Claw compressor and method for designing claw compressor

Abstract

Provided are a claw compressor and a method for designing claw compressor that enable efficiency to be improved by reducing pressure loss in a suction passage. Assuming a first limit position (P1) to be a position on a first cylindrical surface (S1) where an end portion toward the rear of one first claw part in the rotation direction thereof is present at the moment when an end portion toward the rear of another first claw part in the rotation direction thereof reaches a compression-side intersection line (L2), assuming a second limit position (P2) to be a position on a second cylindrical surface (S2) where an end portion toward the rear of one second claw part in the rotation direction thereof is present at the moment when an end portion toward the rear of another second claw part in the rotation direction thereof reaches the compression-side intersection line (L2), and assuming a suction range (R) to be a range along the first cylindrical surface (S1) and the second cylindrical surface (S2) and extending from the first limit position (P1) including a suction-side intersection line (L1) to the second limit position (P2), then a suction port faces the suction range (R), and the opening area of the suction port is 20% or more of the area of the suction range (R).

Description

Claw compressor and claw compressor design method

[0001] The present disclosure relates to claw compressors and methods for designing claw compressors.

[0002] A claw compressor includes a pair of rotors, each with a hook-shaped claw, housed in a housing. The rotors rotate at the same speed in opposite directions without contact while maintaining a predetermined clearance. The two rotors and the housing form a suction chamber and a compression chamber. Fluid taken into the suction chamber from outside the housing through a suction port is compressed in the compression chamber, and the compressed fluid is discharged to the outside of the housing through a discharge port. Such claw compressors are often used primarily as vacuum pumps and blowers (see, for example, Patent Document 1).

[0003] Patent No. 6845596

[0004] When a claw compressor is used to compress steam generated by a steam generating heat pump used as a boiler replacement, the claw compressor takes in low-pressure steam. Because the density of low-pressure steam is low, pressure loss in the intake path significantly affects efficiency. Therefore, reducing pressure loss is essential to improve efficiency (or to prevent efficiency from decreasing).

[0005] The present disclosure has been made in consideration of the above circumstances, and aims to provide a claw compressor and a method for designing a claw compressor that can reduce pressure loss in the suction path and improve efficiency.

[0006] In order to solve the above problems, the claw compressor and the design method of the claw compressor according to one aspect of the present disclosure employ the following means: A claw compressor according to one aspect of the present disclosure includes a first rotor that rotates about a first axis and has two first claws that protrude in a radial direction relative to the first axis, a second rotor that rotates in an opposite direction to the first rotor about a second axis that is parallel to the first axis and has two second claws that protrude in a radial direction relative to the second axis, and a housing that houses the first rotor and the second rotor and has a suction port for taking in a fluid, wherein when a side surface of an imaginary cylinder described by the first claws of the rotating first rotor is defined as a first cylindrical surface, and a side surface of an imaginary cylinder described by the second claws of the rotating second rotor is defined as a second cylindrical surface, and when intersection lines between the overlapping first cylindrical surface and the second cylindrical surface are defined as an suction side intersection line and a compression side intersection line, the suction side intersection line is a line that intersects with the suction port. The compression-side intersection line is the intersection line on the side of the compression chamber where the fluid is compressed, and a position on the first cylindrical surface where a rear end of one of the first claws in the rotational direction is located when the rear end of the other first claw reaches the compression-side intersection line is defined as a first limit position, and a position on the second cylindrical surface where a rear end of the other second claw is located when the rear end of the other second claw in the rotational direction is located when the rear end of the other second claw reaches the compression-side intersection line is defined as a second limit position. When the range along the first and second cylindrical surfaces from the first limit position to the second limit position, including the suction-side intersection line, is defined as an suction range, the suction port faces the suction range, and an opening area of ​​the suction port is 20% or more of the area of ​​the suction range.

[0007] A design method for a claw compressor according to one aspect of the present disclosure is a design method for a claw compressor including: a first rotor that rotates about a first axis and has two first claws that protrude in a radial direction relative to the first axis; a second rotor that rotates in an opposite direction to the first rotor about a second axis that is parallel to the first axis and has two second claws that protrude in a radial direction relative to the second axis; and a housing that houses the first rotor and the second rotor and has a suction port for taking in a fluid, wherein the design method defines a first cylindrical surface as a side surface of an imaginary cylinder that is described by the first claws of the rotating first rotor, a second cylindrical surface as a side surface of an imaginary cylinder that is described by the second claws of the rotating second rotor, and a suction-side intersection line between the overlapping first and second cylindrical surfaces. and compression side intersection line, the suction side intersection line is the intersection line on the suction chamber side where fluid is taken in through the suction port, and the compression side intersection line is the intersection line on the compression chamber side where fluid is compressed. A first limit position is a position on the first cylindrical surface where a rear end of one of the first claws in the rotational direction is located when the rear end of the other first claw reaches the compression side intersection line, and a second limit position is a position on the second cylindrical surface where a rear end of the other second claw in the rotational direction is located when the rear end of one of the second claws in the rotational direction is located when the rear end of the other second claw reaches the compression side intersection line. A range along the first cylindrical surface and the second cylindrical surface from the first limit position to the second limit position, including the suction side intersection line, is defined as an suction range, and the suction port is positioned to face the suction range.

[0008] According to the present disclosure, pressure loss in the intake path can be reduced, improving efficiency.

[0009] FIG. 1 is a perspective view of a claw compressor according to a first embodiment of the present disclosure; FIG. 2 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 3 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 4 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 5 is a front view of a claw compressor according to a third embodiment of the present disclosure; FIG. 6 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 7 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 8 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 9 is a front view of a claw compressor according to a first embodiment of the present disclosure (without cover); FIG. 10 is a perspective view of a first cylindrical surface and a second cylindrical surface with an inlet region indicated; FIG. 11 is a cross-sectional view of a first housing of a claw compressor according to a second embodiment of the present disclosure; FIG. 12 is a cross-sectional view of a first housing of a claw compressor according to a second embodiment of the present disclosure; FIG. 13 is a cross-sectional view of a first housing of a claw compressor according to a third embodiment of the present disclosure;

[0010] Hereinafter, a claw compressor and a method for designing a claw compressor according to an embodiment of the present disclosure will be described with reference to the drawings.

[0011] In the following description, the vertical direction refers to the direction from top to bottom or bottom to top, the front-to-back direction refers to the direction from front to back or back to front, and the left-to-right direction refers to the direction from left to right or right to left. The vertical, front-to-back, and left-to-right directions are generally perpendicular to each other. These directions are terms used to facilitate understanding of the description and do not limit the actual position of the product.

[0012] [Basic Configuration] The claw compressor 1 is a device that compresses a fluid. The claw compressor 1 is used, for example, to compress steam generated by a steam generation heat pump that is used as a substitute for a boiler. As shown in Figures 1 and 2, the claw compressor 1 includes a housing 10, a first rotor 30 serving as a male rotor, and a second rotor 40 serving as a female rotor.

[0013] The housing 10 accommodates the first rotor 30, the second rotor 40, shafts (not shown) that transmit driving force to each rotor 30, 40, bearings (not shown) that rotatably support the shafts, sealing members (not shown), and timing gears (not shown) that are provided on each shaft and mesh with each other.

[0014] The housing 10 has a first housing 11, a second housing 12 attached to the rear of the first housing 11, and a lid 13 attached to the front of the first housing 11. The first housing 11 has a first housing portion 11X corresponding to the front portion, a second housing portion 11Y corresponding to the rear portion, and legs 14. The first housing portion 11X, together with the lid 13, forms a rotor housing portion 16 that houses a first rotor 30 and a second rotor 40. The second housing portion 11Y, together with the second housing 12, forms a gear housing portion 17 that houses a timing gear. The second housing portion 11Y itself and the second housing 12 themselves house bearings, seal members, etc.

[0015] Two shafts are provided spaced apart in the left-right direction and extend in the front-rear direction through the first housing 11 from the rotor accommodating portion 16 to the gear accommodating portion 17. The first shaft is connected to the first rotor 30, and the second shaft is connected to the second rotor 40. For example, the first shaft is a drive shaft having a central axis along a first axis X1 (see FIG. 2) extending in the front-rear direction, and receives driving force from an external device (not shown). In contrast, the second shaft is a driven shaft having a central axis along a second axis X2 (see FIG. 2) extending in the front-rear direction, and receives driving force from the first shaft via a timing gear accommodated in the gear accommodating portion 17.

[0016] As shown in Fig. 1, a plurality of legs 14 are provided on the lower part of the first housing 11. The claw compressor 1 is placed on an installation surface via these legs 14. In the case of Fig. 1, the number of legs 14 is four, and these legs 14 are arranged symmetrically in the front-rear and left-right directions.

[0017] At least one suction port 11a is provided in the first storage portion 11X of the first housing 11. The suction port 11a is a port for taking in fluid from the outside and defines an intake flow path through which the fluid flows. The suction port 11a is connected to the suction chamber C1, which will be described later. The suction port 11a is provided in the upper part of the first storage portion 11X. In the case of FIG. 1, three suction ports 11a facing upward are provided in the upper part of the first storage portion 11X.

[0018] The lid 13 is provided with a discharge port 13b. The discharge port 13b is a port for discharging the fluid (compressed fluid) to the outside and defines an exhaust flow path through which the fluid flows. The discharge port 13b communicates with a compression chamber C2, which will be described later. In the case of FIG. 1 , the discharge port 13b facing forward is provided on the front surface of the lid 13.

[0019] Fig. 2 shows the claw compressor 1 with the lid 13 removed. As shown in Fig. 2, the first storage portion 11X of the first housing 11 defines a storage chamber C0 by an inner wall 11w. A pair of first and second rotors 30 and 40 are housed in the storage chamber C0 and are arranged side by side in the left-right direction.

[0020] The first rotor 30 is a component having a predetermined thickness in the front-to-rear direction, and has two first claws 31. The first claws 31 are hook-shaped portions that protrude in the radial direction relative to the first axis X1, and are provided symmetrically with respect to the first axis X1. The first rotor 30 rotates counterclockwise (in the direction of arrow A1) in FIG. 2 about the first axis X1.

[0021] The second rotor 40 is a component having the same thickness in the front-to-rear direction as the first rotor 30, and has two second claws 41. The second claws 41 are hook-shaped portions that protrude in the radial direction relative to the second axis X2, and are provided symmetrically with respect to the second axis X2. The second rotor 40 rotates clockwise (in the direction of arrow A2) in FIG. 2 about the second axis X2.

[0022] The first claw portions 31 of the first rotor 30 and the second claw portions 41 of the second rotor 40 are configured to mesh with each other without contacting each other.

[0023] As shown in FIGS. 2 and 3 , the inner wall 11w of the first housing portion 11X, which defines the housing chamber C0, has a shape in which two cylindrical surfaces are partially overlapped. This shape is slightly larger (one size larger) than the external shapes of the partially overlapping first and second cylindrical surfaces S1 and S2 in the vertical and horizontal directions. Here, the first cylindrical surface S1 is defined as the side of an imaginary cylinder described by the ends of the first claws 31 of the rotating first rotor 30. The second cylindrical surface S2 is defined as the side of an imaginary cylinder described by the ends of the second claws 41 of the rotating second rotor 40. Therefore, the ends of the claws 31 and 41 of each rotor 30, 40 run along the inner wall 11w of the first housing portion 11X with a predetermined clearance (see FIGS. 4 and 5 ). The longitudinal dimensions of each cylindrical surface S1 and S2 correspond to the thickness of each rotor 30, 40. The dimension of the inner wall 11w of the first housing portion 11X in the front-rear direction is approximately the same as the dimension of each of the cylindrical surfaces S1 and S2 in the front-rear direction.

[0024] As shown in Figure 3, two intersection lines extending in the vertical direction defined by the partially overlapping first cylindrical surface S1 and second cylindrical surface S2 are defined as an intake-side intersection line L1 and a compression-side intersection line L2. The intake-side intersection line L1 is an intersection line located on the side of a suction chamber C1 (described later) and is located at the top in Figure 3. The compression-side intersection line L2 is an intersection line other than the intake-side intersection line L1, located on the side of a compression chamber C2 (described later), and is located at the bottom in Figure 3.

[0025] As shown in FIG. 4 , a predetermined clearance is provided between the end of the first claw portion 31 of the first rotor 30 and the inner wall 11w of the first housing portion 11X. Therefore, the first claw portion 31 does not slide against the inner wall 11w. Here, from the viewpoint of reducing the amount of fluid leakage, it is preferable to set the clearance as small as possible within a range in which the first claw portion 31 does not come into contact with the inner wall 11w. The end of the first claw portion 31 includes a front end 31a located forward in the rotational direction of the first rotor 30 and a rear end 31b located rearward in the rotational direction. The range from the front end 31a to the rear end 31b of the first claw portion 31 is arc-shaped along the first cylindrical surface S1. In other words, the range from the front end 31a to the rear end 31b of the first claw portion 31 is approximately parallel to the inner wall 11w of the first housing portion 11X (the clearance is approximately constant).

[0026] As shown in FIG. 5 , a predetermined clearance is provided between the end of the second claw portion 41 of the second rotor 40 and the inner wall 11w of the first housing portion 11X. Therefore, the second claw portion 41 does not slide against the inner wall 11w. Here, from the viewpoint of reducing the amount of fluid leakage, it is preferable to set the clearance as small as possible within a range in which the second claw portion 41 does not come into contact with the inner wall 11w. The end of the second claw portion 41 includes a front end 41a located forward in the rotation direction of the second rotor 40 and a rear end 41b located rearward in the rotation direction. The range from the front end 41a to the rear end 41b of the second claw portion 41 is arc-shaped along the second cylindrical surface S2. In other words, the range from the front end 41a to the rear end 41b of the second claw portion 41 is approximately parallel to the inner wall 11w of the first housing portion 11X (the clearance is approximately constant).

[0027] FIG. 6 shows the first rotor 30 and the second rotor 40 at a first angular position (top view), the first rotor 30 and the second rotor 40 at a second angular position rotated a predetermined angle from the first angular position (middle view), and the first rotor 30 and the second rotor 40 at a third angular position rotated a further predetermined angle from the second angular position (bottom view). As shown in FIG. 6 , the accommodation chamber C0 defined by the inner wall 11w is partitioned by the first rotor 30 and the second rotor 40 into a suction chamber C1, a compression chamber C2, and a transport chamber C3. Note that, depending on the angular positions of the first rotor 30 and the second rotor 40, the transport chamber C3 may not be defined. Furthermore, the suction chamber C1, the compression chamber C2, and the transport chamber C3 are not fixed, but move or deform as the first rotor 30 and the second rotor 40 rotate. Furthermore, the chambers are not completely partitioned and sealed, but are communicated with each other via the aforementioned clearance and the gap between the rotors 30, 40. The suction chamber C1 is the space where the fluid taken into the accommodation chamber C0 through the suction port 11a first arrives. The suction chamber C1 is connected to the suction port 11a. The compression chamber C2 is the space where the fluid is compressed. The compression chamber C2 is connected to the discharge port 13b. As the first rotor 30 and the second rotor 40 rotate, the volume of the compression chamber C2 gradually decreases, thereby gradually compressing the fluid present in the compression chamber C2. The transfer chamber C3 is a space located between the suction chamber C1 and the compression chamber C2 that is not connected to either the suction port 11a or the discharge port 13b. On the first rotor 30 side, the transfer chamber C3 is defined by the first rotor 30 and the inner wall 11w of the first accommodation section 11X, and on the second rotor 40 side, the transfer chamber C3 is defined by the second rotor 40 and the inner wall 11w of the first accommodation section 11X. The transport chamber C3 is a space for simply transporting the fluid along the rotational direction, not for compressing the fluid. When the rear ends 31b of the first claws 31 move away from the compression-side intersection line L2 as the first rotor 30 rotates, the transport chamber C3 switches to the compression chamber C2. Thereafter, when the rear ends 41b of the second claws 41 move away from the compression-side intersection line L2 as the second rotor 40 rotates, the transport chamber C3 communicates with the previously defined compression chamber C2 and switches to the compression chamber C2.As the first rotor 30 and the second rotor 40 continue to rotate, the volume of the compression chamber C2 gradually decreases, and the fluid present in the compression chamber C2 is gradually compressed.

[0028] [Position of the Suction Port and Opening Area of ​​the Suction Port] From the viewpoint of reducing pressure loss, it is preferable to make the opening area of ​​the suction port 11a facing the suction chamber C1 as large as possible. Therefore, in this embodiment, the claw compressor 1 is designed as follows.

[0029] First, an intake range R is determined as a range in which the intake port 11a may be provided (a range in which the intake port 11a can be provided).

[0030] As shown in Fig. 7, when the rear end 31b of one first claw portion 31 of the first rotor 30 reaches the compression-side intersection line L2, the position on the first cylindrical surface S1 at which the rear end 31b of the other first claw portion 31 exists is defined as a first limit position P1. In other words, the position on the first cylindrical surface S1 at which the rear end 31b of the other first claw portion 31 exists at the moment when the transfer chamber C3 on the first rotor 30 side switches to the compression chamber C2 is defined as the first limit position P1. Note that although the first limit position P1 is indicated by a dot in Fig. 7, it is actually a line extending in the front-to-rear direction.

[0031] As shown in Fig. 8, when the rear end 41b of one second claw portion 41 of the second rotor 40 reaches the compression-side intersection line L2, the position on the second cylindrical surface S2 at which the rear end 41b of the other second claw portion 41 exists is defined as the second limit position P2. In other words, the position on the second cylindrical surface S2 at which the rear end 41b of the other second claw portion 41 exists at the moment when the transfer chamber C3 on the second rotor 40 side communicates with the previously defined compression chamber C2 and switches to the compression chamber C2 is defined as the second limit position P2. Note that although the second limit position P2 is indicated by a dot in Fig. 8, it is actually a line extending in the front-to-rear direction.

[0032] 9 and 10, the range (area) along the first cylindrical surface S1 and the second cylindrical surface S2 from the first limit position P1 to the second limit position P2, including the suction-side intersection line L1, is defined as the suction range R. The suction range R is a curved surface along the first cylindrical surface S1 and the second cylindrical surface S2, and is indicated by cross-hatching in FIG.

[0033] 11 to 14, the suction port 11a can be provided at a position facing this suction range R. In other words, the suction port 11a (suction flow path) forms an opening in a range (area) of the inner wall 11w of the first housing portion 11X that faces the suction range R. This allows the suction port 11a to communicate with a position where fluid can be taken into the suction chamber C1 from the outside until immediately before each transfer chamber C3 switches to the compression chamber C2. In other words, the suction port 11a can be provided over as wide an area as possible.

[0034] The total area of ​​the opening formed by the suction port 11a is set to 20% or more of the area of ​​the suction range R. Specifically, the area of ​​the opening formed by the suction port 11a relative to the range of the inner wall 11w of the first housing portion 11X facing the suction range R is set to 20% or more of the area of ​​that range of the inner wall 11w. This makes it possible to maximize the opening area of ​​the suction port 11a facing the suction chamber C1, allowing a large amount of fluid to be taken into the suction chamber C1 at one time.

[0035] Here, an embodiment will be described in which suction ports 11a are provided at positions facing suction range R, and the total area of ​​the openings formed by suction ports 11a is configured to be 20% or more of the area of ​​suction range R. Note that these are merely examples, and configurations other than those of the embodiments may be used as long as suction ports 11a are provided at positions facing suction range R, and the total area of ​​the openings formed by suction ports 11a is configured to be 20% or more of the area of ​​suction range R.

[0036] <Example 1> Fig. 11 shows a cross section (cross section taken along a cut surface perpendicular to the front-rear direction) of the first housing 11 (first accommodating portion 11X). As shown in Fig. 11, the claw compressor 1 of this example has three suction ports 11a (first suction port 11a, second suction port 11a, and third suction port 11a) aligned in the left-right direction. The cross-sectional shape of each suction port 11a (cross section shape taken along a cut surface perpendicular to the up-down direction) is, for example, circular, but may be a shape other than circular.

[0037] The first suction port 11a faces near the first limit position P1. The vicinity of the first limit position P1 refers to the range of the first cylindrical surface S1 from the first limit position P1 to the first axis X1 in the left-right direction, as shown in FIG. 9 . At least a portion of the first suction port 11a needs to overlap this range in the left-right direction. The second suction port 11a faces near the second limit position P2. The vicinity of the second limit position P2 refers to the range of the second cylindrical surface S2 from the second limit position P2 to the second axis X2 in the left-right direction, as shown in FIG. 9 . At least a portion of the second suction port 11a needs to overlap this range in the left-right direction. The third suction port 11a faces near the suction side intersection line L1. The vicinity of the suction side intersection line L1 refers to the range from the first axis X1 to the second axis X2 in the left-right direction, including the position of the suction side intersection line L1, as shown in FIG. 9 . In the case of FIG. 9, the first suction port 11a is located approximately in the center of the first housing 11 in the left-right direction.

[0038] It is also possible to omit any of the first to third suction ports 11 a and enlarge the remaining suction ports 11 a. For example, the central third suction port 11 a may be omitted and the first and second suction ports 11 a located on the left and right may be used to ensure the required opening area, or the left and right first and second suction ports 11 a may be omitted and the central third suction port 11 a may be used to ensure the required opening area.

[0039] 12 to 14 show cross sections (cross sections taken along a plane perpendicular to the front-rear direction) of the first housing 11 (first accommodating portion 11X). As shown in Fig. 12 to 14, the claw compressor 1 of this embodiment has one suction port 11a extending in the left-right direction. The suction port 11a faces substantially the entire suction range R.

[0040] The inner wall surface 11a1 defining the suction port 11a may be a surface extending in the vertical direction as shown in FIG. 12, or may be an inclined surface as shown in FIGS.

[0041] As shown in Figure 13, the inner wall surface 11a1 is inclined to gradually expand the suction flow passage along the fluid flow direction, thereby preventing a sudden expansion of the flow passage area. Furthermore, as shown in Figure 14, when the tangent surface of the first cylindrical surface S1 at the first limit position P1 is defined as the first tangent surface and the tangent surface of the second cylindrical surface S2 at the second limit position P2 is defined as the second tangent surface, the inclined inner wall surface 11a1 preferably extends along the first and second tangent surfaces. This makes it easy to determine a shape of the suction port 11a that can effectively reduce pressure loss. Furthermore, while preventing a sudden expansion of the flow passage area, the suction port 11a and, therefore, the claw compressor 1 can be made more compact in the vertical direction.

[0042] Third Embodiment Fig. 15 shows a cross section (a cross section taken along a plane perpendicular to the front-rear direction) of the first housing 11 (first accommodating portion 11X). As shown in Fig. 15, the claw compressor 1 of this embodiment has one suction port 11a extending in the left-right direction. The inner wall surface 11a1 defining the suction port 11a is an inclined surface.

[0043] Here, a line (extending in the front-to-rear direction) located near the first limit position P1 (see FIG. 9) is defined as a first start position Q1. The first start position Q1 can be any position near the first limit position P1. Furthermore, a line (extending in the front-to-rear direction) located near the second limit position P2 (see FIG. 9) is defined as a second start position Q2. The second start position Q2 can be any position near the second limit position P2.

[0044] When the tangent surface of the first cylindrical surface S1 at the first start end position Q1 is defined as the first tangent surface and the tangent surface of the second cylindrical surface S2 at the second start end position Q2 is defined as the second tangent surface, the inclined inner wall surface 11a1 preferably extends along the first and second tangent surfaces. This allows for easy determination of a shape of the suction port 11a that can effectively reduce pressure loss. Furthermore, it is possible to vertically compact the suction port 11a and, by extension, the claw compressor 1 while preventing a sudden expansion of the flow path area. When the first start end position Q1 coincides with the first limit position P1 and the second start end position Q2 coincides with the second limit position P2, the suction port 11a faces substantially the entire suction range R, as in the second embodiment.

[0045] [Effects] According to this embodiment, the following effects are achieved.

[0046] The suction port 11a faces the suction range R, and the opening area of ​​the suction port 11a is set to be 20% or more of the area of ​​the suction range R, ensuring a large area for taking in fluid. This reduces pressure loss in the suction path and improves efficiency.

[0047] Since the suction port 11a faces at least the suction range R near the first limit position P1 and / or the second limit position P2, the suction port 11a can be provided over as wide an area as possible, which ensures a large area for taking in the fluid and allows the fluid to be taken in for a long period of time, thereby reducing pressure loss in the suction path and improving efficiency.

[0048] The suction port 11a faces the vicinity of the suction-side intersection line L1 within the suction range R, so that a large area for taking in the fluid can be ensured.

[0049] Since the suction port 11a faces almost the entire suction range R, it is possible to maximize the area for taking in fluid and to take in fluid for a long period of time. Furthermore, compared to when multiple suction ports 11a are provided, the effort required to process multiple suction ports 11a is reduced, and there is no need to branch the piping according to the number of suction ports 11a, which reduces manufacturing costs.

[0050] When the tangent surface of the first cylindrical surface S1 at the first start end position Q1 is defined as the first tangent surface and the tangent surface of the second cylindrical surface S2 at the second start end position Q2 is defined as the second tangent surface, the suction port 11a has an inner wall surface along the first and second tangent surfaces. This prevents a sudden expansion of the flow path area through which the fluid flows toward the suction chamber C1, thereby reducing pressure loss in the suction path. Furthermore, a shape of the suction port 11a that can effectively reduce pressure loss can be easily determined. This allows the claw compressor 1 to be compact while preventing a sudden expansion of the flow path area. Furthermore, when the first start end position is the first limit position and the second start end position is the second limit position, the suction port faces substantially the entire suction range, thereby maximizing the area for fluid intake and enabling fluid to be taken in for a long period of time.

[0051] [Additional Notes] One embodiment of the present disclosure described above can be understood, for example, as follows.

[0052] A claw compressor (1) according to a first aspect of the present disclosure includes a first rotor (30) that rotates about a first axis (X1) and has two first claws (31) that protrude in a radial direction relative to the first axis, a second rotor (40) that rotates in a direction opposite to the first rotor about a second axis (X2) that is parallel to the first axis and has two second claws (41) that protrude in a radial direction relative to the second axis, and a housing that houses the first rotor and the second rotor. and a housing (10) in which an intake port (11a) for taking in a fluid is formed, wherein when a side surface of an imaginary cylinder described by the first claw portions of the rotating first rotor is defined as a first cylindrical surface (S1), a side surface of an imaginary cylinder described by the second claw portions of the rotating second rotor is defined as a second cylindrical surface (S2), and intersection lines between the overlapping first cylindrical surface and the second cylindrical surface are defined as an intake side intersection line (L1) and a compression side intersection line (L2), is the intersection line on the side of the suction chamber (C1) into which fluid is taken in through the suction port, and the compression side intersection line is the intersection line on the side of the compression chamber (C2) where the fluid is compressed. When a position on the first cylindrical surface where a rear end (31 b) of one of the first claws in the rotational direction is located when a rear end (31 b) of the other first claw portion reaches the compression side intersection line is defined as a first limit position (P1), and a position on the second cylindrical surface where a rear end (41 b) of the other second claw portion in the rotational direction is located when a rear end (41 b) of one of the second claws in the rotational direction is located when a rear end (41 b) of the other second claw portion reaches the compression side intersection line is defined as a second limit position (P2), and the range along the first cylindrical surface and the second cylindrical surface from the first limit position to the second limit position, including the suction side intersection line, is defined as an suction range (R), the suction port faces the suction range, and an opening area of ​​the suction port is 20% or more of the area of ​​the suction range.

[0053] The suction port faces the suction area, and the opening area of ​​the suction port is set to be 20% or more of the area of ​​the suction area, ensuring a large area for taking in fluid, thereby reducing pressure loss in the suction path and improving efficiency.

[0054] A claw compressor according to a second aspect of the present disclosure is the first aspect, wherein the suction port faces at least a portion of the suction range near the first limit position and / or a portion of the suction range near the second limit position.

[0055] Since the suction port faces at least the suction range near the first limit position and / or the second limit position, the suction port can be provided over as wide an area as possible, thereby ensuring a large area for intake of fluid and enabling fluid to be taken in for a long period of time, thereby reducing pressure loss in the suction path and improving efficiency.

[0056] A claw compressor according to a third aspect of the present disclosure is the claw compressor of the first or second aspect, wherein the suction port faces a portion of the suction range near the suction-side intersection line.

[0057] The suction port faces the vicinity of the suction-side intersection line within the suction range, so that a large area for taking in fluid can be ensured.

[0058] A claw compressor according to a fourth aspect of the present disclosure is the claw compressor of any one of the first to third aspects, wherein the suction port faces substantially the entire suction range.

[0059] The suction port faces almost the entire suction range, ensuring a maximum area for taking in fluid and enabling fluid to be taken in for a long period of time. Furthermore, compared to when multiple suction ports are provided, the time required to process multiple suction ports is reduced, and there is no need to branch the piping according to the number of suction ports, which reduces manufacturing costs.

[0060] In the claw compressor according to the fifth aspect of the present disclosure, in the first aspect, when a tangent surface of the first cylindrical surface at a first start end position (Q1) located near the first limit position is defined as a first tangent surface and a tangent surface of the second cylindrical surface at a second start end position (Q2) located near the second limit position is defined as a second tangent surface, the suction port has an inner wall surface (11a1) that follows the first tangent surface and the second tangent surface.

[0061] When the tangent surface of the first cylindrical surface at the first start end position, which is located near the first limit position, is defined as the first tangent surface, and the tangent surface of the second cylindrical surface at the second start end position, which is located near the second limit position, is defined as the second tangent surface, the suction port has an inner wall surface that conforms to the first tangent surface and the second tangent surface. This prevents a sudden expansion of the flow path area through which fluid flows toward the suction chamber, thereby reducing pressure loss in the suction path. Furthermore, it is easy to determine a shape of the suction port that can effectively reduce pressure loss. This allows the claw compressor to be made more compact while preventing a sudden expansion of the flow path area.

[0062] A sixth aspect of the present disclosure provides the claw compressor of the fifth aspect, wherein the first start end position is the first limit position and the second start end position is the second limit position.

[0063] Because the first start end position is the first limit position and the second start end position is the second limit position, a sudden expansion of the flow path area through which fluid flows toward the suction chamber can be prevented, thereby reducing pressure loss in the suction path. Furthermore, a shape of the suction port that can effectively reduce pressure loss can be easily determined. This allows the claw compressor to be made compact while preventing a sudden expansion of the flow path area. Furthermore, because the suction port faces substantially the entire suction range, the area for taking in fluid can be maximized, and fluid can be taken in for a long period of time.

[0064] A seventh aspect of the present disclosure provides a claw compressor design method including: a first rotor that rotates about a first axis and has two first claws that protrude in a radial direction relative to the first axis; a second rotor that rotates in an opposite direction to the first rotor about a second axis that is parallel to the first axis and has two second claws that protrude in a radial direction relative to the second axis; and a housing that houses the first rotor and the second rotor and has a suction port formed therein for taking in a fluid, wherein the design method includes: defining a side surface of an imaginary cylinder that is described by the first claws of the rotating first rotor as a first cylindrical surface; defining a side surface of an imaginary cylinder that is described by the second claws of the rotating second rotor as a second cylindrical surface; and defining an intersection line between the overlapping first cylindrical surface and the second cylindrical surface as a suction-side intersection line. and compression side intersection line, the suction side intersection line is the intersection line on the suction chamber side where fluid is taken in through the suction port, and the compression side intersection line is the intersection line on the compression chamber side where fluid is compressed. A first limit position is a position on the first cylindrical surface where a rear end of one of the first claws in the rotational direction is located when the rear end of the other first claw reaches the compression side intersection line, and a second limit position is a position on the second cylindrical surface where a rear end of the other second claw in the rotational direction is located when the rear end of one of the second claws in the rotational direction is located when the rear end of the other second claw reaches the compression side intersection line. A range along the first cylindrical surface and the second cylindrical surface from the first limit position to the second limit position, including the suction side intersection line, is defined as an suction range, and the suction port is positioned to face the suction range.

[0065] DESCRIPTION OF SYMBOLS 1 Claw compressor 10 Housing 11 First housing 11X First storage section 11a Suction port 11a1 Inner wall surface 11w Inner wall 11Y Second storage section 12 Second housing 13 Lid 13b Discharge port 14 Leg 16 Rotor storage section 17 Gear storage section 30 First rotor (male rotor) 31 First claw portion 31a Front end 31b Rear end 40 Second rotor (female rotor) 41 Second claw portion 41a Front end 41b Rear end C0 Storage chamber C1 Suction chamber C2 Compression chamber C3 Transfer chamber L1 Suction side intersection line L2 Compression side intersection line P1 First limit position P2 Second limit position Q1 First start end position Q2 Second start end position R Suction range S1 First cylindrical surface S2 Second cylindrical surface X1 1st axis X2 2nd axis

Claims

1. A compressor comprising: a first rotor that rotates about a first axis and has two first claws that protrude in a radial direction relative to the first axis; a second rotor that rotates in the opposite direction to the first rotor about a second axis that is parallel to the first axis and has two second claws that protrude in a radial direction relative to the second axis; and a housing that houses the first and second rotors and has an intake port formed therein for taking in a fluid, wherein when the side of an imaginary cylinder described by the first claws of the rotating first rotor is defined as a first cylindrical surface, and the side of an imaginary cylinder described by the second claws of the rotating second rotor is defined as a second cylindrical surface, and the intersection lines between the overlapping first and second cylindrical surfaces are defined as an intake side intersection line and a compression side intersection line, the intake side intersection line is the intersection line on the side of an intake chamber where fluid is taken in via the intake port, and the compression side intersection line is the intersection line on the side of a compression chamber where fluid is compressed, a first limit position is a position on the first cylindrical surface where the rear end of one of the first claws in the rotational direction is located when the rear end of the other first claw reaches the compression side intersection line; and a second limit position is a position on the second cylindrical surface where the rear end of the other second claw is located when the rear end of one of the second claws in the rotational direction is located when the rear end of the other second claw reaches the compression side intersection line; and the range along the first and second cylindrical surfaces from the first limit position to the second limit position, including the suction side intersection line, is defined as an suction range, wherein the suction port faces the suction range, and an opening area of ​​the suction port is 20% or more of the area of ​​the suction range.

2. A claw compressor according to claim 1, wherein the suction port faces at least the vicinity of the first limit position and / or the vicinity of the second limit position of the suction range.

3. A claw compressor according to claim 1 or 2, wherein the suction port faces a portion of the suction range near the suction side intersection line.

4. A claw compressor according to claim 1, wherein the suction port faces substantially the entire suction range.

5. A claw compressor as described in claim 1, wherein when a tangent surface of the first cylindrical surface at a first start end position located near the first limit position is defined as a first tangent surface, and a tangent surface of the second cylindrical surface at a second start end position located near the second limit position is defined as a second tangent surface, the suction port has inner wall surfaces that conform to the first tangent surface and the second tangent surface.

6. A claw compressor according to claim 5, wherein the first start position is the first limit position, and the second start position is the second limit position.

7. A design method for a claw compressor comprising: a first rotor that rotates about a first axis and has two first claws that protrude in a radial direction relative to the first axis; a second rotor that rotates in the opposite direction to the first rotor about a second axis that is parallel to the first axis and has two second claws that protrude in a radial direction relative to the second axis; and a housing that houses the first rotor and the second rotor and is formed with a suction port for taking in a fluid, wherein when the side of an imaginary cylinder described by the first claws of the rotating first rotor is defined as a first cylindrical surface, and the side of an imaginary cylinder described by the second claws of the rotating second rotor is defined as a second cylindrical surface, and the intersection lines between the overlapping first cylindrical surface and second cylindrical surface are defined as a suction side intersection line and a compression side intersection line, the suction side intersection line is the intersection line on the side of a suction chamber where fluid is taken in via the suction port, and the compression side intersection line is the intersection line on the side of a compression chamber where fluid is compressed, a first limit position being a position on the first cylindrical surface where a rear end of one of the first claw portions in the rotational direction exists when the rear end of the other first claw portion reaches the compression side intersection line; a second limit position being a position on the second cylindrical surface where a rear end of the other second claw portion in the rotational direction exists when the rear end of one of the second claw portions in the rotational direction reaches the compression side intersection line; a suction range being a range along the first cylindrical surface and the second cylindrical surface from the first limit position to the second limit position, including the suction side intersection line; and a position of the suction port being set to face the suction range.

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