Claw compressor and method for designing claw compressor

Abstract

To provide a claw compressor capable of improving efficiency by reducing pressure loss in a suction passage, and a design method of the claw compressor.SOLUTION: When a first limit position L2 is defined as a position on the first cylindrical surface S1 where the end portion of the other first claw portion on the rear side in the rotation direction is present when the end portion of the one first claw portion on the rear side in the rotation direction reaches the compression-side intersection line P1, the suction port faces a suction range R, and an opening area of the suction port is 20% or more of an area of the suction range R, where the suction range R is a range from the first limit position L2 to a second limit position S2 including the suction-side intersection line P2 along the first cylindrical surface L1 and the second cylindrical surface P1, and the second limit position P2 is a position on the second cylindrical surface S1 at which the end portion of the other second lug portion on the rear side in the rotation direction is present when the end portion of the one second lug portion on the rear side in the rotation direction reaches the compression-side intersection line S2.SELECTED DRAWING: Figure 9

Description

[Technical Field]

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

[0002] A claw compressor has a pair of rotors with hook-shaped claws housed in a housing. The rotors rotate at the same speed in opposite directions without contact while maintaining a predetermined clearance, and 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 mainly as vacuum pumps or blowers (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

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

[0004] When a claw compressor is used to compress steam generated by a steam generating heat pump that is 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. [Means for solving the problem]

[0006] In order to solve the above problems, the claw compressor and the design method for the claw compressor of the present disclosure employ the following measures. 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 accommodates the first rotor and the second rotor and has a suction port formed therein for taking in a fluid. 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 defined as a suction port. The compression-side intersection line is the intersection line on the side of the compression chamber where the fluid is compressed, and the 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 is defined as a first limit position, and the position on the second cylindrical surface where the 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 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 drawn by the first claws of the rotating first rotor, a second cylindrical surface as a side surface of an imaginary cylinder that is drawn 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. [Effects of the Invention]

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

[0009] [Figure 1] FIG. 1 is a perspective view of a claw compressor according to a first embodiment of the present disclosure. [Figure 2] 1 is a front view of a claw compressor according to a first embodiment of the present disclosure (a cover is omitted). FIG. [Figure 3]FIG. 2 is a perspective view of a first cylindrical surface and a second cylindrical surface. [Figure 4] FIG. 4 is a partially enlarged view of an end portion of a first claw portion. [Figure 5] FIG. 10 is a partially enlarged view of the end of the second claw portion. [Figure 6] This is a front view of a claw compressor (lid omitted) in which each rotor is housed at a first angular position (top view), a second angular position (middle view), and a third angular position (bottom view). [Figure 7] 1 is a front view of a claw compressor according to a first embodiment of the present disclosure (a cover is omitted). FIG. [Figure 8] 1 is a front view of a claw compressor according to a first embodiment of the present disclosure (a cover is omitted). FIG. [Figure 9] 1 is a front view of a claw compressor according to a first embodiment of the present disclosure (a cover is omitted). FIG. [Figure 10] FIG. 2 is a perspective view of the first and second cylindrical surfaces with the suction areas indicated. [Figure 11] 2 is a cross-sectional view of a first housing of the claw compressor according to the first embodiment. FIG. [Figure 12] FIG. 10 is a cross-sectional view of a first housing of a claw compressor according to a second embodiment. [Figure 13] FIG. 10 is a cross-sectional view of a first housing of a claw compressor according to a second embodiment. [Figure 14] FIG. 10 is a cross-sectional view of a first housing of a claw compressor according to a second embodiment. [Figure 15] FIG. 10 is a cross-sectional view of a first housing of a claw compressor according to a third embodiment. DETAILED DESCRIPTION OF THE INVENTION

[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 up-down 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 up-down direction, the front-rear direction, and the left-right direction are substantially perpendicular to one another. Furthermore, these directions are terms used for the sake of easy understanding of the explanation, and do not limit the actual posture 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 FIGS. 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 receiving portion 11X corresponding to the front portion, a second receiving portion 11Y corresponding to the rear portion, and legs . The first housing portion 11X, together with the lid 13, forms a rotor housing portion 16 that houses the first rotor 30 and the second rotor 40. The second accommodating portion 11Y, together with the second housing 12, forms a gear accommodating portion 17 that accommodates a timing gear. The second accommodating portion 11Y itself and the second housing 12 itself accommodate bearings, seal members, and the like.

[0015] Two shafts are provided spaced apart in the left-right direction and extend in the front-rear direction so as to penetrate first housing 11 from rotor accommodating portion 16 to gear accommodating portion 17. In this case, the first shaft is connected to first rotor 30, and the second shaft is connected to second rotor 40. For example, the first shaft is a drive shaft having a first axis X1 (see FIG. 2) extending in the front-rear direction as its central axis, to which a driving force is input from an external device (not shown). On the other hand, the second shaft is a driven shaft having a second axis X2 (see FIG. 2) extending in the front-rear direction as its central axis, to which a driving force is transmitted from the first shaft via a timing gear housed in a gear housing portion 17.

[0016] 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] The first accommodating portion 11X of the first housing 11 is provided with at least one suction port 11a. 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 communicates with the suction chamber C1, which will be described later. The suction port 11a is provided in the upper part of the first housing portion 11X. In the case of FIG. 1, three suction ports 11a facing upward are provided in the upper part of the first housing 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. 2, the first accommodating portion 11X of the first housing 11 defines an accommodating chamber C0 by an inner wall 11w. A pair of first and second rotors 30 and 40 are accommodated in the accommodating 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-rear direction, and has two first claws 31. The first claw portions 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 around the first axis X1.

[0021] The second rotor 40 is a component having the same thickness as the first rotor 30 in the front-rear direction, and has two second claws 41. The second claw portions 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 around 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] 2 and 3, the inner wall 11w of the first storage section 11X that defines the storage chamber C0 has a shape in which two cylindrical surfaces are partially overlapped. The shape is slightly larger (one size larger) than the outer shapes of the partially overlapping first cylindrical surface S1 and second cylindrical surface S2 in the vertical and horizontal directions. Here, the first cylindrical surface S1 is defined as the side surface 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 surface 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, 41 of the rotors 30, 40 run along the inner wall 11w of the first housing portion 11X with a predetermined clearance (see FIGS. 4 and 5) between them. The front-rear dimension of each of the cylindrical surfaces S1, S2 corresponds to the thickness of each of the rotors 30, 40. The front-rear dimension of the inner wall 11w of the first accommodating portion 11X is approximately the same as the front-rear dimension of each of the cylindrical surfaces S1, S2.

[0024] As shown in FIG. 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 a suction side intersection line L1 and a compression side intersection line L2. The suction-side intersection line L1 is an intersection line located on the side of a suction chamber C1, which will be described later, and is located at the top in FIG. The compression-side intersection line L2 is an intersection line different from the suction-side intersection line L1, an intersection line located on the compression chamber C2 side described later, and is located at the bottom in FIG.

[0025] 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 where the first claw portion 31 does not come into contact with the inner wall 11w. The ends of the first claws 31 include 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 claws 31 is formed in an arc shape along the first cylindrical surface S1. In other words, the range from the front end 31a to the rear end 31b of the first claws 31 is approximately parallel to the inner wall 11w of the first accommodating portion 11X (the clearance is approximately constant).

[0026] 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 where the second claw portion 41 does not come into contact with the inner wall 11w. The ends of the second claws 41 include a front end 41a located in front of the second rotor 40 in the direction of rotation and a rear end 41b located in the rear of the direction of rotation. The area from the front end 41a to the rear end 41b of the second claws 41 is arc-shaped along the second cylindrical surface S2. That is, the area from the front end 41a to the rear end 41b of the second claws 41 is approximately parallel to the inner wall 11w of the first housing portion 11X (the clearance is approximately constant).

[0027] Figure 6 shows the first rotor 30 and the second rotor 40 at a first angular position (top figure), the first rotor 30 and the second rotor 40 at a second angular position rotated a predetermined angle from the first angular position (middle figure), 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 figure). As shown in Figure 6, the storage chamber C0 defined by the inner wall 11w is divided into a suction chamber C1, a compression chamber C2, and a transfer chamber C3 by the first rotor 30 and the second rotor 40. Note that the transfer chamber C3 may not be defined depending on the angular positions of the first rotor 30 and the second rotor 40. Furthermore, the suction chamber C1, the compression chamber C2, and the transfer 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 communicate with each other via the aforementioned clearance and the gap between the rotors 30, 40. The suction chamber C1 is a space where the fluid taken into the storage chamber C0 through the suction port 11a first reaches. The suction chamber C1 is in communication with the suction port 11a. The compression chamber C2 is a space where the fluid is compressed. The compression chamber C2 is in communication with the discharge port 13b. As the first rotor 30 and the second rotor 40 rotate, the volume of the compression chamber C2 gradually decreases, and the fluid present in the compression chamber C2 is gradually compressed. The transfer chamber C3 is a space located between the suction chamber C1 and the compression chamber C2, and 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 housing portion 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 housing portion 11X. The transfer chamber C3 is a space simply for transporting a fluid along the rotational direction, and is not a space 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 transfer 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 transfer chamber C3 communicates with the previously defined compression chamber C2 and switches to the compression chamber C2. Then, 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] [Intake port location and opening area] 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] 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 where the rear end 31b of the other first claw portion 31 exists is defined as the first limit position P1. In other words, the position on the first cylindrical surface S1 where 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. Although the first limit position P1 is shown as a dot in FIG. 7, it is actually a line extending in the front-rear direction.

[0031] 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 where 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 where 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. Although the second limit position P2 is shown as a dot in FIG. 8, it is actually a line extending in the front-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. Note that 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 the 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 storage portion 11X facing the suction range R. This allows the suction port 11a to be connected to a position where fluid can be taken into the suction chamber C1 from the outside until just 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 openings formed by the suction ports 11a is set to 20% or more of the area of ​​the suction range R. Specifically, the area of ​​the openings formed by the suction ports 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 allows the opening area of ​​the suction port 11a facing the suction chamber C1 to be as large as possible, making it possible to take in a large amount of fluid 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 the suction range R, and the total area of ​​the openings formed by the suction ports 11a is 20% or more of the area of ​​the suction range R. Note that these are merely examples, and configurations other than those of the examples may be used as long as the intake port 11a is provided at a position facing the intake range R and the total area of ​​the openings formed by the intake port 11a is 20% or more of the area of ​​the intake range R.

[0036] Example 1 FIG. 11 shows a cross section (a cross section taken along a cutting plane 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 embodiment 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 (the cross-sectional shape in a cut surface perpendicular to the vertical direction) is, for example, circular, but may be a shape other than circular.

[0037] The first suction port 11a faces the vicinity of the first limit position P1. The vicinity of the first limit position P1 is, for example, 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. It is sufficient that at least a portion of the first suction port 11a overlaps with this range in the left-right direction. The second suction port 11a faces the vicinity of the second limit position P2. The vicinity of the second limit position P2 is, for example, 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. It is sufficient that at least a portion of the second suction port 11a overlaps with this range in the left-right direction. The third suction port 11a faces the vicinity of 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, which includes the position of the suction-side intersection line L1, as shown in Fig. 9. In Fig. 9, the first suction port 11a is located approximately in the center of the first housing 11 in the left-right direction.

[0038] Note that any of the first to third suction ports 11a may be omitted, and the remaining suction ports 11a may be enlarged. For example, the centrally located third suction port 11a may be omitted, and the first and second suction ports 11a located on the left and right may be provided with the necessary opening area, or the left and right first and second suction ports 11a may be omitted, and the centrally located third suction port 11a may be provided with the necessary opening area.

[0039] <Example 2> 12 to 14 show a cross section (a cross section taken along a cutting plane perpendicular to the front-rear direction) of the first housing 11 (first accommodating portion 11X). As shown in FIGS. 12 to 14, the claw compressor 1 of this embodiment has one suction port 11a extending in the left-right direction. The intake port 11a faces substantially the entire intake 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] At this time, as shown in FIG. 13, by inclining the inner wall surface 11a1 and gradually expanding the intake flow path along the direction of fluid flow, it is possible to prevent a sudden expansion of the flow path 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, it is preferable that the inclined inner wall surface 11a1 is aligned along the first tangent surface and the second tangent surface. This makes it easy to determine a shape of the suction port 11a that can effectively reduce pressure loss. Furthermore, it is possible to prevent a sudden expansion of the flow passage area and make the suction port 11a and, therefore, the claw compressor 1, more compact in the vertical direction.

[0042] Example 3 FIG. 15 shows a cross section (a cross section taken along a cutting 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 intake 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. Also, 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 makes it easy to determine a shape of the suction port 11a that can effectively reduce pressure loss. Furthermore, this prevents a sudden expansion of the flow passage area and allows the suction port 11a and, therefore, the claw compressor 1 to be made more compact in the vertical direction. Furthermore, when the first starting end position Q1 coincides with the first limit position P1 and the second starting end position Q2 coincides with the second limit position P2, the intake port 11a faces almost the entire intake range R, as in Example 2.

[0045] [effect] 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. This 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 substantially the entire suction range R, it is possible to secure a maximum area for taking in the fluid, and it is possible to take in the fluid for a long period of time. Furthermore, compared to providing multiple suction ports 11a, the effort required to process multiple suction ports 11a is eliminated, and there is no need to branch the piping according to the number of suction ports 11a, thereby reducing 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 that conforms to the first tangent surface and the second tangent surface, thereby preventing a sudden expansion of the area of ​​the flow path through which the fluid flows toward the suction chamber C1, and reducing pressure loss in the suction path. Furthermore, it is possible to easily determine a shape of the suction port 11a that can effectively reduce pressure loss, thereby making it possible to make the claw compressor 1 compact while preventing a sudden increase in the flow passage area. Furthermore, when the first starting end position is set to the first limit position and the second starting end position is set to the second limit position, the intake port faces almost the entire intake range, thereby maximizing the area for taking in fluid and enabling fluid to be taken in for a long period of time.

[0051] [Note] 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 a suction 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 a suction 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. A position on the first cylindrical surface where a rear end (31 b) of one of the first claws in the rotational direction of the other first claw portion exists when a rear end (31 b) of the other first claw portion in the rotational direction 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 one of the second claws in the rotational direction of the other second claw portion exists when a rear end (41 b) of the one second claw portion in the rotational direction of the other second claw portion exists when a rear end (41 b) of the one second claw portion in the rotational direction reaches the compression side intersection line is defined as a second limit position (P2). When 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 (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 its opening area 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] The suction port faces at least the suction range near the first limit position and / or the second limit position, so that the suction port can be provided over as wide an area as possible, which ensures a large area for taking in fluid and allows 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] Since the suction port faces almost the entire suction range, it is possible to maximize the area for taking in fluid, and it is possible to take in fluid for a long period of time. Furthermore, compared to providing multiple suction ports, the effort required to process multiple suction ports is eliminated, and there is no need to branch the piping according to the number of suction ports, thereby reducing manufacturing costs.

[0060] In the claw compressor according to the fifth aspect of the present disclosure, in the first aspect, when the 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 the 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 inner wall surfaces that conform to the first tangent surface and the second tangent surface. This prevents a sudden expansion of the area of ​​the flow path through which the fluid flows toward the suction chamber, thereby reducing pressure loss in the suction path. Furthermore, it is possible to easily determine a shape of the suction port that can effectively reduce pressure loss, thereby preventing a sudden increase in the flow path area and making the claw compressor more compact.

[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] The first start end position is set to the first limit position, and the second start end position is set to the second limit position, thereby preventing a sudden expansion of the area of ​​the flow path through which the fluid flows toward the suction chamber, and reducing pressure loss in the suction path. Furthermore, it is possible to easily determine a shape of the suction port that can effectively reduce pressure loss, thereby preventing a sudden increase in the flow path area and making the claw compressor more compact. Furthermore, since the suction port faces almost the entire suction range, the area for taking in the fluid can be maximized, and the 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 drawn by the first claws of the rotating first rotor as a first cylindrical surface; defining a side surface of an imaginary cylinder that is drawn 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. [Explanation of symbols]

[0065] 1 Claw compressor 10. Housing 11 First Housing 11X First storage compartment 11a Intake port 11a1 Inner wall surface 11w inner wall 11Y Second Storage Unit 12 Second Housing 13 Lid 13b Discharge port 14 Legs 16 Rotor housing 17 Gear housing 30 First rotor (male rotor) 31 1st claw part 31a front end 31b rear end 40 Second rotor (female rotor) 41 2nd claw part 41a front end 41b rear end C0 Containment Cell C1 suction chamber C2 compression chamber C3 Transport room L1 Suction side intersection line L2 Compression side intersection line P1 First limit position P2 Second limit position Q1 1st starting position Q2 2nd starting position R Inhalation range S1 First cylindrical surface S2 2nd cylindrical surface X1 1st axis X2 2nd axis

Claims

1. 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; a housing that accommodates the first rotor and the second rotor and has an intake port formed therein for taking in a fluid; Equipped with 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, 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, and 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 suction chamber side into which fluid is taken in through the suction port, the compression-side intersection line is the intersection line on the compression chamber side where the fluid is compressed, a position on the first cylindrical surface at which a rear end of one of the first claw portions in the rotation direction is present when the rear end of the other first claw portion reaches the compression side intersection line is defined as a first limit position, a position on the second cylindrical surface at which a rear end of one of the second claw portions in the rotation direction is present when the rear end of the other second claw portion reaches the compression side intersection line is defined as a second limit position, When a range from the first limit position to the second limit position including the suction side intersection line along the first cylindrical surface and the second cylindrical surface is defined as a suction range, the intake port faces the intake area; The opening area of ​​the intake port is set to 20% or more of the area of ​​the intake range. Claw compressor.

2. 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.

2. The claw compressor of claim 1.

3. The suction port faces the vicinity of the suction side intersection line within the suction range.

3. The claw compressor according to claim 1 or 2.

4. The suction port faces substantially the entire suction range.

2. The claw compressor of claim 1.

5. 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 intake port has an inner wall surface along the first contact surface and the second contact surface.

2. The claw compressor of claim 1.

6. The first start position is the first limit position, The second start position is the second limit position.

6. The claw compressor of claim 5.

7. 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; a housing that accommodates the first rotor and the second rotor and has an intake port formed therein for taking in a fluid; A method for designing a claw compressor comprising: 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, 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, and 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 suction chamber side into which fluid is taken in through the suction port, the compression-side intersection line is the intersection line on the compression chamber side that compresses the fluid, a position on the first cylindrical surface at which a rear end of one of the first claw portions in the rotation direction is present when the rear end of the other first claw portion reaches the compression side intersection line is defined as a first limit position, a position on the second cylindrical surface at which a rear end of one of the second claw portions in the rotation direction is present when the rear end of the other second claw portion reaches the compression side intersection line is defined as a second limit position, a range from the first limit position to the second limit position, including the suction side intersection line, along the first cylindrical surface and the second cylindrical surface, is defined as an suction range, The position of the intake port is set so as to face the intake area. How to design a claw compressor.

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