevented.
[Third Modification Example]
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The injection port 60 in the present embodiment discharges the fluid to the fourth clearance CL4 between the accommodation surface 7a of the compression part 3 and the end surface 26e of the female rotor 26 that faces the accommodation surface 7a; however, other aspects may also be adopted. For example, an injection port 60C of the third modification example shown in FIG. 10 may be used. FIG. 10 is a view showing a third modification example of the injection port 60 of the first embodiment of the present disclosure.
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The claw compressor 1 of the third modification example includes the injection port 60C that supplies a fluid for reducing a temperature of the vapor compressed by the male rotor 24 and the female rotor 26 to the compression chamber 20. The second housing 9 of the compression part 3 has a connecting surface 9c that connects the accommodation surface 7a and the accommodation surface 9b and that is disposed to surround the compression chamber 20 in the radial direction. The injection port 60C supplies the fluid (for example, water) from the outer side of the connecting surface 9c toward a clearance CL5 between the female rotor 26 of the compression chamber 20 and the connecting surface 9c along the radial direction orthogonal to the first rotating shaft 32 and the second rotating shaft 42.
[Fourth Modification Example]
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The claw compressor 1 of the third modification example includes the injection port 60C that supplies the fluid from the outer side of the connecting surface 9c toward the compression chamber 20; however, other aspects may also be adopted. For example, an injection port 60D of the fourth modification example shown in FIG. 11 may be used. FIG. 11 is a view showing a fourth modification example of the injection port 60 of the first embodiment of the present disclosure. The injection port 60D of the fourth modification example shown in FIG. 11 is a port that supplies the fluid (for example, water) from a supply source (not shown) of the fluid to the compression chamber 20 through an internal flow path 42D of the second rotating shaft 42 and an internal flow path 26g of the female rotor 26.
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The injection port 60D of the fourth modification example causes the fluid guided from the internal flow path 42D of the second rotating shaft 42 to branch in three directions in the internal flow path 26g and guides the fluid in the radial direction orthogonal to the second rotating shaft 42, and supplies the fluid (for example, water) from the tip of the claw part 26a toward the clearance CL5 between the female rotor 26 and the connecting surface 9c.
[Second Embodiment]
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Hereinafter, 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 increases the air-tightness of the clearances between the male rotor 24 and an inner peripheral surface of the compression chamber 20 and between the female rotor 26 and the inner peripheral surface by disposing the tip seal in at least one of the first clearance CL1, the second clearance CL2, the third clearance CL3, and the fourth clearance CL4. On the other hand, the claw compressor 1 according to the present embodiment increases the air-tightness of the clearances between the male rotor 24 and an inner peripheral surface of the compression chamber 20 and between the female rotor 26 and the inner peripheral surface by supplying the fluid to at least one of the first clearance CL1, the second clearance CL2, the third clearance CL3, and the fourth clearance CL4.
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FIG. 12 is a cross-sectional view showing a 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 a 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 which are shown in FIGS. 12 and 13 as viewed from the side of the gear part 5. FIG. 15 is a view of the male rotor 24 and the female rotor 26 which are shown in FIGS. 12 and 13 as viewed from the side of the discharge port 15.
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As shown in FIG. 12, the first groove part 24d1 is formed in the end surface 24d of the male rotor 24 that faces the accommodation surface 9b, and the third groove part 24e1 is formed in the end surface 24e of the male rotor 24 that faces the accommodation surface 7a. As shown in FIG. 13, the second groove part 26d1 is formed in the end surface 26d of the female rotor 26 that faces the accommodation surface 9b, and the fourth groove part 26e1 is formed in the end surface 26e of the female rotor 26 that faces the accommodation surface 7a.
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As shown in FIG. 12, the claw compressor 1 of the present embodiment has an injection port 60E that supplies the fluid (for example, water) from a supply source (not shown) of the fluid to the compression chamber 20 through an internal flow path 32E of the first rotating shaft 32 and an internal flow path 24f of the male rotor 24. The injection port 60E is a port that supplies a fluid (for example, water) for reducing a temperature of the vapor compressed by the male rotor 24 and the female rotor 26 to the compression chamber 20. The internal flow path 24f supplies the fluid to the bottom surface of the first groove part 24d1 and the bottom surface of the third groove part 24e1.
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The fluid supplied to the bottom surface of the first groove part 24d1 is supplied to a region of the first clearance CL1, between the accommodation surface 9b and the end surface 24d of the male rotor 24, that faces the first groove part 24d1, and forms a first sealing region Se1 corresponding to the shape of the first groove part 24d1. Therefore, the air-tightness between the first groove part 24d1 and the accommodation surface 9b is improved. As shown in FIG. 14, the first sealing region Se1 has a shape corresponding to the first groove part 24d1.
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The fluid supplied to the bottom surface of the third groove part 24e1 is supplied to a region of the third clearance CL3, between the accommodation surface 7a and the end surface 24e of the male rotor 24, that faces the third groove part 24e1, and forms a third sealing region Se3 corresponding to the shape of the third groove part 24e1. Therefore, the air-tightness between the third groove part 24e1 and the accommodation surface 7a is improved. As shown in FIG. 15, the third sealing region Se3 has a shape corresponding to the third groove part 24e1.
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As shown in FIG. 13, the claw compressor 1 of the present embodiment has an injection port 60F that supplies the fluid (for example, water) from a supply source (not shown) of the fluid to the compression chamber 20 through an internal flow path 42F of the second rotating shaft 42 and the internal flow path 26g of the female rotor 26. The injection port 60F is a port that supplies a fluid (for example, water) for reducing a temperature of the vapor compressed by the male rotor 24 and the female rotor 26 to the compression chamber 20. The internal flow path 26g supplies the fluid to the bottom surface of the second groove part 26d1 and the bottom surface of the fourth groove part 26e1.
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The fluid supplied to the bottom surface of the second groove part 26d1 is supplied to a region of the second clearance CL2, between the accommodation surface 9b and the end surface 26d of the female rotor 26, that faces the second groove part 26d1, and forms a second sealing region Se2 corresponding to the shape of the second groove part 26d1. Therefore, the air-tightness between the second groove part 26d1 and the accommodation surface 9b is improved. As shown in FIG. 14, the second sealing region Se2 has a shape corresponding to the second groove part 26d1.
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The fluid supplied to the bottom surface of the fourth groove part 26e1 is supplied to a region of the fourth clearance CL4, between the accommodation surface 7a and the end surface 26e of the female rotor 26, that faces the fourth groove part 26e1, and forms a fourth sealing region Se4 corresponding to the shape of the fourth groove part 26e1. Therefore, the air-tightness between the fourth groove part 26e1 and the accommodation surface 7a is improved. As shown in FIG. 15, the fourth sealing region Se4 has a shape corresponding to the fourth groove part 26e1.
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According to the claw compressor 1 of the present embodiment, the temperature of the vapor discharged from the discharge port 15 can be maintained at an appropriate temperature by supplying the fluid for reducing the temperature of the vapor to the first groove part 24d1, the second groove part 26d1, the third groove part 24e1, and the fourth groove part 26e1. In addition, the sealing regions corresponding to the shapes of the first groove part 24d1, the second groove part 26d1, the third groove part 24e1, and the fourth groove part 26e1 can be formed by the fluid, and the air-tightness of the first clearance CL1, the second clearance CL2, the third clearance CL3, and the fourth clearance CL4 can be increased.
[Modification Example]
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The claw compressor 1 of the present embodiment includes the injection port 60E that supplies the fluid from the internal flow path 32E of the first rotating shaft 32 to the internal flow path 24f of the male rotor 24, and the injection port 60F that supplies the fluid from the internal flow path 42F of the second rotating shaft 42 to the internal flow path 26g of the female rotor 26; however, other aspects may also be adopted. For example, the claw compressor 1 may include an injection port 60G that supplies the fluid from a side of the first housing 7 to the internal flow path 24g of the male rotor 24, and an injection port 60H that supplies the fluid from the side of the first housing 7 to an internal flow path 26h of the female rotor 26.
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FIG. 16 is a cross-sectional view showing a vicinity of the male rotor 24 of the claw compressor 1 according to a modification example of the second embodiment of the present disclosure. FIG. 17 is a cross-sectional view showing a vicinity of the female rotor 26 of the claw compressor 1 according to the modification example of the second embodiment of the present disclosure.
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As shown in FIG. 16, the claw compressor 1 according to the modification example includes the injection port 60G that supplies the fluid from the side of the first housing 7 to the recess 24c of the male rotor 24. The fluid supplied to the recess 24c from the injection port 60G is guided to the third groove part 24e1 through a groove part 24e2 and a groove part 24e3 which are formed in the end surface 24e of the male rotor 24. The fluid guided to the third groove part 24e1 is guided to the first groove part 24d1 through the internal flow path 24g.
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As shown in FIG. 17, the claw compressor 1 according to the modification example includes the injection port 60H that supplies the fluid from the side of the first housing 7 to the recess 26c of the female rotor 26. The fluid supplied to the recess 26c from the injection port 60H is guided to the fourth groove part 26e1 through a groove part 26e2 and a groove part 26e3 which are formed in the end surface 26e of the female rotor 26. The fluid guided to the fourth groove part 26e1 is guided to the second groove part 26d1 through the internal flow path 26h.
[Other Embodiments]
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In the above, the male rotor 24 has a pair of claw parts 24a and a pair of recessed parts 24b, and the female rotor 26 has a pair of claw parts 26a and a pair of recessed parts 26b; however, other aspects may also be adopted. For example, the male rotor 24 may have three or more claw parts 24a and three or more recessed parts 24b, and the female rotor 26 may have three or more claw parts 26a and three or more recessed parts 26b.
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In this manner, the compression step occurs at any timing in a case where 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 meshing of the gear part 5 from being released and an error due to backlash from occurring in a case where a timing at which the compression step does not occur occurs.
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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) that has a plurality of first claw parts (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 parts (26a) protruding in the radial direction, a second rotating shaft (42) that rotatably supports the second rotor, a compression part (3) that forms a compression chamber (20) accommodating the first rotor and the second rotor, and a seal part (50) that increases air-tightness of clearances between the first rotor and the compression part and between the second rotor and the compression part, in which the first rotor has a plurality of first recessed parts (24b) that receive the plurality of second claw parts, the second rotor has a plurality of second recessed parts (26b) that receive the plurality of first claw parts, the compression part forms the compression chamber between a first accommodation surface (9b) and a second accommodation surface (7a) that are orthogonal to the first rotating shaft and the second rotating shaft, and the seal part increases air-tightness of at least one of a first clearance (CL1) between the first accommodation surface and an end surface (24d) of the first rotor that faces the first accommodation surface, a second clearance (CL2) between the first accommodation surface and an end surface (26d) of the second rotor that faces the first accommodation surface, a third clearance (CL3) between the second accommodation surface and an end surface (24e) of the first rotor that faces the second accommodation surface, and a fourth clearance (CL4) between the second accommodation surface and an end surface (26e) of the second rotor that faces the second accommodation surface.
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According to the claw compressor according to the first aspect of the present disclosure, the air-tightness of at least one of the first clearance between the first accommodation surface and the end surface of the first rotor that faces the first accommodation surface, the second clearance between the first accommodation surface and the end surface of the second rotor that faces the first accommodation surface, the third clearance between the second accommodation surface and the end surface of the first rotor that faces the second accommodation surface, and the fourth clearance between the second accommodation surface and the end surface of the second rotor that faces the second accommodation surface is increased by the seal part. Therefore, in a case where the claw compressor is used for the vapor compression application, high compression efficiency can be achieved.
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A claw compressor according to a second aspect of the present disclosure further includes the following configuration in the first aspect. That is, the seal part has a first tip seal (51) disposed in a first groove part (24d1) formed in the end surface of the first rotor that faces the first accommodation surface, a second tip seal (52) disposed in a second groove part (26d1) formed in the end surface of the second rotor that faces the first accommodation surface, and a third tip seal (53) disposed in a third groove part (24e1) formed in the end surface of the first rotor that faces the second accommodation surface, and a discharge port (15) that discharges vapor compressed between the first claw parts and the second recessed parts or between the second claw parts and the first recessed parts is formed in a region of the second accommodation surface that faces the end surface of the second rotor.
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According to the claw compressor according to the second aspect of the present disclosure, the first tip seal is disposed in the first groove part, the second tip seal is disposed in the second groove part, and the third tip seal is disposed in the third groove part, so that the air-tightness of the first clearance, the second clearance, and the third clearance can be increased. In addition, since the tip seal is not disposed in the fourth clearance, it is possible to prevent a problem in which the tip seal wears by the contact with the corner part of the boundary portion between the discharge port and the second accommodation surface by disposing the tip seal in the fourth clearance.
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A claw compressor according to a third aspect of the present disclosure further includes the following configuration in the second aspect. That is, the claw compressor includes a fluid supply port (60A) that supplies a fluid for reducing a temperature of the vapor to at least one of the first groove part, the second groove part, and the third groove part.
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According to the claw compressor according to the third aspect of the present disclosure, the temperature of the vapor discharged from the discharge port can be maintained at an appropriate temperature because the fluid for reducing the temperature of the vapor is supplied to at least one of the first groove part, the second groove part, and the third groove part. In addition, since 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, the sealing performance of the tip seal is improved.
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A claw compressor according to a fourth aspect of the present disclosure further includes the following configuration in the second aspect. That is, the claw compressor includes a fluid supply port (60) that supplies a fluid for reducing a temperature of the vapor compressed between the first claw parts and the second recessed parts or between the second claw parts and the first recessed parts to the compression chamber, in which the fluid supply port supplies the fluid from the second accommodation surface to the fourth clearance.
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According to the claw compressor according to the fourth aspect of the present disclosure, the fluid is supplied from the second accommodation surface to the fourth clearance in which the tip seal is not disposed, so that a problem in which the tip seal is worn by the fluid supply port provided on the second accommodation surface does not occur.
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A claw compressor according to a fifth aspect of the present disclosure further includes the following configuration in the first aspect. That is, the claw compressor includes a fluid supply port (60) that supplies a fluid for reducing a temperature of vapor compressed between the first claw parts and the second recessed parts or between the second claw parts and the first recessed parts to the compression chamber, in which the seal part has a first tip seal (51) disposed in a first groove part (24d1) formed in the end surface of the first rotor that faces the first accommodation surface, and a second tip seal (52) disposed in a second groove part (26d1) formed in the end surface of the second rotor that faces the first accommodation surface, and the fluid supply port supplies the fluid from the second accommodation surface to the third clearance and the fourth clearance.
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According to the claw compressor according to the fifth aspect of the present disclosure, the fluid is supplied from the second accommodation surface to the third clearance and the fourth clearance in which the tip seal is not disposed, so that a problem in which the tip seal is worn by the fluid supply port provided on the second accommodation surface does not occur.
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A claw compressor according to a sixth aspect of the present disclosure further includes the following configuration in the first aspect. That is, the claw compressor includes a fluid supply port (60C) that supplies a fluid for reducing a temperature of vapor compressed between the first claw parts and the second recessed parts or between the second claw parts and the first recessed parts to the compression chamber, in which the compression part has a connecting surface (9c) that connects the first accommodation surface and the second accommodation surface and that is disposed to surround the compression chamber, and the fluid supply port supplies the fluid from the connecting surface to the compression chamber along a radial direction orthogonal to the first rotating shaft and the second rotating shaft.
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According to the claw compressor according to the sixth aspect of the present disclosure, the fluid is supplied from the connecting surface to the compression chamber along the radial direction orthogonal to the first rotating shaft and the second rotating shaft, so that the fluid can be supplied to the compression chamber without wearing the tip seal, and the temperature of the vapor discharged from the discharge port can be maintained at an appropriate temperature.
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A claw compressor according to a seventh aspect of the present disclosure further includes the following configuration in the first aspect. That is, the claw compressor includes a fluid supply port (60A) that supplies a fluid for reducing a temperature of vapor compressed between the first claw parts and the second recessed parts or between the second claw parts and the first recessed parts to the compression chamber through an internal flow path (26f) formed inside the second rotor.
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According to the claw compressor according to the seventh aspect of the present disclosure, the fluid supply port supplies the fluid to the compression chamber through the internal flow path (26f) formed inside the second rotor, so that the temperature of the vapor discharged from the discharge port can be maintained at an appropriate temperature.
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A claw compressor according to an eighth aspect of the present disclosure further includes the following configuration in the seventh aspect. That is, the compression part has a connecting surface (9c) that connects the first accommodation surface and the second accommodation surface and that is disposed to surround the compression chamber, and the fluid supply port (60C) supplies the fluid to a clearance between the second rotor and the connecting surface.
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According to the claw compressor according to the eighth aspect of the present disclosure, the fluid is supplied to the clearance between the second rotor and the connecting surface through the internal flow path (26f) formed inside the second rotor, so that the fluid can be supplied to the compression chamber without wearing the tip seal, and the temperature of the vapor discharged from the discharge port can be maintained at an appropriate temperature.
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A claw compressor according to a ninth aspect of the present disclosure further includes the following configuration in the first aspect. That is, a first groove part (24d1) is formed in the end surface of the first rotor that faces the first accommodation surface, a second groove part (26d1) is formed in the end surface of the second rotor that faces the first accommodation surface, a third groove part (24e1) is formed in the end surface of the first rotor that faces the second accommodation surface, a fourth groove part (26e1) is formed in the end surface of the second rotor that faces the second accommodation surface, and the seal part has a fluid supply port (60E, 60F) that supplies a fluid for reducing a temperature of vapor to the first groove part, the second groove part, the third groove part, and the fourth groove part.
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According to the claw compressor according to the ninth aspect of the present disclosure, the temperature of the vapor discharged from the discharge port can be maintained at an appropriate temperature by supplying the fluid for reducing the temperature of the vapor to the first groove part, the second groove part, the third groove part, and the fourth groove part. In addition, the sealing regions corresponding to the shapes of the first groove part, the second groove part, the third groove part, and the fourth groove part can be formed by the fluid, and the air-tightness of the first clearance, the second clearance, the third clearance, and the fourth clearance can be increased.
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A claw compressor according to a tenth aspect of the present disclosure further includes the following configuration in any one of the third to ninth aspects. That is, the claw compressor includes a regulating valve that regulates a supply amount of the fluid supplied from the fluid supply port to the compression chamber in accordance with a temperature of a fluid discharged from the compression chamber.
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According to the claw compressor according to the tenth aspect of the present disclosure, the supply amount of the fluid supplied from the fluid supply port to the compression chamber is regulated in accordance with the temperature of the fluid discharged from the compression chamber, so that the temperature of the fluid discharged from the compression chamber can be maintained within an appropriate range.
Reference Signs List
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- 1: claw compressor
- 3: compression part
- 5: gear part
- 7: first housing
- 7a: accommodation surface
- 7b: recess
- 9: second housing
- 9a: inner wall
- 9b: accommodation surface
- 9c: connecting surface
- 11: third housing
- 13: suction port
- 15: discharge port
- 20: compression chamber
- 21: gear chamber
- 24: male rotor (first rotor)
- 24a, 26a: claw part
- 24b, 26b: recessed part
- 24c, 26c: recess
- 24d, 24e, 26d, 26e: end surface
- 24d1: first groove part
- 24e2, 24e3, 26e2, 26e3: groove part
- 24e1: third groove part
- 24f, 24g, 26f, 26g, 26h, 32E, 42A, 42D, 42F: internal flow path
- 26: female rotor (second rotor)
- 26d1: second groove part
- 26e1: fourth groove part
- 32: first rotating shaft
- 42: second rotating shaft
- 50: seal part
- 51, 52, 53: tip seal
- 60, 60A, 60B, 60C, 60D, 60E, 60F, 60G, 60H: fluid supply port
- CL1: first clearance
- CL2: second clearance
- CL3: third clearance
- CL4: fourth clearance
- O1: first rotational axis
- O2: second rotational axis
- S1: first space
- S2: second space
- Se1: first sealing region
- Se2: second sealing region
- Se3: third sealing region
- Se4: fourth sealing region