JP5777733B2 - Vane type compressor - Google Patents

Description

  The present invention relates to a vane type compressor.

  Conventionally, a vane groove formed in one or a plurality of locations in a rotor portion of a rotor shaft (integrated with a cylindrical rotor portion that rotates in a cylinder and a shaft that transmits rotational force to the rotor portion) There has been proposed a general vane type compressor having a configuration in which a vane is inserted therein and the tip of the vane slides while contacting the inner peripheral surface of the cylinder (see, for example, Patent Document 1).

  In addition, the inner side of the rotor shaft is hollow and a vane fixed shaft is disposed therein. The vane is rotatably attached to the fixed shaft, and a pair of semi-cylindrical clamps are provided near the outer periphery of the rotor portion. There has also been proposed a vane type compressor in which a vane is held rotatably (swingable) with respect to a rotor portion via a member (hereinafter referred to as a bush) (see, for example, Patent Document 2).

Japanese Patent Laid-Open No. 10-252675 (summary, FIG. 1) JP 2000-352390 A (summary, FIG. 1)

  In a conventional general vane type compressor (for example, Patent Document 1 described above), since the vane direction is regulated by a vane groove formed in the rotor portion of the rotor shaft, the vane is always the same as the rotor portion. It is held so as to be inclined. For this reason, with the rotation of the rotor shaft, the angle formed by the vane and the cylinder inner peripheral surface changes. Therefore, in order for the vane tip to contact the entire circumference of the cylinder inner peripheral surface, it is necessary to configure the radius of the arc of the vane tip to be smaller than the radius of the cylinder inner peripheral surface.

  That is, when the vane tip is brought into contact with the entire circumference of the cylinder inner circumferential surface in a conventional general vane type compressor, the cylinder inner circumferential surface and the vane tip having different radii slide. For this reason, the lubrication state between the two parts (cylinder, vane) is not a fluid lubrication state in which an oil film is formed between the two parts and slides through the oil film, but a boundary lubrication state occurs. In general, the friction coefficient according to the lubrication state is about 0.001 to 0.005 in the fluid lubrication, but becomes very large in the boundary lubrication state, and is generally about 0.05 or more.

  Therefore, in the conventional general vane type compressor configuration, sliding resistance is increased by sliding the tip of the vane and the inner peripheral surface of the cylinder in the boundary lubrication state, and the efficiency of the compressor is increased by increasing the mechanical loss. There was a problem that a significant decrease would occur. Further, in the configuration of the conventional general vane compressor, there is a problem that the tip of the vane and the inner peripheral surface of the cylinder are easily worn, and it is difficult to ensure a long life.

  Then, there exists a conventional vane type compressor of patent documents 2 as one of those proposed in order to solve the above-mentioned subject. By adopting a configuration like the conventional vane type compressor described in Patent Document 2, the vane is rotationally supported at the center of the cylinder inner peripheral surface, so that the longitudinal direction of the vane is always the cylinder inner peripheral surface. The normal direction of That is, since the longitudinal direction of the vane is always directed to the center of the cylinder inner peripheral surface, the vane tip rotates along the inner peripheral surface of the cylinder. For this reason, a minute gap is maintained between the vane tip and the inner peripheral surface of the cylinder, and it is possible to operate without contact, no loss occurs due to sliding at the vane tip, and the vane tip and the cylinder inner A vane type compressor can be obtained in which the peripheral surface is not worn.

  However, since the conventional vane type compressor described in Patent Document 2 needs to configure the interior of the rotor shaft to be hollow, it is difficult to apply a rotational force to the rotor portion and to support the rotation of the rotor portion. More specifically, the conventional vane type compressor described in Patent Document 2 is provided with end plates (rotation base 2a, rotation holding member 2b) on both end faces of the rotor portion. The end plate (rotary base 2a) on one side has a disk shape because it needs to transmit power from the rotating shaft, and the rotating shaft is connected to the center of the end plate. Further, the other end plate (rotation holding member 2b) needs to be configured so as not to interfere with the rotation range of the vane fixed shaft (fixed shaft 1b) and the vane shaft support member (axial support member 1a). It is necessary to form a ring with a hole in the part. For this reason, the part which rotates and supports the end plate that rotates together with the rotor part needs to be configured to have a larger diameter than the rotating shaft (the rotating shaft 2c), and there is a problem that bearing sliding loss increases.

  In addition, since a narrow gap is formed between the rotor portion and the cylinder inner peripheral surface so that compressed gas (gaseous refrigerant) does not leak, high accuracy is required for the outer diameter and rotation center of the rotor portion. The However, in the conventional vane type compressor described in Patent Document 2, since the rotor part and the end plate are composed of separate parts, the distortion generated by the fastening of the rotor part and the end plate or the rotor part and the end plate There is a problem that the outer diameter of the rotor part and the accuracy of the rotation center are deteriorated due to the coaxial misalignment.

  Further, the conventional vane type compressor described in Patent Document 2 can theoretically be operated in a non-contact manner while maintaining a minute gap between the vane tip and the cylinder inner peripheral surface. . However, in Patent Document 2, since the relationship between the radius of the vane tip and the radius of the cylinder inner peripheral surface is not defined, depending on the machining tolerance of the vane and the cylinder, the width direction end of the vane tip and the inside of the cylinder There existed a subject that a surrounding surface might contact.

  The present invention has been made to solve the above-described problems, and reduces the bearing sliding loss of the rotating shaft and reduces leakage loss by forming a narrow gap between the rotor portion and the inner peripheral surface of the cylinder. In order to reduce this, a mechanism (mechanism in which the vane rotates around the center of the cylinder) necessary for the compression operation so that the arc at the tip of the vane and the normal line of the cylinder inner surface almost always coincide with each other is used. An object of the present invention is to provide a vane type compressor that can be realized by integrally forming a rotor part and a rotating shaft without using an end plate of the rotor part that causes deterioration of the outer diameter of the part and the rotational center accuracy.

A vane type compressor according to the present invention is substantially cylindrical and has a cylinder that is open at both ends in the axial direction, a cylinder head and a frame that closes both ends of the cylinder in the axial direction, and a rotational movement within the cylinder. In a vane type compressor having a cylindrical rotor portion and a rotor shaft having a shaft portion for transmitting rotational force to the rotor portion, and a plurality of vane portions installed in the rotor portion, the frame and the cylinder head A recess or ring-shaped groove whose outer peripheral surface is concentric with the inner peripheral surface of the cylinder is formed on the end surface on the cylinder side, and is slidably rotated along the outer peripheral surface to support the vane portion. The vane aligner portion has a partial ring shape with an outer peripheral surface having an arc shape, and each of the vane portions has its own vane aligner portion. Direction end in one revolution of the rotor portion overlap in the axial direction and the circumferential end portion of the other of said vane aligner portion, the circumferential end portion to each other of the axial direction overlapping the vane aligner unit in said groove The cylinders are provided so as not to interfere with each other by being displaced in the direction of the central axis of the cylinder.

In the vane type compressor according to the present invention, a recess or ring-shaped groove whose outer peripheral surface is concentric with the inner peripheral surface of the cylinder is formed on the cylinder side end surface of the frame and the cylinder head. A vane aligner portion that rotates slidably along the outer peripheral surface of the groove and supports the vane portion is provided. For this reason, a mechanism (mechanism in which the vane portion rotates around the center of the cylinder) necessary to perform the compression operation so that the arc of the tip of the vane portion and the normal line of the cylinder inner circumferential surface substantially coincide with each other is It can be realized with a configuration in which the portion and the shaft portion (rotating shaft) are integrated. Moreover, in the vane type compressor according to the present invention, each of the plurality of vane portions includes a circumferential end portion of its own vane aligner portion and a circumferential end portion of another vane aligner portion during one rotation of the rotor portion. The circumferential end portions of the vane aligner portions that overlap in the axial direction and overlap in the axial direction are provided so as not to interfere with each other by being shifted in the direction of the central axis of the cylinder in the groove . For this reason, the arc angle of the vane aligner portion can be increased.
Therefore, by supporting the rotating shaft with a small diameter, bearing sliding loss is reduced, and the accuracy of the outer diameter of the rotor part and the center of rotation is improved, so that a gap between the rotor part and the inner peripheral surface of the cylinder is formed with a narrow gap. Loss can be reduced.

It is a longitudinal cross-sectional view which shows the vane type compressor which concerns on Embodiment 1 of this invention. It is a disassembled perspective view which shows the compression element of the vane type compressor which concerns on Embodiment 1 of this invention. It is drawing which shows the 1st vane and 2nd vane of the compression element which concern on Embodiment 1 of this invention. It is a perspective view which shows the bush of the compression element which concerns on Embodiment 1 of this invention. It is a principal part enlarged view (plan view) which shows the vane part front-end | tip and cylinder inner peripheral surface vicinity. It is sectional drawing of the compression element which concerns on Embodiment 1 of this invention, and is sectional drawing along the II line | wire of FIG. It is explanatory drawing which shows the compression operation | movement of the compression element which concerns on Embodiment 1 of this invention, and is sectional drawing along the II line | wire of FIG. It is explanatory drawing for demonstrating rotation operation | movement of the vane aligner part which concerns on Embodiment 1 of this invention, and is sectional drawing along the II-II line | wire of FIG. It is a principal part enlarged view which shows the vane part vicinity of the vane which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating another example of the compression element which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating another example of the compression element which concerns on Embodiment 1 of this invention. It is explanatory drawing (sectional drawing) which shows the compression operation | movement of the compression element shown in FIG. It is drawing which shows the vane of the compression element of the vane type compressor which concerns on Embodiment 2 of this invention. It is drawing which shows another example of the vane of the compression element which concerns on Embodiment 2 of this invention. It is a disassembled perspective view which shows another example of the compression element which concerns on Embodiment 2 of this invention. It is drawing which shows the vane of the compression element of the vane type compressor which concerns on Embodiment 3 of this invention.

  Hereinafter, in each of the following embodiments, an example of a vane compressor according to the present invention will be described.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing a vane type compressor according to Embodiment 1 of the present invention. FIG. 2 is an exploded perspective view showing a compression element of the vane type compressor. FIG. 3 is a view showing a first vane and a second vane of the compression element, FIG. 3A is a plan view of the first vane and the second vane, and FIG. 3B is a first view. The front view of a vane and a second vane is shown. FIG. 4 is a perspective view showing a bush of the compression element. FIG. 5 is an enlarged view (plan view) of a main part showing the vane end of the compression element and the vicinity of the cylinder inner peripheral surface. In FIG. 1, solid arrows indicate the flow of gas (refrigerant), and broken arrows indicate the flow of the refrigerator oil 25. Hereinafter, the vane type compressor 200 according to the first embodiment will be described with reference to FIGS. 1 to 5.

  In the vane compressor 200, a compression element 101 and an electric element 102 that drives the compression element 101 are housed in an airtight container 103. The compression element 101 is disposed at the lower part of the sealed container 103. The electric element 102 is disposed on the upper portion of the sealed container 103 (more specifically, above the compression element 101). An oil sump 104 for storing the refrigerating machine oil 25 is provided at the bottom of the sealed container 103. A suction pipe 26 is attached to the side surface of the sealed container 103, and a discharge pipe 24 is attached to the upper surface.

  The electric element 102 that drives the compression element 101 is constituted by, for example, a brushless DC motor. The electric element 102 includes a stator 21 fixed to the inner periphery of the hermetic container 103, and a rotor 22 disposed inside the stator 21 and using a permanent magnet. When electric power is supplied to the coil of the stator 21 through the glass terminal 23 fixed to the sealed container 103 by welding or the like, a driving force is applied to the permanent magnet of the rotor 22 by the magnetic field generated in the stator 21, The rotor 22 rotates.

  The compression element 101 sucks and compresses low-pressure gas refrigerant from the suction pipe 26 into the compression chamber, and discharges the compressed refrigerant into the sealed container 103. The refrigerant discharged into the sealed container 103 passes through the electric element 102 and is discharged to the outside (the high pressure side of the refrigeration cycle) from the discharge pipe 24 fixed (welded) to the upper part of the sealed container 103. The compression element 101 has the following elements. In addition, the vane type compressor 200 according to the first embodiment shows that the number of vanes is two (the first vane 5 and the second vane 6).

(1) Cylinder 1: The overall shape is substantially cylindrical, and both ends in the central axis direction are open. Further, a part of the cylinder inner peripheral surface 1b formed in a substantially cylindrical shape is provided with a notch portion 1c penetrating in the direction of the central axis and curled outward (projected on the outer peripheral side). Yes. And in the notch part 1c, the suction port 1a is opened from the outer peripheral surface to the cylinder inner peripheral surface 1b. In addition, a discharge port 1d is formed at a position opposite to the suction port 1a with a nearest contact point 32 described later interposed therebetween. The discharge port 1d is formed in the vicinity of the closest contact point 32 and is formed on the side facing the frame 2 described later (see FIGS. 2 and 6). Further, an oil return hole 1e penetrating in the axial direction (a direction along the central axis of the cylinder inner peripheral surface 1b) is formed in the outer peripheral portion.

(2) Frame 2: A cylindrical member is provided on the upper part of a substantially disk-shaped member, and its longitudinal section is substantially T-shaped. The substantially disk-shaped member closes one opening (upper side in FIG. 2) of the cylinder 1. On the cylinder 1 side end surface (the lower surface in FIG. 2) of this substantially disk-shaped member, a bottomed cylindrical recess 2a that is concentric with the cylinder inner peripheral surface 1b of the cylinder 1 is formed. A vane aligner portion 5c of the first vane 5 and a vane aligner portion 6c of the second vane 6, which will be described later, are inserted into the recess 2a, and are supported (rotated and slid by the vane aligner bearing portion 2b which is the outer peripheral surface of the recess 2a. Supported freely). Further, the frame 2 has a through hole so as to penetrate the substantially cylindrical member from the end surface of the substantially disk-shaped member on the cylinder 1 side. The through-hole is provided with a main bearing portion 2c. The main bearing portion 2c supports a rotating shaft portion 4b of the rotor shaft 4 described later. The frame 2 has a discharge port 2d communicating with the discharge port 1d. Further, a discharge valve 27 (shown only in FIG. 2) covering the opening of the discharge port 2d and a discharge for regulating the opening degree of the discharge valve 27 are provided on the surface of the substantially disk-shaped member opposite to the cylinder 1. A valve presser 28 (shown only in FIG. 2) is attached. In addition, you may form the recessed part 2a as a groove part (ring-shaped groove | channel) concentric with the cylinder internal peripheral surface 1b.

(3) Cylinder head 3: A cylindrical member is provided at the lower part of a substantially disk-shaped member, and the longitudinal section is substantially T-shaped. The substantially disk-shaped member closes the other opening (lower side in FIG. 2) of the cylinder 1. On the cylinder 1 side end surface (upper surface in FIG. 2) of this substantially disk-shaped member, a bottomed cylindrical concave portion 3a concentric with the cylinder inner peripheral surface 1b of the cylinder 1 is formed. A vane aligner portion 5d of the first vane 5 and a vane aligner portion 6d of the second vane 6, which will be described later, are inserted into the recess 3a and supported by the vane aligner bearing portion 3b which is the outer peripheral surface of the recess 3a. The cylinder head 3 is formed with a through hole so as to penetrate the substantially cylindrical member from the cylinder 1 side end surface of the substantially disk-shaped member. A main bearing 3c is provided in the through hole. The main bearing portion 3c supports a rotating shaft portion 4c of the rotor shaft 4 described later. In addition, you may form the recessed part 3a as a groove part (ring-shaped groove) concentric with the cylinder internal peripheral surface 1b.

(4) Rotor shaft 4: A substantially cylindrical rotor portion 4a that rotates in a center axis that is eccentric from the center axis of the cylinder 1 in the cylinder 1, and the upper portion of the rotor portion 4a so as to be concentric with the rotor portion 4a. The rotary shaft portion 4b provided and the rotary shaft portion 4c provided at the lower portion of the rotor portion 4a so as to be concentric with the rotor portion 4a are provided. The rotor portion 4a, the rotating shaft portion 4b, and the rotating shaft portion 4c are formed as an integral structure. As described above, the rotary shaft portion 4b and the rotary shaft portion 4c are supported by the main bearing portion 2c and the main bearing portion 3c. The rotor portion 4a is formed with a plurality of substantially cylindrical through holes (bush holding portions 4d and 4e and vane relief portions 4f and 4g) penetrating in the axial direction. Among these through holes, the bush holding portion 4d and the vane relief portion 4f communicate with each other at the side surface, and the bush holding portion 4e and the vane relief portion 4g communicate with each other at the side surface portion. Further, the bush holding portion 4d and the bush holding portion 4e are open on the outer peripheral portion side of the rotor portion 4a. Further, the axial ends of the vane escape portion 4 f and the vane escape portion 4 g communicate with the recess 2 a of the frame 2 and the recess 3 a of the cylinder head 3. Further, the bush holding portion 4d, the bush holding portion 4e, the vane relief portion 4f, and the vane relief portion 4g are disposed at substantially symmetrical positions with respect to the rotation axis of the rotor portion 4a (see also FIG. 6 described later). .

  Further, an oil pump 31 (shown only in FIG. 1) as described in, for example, Japanese Patent Application Laid-Open No. 2009-264175 is provided at the lower end portion of the rotor shaft 4. The oil pump 31 sucks the refrigeration oil 25 in the oil sump 104 using the centrifugal force of the rotor shaft 4. This oil pump 31 is provided in the axial center portion of the rotor shaft 4 and communicates with an oil supply passage 4h extending in the axial direction, and between the oil supply passage 4h and the recess 2a, between the oil supply passage 4i and between the oil supply passage 4h and the recess 3a. Is provided with an oil supply passage 4j. An oil drain hole 4k (shown only in FIG. 1) is provided at a position above the main bearing portion 2c of the rotating shaft portion 4b.

(5) First vane 5: The vane portion 5a, the vane aligner portion 5c, and the vane aligner portion 5d are integrally formed. The vane portion 5a is a plate-like member having a substantially square shape when viewed from the side, and has substantially the same dimensions as the cylinder 1 in the central axis direction of the cylinder inner peripheral surface 1b. The vane portion 5a is formed in an arc shape in which a vane tip portion 5b (tip portion on the side protruding from the rotor portion 4a) located on the cylinder inner peripheral surface 1b side of the cylinder 1 is convex outward in plan view. . The radius of the arc shape of the vane tip 5b is configured to be substantially equal to the radius of the cylinder inner peripheral surface 1b of the cylinder 1 (see FIG. 5). Further, in the vicinity of the end of the vane portion 5a opposite to the vane tip portion 5b (hereinafter referred to as an inner peripheral end), the vane portion 5a is connected to the upper surface (the surface facing the frame 2) via the connection portion 5e. A vane aligner portion 5c having a partial ring shape (a part of the ring shape, an arc shape) is provided. Similarly, a partial ring-shaped vane aligner portion 5d that supports the vane portion 5a via the connecting portion 5f is provided on the lower surface (the surface facing the cylinder head 3) in the vicinity of the inner peripheral end of the vane portion 5a. It has been. Here, the vane portion 5a, the vane aligner portion 5c, and the vane aligner portion 5d are formed so that the vane longitudinal direction of the vane portion 5a and the normal direction of the arc of the vane tip portion 5b are the centers of arcs that form the vane aligner portions 5c and 5d. It is formed to pass. In addition, after forming the vane part 5a, the vane aligner part 5c, and the vane aligner part 5d separately, the vane aligner part 5c and the vane aligner part 5d may be integrally attached to the vane part 5a.

  Further, the vane aligner portion 5c of the first vane 5 does not come into contact with each other in one rotation with the circumferential end portion 6g of the vane aligner portion 6c of the second vane 6 described later. It is provided in the recess 2a of the frame 2 (see FIGS. 1 and 3). Specifically, the length of the connecting portion 5e that connects the vane portion 5a and the vane aligner portion 5c is different from the length of the connecting portion 6e that connects the vane portion 6a and the vane aligner portion 6c described later (the connecting portion 6e). Longer than). The vane aligner portion 5c of the first vane 5 and the vane aligner portion 6c of the second vane 6 are more specifically (in the vicinity of the circumferential end portion 5g of the vane aligner portion 5c and the circumferential end of the vane aligner portion 6c. And the vicinity of the portion 6g) is provided in the recess 2a of the frame 2 so as to overlap with a gap in the central axis direction of the cylinder inner peripheral surface 1b. Similarly, the vane aligner portion 5d of the first vane 5 is arranged such that its circumferential end portion 5h does not contact each other in one rotation with the circumferential end portion 6h of the vane aligner portion 6d of the second vane 6 described later. The cylinder head 3 is provided in the recess 3a (see FIGS. 1 and 3). Specifically, the length of the connecting portion 5f that connects the vane portion 5a and the vane aligner portion 5d is different from the length of the connecting portion 6f that connects the vane portion 6a and the vane aligner portion 6d described later (the connecting portion 6f). Longer than). The vane aligner portion 5d of the first vane 5 and the vane aligner portion 6d of the second vane 6 (more specifically, the vicinity of the circumferential end portion 5h of the vane aligner portion 5d and the circumferential end of the vane aligner portion 6d) And the vicinity of the portion 6h) are provided in the recess 3a of the cylinder head 3 so as to overlap with each other via a gap in the central axis direction of the cylinder inner peripheral surface 1b.

(6) Second vane 6: The vane portion 6a, the vane aligner portion 6c, and the vane aligner portion 6d are integrally formed. The vane portion 6a is a plate-like member having a substantially square shape when viewed from the side, and has substantially the same dimensions as the cylinder 1 in the central axis direction of the cylinder inner peripheral surface 1b. The vane portion 6a is formed in an arc shape in which a vane tip portion 6b (tip portion protruding from the rotor portion 4a) located on the cylinder inner peripheral surface 1b side of the cylinder 1 is convex outward in plan view. . The radius of the arc shape of the vane tip 6b is configured to be substantially equal to the radius of the cylinder inner peripheral surface 1b of the cylinder 1 (see FIG. 5). Further, in the vicinity of the end of the vane portion 6a opposite to the vane tip portion 6b (hereinafter referred to as an inner peripheral end), the vane portion 6a is connected to the upper surface (the surface facing the frame 2) via the connection portion 6e. Is provided with a partial ring-shaped vane aligner portion 6c. Similarly, a partial ring-shaped vane aligner portion 6d that supports the vane portion 6a via a connecting portion 6f is provided on the lower surface (the surface facing the cylinder head 3) in the vicinity of the inner peripheral side end portion of the vane portion 6a. It has been. Here, the vane portion 6a, the vane aligner portion 6c, and the vane aligner portion 6d are configured such that the vane longitudinal direction of the vane portion 6a and the normal direction of the arc of the vane tip portion 6b are the centers of arcs that form the vane aligner portions 6c and 6d. It is formed to pass. In addition, after forming the vane part 6a, the vane aligner part 6c, and the vane aligner part 6d separately, you may attach the vane aligner part 6c and the vane aligner part 6d integrally to the vane part 6a.

  Further, as described above, the vane aligner portion 6c of the second vane 6 does not contact the circumferential end portion 6g of the vane aligner portion 5c of the first vane 5 during one rotation. Thus, it is provided in the recess 2a of the frame 2 (see FIGS. 1 and 3). Specifically, the length of the connecting portion 6e that connects the vane portion 6a and the vane aligner portion 6c is shorter than the length of the connecting portion 5e that connects the vane portion 5a and the vane aligner portion 5c. The vane aligner portion 5c of the first vane 5 and the vane aligner portion 6c of the second vane 6 are more specifically (in the vicinity of the circumferential end portion 5g of the vane aligner portion 5c and the circumferential end of the vane aligner portion 6c. And the vicinity of the portion 6g) is provided in the recess 2a of the frame 2 so as to overlap with a gap in the central axis direction of the cylinder inner peripheral surface 1b. Similarly, the vane aligner portion 6d of the second vane 6 has a cylinder end 6h so that the circumferential end portion 6h does not come into contact with the circumferential end portion 5h of the vane aligner portion 5d of the first vane 5 in one rotation. It is provided in the recess 3a of the head 3 (see FIGS. 1 and 3). Specifically, the length of the connecting portion 6f that connects the vane portion 6a and the vane aligner portion 6d is shorter than the length of the connecting portion 5f that connects the vane portion 5a and the vane aligner portion 5d. The vane aligner portion 5d of the first vane 5 and the vane aligner portion 6d of the second vane 6 (more specifically, the vicinity of the circumferential end portion 5h of the vane aligner portion 5d and the circumferential end of the vane aligner portion 6d) And the vicinity of the portion 6h) are provided in the recess 3a of the cylinder head 3 so as to overlap with each other via a gap in the central axis direction of the cylinder inner peripheral surface 1b.

(7) Bushes 7 and 8: A substantially semi-cylindrical member is configured as a pair. The bush 7 is rotatably inserted into the bush holding portion 4d of the rotor portion 4a while sandwiching the vane portion 5a of the first vane 5. The bush 8 is rotatably inserted into the bush holding portion 4e of the rotor portion 4a in a state where the vane portion 6a of the second vane 6 is sandwiched. That is, when the vane portion 5a of the first vane 5 slides between the bushes 7, the first vane 5 is supported so as to be rotatable and movable (slidable) with respect to the rotor portion 4a. Moreover, the 1st vane 5 can be rock | fluctuated when the bush 7 rotates within the bush holding | maintenance part 4d of the rotor part 4a. Similarly, when the vane portion 6a of the second vane 6 slides between the bushes 8, the second vane 6 is supported so as to be rotatable and movable (slidable) with respect to the rotor portion 4a. Moreover, the 2nd vane 6 can rock | fluctuate because the bush 8 rotates within the bush holding | maintenance part 4e of the rotor part 4a.

  Further, the bush 7 according to the first embodiment has the bush arcuate portion 7b (the arcuate outer peripheral portion of the bush 7), the end portion on the cylinder inner peripheral surface 1b side being cut out flat, and the bush cutout surface 7c being Is formed. Further, the end of the bushing arc portion 7b opposite to the cylinder inner peripheral surface 1b is also cut out flat to form a bushing cutout surface 7d. By forming the bush notch surface 7c, even when the outer diameter of the rotor portion 4a is reduced, the bush 7 is prevented from protruding from the outer periphery of the rotor portion 4a when the bush 7 rotates in the bush holding portion 4d. (In other words, the bush 7 can be prevented from contacting the cylinder inner peripheral surface 1b). Similarly, in the bush 8 according to the first embodiment, the end of the bush circular arc portion 8b (the arc-shaped outer peripheral portion of the bush 8) on the cylinder inner peripheral surface 1b side is cut out flat, and the bush cut-out surface 8c. Is formed. Further, the end of the bushing arc portion 8b opposite to the cylinder inner peripheral surface 1b is also cut out flat to form a bushing cutout surface 8d. By forming the bush notch surface 8c, even when the outer diameter of the rotor portion 4a is reduced, the bush 8 is prevented from protruding from the outer periphery of the rotor portion 4a when the bush 8 rotates in the bush holding portion 4d. (In other words, the bush 8 can be prevented from coming into contact with the cylinder inner peripheral surface 1b).

  Here, the vane aligner portions 5c, 5d, 6c, 6d, the vane aligner bearing portions 2b, 3b of the recesses 2a, 3a, the bush holding portions 4d, 4e, and the bushes 7, 8 correspond to the vane angle adjusting means in the present invention. To do.

(Description of operation)
Next, the operation of the vane compressor 200 according to the first embodiment will be described.
FIG. 6 is a cross-sectional view of the compression element according to Embodiment 1 of the present invention. This figure is a cross-sectional view taken along the line II in FIG. 1, and shows a state in which the rotation angle of the rotor portion 4a (rotor shaft 4) is 90 °, as will be described later with reference to FIG.

As shown in FIG. 6, the rotor portion 4 a of the rotor shaft 4 and the cylinder inner peripheral surface 1 b of the cylinder 1 are in closest contact at one place (the closest point 32 shown in FIG. 6).
Here, when the radius of the vane aligner bearing portions 2b and 3b is r _a (see FIG. 8 described later) and the radius of the cylinder inner peripheral surface 1b is r _c (see FIG. 6), the vane aligner of the first vane 5 is used. The distance X _v (see FIG. 3) between the outer peripheral surface side of the portions 5c and 5d and the vane tip 5b is set as in the following expression (1).
(Equation 1)
X _v = r _c −r _a −δ (1)

δ is the minimum gap between the vane tip 5b and the cylinder inner peripheral surface 1b (see FIG. 5), and by setting _Xv as shown in the equation (1), the first vane 5 has the cylinder inner peripheral surface 1b. It will rotate without touching. Here, [delta] is set to X _v to as small as possible to minimize a leakage of the refrigerant from the vane tip 5b. The relationship of the formula (1) is the same for the second vane 6, and the second vane 6 is maintained while maintaining a narrow gap between the vane tip 6b of the second vane 6 and the cylinder inner peripheral surface 1b. It will rotate.

The minimum gap δ between the vane tip 5b and the cylinder inner peripheral surface 1b is assumed to be a gap between the substantially central portion of the vane tip 5b, 6b in the width direction and the cylinder inner peripheral surface 1b. Therefore, the cylinder inner peripheral surface 1b and vane tip 5b, the machining tolerances of 6b is larger than the radius _{r c} of the vane tip 5b, 6b of the radius _{r v} (see FIG. 5) is the cylinder inner peripheral surface 1b Sometimes it becomes. In such a case, there is a concern that the end portions in the width direction of the vane tip portions 5b and 6b come into contact with the cylinder inner peripheral surface 1b. Therefore, vane tip 5b, as 6b of radius _{r v} relationship (see FIG. 5) and the radius _{r c} of the cylinder inner peripheral surface 1b satisfies the following formula (2), the cylinder 1, the first vane 5 And the second vane 6 is designed.
(Equation 2)
r _v ≦ r _c (2)

Furthermore, too small than a r _v r _{c, (see} FIG. 5) a gap [delta] _m between the vane tip 5b, the widthwise end portion of 6b and the cylinder inner peripheral surface 1b since increases, increased leakage losses There is a problem to do. Therefore, it is desirable to design the cylinder 1, the first vane 5, and the second vane 6 so that δ _m and δ satisfy the expression (3) (see FIG. 5).
(Equation 3)
δ _m ≦ 2δ (3)

In order to satisfy the expression (3), the widths of the vane tip portions 5b and 6b are set to t _v (see FIG. 5), α = r _v / r _c , β = t _v / 2r _c , δ ^* = δ / r _c Then, the cylinder 1, the first vane 5, and the second vane 6 may be designed so as to satisfy the dimensional relationship of the following expression (4).
(Equation 4)
(-1+ (1-β ² ) + α (1- (1- (β / α) ² ) ^0.5 )) ≧ δ ^* (4)

  It should be noted that the dimensional relations of the expressions (2) and (3) are not related to the vane type compressor according to the first embodiment, and all the vanes that operate while maintaining a certain clearance between the vane tip and the cylinder inner peripheral surface. The present invention is also applicable to a type compressor (for example, see Patent Document 2).

  As described above, the first vane 5 and the cylinder inner peripheral surface 1b, and the second vane 6 and the cylinder inner peripheral surface 1b each maintain a narrow gap, so that there are three spaces (suction chamber 9) in the cylinder 1. Intermediate chamber 10 and compression chamber 11) are formed. A suction port 1a communicating with the low pressure side of the refrigeration cycle is opened in the suction chamber 9 through a notch 1c. The compression chamber 11 communicates with a discharge port 2 d formed in the frame 2 via a discharge port 1 d provided in the cylinder 1. The discharge port 2d is closed by the discharge valve 27 except during discharge. In FIG. 6 (rotation angle 90 °), the notch 1c is provided from the vicinity of the closest point 32 to the range of point A where the vane tip 5b of the first vane 5 and the cylinder inner peripheral surface 1b face each other. It has been.

  Therefore, the intermediate chamber 10 communicates with the suction port 1a up to a rotation angle of 90 °, but thereafter has a rotation angle range that does not communicate with either the suction port 1a or the discharge port 1d, and then communicates with the discharge port 1d. In addition, 7a and 8a shown in FIG.4 and FIG.6 are the bush centers of the bushes 7 and 8, and are the rotation centers of the bushes 7 and 8, respectively.

First, the rotational operation of the vane type compressor 200 according to the first embodiment will be described.
When the rotating shaft portion 4b of the rotor shaft 4 receives the rotational power from the electric element 102 as the driving portion, the rotor portion 4a rotates in the cylinder 1. Along with the rotation of the rotor part 4a, the bush holding parts 4d and 4e arranged near the outer periphery of the rotor part 4a move on the circumference with the rotor shaft 4 as the rotation axis (center axis). The pair of bushes 7 held in the bush holding portion 4d and the vane portion 5a of the first vane 5 slidably held between the pair of bushes 7 also rotate together with the rotor portion 4a. Similarly, the pair of bushes 8 held in the bush holding portion 4e and the vane portion 6a of the second vane 6 slidably held between the pair of bushes 8 also rotate together with the rotor portion 4a. To do.

  The first vane 5 and the second vane 6 receive a centrifugal force due to rotation, and the vane aligner portions 5c and 6c and the vane aligner portions 5d and 6d are pressed against the vane aligner bearing portions 2b and 3b, respectively, while sliding. The vane aligner bearing portions 2b and 3b rotate around the central axis. Here, as described above, the vane aligner bearing portions 2b and 3b and the cylinder inner peripheral surface 1b are concentric. For this reason, the first vane 5 and the second vane 6 rotate around the center of the cylinder inner peripheral surface 1b. Then, the bushes 7 and 8 rotate around the bush centers 7a and 8a in the bush holding portions 4d and 4e so that the longitudinal direction of the vane portion 5a of the first vane 5 is directed to the cylinder center.

  In the operation described above, the side surfaces of the bush 7 and the vane portion 5a of the first vane 5 and the side surfaces of the bush 8 and the vane portion 6a of the second vane 6 slide with each other. Further, the bush holding portion 4d and the bush 7 and the bush holding portion 4e and the bush 8 of the rotor shaft 4 slide on each other.

  FIG. 7 is an explanatory diagram showing a compression operation of the compression element according to Embodiment 1 of the present invention. FIG. 7 is a cross-sectional view taken along the line II of FIG. Hereinafter, the manner in which the volumes of the suction chamber 9, the intermediate chamber 10, and the compression chamber 11 change with the rotation of the rotor portion 4a (rotor shaft 4) will be described with reference to FIG. In FIG. 7, for the sake of simplicity, the suction port 1a, the cutout portion 1c, and the discharge port 1d are omitted, and the suction port 1a and the discharge port 1d are indicated as “suction” and “discharge” by arrows, respectively. First, with the rotation of the rotor shaft 4, low-pressure refrigerant flows from the suction pipe 26 into the suction port 1a. Here, in describing the volume change of each space (suction chamber 9, intermediate chamber 10, compression chamber 11), the rotation angle of the rotor portion 4a (rotor shaft 4) is defined as follows. First, a state where the sliding portion (contact portion) between the first vane 5 and the cylinder inner peripheral surface 1b of the cylinder 1 coincides with the closest point 32 is defined as “angle 0 °”. In FIG. 7, the positions of the first vane 5 and the second vane 6 in the state of “angle 0 °”, “angle 45 °”, “angle 90 °”, and “angle 135 °”, and the suction at that time The state of the chamber 9, the intermediate chamber 10, and the compression chamber 11 is shown.

  The arrow shown in the “angle 0 °” diagram of FIG. 7 is the rotational direction of the rotor shaft 4 (clockwise in FIG. 7). However, in other drawings, an arrow indicating the rotation direction of the rotor shaft 4 is omitted. Further, in FIG. 7, the state after “angle 180 °” is not shown because when “angle 180 °” is reached, the first vane 5 and the second vane 6 are switched at “angle 0 °”. This is because the same compression operation is performed from “angle 0 °” to “angle 135 °” thereafter.

  At the “angle of 0 °” in FIG. 7, the space on the right side partitioned by the nearest contact point 32 and the second vane 6 is the intermediate chamber 10 and communicates with the suction port 1a via the notch 1c. Inhale refrigerant. The space on the left side partitioned by the closest contact 32 and the second vane 6 becomes the compression chamber 11 communicating with the discharge port 1d.

  At “angle 45 °” in FIG. 7, the space partitioned by the first vane 5 and the closest contact point 32 becomes the suction chamber 9 communicating with the suction port 1a through the notch 1c. The space partitioned by the first vane 5 and the second vane 6 is an intermediate chamber 10. In this state, the intermediate chamber 10 communicates with the suction port 1a through the notch 1c. Since the volume of the intermediate chamber 10 becomes larger than that at the “angle 0 °”, the gas suction is continued. The space partitioned by the second vane 6 and the nearest contact point 32 is the compression chamber 11, and the volume of the compression chamber 11 becomes smaller than that at the “angle 0 °”, and the refrigerant is compressed and its pressure gradually increases. .

  At “angle 90 °” in FIG. 7, the vane tip 5b of the first vane 5 overlaps with the point A on the cylinder inner peripheral surface 1b of the cylinder 1, so that the intermediate chamber 10 does not communicate with the suction port 1a. Thereby, the suction of the gas in the intermediate chamber 10 is completed. In this state, the volume of the intermediate chamber 10 is substantially maximum. The volume of the compression chamber 11 becomes even smaller than when the angle is 45 °, and the refrigerant pressure rises. The volume of the suction chamber 9 becomes larger than that at the “angle 45 °”, and the suction is continued.

  At “angle 135 °” in FIG. 7, the volume of the intermediate chamber 10 becomes smaller than that at “angle 90 °”, and the refrigerant pressure increases. Further, the volume of the compression chamber 11 becomes smaller than that at the “angle 90 °”, and the pressure of the refrigerant rises. The volume of the suction chamber 9 becomes larger than that at the “angle 90 °”, and the suction is continued.

  Thereafter, as the second vane 6 approaches the discharge port 1d, the pressure in the compression chamber 11 increases. When the pressure in the compression chamber 11 exceeds the high pressure of the refrigeration cycle (including the pressure necessary to open the discharge valve 27), the discharge valve 27 is opened, and the refrigerant in the compression chamber 11 flows into the discharge port 1d and the discharge port 2d. Then, it is discharged into the sealed container 103 (see FIG. 1). The refrigerant discharged into the sealed container 103 passes through the electric element 102 and is discharged to the outside (the high pressure side of the refrigeration cycle) from the discharge pipe 24 fixed (welded) to the upper part of the sealed container 103. Therefore, the pressure in the sealed container 103 is a high discharge pressure.

  When the second vane 6 passes through the discharge port 1d, a little high-pressure refrigerant remains in the compression chamber 11 (a loss occurs). When the compression chamber 11 disappears at an “angle of 180 °” (not shown), the high-pressure refrigerant changes to a low-pressure refrigerant in the suction chamber 9. At “angle 180 °”, the suction chamber 9 moves to the intermediate chamber 10, the intermediate chamber 10 moves to the compression chamber 11, and the compression operation is repeated thereafter.

  In this way, the volume of the suction chamber 9 gradually increases due to the rotation of the rotor portion 4a (rotor shaft 4), and continues to suck gas. Thereafter, the flow proceeds to the intermediate chamber 10, but the volume gradually increases to the middle, and the gas suction is further continued. On the way, the volume of the intermediate chamber 10 is maximized and is not communicated with the suction port 1a. Thereafter, the volume of the intermediate chamber 10 gradually decreases and compresses the gas. Thereafter, the intermediate chamber 10 moves to the compression chamber 11 and continues to compress the gas. The gas compressed to a predetermined pressure pushes up the discharge valve 27 through the discharge port 1d and the discharge port 2d, and is discharged into the sealed container 103.

  FIG. 8 is an explanatory diagram for explaining the rotation operation of the vane aligner unit according to the first embodiment of the present invention, and is a cross-sectional view taken along the line II-II in FIG. 1. In addition, in FIG. 8, rotation operation | movement of the vane aligner parts 5c and 6c is shown. Further, the arrow shown in the “angle 0 °” diagram of FIG. 8 is the rotation direction of the vane aligner portions 5c and 6c (clockwise in FIG. 8). However, in other drawings, the arrows indicating the rotation direction of the vane aligner portions 5c and 6c are omitted.

  The rotation of the rotor shaft 4 causes the vane portion 5a of the first vane 5 and the vane portion 6a of the second vane 6 to rotate around the central axis of the cylinder 1 (FIG. 7). Accordingly, as shown in FIG. 8, the vane aligner portions 5c and 6c are supported by the vane aligner bearing portion 2b and rotate around the central axis of the cylinder inner peripheral surface 1b in the recess 2a. This operation is the same for the vane aligner portions 5d and 6d that rotate while being supported by the vane aligner bearing portion 2b in the recess 3a.

Next, the refueling operation during the refrigerant compression operation will be described.
As the rotor shaft 4 rotates in the above refrigerant compression operation, the refrigeration oil 25 is sucked up from the oil sump 104 by the oil pump 31 and sent out to the oil supply path 4h, as indicated by broken line arrows in FIG. The refrigerating machine oil 25 sent out to the oil supply passage 4h passes through the oil supply passage 4i and is sent out to the recess 3a of the cylinder head 3 through the recess 2a of the frame 2 and the oil supply passage 4j.

  The refrigerating machine oil 25 fed to the recesses 2a and 3a lubricates the vane aligner bearing portions 2b and 3b, and a part thereof is supplied to the vane relief portions 4f and 4g communicating with the recesses 2a and 3a. Here, since the pressure in the sealed container 103 is a high discharge pressure, the pressures in the recesses 2a and 3a and the vane relief portions 4f and 4g are also discharge pressures. A part of the refrigerating machine oil 25 fed to the recesses 2 a and 3 a is supplied to the main bearing portion 2 c of the frame 2 and the main bearing portion 3 c of the cylinder head 3.

  The refrigerating machine oil 25 sent out to the vane relief parts 4f and 4g flows as follows.

  FIG. 9 is a main part enlarged view showing the vicinity of the vane portion of the vane according to Embodiment 1 of the present invention. 9 is an enlarged view of a main part showing the vicinity of the vane portion 5a of the first vane 5 in FIG. 6, and the arrows shown by solid lines in the drawing indicate the flow of the refrigerating machine oil 25.

  As described above, since the pressure of the vane escape portion 4f is the discharge pressure and is higher than the pressure of the suction chamber 9 and the intermediate chamber 10, the refrigerating machine oil 25 lubricates the sliding portion between the side surface of the vane portion 5a and the bush 7. However, it is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force. The refrigerating machine oil 25 is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force while lubricating the sliding portion between the bush 7 and the bush holding portion 4d of the rotor shaft 4. A part of the refrigerating machine oil 25 fed to the intermediate chamber 10 flows into the suction chamber 9 while sealing the gap between the vane tip 5b and the cylinder inner peripheral surface 1b of the cylinder 1.

  Although FIG. 9 shows the case where the space partitioned by the first vane 5 is the suction chamber 9 and the intermediate chamber 10, the rotation proceeds and the space partitioned by the first vane 5 is The same applies to the compression chamber 11. Even when the pressure in the compression chamber 11 reaches the same discharge pressure as the pressure of the vane escape portion 4f, the refrigerating machine oil 25 is sent out toward the compression chamber 11 by centrifugal force. Although the above operation is shown for the first vane 5, the same operation is performed for the second vane 6.

  In the above-described oil supply operation, as shown in FIG. 1, the refrigerating machine oil 25 supplied to the main bearing portion 2 c is discharged into the space above the frame 2 through the gap of the main bearing portion 2 c, and then the outer periphery of the cylinder 1. It is returned to the oil sump 104 through the oil return hole 1e provided in the section. Further, the refrigerating machine oil 25 supplied to the main bearing portion 3c is returned to the oil sump 104 through the gap of the main bearing portion 3c. Further, the refrigerating machine oil 25 sent to the suction chamber 9, the intermediate chamber 10 and the compression chamber 11 through the vane relief portions 4f and 4g was finally discharged together with the refrigerant from the discharge port 2d to the space above the frame 2. Thereafter, the oil is returned to the oil sump 104 through an oil return hole 1 e provided in the outer peripheral portion of the cylinder 1. Of the refrigerating machine oil 25 sent out to the oil supply passage 4 h by the oil pump 31, the surplus refrigerating machine oil 25 is discharged from the oil drain hole 4 k above the rotor shaft 4 into the space above the frame 2, and then cylinder 1 is returned to the oil sump 104 through an oil return hole 1e provided in the outer periphery of the oil reservoir 1.

  As described above, in the vane type compressor 200 according to the first embodiment, the vane portions 5a and 6a are rotatably supported by the rotor portion 4a, and the vane aligner portions 5c and 6c are supported in the recess 2a of the frame 2. The vane aligner portions 5 d and 6 d are rotatably supported in the recess 3 a of the cylinder head 3. Therefore, a mechanism (first vane 5 and second vane required for performing the compression operation so that the arcs of the vane tip 5b and the vane tip 6b and the normal line of the cylinder inner peripheral surface 1b substantially coincide with each other at all times. 6 can be realized by the rotor shaft 4 in which the rotor portion 4a and the rotating shaft portions 4b and 4c are integrated.

  Further, in the vane compressor 200 according to the first embodiment, the vane aligner portion 5c of the first vane 5 and the vane aligner portion 6c of the second vane 6 have a gap in the height direction in the recess 2a. The vane aligner portion 5d of the first vane 5 and the vane aligner portion 6d of the second vane 6 overlap with each other via a gap in the height direction in the recess 3a. Arranged in a relationship. That is, during one rotation, the circumferential end 5g of the vane aligner portion 5c of the first vane 5 and the circumferential end 6g of the vane aligner portion 6c of the second vane 6 do not interfere (contact). Is provided. Similarly, during one rotation, the circumferential end 5h of the vane aligner portion 5d of the first vane 5 and the circumferential end 6h of the vane aligner portion 6d of the second vane 6 do not interfere (contact). Is provided. For this reason, the arc angle of the vane aligner portions 5c, 5d, 6c, 6d can be increased, and the effect of improving the reliability of the vane aligner portion as a partial bearing can be obtained.

  For this reason, the vane compressor 200 according to the first embodiment can reduce the bearing sliding loss by being able to support the rotating shaft portions 4b and 4c with the small-diameter main bearing portions 2c and 3c, and the rotor portion 4a. The accuracy of the outer diameter and the rotation center can be improved. Therefore, the vane compressor 200 according to the first embodiment can reduce leakage loss by forming a narrow gap between the rotor portion 4a and the cylinder inner peripheral surface 1b. The compressor 200 can be obtained.

Although the vane type compressor 200 in the case where the number of vanes is two has been described above, the present invention can be implemented even if the number of vanes is three or more.
FIG. 10 is an explanatory diagram for explaining another example of the compression element according to Embodiment 1 of the present invention. 10A is a plan view of the first vane 5, the second vane 6 and the third vane 107, and FIG. 10B is a plan view of the first vane 5, the second vane 6 and A front view of the third vane 107 is shown.

  The third vane 107 includes the same components as the first vane 5 and the second vane 6. In other words, in the vicinity of the inner peripheral side end of the vane portion 107a in the third vane 107, a partial ring-shaped vane aligner portion 107c is provided on the upper surface (the surface facing the frame 2) via the connection portion 107e. Yes. Similarly, a vane aligner portion 107d having a partial ring shape is provided on the lower surface (the surface facing the cylinder head 3) in the vicinity of the inner peripheral end of the vane portion 107a via a connecting portion 107f.

  In the first vane 5, the second vane 6, and the third vane 107, the connection portion 5 e of the first vane 5, the connection portion 6 e of the second vane 6, and the connection portion 107 e of the third vane 107. Are different in length. For this reason, the vane aligner portion 5c of the first vane 5, the vane aligner portion 6c of the second vane 6, and the vane aligner portion 107c of the third vane 107 are overlapped with the recess 2a of the frame 2 via a gap. Can be placed. That is, during one rotation, the circumferential end portion 5g of the vane aligner portion 5c of the first vane 5, the circumferential end portion 6g of the vane aligner portion 6c of the second vane 6, and the vane aligner portion of the third vane 107. The circumferential ends 107g of the 107c can be prevented from interfering (contacting) with each other. In the first vane 5, the second vane 6, and the third vane 107, the connection portion 5 f of the first vane 5, the connection portion 6 f of the second vane 6, and the connection of the third vane 107. The lengths of the portions 107f are different from each other. For this reason, the vane aligner portion 5d of the first vane 5, the vane aligner portion 6d of the second vane 6, and the vane aligner portion 107d of the third vane 107 overlap with the recess 3a of the cylinder head 3 via a gap. Can be arranged as follows. That is, during one rotation, the circumferential end portion 5h of the vane aligner portion 5d of the first vane 5, the circumferential end portion 6h of the vane aligner portion 6d of the second vane 6, and the vane aligner portion of the third vane 107. The circumferential end 107h of 107d can be prevented from interfering (contacting) with each other.

  Thus, even when the number of vanes is three or more, the vane aligner portions of the vanes can be arranged in the recesses 2a and 3a so as to overlap with each other through a gap, so that the arc angle of each vane aligner portion is increased. Thus, the reliability of the vane aligner as a partial bearing can be improved.

  In the above, in the first vane 5 and the second vane 6, the vane longitudinal direction of the vane portions 5a and 6a and the normal direction of the arc of the vane tip portions 5b and 6b are substantially the same direction. For example, the first vane 5 and the second vane 6 may be configured as follows.

FIG. 11 is an explanatory diagram for explaining yet another example of the compression element according to Embodiment 1 of the present invention. FIG. 11 is a cross-sectional view taken along the line II-II in FIG.
In FIG. 11, B has shown the vane longitudinal direction of the vane parts 5a and 6a. Moreover, C has shown the normal line direction of the circular arc of vane front-end | tip part 5b, 6b. That is, the vane portions 5a and 6a are provided to be inclined in the direction B with respect to the vane aligner portions 5c, 5d, 6c, and 6d. The normal C of the arc of the vane tip portions 5b and 6b is inclined with respect to the vane longitudinal direction B, and is formed so as to pass through the center of the arc forming the vane aligner portions 5c, 5d, 6c, and 6d. Yes.

  Also in the configuration shown in FIG. 11, as shown in FIG. 12, the compression operation can be performed in a state where the arcs of the vane tip portions 5b and 6b and the normal line of the cylinder inner peripheral surface 1b of the cylinder 1 always coincide with each other during the rotation. It is. Further, by tilting the normal C of the arc of the vane tip portions 5b and 6b with respect to the vane longitudinal direction B, the arc length of the vane tip portions 5b and 6b can be increased, and the seal length is increased. . For this reason, it is also possible to further reduce the leakage loss at the vane tip portions 5b and 6b.

Embodiment 2. FIG.
In each vane, when the circumferential end portion of its own vane aligner portion does not interfere (contact) with the circumferential end portion of the vane aligner portion of another vane, it is limited to the shape of the vane shown in the first embodiment. Instead, for example, each vane may be configured as follows. Note that items not particularly described in the second embodiment are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.

  FIG. 13 is a drawing showing a vane of a compression element of a vane type compressor according to Embodiment 2 of the present invention. FIG. 13A shows a plan view and a front view of the first vane 5, and FIG. 13B shows a plan view and a front view of the second vane 6.

  As shown in FIG. 13A, the vane aligner portions 5c and 5d of the first vane 5 are stepped so that the arc angles are different along the height direction (the central axis direction of the cylinder inner peripheral surface 1b). It has a shape. Similarly, as shown in FIG. 13B, the vane aligner portions 6c and 6d of the second vane 6 also have different arc angles along the height direction (the central axis direction of the cylinder inner peripheral surface 1b). It has a stepped shape. The vane aligner portion 5c of the first vane 5 and the vane aligner portion 6c of the second vane 6 arranged in the recess 2a of the frame 2 are located in the height direction (the cylinder inner circumference) In the direction of the central axis of the surface 1b). Further, in the vane aligner portion 5d of the first vane 5 and the vane aligner portion 6d of the second vane 6 arranged in the recess 3a of the cylinder head 3, the portion where the arc angle is the largest is in the height direction (in the cylinder In the direction of the central axis of the peripheral surface 1b).

  For this reason, it arrange | positions in the recessed part 2a of the flame | frame 2 so that the location where the circular arc angle of the vane aligner part 5c becomes the largest and the location where the circular arc angle of the vane aligner part 6c becomes the largest may overlap. During rotation, the circumferential end 5g of the vane aligner portion 5c of the first vane 5 and the circumferential end 6g of the vane aligner portion 6c of the second vane 6 can be prevented from interfering with each other. Further, by disposing the vane aligner portion 5d in the recess 3a of the cylinder head 3 so that the portion where the arc angle is the largest and the portion where the arc angle is the largest of the vane aligner portion 6d overlap each other through a gap, 1 During rotation, the circumferential end 5h of the vane aligner portion 5d of the first vane 5 and the circumferential end 6h of the vane aligner portion 6d of the second vane 6 can be prevented from interfering with each other. In addition, the locations other than the location where the arc angle of the vane aligner portion 5c is the largest and the locations other than the location where the arc angle of the vane aligner portion 6c is the largest are arranged so as not to overlap in the central axis direction. Similarly, the portion other than the portion where the arc angle of the vane aligner portion 5d becomes the largest and the portion other than the portion where the arc angle of the vane aligner portion 6d becomes the largest are arranged so as not to overlap in the central axis direction.

  Furthermore, in the second embodiment, as shown in FIG. 13A, the first vane 5 has a vane aligner portion 5c and a vane aligner portion 5d that are symmetrical with respect to the vane portion 5a. . As shown in FIG. 13B, the second vane 6 has a vane aligner portion 6c and a vane aligner portion 6d that are symmetrical with respect to the vane portion 6a.

  As described above, also in the vane compressor 200 configured as in the second embodiment, the arc angle of the vane aligner portions 5c, 5d, 6c, and 6d can be increased, and the vane aligner portion is reliable as a partial bearing. The effect which improves property is acquired.

  In the second embodiment, since the vane aligner portions 5c, 5d, 6c, and 6d are stepped, the bearing areas (vanes) of the vane aligner portions 5c, 5d, 6c, and 6d are compared to the first embodiment. The contact area with the aligner bearing portions 2b and 3b) can be increased. For this reason, the surface pressure which acts on the vane aligner parts 5c, 5d, 6c, and 6d can be reduced, and the reliability as a partial bearing can be further improved. Furthermore, since the width in the height direction of the vane aligner portions 5c, 5d, 6c, and 6d can be increased over a wide range, the rigidity is improved and the strength reliability can be improved.

  Further, in the second embodiment, the vane aligner portion 5c and the vane aligner portion 5d are symmetrical with respect to the vane portion 5a, and the vane aligner portion 6c and the vane aligner portion 6d are symmetrical with respect to the vane portion 6a. For this reason, the load applied to the vane aligner portion 5c and the load applied to the vane aligner portion 5d can be canceled with each other, and the occurrence of a rotational moment in the vertical direction around the vane portion 5a can be suppressed. The effect of preventing the frame 2 and the end face of the cylinder head 3 from coming into contact with the corner is obtained. Similarly, the load applied to the vane aligner portion 6c and the load applied to the vane aligner portion 6d can be canceled each other, and the occurrence of a rotational moment in the vertical direction around the vane portion 6a can be suppressed. The effect of preventing the frame 2 and the end face of the cylinder head 3 from coming into contact with the corner is obtained.

  In the second embodiment, the vane aligner portions 5c, 5d, 6c, and 6d are stepped, so that the vane aligner portions 5c, 5c, and 5c are formed along the height direction (the central axis direction of the cylinder inner peripheral surface 1b). The arc angles of 5d, 6c, and 6d were made different. For example, the vane aligner portions 5c, 5d, 6c, and 6d are formed as shown in FIG. 14, and the vane aligner portions 5c, 5d, and 6c are formed along the height direction (the central axis direction of the cylinder inner peripheral surface 1b). , 6d may have different arc angles.

FIG. 14 is a drawing showing another example of a vane of a compression element according to Embodiment 2 of the present invention. FIG. 14A shows a plan view and a front view of the first vane 5, and FIG. 14B shows a plan view and a front view of the second vane 6.
As shown in FIG. 14, the vane aligner portions 5 c, 5 d, 6 c, and 6 d have straight end portions in the circumferential direction so that the arc angles are different along the height direction (the central axis direction of the cylinder inner peripheral surface 1 b). The shape is inclined in a curved or curved manner. Thus, even if the vane aligner portions 5c, 5d, 6c, and 6d are formed, the same effect as described above (FIG. 13) can be obtained.

  Also in the second embodiment, as described in FIGS. 11 and 12 of the first embodiment, the vane longitudinal direction of the vane portions 5a and 6a is set to the normal line of the arc of the vane tip portions 5b and 6b. A tilted configuration may be used.

  Further, in the second embodiment, the vane type compressor 200 in the case where the number of vanes is two has been described. However, as in the first embodiment, even if the number of vanes is three or more as shown in FIG. It is the same structure and the same effect is acquired.

Embodiment 3 FIG.
FIG. 16 is a diagram illustrating a vane of a compression element of the vane type compressor according to the third embodiment. FIG. 16A is a plan view of the first vane 5, the second vane 6, the third vane 107, and the fourth vane 108, and FIG. The perspective view of the vane 5, the 2nd vane 6, the 3rd vane 107, and the 4th vane 108 is shown. Note that items not specifically described in the third embodiment are the same as those in the first or second embodiment, and the same functions and configurations are described using the same reference numerals.

  As shown in FIG. 16, among the four vanes, the vanes arranged symmetrically with respect to the central axis (that is, the combination of the first vane 5 and the third vane 107, or the second vane 6). And the fourth vane 108) are arranged at the same height, and the vane aligner portions 6c and 108c are arranged farther from the cylinder 1 than the vane aligner portions 5c and 107c. The arc angle of the vane aligner portions 6c and 108c is configured to be larger than the arc angle of the vane aligner portions 5c and 107c.

  Further, in the third embodiment, the first vane 5 has a vane aligner portion 5c and a vane aligner portion 5d that are symmetrical with respect to the vane portion 5a. As for the 2nd vane 6, the vane aligner part 6c and the vane aligner part 6d are symmetrical with respect to the vane part 6a. In the third vane 107, the vane aligner portion 107c and the vane aligner portion 107d are symmetrical with respect to the vane portion 107a. In the fourth vane 108, the vane aligner portion 108c and the vane aligner portion 108d are symmetrical with respect to the vane portion 108a.

  Thus, when the number of vanes is four or more and a plurality of vanes, the height of the vane aligner portions of the vanes arranged symmetrically with respect to the central axis is made the same so that the number of overlap of the vane aligner portions can be reduced. Even if the number of vanes is half, the arc angle can be increased. For this reason, the reliability as a partial bearing of a vane aligner part is improved, and the effect of reducing the increase in height by making a vane aligner part into an overlapping structure is acquired.

Further, the circumferential end surfaces 5g, 5h of the vane aligner portions 5c, 5d of the first vane 5 and the circumferential end surfaces 107g, 107h of the vane aligner portions 107c, 107d of the third vane 107 are the second in one rotation. The configuration must be such that it does not interfere with the connecting portions 6e and 6f of the vane 6 and the connecting portions 108e and 108f of the fourth vane 108.
On the other hand, the vane aligner portions 6c and 6d of the second vane 6 and the vane aligner portions 108c and 108d of the fourth vane 108 may be configured such that the circumferential ends do not interfere with each other during one rotation.
Therefore, the arc angle of the vane aligner portion of the second vane 6 and the fourth vane 108 can be made larger than the arc angle of the vane aligner portion of the first vane 5 and the third vane 107, The bearing length (that is, the height of the vane aligner portion) can be reduced by the amount.

  In the first to third embodiments, the oil pump 31 using the centrifugal force of the rotor shaft 4 has been described. However, any oil pump may be used, for example, as described in JP-A-2009-62820. A positive displacement pump may be used as the oil pump 31.

  1 cylinder, 1a suction port, 1b cylinder inner surface, 1c notch, 1d discharge port, 1e oil return hole, 2 frame, 2a recess, 2b vane aligner bearing, 2c main bearing, 2d discharge port, 3 cylinder Head, 3a recess, 3b vane aligner bearing part, 3c main bearing part, 4 rotor shaft, 4a rotor part, 4b rotating shaft part, 4c rotating shaft part, 4d bush holding part, 4e bush holding part, 4f vane relief part, 4g Vane relief portion, 4h oil supply passage, 4i oil supply passage, 4j oil supply passage, 4k oil discharge hole, 5 first vane, 5a vane portion, 5b vane tip portion, 5c vane aligner portion, 5d vane aligner portion, 5e connection portion, 5f connecting portion, 5g circumferential end, 5h circumferential end, 6 second vane, 6a vane portion, 6b vane End, 6c vane aligner, 6d vane aligner, 6e connection, 6f connection, 6g circumferential end, 6h circumferential end, 7 bush, 7a bush center, 7b bush arc, 7c bush notch , 7d Bush notch surface, 8 Bush, 8a Bush center, 8b Bush arc, 8c Bush notch surface, 8d Bush notch surface, 9 Suction chamber, 10 Intermediate chamber, 11 Compression chamber, 21 Stator, 22 Rotor , 23 Glass terminal, 24 Discharge pipe, 25 Refrigerating machine oil, 26 Suction pipe, 27 Discharge valve, 28 Discharge valve retainer, 31 Oil pump, 32 Nearest contact point, 101 Compression element, 102 Electric element, 103 Sealed container, 104 Oil sump, 107 Third vane, 107a vane, 107b vane tip, 107c vane aligner, 107 d Vane aligner part, 107e connection part, 107f connection part, 107g circumferential end part, 107h circumferential end part, 108 fourth vane, 108a vane part, 108b vane tip part, 108c vane aligner part, 108d vane aligner part, 108e connection part, 108f connection part, 108g circumferential end, 108h circumferential end, 109 bush, 200 vane compressor.

Claims (12)

A substantially cylindrical cylinder with both axial ends open;
A cylinder head and a frame for closing both axial ends of the cylinder;
A rotor shaft having a cylindrical rotor portion that rotates in the cylinder and a shaft portion that transmits a rotational force to the rotor portion;
In the vane type compressor having a plurality of vane portions installed in the rotor portion,
A recess or ring-shaped groove whose outer peripheral surface is concentric with the inner peripheral surface of the cylinder is formed on the cylinder-side end surface of the frame and the cylinder head,
A slidably rotating along the outer peripheral surface, provided with a vane aligner portion that supports the vane portion,
The vane aligner portion is a partial ring shape whose outer peripheral surface has an arc shape,
In each of the vane portions, the circumferential end portion of the vane aligner portion overlaps with the circumferential end portion of the other vane aligner portion in the axial direction during one rotation of the rotor portion, and overlaps in the axial direction. A vane type compressor characterized in that circumferential end portions of the vane aligner portion are arranged in the groove so as not to interfere with each other by being shifted in the direction of the central axis of the cylinder.   2. The vane compressor according to claim 1, wherein each of the vane portions is inserted into the recess so that the vane aligner portions overlap with each other via a gap in the direction of the central axis. The vane aligner portion has a stepped shape so that the arc angle varies along the direction of the central axis,
Each of the vane portions is different in the direction of the central axis in the portion of the vane aligner portion inserted into the same concave portion in the direction of the central axis, and the portion of the largest circular arc angle is in the direction of the central axis. The vane type compressor according to claim 1, wherein the vane type compressor is inserted into the recess so as to overlap with a gap. The vane aligner portion has a shape in which a circumferential end thereof is inclined linearly or curvilinearly so that a circular arc angle is different along the direction of the central axis.
Each of the said vane parts is provided so that the circumferential direction edge part of the own vane aligner part may not interfere with the circumferential direction edge part of the other said vane aligner part. Vane type compressor. The number of the vane portions is an even number of four or more is, according to claim 2, characterized in that a said vane aligner portion of the vane portions disposed symmetrically with respect to prior Symbol central axis at the same height The vane type compressor described in 1. The arc angle of the vane aligner portion disposed most apart against the Cylinders are vane compressor according to claim 5, wherein greater than the arc angle of the vane aligner unit otherwise.   The vane aligner portion provided on the same vane portion includes the vane aligner portion provided on the surface facing the frame and the vane aligner portion provided on the surface facing the cylinder head. The vane compressor according to any one of claims 1 to 6, wherein the vane compressor is symmetrical with respect to the vane portion. Is intended to hold the vane portion always such that a gap is formed between the inner peripheral surface of the a tip portion of the front Symbol vane unit cylinder, the radius of the tip of the vane portion r _v, when a radius of the inner peripheral surface of the cylinder was set to r _{c,
r v} ≦ r _c
The vane type compressor according to any one of claims 1 to 7, wherein the dimensional relationship is satisfied. The width of the tip portion of the vane portion is t _v , and the minimum gap between the tip portion of the vane portion and the inner peripheral surface of the cylinder is δ, α = r _v / r _c , β = t _v / 2r _{c, δ} ^* = when the δ / _{r c,}
(-1+ (1-β ² ) + α (1- (1- (β / α) ² ) ^0.5 )) ≧ δ ^*
The vane type compressor according to claim 8, wherein the dimensional relationship is satisfied.   The vane type compressor according to any one of claims 1 to 9, wherein the vane aligner portion is attached integrally with the vane portion or formed integrally with the vane portion.   The vane compressor according to any one of claims 1 to 10, wherein the vane unit is supported so as to be rotatable and slidable with respect to the rotor unit.   The rotor part is formed with a substantially cylindrical bush holding part penetrating in the axial direction. A pair of substantially semi-cylindrical bushes are inserted into the bush holding part, and the vane part is sandwiched between the bushes. The vane type compressor according to claim 11, wherein the vane compressor is supported so as to be rotatable and slidable with respect to the rotor portion.

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